DE202020102529U1 - Link chain with a chain width for a belt transmission - Google Patents

Abstract

Link chain (1) with a chain width (2) for a belt transmission (3), comprising at least the following components:
- A plurality of tabs (4,5,6), namely short tabs (4) and long tabs (5,6); and
a corresponding number of pairs of weighing pressure pieces (7, 8, 9, 10), each comprising a fixed weighing pressure piece (11, 12) and a free weighing pressure piece (13, 14), with a transverse extension (15) in the direction of the chain width (2), wherein the plurality of lugs (4, 5, 6), the pairs of weighing plungers (7, 8, 9, 10) are linked to form a closed ring in a manner that transmits tractive force, and thus a chain running direction (16) and a radial direction (17) transverse to the chain running direction (16 ) and define transverse to the chain width (2), the radial direction (17) pointing from inside the ring to outside the ring,
wherein each tab (4,5,6) surrounds two pairs of weighing pressure pieces (7,8,8,9,9,10), so that in each tab (4,5,6) in the chain running direction (16) two fixed weighing pressure pieces (11 , 12) and two free weighing pressure pieces (13, 14) are arranged at a predetermined distance and thus define a division length (19, 20) between the contact points of the weighing pressure pieces (11, 13, 12, 14), each tab (4, 5 , 6) has a radially outer link bracket (21), a radially inner link bracket (22), a front side bracket (23) and a rear side bracket (24), the link bracket (21, 22) having a greatest extension in the chain running direction ( 16) and the side brackets (23, 24) have the greatest extent in the radial direction,
characterized in that
a division ratio of the long division length (20) to the short division length (19) is greater than 1.35.

Description

• - eine Vielzahl von Laschen, und zwar Kurzlaschen und Langlaschen; und
• - eine korrespondierende Anzahl von Wiegedruckstückpaaren,

wobei jeweils eine Lasche zwei Wiegedruckstückpaare umschließt, sodass in einer Lasche in Kettenlaufrichtung jeweils zwei feste Wiegedruckstücke und zwei freie Wiegedruckstücke in einem vorbestimmten Abstand angeordnet sind und so eine Teilungslänge zwischen den Berührungspunkten der Wiegedruckstücke definieren, wobei jede Lasche einen radial-äußeren Laschenbügel, einen radial-inneren Laschenbügel, einen vorderen Seitenbügel und einen hinteren Seitenbügel aufweist. Die Laschenkette ist vor allem dadurch gekennzeichnet, dass ein Teilungsverhältnis von der langen Teilungslänge zu der kurzen Teilungslänge größer als 1,35 ist und/oder der vordere Seitenbügel einen Überlappzipfel mit Erstreckung in Kettenlaufrichtung von dem betreffenden festen Wiegedruckstück wegweisend aufweist. Weiterhin betrifft die Erfindung ein Umschlingungsgetriebe mit einer solchen Laschenkette für einen Antriebsstrang, sowie einen Antriebsstrang mit einem solchen Umschlingungsgetriebe.The invention relates to a link chain with a chain width for a belt transmission, comprising at least the following components:

• - a variety of plates, namely short plates and long plates; and
• a corresponding number of pairs of weighing pressure pieces,

where each tab surrounds two pairs of rocker plates so that two fixed rocker blocks and two free rocker blocks are arranged in a link in the chain running direction at a predetermined distance and thus define a pitch length between the points of contact of the rocker blocks, each tab having a radially outer link bracket, one radially - Has inner strap bracket, a front side bracket and a rear side bracket. The link chain is characterized in particular by the fact that a division ratio of the long division length to the short division length is greater than 1.35 and / or the front side bracket has an overlapping tip with an extension in the chain running direction pointing away from the fixed weighing pressure piece in question. Furthermore, the invention relates to a belt transmission with such a link chain for a drive train, and a drive train with such a belt transmission.

From the prior art, link chains are known as belt means for belt transmission, for example a so-called CVT (continuous variable transmission), as a traction device. Such a CVT is for example from the DE 100 17 005 A1 known. Such a link chain is set up for transmitting high torques and high speeds, as are known, for example, from engine construction for motor vehicles. Because the gearbox noises are unusual and are generally perceived as annoying, it is a constant challenge to create a link chain that has the lowest possible noise emissions. At the same time, however, a long lifespan of the link chain, freedom from exchange over the lifespan of a motor vehicle, and high efficiency are also sought. Furthermore, the smallest possible effective circles (that is, diameters effective for the translation) are aimed at the conical pulley pairs of a belt transmission, so that a large transmission ratio can be achieved in a small (radial) installation space. A link chain with weighing pressure pieces is known for example from WO 2016/095 913 A1.

Proceeding from this, the present invention is based on the object of at least partially overcoming the disadvantages known from the prior art. The features according to the invention result from the independent claims, for which advantageous configurations are shown in the dependent claims. The features of the claims can be combined in any technically sensible manner, the explanations from the following description and features from the figures, which include additional embodiments of the invention, being able to be used for this purpose.

• - eine Vielzahl von Laschen, und zwar Kurzlaschen und Langlaschen; und
• - eine korrespondierende Anzahl von Wiegedruckstückpaaren, umfassend jeweils ein festes Wiegedruckstück und ein freies Wiegedruckstück, mit einer Quererstreckung in Richtung der Kettenbreite,

wobei mittels der Vielzahl der Laschen die Wiegedruckstückpaare zugkraftübertragend zu einem geschlossenen Ring verkettet sind und so eine Kettenlaufrichtung sowie eine Radialrichtung quer zu der Kettenlaufrichtung und quer zu der Kettenbreite definieren, wobei die Radialrichtung von innerhalb des Rings nach außerhalb des Rings weist, wobei jeweils eine Lasche zwei Wiegedruckstückpaare umschließt, sodass in einer Lasche in Kettenlaufrichtung jeweils zwei feste Wiegedruckstücke und zwei freie Wiegedruckstücke in einem vorbestimmten Abstand angeordnet sind und so eine Teilungslänge zwischen den Berührungspunkten der Wiegedruckstücke definieren, wobei jede Lasche einen radial-äußeren Laschenbügel, einen radial-inneren Laschenbügel, einen vorderen Seitenbügel und einen hinteren Seitenbügel aufweist, wobei die Laschenbügel eine größte Erstreckung in Kettenlaufrichtung aufweisen und die Seitenbügel eine größte Erstreckung in radialer Richtung aufweisen.The invention relates to a link chain with a chain width for a belt transmission, comprising at least the following components:

• - a variety of plates, namely short plates and long plates; and
• a corresponding number of pairs of weighing pressure pieces, each comprising a fixed weighing pressure piece and a free weighing pressure piece, with a transverse extension in the direction of the chain width,

wherein by means of the plurality of lugs, the pairs of weighing plungers are linked to form a closed ring in order to transmit tensile force and thus define a chain running direction and a radial direction transverse to the chain running direction and transverse to the chain width, the radial direction pointing from inside the ring to the outside of the ring, one tab each encloses two pairs of rocker plates so that two fixed rocker blocks and two free rocker blocks are arranged in a link in the chain running direction at a predetermined distance and thus define a pitch length between the contact points of the rocker blocks, each link having a radially outer link bracket, a radially inner link bracket, has a front side bracket and a rear side bracket, the link brackets having a greatest extent in the chain running direction and the side brackets having a greatest extent in the radial direction.

The link chain is primarily characterized in that a division ratio of the long division length to the short division length is greater than 1.35 [one hundred thirty-five hundredths].

Unless explicitly stated to the contrary, ordinal numbers used in the preceding and subsequent description serve only to clearly distinguish them and do not reflect the order or ranking of the components identified. An ordinal number greater than one does not necessarily mean that another such component must be present.

The link chain proposed here is set up for a belt transmission as a traction means, for example for a CVT. In the case of a belt transmission, a link chain forms a belt section at the transmission shafts and between them two strands, one being a train strand or load strand and the other an empty strand. The link chain has a chain width and, as a rule, a plurality of links are arranged adjacent to one another via this chain width and form a link group. In use, the chain width is aligned parallel to the alignment of the at least two transmission shafts. The direction of the chain width is therefore referred to as the axial direction and is constantly oriented in the same way during operation. The chain extension is referred to as the chain running direction, which thus runs in a ring-like manner as described above and changes its orientation in use via the movement of the link chain. Insofar as one speaks of a ring, this is not a ring with a constant radius, but rather a circumferentially closed structure. The shape is defined by the (set) active circles of the conical pulley pairs of the belt transmission and is (ideally) composed of two partial circles with constant (mostly different) diameters and two strands with a straight extension tangential to the partial circles (see below). The third spatial direction, which is perpendicular to the other two and points outwards from the inside of the closed ring formed, is referred to as the radial direction and changes its orientation with respect to a weighing pressure piece or a plate with the chain movement. When one speaks of the chain running direction, this does not mean a single (circumferential) running direction as in use, but the two-sided course of the plates and weighing pressure pieces in the closed ring, i.e. also the opposite direction to the running direction in use.

The link chain comprises a plurality of links and a plurality of link types, for example two link types, namely a short link and a long link. The tabs each have a radially outer link bracket, a radially inner link bracket, a rear side bracket and a front side bracket. The link brackets have the greatest extension in the direction of the chain running (on both sides). The side brackets have the greatest extent in the radial direction. The stirrups can be viewed approximately as rectangles, the greatest extent of the stirrup then corresponding to the long side of the (enveloping) rectangle. The tabs each comprise two pairs of rocker pieces. A pair of weighing pressure pieces each has a fixed weighing pressure piece and a free weighing pressure piece. The cradle pieces are pin-shaped and have a greatest extent (corresponding to a pin axis) in the axial direction, that is to say a transverse extent, the ends of the cradle pieces defining the chain width. Two tabs are each connected to each other by means of a common pair of rocker pressure elements to transmit tensile force. The two weighing pressure pieces of a pair of weighing pressure pieces lie directly against one another. The two rocker thrust pieces of the pair of rocker thrust pieces thus transmit the tensile force of the tabs to one another as compressive force and roll on one another during movement in a belt transmission, thus describing a weighing movement on one another. In order to accommodate the majority of the plates, the weighing pressure pieces have a corresponding axial length, which generally defines the maximum width of the plate chain, that is to say the chain width. In the case of, for example, a CVT, the ends of the weighing pressure pieces are formed obliquely so as to form an approximately parallel contact surface with the surfaces of the conical disk pairs. In the case of a CVT, a torque is frictionally introduced into the link chain via the ends of the weighing pressure pieces. The weighing pressure pieces are therefore loaded on both sides with an axial pressure force. The tabs transmit the torque as a tensile load to the respectively associated weighing pressure pieces, for example the immediately adjacent weighing pressure piece, at least to the straight free, that is to say not axially pressed, weighing pressure pieces (at least the load room). The weighing plungers or pairs of weighing plungers are therefore linked by means of the plurality of tabs to transmit tensile force.

The pairs of weigh plungers are each arranged at a predefined distance from one another, this distance being defined by the respective inside flap dimension, the (short) inside flap dimension being in the short flap and the (long) inside flap dimension in the long flaps. The pairs of weigh plungers are each arranged at a predefined distance from one another, this distance being defined by the respective inside flap dimension, the (short) inside flap dimension being in the short flap and the (long) inside flap dimension in the long flaps. The width of the pair of weigh plungers in interaction with the respective inner lug dimension define the division length, which is defined by the respective point of contact of the weigh plungers of a pair of weigh plungers in a flap, with a short division length in the short flap and a (relatively) long division length in the long flap. In many embodiments, a link chain only includes these two types of links. Alternatively, the longest tab and the shortest tab define the division ratio, that is to say the ratio of the long (or longest) inside dimension to the short (or shortest) inside dimension. It is for handling the link chain before assembly or during maintenance work required that a chain kinking and / or slipping of the weighing pressure pieces or weighing pressure piece pairs is avoided. In consideration of a single tab, the fixed, i.e. side bracket-side, weighing pressure piece of the two rocker pressure piece pairs held with a side bracket is in tensile force-transmitting contact, and the free, that is, different (inside of the tongue) weighing pressure piece of the pair of weighing pressure pieces is exclusively in tension-transmitting contact with the side bracket of the adjacent bracket. If there is no (sufficient) tensile force, the free weighing pressure piece and possibly also the fixed weighing pressure piece can be moved in the chain running direction. This must be prevented, but the mass of the plates, that is the plate chain, and the friction during the movement of the plate chain must be kept low for good efficiency of the belt transmission.

Due to the small (short) inside flap dimension of the short flap, the distance between the first pair of weighing plungers and the second pair of weighing plungers, or between the free weighing plungers of the short flap, can be secured from the front side bracket of the adjacent flap, because the width of the front side bracket can be adjusted to the short inside flap dimension . The bracket width is the (generally maximum) extension of the side bracket in question in the chain running direction and is also referred to as the bracket thickness. It is advantageous if both side brackets have the same bracket width for one tab; It is particularly advantageous if the side brackets of the entire link chain all have the same bracket width. This results in an identical or similar stress distribution in the (equally wide) side arms and thus an identical or similar stretch plasticization with the same external load. If, as here, a long link and a short link in the link chain (compare 2nd ) are used, the distance between the free cradle pieces of the long straps is so different from the distance to the free cradle pieces of the short straps that this cannot be depicted by means of side brackets of the same width.Conventionally, a (single) widened side bracket as the rear one Side bracket of the first long bracket used or a radial bracket used, which extends like a web between the two bracket brackets of the bracket in question (not shown here).

It is now proposed here that the division ratio is greater than 1.35. This allows the link chain to have a low mass. So far, a division ratio of 1.3 has not been exceeded, because it was expected (when using a thickened side bracket) to great disadvantages with regard to the stress profiles and thus different stretch plasticization in the tabs or (when using a radial web) too much friction. In one embodiment, the possibility of the weighing pressure pieces slipping is accepted and, for example, reliably prevented by providing assembly mimics on which the link chain is held with at least a minimum chain tension in a belt transmission during transport and handling before assembly. Alternatively, where necessary, the side bracket is widened in accordance with the greater distance between the free weighing pressure pieces in the long flap. Alternatively, an overlap is provided, for example as described below.

With an increasing division ratio, the mass of the link chain is reduced and the number of pressure plates is reduced. This in turn reduces the friction in the link chain. Alternatively or at the same time, the minimum possible bending radius of the link chain and thus the smallest possible (minimum) effective circle on a conical pulley pair of a belt transmission is reduced by the short link being further shortened in comparison to the long link and thus being shorter than a conventional short link.

It is further proposed in an advantageous embodiment of the link chain that the division ratio from the long division length to the short division length is greater than or equal to 1.4 [fourteen tenths], preferably the division ratio is greater than or equal to 1.5 [fifteen tenths].

Given the current demands for the smallest possible effective circle of action on a conical pulley pair of a belt transmission for a high transmission ratio in a small installation space, i.e. a small radial expansion of the conical pulleys, a division ratio of 1.5 is sufficient for most applications, for limit cases of 1, 4 sufficient.

• - eine Vielzahl von Laschen, und zwar Kurzlaschen und Langlaschen; und
• - eine korrespondierende Anzahl von Wiegedruckstückpaaren, umfassend jeweils ein festes Wiegedruckstück und ein freies Wiegedruckstück, mit einer Quererstreckung in Richtung der Kettenbreite,

wobei mittels der Vielzahl der Laschen die Wiegedruckstückpaare zugkraftübertragend zu einem geschlossenen Ring verkettet sind und so eine Kettenlaufrichtung sowie eine Radialrichtung quer zu der Kettenlaufrichtung und quer zu der Kettenbreite definieren, wobei die Radialrichtung von innerhalb des Rings nach außerhalb des Rings weist, wobei jeweils eine Lasche zwei Wiegedruckstückpaare umschließt, sodass in einer Lasche in Kettenlaufrichtung jeweils zwei feste Wiegedruckstücke und zwei freie Wiegedruckstücke in einem vorbestimmten Abstand angeordnet sind und so eine Teilungslänge zwischen den Berührungspunkten der Wiegedruckstücke definieren, wobei jede Lasche einen radial-äußeren Laschenbügel, einen radial-inneren Laschenbügel, einen vorderen Seitenbügel und einen hinteren Seitenbügel aufweist, wobei die Laschenbügel eine größte Erstreckung in Kettenlaufrichtung aufweisen und die Seitenbügel eine größte Erstreckung in radialer Richtung aufweisen.According to a further aspect, a link chain with a chain width for a belt transmission is proposed, comprising at least the following components:

• - a variety of plates, namely short plates and long plates; and
• a corresponding number of pairs of weighing pressure pieces, each comprising a fixed weighing pressure piece and a free weighing pressure piece, with a transverse extension in the direction of the chain width,

wherein, by means of the multiplicity of lugs, the pairs of weighing pressure pieces are linked to form a closed ring to transmit tensile force, and thus a chain running direction and a radial direction transverse to the chain running direction and transverse to the chain width define, with the radial direction from inside the ring to the outside of the ring, with one tab enclosing two pairs of rocker plates, so that two fixed rocker blocks and two free rocker blocks are arranged in a plate in the chain running direction at a predetermined distance and thus a pitch length between the points of contact of the cradle pieces, each link having a radially outer link bracket, a radially inner link bracket, a front side bracket and a rear side bracket, the link brackets having a greatest extent in the chain running direction and the side brackets having a greatest extent in the radial direction.

The link chain is primarily characterized in that, in at least one of the links, the front side bracket and the rear side bracket have the same bracket width in the chain running direction, the front side bracket having an overlap point with an extension in the chain running direction pointing away from the respective fixed weighing pressure piece.

Apart from the division ratio (and the specific shape of the rear side bracket), the link chain described here corresponds to the link chain described above. The link chain is preferably identical to an embodiment according to the preceding description, that is to say also the same with regard to the division ratio.

It is now proposed here that the two side brackets of at least one of the link plates, because of the large proportion of mass in relation to the chain length, preferably at least the short link plate, have the same bracket width and that an overlap tip is additionally provided on the rear side bracket. A corner differs from a pure bulge of the side bracket in that its radial extension is significantly less than the radial extension of the side bracket, for example less than 70% [seventy percent], preferably less than 50%, particularly preferably less than 20% [twenty percent ] is. The radial extent of the overlap is the mean radial extent without rounding transitions, for example somewhat in the middle of the chain running direction of the overlap. The smaller the radial expansion, the lower the mass of the tab in question and the less the influence on the stress profiles in the associated side bracket, and thus the influence on the stretch plasticization. The front side bracket is preferably the side bracket which, when the link chain is running in use in a belt transmission, is first drawn onto the respective pair of conical pulleys. In one embodiment, an overlap tip is also provided on the rear side bracket. The overlapping tip extends away from the associated (for example front) side bracket and indeed away from the associated fixed weighing pressure piece and thus towards the fixed weighing pressure piece of the (then for example) rear side bracket of the next but one tab. For a low mass and low friction in connection with a small number of different link shapes (of one link type, that is to say) of short links and / or long links, an overlap tip is provided only on the front side bracket. The total length, i.e. the width in the chain running direction, of the overlap apex is defined as the distance (in the chain running direction) between the point of maximum extension in the chain running direction of the overlap apex and the point of maximum extension in the chain running direction of the associated (front) side bracket of the link in question.

In comparison to a link chain with a widened side bracket, the mass of different stretch plastification on the weighing pressure pieces is reduced, thus extending the service life and increasing the efficiency of the link chain. In addition, a difference in the stretch plasticization is reduced or prevented as a result of a similar tension curve in the link plate with the overlap tip compared to a link plate with a (single) widened side bracket, so that the strength of the link chain is increased.

It is further proposed in an advantageous embodiment of the link chain that the link adjacent to the link with the overlap tip is free of a radial web,
preferably all tabs are free of a radial web.

By (at least partially) dispensing with a radial web, the friction between the tab body and the relevant (free) weighing pressure piece is significantly reduced. However, this also reduces the mass of the link in question, which increases the efficiency of the link chain.

It is further proposed in an advantageous embodiment of the link chain that the front side bracket has an overlap according to an embodiment as described above,
wherein the overlap tip has a total length in the chain running direction, the total length being composed of a compensating length and an overlap length,
the compensation length being 8% [eight percent] to 20% [twenty percent] of the short pitch length and the overlap length being 10% [ten percent] to 20% [twenty percent] of the short pitch length.

The total length, i.e. the width in the chain running direction, of the overlap tip is composed in this embodiment of a compensation length and an overlap length, the area of the compensation length and the area being exposed in the stretched state of the relevant section of the link chain (in use in a belt transmission) the overlap length overlaps with the adjacent (rear) side bracket of the next but one tab. The compensation length is determined from the division ratio of the link chain and the desired or possible bracket width between the free weighing pressure pieces in the short link.

mit x_SB als Breite des betreffenden Seitenbügels, t_K der kurzen Teilungslänge und x_WD die Dicke (Breite in Kettenlaufrichtung) des Wiegedruckstücks eines Wiegedruckstückpaars ist. $$x_{WD}=\left(I_{i,K}-t_K\right)/\mathrm{2,}$$

mit I_i,K als kurzem Lascheninnenmaß.The total length is calculated as follows: $$x_{SB}=t_K-\mathrm{2nd}\cdot x_{WD},$$

with x _SB as the width of the side bracket concerned, t _K the short pitch length and x _WD is the thickness (width in the chain running direction) of the weighing pressure piece of a pair of weighing pressure pieces. $$x_{WD}=\left({\mathrm{I.}}_{i,K}-t_K\right)/\mathrm{2,}$$

with I _{i, K} as a short tab inside dimension.

The division ratio TV is the ratio of the long division length t _L to the short pitch length t _K and thus applies: $$t_L=t_K\cdot TV$$

sodass sich aus dem obigen Zusammenhang der Formeln (1) bis (4) für die Ausgleichslänge A das folgende näherungsweise ergibt: $$A=t_K\cdot \left(TV-3\right)+I_{i,K}$$

The compensation length A is roughly calculated as follows: $$A=t_L-\mathrm{2nd}\cdot x_{WD}-\mathrm{2nd}\cdot x_{SB},$$

so that from the above relationship of formulas (1) to (4) for the compensation length A the following approximates: $$A=t_K\cdot \left(TV-\mathrm{3rd}\right)+{\mathrm{I.}}_{i,K}$$

For example, A is 0.58 mm to 1.2 mm [millimeters] with a short pitch length t _K of 6.2 mm. This results in an overall length with a, for example conventional, overlap length of 0.8 mm to 1.2 mm from 1.38 mm to 2.4 mm.

• - ein erstes Kegelscheibenpaar mit einer ersten Rotationsachse und mit einem veränderbaren axialen ersten Scheibenabstand;
• - ein zweites Kegelscheibenpaar mit einer zweiten Rotationsachse und mit einem veränderbaren axialen zweiten Scheibenabstand; und
• - eine Laschenkette nach einem der vorhergehenden Ansprüche,

wobei die beiden Kegelscheibenpaare mittels der Laschenkette, welche als in Richtung der Kettenbreite in jeweils einem Kegelscheibenpaar axial eingepresstes Zugmittel angeordnet ist, abhängig von den eingestellten Scheibenabständen übersetzend drehmomentübertragend miteinander verbunden sind.According to a further aspect, a belt transmission for a drive train is proposed, comprising at least the following components:

• - A first pair of conical disks with a first axis of rotation and with a variable axial first disk distance;
• - A second pair of conical disks with a second axis of rotation and with a variable axial second disk distance; and
• a link chain according to one of the preceding claims,

wherein the two conical pulley pairs are connected to each other in a torque-transmitting manner by means of the link chain, which is arranged as a traction means which is axially pressed in in the direction of the chain width in each conical pulley pair, depending on the set pulley spacings.

With the belt transmission proposed here, which is also referred to in the embodiment explained here as a conical pulley belt transmission, torque can be transmitted from a transmission input shaft to a transmission output shaft, and vice versa, in a step-up or step-down manner, the transmission being continuously adjustable, at least in some areas.

The belt transmission is set up for a drive train, for example of a motor vehicle, and comprises at least one first cone pulley arranged on a first shaft, for example the transmission input shaft, and a second cone pulley arranged on a second shaft, for example the transmission output shaft, and one provided for torque transmission between the cone pulley pairs Wrapping means, namely the link chain described above. A pair of conical disks comprises two conical disks which are aligned with one another with corresponding conical surfaces and are axially movable relative to one another. The (first) conical disk, also known as a loose disk or a moving disk, can be moved (axially displaceable) along its shaft axis and the (second) conical disk, also known as a fixed disk, is fixed (axially fixed) in the direction of the shaft axis. The respective disc spacing can thus be changed.

During operation of the belt transmission, the link chain becomes radial due to the conical surfaces of the conical pulleys by means of a relative axial movement of the conical pulleys of a pair of conical pulleys between an inner position (small or minimal effective circle) and an outer position (large or maximal effective circle) Direction shifted. The link chain thus runs on a changeable effective circle, i.e. with a changeable running radius. This results in a different speed ratio and torque ratio adjustable from one pair of conical disks to the other pair of conical disks, preferably continuously.

The belt transmission proposed here has a link chain as described above, the link chain having a low internal friction and thus a high degree of efficiency, at the same time providing adequate protection against chain buckling. The strength of the link chain is also increased. Alternatively or at the same time, a reduced minimal effective circle can be carried out with the link chain by shortening the short links in comparison to conventional short links.

• - zumindest eine Antriebsmaschine;
• - zumindest einen Verbraucher; und
• - ein Umschlingungsgetriebe nach einer Ausführungsform gemäß der obigen Beschreibung,

wobei die zumindest eine Antriebsmaschine zur Drehmomentübertragung mittels des Umschlingungsgetriebes mit dem zumindest einen Verbraucher mit veränderbarer Übersetzung verbunden ist.According to a further aspect, a drive train is proposed, comprising at least the following components:

• - at least one engine;
• - at least one consumer; and
• a belt transmission according to an embodiment as described above,

wherein the at least one drive machine for torque transmission by means of the belt transmission is connected to the at least one consumer with variable translation.

The drive train, for example of a motor vehicle used to propel it via at least one drive wheel, is set up to be provided by one or a plurality of drive units, for example an internal combustion engine and / or an electrical machine, and via its respective drive shaft, for example the combustion engines -Drive shaft and / or the electric drive shaft (rotor shaft), transmitted torque for use by a consumer as required, so taking into account the required speed and torque. One use is, for example, an electrical generator for providing electrical energy or the transmission of a torque to a drive wheel of a motor vehicle to propel it.

In order to transmit the torque in a targeted manner and / or by means of a manual transmission with different gear ratios, the use of the belt transmission described above is particularly advantageous because the link chain has a very high efficiency of torque transmission and / or as a result of a small, minimally permissible effective circuit on a small (radial) Space allows a high spread of translation.

• 1: ein Ausschnitt einer Laschenkette; und
• 2: ein Umschlingungsgetriebe in einem Antriebsstrang.

The invention described above is explained in detail below against the relevant technical background with reference to the accompanying drawings, which show preferred configurations. The invention is in no way restricted by the purely schematic drawings, it being noted that the drawings are not true to size and are not suitable for defining size relationships. It is shown in

• 1 : a section of a link chain; and
• 2nd : a belt transmission in a drive train.

In 1 are three plates of a plate chain 1 (compare 2nd ) shown in an axial top view, namely a short tab 4th (shown on the left, with a solid line) adjacent to a first long flap 5 (in the middle, shown with a dashed line), again adjacent to a second long flap 6 (shown on the right, with a dash-dotted line). The tabs 4th , 5 , 6 each have a radially outer bracket 21st , a radially inner bracket 22 , a front side bar 23 (as shown on the right) and a rear side bracket 24th (as shown on the left). The strap bracket 21st , 22 point in the chain running direction 16 the greatest extension. The side bracket 23 , 24th have the greatest extent in the radial direction 17th on. The tabs 4th , 5 , 6 each comprise two pairs of weighing plungers 7 , 8th , 9 , 10 . A pair of weigh plungers 7 , 8th , 9 , 10 each has a fixed pressure piece 11 , 13 and a free weighing pressure piece 12th , 14 on. The weighing pads 11 , 13 , 12th , 14 are pin-shaped and have the greatest extent (corresponding to a pin axis) in the axial direction 18th on, so a transverse extension 15 , with the ends of the rocker pieces 11 , 13 , 12th , 14 the chain width 2nd Are defined. The axial direction 18th shows in this representation in the leaf plane. Two tabs 4th , 5 ; 5 , 6 are each by means of a common pair of weighing plungers 8th , 9 connected with each other. The chain running direction points in the leaf plane 16 left and right and the radial direction 17th from the bottom up. The tabs 4th , 5 , 6 thus link in the entire link chain 1 (compare 2nd ) the pairs of weigh plungers 7 , 8th , 9 , 10 transferring traction to a closed ring (cf. 2nd ).

The tabs 4th , 5 , 6 are arranged here in the chain running direction 16 a first long flap 5 between a short flap 4th and a second long flap 6 is arranged. The pairs of weigh plungers 7 , 8th ; 8th , 9 ; 9 , 10 are each arranged at a predefined distance from one another, this distance from the respective inner tab dimension 43 , 44 is defined, whereby the (short) inside flange dimension 43 in the short flap 4th is present and the (long) tab inside dimension 44 in the long flaps 5, 6 is present. The fat 46 the pair of rocker pieces 7 , 8th ; 8th , 9 in interaction with the respective inside flap dimension 43 , 44 define the pitch length 19th , 20 which of the respective point of contact of the weighing pressure pieces 11 , 13 a pair of rocker pieces 7 , 8th ; 8th , 9 in a flap 4th , 5 is defined, so in the short tab 4th a short pitch 19th and in the long flap 5 a (relatively) long pitch length 20 is present. In many embodiments, a link chain comprises 1 (compare 2nd ) only these two types of tabs 4th , 5 , 6 . As in the short flap 4th can be seen, the distance between the first pair of weighing plungers 7 and the second pair of weigh plungers 8th , or between the free pressure pieces 12th , 14 the short flap 4th from the rear side bracket 24th the adjacent second long flap 5 secured because of the temple width 25th of the rear side bracket 24th to the short inside tab dimension 43 is coordinated. The temple width 25th is the (usually maximum) extension of the front (and rear) side bracket 23 , 24th . It is advantageous if both side brackets are in one tab 23 , 24th the same temple width 25th exhibit; is particularly advantageous if the side bracket 23 , 24th the entire link chain 1 (compare 2nd ) all the same bracket width 25th exhibit. So there is an equal or similar tension distribution in the (equally wide) side arms 23 , 24th and thus an identical or similar stretch plasticization occurs with the same external load.

If a long strap 5 and a short flap 4th in the link chain 1 (compare 2nd ) is used, is the distance between the free weighing pressure pieces 12th , 14 the long flaps 5 , 6 but so different that this cannot be achieved by means of side brackets of the same width 23 , 24th can be depicted, therefore, a (single) widened side bracket is conventional 45 like the (front) side bar 45 the first long flap 5 used or a radial web (or radial bracket) used, which is web-like between the two bracket brackets 21st , 22 of the tab in question (not shown here).

Here it is now proposed that the two side brackets 23 , 24th (here with the short flap 4th ) the same bracket width 25th have and also an overlap 26 on the front side bracket 23 is provided. The front side bar 23 is preferably the side bracket which is in a running direction of the link chain 1 in use in a belt transmission 3rd first on the respective conical disk pair 31 , 34 is pulled (compare 2nd ). So here with an assumed running direction to the right the right of the two side brackets 23 a tab 4th , 5 , 6 . The total length 27 , i.e. the width in the chain running direction 16 , the overlap 26 consists of the compensation length 28 and the overlap length 29 together, in the shown (stretched) state of the link chain 1 the range of the compensation length 28 exposed and the area of overlap length 29 with the adjacent (rear) side bracket 24th the next but one (here second long) tab 6 overlaps. The total length 27 is defined as the distance (in the chain running direction 16 ) between the point of maximum extension in the chain running direction 16 of the overlap 26 and the point of maximum extension in the chain running direction 16 of the associated (front) side bracket 23 the tab in question 4th . The compensation length 28 is determined from the division ratio of the link chain 1 and the desired or possible bracket width 25th between the free weigh plungers 11 , 13 in the short flap 4th .

In 2nd is a belt transmission 3rd in a perspective view in a section of a drive train 30th shown, in which a link chain 1 as a traction device on two pairs of conical disks 31 , 34 expires. The link chain 1 has a chain width 2nd with a transverse extension 15 in the axial direction 18th (parallel to the axis of rotation 32 , 35 ) so that a defined disc distance 33,36 to a resulting effective circle on the respective conical disc pair 31 , 34 leads. So that is a translation by means of the belt transmission 3rd from a first wave 39 , for example a transmission input shaft, with a first axis of rotation 32 and a second wave 40 , for example a transmission output shaft, with a second axis of rotation 35 set.

The tabs 4th , 5 , 6 (Not individually labeled here, compare 1 ), are by means of the large number of pairs of weighing pressure pieces 7 , 8th , 9 , 10 with each other for the transmission of traction in the dreams 41 , 42 chained together to form a ring. There are a plurality of tabs in the axial direction 18th arranged side by side. Here is a (two-sided) chain running direction 16 (as well as the axial direction 18th (corresponds to the direction of the chain width 2nd ) and radial direction 17th ) at any point in the link chain 1 defined, whose orientation in space changes with the movement of the link chain 1 changed. For example, on the first wave 39 a prime mover 37 connected, only the torque-absorbing input gear is shown here. For example, on the second shaft 40 a consumer 38 , for example at least one drive wheel, connected, only the torque-emitting output gear being shown here.

The link chain proposed here has a particularly long service life with a high overall strength of the link chain and / or enables operation with a very small, minimal effective circuit.

Reference list

1

Link chain

2nd

Chains wide

3rd

Belt transmission

4th

Short flap

5

first long strap

6

second long strap

7

first pair of weigh plungers

8th

second pair of weigh plungers

9

third pair of weigh plungers

10th

fourth pair of weigh plungers

11

first fixed weighing pressure piece

12th

first free weighing pressure piece

13

second fixed pressure piece

14

second free weighing pressure piece

15

Transverse extension

16

Chain running direction

17th

Radial direction

18th

Axial direction

19th

short pitch length

20

long pitch length

21

radial outer bracket

22

radial inner bracket

23

front side bar

24th

rear side bracket

25th

Bracket width

26

Overlap

27

overall length

28

Compensation length

29

Lap length

30th

Powertrain

31

first pair of conical disks

32

first axis of rotation

33

first disc distance

34

second pair of conical disks

35

second axis of rotation

36

second disc distance

37

Prime mover

38

consumer

39

first wave

40

second wave

41

first run

42

second strand

43

short flap inside dimension

44

long inside flap dimension

45

wide side bar

46

Thickness of the pair of weigh plungers

QUOTES INCLUDE IN THE DESCRIPTION

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

Patent literature cited

• DE 10017005 A1 [0002]

Claims (7)

Link chain (1) with a chain width (2) for a belt transmission (3), comprising at least the following components: - a plurality of links (4,5,6), namely short links (4) and long links (5,6); and a corresponding number of pairs of weighing pressure pieces (7, 8, 9, 10), each comprising a fixed weighing pressure piece (11, 12) and a free weighing pressure piece (13, 14), with a transverse extension (15) in the direction of the chain width (2) , whereby the pairs of weighing plungers (7, 8, 9, 10) are linked to form a closed ring by means of the plurality of plates (4, 5, 6), thus transmitting a chain running direction (16) and a radial direction (17) transverse to the chain running direction ( 16) and define transversely to the chain width (2), the radial direction (17) pointing from inside the ring to the outside of the ring, with one tab (4,5,6) each pair of rocker pressure pieces (7,8,8,9, 9, 10) encloses, so that in each case two fixed cradle pieces (11, 12) and two free cradle pieces (13, 14) are arranged at a predetermined distance in a link (4, 5, 6) in the chain running direction (16) and thus a pitch length (19,20) between the points of contact of the weighing pressure pieces (11,13,12,14), wherein each tab (4,5,6) has a radially outer tab bracket (21), a radially inner tab bracket (22), a front side bracket (23) and a rear side bracket (24), the tab bracket (21,22 ) have a greatest extent in the chain running direction (16) and the side brackets (23, 24) have a greatest extent in the radial direction, characterized in that a division ratio of the long division length (20) to the short division length (19) is greater than 1, 35 is. Link chain (1) after Claim 1 , wherein the division ratio of the long division length (20) to the short division length (19) is greater than or equal to 1.4, preferably the division ratio is greater than or equal to 1.5. Link chain (1) with a chain width (2) for a belt transmission (3), comprising at least the following components: - a plurality of links (4,5,6), namely short links (4) and long links (5,6); and a corresponding number of pairs of weighing pressure pieces (7, 8, 9, 10), each comprising a fixed weighing pressure piece (11, 12) and a free weighing pressure piece (13, 14), with a transverse extension (15) in the direction of the chain width (2) , whereby the pairs of weighing plungers (7, 8, 9, 10) are linked to form a closed ring by means of the plurality of plates (4, 5, 6), thus transmitting a chain running direction (16) and a radial direction (17) transverse to the chain running direction ( 16) and define transversely to the chain width (2), the radial direction (17) pointing from inside the ring to the outside of the ring, with one tab (4,5,6) each pair of rocker pressure pieces (7,8,8,9, 9, 10) encloses, so that in each case two fixed cradle pieces (11, 12) and two free cradle pieces (13, 14) are arranged at a predetermined distance in a link (4, 5, 6) in the chain running direction (16) and thus a pitch length (19,20) between the points of contact of the weighing pressure pieces (11,13,12,14), wherein each tab (4,5,6) has a radially outer tab bracket (21), a radially inner tab bracket (22), a front side bracket (23) and a rear side bracket (24), the tab bracket (21,22 ) have a greatest extent in the chain running direction (16) and the side brackets (23, 24) have a greatest extent in the radial direction, characterized in that in at least one of the tabs (4) the front side bracket (23) and the rear side bracket (24 ) have the same bracket width (25) in the chain running direction (16), the front side bracket (23) having an overlap tip (26) with an extension in the chain running direction (16) pointing away from the relevant fixed pressure piece (14). Link chain (1) according to one of the preceding claims, wherein the link (5) adjacent to the link (4) with the overlap tip (26) is free of a radial web, preferably all links (4,5,6) are free of a radial web . Link chain (1) according to any one of the preceding claims, wherein the front side bracket (24) according to an overlap (26) Claim 3 The overlap tip (26) has a total length (27) in the chain running direction (16), the total length (27) being composed of a compensation length (28) and an overlap length (29), the compensation length (28) 8% to 20% of the short pitch length (19) and the overlap length (29) from 10% to 20% of the short pitch length (19). Belt transmission (3) for a drive train (30), comprising at least the following components: - a first pair of conical pulleys (31) with a first axis of rotation (32) and with a variable axial first pulley spacing (33); - A second pair of conical disks (34) with a second axis of rotation (35) and with a variable axial second disk distance (36); and - a link chain (1) according to one of the preceding claims, wherein the two conical disk pairs (31, 34) by means of the link chain (1), which as axially pressed in the direction of the chain width (2) in each conical disk pair (31, 34) traction means is arranged depending on the set disc spacings (33, 36) are connected to one another in a torque-transmitting manner. Drive train (30), comprising at least the following components: - at least one drive machine (37); - at least one consumer (38); and - a belt transmission (3) after Claim 6 , wherein the at least one drive machine (37) for torque transmission by means of the belt transmission (3) is connected to the at least one consumer (38) with variable translation

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