CN213088652U

CN213088652U - Plate link chain for a belt-driven transmission, belt-driven transmission for a drive train and drive train

Info

Publication number: CN213088652U
Application number: CN202021001921.7U
Authority: CN
Inventors: C·特劳特曼; P·弗里茨
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2019-06-07
Filing date: 2020-06-04
Publication date: 2021-04-30
Anticipated expiration: 2030-06-04
Also published as: DE202020102529U1

Abstract

The utility model relates to a plate link chain, be used for driving system's wound form derailleur, drive system for wound form derailleur, plate link chain have the chain width, the plate link chain has following part at least: a plurality of plates, i.e., short plates and long plates; and a corresponding number of pairs of rocking pressure members, wherein a plate surrounds each of the two pairs of rocking pressure members, such that two fixed rocking pressure members and two free rocking pressure members are arranged in a plate at a predetermined distance in the chain running direction, thereby defining an indexing length between contact points of the rocking pressure members, wherein each plate has a radially outer plate bow, a radially inner plate bow, a front side bow and a rear side bow. The plate link is characterized in that the ratio of the long to the short indexing length is greater than 1.35, and/or the front bracket has an overlapping tip with an extension pointing away from the associated fixed oscillating pressure element in the chain running direction.

Description

Plate link chain for a belt-driven transmission, belt-driven transmission for a drive train and drive train

Technical Field

The utility model relates to a plate link chain for winding type derailleur, it has the chain width, the plate link chain has following part at least:

-a plurality of plates, short and long; and

-a corresponding number of pairs of rocking pressure members,

wherein a plate surrounds the two pairs of rocking pressure members, so that two fixed rocking pressure members and two free rocking pressure members, respectively, are arranged in a plate at predetermined intervals in the chain running direction and thus define the indexing length between the contact points of the rocking pressure members,

wherein each plate has a radially outer plate bow, a radially inner plate bow, a front side bow and a rear side bow. The plate link is characterized in that the ratio of the long to the short pitch length is greater than 1.35, and/or the front bracket has an overlapping tip with an extension pointing away from the associated fixed oscillating pressure element in the chain running direction. Furthermore, the invention relates to a wrap-around transmission for a drive train having such a plate link chain and to a drive train having such a wrap-around transmission.

Background

Plate chains are known from the prior art as winding means for a winding transmission, for example a so-called CVT (continuously variable transmission), as traction means. Such a CVT is known, for example, from DE 10017005 a 1. Such plate links are provided for transmitting high torques and high rotational speeds, as are known, for example, from the manufacture of engines for motor vehicles. Because transmission noise is unusual and is generally considered to be disturbing, it is a continuing challenge to provide a plate link with as low noise emissions as possible. However, at the same time, a long service life of the plate link chain, as far as possible no replacement within the service life of the motor vehicle, and high efficiency are desired. Furthermore, the smallest possible active circuit (i.e. the effective diameter for the transmission ratio) on the conical disk pairs of the wrap-around transmission is sought, so that a large transmission ratio is achieved in a small (radial) installation space. A plate link chain with a rocking pressure element is known, for example, from WO 2016/095913 a 1.

SUMMERY OF THE UTILITY MODEL

Starting from this, the 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 description, for which an advantageous configuration is shown in the description. The features according to the invention can be combined in any technically expedient manner and method, wherein for this purpose the explanations from the following description and the features from the drawings, which include the complementary embodiments of the invention, can also be considered.

-a plurality of plates, short and long; and

a corresponding number of pairs of rocking pressure members comprising a fixed rocking pressure member and a free rocking pressure member, respectively, and having a transverse extension in the direction of the chain width,

wherein, by means of the plurality of plates, the pair of rocking pressure members are linked in a manner transmitting traction forces into a closed loop and thus define a chain running direction and a radial direction transverse to the chain running direction and transverse to the chain width, wherein the radial direction is directed from the loop interior to the loop exterior,

wherein a plate surrounds the two pairs of rocking pressure members, so that two fixed rocking pressure members and two free rocking pressure members are arranged in a plate at predetermined intervals in the chain running direction, and thus the indexing length between the contact points of the rocking pressure members is defined,

wherein each plate has a radially outer plate bow, a radially inner plate bow, a front side bow and a rear side bow, wherein the plate bows have a maximum extension in the chain running direction and the side bows have a maximum extension in the radial direction.

The plate link is characterized in that the pitch ratio of the long pitch length to the short pitch length is greater than 1.35 (one hundred and thirty-five percent).

Ordinal numbers used in the foregoing and following description are used for explicit differentiability only and do not indicate a sequence or order of the labeled components unless explicitly stated to the contrary. An ordinal number greater than one does not imply that additional such elements must necessarily be present.

The plate link chain proposed here is provided as a traction means for a wrap-around transmission, for example for a CVT. In a wrap-around transmission, the plate link forms a wrap-around circle segment at the transmission shafts and two return sections between the transmission shafts, wherein one return section is a traction return section or a load return section and the other return section is an idle return section. The plate link chain has a chain width, and a plurality of plates are usually arranged adjacent to one another over the chain width and form a plate pack. In use, the chain width is oriented parallel to the orientation of the at least two variator axes. The direction of the chain width is therefore referred to as the axial direction and is constantly aligned in operation. The chain extension is referred to as the chain running direction, and therefore extends annularly as explained above and changes its orientation in use by movement of the plate chain. By loop is meant herein not a loop with a constant radius, but a structure in which the loop is closed around. This shape is defined by the (set) active circuit of the conical disk pair of the wrap-around transmission and (ideally) consists of two part circles of constant (mostly different) diameter and two return sections with a straight extension tangential to these part circles (see below). The third spatial direction, which is perpendicular to the other two spatial directions and points outwards from the inside of the closed loop formed, is referred to as the radial direction and changes its orientation with the chain motion with respect to the rocking pressure piece pairs or plates. When referring to the chain running direction, this does not mean the only running (swivel) direction as in use, but the course of the plate and the rocking pressure element on both sides in the closed loop, i.e. also the direction opposite to the running direction in use.

The plate link comprises a plurality of plates and a plurality of plate types, for example two plate types, namely short plates and long plates. The plates each have a radially outer plate arch, a radially inner plate arch, a rear side arch and a front side arch. The plate bow has a maximum extent in the chain running direction (directed to both sides). The side bow has a maximum extension in the radial direction. The bow can be considered approximately rectangular, wherein the maximum extension of the bow corresponds to the long side of the (enveloping) rectangle. The plates each include two rocking pressure member pairs. The pair of rocking pressure members has a fixed rocking pressure member and a free rocking pressure member, respectively. The rocking pressure piece is configured in the form of a pin and has a maximum extent (corresponding to the pin axis) in the axial direction, i.e. a transverse extent, wherein the ends of the rocking pressure piece define the chain width. The two plates are connected to each other in a traction-transmitting manner by means of a common pair of rocking pressure elements. The two rocking pressure members of a rocking pressure member pair abut directly against each other. The two wobble pressure elements of the wobble pressure element pair thus transmit the tractive forces of the plates to one another as pressure forces and roll over one another when moving in the wrap-around transmission, i.e. describe a wobbling movement of one another. For receiving a plurality of plates, the rocking pressure elements have a corresponding axial length which usually defines the maximum width of the plate chain, i.e. the chain width. In a CVT, for example, the ends of the wobble pressure element are designed at an angle in order to form contact surfaces that are approximately parallel to the surfaces of the conical disk pairs. In a CVT, a torque is introduced into the plate link chain in a friction-locking manner by the ends of the wobble pressure piece. The rocking pressure member is thus loaded with axial pressure on both sides. The plate transmits the torque as a tensile load to the wobble pressure elements (at least of the load return section) which are just free, i.e. not axially pressed, and the tensile load acts on the respectively associated wobble pressure element, for example the respectively directly adjacent wobble pressure element. The oscillating pressure elements or oscillating pressure element pairs are thus linked in a traction-transmitting manner by means of a plurality of plates.

The pairs of rocking pressure members are each arranged at a predefined distance from one another, wherein the distance is defined by a respective in-board dimension, wherein the (short) in-board dimension is present in the short board and the (long) in-board dimension is present in the long board. The pairs of rocking pressure members are each arranged at a predefined distance from one another, wherein the distance is defined by a respective in-board dimension, wherein the (short) in-board dimension is present in the short board and the (long) in-board dimension is present in the long board. The width of the rocking pressure element pairs, which jointly with the respective in-plate dimension defines the indexing length, which is defined by the respective contact points of the rocking pressure elements of a rocking pressure element pair in a plate, wherein in the short plate there is a short indexing length and in the long plate there is a (relatively) long indexing length. In various embodiments, the plate link includes only these two types of plates. Alternatively, the longest and shortest plates define an indexing ratio, i.e., the ratio of the long (or longest) in-plate dimension to the short (or shortest) in-plate dimension. In order to handle the plate link chain before assembly or during maintenance work, it is necessary to avoid buckling of the chain and/or to avoid slipping of the wobble pressure elements or wobble pressure element pairs. When viewing a single plate, the fixed, i.e. on the side bracket side, rocking pressure elements of the two held rocking pressure element pairs are in traction-transmitting contact with the side brackets, while the free, i.e. respectively other (on the inner side of the plate) rocking pressure element of the rocking pressure element pair is in traction-transmitting contact only with the side brackets of the adjacent plate. The free-running and in some cases fixed-running pressure elements are also displaced in the chain running direction if there is no (sufficient) traction action. This must be prevented, wherein, however, for good efficiency of the wrap-around transmission, the mass of the plate, i.e. the plate link chain, and the friction during movement of the plate link chain must be kept small.

Due to the small (short) panel internal dimensions in the short panels, the distance between the first and second pairs of rocking pressure elements or the distance between the free rocking pressure elements of the short panels can be ensured by the front bow of the adjacent panel, since the bow width of this front bow can be matched to the short panel internal dimensions. The bracket width is the (usually largest) extension of the relevant side bracket in the chain running direction and is also referred to as the bracket thickness. Advantageously, in a panel both side brackets have the same bracket width. It is particularly advantageous if the side brackets of the entire plate link chain all have the same bracket width. The same or similar stress distribution and therefore the same or similar tensile plasticization occurs under the same external load in the (equally wide) side brackets. When long and short plates are used in a plate link chain (see fig. 2) as in the present case, the spacing between the free-running pressure elements of the long plates differs from the spacing between the free-running pressure elements of the short plates, so that this cannot be represented by means of side brackets of equal width. For this purpose, it is usual to use (single) widened side brackets, such as the rear bracket of the first long plate, or to use radial brackets which extend in a web-like manner between two bracket brackets of the respective plate (not shown here).

It is now proposed here that the indexing ratio is greater than 1.35. Thus, a small mass of the plate link chain can be set. Hitherto, the indexing ratio has not exceeded 1.3, since (when using thickened side brackets) excessive disadvantages are to be expected in terms of the stress distribution in the plates and thus in terms of different tensile plastifications in the plates or (when using radial webs) excessive friction is to be expected. In one embodiment, the possibility of slipping of the wobble pressure element can be accepted and reliably prevented, for example, by providing a mounting assembly on which the plate link chain is held with at least a minimum chain tension during transport and handling before being mounted in the transmission. Alternatively, the side brackets are widened, where necessary, in correspondence with the thus greater spacing of the free-running pressure elements in the long plates. Alternatively, overlapping tips are provided, for example as described below.

As the indexing ratio increases, the mass of the plate link decreases and the number of rocking pressure members decreases. Thus, the friction in the plate link chain is reduced again. Alternatively or simultaneously, the smallest possible bending radius of the plate link chain and thus the smallest possible (smallest) effective circuit on the conical disk pair of the transmission are reduced in that the short plate is further shortened compared to the long plate and is therefore shorter than conventional short plates.

In an advantageous embodiment of the plate link, it is furthermore provided that the indexing ratio of the long indexing length to the short indexing length is greater than or equal to 1.4 (fourteen tenths), preferably greater than or equal to 1.5 (fifteen tenths).

With the current requirement for the smallest possible active circuit (i.e. a small radial extent of the cone disk pair) on the cone disk pair of a wrap-around transmission to achieve a high transmission ratio in a small installation space, an indexing ratio of 1.5 is sufficient for most applications, and a limit case of 1.4 is sufficient.

According to another aspect, a plate chain for a wrap-around transmission is proposed, having a chain width, the plate chain having at least the following components:

-a plurality of plates, short and long; and

The plate link is characterized in that, in at least one of the plates, the front bracket and the rear bracket have the same bracket width in the link running direction, wherein the front bracket has an overlapping tip with an extension pointing away from the associated fixed rocker pressure element in the link running direction.

The plate link described here corresponds to the previously described plate link, except for the indexing ratio (and the specific shape of the rear bracket). Preferably, the plate link is identical to the embodiment according to the preceding description, i.e. also in terms of the indexing ratio.

It is now proposed that, due to the large mass fraction (preferably of at least short plates) with respect to the chain length, the two side brackets of at least one of the plates have the same bracket width and that an overlapping tip is additionally provided on the rear side bracket. The tip differs from the pure thickness of the side bracket in that the radial extent of the tip is significantly smaller than the radial extent of the side bracket, for example less than 70% (seventy percent), preferably less than 50%, particularly preferably less than 20% (twenty percent). The radial extension of the overlapping tip is a radial extension in the middle, i.e. without a rounded transition, for example approximately in the center of the overlapping tip in the chain running direction. The smaller the radial extension, the smaller the mass of the relevant plate and the smaller the influence on the stress profile in the associated side bow and thus on the tensile plasticization. The front bracket is preferably a side bracket which, in the operating direction of the plate link chain when it is used in a wrap-around transmission, is initially pulled onto the respective cone pulley pair. In one embodiment, the rear bracket is also provided with an overlapping tip. The overlap tip extends away from the associated (e.g. front) side bracket, i.e. away from the associated fixed pivoting pressure piece and thus towards the fixed pivoting pressure piece of the (then e.g.) rear side bracket of the next following plate. Preferably, in order to combine a low mass and low friction with a small number of different plate shapes of short and/or long plates (i.e. one plate type), only overlapping tips are provided on the front bow. The total length of the overlapping tip, i.e. the width in the chain running direction, is defined as the distance (in the chain running direction) between the point of maximum extension of the overlapping tip in the chain running direction and the point of maximum extension of the associated (front) side bow of the associated plate in the chain running direction.

The quality of the differential tensile plasticization on the oscillating pressure element is therefore reduced in comparison with plate chains having widened side brackets, so that the service life is extended and the efficiency of the plate chain is increased. In addition, due to the same type of stress profile in the plate link with overlapping tips, differences in the tensile plasticization are reduced or prevented compared to plate links with (single) widened side brackets, so that the strength of the plate link is thereby increased.

In an advantageous embodiment of the plate link, it is furthermore provided that the plates adjacent to the plate with the overlapping tip do not have radial webs, preferably all plates do not have radial webs.

By (at least partially) eliminating the radial webs, the friction between the plate body and the associated (free) rocking pressure element is significantly reduced. But also the mass of the associated plate is reduced thereby increasing the efficiency of the plate link chain.

In an advantageous embodiment of the plate link, it is provided that the front bow according to any of the embodiments described above has an overlapping tip, wherein the overlapping tip has an overall length in the chain running direction, wherein the overall length is composed of a compensation length and an overlapping length, wherein the compensation length is 8% (eight percent) to 20% (twenty percent) of the short pitch length, and wherein the overlapping length is 10% (ten percent) to 20% (twenty percent) of the short pitch length.

In this embodiment, the total length of the overlapping tip, i.e. the width in the chain running direction, is composed of a compensation length, the area of which is exposed and which overlaps with the adjacent (rear) side bow of the next plate in the extended state of the relevant section of the plate chain (in the return section used in the input wrap-around transmission). The compensation length is determined by the indexing ratio of the plate link and the desired or possible bow width between the free-running pressure elements in the short plates.

The total length is calculated as follows:

(1)x_SB＝t_K-2·x_WD，

wherein x is_SBFor the width of the associated side bow, t_KIs a short index length and x_WDThe thickness (width in the chain running direction) of the rocking pressure members that are the pair of rocking pressure members.

(2)x_WD＝(l_i,K-t_K)/2，

Wherein l_i,KIs the short panel inner dimension.

The division being longer than TV by a division length t_LWith short indexing length t_KAnd therefore applies:

(3)t_L＝t_K·TV。

the compensation length a is calculated approximately as follows:

(4)A＝t_L-2·x_WD-2·x_SB，

so that it is approximately obtained from the above-described relationship of equations (1) to (4) for the compensation length a:

(5)A＝t_K·(TV-3)+l_i,K。

for example, at short indexing lengths t_KIn the case of 6.2mm, A is 0.58mm to 1.2mm (mm). In this case, a total length of 1.38mm to 2.4mm is obtained, which has an overlap length of, for example, conventional 0.8mm to 1.2 mm.

According to another aspect, a wrap-around transmission for a drive train is proposed, comprising at least the following components:

-a first pair of conical discs having a first rotation axis and a variable axial first disc spacing;

-a second pair of discs having a second axis of rotation and a variable axial second disc spacing; and

-a plate link according to any of the embodiments described above,

the two cone pulley pairs are connected to each other in a torque-transmitting manner in a driving manner according to a set pulley pitch by means of a plate chain, which is arranged in the chain width direction and is pressed axially into the traction means of a cone pulley pair.

With the wrap-around transmission proposed here (also referred to as a cone-pulley wrap-around transmission in the embodiments set forth here), it is possible to transmit torque from the transmission input shaft (in an accelerating or decelerating manner) to the transmission output shaft and vice versa, wherein the transmission can be at least partially steplessly adjusted.

The wrap-around transmission is provided for a drive train of, for example, a motor vehicle and comprises at least one first cone pulley pair arranged on a first shaft (for example a transmission input shaft) and a second cone pulley pair arranged on a second shaft (for example a transmission output shaft) and a wrap-around means provided for transmitting torque between the cone pulley pairs, i.e. the plate link described above. The conical disk pair comprises two conical disks which are oriented with the respective conical surfaces toward one another and are axially movable relative to one another. The (first) cone disc, also called a floating disc or a displacement disc, is displaceable (axially displaceable) along the axis of its shaft, while the (second) cone disc, also called a fixed disc, is fixed (axially fixed) in the direction of the shaft axis. The corresponding disc spacing can thus be changed.

During operation of the wrap-around transmission, the plate link (with respect to the axis of the respective shaft) is displaced in the radial direction by means of a relative axial movement of the conical disks of the conical disk pair between an inner position (small or minimum active circuit) and an outer position (large or maximum active circuit) due to the conical surfaces of the conical disks. The plate link thus runs on a variable operating circuit, i.e. with a variable running radius. In this way, different rotational speed and torque transmission ratios from one conical disk pair to the other can be set, preferably steplessly.

The wrap-around transmission proposed here has a plate chain according to the above description, wherein the plate chain has a low internal friction and therefore a high efficiency, wherein at the same time sufficient protection against chain buckling is provided. In addition, the strength of the plate link chain is improved. Alternatively or simultaneously, a reduced minimum effective circuit can be implemented with the plate link in that the short plates are shortened compared to conventional short plates.

According to another aspect, a drive train is proposed, which has at least the following components:

-at least one drive machine;

-at least one consumer; and

-a wrap-around transmission according to any of the embodiments described above,

wherein the at least one drive machine is connected with the at least one consumer by means of a wrap-around transmission in a variable transmission ratio for transmitting torque.

The drive train (e.g. of a motor vehicle for driving the motor vehicle via at least one drive wheel) is provided for transmitting a torque for use by the consumer, which is provided by one or more drive units, e.g. an internal combustion engine and/or an electric machine, and is output via its respective drive shaft, e.g. an internal combustion engine drive shaft and/or an electric drive shaft (rotor shaft), as required, i.e. taking into account a required rotational speed and a required torque. One use is, for example, generators for providing electrical energy or for transmitting torque to the drive wheels of a motor vehicle for driving the motor vehicle.

In order to transmit torque in a targeted manner and/or by means of a shift transmission having different transmission ratios, the use of the above-described wrap-around transmission is particularly advantageous, since the plate link enables a very high torque transmission efficiency and/or a high transmission ratio expansion due to a small minimum permissible working circuit in a small (radial) installation space.

Drawings

Hereinafter, the above-described utility model is explained in detail in the related art background with reference to the accompanying drawings showing a preferred configuration. The invention is not limited in any way by the purely schematic drawings, wherein it should be noted that the drawings are not dimensionally exact and are not suitable for defining dimensional proportions. The figures show:

FIG. 1 is a fragmentary portion of a plate link chain; and

FIG. 2 is a wrap-around transmission in a drive train.

Detailed Description

In fig. 1, three plates of the plate link 1 (see fig. 2) are shown in axial plan view, namely a short plate 4 (left-hand side, shown in solid lines) adjacent to a first long plate 5 (middle, shown in dashed lines) and a second long plate 6 (right-hand side, shown in dashed and dotted lines). The plates 4, 5, 6 each have a radially outer plate bracket 21, a radially inner plate bracket 22, a front bracket 23 (on the right in the illustration), and a rear bracket 24 (on the left in the illustration). The

plate bow

21, 22 has a maximum extension in the chain running direction 16. The

side brackets

23, 24 have a maximum extent in the radial direction 17. The plates 4, 5, 6 each comprise two pairs of rocking

pressure members

7, 8, 9, 10. The wobble pressure pairs 7, 8, 9, 10 each have a fixed

wobble pressure

11, 13 and a

free wobble pressure

12, 14. The rocking

pressure pieces

11, 13, 12, 14 are pin-shaped and have a maximum extent (corresponding to the pin axis) in the axial direction 18, i.e. a transverse extent 15, wherein the ends of the rocking

pressure pieces

11, 13, 12, 14 define the chain width 2. In this illustration, the axial direction 18 is directed into the plane of the page. Two plates 4, 5; 5. 6 are connected to each other by means of a common rocking pressure 8, 9. In the plane of the page, the chain run directions 16 point to the left and right, while the radial direction 17 points from below to above. The plates 4, 5, 6 thus link the pairs of rocking

pressure elements

7, 8, 9, 10 in a traction-transmitting manner in a closed loop (see fig. 2) throughout the plate link chain 1 (see fig. 2).

The plates 4, 5, 6 are here arranged such that the first long plate 5 is arranged between the short plate 4 and the second long plate 6 in the chain running direction 16. A pair of rocking

pressure members

7, 8; 8. 9; 9. 10 are each arranged at a predefined distance from one another, wherein the distance is defined by a respective in-

board dimension

43, 44, wherein the (short) in-board dimension 43 is present in the short board 4 and the (long) in-board dimension 44 is present in the long boards 5, 6. A pair of rocking

pressure members

7, 8; 8. the thickness 46 of 9 defines, in cooperation with the respective plate

inner dimensions

43, 44, the

indexing length

19, 20 defined by the rocking

pressure element pair

7, 8; 8. the respective contact points of the rocking

pressure elements

11, 13 of 9 define, wherein there is therefore a short indexing length 19 in the short plate 4 and a (relatively) long indexing length 20 in the long plate 5. In various embodiments, the plate link 1 (see fig. 2) comprises only these two types of plates 4, 5, 6. As can be seen in the short plates 4, the distance between the first and second rocking pressure part pairs 7, 8 or between the free

rocking pressure parts

12, 14 of the short plates 4 is ensured by the rear bracket 24 of the adjacent first long plate 5, since the bracket width 25 of this rear bracket 24 is matched to the short plate inner dimension 43. The bow width 25 is the (usually largest) extension of the front (and rear) side bows 23, 24. Advantageously, in a panel both

side brackets

23, 24 have the same bracket width 25; it is particularly advantageous if the

side brackets

23, 24 of the entire plate link 1 (see fig. 2) all have the same bracket width 25. As a result, the same or similar stress distribution and therefore the same or similar tensile plasticization occurs under the same external load in the (equally wide)

side brackets

23, 24.

When long plates 5 and short plates 4 are used in a plate link 1 (see fig. 2), the spacing between the free-running

pressure elements

12, 14 of the long plates 5, 6 is different, so that this cannot be represented by means of side brackets 23 of equal width. Therefore, it is usual to use (single) widened side brackets 45, for example (front) side brackets 45 of the first long plate 5, or to use radial webs (or radial brackets) which extend in a sheet-like manner between the two

plate brackets

21, 22 of the respective plate (not shown here).

It is now proposed here that the two side brackets 23, 24 (here in the short plate 4) have the same bracket width 25 and that an overlapping tip 26 is additionally provided on the front side bracket 23. The front bracket 23 is preferably a side bracket which, in the operating direction of the plate link chain 1 when it is used in the transmission 3, is initially pulled onto the respective conical pulley pair 31, 34 (see fig. 2). It is therefore assumed here that the direction of operation is to the right, which is the right side bow 23 of the two side bows of the plates 4, 5, 6. The total length 27 of the overlapping tip 26, i.e. the width in the chain running direction 16, is composed of a compensation length 28 and an overlap length 29, wherein in the illustrated (extended) state of the plate link 1, a region of the compensation length 28 is exposed and a region of the overlap length 29 overlaps with the adjacent (rear) side bow 24 of the next (here second long) plate 6. The total length 27 is defined as the distance between the point of maximum extension of the overlapping tip 26 in the chain running direction 16 and the point of maximum extension of the associated (front) side bow 23 of the associated plate 4 in the chain running direction 16 (in the chain running direction 16). The compensation length 28 is determined by the indexing ratio of the plate link 1 and the desired or possible bow width 25 between the free-running

pressure elements

11, 13 in the short plate 4.

In fig. 2, the transmission 3 is shown in a perspective view in a section of the drive system 30, wherein the plate link chain 1 runs as a traction means on two conical disk pairs 31, 34. The plate link 1 has a link width 2 which has a transverse extent 15 in the axial direction 18 (parallel to the rotational axes 32, 35) such that a defined disk spacing 33, 36 results in an action loop on the respective

conical disk pair

31, 34. Thus, by means of the wrap-around transmission 3, the transmission ratio is set by a first shaft 39 having a first axis of rotation 32, e.g. a transmission input shaft, and a second shaft 40 having a second axis of rotation 35, e.g. a transmission output shaft.

The plates 4, 5, 6 (not individually labeled here, see fig. 1) are linked to each other in a ring by means of a plurality of rocking pressure element pairs 7, 8, 9, 10 for transmitting tractive forces in the

return sections

41, 42. The plurality of plates are arranged side by side along the axial direction 18. Here, a (bilateral) chain run direction 16 (and also an axial direction 18 and a radial direction 17 (corresponding to the chain width 2 direction)) is defined at any point of the plate link chain 1, the orientation of which in space changes with the movement of the plate link chain 1. For example, a drive machine 37 is connected to the first shaft 39, wherein only the input gear receiving the torque is shown here. For example, a consumer 38, for example at least one drive wheel, is connected to the second shaft 40, wherein only the output gear for the output torque is shown here.

The plate link chain proposed here has a particularly long service life with a high overall strength of the plate link chain and/or can be operated with a very small minimum operating loop.

List of reference numerals

1 plate link chain

2 chain width

3 winding type speed variator

4 short plate

5 first long plate

6 second long plate

7 first pair of rocking press members

8 second pair of rocking pressure members

9 third rocking pair of pressure members

10 fourth rocking press pair

11 first fixed oscillating pressure element

12 first free rocking pressure member

13 second fixed rocking pressure member

14 second free-swinging pressure member

15 extend transversely

16 chain running direction

17 radial direction

18 axial direction

19 short index length

Index length of 20

21 radially outer plate segment

22 radially inner plate segment

23 front side bow

24 rear side bow

25 bow width

26 overlapping tip

27 total length

28 offset length

29 length of overlap

30 drive train

31 first conical disk pair

32 first axis of rotation

33 first disc space

34 second cone plate pair

35 second axis of rotation

36 second disc space

37 driving machine

38 consumption device

39 first shaft

40 second axis

41 first return section

42 second return section

43 short inboard dimension

44 long in-plane dimension

45 wide side bow

46 thickness of rocking pressure member pair

Claims

1. A plate link chain (1) for a wrap-around transmission (3) having a chain width (2) and having at least the following:

-a plurality of plates (4, 5, 6), i.e. short plates (4) and long plates (5, 6); and

-a corresponding number of pairs of rocking pressure members (7, 8, 9, 10) comprising a fixed rocking pressure member (11, 13) and a free rocking pressure member (12, 14), respectively, and having a transverse extension (15) in the direction of the chain width (2),

wherein, by means of the plurality of plates (4, 5, 6), the pairs of rocking pressure elements (7, 8, 9, 10) are linked in a manner transmitting traction forces into a closed loop and thus define a chain running direction (16), and a radial direction (17) transverse to the chain running direction (16) and transverse to the chain width (2), wherein the radial direction (17) is directed from the loop interior to the loop exterior,

wherein a plate (4, 5, 6) surrounds two oscillating pressure element pairs (7, 8; 8, 9; 9, 10) in each case, so that two fixed oscillating pressure elements (11, 13) and two free oscillating pressure elements (12, 14) are arranged in a plate (4, 5, 6) at a predetermined distance in the chain running direction (16) and thus define an index length (19, 20) between the contact points of the oscillating pressure elements (11, 12; 13, 14),

wherein each plate (4, 5, 6) has a radially outer plate bow (21), a radially inner plate bow (22), a front side bow (23) and a rear side bow (24), wherein the plate bows (21, 22) have a maximum extension in the chain running direction (16) and the front and rear side bows have a maximum extension in the radial direction,

it is characterized in that the preparation method is characterized in that,

the indexing ratio of the long indexing length (20) to the short indexing length (19) is greater than 1.35.

2. Plate link chain (1) according to claim 1, characterized in that,

the indexing ratio of the long indexing length (20) to the short indexing length (19) is greater than or equal to 1.4.

3. A plate link chain (1) according to claim 2, wherein the indexing ratio of the long indexing length (20) to the short indexing length (19) is greater than or equal to 1.5.

4. A plate link chain (1) for a wrap-around transmission (3) having a chain width (2) and having at least the following:

it is characterized in that the preparation method is characterized in that,

in at least one of the plates (4), the front bracket (23) and the rear bracket (24) have the same bracket width (25) in the chain running direction (16), wherein the front bracket (23) has an overlapping tip (26) with an extension pointing away from the associated fixed wobble pressure element (13) in the chain running direction (16).

5. Plate link chain (1) according to claim 4, characterized in that,

the plates (5) adjacent to the plate (4) with the overlapping tips (26) do not have radial webs.

6. Plate link chain (1) according to claim 5, characterized in that all plates (4, 5, 6) do not have radial webs.

7. Plate link chain (1) according to one of claims 4 to 6, characterized in that,

the front bow (23) having an overlapping tip (26) according to claim 4,

wherein the overlapping tip (26) has an overall length (27) in the chain running direction (16), wherein the overall length (27) consists of a compensation length (28) and an overlap length (29), wherein the compensation length (28) is 8% to 20% of the short division length (19), wherein the overlap length (29) is 10% to 20% of the short division length (19).

8. A wrap-around transmission (3) for a drive train (30), characterized in that it comprises at least the following components:

-a first pair of conical discs (31) having a first rotation axis (32) and a variable axial first disc pitch (33);

-a second pair of discs (34) having a second axis of rotation (35) and a variable axial second disc spacing (36); and

-a plate link (1) according to any of the preceding claims,

wherein the two cone pulley pairs (31, 34) are connected to each other in a torque-transmitting manner in a driving manner according to a set pulley distance (33, 36) by means of the plate link chain (1), which is arranged to be pressed axially into the traction means in each cone pulley pair (31, 34) in the direction of the chain width (2).

9. Drive train (30), characterized in that the drive train has at least the following components:

-at least one drive machine (37);

-at least one consumer (38); and

-a wrap-around transmission (3) according to claim 8,

wherein the at least one drive machine (37) is connected with the at least one consumer (38) by means of the wrap-around transmission (3) in a variable transmission ratio for torque transmission.