JP2009510367A - Chain link plate, chain including this chain link plate, chain drive formed by this chain, and vehicle equipped with this chain drive - Google Patents

Abstract

  The present invention relates to a chain link plate (4) and a link plate chain comprising a number of chain link plates hinged to one another via a pressing member (2) for driving the vehicle. The pressing member extends in the lateral direction with respect to the longitudinal direction of the link plate chain, and contact surfaces are formed on the pressing member and the chain link plate, respectively. Along the abutting surface, the pressing member and the chain link plate abut against each other for force transmission. Each contact surface is formed to be optimized.

Description

  The present invention relates to a chain link plate of the type described in the superordinate conceptual part of claim 1. Further advantageous configuration possibilities of the invention are described in the dependent claims. The invention further relates to a link plate chain formed under the use of a chain link plate according to the invention as well as a chain drive constructed under the inclusion of such a link plate chain. The invention further relates to a vehicle comprising this type of chain drive.

  Chain link plates of the type mentioned at the outset as well as link plate chains are known from the prior art in various forms, as will be explained later. In addition, this type of chain link plate as well as the link plate chain formed under its use is limited in terms of its force transmission capacity, so that the chain link plate is first damaged, for example by force peaks, It is known that it can lead to failure. This malfunction appears as a tear of the chain link plate. The chain link plate may end up leading to failure or tearing of the entire link plate chain. This is because separate chain link plates, each arranged between the same joint members, have to handle the force transmission of the broken chain link plate, which results in a stronger load. It is. This stronger load leads to individual chain link plates approaching the limit of force transmission capacity, or even exceeding this limit.

  An object of the present invention is to provide a chain link plate having higher strength and a link plate chain using the same. In addition, it is desirable that wear be reduced and that the elastic elongation of the chain link plate or link plate chain be less. In particular, the present invention should have few parts that must be assembled for the production of the link plate chain. This is achieved according to the invention by the fact that at least the individual link plates have a greater link plate thickness, i.e. the chain link plates according to the invention are thicker.

  This leads to a high shear area with a large abutment surface between the chain link plate and the pressing member or rocking member at the chain joint or chain connection and a smoother punching surface. Furthermore, this achieves a very good squareness between the swinging member or pressing member and the chain link plate. With this type of clean abutment surface, chain shear can be reduced or even avoided. The lower pressure also reduces the rim flow and can best be avoided.

  However, the link plate thickness cannot be increased arbitrarily in view of the punching quality and the bending load of the rocking member or the pressing member. Similarly, it should also be taken into account that the tool cost increases greatly depending on the punching thickness.

  Tilt movement during the entry of the chain into the gear, caused by the moment between the teeth and the link plate, during the formation of the chain link plate according to the invention and in the use of the chain link plate in a toothed chain Has the advantage that it is advantageously influenced. This is because a good squareness of the link plate with respect to the teeth is guaranteed. This results in better guidance and reduction or avoidance of the shear load at the mesh. In addition, this creates a lower pressure. As a result, edge flow can be reduced or avoided.

  According to the invention, several dimensional ratios that can be grasped as numerical values have proved particularly advantageous. For example, it is particularly advantageous if the ratio of the pitch 1 to the link plate thickness d is in the range of 3.7 to 5.5. Again, it is advantageous if the ratio of the rocking member height or the pressing member height h to the link plate thickness d is in the range of 1.3 to 1.9. A ratio of the rocking member width or pressing member width w to link plate thickness d in the range of 0.8 to 1.2 is also particularly advantageous. Furthermore, it is particularly advantageous if the ratio of web width s to link plate thickness d is in the range from 0.8 to 1.2.

  As described above, the present invention comprises a number of chain link plates that are hingedly connected to one another via a swinging member or a pressing member, particularly for vehicle transmissions, vehicle drive trains or vehicle engine auxiliary drives. It also relates to the link plate chain provided. At this time, the pressing member extends in the lateral direction with respect to the longitudinal direction of the link plate chain, and the pressing member and the chain link plate are each formed with a curved contact surface. Along the abutment surface, the pressing member and the chain link plate abut against each other for force transmission, each abutment surface has a width extending in a direction transverse to the longitudinal direction of the link plate chain, Within the cross section extending transversely to this width, it has the length of the arc as viewed in the longitudinal direction of the link plate chain.

  There are different configurations for the link plate chain of the type described here, depending on its use in vehicle drive. When used in a continuously variable conical pulley chain variator (CVT) as part of a vehicle transmission, the pressing member has a specially shaped end face. A tensile force between the conical disk, so-called conical pulley, and the chain is transmitted as a frictional force through the end face. For most other uses in vehicle drive, the link plate chain is a toothed chain. That is, the chain link plate has teeth on at least one side, and a tensile force is transmitted between the gear and the chain via the teeth. This type of toothed chain is known from the background art, for example US Pat. No. 4,906,224. Such a toothed chain can be used in a number of situations relating to vehicle drive, for example in an all-wheel drive distribution transmission, in a front-side transmission for bridging the axle distance differentially, in a hydraulic auxiliary in the transmission. As a drive chain of the unit, as a valve mechanism control chain of an internal combustion engine, or other auxiliary unit of a vehicle (refrigerant pump, lubricant pump, air conditioning compressor, generator, starter motor, hybrid additional motor, brake power booster And the like).

  A link plate chain of the kind described here consists of a number of chain link plates that are hingedly connected to one another via pressing members.

  In this case, force transmission between the pressing member and the chain link plate is performed on the pressing member and the chain link plate, and the pressing member and the chain link plate are brought into contact with each other along the pressing surface. The pressing members are also called pins, and are inserted into the two link plate openings as a pair of swing joints. The two link plate openings are often combined into one large opening in the case of a chain for a conical disk drive.

  Various functional surfaces are formed on the pressing member. The pair of pressing members positioned opposite to each other in one opening of the link plate chain abuts each other in the rolling region or the rolling surface. When the chain is bent, a rolling motion is performed at this position by a predetermined bending angle based on the geometric shape of the pressing member.

  At the contact surface of the pressing member, the pressing member contacts the contact surface of the chain link plate. As a result, a surface pressure is generated between the contact surface of the chain link plate and the contact surface of the pressing member. These abutment surfaces must satisfy a number of requirements. First, the generated surface pressure should not be excessively large based on the shape of the abutment surface, and secondly, the abutment surface prevents the pressing member from rotating within the opening of the chain link plate. It should also serve as anti-rotation.

  For this purpose, link plate chains are already known with segmented abutment surfaces having two radii that are clearly different for each segment. For example, US Pat. No. 6,277,046 shows a link plate chain comprising two abutment surfaces with two different radii on the pressing member. These different radii achieve rotation prevention. As a result, the pressing member does not rotate within the opening of the chain link plate. Another known link plate chain is described in US Pat. No. 5,236,399. In this known link plate chain, two different radii are again provided on the abutment surface or the center of the radius is shifted to prevent rotation.

  In addition to this rotation prevention, the abutment surface must also meet the requirements of a tear-resistant and durable link plate chain. For this purpose, the contact pressure in the contact area between the pressing member and the chain link plate must not exceed a predetermined value. According to the understanding so far, here a contact surface having a small curvature and thus a large radius of curvature was required. Therefore, according to the known link plate chain described above, it is necessary to increase the radius of curvature in order to achieve a reduction in contact pressure at the abutment surface.

  Surprisingly, the local stress peak is not the cause of the occurrence of the compressive stress peak in the contact area of the abutment surface of the pressing member and the link plate chain is due to the small radius of curvature (and hence the large curvature) It was found that it occurred strongly in the transition area between the radii of curvature. This is because in known link plate chains, a clear stress peak is presented in the transition region from one radius of curvature to another, and strictly speaking when this transition extends tangentially, i.e. without creases. Leads to the recognition that it is also presented.

  A corresponding description is shown in FIG. FIG. 1 shows that a compressive stress peak occurs in the transition region between a small radius of curvature indicated by K and a large radius of curvature indicated by G, and the compressive stress in the region of small radius of curvature is in the region of large radius of curvature. It shows that it is not clearly higher than the compression region. That is, it is recognized that a small radius of curvature is not the cause of the occurrence of a local high compressive stress peak, but a transition region from one radius of curvature to another radius of curvature is a problem.

  That is, it has been found that although the rolling surface is provided on the pressing member for rotation when the link plate chain is bent, the pressing member rotates on the contact surface. That is, even in the link plate chain provided with the rotation preventing means, relative rotation occurs in the contact surface area between the chain link plate of the link plate chain and the pressing member. That is, a shearing motion is generated on the contact surface between the pressing member and the chain link plate. This leads to incorrect correspondence of the abutment surface at the transition from one radius of curvature to another. That is, the curvature of the chain link plate no longer matches the curvature of the pressing member.

  Now, this shearing results in a transition from planar support in the contact area between the pressing member and the chain link plate to linear support observed across the width of the pressing member, and thus in the increased contact pressure in this contact area. It reaches. As a result, the maximum pressure value shown in FIG. 1 is generated here. This situation has never been taken into account. This is because, in the current understanding, only the maximum radius of curvature has been aimed at to reduce the load in the contact area between the pressing member and the chain link plate.

  In other words, in the contact surface region, on the one hand, an allowable surface pressure requirement must be considered, and on the other hand, the rotation of the pressing member relative to the chain link plate must be prevented. Exists.

  The link plate chain is formed for driving a vehicle with a plurality of chain link plates hingedly connected to each other via a pressing member. At that time, the pressing member extends in the transverse direction with respect to the longitudinal direction of the link plate chain, and the pressing member and the chain link plate are formed with curved contact surfaces, respectively, along the contact surface. Thus, the pressing member and the chain link plate abut against each other for force transmission, and each abutment surface has a width extending in a direction transverse to the longitudinal direction of the link plate chain and a direction transverse to the width. In the cross-section extending in the direction of the length of the link plate chain, and having at least three regions each having a different curvature along the length of the arc.

  In other words, a link plate chain having an abutment surface having at least three regions each having a different curvature along the length of the curve as seen in a cross-sectional view along the longitudinal direction of the link plate chain. As a result, a large jump in curvature is avoided, and nevertheless, a region having a large and small radius of curvature is provided to prevent rotation of the pressing member relative to the chain link plate.

  Thus, it is not important for the known recognition to form as small a curvature as possible with a large radius of curvature in the contact surface area, but the contact surface of the pressing member and the contact surface of the chain link plate This translates into the recognition that a sufficient number of different curvatures are provided, yet a jump in curvature to high stress peaks is avoided.

  In this case, in an advantageous configuration, the ratio of the maximum curvature to the minimum curvature is at least 2. According to this configuration, there is sufficient prevention of rotation of the pressing member relative to the chain link plate, and at least three different curvatures are provided on the contact surface along the length of the arc or curve. Combined with the feature of being, it is achieved that the jump in curvature is sufficiently small. As a result, an unacceptably high compressive stress does not occur in a region where the curvature of the contact surface jumps.

  In so doing, the curvature in at least three regions can be constant along the length of the arc in each region. That is, the length of the curve or arc can be constituted by at least three arc segments as viewed in a cross-sectional view along the axial direction of the link plate chain. As a result, the jump between the different curvatures of the arc segment becomes small, and when viewed as the radius of curvature, the large radius jump leading to a high stress peak is 1 to 5 mm in the pressing member of the link plate chain for driving the vehicle. In contrast, the jump in the individual radius of curvature is achieved, for example, first from 1 mm to 3 mm and then from 3 mm to 5 mm.

  Further, the curvature in at least three regions may change along the length of the arc in each region. In other words, this means that a constant curvature is not provided in three different regions, but the curvature can vary, for example, continuously in individual regions. As a result, it is possible for the link plate chain to be composed of spiral segments whose curvature, and thus the radius of curvature, varies continuously along the length of the arc, as viewed in the axial longitudinal section of the link plate chain. In addition to this spiral segment, it is also possible to have an abutment surface shape consisting of an elliptical segment whose curvature changes continuously between a minimum value and a maximum value when viewed in an axial longitudinal section. In addition to these shapes, the curved length segment can be a hyperbolic or parabolic segment, or a contact surface with a curved segment whose second derivative is generally continuous along the length of the arc. It is.

  In another configuration, the abutment surface further includes a curved segment along the length of the arc, with a minimum radius of curvature along the length of the arc and approximately in the middle of the length of the arc.

  By arranging the minimum radius of curvature approximately in the middle of the length of the arc, it is achieved that the maximum curvature is located outside the respective end region of the abutment surface. As a result, in the pressing member, it is achieved that the initial radius of curvature is more rigid and thus more difficult to bend than the arrangement in which the initial radius of curvature is located in the respective end region of the abutment surface. That is, if the deflection of the pressing member is small, the tensile force is more evenly distributed to all the chain link plates arranged side by side, the chain link plate achieves higher fatigue strength, and the link plate chain Can transmit higher tensile forces overall.

  In other words, with such a link plate chain, it is achieved that no significant jump of contact stress occurs in the transition regions between the different radii of curvature of the contact surfaces. The prevention of the rotation of the pressing member in the opening of the chain link plate is also improved as compared with the known link plate chain.

The present invention will be described in detail below with reference to the drawings.
FIG. 1 is a diagram showing the course of surface pressure in the contact area of the abutment surface of the pressing member and the chain link plate in a known configuration with two distinctly different radii of curvature;
FIG. 2 is a schematic view of a known link plate chain for use in a CVT transmission, where the area indicated by A is shown enlarged in FIG. 1;
3 is an enlarged view of the chain link plate and the pressing member according to the first embodiment;
FIG. 4 is an enlarged view of the pressing member according to the second embodiment.
FIG. 5 is an enlarged view of the pressing member according to the third embodiment and a view showing a toothed chain constituted by the pressing member.
FIG. 6 is an enlarged view of a pressing member for explaining individual symbols.
FIG. 7 is a view similar to FIG. 1 for explaining the surface pressure progress in the contact surface area between the pressing member of the link plate chain and the chain link plate.
FIG. 8 is a view showing a chain link plate provided with a swing pressing member according to the present invention.

  As already mentioned above, FIG. 1 shows the course of the surface pressure in the abutment surface area between the pressing member of the known link plate chain and the chain link plate. In the transition region between the small radius of curvature indicated by K and the large radius of curvature indicated by G, a conspicuous maximum value of the contact pressure between the pressing member and the chain link plate occurs. In this case, the cause is a discontinuous curvature radius between the small curvature radius K and the large curvature radius G, that is, the jump of the curvature radius.

  FIG. 2 shows an excerpt of a known CVT link plate chain 1. The CVT link plate chain 1 includes a large number of swing members or pressing members 2 and 3, so-called rocker pins, thrust pieces or cradle transmission members, and a large number of chain link plates 4. Since the area indicated by A in FIG. 2 is enlarged and shown in FIG. 1, FIG. 1 shows the pressing member 2 and the chain link plate 4.

  FIG. 3 shows an enlarged view of the pressing member 5 and the chain link plate 6 of the link plate chain 7 according to the first embodiment.

  As can be seen without any problem, two contact surface regions 8 and 11 are formed between the pressing member 5 and the chain link plate 6. At that time, the contact surface region 8 is formed by the contact surface 9 on the pressing member 5 side and the contact surface 10 formed on the chain link plate 6 side in a complementary manner. Similarly, the contact surface region 11 includes a contact surface on the pressing member 5 side and a contact surface on the chain link plate 6 side.

  The pressing member 5 and the chain link plate 6 are in contact with each other on the contact surface 9 or the contact surface 10 for force transmission. The chain link plate 6 has a specific width in the lateral direction with respect to the drawing plane of FIG. 3, and a plurality of the chain link plates are arranged side by side and come into contact with the same pressing member 5. The tensile force transmitted by is distributed to the individual abutment surface areas between the pressing member and the chain link plate. Seen in an axial longitudinal section extending transversely to the width of the link plate chain 7, each abutment surface 9, 10 has an arc or curved length represented by braces 12 in the drawing, respectively.

  FIG. 3 shows a first embodiment of a link plate chain according to the invention. In the first embodiment, the contact surface 9 of the pressing member 5 and the contact surface 10 of the chain link plate 6 that is complementary to the contact surface 9 have different curvatures, that is, a plurality of regions having different curvatures. It is formed in preparation. In order to represent these curves on the drawing, FIG. 3 shows regions with different curves each having a different radius of curvature 13, 14, 15, 16 in broken lines. In this case, in order to express different curvatures in the contact surfaces 9 and 10 on the drawing, which are difficult to visually recognize, the respective curvature radii 13, 14, 15, and 16 are respectively set to areas having different curvatures. Are shown vertically.

  FIG. 3, however, clearly shows that the curvature in the region of curvature radius 13 is smaller than the curvature in the region of curvature radius 14. As a result, the radius of curvature in the region 13 is larger than the radius of curvature in the region 14. Correspondingly, the radius of curvature in region 15 is smaller than the radius of curvature in region 14 and the curvature in region 15 is greater than the curvature in region 14. As a result, the contact surface 9 of the pressing member 5 in the contact surface region 8 and the contact surface 10 of the chain link plate 6 which is complementary thereto already have three different curvatures. Or along the length of the curve. In addition, FIG. 3 shows that an abutment surface 9, 10 is formed with another fourth region 16 having a radius of curvature 16 different from the radius of curvature regions 13, 14, 15 along the length of the arc. It also shows that. Correspondingly, the contact surface area 11 also has areas with different curvatures. At that time, the contact surface region 11 is provided with only three regions having different curvatures.

  FIG. 4 shows a pressing member of a link plate chain according to the second embodiment. In this case, this pressing member is also a pressing member of the link plate chain for the conical disk winding transmission.

  In this pressing member 5, reference numeral 17 is attached to the rolling surface. With the rolling surface 17, the pressing member 5 is in rolling contact with the pressing member positioned opposite (again, in the case of a pressing member pair). In this case, the basic configuration is as shown in FIG. The pressing member 5 also has two abutting surfaces 18 and 19 arranged on the abutting surfaces formed complementarily of a chain link plate (not shown). The upper contact surface 18 has a point indicated by B. On this point B, the maximum curvature value is located. In short, at the point B, the radius of curvature depicted perpendicularly to the abutment surface 18 for the sake of explanation takes its minimum value. From this point B, the radius of curvature increases in both directions. As a result, the curvature continuously decreases in both directions starting from the point B on the contact surface 18. At that time, the radius of curvature starts from the point B and increases in accordance with the elliptical segment in the direction of the arrow 20 and increases in accordance with the spiral segment in the direction of the arrow 21.

  FIG. 4 shows a similar characteristic from the point C having the maximum value of curvature at the lower abutment surface 19. The radius of curvature then increases in the direction of the arrow 22 according to the hyperbolic segment and in the direction of the arrow 23 according to the parabolic arc segment.

  FIG. 5 is a view similar to FIG. In this case, the pressing member 24 shown in FIG. 5 is a pressing member of a toothed chain, and the toothed chain can be used, for example, as a toothed chain for a drive device or as a toothed chain in a conveying device. The pressing member 24 also has a rolling surface 25, and the rolling surface 25 can make rolling contact with the pressing member disposed in correspondence with the pressing member pair. The pressing member 24 also has an upper contact surface 26 and a lower contact surface 27. At that time, the configuration of the abutting surface 26 is such that the radius of curvature from the point B (the radius of curvature is also depicted by a broken line perpendicular to the contour of the abutting surface) in both directions of the abutting surface 26. It has been selected to increase along the length of the arc represented by brackets 12. Correspondingly, the radius of curvature of the abutment surface 27 increases in both directions from the point indicated by C having the greatest curvature (depending on the smallest radius of curvature).

  Further, as can be seen, when the maximum curvature of the contact surface, and hence the minimum radius of curvature, extends in the center of the contact surface as seen by the length of the arc or curve of the contact surface, A rigid design is possible with respect to pressure.

  FIG. 6 serves to illustrate this relationship. Again, the alphabet B or C indicates that the upper contact surface or the lower contact surface has the maximum curvature and thus the minimum radius of curvature in the respective contact surfaces. As can be seen from the drawing without any problem, the point B or C is located approximately in the middle of the arc length 28. Even under this, a region having a radius of curvature indicated by a broken line extends. It has been mentioned earlier that the point with the greatest curvature is located along the length of the arc (measured by arc length 28) approximately in the middle of the abutment surface. It has been found that a similar advantageous effect is achieved in the region D of 40% to 60% of the length 28. This region coincides with an angle region of 30 ° to 60 ° of the tangent line on the lower contact surface of the pressing member. In this case, an angle of 30 ° to 60 ° is measured between the tangent line 29 and the chain traveling direction 30. The point having the maximum curvature of each contact surface is within 40% to 60% of the total length of the arc length 28 or 30 ° to 60 ° of the angle formed by the tangent line 29 and the chain traveling direction 30. Thus, a pressing member that is rigid and thus resistant to bending can be obtained. This again leads to an increase in the tensile force that can be transmitted by the link plate chain or the toothed chain.

  FIG. 7 shows the progress of contact pressure between the pressing member 5 of the link plate chain and the chain link plate 6 at the lower contact surface selected in the drawing (in this case, the concept of the link plate chain is toothed) Including chains). Comparing the contact pressure progress of the known link plate chain shown in FIG. 1 with the contact pressure progress of the link plate chain shown in FIG. 7, the outstanding maximum contact pressure shown in FIG. 1 disappears. Can be seen immediately. In order to depict the course of contact pressure at the abutment surface, a representation that is standardized to each other is selected in both figures. As a result, the length of each arrow represents the height of the contact pressure at each observed point on the contact surface. Thus, it can be seen that the outstanding contact pressure maximum value shown in FIG. 1 disappears without any problem based on visual inspection.

FIG. 8 shows the chain link plate 4 and the swing member of the pair of pressing members or the pressing member 2 according to the present invention. The symbols used there serve to clarify the dimension ratios already mentioned and have the meaning explained below:
d: Link plate thickness s: Web width l: Pitch h: Oscillating member height (oscillating pressing member height or pressing member height)
w: swing member width b: inner web width.

According to it, the dimension ratios according to the invention already described are as follows:
l / d = 3.7 to 5.5 and / or h / d = 1.3 to 1.9 and / or w / d = 0.8 to 1.2 and / or s / d = 0.8 to 1.2.

  The advantages obtained from these values have already been explained above. Also advantageously, the chain link plate is manufactured as a stamped part, in particular as a precision stamped part, and the proportion of the smooth cut surface is at least approximately 70% of the link plate thickness.

It is a figure which shows progress of the surface pressure in the contact surface area | region of the contact surface of a press member and a chain link plate in the well-known structure which has two different curvature radii. 1 is a schematic view of a known link plate chain for use in a CVT transmission (FIG. 1 is an enlarged view of the area indicated here by A). It is an enlarged view of a chain link plate and a pressing member according to the first embodiment. It is an enlarged view of the pressing member by 2nd Embodiment. It is a figure which shows the enlarged view of the press member by 3rd Embodiment, and the toothed chain comprised from this press member. It is an enlarged view of the pressing member for demonstrating each code | symbol. It is a figure similar to FIG. 1 for demonstrating surface pressure progress in the contact surface area | region between the press member of a link plate chain, and a chain link plate. It is a figure which shows the chain link plate provided with the rocking | swiveling press member by this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Link plate chain 2 Press member 3 Press member 4 Chain link plate 5 Press member 6 Chain link plate 7 Link plate chain 8 Contact surface area 9 Contact surface of press member 10 Contact surface of chain link plate 11 Contact surface area 12 Curly braces 13 Curvature radius 14 Curvature radius 15 Curvature radius 16 Curvature radius 17 Rolling surface 18 Contact surface 19 Contact surface 20 Arrow 21 Arrow 22 Arrow 23 Arrow 24 Press member 25 Rolling surface 26 Upper contact surface 27 Lower Side contact surface 28 Arc length 29 Tangent 30 Chain traveling direction B Point having maximum curvature C Point having maximum curvature D Region of 40% to 60% of arc length d Link plate thickness s Web Width l Pitch h Swing member height w Swing member width b Inner web width

Claims (11)

  In a link plate chain, particularly a chain link plate for a link plate chain for driving a vehicle, the chain link plate is operatively connected to at least one joint member, for example, a swing member, a pressing member or a swing pressing member. The chain link plate is characterized in that the numerical ratio of the swing member width to the link plate thickness is 0.8 to 1.2.   The chain link plate according to claim 1, wherein a numerical ratio of the swing member height to the link plate thickness is 1.3 to 1.9.   The chain link plate according to claim 1 or 2, wherein a numerical ratio of a link plate chain pitch to a link plate thickness is 3.7 to 5.5.   The chain link plate according to any one of claims 1 to 3, wherein a numerical ratio of the web width to the link plate thickness is 0.8 to 1.2.   The chain link plate according to any one of claims 1 to 4, wherein the chain link plate is manufactured as a punched part, particularly as a precision punched part.   The chain link plate of claim 5, wherein the proportion of the smooth cut surface is at least approximately 70% of the link plate thickness.   A link plate chain, wherein the chain link plate according to any one of claims 1 to 6 is used.   The link plate chain according to claim 7, wherein the link plate chain is configured as a CVT chain.   The link plate chain according to claim 7, wherein the link plate chain is configured as a toothed chain.   A chain drive, wherein the link plate chain according to any one of claims 1 to 9 is used.   A vehicle, characterized in that the chain drive according to claim 10 is used.

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