EP1893890A2

EP1893890A2 - Chain

Info

Publication number: EP1893890A2
Application number: EP06742353A
Authority: EP
Inventors: Marcus Junig; Anton Simonov; Martin Vornehm; Olga Ispolatova; Michael Pichura
Original assignee: LuK Lamellen und Kupplungsbau Beteiligungs KG; LuK Lamellen und Kupplungsbau GmbH
Current assignee: Schaeffler Buehl Verwaltungs GmbH; LuK Lamellen und Kupplungsbau GmbH
Priority date: 2005-06-14
Filing date: 2006-05-17
Publication date: 2008-03-05
Also published as: WO2006133667A2; JP5082163B2; DE112006001340A5; KR20080015396A; CN101198808A; CN101198808B; JP2008544173A; WO2006133667A3

Abstract

The invention relates to a chain, in particular, an inverted tooth chain, made from a number of chain links forming link bundles, connected by means of a joint to adjacent link bundles. Each roller piece of a joint is connected to the links of a link bundle through a fixing opening and two roller pieces of adjacent link bundles form the joint. The roller pieces roll and/or slide on each other with one bearing profile each and the link bundles comprise at least one guide link. The roller piece comprises a guide profile connected to a bearing profile by means of a first connector profile and a second connector profile, the guide link comprising at least one fixing opening with an undercut in the region of the first and/or second connector profile.

Description

link chain

The present invention relates to a link chain and a guide tab for a link chain.

Chains are known in many ways from the prior art. Can be used chains, z. B. in a frictional torque transmission in a chain-disc belt transmission (CVT transmission) and in a form-fitting Drehmomentübertragungsweise as pin chains, roller chains or chains, for example. Such toothed chains can in turn have a joint connection, which comprises two hinged pressure plates which articulate on each articulated joint.

For example, in toothed chains different types of tabs are used, since the chain must be guided transversely to its direction of rotation. So-called guide straps are integrated into the chain especially for these tasks, whereby it is fundamentally possible to distinguish between internally guided and externally guided toothed chains. In this case, internally guided toothed chains are guided over special chain links in the region of the middle of their extension transversely to the direction of rotation. Another possibility is realized in an externally guided chain, in which the outermost link plates in a special embodiment, the chain lead, that is, the chain protrudes laterally with their guide plates on the working together with her gear out.

For these guide plates, in turn, a plurality of embodiments is known from the prior art, which among other things also result from the load, which differs substantially in such guide plates from the load on the remaining chain links.

Areas of use for such toothed chains are, for example, timing chains which at least indirectly connect the crankshaft to the camshaft of an internal combustion engine and thus control the valves which serve to change the gas. How such timing chains or chain drives are performed is known in the art and will not be further elaborated here. A further field of application for such toothed chains are, for example, four-wheel drive concepts in which, starting from a transfer case, part of the drive power is conducted to the rear wheels via a cardan shaft, while the remaining part is led via such a chain drive to a further shaft extending substantially parallel to the drive shaft which then leads the power to the front wheels.

From the prior art, such as. For example, US Pat. No. 5,445,570, it is known that a press fit is used between the guide plate and the entire rocker pressure piece circumference, which fixes the two parts to one another. This interference fit causes very high stresses in the guide plate at the smallest radii. Furthermore, the reduced stiffness of the edge guide tab relative to the toothed plate causes a uniform elongation of the chain links and thus a uniform pitch throughout the chain according to the prior art. This reduced rigidity is achieved in a variety of ways, for. B. by a deep incision on the axis of symmetry from the upper back of the guide tab forth, or by a smaller thickness of the guide tab. This incision in turn causes a deflection of the edge tab or guide tab, because the neutral fiber is in the lower region, as can be seen from the figures.

Based on this prior art, the present invention seeks to provide a guide plate of a silent chain with improved elastic properties of the overall plate and the contact zone to the chain link.

This problem is solved by a link chain, in particular toothed link chain, of a plurality of tabs, which each form latches, which are connected to a hinge in each case with adjacent latches stacks, wherein in each case a rocker joint of a joint with the lugs of a lug stack is connected by a mounting opening and two rocker pieces of adjacent plate stacks form the joint, whereby the rocker pieces can roll and / or slide on each other with a rolling profile and wherein the plate stacks comprise at least one guide plate, wherein the weighing piece comprises a guide profile which has a first connecting profile and a second connecting profile with a weighing profile is connected, wherein the guide tab has at least one attachment opening, which has an undercut in the region of the first and / or second connection profile. In a further development, it is provided that one undercut is arranged in each case in the region of the first connection profile and the second connection profile of both rocker pieces. In this case, at least one of the undercuts may be arranged in the region of a rolling ridge of a rocker.

The above-mentioned problem is also solved by a guide tab for a link chain, in particular toothed link chain, with two mounting holes for attachment to a respective bolt, in particular a rocker, wherein the mounting holes has large and small radii over its circumference, wherein in at least one area with a small radius of the mounting holes an undercut is arranged.

The undercut may preferably be at least partially parabolic. It is preferably provided that the attachment opening has two areas with small radii, in each of which an undercut is arranged.

The above-mentioned problem is also solved by a guide tab for a link chain, in particular toothed link chain, with mounting holes for attachment to a bolt, in particular a rocker, wherein the guide plate between the mounting holes on one side has a recess and on the other side a bulge, said the recess and the bulge are arranged so that a waisting arises between the plane of symmetry and the fastening openings.

The aforementioned problem is also solved by a transmission with a link chain according to one of the preceding claims.

According to the invention, this is achieved by a shape optimization of the guide tab to reduce the critical stresses. Furthermore, in some places with particularly small radii by form optimization, the risk of damage is reduced by a production-related degree of rolling. The shape optimization is carried out so that the Zahnlaschenelastizität this edge tab or guide tab is improved both in terms of pure longitudinal stiffness, as well as with respect to a bending under tensile force. For this purpose, contour sections are used for special undercuts that can be described by a parabolic function. These undercuts are executed at the places where a rolling ridge is to be expected. The undercut detaches in a zone from the rocker, in - A - there is a slight curvature of the rocker pressure contour. As a result, although the contact area between the rocker pressure plate and the link plate is deliberately reduced, this in turn reduces the stresses and thus reduces or even avoids the risk of chain linkage failure.

A double waisting of the guide plate in each case between the axis of symmetry and the bores makes it possible to reduce both the longitudinal rigidity and, at the same time, to achieve a lower deflection under tensile force comparable to the toothed plates. This lower deflection results from the fact that the neutral fiber is much less underneath the holes and thus differs significantly from the prior art. At the same time, the guiding property, that is, the tooth coverage, is sufficiently maintained. Thus, the elastic properties of the guide tab are matched to those of the toothed plate, so that they in turn have substantially the same pitch in operation.

In the following, embodiments of the invention will be explained with reference to the accompanying drawings. Showing:

Fig. 1 is a side view of a link chain;

Fig. 2 is a plan view of a link chain;

3 shows an embodiment of a guide tab according to the invention;

FIG. 4 shows the weight piece and the contour of the associated receiving opening in FIG. 3; FIG.

5 shows a further embodiment of a guide tab according to the invention;

Fig. 6 is a guide plate according to the prior art;

7 shows the longitudinal expansion in the guide strip according to the invention;

Fig. 8 shows the bending of a guide tab according to the invention. Fig. 1 shows a side view and Fig. 2 is a plan view of a prior art link chain with Zweilaschenverband. With reference to Figures 1 and 2, the basic structure of link chains and the terms used in the embodiments of the invention will be explained. The exemplary embodiments are described using the example of a link chain with a two-strap connection, but are also applicable to a link chain with a three-link bandage. The link chain 1 comprises a plurality of tabs 2 and counter-tabs 2 '. The tabs 2 and opposing tabs 2 'are each arranged alternately and connected to hinge pin 4 as a joint. Both ends of a tab are thus connected by means of a joint with one or two counter-tabs, correspondingly both ends of a counter-tab are connected by means of a hinge with one or two tabs. The hinge pin 4 may be in one piece, but are preferably in two parts, wherein a rocker 5 is associated with the tabs and on one of the mating flap 2 associated rocking piece 5 'unrolls. For this purpose, the rocker pieces 5, 5 'each have a rolling profile 7 or T, with which they can roll or slide on one another. The rolling profiles 7, T may be identical or different. Transversely to the direction L, this is marked with an arrow with the reference L, the tabs 2 and 2 'counter-tabs are stacked so that between two transverse to the direction L juxtaposed hinge pin 4 is arranged an overlapping arranged counter-tab and vice versa between two transverse to Running direction adjacent counter-tabs each overlapping a tab is arranged. Of course, this does not apply to the tabs 2 or counter-tabs 2 'arranged on the outside transversely to the running direction L, these have a neighbor only on one side. The lug sets of tabs 2 thus formed in each case form a chain link 8 in packets, correspondingly, the (counter) tab packets of counter tabs 2 'form a chain link 8' in packets. The tabs 2 and counter-tabs 2 'are identical components in the present embodiment, a distinction between tabs 2 and 2 opposite tabs can be seen only by the arrangement. Therefore, only tabs 2 are discussed below, since they are identical to the counter-tabs except for the packet-wise arrangement. In Fig. 2, a stack of three tabs 2 and two opposing tabs 2 'is shown, but here also can be provided with any other number of tabs 2 and mating tabs 2' stack.

The tabs 2 are - as can be seen in Fig. 1 - each provided with tab teeth 9. With the tab teeth 9, the link chain 1 with a toothing, z. B. a gear, comb. The division between tabs 2 and counter-tabs 3 is designed so that a total of stretched chain uniform pitch between the tab teeth 9 results. The counter-plates 3 are provided with tab teeth 9, so that all tabs and counter-tabs are each provided with tab teeth 9. However, it is also possible to provide either only tabs 2 or counter-tabs 2 'with two tab teeth 9 or to provide tabs and counter tabs with only one tab tooth 9. The tab packages are closed on both sides by guide tabs 10.

FIG. 3 shows a guide strip 10 according to the invention with two rocker pieces 5, which are each arranged in an opening 11. The openings 11 each have a first undercut 17 and a second undercut 18, as will be described below with reference to FIG. 4.

4 shows the weight 5 and the contour of the associated receiving opening 11 of a guide plate 10. The weight 5 comprises a guide profile 12, with which this is supported on the tabs 2 and the guide plate 10. Furthermore, the weighing piece 5 comprises a weighing profile 13, with which the weighing piece 5 can roll on or slide off on a respective associated weighing piece 5 'of another set of lugs 8'. The guide profile 12 and the cradle 13 are connected via a first connection profile 14 and a second connection profile 15. The cradle 13 always merges at its two end sides into the first connection profile 14 or into the second connection profile 15, the two connection profiles 14, 15 The first connection profile has a radius of curvature (or a curvature, which can be designated by radii of tangential circles, radius of curvature is also synonymous with radius, shown with radii of tangential circles), which extends over the circumferential length of the first connection profile 14 is continuously reduced from a large radius of curvature R14_1 up to a minimum radius of curvature of R14_2 and then becomes larger again up to a large radius of curvature R14_3 and with this radius of curvature steadily merges into a radius of curvature R12_1 of the guide profile 12. Also the Führu ngsprofil 12 has over its circumference changing diameter, wherein a minimum radius of curvature R12_2 is significantly greater than the minimum radius of curvature R14_2 of the first connection profile 14. The guide profile 12 has a recess 16 for fixing the rocker 5 on.

Corresponding to the first connection profile 14, the second connection profile 15 has a small minimum radius of curvature R15_2 and has a large radius of curvature R15_1 in the region of the transition to the weighing profile 13 and also a large radius of curvature R15_3 in the region of the transition to the guide profile 12. Again, the overview gears from the second connection profile 15 respectively to the guide profile 12 and the cradle 13 steadily.

In the region of the first connection profile 14, a first undercut 17 is arranged, correspondingly a second undercut 18 is arranged in the region of the second connection profile 15. The radius of curvature R14_2 is constant and extends from a starting point 19 to an end point 20. Accordingly, the radius of curvature R15_2 is constant and extends from a starting point 21 to an end point 22.

In the region of the constant radius of curvature R14_2, the gap width y of the first undercut 17 is constant. At the two ends of the first undercut 17 each parabolic Cl- transition 23 are arranged until the disappearance of the gap (gap width equal to zero).

Corresponding to the first undercut 17, the second undercut 18 has a constant gap width x in the region of the constant radius of curvature R15_2 and likewise merges at both ends in parabolic transitions 23 to a gap width of zero. In Fig. 4 is a rolling ridge 24, which may arise in the manufacture of the rocker 5, indicated. The burr 24 is arranged so that it falls within the range of one of the undercuts 17, 18, in the present embodiment, the mill ridge 24 is in the region of the second undercut 18. By the undercuts 17, 18 are stress peaks in areas of large curvatures, with small radii of curvature, can arise, reduced.

Fig. 5 shows another embodiment of a guide tab according to the invention. Fig. 6 shows in comparison to a guide plate according to the prior art. In each case, the receiving openings 11 can be seen with the jaws 5 arranged therein. The guide plates 10 each have wings 25 which provide a guide for the toothed plate chain on which the guide plates 10 are arranged. In the toothed tongue according to the invention, the corner widths do and you above and below the openings 11 are approximately the same size. As can be seen in Fig. 6, this is not the case in the prior art. Outside the region of the openings 11, the guide tab according to the invention has waistings 26, which merge into a wing 27 towards a center line 27. The width a of the guide plate 10 in the region of the waist 26 is thus smaller than the width b in the region of the maximum thickness of the wing 25, this maximum thickness b is in the embodiment of FIG. 25 in the region of the center line 27th As can be seen from FIG. 6, in the case of a guide lug 10 according to the prior art, the minimum width b of the guide lug between the two jaw pieces 5 is approximately centered, thus coinciding approximately with the center line 27. In this respect, in the case of a guide lashing according to the state of the art, the region of lowest bending stiffness also falls approximately in the middle of the lug. 5, the areas of lowest bending stiffness fall approximately in the vicinity of the rocker 5. In Fig. 5 and 6, the neutral fibers of the two guide plates are each shown as a dashed line d. In the inventive guide plate according to FIG. 5, the maximum distance c of the neutral fiber d to an imaginary force application line through the weighing pieces 5 is significantly less than the maximum distance c for a guide plate according to the prior art.- The smaller distance between the neutral fiber b and the line of action The tensile force F causes a lower bending of the guide plate relative to a guide plate according to the prior art as shown in Fig. 6.

In Fig. 7, the longitudinal strain in the guide plate 10 according to the invention is shown in FIG. 6, in Fig. 8, the bending of such a guide tab is shown. The thicker lines denote the undeformed guide tab 10, the thinner lines the deformed guide tab 10; in the longitudinal expansion as shown in Fig. 7, the rocker 5 are pulled apart in the direction of the double arrow 28, the guide plate 10 thus stretched as a whole, in the bend as this is shown in Fig. 8 is carried out essentially a bend to both sides (Rotation) about a pivot point 29, which lies for example in the region of the neutral fiber approximately in the center of the guide tab. In a guide flap according to the invention according to FIG. 6, in particular the bend as explained in FIG. 8 is reduced compared to a guide flap 10 according to the prior art, because the neutral fiber has a smaller distance c from the force action line F and also because the flexural rigidity in the region , in which the guide tab 10 has the largest distance c between neutral fiber and force line of action, is particularly large compared to the prior art embodiment. LIST OF REFERENCES

I link chain

2, tab

2 'counter-tab

4 hinge pins

5 weight piece assigned to the tab

5 'weighing piece assigned to the counter-flap

7, T Wälzprofil

8, 8 'plate pack (chain link)

9 teeth

10 guide straps

I 1 opening

12 guide profile

13 weighing profile

14 first connection profile second connection profile

indentation

First underdog

Second underdog

Starting point of constant radius of curvature R14_2

Endpoint constant radius of curvature R14_2

Starting point of constant radius of curvature R15_2

Endpoint constant radius of curvature R15_2

Parabolic transition

Walzgrat

wing

sidecut

center line

elongation

pivot point

Claims

claims

Latch chain (1), in particular toothed link chain, of a plurality of tabs (2, 3), each of the latches stack (8, 8 ') form, with a hinge (4, 5, 5', 11) each with adjacent tab stacks (8, 8 ') are connected, wherein in each case a rocker piece (5) of a joint (4, 5, 5', 11) with the tabs (2, 3) of a tab stack (8, 8 ') through a mounting opening (4) is connected and two rocking pieces (5, 5 ') of adjacent plate stacks form the hinge (4, 5, 5', 11), wherein the rocker pieces (5, 5 ') each roll with one rolling profile (7, T) and / or and wherein the lug stacks (8, 8 ') comprise at least one guide lug (10), characterized in that the lug comprises a guide profile (12) having a first connection profile (14) and a second connection profile (15) with a Wiegeprofil (13) is connected, wherein the guide plate (10) has at least one attachment opening (11) in the region of the first and / or the second connection profile (14, 15) has an undercut (17, 18).

^■ 2. sprocket chain according to claim 1, characterized in that a respective undercut (17, 18) of the two rocker members (5, 5 ') is arranged in the region of the first connecting profile (14) and the second connecting profile (15).

3. Lashing chain according to claim 1 or 2, characterized in that at least one of the undercuts (17, 18) in the region of a roll burr (24) of a rocker (5, 5 ') is arranged.

4. guide plate (10) for a link chain (1), in particular toothed link chain, with two mounting holes (11) for attachment to a respective bolt (4), in particular a rocker (5, 5 '), wherein the mounting holes (11) over their Has circumference large and small radii, characterized in that in at least one region with a small radius of the mounting holes (11) an undercut (17, 18) is arranged.

5. guide plate according to claim 4, characterized in that the undercut (17, 18) is at least partially parabolic.

6. guide plate according to claim 4 or 5, characterized in that the fastening opening (11) has two areas with small radii, in each of which an undercut (17, 18) is arranged.

7. guide tab (10) for a link chain (1), in particular toothed link chain, with mounting holes (11) for attachment to a bolt (4), in particular a rocker (5, 5 '), characterized in that the guide plate (10) between the fastening openings on one side has a recess and on the other side a bulge, wherein the recess and the bulge are arranged so that between the plane of symmetry and the mounting holes a waisting is formed.

8. transmission with a link chain according to one of the preceding claims.