阅读说明：本技术 用于能量引导链的疲劳强度地设计的侧板 (Fatigue-strength designed side plate for an energy guiding chain ) 是由 A·赫尔迈 T-A·耶克尔 G·泰斯 S·施特拉克 于 2020-01-22 设计创作，主要内容包括：本发明涉及一种用于能量引导链的侧板(10；30A,30B),所述侧板包括由塑料制成的一体的板体,其具有两个交叠区域(11A,11B；31A……31D)分别用于与邻接的板的对应的交叠区域能摆动地连接,并且具有在所述交叠区域之间的中间区域(12；32A,32B)。交叠区域和中间区域分别在两个外部的部分面之间具有一定数量的横截面过渡部,在所述横截面过渡部中,至少一个横截面过渡部在所述板体的第一部分面(F11,F21,F31)和与该第一部分面成一角度、尤其90°的角度伸展的第二部分面(F12,F22,F32)之间倒圆或者具有折线(Q1……Q5)。(The invention relates to a side panel (10; 30A, 30B) for an energy guiding chain, comprising a one-piece panel body made of plastic, which has two overlapping regions (11A, 11B; 31A … … 31D) for the pivotable connection to corresponding overlapping regions of adjacent panels, and has an intermediate region (12; 32A, 32B) between the overlapping regions. The overlap region and the intermediate region each have a number of cross-sectional transitions between two outer partial surfaces, in which at least one cross-sectional transition is rounded or has a fold line (Q1 … … Q5) between a first partial surface (F11, F21, F31) of the plate body and a second partial surface (F12, F22, F32) running at an angle, in particular at an angle of 90 DEG, to the first partial surface.)

1. Side plate (10; 30A, 30B) for an energy guiding chain for guiding a pipeline by means of a chain link comprising two opposite side plates which are interconnected by at least one cross-piece, wherein the side plate (10; 30A, 30B) has an integral plate body made of plastic with two overlapping regions (11A, 11B; 31A … … 31D) for a pivotable connection with corresponding overlapping regions of adjoining plates, respectively, and has an intermediate region (12; 32A, 32B) between the overlapping regions; and

wherein the overlap region and the intermediate region each have a number of cross-sectional transitions between two outer partial surfaces, wherein at least one cross-sectional transition is rounded or has a fold line (Q1 … … Q5) between a first partial surface (F11, F21, F31) and a second partial surface (F12, F22, F32) of the plate body which runs at an angle, in particular at an angle of 90 °, to the first partial surface; wherein the at least one cross-sectional transition (Q1 … … Q5) is delimited by an enveloping transition curve (C) which has a course such that a starting Point (PA) of the transition curve (C) on the first partial surface (F11, F21, F31) lies within a distance A from a section line of the first partial surface and the second partial surface, for which starting point an end Point (PZ) of the transition curve (C) on the second partial surface (F12, F22, F32) lies within a distance Z from the section line, wherein 1.7. A. ltoreq. Z. ltoreq. 4.0. A, in particular 2.3. A. ltoreq. Z. ltoreq. 3.4. A, and the cross-sectional area of the cross-sectional transition (Q1 … … Q5) decreases continuously along the transition curve (C) from the starting Point (PA) to the end Point (PZ).

2. The side panel according to claim 1, characterized in that said transition curve (C) corresponds to a smooth or stepless and strictly monotonically decreasing curve.

3. The side panel according to any one of claims 1 to 2, characterized in that the first part face (F11, F21, F31) lies perpendicular to a main plane of the side panel and the second part face (F12, F22, F32) lies parallel to the main plane (H) of the panel body.

4. A side panel according to claim 3, characterized in that the first part-face with the starting Point (PA) is located on the middle area (12; 32A, 32B) and the second part-face with the end Point (PZ) is located on the overlap area (11A, 11B; 31A … … 31D).

5. The side panel according to claim 3, characterized in that the first part-face (F31) having the starting Point (PA) corresponds to a stop-acting stop-face of a stop-groove (15A, 15B) in the overlapping region, while the second part-face (F32) having the end-Point (PZ) corresponds to a bottom-wall which ends the stop-groove (15A, 15B) on one side.

6. The side panel according to claim 3, characterized in that the first part-face with the starting point is located on a swing bolt in the overlap region, while the second part-face with the end point is located on a side wall region, from which the swing bolt protrudes.

7. The side panel according to any one of claims 1 to 3, characterized in that the transition curve (C) defines a cross-sectional transition (Q5) from the outer face of the panel body into a material recess (37A, 37B).

8. The side panel according to any of the preceding claims, in particular claim 2, characterized in that the course of the transition curve (C) is selected such that the end point lies within a distance Z to the intersection line, wherein 2.2-A ≦ Z ≦ 2.6-A, and the course corresponds in particular to a 45 ° circular arc segment of a circle that is tangent to the second partial surface (F12, F22, F32) at the end Point (PZ).

9. The side panel according to any one of the preceding claims, characterised in that the angle between the first partial surface (F11, F21, F31) of the outer portion of the panel body and the second partial surface (F12, F22, F32) of the outer portion remains constantly 90 ° along the cross-sectional transition, and

-the transition curve (C) runs in the starting section at the starting Point (PA) with a tangent which forms an angle of approximately 45 ° +/-5 ° with the first partial surface (F11, F21, F31); and/or

The transition curve has a tangent in the end section at the end Point (PZ), which tangent is essentially parallel to the second partial surface or continuously transitions into the second partial surface.

10. The side panel according to any one of the preceding claims, characterized in that the at least one cross-sectional transition (Q1 … … Q5) is asymmetric with respect to the bisector of the angles of the first and second faces and/or is manufactured integrally with the panel body from a thermoplastic, in particular in an injection molding process.

11. The side panel according to any one of the preceding claims, characterized in that the second part-face (F12, F22, F32) having the end Point (PZ) of the transition curve (C) is provided on a given at least tension-transmitting region of the panel body.

12. The side panel according to any one of the preceding claims, characterised in that it is embodied as an inner panel (30A), as an outer panel (30B) or as a shoulder-shaped panel (10).

13. A link of an energy guiding chain having two opposite side plates (10; 30A, 30B) according to any of the preceding claims.

14. An energy-guiding chain comprising two plate cables, each consisting of a side plate (10; 30A, 30B) according to any one of claims 1 to 12, which are connected to one another so as to be pivotable in the longitudinal direction.

Technical Field

The present invention generally relates to a side plate for an energy guiding chain. The energy-guiding chain serves for dynamically and protectively guiding a flexible line, such as a hose, a cable or the like, between two relatively movable joint positions. The energy-guiding chain is made of chain links which typically each comprise two opposite side plates which are fixedly or releasably connected to each other by means of a crosspiece or two opposite crosspieces. The panel body of a side panel of this type has two overlap regions for pivotable or articulated connection to corresponding overlap regions of an adjoining panel, respectively, and has an intermediate region between the overlap regions.

Background

An energy guiding chain with the following side plates proved to be suitable: the side plates have an integral planar plate body made of plastic. Side panels made of plastic in particular achieve a significant weight reduction compared to metal panels.

Two types of plastic side panels are commonly used: complementary inner and outer plates, which are alternately connected to one another in the longitudinal direction to form a cable (as described, for example, in WO 95/04231 a 1), or else shoulder-shaped side plates in top view (as described, for example, in DE 3531066C 2 or US 4,813,224 a). Both plate types can be produced in each case inexpensively by injection molding.

In both types, the side plates have a number of cross-sectional transitions in each case at the overlap region and/or the central region, in each case between two partial regions of the outer face, since these are present or run at an angle, in particular perpendicularly, relative to one another as a function of function.

It is common practice to make some of these cross-sectional transitions rounded, in particular to avoid sharp-edged transitions or to blunt the edges. For example, the transition from the large side to the narrow side is rounded, for example to avoid interference edges, or the free end-side end of the pivot pin is rounded to facilitate assembly. The rounding of the cross-sectional transitions is typically realized as radial transitions with a small radius in the form of a quarter-circle arc, which is arranged symmetrically with respect to the partial surface.

Regardless of the design, the side plates are subjected to very high forces during operation of the energy guiding chain, in particular at large guide lengths or displacement distances and/or high speeds. Such forces occur in particular by the transmission of the pulling forces required for the movement, but for example in cantilevered applications (with an upper strand spaced apart from the lower strand in a self-supporting manner) or in the steering arc between the chain strands, for example also at the stop for limiting the pivot angle. In this case, the stresses or loads of the side plates are essentially repeated dynamically and often at a high pace, in most cases periodically, as a result of the back-and-forth movement of the moving sections. In such a case, there is an increased risk of fatigue damage due to load changes.

In practice, fatigue weakness is in most cases eliminated by fatigue-resistant designs with suitably increased wall or material thickness in critical areas of the side plates. However, this leads to higher material costs and a higher dead weight of the energy chain. This solution is not optimal, also because the forces to be transmitted during operation increase with gravity.

The aforementioned radial transitions or also, for example, the rounded connecting line sections as cross-sectional transitions can, although used to a lesser extent in this respect, theoretically lead to a certain reduction of stress peaks or notch stresses in the plate body at the load-receiving region and thus to a reduced risk of fatigue failure.

As long-term tests in the laboratory of the applicant have shown, the side plates can also fail after a high limit number of load changes at conventional rounded cross-sectional transitions due to residual notch effects or material stresses. This also occurs when the load is well below the static strength or load capacity and in part fails in the force flow before other sharp-edged transitions. Thus, the usual round radius transitions do not appear to be optimal.

Disclosure of Invention

A first task of the invention is therefore to extend such plastic side plates of an energy guiding chain without oversizing or requiring a more robust design from additional material, so that they still have an increased fatigue strength (english). Furthermore, the possibility of a greater weight saving by reducing the wall thickness or the plastic mass in the side panels should be opened.

According to the invention, a specially shaped cross-sectional transition is provided for this purpose on at least one region of the plate body which is intended for load receiving and which is determined to be critical and has a first and a second partial surface, or on the overlap region, on the intermediate region, or on the transition between the overlap region and the intermediate region. Therefore, the following steps are proposed: this selected cross-sectional transition is defined by a particularly running, enveloping transition curve, wherein the cross-sectional area of the cross-sectional transition decreases continuously, in particular monotonically, along the transition curve from the starting point to the end point (in the sense of a corresponding curve function). The course of the transition curve according to the invention is such that a selected starting point of the transition curve in or on the first partial surface lies within a distance A from an imaginary intersection line of the first partial surface and the second partial surface, for which starting point the curve end point in or on the second partial surface lies within a predefined, larger distance Z from this intersection line, i.e. within a distance Z of 1.7. A. ltoreq. Z.ltoreq.4.0. A, in particular within a distance Z of 2.3. A. ltoreq. Z.ltoreq.3.4. A.

It is briefly understood that the transitions in cross section correspond to a monotonically decreasing curve configuration, which is selected or configured according to the invention in such a way that the end-point distance Z of the curve to the intersection of two adjoining faces is significantly greater than its respective starting-point distance a, i.e. in particular in the range 1.7 ≦ Z/a ≦ 4.0.

Such a cross-sectional transition is significantly more advantageous than the conventionally provided quarter-circle rounding radius in terms of fatigue failure, in particular from local stress concentrations or stress peaks depending on the force flow. The cross-sectional transitions can be adapted to any desired installation space or edge conditions in a scalable manner. In a flat plane, a cross-sectional line (with respect to which the distance between the starting point and the end point is taken into account) corresponds to an intersecting straight line. Whereas in other pairs of faces (e.g. with cylindrical rocking peg faces or curved transition faces in the plane of the plate) the line of intersection is not a straight line. The transition curve of the envelope preferably remains constant at least in some regions or in most cases along the cross-sectional transition, i.e. to the envelope curve of the outer surface of the cross-sectional transition.

It has proven to be particularly advantageous if the transition curve corresponds in the functional analysis sense or mathematically to a smooth or stepless and strictly monotonically decreasing curve. The radius of curvature can be at least partially constant along the curve. It is also possible to use a curve which is locally or completely curvature-stable and which has a starting point spacing A and an end point spacing Z in the range of the proportionality Z/A4.0 of 1.7.

According to a separate aspect, irrespective of the pitch ratio Z/a, the invention also relates to a cross-sectional transition defined by a transition curve which decreases smoothly (steplessly) and strictly monotonically and which is characterized by its particular behavior with respect to the force flow along its course of the curve tangent or the curve slope (or first derivative or differential coefficient). According to the invention, the following transition curves are selected: the curve tangent of the transition curve at the starting point (when considered extremely) intersects the first surface at an angle of approximately 45 ° +/-10 °, in particular +/-5 °, and the transition curve rotates progressively or monotonously along the curve tangent of the curve course in a direction parallel to the second surface and is preferably located at the end point at approximately (+/-10 °, preferably +/-5 °) or is placed technically parallel to the second surface.

The transition curve can comprise a plurality of, for example, straight sections which continuously transition into one another, which sections are, for example, configured according to a method suitable for relieving notch stresses.

The risk of cracks in the case of dynamic loading on the cross-sectional transition according to the invention is significantly reduced by means of the proposed transition profile. As is known from the users of metallic materials, such cracks can occur in the case of relatively more flexible polymer plastics under changing loads and grow until the residue breaks. Accordingly, the use of the cross-sectional transition formed according to the invention enables the production of a fatigue-strength side panel without additional material expenditure. In particular, material savings can also be achieved by avoiding or specifically eliminating unnecessary oversizing in comparison to the existing configuration of the side panels.

Especially in the case of certain side panels for only one-sided overlapping, such as complementary inner and outer panels, or else shoulder-shaped panels, the critical regions are, as a rule of thumb, located at the following places: there, the forces flow from a region extending mainly in the main plane of the plate into a region extending mainly perpendicularly thereto. Preferably, the transition curve is thus disposed with its starting point on or in a first partial surface perpendicular to the main plane of the side plate and, correspondingly, with its end point in a second partial surface parallel to the main plane of the plate body. The invention can be used on substantially all transitions of the side plates that are critical with regard to fatigue damage caused by load changes. However, tests have shown two particularly vulnerable locations, by means of which considerable material savings can be achieved.

The first location critical with respect to fatigue failure is located at the transition between the overlap region and the typically thicker intermediate region, i.e. in a preferred embodiment, the first partial surface with the start point is located at the intermediate region and the second partial surface with the end point is located at the overlap region. In this case, the cross-sectional transition can be provided in particular at the transition between the smaller wall thickness of the overlap region and the larger wall thickness of the intermediate region. Accordingly, corresponding matching contours can be provided at the end-side ends of the side plates to ensure the required movement clearance.

In particular in the case of long chains and in the first third of the driver side of the energy guiding chain, large forces (i.e. alternating pulling and pushing forces) are transmitted through the side plates. Due to the jump in wall thickness and/or lateral offset in the overlap region, the two transitions to the middle region are subjected to considerable loads.

The second position critical with respect to fatigue failure is located in a stop pocket or stop groove which forms a counter stop for a counter stop projection of a directly adjoining or overlapping plate. The stop projection fits into the stop groove to limit the swing angle typically in both swing directions. As tests have shown, the floor transition into the stop recess has an increased risk of breakage, in particular in the case of long, cantilevered energy guiding chains. Accordingly, it is also particularly advantageous if the first partial surface with the starting point forms a stop-acting stop surface of the stop groove in the overlap region, wherein the second partial surface with the end point forms a base wall which terminates the stop groove on one side. In this case, the interaction with the corresponding transition curve on the associated stop projection is advantageous, so that stress concentrations or stress peaks are also reduced or material savings are achieved at the stop projection.

Furthermore, the proposed contour of the cross-sectional transition can also be used in other force-transmitting regions of the side plates, for example in the chain link connection of the side plates. Thus, another embodiment provides for: the first partial surface with the starting point is located on a pivot pin in the overlap region and the second partial surface with the end point is located on a side wall region from which the pivot pin protrudes, wherein the pivot pin is used for the link connection and is subjected to a high force perpendicular to the pivot axis during operation. Correspondingly, conjugated contours can also be provided on the corresponding bolt receptacles, however, here, depending on the type of construction of the side plates, transverse forces do not necessarily occur.

Furthermore, the provision of the proposed transition curve on the material recess lies within the framework of the invention, for example for weight reduction and/or for reducing stress concentrations or stress peaks in the plate body, similar to a relief notch. In this case, a first partial surface having a starting point can be located on the outer face of the plate body, and a second partial surface having an end point can be located in the material recess. The combination of the cross-sectional transition with a material recess of this type for the purpose of minimizing stress concentrations allows a weight reduction without critical stability losses and/or an optimization of the force flow in the side plate, in particular a reduction of the notch stress when the material recess acts in the manner of a load-relieving notch.

It is naturally possible for the cross-sectional transitions according to the invention to be used on only one of the aforementioned face transitions or else cumulatively on a plurality of said face transitions. In a further region of the plate body, an advantageous use of the cross-sectional transition is also under the framework of the invention.

The transition curve, which is particularly simple to implement but is advantageous in computer-aided product development, corresponds to a circular arc, in particular a 45 ° circular arc, i.e., an "eighth circle". In this case, a transition curve with a suitable constant radius is preferably arranged such that the end point lies within a distance Z from the intersection line, the distance having a value of 2.2. A. ltoreq. Z.ltoreq.2.6. A, and a construction circle (for example an osculating circle or a circle of curvature) for the circular segment is arranged tangentially to the second surface. The circle of curvature of the transition curve that is tangent to the second surface can be arranged in particular tangentially to the second surface with a radius that is suitable for the proportionality Z/a of 2.5. The desired proportional relationship Z/a determines the required radius of the arc segment. It is likewise possible to use other suitable curved shapes which, for example, run with an equal or parallel curve to the 45 ° arc segment configured above between two sides with an arc segment spacing d of 0.1 · a of 45 °, where Z/a is approximately 2.5.

The following transition curves are preferred: the transition curve corresponds to a smoothly and strictly monotonically decreasing function at least between the start and end points of the curve, since thereby all jumps or remaining edges between the start and end points can be avoided. For this purpose, for example, trigonometric functions, in particular tangent functions, are suitable.

The angle between the outer first partial surface and the outer second partial surface of the plate body can be constantly 90 ° along the cross-sectional transition, however, the cross-sectional transition can also be arranged on surfaces having other angles relative to one another, wherein an advantageous effect is achieved mainly at angles close to 90 ° (necessarily also in the range 45 ° ≦ α ≦ 135 °).

The problem of stress concentration is pronounced in the case where there are surfaces that are substantially perpendicular to each other in the area where the force is transmitted. In such a noodle, there can be provided: the transition curve runs in the starting section at the starting point with a tangent (determined by a derivative or a differential coefficient or as a curve slope) which intersects the first partial surface at an angle of approximately 45 ° +/-5 °. At this intersection line between the cross-sectional transitions, if necessary, slight edges may remain or can also be avoided by rounding. It is also basically advantageous to select the course of the transition curve such that it is essentially parallel, if appropriate +/-5 °, to the second partial surface at the end point, viewed in the tangent to its curve, in the end section, and ideally lies exactly in the second partial surface, which is achieved in a structurally simple manner, for example by the above-described 45 ° circular arc segment (where Z/a is 2.5).

Basically, the at least one cross-sectional transition is asymmetric with respect to the angle bisector of the first and second faces, since the associated loads are predominantly or in most cases uniaxial.

The provision of a cross-sectional transition is therefore particularly advantageous when the second partial surface having the end point of the transition curve is loaded in tension under a given load, at least in one of two alternative load situations, that is to say in the region of the plate body in which the tensile force is transmitted.

If the cross-sectional transition is produced integrally with the plate body from a thermoplastic, in particular by an injection molding process, the cross-sectional transition can be easily implemented by suitable shaping of the shaping tool and without particular expenditure also in very high numbers. The cross-street transition can be realized without various reworking, such as cutting.

The invention relates to an inner, outer or shoulder plate, in particular an integral plastic plate, which has at least one proposed cross-sectional transition. Correspondingly, the invention also relates to a chain link of an energy guiding chain with two such side plates and to an overall energy guiding chain constructed therefrom.

Drawings

Further features and advantages of the invention will emerge from the following detailed description of preferred embodiments, without limiting the scope of protection, according to the attached drawings. The features and advantages are shown purely by way of example:

FIGS. 1A-1E: a view of the shoulder-shaped side plate according to the first embodiment in a side view of the outer side facing away from the interior of the chain (fig. 1A), in a longitudinal section according to section line a-a (fig. 1B), in an enlarged partial section D (fig. 1D), in a perspective view (fig. 1C) and in an enlarged partial cross section according to section line B-B of fig. 1A (fig. 1E);

FIG. 2: greatly enlarged graphical representations of the transition curves of the cross-sectional transitions, such as those shown in fig. 1D and 1E; and

FIG. 3: the inner panel is shown from the outside in a perspective view (fig. 3A) and the outer panel is shown from the inside in a perspective view (fig. 3B).

Detailed Description

Fig. 1A to 1E show a shoulder-shaped side plate 10 which is produced as a one-piece plate body from plastic by means of an injection molding process. The side plate 10 has two planar, laterally offset overlap regions 11A, 11B and a middle region 12 over half the chain pitch length. The intermediate region 12 has a greater wall thickness than the overlapping regions 11A, 11B. The first overlap region 11A has a link receptacle 13 for pivotable engagement with a corresponding link pin 14 of a side plate 10 of the same construction to be connected. The link pins 14 project outwardly at the opposite second overlap region 11B. Stop recesses 15A, 15B, which are each equally dimensioned, are provided as recesses in the plate body on the circular-arc-shaped end regions of the overlap regions 11A, 11B. Each associated stop projection 16A, 16B of the respectively adjoining side plate 10 engages in each stop recess 15A, 15B in order to limit the relative pivot angle about the pivot axis of the cylindrical link bolt 14 to a desired range. This is done by the stop of the stop projections 16A, 16B in the complementary stop recesses 15A, 15B. The fastening tabs for the transverse webs, for example of the side panels 10, are not shown. Furthermore, the side plates 10 can also be components of a link produced in one piece, which has opposite side plates that are mirror images of the side plates 10 and otherwise have the same construction.

The central region 12 is delimited on both sides in the longitudinal direction of the side plate 10 by respective end faces F11, F12 extending approximately in a circular arc about respective pivot axes, which end faces are perpendicular to the plate main plane H (fig. 1D). The inner side of the outwardly shouldered overlap region 11A constitutes a flat face F21 and the outer side of the inwardly shouldered overlap region 11B constitutes a further flat face F21. The faces F21, F22 are parallel and are placed slightly laterally offset with respect to the main plane H of the plate with a play, that is to say the faces F21, F22 are perpendicular to the end faces F11, F12. The face F21 of the first overlap region 11A and the end face F11 of the intermediate region 12 are connected by a cross-sectional transition Q1. The face F22 of the second overlap region 11B and the further end face F12 of the intermediate region 12 are connected by a cross-sectional transition Q2. The cross-sectional profile of the cross-sectional transitions Q1, Q2 is shaped identically corresponding to the transition curve C shown more closely in fig. 2, for example, which has a shorter leg to the end faces F11, F12 and a longer leg to the lateral faces F21, F22.

Fig. 1E shows a further cross-sectional transition Q3, the profile of which is defined by the transition curve C of fig. 2. The cross-sectional transition Q3 bridges the stop face F31, which serves as an edge of the stop pocket 15B in the overlap region 11B and terminates the bottom wall of the stop pocket 15B on one side, in fig. 1E, toward the chain interior, which has a relatively small wall thickness or thickness compared to the remaining overlap region 11B. In both stop recesses 15A, 15B, a cross-sectional transition Q3 of identical design is provided on both sides, in each case on the stop surfaces used as counter stops for the stop projections 16A, 16B. Alternatively, instead of rounded edges, a cross-sectional transition (not shown) complementary to the cross-sectional transition Q3 can be provided on each stop projection 16A, 16B.

The cross-sectional transitions Q1, Q2, Q3 according to the transition curve C are optimized with regard to fatigue failure, in particular with regard to local stress concentrations or stress peaks in the corresponding regions of the plate body of the side plate 10, which depend on the force flow, since these regions must withstand continuous load changes and/or high forces. The cross-sectional transitions Q1, Q2 or Q3 allow a reduction in the material thickness of the plate body or a reduction to a greater extent of the bottom wall of the stop pockets 15A, 15B or, with the material thickness remaining constant, lead to an increased fatigue strength (strength against repeated load changes) of the adjoining regions of the side plates 10.

Furthermore, the overlap regions 11A, 11B and the central region 12 have cross-sectional transitions in further regions that are not critical with respect to stress peaks, which cross-sectional transitions are rounded as edges of a fold line or conventionally with a radius corresponding to a quarter circle. Here, the conventional radius rounding is shown, for example, for the transition of the lateral faces F21, F22 of the overlap regions 11A, 11B to the upper and lower narrow sides of the side plate 10 (fig. 1C) or for the end faces F11, F12 to the lateral faces of the outer part of the side plate (fig. 1D).

Fig. 2 shows a preferred transition curve C for the configuration of the cross-sectional transitions Q1, Q2 or Q3, wherein the transition curve C can be respectively scaled to the size. As can be seen in fig. 2, the starting point PA of the transition curve C on the partial surfaces F11, F21, F31 has a distance a to the intersection of the first partial surface with the second partial surfaces F12, F22, F32 (here, perpendicular on account of the perpendicular partial surfaces), and the end point PZ of the transition curve C on the second partial surfaces F12, F22, F32 has a distance Z to the intersection of the two partial surfaces (here, perpendicular to the partial surfaces F11, F21, F31). In fig. 2, the distance Z of the end point PZ is approximately 2.5 · a and the transition curve C is a 45 ° circular arc segment, the radius R of which is selected for the desired distance a such that the circle forming the circular arc segment touches the second partial surface F12, F22, F32 tangentially, or only at the point PZ. At the same time, therefore, the cross-sectional area of the cross-sectional transition Q1, Q2 or Q3 decreases continuously along the transition curve C from the starting point PA to the end point PZ, where it decreases according to a strictly monotonically decreasing curve. Preferably, the transition curve C is selected such that 2.3. A.ltoreq.Z.ltoreq.3.4. A is followed, particularly preferably 2.2. A.ltoreq.Z.ltoreq.2.6. A. Other functions, in particular without a radius of curvature that remains constant, can also be envisaged, for example tangent curves (not shown) such as tangens (x), where x is 0 to x (pz) and 1.25 ≦ x (pz) ≦ 1.4, or arranged such that Z/a ≈ 3.4 and the curve intersects the first partial surface F11, F21, F31 at PA approximately 45 °. The latter is especially contemplated for the transition of vertical faces (as in fig. 1A-1E). Other trigonometric functions can also be envisaged or, for example, elliptical segments can be envisaged, as long as the curve tangents rotate continuously, preferably strictly monotonically, along the curve course in a direction parallel to the second partial surfaces F12, F22, F32.

The transition curve, which is advantageous for optimizing the force flow, extends between two equidistant or parallel curves on both sides to a 45 ° arc segment with a distance d of 0.1 · a (Z/a of about 2.5). When extreme values are taken into account, the transition curve C has a tangent at the starting point PA which intersects the first partial surfaces F11, F21, F31 at an angle of approximately 45 ° +/-5 °, wherein the remaining edge at this location can be left as uncritical for structural simplicity.

Fig. 3A-3B illustrate a second embodiment having an inner panel 30A and an outer panel 30B. The inner panel 30A is integrally made of plastic with the second overlap areas 31A, 31B and the middle area 32A. In the injection molding step, the outer panel 30B is also integrally manufactured with the two overlap regions 31C, 31D and the intermediate region 32B. The inner and outer plates 30A, 30B are each symmetrical about their height mid-plane and are swingably interconnected in an alternating sequence as a cable according to a link receptacle 33 (here on the inner plate 30A) and a link pin 34 (here on the outer plate 30B). The inner plate 30A has four stop recesses 35A, 35B, 35C, 35D on the outside, which are distributed rotationally symmetrically about the pivot axis and are identically shaped. For a fitting fit into the stop recesses, the outer plate 30B has four projecting stop projections 36A, 36B, 36C, 36D on the inside for the purpose of limiting the pivot angle.

Analogously to the principle of fig. 1D, according to fig. 3A, the end face F11 of the middle region 32A of the inner plate 30A also transitions via a cross-sectional transition Q1 into a lateral face F21 of the overlap region 31A, 31B, which is perpendicular to the end face F11. The cross-sectional transition Q1 is implemented correspondingly scaled according to the transition curve C of fig. 2. Correspondingly, the end face F12 transitions from the middle region 32B (fig. 3B) of the outer plate 30B via the cross-sectional transition Q1 into the lateral face F21 of the overlap region 31C, 31D, in order to reduce the risk of fatigue fracture in this critical region.

In order to reduce the notch stress, the outer plate 30B has a further cross-sectional transition Q4 according to the invention at the stop projections 36A, 36B, 36C, 36D, in this case, in contrast to fig. 1A to 1E. The cross-sectional transition Q4 runs around on the base of the stop projections 36A, 36B, 36C, 36D and corresponds to the scaled transition curve C of fig. 2. Cross-sectional transitions corresponding to fig. 1E can also be used in the stop recesses 35A, 35B, 35C, 35D, if appropriate.

Fig. 3A to 3B furthermore show two material recesses 37A on the outside in the middle region 32A of the inner plate 30A and four further material recesses 37B in the outer plate 30B, which are respectively arranged rotationally symmetrically and are identically configured. The use of the cross-sectional transition Q5 according to the invention according to the transition curve C in fig. 2 for the transition into these material recesses 37A, 37B enables better material utilization in the plate bodies of the inner plate 30A and the outer plate 30B and thus at the same time a significant reduction in the component quality of each plate or the amount of plastic required, which reduces the material costs and enables an increase in the production cycle time of the injection molding machine.

Finally, for reasons of reduction, reference is made to DE 3531066C 2 (plates with a shoulder shape) or WO 95/04231 a1 (plates with inner/outer plates), in respect of other features of the energy guiding chain which are known per se and are not shown in part here. Subsequently, the terms "inner" and "outer" may be understood with reference to the receiving space for the pipeline in the chain link of the energy guiding chain.

List of reference numerals

FIGS. 1A-1E

10 side board (with shoulder shape)

11A, 11B overlap region

12 middle area

13 chain link receiving part

14-chain link bolt

15A, 15B stop recesses

16A, 16B stop tab

F11, F21, F31 first partial surface

F12, F22, F32 second partial surface

H plate principal plane

Transition of Q1, Q2, Q3 cross section

FIG. 2

Curve of C transition

PA Start point (transition curve)

PZ endpoint (transition curve)

R radius (45 degree arc segment)

FIGS. 3A-3B

30A inner plate

30B outer plate

31A, 31B overlap region (inner plate)

31C, 31D overlap region (outer plate)

32A, 32B intermediate region

33 chain link receiving part

34 chain link bolt

35A, 35B, 35C, 35D stop pockets

36A, 36B, 36C, 36D stop tab

37A, 37B material recess

F11, F21 first partial surface

F12, F22 second partial surface

Transition of Q1, Q2, Q4, Q5 cross section