WO1990003467A1

WO1990003467A1 - Rail clip device

Info

Publication number: WO1990003467A1
Application number: PCT/EP1989/001084
Authority: WO
Inventors: Adolf Ibach
Original assignee: Carl Sülberg Gmbh & Co.
Priority date: 1988-09-27
Filing date: 1989-09-19
Publication date: 1990-04-05
Also published as: DE8911151U1; EP0436580A1; EP0436580B1; DE58903188D1

Abstract

A rail clip device (27) has a fastening element (26) with a coupling part (30), which presses a rail clip (1) against a first part (20) and a second part (22) via bearing flanges (2, 3), in order to clamp the first part (20). Between stiffening ribs (45) on the outer surface (5) of the rail clip (1) is a convex right cylindrical bearing surface on which the coupling part (30), which has a complementary concave right cylindrical recess (31), slides. This permits limited relative transverse motion between the rail clip (1) and a screw of the fastening element (26).

Description

DESCRIPTION

Clamp plate device

The invention relates to a clamping plate device according to the preamble of claim 1.

In a known clamping plate device of this type (US-A-1 024 127), the clamping plate 8 serves to fix a flange 6 of a railroad track to a base plate 7, which rests on a wooden sleeper. The fastening element 14 is designed as a wood screw with a square head 16, under which a convex spherical coupling part 17 is formed. The coupling part 17 rests in an annular concave spherical support zone 12 of the clamping plate 8 and centers the clamping plate. At the inner edge of the support zone 12 there is an opening 13 with considerable play

(Page 1, line 102, 103) opposite the wood screw 14. The clamping plate 8 has no stiffening ribs on its upper side. The support skid 10 of the clamping plate 8 is convexly bent downward in its longitudinal direction (Fig. 5) and is therefore only in Puπktberühruπg on the base plate 7. Stop projections 11 on the clamping plate 8 are intended to restrict their rotation during operation.

In a known clamping plate device (DE-Al-26 26 808), the entire outer surface of the clamping plate 10 is designed as a relatively slightly curved support zone 11, on which the disk-shaped coupling part 12 slides. The opening 13 for the fastening screw 20 in the clamping plate 10 is correspondingly elongated. Depending on the clamping height of the first part 18 to be clamped, the distances of the support runners 15, 16 from the longitudinal axis of the fastening screw 20 change (see FIGS. 4 and 5). . This is disadvantageous because the clamping force on the first support step 15 and the support force on the second support skid 16 change accordingly for a given mounting prestressing force of the fastening screw 20. Too little clamping force or too little support force can lead to undesired loosening of the clamping plate device during operation. Furthermore, the known clamping plate 10 is designed as a narrow rectangle in plan view (FIGS. 2 and 3). This is unfavorable, at least for those applications in which two clamping plates rotated by 90 to one another are seated on a common fastening screw and an intermediate plate representing the common second part is arranged between them. Then the support runners of each known clamping plate do not align with the other clamping plate, which leads to deformation stresses on the intermediate plate and correspondingly ample diminution.

From DE-A-1 400 882, a clamping plate 4 is known per se, on the rounded support surface 10 of which the nut 6 of a fastening screw 5 is directly connected Line contact rests. This leads to tension peaks along the contact line and permanent deformations on the contact surface and / or the nut. The deformation and / or flattening on the contact surface leads to the loosening of the nut by releasing the pretension. Cases are known in practice in which the nuts completely loosened and fell as a result of vibrations or the operation of a system equipped with clamping connections, so that the clamping became ineffective. In addition, undesirable bending stresses of the fastening screw 5 result with larger clamping heights (FIG. 3).

In the case of other clamping plate devices known per se (supplied in the Federal Republic of Germany by PHB Weserhütte Aktiengesellschaft, D-5000 Cologne), the clamping plate consists of the structural steel with the DIN short name St 60 or from the heat-treatable steel with the DIN short name C 45 and the Material number. 1.0503 according to the reference book "Stahlkey", Verlag StahlKey Wegst GmbH, D-7142 Marbach, 14th edition 1986, pages 25 to 28. The fastening element has a hexagon screw and as a coupling part an annular disk according to DIN 7349 or DIN 7989. Here, too, the washer is only in line contact with the support zone of the clamping plate on both sides of the opening. During assembly and in operation, this can lead to permanent and also to further shape changes of the disk and / or the support zone due to changing loads and thus to an impairment of the clamp connection. The deformation and / or flattening on the contact surface leads to the nut being loosened by releasing the pretension. Cases are known in practice in which the nuts completely loosened due to vibrations or the operation of a system equipped with clamping connections and fell, so that the clamping became ineffective.

From US-A-3 164 323 it is known per se to design the clamping plate 18, which is elongated in plan view, to be resilient. The fastening element has a rail anchor 16 which penetrates the clamping plate 18. A special nut 28 with concave recesses 29 on the underside (FIG. 9) serves as a coupling element between the rail anchor 16 and the clamping plate 18. When the nut 28 is tightened, the clamping plate 18 deflects resiliently downward for each recess 29 until one sufficient pretensioning force is reached and the nut 28 is seated with one of its recesses 29 on the convex bulge of the clamping plate 18. This will secure the nut against loosening.

From US-A-2 161 259 it is known per se to support the head 9 of a fastening screw 3 on a flat surface of the clamping plate 1. The outer surface of the clamping plate 1 has a U-shaped circumferential, relatively low and thin wall 8, the task of which is to prevent the head 9 from rotating when the fastening screw 3 is tightened or loosened.

From DE-C2- 33 38 257 a clamping device for fastening rails of a monorail to a ceiling construction is known per se. The clamping device consists of an oblique to the rail with an elongated hole 5 clamping body 1, a threaded bolt 3 penetrating the elongated hole 5 and a special, by a nut 4 of the threaded bolt 3 to the clamping body 1 by pressing washer 21. Biasing stresses of the threaded bolt 3 are to a large extent be avoided. For this purpose, the opposite ring-shaped surfaces 4b, 21a of the nut 4 and the clamping disc are opposite 21 complementary spherical.

A similar arrangement is known per se from DE-Al-34 12 213.

From US-A-3 206 123 it is known per se that the flanges 6 of a rail with resilient clips 11

Specify sheet metal on a threshold 1. The outer support skid 17 of each clip 11 is rolled in a cylindrical cylinder and rests in a special, complementary bearing 4 of the sleeve. Each clip 11 has on its underside two stiffening ribs 21 running transversely to the rail and securing tabs 19 for securing against rotation.

From US-A-1 279 725 it is known per se to fix the flanges of a rail A to a base plate 5 of a sleeper B. A special washer 19 is axially loaded by a banjo bolt 32 and is supported only on one side on the rail flange. The washer 19 is guided at the bottom with a socket 23 in a bore 9 of the base plate 5 and a bushing 11 of the threshold B and has radial stiffening ribs 28 at the top.

From US-A-2 175 453 it is known per se to connect the flange of an I-beam 20 to a plate 22 by means of a clamping plate 2. A flat washer 30 of a hexagon screw 26 rests on an annular elevation of the clamping plate 2 and is loaded by a commercially available hexagon nut 32.

The invention is based on the object in the case of the clamping plate device mentioned at the outset, even when the fastening element produces relatively high ones Pre-stressing changes in shape and in particular the shape changes of the clamping plate device should be avoided as far as possible and the distances between the support runners and the longitudinal axis of the fastening element should be kept at least approximately constant over the entire clamping height adjustment range of the clamping plate.

This object is solved by the features of claim 1. The coupling part is preferably designed as a disc which is arranged between the fastening element and the clamping plate and is rectangular or at least approximately square in plan view. The surface pressure between the fastening element and the clamping plate can also be kept at noncritical values with the locally limited support pin. Permanent deformations are excluded. There is the additional advantage that the support distances from the support runners to the longitudinal axis of the fastening element are approximately the same for all clamping heights, and therefore the clamping forces for the two parts to be connected are likewise the same for each of these parts and are essentially constant over the entire clamping height range . The local delimitation of the support zone and the relatively small opening in the clamping plate mean that the support skids can advantageously be formed continuously. The relatively small opening results in a correspondingly favorably enlarged support zone. The slight play between the fastening element and the opening is dimensioned in such a way that it permits the relative pivoting of the clamping plate during operation without contact with the fastening element. To achieve special strength and dimensional stability, the clamping plate and the coupling part are preferably forged in the die. Thanks to the stiffening ribs, the strength and dimensional stability can be impaired the connecting part of the clamping plate be made relatively thin and / or narrow and / or short and / or have a relatively low weight.

Such clamping plate devices are preferably used for hanging up loads. For example, steel structures as supporting and guiding structures for conveyor systems, stages, lifts, stationary or movable machine assemblies and the like are clamped under building or hall ceilings, to which neither drilling nor welding may be carried out. In accordance with the maximum payload (operating force) to be expected during operation, the appropriate size is selected from a number of available sizes of the clamping plate devices (for example for hexagon screws of sizes MIO, M12, M16, M20 and M24). The maximum clamping force that can be achieved with any size of the clamping plate devices is determined by the permissible maximum assembly pretensioning force of the fastening element. The invention allows particularly high loads to be clamped securely because correspondingly high clamping forces can also be transmitted within the clamping plate device without permanent changes in shape. So-called HV screws can now also be used for high-strength screw connections. Such screws are, for example, socket head screws (with a geometrical regular thread according to DIN 13 part 13 and the head of hexagon screws DIN 931) of class 10.9. Such a screw of class 10.9 and size M16 can be tightened, for example, at μ _ß = 0.12 as the average coefficient of friction in the thread with a maximum tightening torque of 290 Nm, which leads to a maximum

Assembly preload of 110 kN leads. After all, the operating force on such a pre-tensioned clamping plate device may not exceed 80 kN. Even with such high operating power, the preloaded clamping plate Device still has significant collateral. Such a high-strength clamp connection creates the possibility of safely hanging even the largest loads by clamping. In principle, each coupling part and, in general, every component of the fastening element can be made of the same material and, if necessary, with the same heat treatment as the aforementioned socket head screws of class 10.9. The top view of the clamping plate is preferably at least approximately square. It is then very dimensionally stable and can be handled easily. In the aforementioned cases, in which two clamping plates rotated 90 to one another are arranged on opposite sides of an intermediate plate, these clamping plates are essentially axially aligned with one another and therefore cause only minimal deformation stresses in the intermediate plate, which can accordingly be dimensioned more economically.

According to claim 2, in all cases one still remains under the permissible surface pressure between the coupling part and the support zone. This results in very secure clamping connections, because even with different clamping heights on the first support skid, the ratio of support force and clamping force that has been selected is largely retained. It is therefore possible to use HV screws with certainty and tables for these HV screws for uniform and highest clamping values for use can be drawn up using the globally approved DIN 18 800, Part 1 or DIN 15018.

According to claim 3, a washer can be saved under the nut and thus overall height. The same applies if the coupling part is designed as the head of the fastening element designed as a screw. The features of claim 4 lead to a particularly large support surface and thus a correspondingly low surface pressure with a high load capacity of the clamping plate device. The shape of the coupling part can be concave or convex. In any case, a relative pivoting of the clamping plate and the fastening element to a to the _skids, parallel pivot axis is made possible in predetermined limits. Such pivoting is particularly desirable when the clamping height of the clamping plate changes.

The embodiment according to claim 5 makes the clamping plate device statically determined even if relative swings between the clamping plate and the fastening element occur in any direction during operation. In certain limits, there are inclinations of the

Fastening element and / or the clamping plate in relation to the theoretical installation position permitted. Here too, the shape of the coupling part can be concave or convex.

According to claim 6, the centering section can be kept particularly tight, but a sufficient possibility of pivoting the clamping plate is still guaranteed. A relative pivoting on all sides can e.g. can be achieved by a double forging cone, each forging cone widening outwards from the centering section with the smallest clear width of the opening.

According to claim 7, there is a particularly intensive stiffening effect for the clamping plate.

According to claim 8, the endangered cross section is Clamping plate in the area of particularly high bending stress and notch effect is particularly secured by the support runners.

The features of claim 9 lead to an optimized configuration of the stiffening ribs.

According to claim 10, the workpieces are preferably forged and then normalized and tempered. They then have a high toughness, which is highly desirable for practical operation of the clamping device, essentially over the entire cross section.

With the features of claim 11, rotation of the clamping plate relative to the first part and the second part during assembly and operation can be prevented as far as possible.

Further features and advantages of the invention result from the following description of exemplary embodiments with reference to the drawing. It shows:

1 is a top view of a first embodiment of a clamping plate with a convex circular cylindrical support zone and stiffening ribs,

2 shows the end view along line II-II in FIG. 1,

3 shows the sectional view along line III-III in FIG. 1 with the other components of a clamping plate device _. and the first and second part,

4 shows the sectional view along line IV-IV in FIG. 3,

5 shows the sectional view along line VV in FIG. 1, 6 shows the top view of the pane according to line VI-VI in FIG. 3,

7 is a top view of another embodiment of the clamping plate with a concave circular cylindrical support zone and stiffening ribs,

8 shows the longitudinal section along line VIII-VIII in FIG. 7 with a screw with a special screw head,

9 shows the top view of an alternatively usable disc for the clamping plate according to FIGS. 7 and 8 with a standard screw,

10 shows the sectional view according to line ^“ XX in FIG. 9,

11 is a top view of another embodiment of the clamping plate with a concave spherical support zone and stiffening ribs,

12 shows the longitudinal section according to line XII-XII in FIG. 11 with additionally indicated screw and nut complementary to the support zone,

13 is a top view of a further embodiment of the clamping plate with a convex spherical support zone and stiffening ribs,

14 shows the longitudinal section along line XIV-XIV in FIG. 13,

15 is a plan view of a disc along the line XV-XV in Fig. 14,

16 is a top view of yet another embodiment. Ruπgsform of the clamping plate with concave spherical support zone and stiffening ribs,

17 shows the longitudinal section along line XVII-XVII in FIG. 16 with indicated fastening element and complementary washer,

18, 20, 22 and 24 each show a side view of a particular embodiment of a nut of the clamping plate device,

19 shows the longitudinal section along line XIX-XIX in FIG. 18,

21 shows the longitudinal section along line XXI-XXI in FIG. 20,

23 shows the longitudinal section according to line XXIII-XXIII in FIG. 22,

25 shows the longitudinal section along line XXV-XXV in FIG. 24,

26 shows the view along line XXVI-XXVI in FIG. 27 of a so-called carrier double clamping with an intermediate plate,

27 the sectional view according to line XXVII-XXVII in FIG. 26,

23 shows the sectional view along line XXVIII-XXVIII through a further embodiment of the clamping plate with stop projections on the underside,

29 shows the sectional view along line XXIX-XXIX in FIG. 28,

30 schematically shows two extreme assembly cases of the clamping 28 and 29 and

31 shows the top view of FIG. 30.

1 shows a clamping plate 1 with a first support skid 2 and a second support skid 3, which are rigidly connected to one another by a connecting part 4. An outer surface 5 of the connecting part 4 facing away from the lower support skids 2, 3 has a convex cylindrical support zone 6, a longitudinal axis of the circular cylinder running parallel to the support skids 2, 3. The support zone 6 is laterally delimited by a stiffening rib 44 and 45, which run approximately at right angles to the support runners 2, 3 and 10 along the longitudinal sides 10 and 11 of the clamping plate 1. The support zone 6, as also shown in FIG. 3, is formed only in a central region of the outer surface 5 and extends in this exemplary embodiment transversely to the support runners 2, 3, approximately over 39% of the outer surface 5.

The connecting part 4 has the support hole 6 interrupting the opening 7, which is almost circular and has a slightly elongated hole-like configuration. The

Opening 7 has a slightly greater extension in the direction of a longitudinal axis 8 of the clamping plate 1 than in the direction of a transverse axis 9 of the clamping plate 1. The clamping plate 1 is closed in the die and provided with the longitudinal sides 10, 11 with end faces 12 and 13.

In practice, the opening 7 is essentially formed by two partial openings, each with a semicircular cross-sectional area and longitudinal axes 14 and 15, which are spaced apart in the direction of the longitudinal axis 8 on both sides of the transverse axis 9. who are.

2 shows that the opening 7 in the forging process is produced by an upper forging cone 16 and a lower forging cone 17 which merge into one another with their smaller end faces in the interior of the connecting part 4. At this transition there is a centering section 18, which is formed as a punched ridge seam and forged as a stamped ridge seam and has a relatively small extent in the direction of a central vertical axis 19 of the clamping plate 1.

FIG. 2 also shows that the support runners 2, 3 are expediently linear in order to achieve the largest possible support.

3, the first support skid 2 is supported on a first part 20, e.g. the foot of a running rail. The first part 20 has a clamping height 21 which can vary depending on the design of the first part 20. Correspondingly, the clamping plate 1 is also produced in suitable sizes and installed around the transverse axis 9 with a relatively small permissible pivoting angle.

The first part 20 is carried by a second part 22, in this case a steel plate, on the surface of which the second support skid 3 is supported. The second part 22 can, of course, be designed in a very different way in a manner similar to the first part 20, as long as it can absorb a support force 23 and - via the first part 20 lying thereon - a clamping force 24 without damage.

Through the opening 7 of the clamping plate 1 and Bore 25 of the second part 22 extends through a fastening element 26 designed as a hexagon screw, all in all with 27 designated clamping plate devices. The longitudinal axis of the fastener 26 falls. ideally together with the vertical axis 19. As mentioned, deviations only occur when changes in the clamping height 21 result in a pivoting of the clamping plate 1 about the second supporting skid 3 and thus a relative pivoting to the fastening element 26. Such relative oscillations are only possible to a limited extent in the frame defined by the geometry of the opening 7.

3 clearly shows the convex, circular-cylindrical design of the support zone 6 with a radius 28. Along a part of the support zone 6, namely on a circular-cylindrical support surface 29, a coupling part 30 of the fastening element 26 is in sliding contact. For this purpose, the coupling part 30 is provided on its underside with a concave circular-cylindrical shape 31 which is complementary to the support zone 6 and is in contact with the top of the underside of a head 32 of the screw of the fastening element 26. A nut 33 of the fastening element 26 is supported on a lower surface of the second part 22 via a disk 34. When the nut 33 and / or the head 32 of the screw is tightened, the clamping plate 1 can be fixed in the desired manner together with the first part 20 on the second part 22. Depending on. This type of fastening element 26 can be done in different ways. Preferably, especially with higher loads to be clamped, so-called high-strength screw connections are used, in which a tightening force 35 is generated in the elastic deformation area when the screw is tightened. The operating force opposing the assembly preload force 35 is at least the assembly preload force 35 but in terms of the amount of the desired security, it is smaller than the assembly preload force 35.

Thanks to the circular-cylindrical design of the support zone -6, the above-mentioned relative pivoting between the clamping plate 1 and the screw of the fastening element 26 can be permitted in the clamping plate device 27 without the size of the supporting surface 29 thereby decreasing. Rather, there is only a relative sliding between the clamping plate 1 and the coupling part 30, so that the favorable large-area power transmission between these two parts is retained in full. Unfavorably high surface pressures between the two parts are therefore excluded even with the relative pivoting mentioned. Such relative pivots can also occur if, e.g. Due to the uneven underside of the second part 22, the longitudinal axis of the screw of the fastening element 26 should form an angle with the vertical axis 19. Such angles are also made inadmissible by the circular cylindrical coupling of the clamping plate 1 with the coupling part 30

Loads and without the risk of permanent deformations of the clamping plate device 27 are absorbed.

The clamping plate 1 can be designed with its stiffening ribs 44, 45 depending on the selection of the material, the manufacturing process and any subsequent heat treatment in such a way that it is extremely dimensionally stable and can withstand all operating stress, breakage or permanent deformation. In the cross-sectional design of the clamping plate 1 shown in FIG. 3, the endangered cross-section is located approximately in the area of the cut lines IV-IV, not least because of the notch effect on an end 36 of the opening 7 facing one of the first support skids 2 each stiffening rib 44, 45 in the region of the end 36 has its greatest vertical extension 46 at right angles to the outer surface 5. This results in a particularly large stiffening and increase in strength in the area of the endangered cross section of the connecting part 4. In accordance with the bending stresses of the clamping plate 1, each stiffening rib 44, 45 decreases from the greatest height extension 46 on both sides on the outer surface 5 to the supporting skids 2, 3 to zero. The cross-sectional configuration of the stiffening ribs 44, 45 can be seen sufficiently from FIGS. 2, 4 and 5.

5 that the opening 7 is not only double-conical in the direction of the longitudinal axis 8 (FIG. 1) but also transversely thereto "in the direction of the transverse axis 9 (FIG. 1). This double conicity in The sense of the forged cones 16, 17 actually consists in the perforation all around, so that the aforementioned relative pivoting of the clamping plate 1 and screw of the fastening element 26 is correspondingly universally possible Fastening element and the clamping plate.

6 shows that the coupling part 30 is approximately rectangular or square in plan view. The coupling part 30 is forged dimensionally stable in the die in the same way as the clamping plate 1 and therefore, as can also be seen in FIG. 3, has an upper forging cone 37 and a lower forging cone 38 in the area similar to the clamping plate 1 Opening 39 on.

In all drawing figures, the same parts with the same Chen reference numbers.

In the exemplary embodiment according to FIGS. 7 and 8, a concave circular cylindrical support pin 40 is provided in the outer surface 5 of the clamping plate 1 between the stiffening ribs 44, 45. In these figures, again with dashed lines, the fastening element 26 is entered. In this case, the coupling part 41 has a complementary convex circular cylindrical design and is molded directly onto the underside of the head 32, preferably by forging.

7 and 8, the embodiment according to FIGS. 7 and 8 also has sufficient freedom of movement in the event of a relative swing between the clamping plate 1 and the fastening element 26. In such a relative swing, the coupling part 41 slides in the support zone 40 with its radius 28.

Instead of the coupling part 41 integrated into the screw, in the embodiment according to FIGS. 7 and 8 a standard screw of the fastening element 26 can also be used in FIG. 3. In this case there is a coupling part 42 which is essentially rectangular or square in plan view according to FIG. 9 and

10 available. This also has on its underside a convex circular cylindrical shape 43 complementary to the support zone 40 and the opening 39.

The clamping plate 1 of the embodiment according to FIGS.

11 and 12 proceed from the clamping plate 1 according to FIGS. 7 and 8. A coupling part 47 engages in the concave circular cylindrical support zone 40. The coupling part 47 is designed as a nut with a screw of 01 fastening elements 26 is screwed. The coupling part 47 has on its underside a convex circular cylindrical shape 48 with the radius 28 that is complementary to the support zone 40. The fastener ^•

05 26 and the coupling part 47 are shown in dashed lines in FIGS. 11 and 12 for clarity. The plan view according to FIG. 11 shows the essentially rectangular or square design of the formation 48 and the essentially rectangular or square

10 configuration of the coupling part 47 overall. To facilitate assembly in the upper area, key surfaces can also be provided on the coupling part 47, as will be explained later in connection with FIGS. 23 and 25. The coupling part 47 can also be 5 laterally supported on the stiffening ribs 44, 45 and thus additionally secured against rotation relative to the clamping plate 1.

In the embodiment according to FIGS. 13 and 14, the clamping plate 1 of the clamping plate device 27 is provided on the outer surface 5 between the stiffening ribs 44, 45 with a convex spherical support zone 49 with a spherical radius 50. With the support zone 49 there is a coupling part 51 with a concave spherical shape 52 complementary to the support zone 59 in 5 sliding contact. 15 is designed as an annular disk and forged in the die. The coupling part 51 abuts the underside of the head 32 of the screw of the fastening element 26 at the top.

As already indicated above, this spherical coupling of the clamping plate 1 and coupling part 51 allows the universal relative pivoting of these components of the clamping plate device 27. The clamping plate device In this way, device 27 can be installed without constraint under all mounting conditions that occur in practice. In particular, the screw of the fastening element 26 is free of undesired bending moments and, with sufficient security, can be subjected to a correspondingly higher tensile load.

The clamping plate 1 according to FIGS. 16 and 17 is again provided with stiffening ribs 44, 45. The clamping plate 1 has a concave spherical support zone 53 at the upper end of the opening 7. The sphere radius 50 is entered in FIG. 17. A coupling part 54 is in sliding contact with the support zone 53 and is provided with a convex spherical shape 55 complementary to the support zone 53.

As indicated by dashed lines in FIG. 16, the coupling part 54 is designed as an annular disk in plan view with a central opening 39 (FIG. 17).

16 and 17 also allows universal relative pivoting between the clamping plate 1 and the coupling part 54. The coupling part 54 is punched in the die and then tempered to the desired characteristic values.

18 to 25 show several coupling parts, each of which is designed as a nut for a screw of the fastening element. In principle, with this design, the overall length of the fastening element can be saved, because an annular standard washer must be provided in the rule between a standard nut and the opposite component. The overall height of this standard washer is saved in a configuration according to FIGS. 18 to 25. 18 and 19 you can see a coupling part 56 with a concave krisiszylindischesεformung 57 and internal thread 58. In the top view, the coupling part 56 is preferred, rectangular or square.

20 and 21 show the coupling part 47 already explained in connection with FIG. 12.

22 and 23, a coupling part 59 is provided with a convex spherical shape 60 which is concentric with the internal thread 58. In order to prevent the coupling part 59 from rotating during assembly and disassembly of the associated fastening element, it is provided on its side facing away from the formation 60 with opposing key surfaces 61 and 62 for. provide a wrench (not shown).

24 and 25 show a coupling part 63 with a concave spherical shape 64 which is concentric with the internal thread 58. Key surfaces 61, 62 are also provided here as an assembly and disassembly aid.

In the top view, the coupling parts 59, 63 can be designed to be round, square or rectangular or in some other suitable way.

The application example according to FIGS. 26 and 27 represents a so-called carrier double clamping with an intermediate plate. In this case, I-carriers 67 and 68 cross at 90 °. A foot flange of the I-beam 67 forms the first part 20 for opposing clamping plates 1. Similarly, a head flange of the I-beam 63 forms the first part 20 for opposing further clamping plates 1. For all clamping plate devices The intermediate plate 69 in each case represents the second part 22.

On the screw of each fastening element 26 there are two clamping plates 1 which face each other with their underside and are rotated by 90. The upper clamping plate 1 engages on the I-beam 67 and the lower clamping plate 1 on the I-beam 68.

Because of the approximately square design of the clamping plates 1, the two clamping plates 1 of each fastening element 26 are essentially aligned with one another in the axial direction, as the illustration at the top right in FIG. 27 illustrates. As a result, only extremely small deformation stresses are introduced into the intermediate plate 69, so that the intermediate plate 69 can be dimensioned correspondingly small.

26 and 27, the intermediate plate 69 is clamped to the I-beam 67 with four clamping plates 1, while the I-beam 68 is clamped under the intermediate plate 69 with a further four clamping plates 1. As in all applications of this clamping plate device 27, the first parts 20 to be clamped are not drilled here either. Bores 25 for the screws of the fastening elements 26 are only made in the intermediate plate 69.

In the exemplary embodiment according to FIGS. 28 to 31, the clamping plate 1 is essentially designed in accordance with the exemplary embodiment according to FIGS. 1 to 5. The outer surface 5 is opposite an inner surface 70 of the clamping plate 1. A stop projection 71 and 72 extends downward from the inner surface to each side of the opening 7. Each stop projection 71, 72 has a stop surface 73 facing the first support runner 2. The stop face 73 interacts with an end face 74 of the first part 20 according to FIGS. 30 and 31.

30 and 31 show two first parts 20 with a very different clamping height compared to the associated second part 22 for clarification. In the case of the first part 20 shown in FIG. 30 with the larger clamping height, the maximum pivoting of the clamping plate 1 about the horizontal transverse axis 9 (FIG. 1) results in the clockwise direction. The stop surface 73 lies with only a small gap between the end face 74. This state is shown in full lines in FIGS. 30 and 31. When the fastening element 26 is tightened and when vibrations occur during operation, the clamping plate 1 can practically no longer rotate about the central vertical axis 19. The Zεntriεrabschnitt 18 has a favorable effect here, which prevents the clamping plate 1 from laterally deflecting relative to the fastening element 26 and could then still lead to an undesired rotation of the clamping plate 1.

Another borderline case in which the first part 20 has only a minimal clamping height is shown in FIGS. 30 and 31 with dash-dotted lines. In this case, a relatively large gap would result between the stop surface 73 and the end surface 74, which can lead to the maximum rotation of the dash-dotted clamping plate around the central vertical axis 19 shown in FIG. 31. However, this maximum rotation is still suitable for achieving or maintaining a secure clamping connection.

Claims

PATENT CLAIMS

1. Clamping plate device (27) with a metallic clamping plate (1) for releasably fastening a first part (20) to a second part (22) carrying the first part (20),

wherein the clamping plate (1) with a first support skid (2) supported on the first part (20) and a second support skid (3) supported on the second part (22) and with one of the support skids (2,3) rigidly to one another connecting connecting part (4) is different,

wobεi an outer surface (5) of the connecting part (4) facing away from the support runners (2, 3) has a curved support zone (6; 40; 49j53) supporting a fastening element (26) of the clamping plate device (27),

wherein a metallic coupling part (30; 41; 42; 47; 51, - ^■ 54; 56;: 59; 63) of the fastening element (26) with a to the support zone (6; 40; 49; 53) complementary curved shape (31; 43; 48; 52; 55; 57; 60; 64) with the support zone (6; 40; 49; 53) along a support surface ( 29) is in sliding contact,

wherein the connecting part has an opening (7) interrupting the support zone (6; 40; 49; 53) for receiving the fastening element (26),

the opening (7) being dimensioned such that it allows a limited relative swing of the clamping plate (1) and the fastening element (26),

and wherein the support zone (6; 40; 49; 53) is formed only in a central area of the outer surface (5) of the connecting part (4),

characterized in that the opening (7) is provided with only slight play relative to the fastening section (18) having the fastening element (26),

that the opening (7), starting from the center section (18), is widened (16, 17) in the direction of the longitudinal axis (19) of the fastening element (26),

that the clamping plate (1) and the coupling part (30; 41; 42; 47; 51; 54; 56; 59; 63) are designed to be dimensionally stable,

and that at least one stiffening rib (44, 45) extends outwards from the outer surface (5) of the connecting part (4).

2. Klemmplatteπvorrichtung according to claim 1, characterized 01 characterized in that - seen transversely to the longitudinal extension of the support runners (2, 3) - the support zone (6) extends only about 25 to 60% of the outer surface (5).

053. Clamping plate device according to claim 1 or 2, characterized in that the coupling part (47; 56; 59; 63) is designed as a nut which is screwed to the fastening element (26) designed as a screw.

104. Clamping plate device according to one of claims 1 to 3, characterized in that the support zone (6; 40) and the formation (31; 43; 48; 57) are complementary circular cylindrical, the longitudinal axis of the circular cylinder parallel to and in Distance from

15 runs the support runners (2,3).

5. Clamping plate device according to one of claims 1 to 4, characterized gekeπnzεichnεt that diε Abützenzoπε (49) convex spherical and the shape (52; 55; 60; 64) are complementary concave spherical.

206. Klemmplatteπvorrichtuπg according to one of claims 1 to 5, characterized gεkenπzεichnεt in that the opening (7) widens from its centering section (18) towards both sides (16, 17).

7. Clamping plate device according to the claims 1 25 to 6, characterized in that a stiffening rib (44, 45) along longitudinal sides (10, 11) of the clamping plate (1) runs at least approximately at right angles to the support runners (2, 3) .

8. clamping plate device according to claim 7, characterized characterized in that each stiffening rib (44, 45) in the region of one end (36) of the opening (7) facing the first support skid (2) has its greatest vertical extension (46) at right angles to the outer surface (5).

9. Klemmplatteπvorrichtung according to claim 7 or 8, characterized in that each stiffening rib (44,45) from the largest Höhenerstrεckung (46) decreases on both sides to the support runners (2,3) to zero.

10. Clamping plate device according to one of claims 1 to 9, characterized gekennzeichnεt that the Klεmmplattε (1) and / or the coupling part (30; 41; 42; 47; 51; 54; 56; 59; 63; 66) is gεschmiεdet in Gεsεnk and made of normalized and tempered steel with the DIN short name 45 Cr 2 and the material no. 1.7005 according to the reference book "Steel key", 14th edition 1986, pages 41 to 44.

11. Clamping plate device according to one of claims 1 to 10, characterized in that from one of the outer surface (5) opposed inner surface (70) of the clamp plate (1) to each side of the opening (7) has a stop projection (71, 72). extends, which interacts with the first part (20, 73) in order to prevent rotation of the clamping plate (1) relative to the parts (20, 22) at least approximately during assembly and operation.