EP0003707A1 - Device for assembling two adjacent channel arch members of a gallery lining - Google Patents

Abstract

This device comprises a U-shaped stirrup (3), in which is mounted an axle (5) passing through a rotary clamping cam with two identical plates (7a), (7b) which are independent or mutually fixed and which crush onto the wings of the sections an interposed pin made of round iron (25). The double cam can execute a rotation equal to the distance between the stirrup (3) and the stops (14) welded to the wings of the section (1), this distance being preset by means of an elastomer (26) which is compressed as a result of the rotation of the plates, the initial clamping being produced by a jack (21), the piston (23) of which bears on the section (1) and the body of which catches on the lugs (24a), (24b) of the plates of the double cam. <IMAGE>

Description

The subject of the present invention is a device for assembling two gutter profiles fitted into one another, usable in particular in a friction forestay or in a sliding gallery support hanger, by means of a lock comprising a stirrup which envelops the profiles, is engaged with the wings of the internal profile and supports two identical rotary cams, exerting pressure on the external profile to secure the two profiles by friction, with an initial tightening whose protrusion causes rotation of the cams.

In DAS 1114761 (Bergbaustahl) which describes such an arrangement, the two rotary cams are spaced from one another in the plane of symmetry common to the profiles and are engaged with the bottom of the external profile, so as to create by friction between the sides of the profiles, a fastening of the latter. A drawback of this known arrangement is that the tolerances due to rolling are a cause of significant dispersion of the values of the sliding resistance, due to the contact of the sides, despite the metering of the clamping force of the rotary cams which in principle is obtained by the use of a dynamometric key for the rotation of these cams. In addition, because the cams exert their action on the bottom of the external profile, their radius of curvature is necessarily small, which makes it random the possibility of entrainment in rotation of the cams under the effect of the sliding of the external profile. . Assuming that this rotation occurs it is not subject to any limitation, so that the resulting tightening can itself grow indefinitely so that the sliding resistance is practically indeterminate and may even exceed the compression resistance of the profiles, the internal profile whose wings are in abutment on plates closing the corresponding end section of the stirrup, being itself incapable of sliding.

The use, now conventional, of gutter profiles which are in contact by their wings, to the exclusion of any contact on the sides, has been progress from the point of view of the regularity of the resistance to sliding, any dispersion due at an interpenetration of random amplitude, by wedge effect, being suppressed. However, due to the fact that in known devices for assembling gutter profiles with tightening by the wings, bolted stirrups are used, it has turned out, on the one hand, that tightening by an admissible number of bolts only provides resistance to insufficient sliding and, on the other hand, that a significant length of thread became unnecessary, the games to be made up being small and little different.

The present invention aims to improve the known device with rotary cams for the assembly of gutter profiles by simplifying the means to be implemented and by ensuring a simple and rapid installation and a sftr operation, making it possible to automatically obtain, in addition to resistance to high sliding from the start of sliding, subsequent sliding under constant load.

This object is achieved by means of a device characterized in that the tightening contact taking place, as known per se, exclusively between the wings of the profiles, the two cams are mounted on a common axis and are spaced in the direction perpendicular to the plane of symmetry common to the two sections, so as to apply to the respective wings of the external section, and in that stop means are provided to limit the amplitude of rotation of the cams and thus allow, after setting in stop , a sliding under constant load of the internal profile relative to the stirrup, the end faces of which are uncovered for this purpose.

This sliding under constant load is obtained, after sliding under increasing load, from the initial clamping position which provides an already high sliding resistance since the two cams are clamped on the wings of the internal profile and therefore have a large radius of curvature, in fact greater than the height of the section of the profile. In addition, the presence of the stop means enables minors, when the constant sliding load is not reached, to observe the relative position of these means and of the stirrup and therefore to know approximately the load exerted on a forestay or on a support hanger by the overlying grounds. In the particular case of yachts, it is thus possible to optimize the density of props necessary to support a gallery.

The stirrup is advantageously constituted by a flat iron folded in the shape of a U with long branches at the bottom of which is welded a short section of the same profile as those to be joined, serving as a tightening and guiding plywood. The axis which supports the cams crosses the two branches of the U near the ends of these. The two clamping cams, which the axis crosses, form plates of the same profile, which are maintained at a distance equal to that of the wings of the profile by a tubular spacer, the assembly affecting the general shape of a coil inserted between the branches of the U and of which the constituent parts can be free or welded into a single, each of the plates of the double cam exerting a tightening to the right of each corresponding wing on the profiles to be joined. The initial tightening of the double cam can be obtained by a few hammer blows or, better, by a removable hydraulic device.

Another feature of the invention consists in that, to avoid permanent deformation of the profile of the wings at the point of contact with each of the plates of the double cam under pressure exerted by the point thereof, is interposed between the _e edge of each tray and the wing of the profile which serves as its raceway an intermediate piece in the round of extra-mild steel folded in the form of a pin for easy insertion between each periphery of the tray and the wing corresponding to the profile, the role of said part being to crush under the significant point pressure of each cam plate and, consequently, to distribute this compression force over a larger surface of the profile wings, which thus do not risk to be damaged, this crushing part having the advantages on the one hand, of simplifying the manufacture of the double cam whose periphery of the plates does not require machining and, on the other hand, allowing the adaptation of the system with all shapes of profile wings.

The stop means provided to limit the rotation stroke of the cam (equal to the movement of the lock) preferably comprises two stops welded laterally on the respective wings of the external profile serving as raceways for the two plates of the double cam , these two stops receiving in support, at the end of the rotation stroke, the U-shaped stirrup. The contact of the U-shaped stirrup with the stops has the effect of mechanically locking the lock relative to the external profile on the wings from which the double cam rolled, the other internal profile, which could then slide under a load which is a function of the tension induced in the lock by the preset rotation of the double cam. The stroke of the latter (therefore the displacement of the lock) is kept constant for a given adjustment by two springs, preferably made of elastomer, in the form of hollow cylinders each crossed by a fixing and adjusting bolt, and fixed laterally on the respective faces of the stirrup, to the right of the wings of the external profile on which the lateral stops have been welded, the initial distance between the U-shaped stirrup and these stops being adjusted by a more or less prior compression of the elastomers by the bolts adjustment, the role of the elastomers being, after removal, to automatically return the device to the constant high initial position for new use.

• la Fig. 1 représente, en élévation, l'ensemble du dispositif faisant l'objet de l'invention, appliqué à un étai, montrant : la serrure maintenue en position haute par les ressorts en élastomère qui s'appuient sur les butées soudées latéralement au profilé inférieur, le fer rond en forme d'épingle disposé entre les plateaux de la came double et les ailes de profilé servant de chemins de roulement à ces plateaux, l'aménagement du dispositif hydraulique amovible de serrage initial des plateaux de came et les ergots soudés sur ces plateaux, ergots sur lesquels il est destiné à venir s'accrocher;
• la Fig. 2 est une vue en plan de l'ensemble composant la Fig. 1;
• la Fig. 3 est une vue perspective de la pièce d'écrasement en fer rond replié en forme d'épingle, à intercaler lors de la pose entre les bords non usinés des plateaux de la came double et les ailes de profilé correspondantes;
• la Fig. 4 est une vue en élévation d'un des deux éléments du dispositif de réglage de la course de la came double, éléments situés de part et d'autre de la serrure, au droit des ailes du profilé inférieur sur lesquelles sont soudées les butées, elle montre l'élastomère précomprimé à la valeur choisie pour la course, par léger serrage de l'écrou du boulon qui le traverse;
• la Fig. 5 est une vue du même élément annexe, selon une coupe suivant la ligne A-A de la Fig. 4;
• la Fig. 6 est un diagramme représentatif de la caractéristique charge/coulissement d'un étai conforme aux Fig. 1 et 2;
• la Fig. 7 est une vue analogue à la coupe de la Fig. 5, représentant une variante;
• les Fig. 8 et 9 sont des vues, en élévation et en plan, correspondant aux Fig. 1 et 2, d'un mode d'exécution simplifié d'un dispositif conforme.à l'invention.

To better understand the object of the invention and to highlight its other characteristics and advantages, a nonlimiting embodiment will be described below, illustrated by the appended drawing, in which:

• Fig. 1 represents, in elevation, the whole of the dispo sitive which is the subject of the invention, applied to a forestay, showing: the lock held in the high position by the elastomer springs which rest on the stops welded laterally to the lower profile, the pin-shaped round iron disposed between the plates of the double cam and the profile wings serving as raceways for these plates, the arrangement of the removable hydraulic device for initial tightening of the cam plates and the pins welded to these plates, pins on which it is intended to come and hang on;
• Fig. 2 is a plan view of the assembly making up FIG. 1;
• Fig. 3 is a perspective view of the round iron crushing piece folded back in the form of a pin, to be inserted during installation between the non-machined edges of the plates of the double cam and the corresponding profile wings;
• Fig. 4 is an elevation view of one of the two elements of the device for adjusting the travel of the double cam, elements located on either side of the lock, in line with the wings of the lower profile on which the stops are welded, it shows the elastomer precompressed to the value chosen for the stroke, by lightly tightening the nut of the bolt passing through it;
• Fig. 5 is a view of the same additional element, in a section along the line AA in FIG. 4;
• Fig. 6 is a diagram representative of the load / sliding characteristic of a forestay in accordance with FIGS. 1 and 2;
• Fig. 7 is a view similar to the section in FIG. 5, representing a variant;
• Figs. 8 and 9 are views, in elevation and in plan, corresponding to FIGS. 1 and 2, of a simplified embodiment of a device according to the invention.

In Figs. 1 and 2, a gutter profile 2 is fitted into a profile of the same cross section 1, the contact between the profiles taking place only by the wings has at 9. The two profiles are secured by a lock comprising a stirrup 3 constituted a flat iron folded into a U with long branches, at the bottom of which is welded a section 4 of the same profile that 1 and 2, which serves as a guide plywood, and has an 8-shaped contact with the wing has internal profile 2. The stirrup 3, which embraces the profiles 1 and 2 and whose end faces 3a, 3b are uncovered , supports an axis 5, provided with pins 5a 5b, which passes through two holes 6 drilled in the branches of the U of the stirrup 3 near the ends thereof. The axis 5 also crosses, with a clearance allowing rotation, a double cam whose plates of the same profile 7a 7b, arranged between the branches of the U-shaped stirrup, are kept at a distance equal to that of the wings of the profile 1 by a tubular spacer 7d which can be free or welded to each of the plates 7a 7b.

The U-shaped stirrup 3 being initially maintained in the high position shown by an elastic mounting which will be described below, the cam plates 7a 7b can be brought into the initial clamping position by a few hammer blows but an initial clamping is obtained constant by hanging on two lugs 24a and 24b, welded in a zone of the plates 7a 7b located outside the stirrup and adjacent to the less eccentric part of the active edge of the double cam, two hooks 22a and 22b welded to the body of a hydraulic cylinder 21 whose piston 23 rests on the bottom of the profile 1 and which can be actuated by a lever pump 21a.

Between the edges of the plates 7a 7b of the double cam and the corresponding wings of the profile 1 is disposed a crushing piece 25 in the form of a pin, of circular section, made of extra mild steel, which is the subject of FIG. . 3. This part is intended to be crushed under the point pressure of each of the plates of the double cam on each of the wings and, consequently, to distribute this compression force over a larger surface, preventing damage to the wings of the profile 1. This pin is replaced with each new use of the device, which has the effect of putting it back in identical initial conditions and, thereby, ensuring the consistency of the operating results.

As shown in Figs. 4 and 5, two stops 14 are welded laterally on the respective wings of the profile 1. With respect to these two stops, the adjacent end section 3b of the stirrup 3 is initially maintained at a distance "d" equal to the stroke provided for the rotation of the double cam 7a 7b, by means of two elastomer springs 26 which are located on either side of the branches of the stirrup 3 and are each arranged, with the interposition of cups 30, between two welded angle brackets, one 27 at the adjacent face of the U-shaped stirrup 3 of the lock, the other 28 at the stop 14 welded to the corresponding wing of profile 1. Each of these elastomer springs, in the form of a hollow cylinder is, before the implementation of the device, slightly compressed by a bolt 29 which passes through the hollow cylinder and the two fasteners and is provided a nut 29a applied externally to the fastener 27. A slight tightening of the bolt 29 has the advantage of making the distance "d" constant (all games taken up) by limiting the relaxation of the elastomer after depositing at this constant value, thus bringing the whole to identical initial conditions, without inter human vention.

During the implementation of the device, the U-shaped stirrup 3 being in the high position at the distance "d" from the stops 14 (see Fig. 4 and 5) and the double cam having received its initial tightening: - resistance to sliding of the profile 2 depends on the surfaces 8 and 9 which work on sliding friction; - that of the profile 1 depends, on the one hand on the surface 9 which works on sliding friction and, on the other hand, on the surface 10 of contact with the double cam 7a 7b of the wings of the profile 1 by means of the crushing part 25, which surface 10 also works on sliding friction. But this friction surface 10 acts on the double cam which works on the rolling by its axis 5 around which the two plates can rotate.

The rolling resistance being significantly lower than that due to sliding friction, the section 1 will slide first, the two plates 7a 7b performing a rotation equal to the descent of the U-shaped stirrup 3 remained integral with the section 2 by the friction sliding on the surface 8. This descent of the lock will compress the elastomer springs 26 while, due to the rotation of the plates 7a 7b the double cam will exert an increased tightening, increasing the tension in the lock and consequently the resistance to sliding. This rotation of the plates and the subsequent increase in clamping will be limited by the support of the terminal section 3b of the stirrup 3 on the stops 14, the elastomers 26 being compressed the value "d". The tightening of the double cam will therefore remain constant (the lock being locked mechanically by the stops) and 1- profile 2 will then slide under constant load.

It should be noted that, during the implementation of the device, there is a possibility of action on the sliding resistance to be obtained: greater tightening of the bolt 29, carried out initially, decreases the distance "d" and, by next, the sliding resistance while a slight loosening of the same bolt produces the opposite effect (the loosening should not, of course, be complete in order to always leave the a-lastomer in slight compression in order to catch up games, source of dispersion).

The diagram in FIG. 6 gives the load / sliding characteristic of a forestay according to the invention. Point A (zero sliding) corresponds to the initial load produced by the tightening of the cams under the action of the jack 21. When the terrain load exceeds this initial load the cams rotate and consequently rapidly increase the sliding resistance. The evolution of the load is represented by the straight line segment AB with a steep slope, the point B corresponding to the stopping of the stirrup. From this point the internal profile 2 slides in the stirrup under the constant load N represented by the line B _D.

In the variant of FIG. 7 the lower end of the bolt 29 is welded to the corresponding cup 30 which is simply pressed on the adjacent stop forming a console 114 fixed on the external profile 1. As in the case of FIG. 5 the compression of the elastomer 26 is obtained by tightening the upper nut 29a.

In the simplified embodiment of FIGS. 8 and 9 the cam plates 7a 7b are applied to the wings of the external profile 1 by means of the extra mild steel pin 25, and the two stops 214 constitute lugs fixed or formed on the respective cam plates which in their limit position come to apply on the upper end face 3a of the U-shaped bracket. In addition, there is no cylinder for the initial tightening of the cams which is obtained by a few hammer blows.

Another difference from Figs. 1 and 2 that the relative position of sections 1 and 2 is reversed. Indeed, while in the previous example the external profile 1 which supports the lock, has a lower position, it is the internal profile 2 which is in the lower position in the example of FIGS. 8 and 9, the direction of rotation of the double cam being, of course, reversed.

• - résistance au coulissement (N sur la Fig. 6) quasi immédiate,
• - auto-régulation de cette résistance, la rotation de chaque plateau de came étant limitée à une valeur constante,
• - minimum de jeux à rattraper, aucune déformation des profilés, d'où un rendement surpassant celui des dispositifs habituels qui compriment toute la section droite des profilés,
• - facilité et rapidité de pose et de dépose,
• - contrôle visuel instantané de la charge effective du soutènement.

Whatever its execution details, the assembly device proposed by the invention is applicable to any sliding retaining construction of an underground gallery, composed of profiles in gutters, in contact with their wings and used in rectilinear elements (props) or curvilinear (hangers), to which it brings the following intrinsic advantages:

• - resistance to sliding (N in Fig. 6) almost immediate,
• - self-regulation of this resistance, the rotation of each cam plate being limited to a constant value,
• - minimum clearance to be made up, no deformation of the profiles, resulting in a performance surpassing that of the usual devices which compress the entire cross section of the profiles,
• - ease and speed of installation and removal,
• - instant visual control of the effective support load.

Claims (14)

1 - Device for assembling two gutter profiles fitted one inside the other, usable in particular in a friction forestay or in a sliding gallery support hanger, by means of a lock comprising a stirrup which envelops the profiles , is engaged with the wings of the internal profile and supports two identical rotary cams, exerting pressure on the external profile to secure the two profiles by friction, with an initial tightening, the protrusion of which causes rotation of the cams, characterized in that the tightening contact taking place, as known per se, exclusively between the wings (a) of the profiles (1,2), the two cams (7a, 7b) are mounted on a common axis (5) and are spaced in the perpendicular direction in the plane of symmetry common to the two sections, so as to apply to the respective wings (a) of the external section (1), and in that stop means (14, 114, 214) are provided to limit the amplitude of cam rotation e t thus allow, after being brought into abutment, sliding under constant load of the internal profile (2) with respect to the stirrup (3) whose end faces (3a, 3b) are thus discovered. 2 - Device according to claiml, characterized in that the stirrup (3) is constituted by a flat iron folded in the shape of a U with long branches at the bottom of which is welded a short section (4) of a profile of section identical to that of the profiles (1, 2) to be joined. 3 - Device according to one of claims 1 and 2, characterized in that the two cams are constituted by two plates (7a, 7b) having the same profile, which are kept spaced apart by a tubular spacer (7d) at a distance equal to that of the wings (a) of the profiles. 4 - Device according to claim 3, characterized in that the plates (7a, 7b) are welded to the tubular spacer (7d), the assembly in the form of a coil constituting a single piece. 5 - Device according to one of claims 1 to 4, characterized in that a crushing part (25) is interposed between the edges of the two cam plates (7a, 7b) and the corresponding wings (a) of the external profile (1). 6 - Device according to claim 5, characterized in that the crushing part (25), which preferably is made of extra mild steel and has a circular cross section, is in the form of a pin. 7 - Device according to one of claims 1 to 6, characterized in that the stop means comprise two stops (14,114) welded laterally on the wings (a) of the external profile which receive support, at the end of the travel of rotation of the cams (7a, 7b) the caliper (3). 8 - Device according to claim 7, characterized in that the two lateral stops are initially maintained at an adjustable distance (d) from the stirrup (3). 9 - Device according to claim 8, characterized in that the adjustable distance (d) is initially maintained between one of the end faces (3b) of the stirrup (3) and the respective stops (14,114) welded laterally on the profile external (1), by means of two elastic devices each comprising a tubular spring (26), preferably made of elastomer, traversed by a bolt provided for adjusting the compression of the spring. 10 - Device according to claim 9, characterized in that each of the adjustment bolts (29) is supported by the stirrup (3) and bears, by gravity, on the corresponding stop (114). 11 - Device according to claim 9, characterized in that each bolt (29) is clamped between two elements (27,28) respectively secured to the stirrup (3) and the corresponding stop (14). 12 - Device according to one of claims 1 to 6, characterized in that the stop means comprise two stops (2 ₁ 4) integral with the respective cams (7a, 7b) and cooperating with one (3a) of the end faces of the stirrup (3). 13 - Device according to any one of claims 1 to 11, characterized in that the initial tightening of the cams (7a, 7b) is obtained by means of a removable cylinder (21). 14 - Device according to claim 13, characterized in that two lugs (24a, 24b) are welded laterally on the respective cams (7a, 7b) so as to be able to be engaged with two hooks (22a, 22b) fixed on the body (21) of the jack, the piston (23) of which is adapted to bear on the bottom of the external profile (1).

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