The present invention relates to a spring-biassed nut arrangement of the kind defined in the preamble of the following Claim 1.

By "spring-biassed nut" is meant a nut which is fitted with a spring and which is intended for movement along and within a slotted hollow profiled rail.

The spring fitted to the nut functions to press the nut against the inner surface of the two mutually opposing rail flanges that define the slot in the rail, so that as a result of friction against the flanges the nut will remain in the position to which it is set along the rail. A screw can be inserted through the slot and screwed into the nut exposed in the slot.

In the simplest case, the spring-biassed nut is fitted by inserting the nut from one end of the rail. It is desirable, however, to be able to fit the nut general¬ ly radially into the rail through the slot at any chosen position therealong. The nut shall be held against rotation in the rail and in order to be on the safe side, it has been necessary in practice to avoid nut constructions which include movable parts by means of which the nut is fitted to the rail.

DE-C-2,635,439 and SE-B-427,211 describe spring-bi¬ assed nuts of the desired kind which lack mutually movable parts for insertion of the nut in the rail and which prevent the nut from rotating when fitted.

The rails concerned can be combined to form an appa¬ ratus support stand or frame structure, apparatus cabinet, cable holder or the like, and because the nuts can be displaced along the rails a great deal of freedom is provided with regard to positioning of the

screws by means of which the apparatus, the cabinet or the like is secured to the rails of said structure.

The type of spring-biassed nut arrangement disclosed in DE-C-2,635,439 and SE-B-427,211, however, is un¬ satisfactory in operation, particularly with regard to its fitting to the rail. For instance, the task of fitting the nut manually to the rail is difficult to achieve, since it is first necessary to heavily com- press the spring of the known nut and then to insert the nut, with the spring compressed, in through the slot in the rail while holding the nut in a position which deviates from the fitted position of the nut by 90". This nut arrangement requires primarily a rail having a depth which is greater than the length of the nut in its insertion direction, and the spring is relieved of its compressive load immediately it has passed through the slot in the rail, therewith allow¬ ing the spring to expand. Since it is necessary to turn the nut through an angle of 90° after having inserted the nut through the slot, the process of fitting the nut can become extremely difficult at times. For instance, there is the risk that the nut will be unintentionally turned through 90° in the "wrong" direction, so that the nut faces towards the bottom wall of the rail while the spring faces the slot. Naturally, there is also the risk of the nut spring supporting against the bottom-wall region of the slot in a decentred position. A further drawback with this known type of spring-biassed nut arrangement is that it is very difficult to remove the nut from the rail radially through the slot.

Because the spring-biassed nut requires a large amount of free space within the hollow rail, the rail is relatively large in relation to the nut and is given a depth which is at least equal to the internal width of the rail. This results in mechanical strength problems and leads to a relatively high consumption of material

in the manufacture of the rail, and also creates geometrical problems with regard to extruded profiled elements of generally rectangular cross-section, in which each element side defines two mutually opposing flanges and an intermediate slot in a hollow profiled rail for spring-biassed nuts of the aforedescribed kind.

Accordingly, one object of the present invention is to provide a spring-biassed nut which can be easily fitted manually into an associated slotted rail and which enables the relative depth of the rail to be limited.

Further objects of the invention are stated directly or indirectly herein, or will be realized by the person skilled in this art.

The object of the invention is achieved with a spring- biassed nut according to the following Claim 1.

The preamble to Claim 1 is intended to include the technique disclosed in DE-C-2,635,439 or SE-B-427,211.

Embodiments of the invention are defined in the fol¬ lowing dependent Claims.

The invention will now be described in more detail with reference to exemplifying embodiments thereof and also with reference to the accompanying drawings, in which Figure 1 illustrates schematically an inventive spring-biassed nut from above; Figure 2 is a side view of the nut shown in Figure 1, taken on the line II-II in said Figure;

Figure 3 is a schematic axial section view of the nut shown in Figure 1, taken on the line III-III in said Figure;

Figure 4 is a schematic cross-sectional view of a profiled element comprising four mutually identical hollow rails of the kind indicated in Figure 3;

Figure 5 illustrates schematically fitting of the inventive nut into a hollow rail; and

Figure 6 illustrates schematically a variant of the nut and its hollow rail in a view corres¬ ponding to the view of Figure 5.

Figures 1-3 illustrate a preferred embodiment of the inventive spring-biassed nut, which is intended for coaction with a hollow profiled rail which preferably has the cross-sectional shape indicated in Figure 3..

The nut 1 includes a rectangular, approximately square body 10 formed from a sheetmetal blank in whose centre there is punched a deep-drawn hole. The blank also includes two mutually opposing long-edge regions 3 which are bent-up through an angle of 90° to form a stiffening element 3. The body 10 thus includes a generally flat circumferential region which merges with a cylindrical part which includes the internal screw-thread 20 of the nut body, via an annular coni- cally tapering part.

A generally C-shaped spring element 5 has essentially the same length as the body 10. Provided centrally in the web 53 of the C-shaped element 5 is an opening which encircles the outer side 121 of the screw- threaded body part and which is fixed thereto, for instance press-fitted thereto.

As shown in Figure 3, the length of respective long- edge elements 3 corresponds essentially to the free distance between the mutually opposing legs of the rail, i.e. corresponds to the width of the slot in the rail 60. It will also be seen that the element 3 has a stepped height in its centre part, so as to be sub-

jected to essentially the same bending or flexural strain along the whole of its length. The two long edge-parts 4 of the body 10 have the form of wedge-shaped flanges 4 whose upper surfaces 41 are angled upwardly through about 10° from the main sur¬ face of said body.

The legs 64 of the rail 60 have an inner surface 66 which slopes correspondingly through an angle of about 10 ^β to the plane defined by the outer surfaces of the legs, so that the outer flange surfaces 41 and the inner leg surfaces 66 will be in flat engagement with one another. Thus, if the nut 1 is subjected to a force which strives to pull the nut out of the rail, the legs are able to flex outwardly to some extent in the absence of slip between the flanges and the legs in the main plane of the nut surface.

In Figures 1 and 2, the line 23 illustrates the tran- sition between the generally flat part of the nut body and the conical part thereof, the outer surface of said conical part being referenced 120 and the inner surface thereof being referenced 220. The circle 22 represents the transition or junction between the upper flat surface 11 of the nut body and the conical inner surface 220 thereof. The outer surface of the generally cylindrical deep-drawn part is referenced 121.

As will be seen from Figure 3, the spring 5 urges the spring-biassed nut 1 upwardly into contact with the legs 64 of the rail, so as to hold the nut 1 in a desired position along the rail 60. It will also be seen that legs 51, 52 of the spring 5 support against side-wall regions of the rail 60, thus providing a nut centering function which centres the nut in relation to the centre of the groove. Although it will be evident from Figure 3 that the nut is held centered because the outer corners of the flanges 64 engage in

corresponding angled recesses between the end-walls 32 of the long-edge stiffenings and the nut flanges 41, the centering function of the spring 5 has particular significance with regard to fitting the nut in the rail 60.

Figure 5 illustrates a stage in which one flange part A of the nut 1 has been inserted into the inner corner region 70 between the rail flange 64 and the side-wall 62 while compressing one leg 51 of the spring in a general direction which lies in the plane of Figure 5 and which is parallel with the main surface 11 of the nut body 10.

The end-part A of the nut body is in contact with the wall 62 in a region referenced LP. The width of the nut between the tips of the flanges 4 is slightly smaller than the distance between the point LP and the corner point SP on the legs 64. It will be seen that when the end-part A is inserted as far as possible into the inner corner region 70, the nut 1 is able to swing around the point LP, so that the movable flange 4 is able to pass the opposite point SP with a small clearance thereto, wherein this swinging movement, generally indicated by the arrow Z, is counteracted by compression of the spring leg 51. When the flange 4 has passed beyond the point SP, the reaction force FR exerted by the spring leg 51 will displace the whole of the nut 1 so that the flange 4, which was earlier free, is driven in beneath the flange 64 at the region B and grips said flange. As a result of the efect exerted by the flange surfaces 41 and the leg surfaces 66, there is obtained an automatic, centering wedge action, due to the force exerted axially by the spring 5.

It will be seen that the rail 60 has a free cross- section which tapers conically from its upper slotted

part in a direction towards the slot bottom region against which the spring 5 acts.

An important feature of the inventive arrangement is that the nut is constructed for insertion of one end region A inwardly of one leg 64 of the rail 60 and for subsequent rotation of the nut against the action of a laterally acting spring element, so that the chosen length of the nut will allow the opposing flange part of the nut to just pass the opposite leg of the rail, whereafter the force exerted by the compressed spring is employed to displace the nut until its earlier free leg grips beneath the adjacent leg.

Schematically illustrated in Figure 5 is a force vector F which can be assumed to be exerted by the operator with a finger of one hand, wherein the force F can be divided into a force component F2 which acts generally in the axial direction 70 of the nut, and a force component Fl which results in an oppositely acting reaction force FR, as described above.

The person skilled in this art will perceive that the nut can be easily removed from the rail 60, for in- stance by inserting a screwdriver into the screw- threaded hole of the nut, so as to press down the nut 1 and forcing one edge-region A into the corner region 70, as illustrated in Figure 5, and then twisting the nut up around the pivot point LP with the aid of the screwdriver.

As shown in Figure 4, the inventive spring-biassed nut enables the rail 60 to be tapered conically down towards its bottom part. Consequently, rails 60 can advantageously be combined to form an element 6 which includes four mutually identical rails 6Q, wherein the element 6 has a central, generally rectangular part 68 in which a penetrating cylindrical passageway 69 can be provided, for instance so as to enable several such

elements 6 to be joined together or to facilitate mounting of the element 6 on a supportive surface.

One feature of the invention is that in addition to its conventional function the spring arrangement has a laterally acting spring function which presses the nut against the inner surface of respective rail flanges.

Another feature of the invention is that the rail is configured so as to form preferably in its upper part a pivoting point for one flange of the nut when the nut body extends through the rail slot and the spring arrangement is located within the rail. Another fea¬ ture is that the length of the nut body is adapted so that as the nut swings around this pivot point, the other flange of said nut will just pass the adjacent leg of the rail while compressing the spring device on the opposite side thereof, so that said spring device will drive the nut towards a slot centered position as soon as the other flange has passed the rail leg.

Although it has been indicated above that the nut pivoting point lies on the tip of the nut flange 4, it will be seen from Figure 5 that the actual point about which the nut swings may be formed at least temporari¬ ly by the contact point between the long edge 3 and the rail legs 64, or the contact point between the side-walls 62 and the underside 42 of the flange. In this regard, it is important that the length of the nut is so chosen that the free end of the nut will just swing past the adjacent legs 64 and that a nut pivoting region is found, for example in the rail angle between leg and side-wall.

Although the hollow space defined by the profiled rail has been shown to have a generally trapezoidal cross- sectional shape by way of example, it will be under¬ stood that other cross-sectional shapes are possible, for instance a generally rectangular shape.

Furthermore, the spring-biassed nut has been shown to coact with a side-wall of the hollow rail, on the basis that the rail has an upper slotted wall, a bottom wall and two side-walls. It will be understood, however, that the bottom wall may alternatively have a raised portion or a sunken portion and that the nut spring can be arranged to coact with the side-walls of said portions in a manner to centre the nut in the slot. In this case, the nut spring is provided with spring means capable of coacting with both sides of the recessed portion or raised portion and the spring shall also support against upwardly turned surfaces in the hollow rail so as to tension the nut upwardly into stable frictional contact with downwardly facing rail surfaces. The internal width of the hollow rail be¬ tween the side surfaces thereof will preferably be greater than the height between the bottom wall and the legs of the rail. The hollow space contained by the rail and the spring nut will preferably have a cross-sectional shape which is symmetrical in relation to a centre plane between the rail legs and the nut flanges respectively.

The variant illustrated in Figure 6 corresponds to the variant illustrated in Figure 5 with the following exceptions. The bottom region of the profiled hollow rail includes a central, longitudinally extending elevation 160 which forms a guide strip. The nut has springs 51, 52 which are formed for coaction with the sides 162 of the elevation 160, so that at least one of the nut springs will support against one side 162 and be compressed thereby as the nut is swung in through the slot, and then move the nut to a central position in relation to the slot, at the same time as the springs 51, 52 press the nut against the flanges

64. In the case of the Figure 6 embodiment, the spring device has the form of a rectangular sheetmetal ele¬ ment and the nut body extends through a centre region of said element. Two mutually opposing edge-parts of

the element are bent through an angle of about 270°, for instance, to form the springs 51, 52, and are intended to receive and contact the elevation 160 therebetween.