KR830001375B1 - Workpiece Assembly Fasteners - Google Patents

Abstract

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Description

Workpiece Assembly Fasteners

1 is a partial cutaway view of a fastener according to the present invention showing an operating relationship for a pair of workpieces with the mounting tool in initial engagement with the fastener.

2 is an enlarged cross-sectional view of the shape of the groove of the fastener according to the present invention by enlarging a part of the axial direction of the pin of the fastener of FIG.

3, 4, and 5 are cross-sectional views similar to those of FIG. 1 showing a mounting sequence in which the indentation is completed from the initial indentation of the tubular member and the pin is broken.

6 is a partial cutaway view of a modified form of a fastener according to the invention showing a part of a workpiece and mounting tool of maximum mating thickness.

FIG. 7 is a partial cutaway view of the modified form of the fastener of FIG. 6 showing a portion of the workpiece and mounting tool of minimum mating thickness.

FIG. 8 is an enlarged cross-sectional view of the shape of the tension groove on the pin as seen in an enlarged portion of the circle 8 of the pin of the fastener of FIG.

TECHNICAL FIELD The present invention relates to fasteners, and in particular, to two-part workpiece assembly fasteners used to secure a wide range of materials.

In some cases, it is advantageous to use a two-part fastener in the form of a pin having a groove that also serves to fasten and break and a tubular member that is pressed into the groove. Thus, some of these grooves can act as a break so that a single fastener can be used for a wide range of material thicknesses. One problem with such fasteners is to provide a structure in which pins continue to break precisely where desired among the combination grooves.

This is accomplished by the present invention using a pin having the shape of a special combination groove. It is also believed that the selective use of the relative hardness between the pin and its associated tubular member will allow the fastener to perform a more appropriate function. In the present invention, the axial force generated by injecting the tubular member into the preselected grooves of the combination grooves is applied to the preselected grooves, the force being applied through a plurality of jaws by the mounting tool. When combined, the selected tension is applied to the selected groove. This causes the break in the selected groove while breaking. The groove structure includes a pair of radially outwardly extending sidewalls constituting each groove, each sidewall being formed at a different angle with respect to a radial plane extending laterally through the pin member.

Due to the special shape of the combination groove, the structure of a conventional jaw in a mounting tool is preferred in that the modified jaw portion has a tooth with a contour almost similar to that of the combination groove because in some cases its service life is shortened. However, in some cases it is desirable to use a tool having the structure of the current jaw. Therefore, in the present invention, a combination groove and a plurality of tension grooves having different shapes are provided at the end of the pin so that the structure of the current jaw can be used together.

Accordingly, the present invention provides an improved two-part workpiece assembly fastener having a fastening and breaking groove at the same time. These grooves extend along the axis of the pin only a distance from the length of that axis at least equal to the minimum thickness of the material in which the fastener is used. The fastener according to the invention makes it possible to fasten materials having various overall thicknesses as a single fastener. This feature can reduce the number of different fasteners that need to be purchased and stored as inventory, thus providing substantial cost savings to users of these fasteners, as well as the possibility of inadvertent use of fasteners with inappropriate coupling ranges. This reduces the reliability of the product. In the embodiment according to the present invention, the end of the pin is provided with a plurality of tension grooves of a different shape than the formation of the combination groove, the tension grooves are to be used in the structure of the current jaw.

Particular embodiments according to the present invention will be described in detail below with reference to the accompanying drawings.

Referring to the drawings, FIGS. 1 and 2 show a fastener 10 according to the invention. The fastener 10 consists of a pin member 12 having a head 14 and an extended shaft portion 16 provided at one end thereof.

The shaft portion 16 is provided with a plurality of substantially identical annular fastening and breaking grooves 18 along its entire length and a relatively short cylindrical portion 19 immediately adjacent to the junction of the head 14. Although the cylindrical portion 19 is shown here relatively short, it may extend to a length equal to the predetermined minimum thickness of the material for which the fastener 10 is to be used. Thus, the groove 18 will thus be formed along the length of the shaft 16 from a point larger than the predetermined minimum thickness of the material. Each groove 18 consists of sidewalls 20, 22 that project radially outwardly, which sidewalls 20, 22 are connected at radially inwardly concave ends 24. The radially outward ends of the sidewalls 20 are generally connected to each other with radially outward ends of the sidewalls 22 of other adjacent grooves 18 by convex ends 26.

As shown in FIG. 2, the side wall 20 is larger than the angle 32 between the side wall 22 and the vertical plane 30 with respect to the vertical plane 30 extending laterally with respect to the shaft portion 16. Actually formed at less angles 28. The present invention provides the most satisfactory results when the angle 28 is about 20 ° and the angle 32 is about 45 °.

Another important feature of the present invention is the convex end 26 and the concave end 24. Good results were seen in the fin member having an axis diameter of approximately 6.35 mm when the concave end 24 had a radius of about 0.127 mm, preferably when the radius was in the range between about 0.127 to 0.254 mm. In addition, good results were obtained even in such a fin member having a convex end 26 having a radius of about 0.254 mm or less. By selecting the radius for the concave end 24 and the convex end 25 as described above, work can be made consistent. As the diameter of the pin increases, the good range of the pin diameter for the concave end 24 will also increase while maintaining a ratio within the range of approximately 50: 1 to 50: 2.

As shown in FIGS. 1 and 3 to 5, the fasteners 10 are formed in the pair of workpieces 38 and 40 respectively engaged by the fasteners 10 and fitted to each other. It is inserted in (34, 35). The tubular member 42, generally in the form of a cylindrical collar, is located on the shaft 16 with its flanged end 44 engaged with the workpiece 40. As shown, the shaft portion 16 is longer in length than the sum of the total thickness of the workpieces 38 and 40 and the length of the tubular member 42, thereby causing the pulling of the pulling tool 50. An end 46 is provided having a combination groove 18 which is engaged with the jaw 48.

Tension tool 50 has a bending anvil 52 that extends outwardly from tip 54 of tension tool 50 as a conventional structure. The jaw portion 48 is adapted to be movable rearward with respect to the bending anvil 52 as shown in the figure. A conical hole 58 is provided at the inner center of the bending and bill 52 of the tension ball 50. The conical hole 58 has a relatively sharply inclined first interior 60 and a gently inclined second interior ( 62) is formed. The first interior 60 of the anvil 52 extends inwardly by a distance of about 2.286 mm with a slope of about 1.5 ° with respect to its axis, and the second interior 92 also has about 70 with respect to its axis. It has been shown that the anvil 52 formed as described above provides a satisfactory result in coupling the fastener according to the present invention.

Due to the action of the tensioner 50, the jaw portion 48 is bitten while contacting a predetermined number of combination grooves 18, thereby causing a tensile force to be applied on the pin member 12 and the tubular member 42. During the initial phase of the tensioning action, the anvil 52 exerts an opposite force on the tubular member 42, thereby causing the workpieces 38 and 40 to interlock.

Thereafter, the first inner portion 60 of the anvil 52 deforms the outer end 56 of the tubular member 42, as shown in FIG. 3 well, so that the predetermined groove 18 a of the combination groove 18. It pushes you in. Due to this initial deformation, the tubular member 42 and the pin member 12 are fixed to each other. Subsequently, if the jaw portion 48 continues to move, the anvil 52 moves along the tubular member 42, which causes the tubular member 42 to flow into the combination grooves 18b, 18c, 18d, 18e... By entering the working piece (33, 40) to approach each other and at the same time continue to compress the tubular member pressed into the groove (18a).

Due to the structure of the groove, a local force is applied to the side wall 20 in the axial direction as the tubular member 42 continuously presses and flows into the groove 18a, and a part of the tubular member 42 Is extruded backwards or flows into the outwardly located grooves 18f as shown in the figure. The axial force of the indentation or the flow force of the tubular member, which is generated by the continuous compression and flow of the tubular member in cooperation with the axial tension applied by the tensioning action of the jaw portion 48, breaks the groove 18a. It acts so that the end 46 of the pin 12 breaks in the groove 18a. As shown, the groove 18a is preferably the outermost groove that is first filled in the tubular member.

As noted above, the concave end 24 is selected to provide a predetermined controlled stress concentration area and the stress concentration area facilitates fracture so that the present invention provides a portion 46 of the shaft portion 46. Makes it possible to repeatedly control the desired groove to be separated. The convex end 26 also acts to facilitate metal flow into the grooves 18a, thereby helping to control the choice of grooves where fracture occurs.

The relative hardness of the tubular member 42 relative to the pin 12 is known to be an important factor in producing a commercially acceptable connection in the operation of the present invention. The tubular member 42 having a hardness that is too high relative to the hardness of a given pin 12 does not provide enough metal flow to generate an axial force from the metal flow in the groove 18a. In addition, the overly flexible tubular member 42 satisfactorily performs the breaking action of the pin, but the resulting joint does not have sufficient strength commercially satisfactory or practical. For the pin member (12) having a hardness in the range of steel _C of about 15R to 25R made of _C was found that from about 45R to about 65R _{B B} tubular member 42 having a hardness in the range of satisfactory.

In the present invention, the tensile load required to be applied by an installation tool for breaking the pin of the fastener when installed in cooperation with the tubular member 42 determines the pin without cooperating with the tubular member. It should be noted that it is lower than the required tensile load.

In summary, the present invention uses a pin having a plurality of identically formed grooves, the grooves serving as both fastening and breaking grooves at the same time, and the shape of the groove including the desired circular portion is a tubular member. Any one of the grooves in the selected position adjacent to the outer end of the provides a device to effect the failure. In addition, the proper relative hardness of the pins and tubular members allows to obtain the desired results. By reliably controlling the grooves at which fracture occurs, a single fastener can be applied to workpieces with a wide range of material thicknesses.

More notable facts have been described in relation to the two piece fasteners having a pin and a tubular member that can press-fit, but the principle is that the tubular member 47 has an outer end to press against the pin in a manner similar to that described above. It is also applicable to the manufacture of blind fosteners in the form of cylindrical sleeves.

In some cases, it may be desirable to use the present invention in conjunction with a mounting tool having a jaw with a conventional construction, and in the preferred embodiment shown in FIGS. It has a plurality of tension grooves 202 formed differently from the combination groove 18 in FIG. And also facilitates the use of the jaws of conventional structures. In the preferred embodiments of FIGS. 6 and 7, elements and parts that perform similar functions, such as the respective elements and parts of the preferred embodiments of FIGS. 1 through 5, are denoted by the same numerals plus 100. For example, the workpieces 38 and 40 in FIGS. 1-5 are labeled 133 and 140 in FIG. 6, respectively.

The fastener 110 has an end 200 having a plurality of tension grooves 202 and a tension groove 202 having fastening and breaking grooves 118 (similar to grooves 18 of FIGS. 1 to 8). It can be of such a conventional structure as shown generally at 8 degrees. It is to be noted that the tension groove 202 is formed narrower than the combination groove 118. That is, the top 203 is not higher than the convex end 126 and the bottom 205 is not deeper than the concave end 124. At the same time, the bite teeth of the jaw portion 207 are formed similarly to the tension grooves 202 so that they are well coupled therebetween. It is important that the tubular member 142 is not press-fitted into the tension grooves 202 because the tension grooves 202 do not provide the desired fastening and breaking characteristics of the combination grooves 118. Therefore, the convex end 126 of the combination groove 118 is formed to facilitate the metal flow of the tubular member 142 and the concave end 124 is formed to provide the desired stress concentration as described above. The bottom 205 of the tension groove 202 is formed to avoid effective stress concentration with the concave end 124 of the combination groove 118, and the top portion 203 is not formed to facilitate metal flow. Therefore, the tension groove 202 can be designed so that the tension function and effect of the jaw portion 207 is best exhibited. 6 shows the state of the maximum engagement thickness T _max for the workpieces 138, 140.

At the same time, it is also important that the jaw portion 27 does not bite into the pin member 112 of the combination groove 118 because the jaw portion 207 is formed similarly to the tension groove 202. FIG. 7 shows the state of the minimum bonding thickness T _min for the workpieces 238, 240.

As can be seen in FIG. 7, the length of the interior 204 in which the combination groove 118 is formed to adapt to the minimum coupling thickness T _min is at least the minimum coupling thickness T _min and the length of the tubular member 142. It is equal to the sum of (CL), that is, T _min + CL. When the minimum coupling thickness T _min is determined, the maximum coupling thickness T _max is the minimum coupling with the distance D measured from the point where the tubular member 142 and the anvil 152 are engaged to the front surface of the jaw portion 207. It is equal to the sum of the thicknesses T _min . Now, in order to adapt the maximum coupling thickness T _max , the interior 204 in which the combination groove 118 is formed has a minimum coupling thickness T _min , a length CL of the tubular member 142, and a jaw portion at the anvil 152. It will be approximately equal to the sum of the distances D to 207), ie, T _min + CL + D. The coupling range for the fastener 110 is from T _min to T _max , where the coupling range is approximately equal to the distance D, and this coupling range is defined by the pin member having a length of (T _min + CL + D) inside (204). 112). When applying the above formula, it is also necessary to consider the length of the transition portion 206 located between the combination groove 118 and the tension groove 202. The length of the transition portion 206 should of course be the minimum.

Now, if T _min is 1.59 mm, the length CL of the tubular member 142 is 9.52 mm, and the dimension of D of the mounting tool 150 is 14.3 mm, the length of the interior 204 is T _min + CL + D = 1.59. mm + 9.52mm + 14.3mm, the fastener 110 can be adapted to a workpiece having a bonding range of D = 14.3mm and having a bonding thickness in the range of 1.59mm to 15.9mm. Where 15.9mm is 1.59 + 14.3mm, which is the sum of T _min and D. In addition, a second fin member suitable for a workpiece with a larger bond thickness is easily determined by making T _min equal to 15.9 mm. That is, T _max is equal to 15.9mm + 14.3mm (T _min + D), that is, 30.2mm, and in this latter state, the length of the inner 204 is T _min + CL + D = 15.9mm + 9.52mm + 14.3 mm, that is, 39.7 mm. The bonding range is likewise D and will be 14.3 mm in this example. The description so far is merely illustrative, but an approximation should also be considered.

내지 1배 사이에서 증가되어야 하며, 이와같은 경우에 단부(200)의 길이는 D+JL+D_P×(1/2~1)의 칫수로 대략 확정될 것이다.In some cases, if the total length of the pin 112 can be minimized, the length of the end 200 can be a constant dimension so as not to change the engagement range, and the sum of the dimension D and the length JL of the jaw portion 207. , That is, roughly equal to D + JL. However, for a pin of minimum length, the length of the end 200 in the tensioning state with the workpiece is about the nominal diameter D _P of the pin member 112.

It should be increased between one and one times, in which case the length of the end 200 will be approximately determined by the dimensions D + JL + D _P × (1 / 2-1).

In this way, in the structure of the fastener 110 having the pin member 112, a single pin member can be applied to a wide coupling range and can also be used in the structure of a normal jaw member. Using the approximate minimum length required for the end 200 for a given engagement range, the result is the amount of material that is discarded after the fastener is fixed, ie the length of the pin member 112 from the breaking groove 118 to the end. Will be reduced.

In the latter description, the elements 114, 119, 134, 136, 144, 154, 156, 158, and 162 of FIGS. 6 through 8 correspond to the lower digits 14, 1 through 5. 19 ... etc.) and their shape or function are similar, so a detailed description of these elements is omitted.

Claims (1)

A pin member having a head and at the same time a plurality of grooves are formed in the shaft portion, a tubular member configured to be pressed into and engaged with a groove in a predetermined portion formed in the shaft portion, a bending anvil adapted to be engaged with the tubular member; By applying a tensile force in the axial direction between the pin member and the tubular member by a unidirectional actuating tool, such as a biting device configured to hold a portion of the shaft portion to engage the tubular member in the groove of a predetermined portion on the shaft portion to a minimum thickness. And a two-part fastener for engaging a plurality of workpieces having various thicknesses between the maximum thicknesses, wherein the grooves 18 of the pin members 12 are radially outwardly spaced apart from the first and second inner walls. And a first inner wall 20 positioned on the head 14 with respect to the second inner wall 22, and is positioned against the vertical plane 30 of the shaft portion 16. By forming a predetermined angle (28, 32) into the groove (18a) adjacent to the outer end 56 of the tubular member 42 when the tubular member 42 is pressed against the shaft portion (16) By causing a portion of the tubular member 42 to be pushed in to cause the shaft portion 16 to be broken at the position of the groove 18a, while at the opposite end of the head 14, the shaft portion is bitten by the jaw portion 48. Fastener for workpiece assembly, characterized in that to form a groove in a shape different from the groove 18 at a minimum distance from the portion of the groove 18 to prevent a cutting function such as the groove.

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