HUE034868T2

HUE034868T2 - Rögzítõelem Belleville fejjel

Info

Publication number: HUE034868T2
Application number: HUE14840744A
Authority: HU
Inventors: Michael J Maloney; Brian Bentrim; William Mcdonough
Original assignee: Pem Man Inc
Priority date: 2013-08-28
Filing date: 2014-08-28
Publication date: 2018-03-28
Also published as: TWI620877B; JP6421187B2; CN105683594B; MX2016002475A; TW201525308A; SG11201601411UA; CA2922677C; EP3039306A4; EP3039306A1; JP2016535217A; MX371271B; CA2922677A1; CN105683594A; PL3039306T3; US9816545B2; MY180864A; EP3039306B1; WO2015031557A1; US20150063944A1

Description

^|1|| European g JJII Patent Office w Office europien des brevets

(12) EUROPEAN PATI (45) Date of publication and mention of the grant of the patent: 19.07.2017 Bulletin 2017/29 (21) Application number: 14840744.8 (22) Date of filing: 28.08.2014

(54) FASTENER WITH A BELLEVILLE HEAD

BEFESTIGUNGSELEMENT MIT TELLERFEI ELEMENT DE FIXATION DOTE D UNE TETI (84) Designated Contracting States:

AL AT BE BG CH CY CZ DE DK EE ES FI FR GE GR HR HU IE IS IT LI LT LU LV MC MK MT NL NC PL PT RO RS SE SI SK SM TR

(30) Priority: 28.08.2013 US 201361871019 P (43) Date of publication of application: 06.07.2016 Bulletin 2016/27 (73) Proprietor: PEM Management, Inc.

Wilmington DE 19803 (US) (72) Inventors: • MALONEY, Michael J.

Doylestown, Pennsylvania 18902 (US) • BENTRIM, Brian

Furlong, Pennsylvania 18925 (US) io o s o 7)

O ^ Note: Within nine months of the publication of the mentic ^ Bulletin, any person may give notice to the European Pa . Implementing Regulations. Notice of opposition shall not y paid. (Art. 99(1) European Patent Convention). (id EP 3 039 306 B1

SPECIFICATION 51) IntCI.: F16B 35104 <200601> F16B 39126 <200601> F16B 391284 <200e 01> F16B 19Ι06<200β 01> 86) International application number: PCT/US2014/053048 87) International publication number: WO 2015/031557 (05.03.2015 Gazette 2015/09)

KOPF

LLEVILLE • MCDONOUGH, William Collegeville, Pennsylvania 19426 (US) 74) Representative: Dunleavy, Kevin James et al Mendelsohn Dunleavy, P.C. p/o De Vries & Metman Overschiestraat 180 1062 XK Amsterdam (NL) 56) References cited: WO-A1-2011/049643 WO-A1 -2013/019545 WO-A1-2014/014699 DE-U-7 226 710 JP-A- 2000 304 019 US-A- 1 395 960 US-A- 1 875 930 US-A- 2 226 491 US-A- 2 371 452 US-A- 3 469 490 US-A- 4 310 272 US-A- 4 350 465 US-A-4 875 818 US-A1-2003 175 093 US-A1- 2007 071 570 the grant of the European patent in the European Patent Dffice of opposition to that patent, in accordance with the emed to have been filed until the opposition fee has been

Description

Related Application [0001] This patent application is a non-provisional of provisional patent application serial number 61/871,019 entitled "Fastener with a Belleville Head" filed on August 28, 2013, priority from which is hereby claimed.

Field and Overview of the Invention [0002] The present invention relates to very small headed push-in fasteners of the type produced by Penn Engineering & Manufacturing Corp. known as TackPins and TackScrews. More specifically, it relates to a Tack Pin or a Tack Screw with a Belleville head that provides the functionality of a Bellville washer without requiring a separate part.

Background of the Invention [0003] The attachment of two members can be made in a number of differentways. Some attachment methods such as adhesives, glues, or welding can form a strong bond between the members without generating any squeezing or clamping force between the members. Fasteners such as a typical rivet or tack pins / screws, also do not create a clamping force on the members. When a clamping force is desired, screws are a common method of achieving this.

[0004] Many consumer product assemblies are being designed with a thin-walled enclosure that is softer than the fasteners being used to assemble them. This coincidence works in favor of a self-clinching fastener which requires a hardness differential, and clinches at the surface of the panel. This is opposite for a screw however, and limits the available clamp load of the screw. In this case the limiting force for clamp load is equal to the yield strength of the threads engaged by the screw in the enclosure. This invention applies to this type of assembly.

[0005] Because complete stripping of the thread would render an assembly useless, the yield force is used for design purposes to calculate the maximum allowable induced load. The yield force of the female threads is calculated as the yield stress of the thread in the bottom panel as shown in Figure 1, multiplied by the area of the thread that is in shear. The area of the thread in shear is the cylindrical surface per thread that would be left if a screw were to cut the threads out if pulled or pushed vertically. Because the effect of the thread helix on this area is very small, the area of thread in shear can be simplified to be the number of threads in shear multiplied by the cylindrical area of one thread.

[0006] In Figure 1, the clamp load of the prior art is generated when the screw is tightened. Tightening the screw causes a tension force in the screw. That is to say the part of the screw between the underside of the head and the top of the engaging threaded member. Part of the clamp load generated stretches the screw like a spring. Hooke’s Law describes the change in length of the screw. The shorter a screw is made, the less capable it is of stretching. Hooke’s Law applies equally for the top panel, which is compressed by the clamp load. The force experienced by the top sheet is equal to the clamp load. In the case shown in Figure 1, the panel is thin which also tends to limit the potential compression. It is the application of a hard screw into a thin soft enclosure that enables a clinch attachment to compete very well against a screw thread.

[0007] Referring now to Figure 2 another example of a prior art fastener is depicted. Since a tack pin or a tack screw is pressed in, and is not in tension during installation, it can provide little or no clamp load. The compression of the top sheet can provide a component of clamp, however the situation is slightly different from the case of a screw. When the installation load is applied to the tack, and consequently the top sheet, both will change in length (shorten or compress) per Hooke’s law. As long as the parts were not crushed beyond their yield points, both will relax (attempt to return to their original lengths) when the installation load is removed. We can remove force and express relative deflection in terms of known dimensions and material properties. Assuming homogenous properties of the bottom sheet, three different scenarios exist for pin compression compared to panel compression. Given our small part case, we can make the following statements: If the tack and panel have the same deflection, then they will spring back nearly equally after the punch is removed, and no clamp load would be generated. If the tack has a greater stiffness, and hence smallerdeflection than the panel. Panel compression can happen, and consequently a small clamp load, given that the tack will spring back less than the panel tries to. If the panel has a greater stiffness, and hence smallerdeflection than the tack, then no clamp will be generated. The tack might actually spring back higher than the attaching panel, leaving a small gap under the head. An example of where a tack pin/screw would create a small clamp load is where the top sheet might be a gasket material like rubber. As with the screw, the yielding of the undercut in the bottom sheet is the overriding maximum clam p load allowable for a tack pin / screw if the top sheet has the capability of generating such a force.

[0008] Clinching Tack pins / screws are an excellent alternative to very small screws, and provide numerous advantages over a screw, including: 1) No tapping of hole is required 2) Thread stripping as a failure is eliminated 3) Tack pins / screws are pressed in, as such installation is greatly simplified 4) Tack pins / screws do not require a thread locking patch and are inherently non-loosening 5) Tack pins/screws have very thin heads and permit thinner design forms than screws which require thicker heads due to the drivers required in the head.

[0009] However, some shortcomings of Tack Pins / Screws are: 1) Little or no clamp load (while it is minimal, a short screw does provide a bit of clamp load) 2) If under installed, a gap will be left under the head permitting axial float 3) Perfect installation, where the bottom of the head of the tack pin contacts the top sheet during installation, without over pressing, requires expensive equipment.

Simply adding a separate washer to the screw/pin of the assembly creates all of the problems associated with a greater number of parts and Belleville washers cannot be made small enough to be used with a micro screw or very small tack pins having a diameter in the range of 1.0 mm. There is therefore a need in the art for a new type of unitary fastener which when applied can provide a residual clamp load to the elements it has joined.

[0010] JP 2000 304019 A teaches a unitary nail having a conical Belleville disc spring between the head and shaft of the nail. In the embodiment of FIG. 5, the shaft comprises three tapered portions that form two stepped stages that function as stoppers. In the embodiment of FIG. 6, the shaft comprises a single, threaded tapered portion, where the threads perform an anti-slip function. WO 2011/049643 A1 describes a clinch-type fastener.

Summary of the Invention [0011] The shortcomings of tack pins and tack screws listed above are all overcome by a novel design change that would incorporate the design of a Bellville type spring into the head of the tack pin or tack screw. It is believed that with the spring head design improvement, the tack pin or screw can provide all the advantages of a short screw, with the added benefits afforded by ordinary tack pins where because of their miniature size adding a separate washer is not practical. The spring head structure can directly address the clamp load issue as well as adding tolerance to the installation pressing distance, easing the requirement of a perfect installation.

[0012] More specifically the applicant has invented a fastener and an assembly of parts comprising two elements, a top element and a bottom elementface-to-face. The fastener comprises a head having a radially extending cone-shaped flange being the largestdiameterofthe fastener and having an uninterrupted peripheral circular surface adapted to resiliently deflect upwardly against the top element upon application of a downward installation force. The fastener has a shank which utilizes engagement means such as helical threads or a clinch undercut.

[0013] Therefore, it is the primary object of this invention is to add clamp load capability, and increase axial installation tolerance to a tack pin by means of incorporating the design of a Bellville washer into the head of the fastener. Given that the same feature can be added around the head of a micro screw, a secondary object is to devise a screw design that incorporates a Bellville washer into the head for the benefit of preventing loss of preload in the screw. It is a further objective to accomplish these advantages while also providing economy of manufacture and by eliminating an additional loose part that requires assembly.

[0014] In this respect, before explaining at least one embodiment of the invention in detail, it is to be understood that the invention is not limited in its application to the details of construction and to the arrangements of the components set forth in the following description or illustrated in the drawings. The invention is capable of other embodiments and of being practiced and carried out in various ways. Also, it is to be understood that the phraseology and terminology employed herein are for the purpose of description and should not be regarded as limiting.

[0015] In one aspect, the invention is a unitary fastener as claimed in claim 1 for joining a top element and a deformable bottom element face-to-face. In another aspect, the invention is an assembly of parts according to claim 2.

[0016] As such, those skilled in the art will appreciate that the conception, upon which this disclosure is based, may readily be utilized as a basis for the designing of other structures, methods, and systems for carrying out the several purposes of the present invention. It is important, therefore, that the claims be regarded as including such equivalent constructions insofar as they do not depart from the spirit and scope of the present invention.

Brief Description of the Drawings [0017]

Figures 1 and 2 are cross-sectional views of prior art fasteners.

Figure 3 is a cross-sectional view of three embodiments of the invention.

Description of the Preferred Embodiments [0018] Referring now to Figure 3, three embodiments of the fastener of the invention are shown in side-by-side comparison with a Belleville washer. Any one of the embodiments is utilized to create an assembly in place of the fasteners of the prior artshown in Figures 1 or2which join a top sheet to a bottom sheet. Each of the embodiments has a head which includes a cone-shaped flange which approximates the structure and performance of a Belleville washer shown at the far left.

[0019] A Belleville washer creates force opposite to the direction of its compression. This figure depicts how a Belleville washer can be incorporated into the head of a tack pin, a tack screw, and a micro screw. The maximum force capability of a Belleville spring is given by equations that can be sourced from website Spring-I-Pedia at: ht-tp://springipedia.com/belleville-washers-formulas.asp .

[0020] Upon installation, the periphery of the cone-shaped flange deflects resiliently upward as it forcefully contacts the top sheet. By the resilient nature of its material a continual biasing force is applied so that a residual clamp load is maintained.

[0021] For the case of the tack pin with clamp load it is desirable to provide the minimum equivalent clamp force that can be provided by the yield of the metal in its undercut after installation. Incorporating the Bellville washer functionality into the head of at Tack Pin or screw effectively adds top sheet compression distance to the tack. This head design is advantageous where the top sheet changes in length to a greaterdegree than the tack pin or screw thus ensuring that a clamp load will be created. The deflection of the head in this instance is far greater than can be expected from the flat sheet alone. Similarly for the case of a micro screw, the design equation for a Belleville washer head, we set the force equation for the yield strength of the female threads engaged equal to the max force available for a Bellville washer.

[0022] In the case of the screw, the fact that the screw is installed in tension creates the clamp load, and the necessity of the Bellville head to do this is not as important as it is for the tack pin or a tack screw. A Bellville head incorporated into the screw, however does provide the added benefits of: 1) Protection against the loss of preload of the screw 2) Over installation protection, such that a greater range for the tightening torque can be specified.

[0023] From the above description of the invention it can readily be seen that the objects of the invention have been achieved. The incorporation of a Bellville washer type of head into the design of a tack pin provides the capability of supplying a clamp load to an assembly where tack pins are used, where previously only small clamp load was possible for a narrow range of conditions . Additionally the incorporation of this type of head to a tack pin adds tolerance to the installation pressing distance, that helps safeguard an over pressing, or over loading that can cause cosmetic damage. Finally for the tack pin, the elimination of a potential gap under the head, in the case of an under installed part, will give a more firm feel to the assembly. The added benefit of this type of head to a micro screw is that it provides protection against the loss of preload in the screwed joint, as well as installation tolerance on the required installation torque range. By combining the benefits of a separate washer into the structure of the fastener there are economies of manufacture and fewer problems with loose parts and the additional step of assembling the washer which may be impractical for miniature parts.

[0024] Therefore, the foregoing is considered as illustrative only of the principles of the invention. Further, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact construction and operation shown and described, and accordingly, all suitable modifications and equivalents may be resorted to, falling within the scope of the invention.

Claims 1. A unitary fastener for joining a top element and a deformable bottom elementface-to-face, thefasten-er comprising: a head including a cone-shaped flange being the largest diameter of the fastener, said flange having an uninterrupted circular periphery adapted to resiliently deflect upwardly; and a shank extending immediately downward from said head, said shank having one of (a), (b), and (c) as follows: (a) attachment means including: (a1) a collar immediately downward from the head; and (a2) an undercut immediately downward from the collar and adapted to receive the cold flow of material from the deformable bottom element, the largest diameter of the undercut being smaller than the diameter of the collar; (b) attachment means including: (b1) a collar immediately downward from the head; and (b2) a helically threaded shaft adapted to receive the cold flow of material from the deformable bottom element, the largest diameter of the shaft being smaller than the diameter of the collar; and (c) attachment means including a helically threaded shaft immediately downward from the head and adapted to receive the cold flow of material from the deformable bottom element. 2. An assembly of parts, comprising: a fastener according to claim 1; and a top element in face-to-face abutment with a deformable bottom element, said top element including an aperture through which the shank of said fastener passes, wherein: the shank of said fastener is engaged with a preformed hole cavity in said deformable bottom element to a depth where the periphery of the fastener head flange is in forcible contact with the top element and deflected sufficiently to apply a downward re-siliently biasing residual clamp load between said elements. 3. The assembly of claim 2 wherein said fastener is a unitary metal structure. 4. The assembly of any one of claims 2 and 3 wherein said shank attachment means is only the undercut. 5. The assembly of any one of claims 2-4 wherein the diameter of the fastener is 1.0 mm. 6. The assembly of any one of claims 2-5 wherein the cold flow of material of the deformable bottom element is caused by a downward installation force applied to the head. 7. The fastener of claim 1 wherein the fastener is a unitary metal structure. 8. The fastener of any one of claims 1 and 7 wherein said shank attachment means is only the undercut. 9. The fastener of any one of claims 1,7, and 8 wherein the diameter of the fastener is 1.0 mm. 10. The fastener of any one of claims 1 and 7-9 wherein the cold flow of material of the deformable bottom element is caused by a downward installation force applied to the head.

Patentansprüche 1. Ein unitäres Befestigungselement zum Zusammenfügen der Stirnflächen eines oberen Elements und eines verformbaren unteren Elements, wobei das Befestigungselement Folgendes umfasst: einen Kopf enthaltend einen kegelförmigen Flansch mit dem größten Durchmesser des Befestigungselements, wobei besagter Flansch über einen ununterbrochenen kreisförmigen Randbereich verfügt, der so adaptiert ist, dass ersieh elastisch nach oben biegt; und einen Schenkel, dersich von besagtem Kopf unmittelbar nach unten erstreckt, wobei der Schenkel eines von (a), (b) und (c) aufweist, wie nachstehend aufgeführt: (a) Befestigungsmittel enthaltend: (a1) einen Kragen unmittelbar unter halb des Kopfes; und (a2) eine Hinterschneidung unmittelbar unterhalb des Kragens und adaptiert, um den Kaltfluss von Material vom verformbaren unteren Element entgegenzunehmen, wobei der größte Durchmesser der Hinterschneidung kleiner ist als der Durchmesser des Kragens; (b) Befestigungsmittel enthaltend: (b1) einen Kragen unmittelbar unterhalb des Kopfes; und (b2) einen helikal umlaufenden Schraubschaft adaptiert, um den Kaltfluss von Material vom verformbaren unteren Element entgegenzunehmen, wobei der größte Durchmesser des Schenkels kleiner ist als der Durchmesser des Kragens; und (c) Befestigungsmittel enthaltend einen helikal umlaufenden Schraubschaft unmittelbar unterhalb des Kopfes und adaptiert, um den Kaltfluss von Material vom verformbaren unteren Element entgegenzunehmen. 2. Eine Baugruppe aus Teilen umfassend: ein Befestigungselement gemäß Anspruch 1; und ein oberes Element, welches Stirnfläche an Stirnfläche an einem verformbaren unteren Element anliegt, wobei besagtes oberes Element eine Öffnung aufweist, durch die der Schenkel des besagten Befestigungselements geführt wird, wobei: der Schenkel des besagten Befestigungselements so tief in eine vorgeformte Lochkavität im besagten verformbaren unteren Element eingreift, dass der Randbereich des Kopfflansches des Befestigungselements in forciertem Kontakt mit dem oberen Element steht und ausreichend gebogen wird, um eine nach unten gerichtete, elastisch vorspannende Restklemmlast zwischen besagten Elementen anzuwenden. 3. Die Baugruppe gemäß Anspruch 2, wobei das besagte Befestigungselement eine unitäre Metallstruktur ist. 4. Die Baugruppe gemäß irgendeinem der Ansprüche 2 und 3, wobei das besagte Schenkelbefestigungsmittel nur die Hinterschneidung ist. 5. Die Baugruppe gemäß irgendeinem der Ansprüche 2-4, wobei der Durchmesser des Befestigungselements 1,0 mm beträgt. 6. Die Baugruppe gemäß irgendeinem der Ansprüche 2-5, wobei der Kaltfluss von Material vom verformbaren unteren Element durch eine nach unten gerichtete, auf den Kopf angewandte Installationskraft verursacht wird. 7. Das Befestigungselement gemäß Anspruch 1, wobei das Befestigungsmittel eine unitäre Metallstruktur ist. 8. Das Befestigungselement gemäß irgendeinem der Ansprüche 1 und 7, wobei das besagte Schenkelbefestigungsmittel nur die Hinterschneidung ist. 9. Das Befestigungsmittel gemäß irgendeinem der Ansprüche 1,7 und 8, wobei der Durchmesser des Befestigungselements 1,0 mm beträgt. 10. Das Befestigungsmittel gemäß irgendeinem der Ansprüche 1 und 7-9, wobei der Kaltfluss von Material vom verformbaren unteren Elementdurch eine nach unten gerichtete, auf den Kopf angewandte Installationskraft verursacht wird.

Revendications 1. Attache unitaire destinée à joindre un élément supérieur et un élément inférieur déformable face à face, l’attache comprenant : une tête comprenant une collerette de forme conique qui constitue le plus grand diamètre de l’attache, ladite collerette ayant une périphérie circulaire non interrompue conçue pour se déformer élastiquement vers le haut ; et une tige s’étendant immédiatement vers le bas à partirde ladite tête, ladite tige comprenant l’un parmi (a), (b) et (c) ci-après : (a) un moyen de fixation comprenant : (a1) une embase immédiatement en dessous de la tête ; et (a2) un caniveau immédiatement en dessous de l’embase et conçu pour recevoir le fluage de matériau depuis l’élément inférieur déformable, le plus grand diamètre du caniveau étant inférieur au diamètre de l’embase ; (b) un moyen de fixation comprenant : (b1) une embase immédiatement en dessous de la tête ; et (b2) une tige filetée en hélice conçue pour recevoir le fluage de matériau depuis l’élément inférieur déformable, le plus grand diamètre de la tige étant inférieur au diamètre de l’embase ; et (c) un moyen de fixation comprenant une tigefiletéeen hélice immédiatementendes-sous de la tête et conçue pour recevoir le fluage de matériau depuis l’élément inférieur déformable. 2. Assemblage de pièces, comprenant : une attache selon la revendication 1 ; et un élément supérieur abouté face à face avec un élément inférieur déformable, ledit élément supérieur comprenant une ouverture à travers laquelle passe la tige de ladite attache, où : la tige de ladite attache est insérée dans une cavité de trou préformée dans ledit élément inférieur déformable à une profondeur à laquelle la périphérie de la collerette de la tête de l’attache est en contact forcé avec l’élément supérieur et suffisamment déformée pour appliquer une charge de serrage résiduelle de sollicitation élastique en direction du bas entre lesdits éléments. 3. Assemblage selon la revendication 2 dans lequel ladite attache est une structure métallique unitaire. 4. Assemblage selon l’une quelconque des revendications 2 et 3 dans lequel ledit moyen de fixation de la tige est uniquement le caniveau. 5. Assemblage selon l’une quelconque des revendications 2 à 4 dans lequel le diamètre de l’attache est de 1,0 mm. 6. Assemblage selon l’une quelconque des revendications 2 à 5 dans lequel le fluage de matériau de l’élément inférieur déformable est provoqué par une force d’installation dirigée vers le bas appliquée à la tête. 7. Attache selon la revendication 1, ladite attache étant une structure métallique unitaire. 8. Attache selon l’une quelconque des revendications 1 et 7 dans laquelle ledit moyen de fixation de la tige est uniquement le caniveau. 9. Attache selon l’une quelconque des revendications 1, 7 et 8 dans laquelle le diamètre de l’attache est de 1,0 mm. 10. Attache selon l’une quelconque des revendications 1 et 7 à 9 dans laquelle le fluage de matériau de l’élément inférieur déformable est provoqué par une force d’installation dirigée vers le bas appliquée à la tête.

REFERENCES CITED IN THE DESCRIPTION

This list of references cited by the applicant is for the reader’s convenience only. It does not form part of the European patent document. Even though great care has been taken in compiling the references, errors or omissions cannot be excluded and the EPO disclaims all liability in this regard.

Patent documents cited in the description • WO 61871019 A [0001] · WO 2011049643 A1 [0010] • JP2000304019 A[0010]

Claims

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