US20140056664A1 - High performance sleeved interference fasteners for composite applications - Google Patents
High performance sleeved interference fasteners for composite applications Download PDFInfo
- Publication number
- US20140056664A1 US20140056664A1 US14/069,931 US201314069931A US2014056664A1 US 20140056664 A1 US20140056664 A1 US 20140056664A1 US 201314069931 A US201314069931 A US 201314069931A US 2014056664 A1 US2014056664 A1 US 2014056664A1
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- United States
- Prior art keywords
- fastener
- sleeve
- pin
- workpieces
- smooth cylindrical
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- Abandoned
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- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 6
- 230000036316 preload Effects 0.000 description 4
- RTAQQCXQSZGOHL-UHFFFAOYSA-N Titanium Chemical compound [Ti] RTAQQCXQSZGOHL-UHFFFAOYSA-N 0.000 description 3
- 229910002804 graphite Inorganic materials 0.000 description 3
- 239000010439 graphite Substances 0.000 description 3
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- 239000010936 titanium Substances 0.000 description 3
- 229910052719 titanium Inorganic materials 0.000 description 3
- 241001136800 Anas acuta Species 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
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- 230000037431 insertion Effects 0.000 description 2
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- 230000013011 mating Effects 0.000 description 2
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- 238000000926 separation method Methods 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
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- 230000003068 static effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B33/00—Features common to bolt and nut
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B5/00—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them
- F16B5/02—Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them by means of fastening members using screw-thread
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B13/00—Dowels or other devices fastened in walls or the like by inserting them in holes made therein for that purpose
- F16B13/04—Dowels or other devices fastened in walls or the like by inserting them in holes made therein for that purpose with parts gripping in the hole or behind the reverse side of the wall after inserting from the front
- F16B13/06—Dowels or other devices fastened in walls or the like by inserting them in holes made therein for that purpose with parts gripping in the hole or behind the reverse side of the wall after inserting from the front combined with expanding sleeve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B13/00—Dowels or other devices fastened in walls or the like by inserting them in holes made therein for that purpose
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B19/00—Bolts without screw-thread; Pins, including deformable elements; Rivets
- F16B19/04—Rivets; Spigots or the like fastened by riveting
- F16B19/05—Bolts fastening by swaged-on collars
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B33/00—Features common to bolt and nut
- F16B33/002—Means for preventing rotation of screw-threaded elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
- F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
- F16B35/041—Specially-shaped shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B35/00—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws
- F16B35/04—Screw-bolts; Stay-bolts; Screw-threaded studs; Screws; Set screws with specially-shaped head or shaft in order to fix the bolt on or in an object
- F16B35/041—Specially-shaped shafts
- F16B35/048—Specially-shaped necks
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
- F16B39/00—Locking of screws, bolts or nuts
- F16B39/02—Locking of screws, bolts or nuts in which the locking takes place after screwing down
- F16B39/026—Locking of screws, bolts or nuts in which the locking takes place after screwing down by swaging the nut on the bolt, i.e. by plastically deforming the nut
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Insertion Pins And Rivets (AREA)
- Connection Of Plates (AREA)
- Dowels (AREA)
- Manufacture Of Alloys Or Alloy Compounds (AREA)
Abstract
A fastener adapted to pass through aligned holes through workpieces is disclosed. The fastener includes a pin member having a transition portion wherein the diameter of the transition portion decreases radially as it extends from the smooth cylindrical shank portion to the threaded portion. The fastener may also comprise a sleeve member and a clamping means. The clamping means includes a collar, a nut, or any other possible clamping means. In exemplary embodiments, the workpieces can be formed with a plurality of materials, the materials including composite, metallic, or composite/metallic structures, any combination thereof. In particular embodiments, the fastener has interference capability of 0.0005 to 0.0100 inches in composite structures without risk of composite delamination or damage. As a result of the fastener interference, gaps between the fastener and the structure are eliminated thereby providing good electrical conductivity between components. As a result, the potential for electrical sparks is reduced, providing a safer fastener for use with aerospace applications.
Description
- 1. Field
- The present disclosure relates to an improved threaded fastener and method for securing workpieces of composite materials. In particular embodiments, the present disclosure relates to a fastener including a pin and a preformed sleeve which may be placed around the pin for use in interference applications.
- 2. General Background
- More and more graphite composite materials are being incorporated into aircraft structures. Use of graphite composites increase strength, increase life, reduce weight, reduce fuel consumption, increase payload, among other benefits. However, as these newer materials are utilized, new challenges need to be overcome in fastening technology when compared to typical metallic structures.
- Existing aerospace fasteners cannot be safely installed in interference conditions in graphite or mixed graphite-composite metallic structures. Typically, clearance fit fasteners are utilized to avoid concerns of composite delamination and potential structural failure that make these fasteners unsafe to utilize. As a result, fasteners are installed in clearance holes that result in the reduction of dynamic joint performance, gaps in the structure, and other structural concerns.
- The resulting gap between the fastener shank portion and hole prevent uniform contact of structural components. Consequently, safe dissipation of lightning strike current/energy, and electro-magnetic currents is a major concern. Currently, aircraft manufacturers are resorting to elaborate, expensive, and sometimes risky alternative methods to properly ground the structure. For example, copper, or another low conductive strip, may be incorporated onto the surface of the workpieces to provide a preferential low resistance path for any current. Additionally, a film adhesive containing a conductive fiber carrier film capable of conducting high currents between two workpieces may be utilized. However, both of these methods are very expensive and not a cost effective way to provide safe dissipation of current.
- Additionally, prior fasteners cannot be installed with significant amounts of sealant, as is required in most aircraft structures. If sufficient sealant is utilized during installation, the coefficient of friction between the fastener assembly and the workpieces is reduced hindering installation capability. Additionally, there is an inability to flow any excess sealant out of the joint.
- Further, previous pins with mating sleeves manufactured for interference applications are only capable of being installed in 100% graphite composite materials. In addition, these fasteners are limited to applications of short lengths and small diameters. Prior fasteners cannot be installed in any composite/metallic structures and most 100% percent composite structures.
- Additionally, previous fasteners for interference applications are only available in shear load range strength capabilities. The collars utilized in these fasteners are typically commercially pure titanium and subject to creep at fairly low elevated temperatures.
- Thus, there is a need to provide a fastener that allows for interference applications without the possibility of delamination and structural failure.
- There is also a need to provide a fastener that may be used in a variety of different applications. Utilization of a fastener in a variety of composite/metallic structures is needed.
- Additionally, there is a need to provide fasteners which provide safe dissipation of electrical currents caused by lightning strikes and/or static electricity. Fasteners that allow for uniform contact of the structural components will provide the necessary dissipation and a safer, more cost effective solution to the problems involving electrical currents.
- In one aspect of the present disclosure, a fastener is disclosed having a pin. The pin member includes an elongated smooth cylindrical shank portion and an enlarged head for mating with the sleeve. In some embodiments, there is a countersink or protruding head for engagement with a flared end of the sleeve. The pin member also includes a threaded portion and a frangible portion axially aligned with the smooth cylindrical shank portion. The frangible portion includes a pull groove portion having circumferential pull grooves adapted to be gripped for applying a relative axial force to pull the pin member into the sleeve. The pin member includes a breakneck groove between the threaded portion and the frangible portion. As the fastener is installed, the frangible portion is separated at the breakneck groove.
- The pin includes a transition portion between the smooth cylindrical shank portion and the treaded portion designed and optimized to minimize the installation force required for the high interference conditions resulting from installation. In exemplary embodiments, the transition portion may be tapered and have an angle less than or equal to 20 degrees from the pin shank. In other embodiments, the transition portion reduces the radial diameter of the pin shank between 0.004 to about 0.005 inches over a distance of 0.010 to 0.290 inches between the smooth portion and the threaded portion.
- In other embodiments, the fastener further comprises a sleeve and a clamping means to secure together workpieces. The clamping means may comprise a collar or nut member or any other means suitable to fasten the workpieces together with the pin and sleeve. The fastener is installed through aligned holes located in two or more workpieces. In some embodiments, one of the holes through the workpieces includes a countersink, or lead in radius, on its outer opening.
- The sleeve, adapted to fit over the smooth cylindrical shank portion, includes a tubular portion and an enlarged end for engagement with the outer surface of the workpiece. In some embodiments, there is a flared end for engagement with the countersink portion in the workpieces. The sleeve has a length greater than the maximum total thickness of the workpieces to be joined at the location of the aligned holes. The tubular portion of the sleeve has an inner diameter less than the diameter of the smooth cylindrical shank portion and an outer diameter sized to permit fitting of the sleeve into the aligned clearance holes of the workpieces.
- In one aspect, the pin member has a smooth cylindrical shank portion with a diameter greater than the maximum inner diameter of the sleeve. When the smooth cylindrical shank portion enters into and pulls through the sleeve, the sleeve radially expands into an interference fit with the walls of the holes of the workpieces.
- The tubular collar member is adapted to be fit over the threaded portion of the pin member including a counterbore to enable the collar to provide clearance over the sleeve, and an annular flange portion at one end for engagement with the other outer surface of the workpieces. The collar member includes an enlarged cylindrical shank portion having a uniform outside diameter adapted to be swaged into the threaded portion of the pin.
- In another embodiment, the nut member is adapted to fit the threaded portion of the pin member including a counterbore to enable the nut member to provide clearance over the sleeve, and an annular flange portion at one end for engagement with the other outer surface of the workpieces. The nut member includes a threaded portion to be threaded onto the threaded portion of the pin to secure the fastener to the workpieces.
- In another aspect, the sleeve member includes lubrication on the inner diameter surface to reduce friction as the pin smooth cylindrical shank portion enters the sleeve. The outer diameter surface of the sleeve and/or the inner diameter of the aligned holes has a rougher surface. In particular embodiments, the coefficient of friction between the inner surface of the sleeve and the smooth cylindrical shank portion of the pin member is less than the coefficient of friction between the outer surface of the sleeve and inner diameter of the holes, allowing the sleeve to expand radially upon insertion of the smooth cylindrical shank portion of the pin member to be in an interference fit.
- In a further aspect, a fastener is disclosed that has the capability of being installed in composite, metallic, or composite/metallic structures. For example, the disclosed fastener could be installed in, for example, graphite composites, titanium, aluminum, or a mixture of these components.
- In another aspect, as a result of the fastener interference, gaps between the fastener and the structure are eliminated thereby providing good electrical conductivity between components. As a result, the potential for electrical sparks is reduced, providing a safer fastener for use with aerospace applications.
- In another aspect, the fastener has interference capability of 0.0005 to 0.0100 inches in composite and/or metallic structures without risk of composite delamination or damage.
- In an additional aspect of the present disclosure, the fastener has a functional grip capability of about 0.062 to about 0.140 inches.
- Other objects, features, and advantages of the present disclosure will become apparent from the subsequent description and the appended claims, taken in conjunction with the accompanying drawings
- The foregoing aspects and advantages of present disclosure will become more readily apparent and understood with reference to the following detailed description, when taken in conjunction with the accompanying drawings, wherein:
-
FIG. 1 illustrates an exemplary embodiment of the fastener showing the pin and the sleeve of the fastener, the pin having an enlarged flush head. -
FIG. 2 illustrates another exemplary of the fastener showing the pin and the sleeve of the fastener, the pin having an enlarged protruding head -
FIG. 3 illustrates another embodiment of the fastener showing the pin and sleeve of the fastener, the pin having a longer threaded area and no frangible portion and an enlarged flush head. -
FIG. 4 illustrates another embodiment of the fastener showing the pin and sleeve of the fastener, the pin having an enlarged protruding head. -
FIG. 5 illustrates a plurality of workpieces having aligned holes for installation of the fastener to secure the workpieces together. -
FIG. 6 illustrates a plurality of workpieces having aligned holes for installation of the fastener to secure the workpieces together, the outer portion of one of the workpieces having a countersink. -
FIG. 7 illustrates the exemplary fastener before the pin has been pushed or pulled through the sleeve. The sleeve has not expanded and stretched to a desired interference fit. -
FIG. 8 illustrates the fastener after the pin has been pushed or pulled into position and also illustrates the collar placed onto the pin prior to swaging. -
FIG. 9 illustrates the fastener with the collar swaged onto the threaded portion of the pin to secure the fastener prior to pintail separation. -
FIG. 10 illustrates the fastener in an engaged, installed position, after pintail separation. - A fastener for securing together a plurality of
workpieces holes fastener 10 includes apin member 15, asleeve member 20 and acollar 200. In other embodiments, the fastener may include a nut instead of a collar. In exemplary embodiments, theworkpieces workpieces - An embodiment of the pin and
sleeve assembly 12 is shown inFIGS. 1 and 2 . Thepin member 15 includes anelongated shank portion 40 which terminates at oneend 30 with anenlarged flush head 37 or protrudinghead 35. Thepin shank portion 40 includes a substantially smoothcylindrical portion 45, a threadedportion 50, and afrangible portion 60. The smooth cylindrical shank portion extends from thehead expansion sleeve 20. Following the substantially smoothcylindrical portion 45 is a threadedportion 50. The threadedportion 50 is generally uniformly threaded throughout its length. A taperedtransition portion 55 smoothly merges the threadedportion 50 with the smoothcylindrical shank portion 45. - The
frangible portion 60 of thepin member 15 extends from the threadedportion 50. Thefrangible portion 60 includes a cylindrical land 70 and apull groove portion 75 having circumferential pullgrooves 75. Abreakneck groove 65 that is located adjacent to the threadedportion 50 and defines the weakest portion of thefastener 10. - In some embodiments, the threaded
portion 50,breakneck groove 65, straight land 70 and pullgroove portion 75 has a maximum diameter which is less than the diameter of the smoothcylindrical portion 45 of the shank portion, the straight land portion 70 having a diameter smaller than that of the threadedportion 50 and pullgroove portion 75. - In this embodiment, the
expansion sleeve member 20 has a generally uniformtubular portion 80 that terminates in an enlarged flanged shapedhead 85 to receive theflush head 37 or protrudinghead 35 of thepin member 15. Thesleeve 20 has an internal diameter that is greater than the threadedportion 50 andfrangible portions 60 of thepin 15, but less than the diameter of the smoothcylindrical shank portion 45. - The inner diameter of the
sleeve member 20 includes a low friction coating on itssurface 90 to facilitate movement of thepin member 15 into thesleeve 20 during installation. In a particular embodiment, thesleeve member 20 is coated with low friction coating to eliminate the resistance between the smoothcylindrical shank portion 45 of thepin member 15 and theinner diameter surface 90 of thesleeve tubular portion 80. The low friction coating on the inner diameter of the sleeve allows thepin member 15 to slide through thesleeve member 20 easier due to reduced frictional loading. - Additionally, the coating on the
inside diameter surface 90 enables the installation of the fastener to function when fasteners are installed with minimum, moderate, or heavy amounts of sealant on the fastener and in the installed joint. - Another embodiment of the fastener is illustrated in
FIG. 3 andFIG. 4 . In this embodiment, thepin member 15 includes anelongated shank portion 40 which terminates at oneend 30 with anenlarged head head 37 as shown in the embodiment inFIG. 2 . Thepin shank portion 40 includes a substantially smoothcylindrical portion 45, a threadedportion 50, but does not include a frangible portion. The smooth cylindrical shank portion extends from thehead expansion sleeve 20. Following the substantially smoothcylindrical portion 45 is a threadedportion 50. The threadedportion 50 is generally uniformly threaded throughout its length. A taperedtransition portion 55 smoothly merges the threadedportion 50 with the smoothcylindrical shank portion 45. - The
workpieces holes FIGS. 5 and 6 . Thefastener assembly 10 extends through the alignedholes workpieces workpieces 115 receive the enlarged head of the sleeve. As seen in the embodiment depicted inFIG. 6 , the opening in theouter workpiece 105 terminates at itsouter surface 115 in acountersink potion 120, or lead in radius portion, which is shaped to receive theenlarged flange 85 of theexpansion sleeve member 20. - The outer diameter of the
sleeve tubular portion 80 before thepin member 15 is pushed or pulled into thesleeve member 20 is smaller than the diameter of the holes placed in theworkpieces FIG. 7 . The outside diameter of thesleeve tubular portion 80, in its pre-expanded state, and the diameter of the bores provide a slip fit when the tubular portion of thesleeve member 20 is located within the holes. - During installation, as the
pin member 15 is pushed or pulled through the sleeve, the sleeve expands radially to a desired interference fit with the walls of theholes workpieces sleeve member 20 as depicted inFIG. 8 . In this manner, thesleeve member 20 is shielding the surfaces of the clearance holes from the pin shank portion, and thus, eliminating delamination of the plurality of workpieces as the pin is pushed or pulled into thesleeve member 20. - The tapered
transition portion 55 is designed and optimized to minimize the installation force required for the high interference conditions resulting from thepin member 15 installation into thesleeve member 20. Thetransition portion 55 has a shallow lead-in angle that reduces the force that is needed for installation. Since less force is needed to install thefastener 10 into the interference condition, thefastener 10 allows for much longer grip lengths while diminishing sleeve stretch and premature sleeve failure. - In exemplary embodiments, the
transition portion 55 may be tapered and have an angle of less than or equal to 20 degrees from the pin shank as the diameter decreases radially from the smooth shank portion to the thread portion. In the embodiment illustrated, the diameter of thetransition portion 55 is tapered and decreases in a uniform fashion. However, the transition portion can be any shape as long as the radius of the pin shank decreases. For example, the transition portion could be a gentle radius decrease shaped as a convex curve, a concave curve or an s-shaped curve, or be in configuration that would allow a reduction in the radius between the smooth shank portion and the threaded portion of the pin. In these embodiments, thetransition portion 55 reduces the radius of the pin shank between 0.004 to about 0.005 inches over a distance of 0.010 to 0.290 inches. In exemplary embodiments, thesleeve 20 radially expands between about 0.003 and 0.012 inches as the fastener is installed. In an exemplary embodiment, the interference of thefastener 10 with theworkpieces - As a result of the fastener interference of the disclosed
fastener 10, gaps between thefastener 10 and the workpiece structures are eliminated. Accordingly, good electrical conductivity between the components is provided. The potential for electrical sparks is reduced making thefastener 10 more safe for use in aerospace applications. - In exemplary embodiments, the surface of the outer diameter of the
sleeve 20 and/or the inner diameter of theholes outer surface 95 of thesleeve member 20 and theinside diameter surface 135 of theholes pin 15 into thesleeve member 20 must be lower than the coefficient of friction and/or the load between the sleeveouter diameter surface 95 and theinner diameter surface 135 of the holes to provide the radial expansion of thetubular portion 80 of thesleeve 20. Without the differential coefficient of friction, thesleeve 20 may be pulled into the holes prior to installation. - In exemplary embodiments, the rougher outer surface of the sleeve and/or the inner surface of the holes combined with the lubrication on the
inner surface 90 of thesleeve member 20 prevents the excessive stretching of thesleeve 20 during installation. The coefficient of friction between theouter surface 95 of the sleeve andinner surface 135 of the holes is greater than the coefficient of friction between the inner surface of the sleeve and the smooth cylindrical shank of the pin member. As a result, thesleeve 20 expands radially into the interference position and the stretching of thesleeve 20 is diminished. - In exemplary applications, the difference in the coefficient of friction will allow the stretching of the
sleeve member 20 to be reduced to less than 0.050 inches. Additionally, the characteristics of the surfaces of thesleeve 20 allow for the use of sealant in the joint and on thefastener 10. - In exemplary embodiments, the optimized angled
transition portion geometry 55 of thepin member 15 is designed to minimize the installation force necessary to install thefastener 10 into the interference conditions up to 0.010 inches. The geometry designed allows the force applied when inserting the pin to be applied perpendicular to theangled transition portion 55, instead of parallel to the insertion of thepin member 15 as with traditional bull-nose transition geometry. A lower force is needed to insert thepin member 15. As a result of the lower force required, thefastener 10 can be installed with a larger variety of workpieces, including metallic, composite and metallic/composite structures. - The transition geometry, the tapered
transition portion 55, on thepin member 15 is also important as it allows functionality with much longer grip lengths without excessive sleeve stretch and/or premature sleeve failure. - To fully clamp the workpieces together, a clamping means is utilized. The clamping means could be either the threaded
nut member 250 depicted inFIG. 3 or thecollar member 200 illustrated inFIG. 8 . Other clamping means may also be utilized to secure the workpieces together. - In one embodiment, a symmetrically shaped,
tubular collar 200 of a pre-selected material is placed over the installed pin andsleeve assembly 12 as illustrated inFIG. 8 . As theworkpieces pin member 15. Thecollar 200 has acounterbore portion 215 that is adapted to be located over the pin shank and a collar through bore, the inner diameter of the throughbore 210 being selected to provide clearance to thepull grooves 75 and threadedportion 50 of thepin 15. The collar geometry is volume balanced. Significantly, the wall thickness of thecollar 200 is uniform and symmetrically shaped for swaging into the threadedportion 50 to provide the desired clamp load. - As illustrated in
FIG. 3 , another embodiment of thefastener 10 utilizes anut member 250 to secure the workpieces together. Thenut member 250 includes a threadedportion 255 to mate with the threadedportion 50 of the pin member. - Both the
collar member 200 ornut member 250 has acounterbore portion 215 at one end that allows thecollar 200 ornut 250 to clear thesleeve component 20. Thus, thecounterbore portion 215 has a diameter greater than the outer diameter of thesleeve 20. As a result, the installedfastener 10 has a reduced height and weight. This makes the fastener 10 a much more cost-effective solution than previous fasteners. - Both the
collar 200 ornut member 250 also include anenlarged flange 220 at one end. Theflange 220, being in engagement with theouter surfaces 140 of the plurality of workpieces, is provided to have a predetermined area of engagement in order to distribute the installation and final clamp loads on theouter surfaces 140 of theworkpieces workpieces flange 220 is selected to be sufficient to resist localized delamination or crushing of the composite material at the outer surfaces of theworkpieces - The collar member of the
fastener 10 is swaged to the threaded portion of thepin member 15 as shown inFIG. 9 . In particular embodiments, the optimized collar geometry balanced with the existing thread forms and installation tools to allow swaging of the collar into the threadedportion 50. Thecollar 200 may be swaged into about 40 to 60% of the depth of thethreads 50 while maintaining control of the collar material and achieving a consistent high, clamp load/preload. - A consistent,
high fastener 10 clamp significantly increases the dynamic joint performance and life of the aircraft structure. In particular embodiments, the high clamp/preload averages about 50 to 96% of the minimum tensile strength of the installed fastener. In more exemplary embodiments, the high clamp/preload averages about 78% of the minimum tensile strength. In typical fasteners, the high clamp/preload averages only about 50% of the minimum tensile strength. - Additionally, the controlled, partial fill of the threaded
portion 50 of thepin member 15 allows for significant and even sealant flowout during installation. The mechanical performance of thefastener 10 is not reduced with this sealant flowout. - The controlled, swaged fill by the
collar 200 is also an improvement compared to prior art fasteners. In typical applications, there is an inherent gap between the internal and external threads of the pin member and the collar or nut. In addition, the non-pressure side of thefastener 10 and the counterbores of the collar or nut has gaps between the components. Thefastener 10 disclosed herein creates full contact on both sides of the threadedportion 50 of thepin 15, eliminating gaps. Accordingly, the fastener has better conductivity and provides a safer fastener for aerospace conditions, in addition to improving fuel tightness. - When the
collar 200 is swaged, it is swaged over the end portion of thesleeve member 20. As a result, thesleeve member 20 is compressed over thetransition angle portion 55 of thepin 15. Accordingly, thesleeve 20 andpin 15 can then be removed as a single unit if necessary. This improves the efficiency and workability of thefastener 10 installed in various applications while also improving conductivity. - An exemplary implementation of the installed
fastener 10 is illustrated inFIG. 9 . Thefastener 10, with the pin having a shank of predetermined length can be selected to fasten the plurality ofworkpieces workpieces - For particular applications of the disclosed fastener, 110% of minimum mechanical performance is achieved with a functional grip capability of about 0.136 inches. Typical fasteners only have a functional grip capability of about 0.062 inches. Having a longer functional grip capability variance provides the
fastener 10 with more versatility to be used with different applications. - To install the
fastener 10, the sleeve is placed onto the pin as is depicted inFIG. 1 . Thesleeve 20 andpin 15 is then placed into the aligned holes of theworkpieces pin 15 extends beyond the outer surface of the plurality ofworkpieces pull grooves 75 of thepin member 15 for pull-in capability. - As the
pin member 15 is pulled by the tool, the smoothcylindrical shank portion 45 of thepin member 15 will be pulled into thesleeve member 20 causing thesleeve 20 to expand radially outward. The magnitude of this expansion is a function of the friction and force required between the smooth cylindricalshank pin portion 45 and theinner diameter surface 90 of the sleeve and the friction and force between the outer diameter of thesleeve 95 and the inner diameter of theholes 135 in the plurality ofworkpieces - Then the
collar member 200 is placed over thepin member 15 andsleeve 20 so that theflange portion 220 sits against theworkpiece surface 140. At this point, a swaging tool is utilized to swage thecollar member 200 onto the threadedportion 50 of the pin member, locking thefastener 10 into place. - In another embodiment, to install the
fastener 10, the sleeve is placed onto the pin as is depicted inFIG. 3 . Thesleeve 20 andpin 15 is then placed into the aligned holes of theworkpieces pin 15 is pushed into thesleeve 20 so that a sufficient length of the threaded portion of thepin 15 extends beyond the outer surface of the plurality ofworkpieces nut 250 can mate with the threaded portion of the pin. Thenut 250 is then installed and tightened to finalize the installation. - Thus, a
unique fastener 10 is disclosed providing an interference fit within composite, metallic, and metallic/composite structures. Thefastener 10 provides an improved dynamic joint performance as a result of better fastener interference and higher clamp loads. The geometry of the various components allows for the interference conditions while eliminating delamination and potential structural failure. The interference eliminates gaps between thefastener 10 and the structure, providing good electrical conductivity and reducing the potential for electrical sparks, increasing the safety of thestructure 10. - While the above description contains many particulars, these should not be considered limitations on the scope of the disclosure, but rather a demonstration of embodiments thereof. The fastener and uses disclosed herein include any combination of the different species or embodiments disclosed. Accordingly, it is not intended that the scope of the disclosure in any way be limited by the above description. The various elements of the claims and claims themselves may be combined any combination, in accordance with the teachings of the present disclosure, which includes the claims.
Claims (8)
1-34. (canceled)
35. A fastener, comprising:
a sleeve member having an enlarged head at one end and a tubular portion, the tubular portion having an inner surface with an inner diameter, and an outer surface with an outer diameter, wherein the outer diameter of the tubular portion is less than an inner diameter of inner surfaces of aligned holes of a plurality of workpieces in which the fastener is adapted to be installed, wherein the inner surface of the tubular portion of the sleeve member is coated with a low friction coating; and
a pin member having an enlarged pin head at one end thereof, a threaded portion at an opposite end thereof, a smooth cylindrical shank portion located below the pin head and having a diameter greater than the inner diameter of the tubular portion of the sleeve member, and a transition portion between the smooth cylindrical shank portion and the threaded portion, wherein the pin member is adapted to be installed within the sleeve member, and wherein the coating of the sleeve member is adapted to reduce the amount of friction as the smooth cylindrical shank portion of the pin member enters the sleeve member, and the transition portion reducing a radius between the smooth cylindrical shank portion and the threaded portion of the pin member for minimizing an installation force required for installing the pin member into the sleeve member, and
wherein a coefficient of friction between the inner surface of the tubular portion of the sleeve member and the smooth cylindrical shank portion of the pin member is less than a coefficient of friction between the outer surface of the tubular portion of the sleeve member and the inner surfaces of the aligned holes of the plurality of workpieces to expand the sleeve member into an interference fit with the plurality of workpieces in a range of about 0.0005 inch to about 0.0100 inch.
36. The sleeve interference fastener of claim 35 , wherein the transition portion includes an angle less than about 20 degrees from the smooth cylindrical shank portion as the diameter decreases radially from the smooth cylindrical shank portion to the threaded portion of the pin member.
37. The fastener of claim 35 , wherein the transition portion includes a length between 0.010 inch and 0.0290 inch, and the diameter of the transition portion decreasing radially between 0.004 inch and 0.005 inch as it extends from the smooth cylindrical shank portion to the threaded portion of the pin member.
38. The fastener of claim 35 , further comprising clamping means adapted to fit over the threaded portion of the pin member.
39. The fastener of claim 38 , wherein the clamping means includes a threaded nut member.
40. The fastener of claim 38 , wherein the clamping means includes a collar.
41. The fastener of claim 38 , wherein the clamping means includes a counterbore portion having a diameter greater than the outer diameter of the sleeve member.
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US14/817,331 US20160097418A1 (en) | 2006-09-21 | 2015-08-04 | High performance sleeved interference fasteners for composite applications |
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US14/069,931 US20140056664A1 (en) | 2006-09-21 | 2013-11-01 | High performance sleeved interference fasteners for composite applications |
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US12/732,396 Continuation US8573910B2 (en) | 2006-09-21 | 2010-03-26 | High performance sleeved interference fasteners for composite applications |
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US14/069,931 Abandoned US20140056664A1 (en) | 2006-09-21 | 2013-11-01 | High performance sleeved interference fasteners for composite applications |
US14/817,331 Abandoned US20160097418A1 (en) | 2006-09-21 | 2015-08-04 | High performance sleeved interference fasteners for composite applications |
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US12/732,396 Active 2027-12-05 US8573910B2 (en) | 2006-09-21 | 2010-03-26 | High performance sleeved interference fasteners for composite applications |
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- 2007-09-18 BR BRPI0703097A patent/BRPI0703097B1/en active IP Right Grant
- 2007-09-19 DE DE602007013505T patent/DE602007013505D1/en active Active
- 2007-09-19 DE DE202007019651.2U patent/DE202007019651U1/en not_active Expired - Lifetime
- 2007-09-19 DE DE202007019163U patent/DE202007019163U1/en not_active Expired - Lifetime
- 2007-09-19 EP EP07116776.1A patent/EP1903221B2/en active Active
- 2007-09-19 ES ES07116776.1T patent/ES2361197T5/en active Active
- 2007-09-19 AT AT07116776T patent/ATE503935T1/en not_active IP Right Cessation
- 2007-09-20 CA CA2603635A patent/CA2603635C/en active Active
- 2007-09-20 JP JP2007244140A patent/JP5044344B2/en active Active
- 2007-09-21 CN CN2007101624286A patent/CN101153623B/en active Active
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US9702396B2 (en) | 2014-09-17 | 2017-07-11 | Arconic Inc. | Fasteners with dual skin depth washers |
US9939004B2 (en) | 2014-09-17 | 2018-04-10 | Arconic Inc | Coated fasteners with conforming seals |
US10457414B2 (en) | 2016-12-13 | 2019-10-29 | Arconic Inc. | Reduced electromagnetic signature of conforming conical seal fastener systems |
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US7695226B2 (en) | 2010-04-13 |
DE202007019163U1 (en) | 2011-01-05 |
JP5044344B2 (en) | 2012-10-10 |
US8573910B2 (en) | 2013-11-05 |
US20080075555A1 (en) | 2008-03-27 |
AU2007216793B2 (en) | 2010-04-22 |
US20160097418A1 (en) | 2016-04-07 |
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US20100278616A1 (en) | 2010-11-04 |
JP2008075876A (en) | 2008-04-03 |
CA2603635A1 (en) | 2008-03-21 |
CN101153623A (en) | 2008-04-02 |
EP1903221A2 (en) | 2008-03-26 |
DE602007013505D1 (en) | 2011-05-12 |
MX2007011651A (en) | 2009-02-11 |
EP1903221A3 (en) | 2008-08-27 |
EP1903221B2 (en) | 2015-06-17 |
KR100915180B1 (en) | 2009-09-02 |
BRPI0703097A2 (en) | 2009-07-21 |
AU2007216793A1 (en) | 2008-04-10 |
EP1903221B1 (en) | 2011-03-30 |
JP2012189222A (en) | 2012-10-04 |
WO2008036666A2 (en) | 2008-03-27 |
KR20080027210A (en) | 2008-03-26 |
DE202007019651U1 (en) | 2014-12-02 |
WO2008036666A3 (en) | 2008-12-11 |
CA2603635C (en) | 2010-11-02 |
CN101153623B (en) | 2012-04-04 |
ES2361197T5 (en) | 2015-08-28 |
ATE503935T1 (en) | 2011-04-15 |
BRPI0703097B1 (en) | 2018-12-26 |
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Owner name: ALCOA GLOBAL FASTENERS, INC., CALIFORNIA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MARCH, MICHAEL U.;ARCINIEGA, OVIEDO;REEL/FRAME:031678/0209 Effective date: 20060922 |
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