WO2024102828A1 - Système de fixation avec agencement d'étanchéité - Google Patents

Système de fixation avec agencement d'étanchéité Download PDF

Info

Publication number
WO2024102828A1
WO2024102828A1 PCT/US2023/079113 US2023079113W WO2024102828A1 WO 2024102828 A1 WO2024102828 A1 WO 2024102828A1 US 2023079113 W US2023079113 W US 2023079113W WO 2024102828 A1 WO2024102828 A1 WO 2024102828A1
Authority
WO
WIPO (PCT)
Prior art keywords
fastener
projection
head portion
bolt
clamped component
Prior art date
Application number
PCT/US2023/079113
Other languages
English (en)
Inventor
Max JUENGEL
Jeramiah SLATER
Gary Sifferman
Original Assignee
Acument Intellectual Properties, Llc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Acument Intellectual Properties, Llc filed Critical Acument Intellectual Properties, Llc
Publication of WO2024102828A1 publication Critical patent/WO2024102828A1/fr

Links

Classifications

    • 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
    • F16B29/00—Screwed connection with deformation of nut or auxiliary member while fastening
    • 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
    • F16B35/06—Specially-shaped heads
    • 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
    • F16B39/22—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening
    • F16B39/28—Locking of screws, bolts or nuts in which the locking takes place during screwing down or tightening by special members on, or shape of, the nut or bolt
    • F16B39/282—Locking by means of special shape of work-engaging surfaces, e.g. notched or toothed nuts

Definitions

  • the present invention generally relates to systems for reducing the clamp force required to effectively install bolts, such as flow bolts and fastening systems with an improved sealing arrangement.
  • Fasteners such as threaded screws and rivets may be employed to mechanically couple components at junctions.
  • a fastener exerts a compressive or clamping load on the joined components using complementary matched threads in the case of a screw, or a deformed end in the case of a rivet, with a corresponding tensile load being exerted upon the fastener.
  • the fasteners that clamp the materials together provide a clamp load or clamp force. While the clamp force needs to be significant enough to adequately secure the materials together, the clamp force should not be so great as to compromise the materials being secured.
  • Torque wrenches are often used to tighten the fasteners. Torque wrenches include a dial that provides a visual indication regarding the amount of torque being applied. Other clamp load indicating devices, such as encapsulated liquids, are sometimes used in the industry to prevent the application of too much clamp force.
  • Flow bolts are bolts which are specifically configured to provide a seal at one or more points, yet allow fluid flow either along a through hole formed through the shaft of the bolt or along a fluid flow path provided along the shaft of the bolt.
  • some flow bolts have one or more external flutes cut or otherwise formed across the threads.
  • the flow bolt can generally handle less clamp force before the threads of either the bolt or a nut member become stripped.
  • the threads on the flow bolt and/or a nut member are susceptible to becoming stripped while the fastener is being tightened in an attempt to achieve sufficient axial force to obtain a proper seal.
  • Even standard flow bolts which do not have one or more external flutes cut or otherwise formed across the threads require a reduced clamp load due to the lower cross-sectional area of the bolt.
  • FIGS. 1 A, and IB one typical application in which a flow bolt 10 is used is in connection with a brake hose 12 for a motor vehicle. More specifically, the flow bolt 10 is inserted through a bore 14 in a connector 16 at the end of the brake hose 12 such that one metal washer 20 is positioned between the head 22 of the flow bolt 10 and the connector 16 at the end of the brake hose 12, and another metal washer 24 is positioned between the connector 16 and a securing member 26, such as a nut member, on the flow bolt 10. Then, the flow bolt 10 is tightened, causing both washers 20, 24 to compress thereby forming a seal between the connector 16 and each of the washers 20, 24, as shown in FIGS. 2 A and 2B. Because the washers 20, 24 must compress during installation of the flow bolt 10, copper is typically chosen as the material for the washers. Also, because the washers effectively compress or crush during installation, the washers used in such an application are often called "crush washers.”
  • An object of an embodiment of the present invention is to provide a deformable fastening system that requires a reduced clamp load to seal the deformable fastening system than is required to seal a conventional fastening system.
  • An object of an embodiment of the present invention is to provide a system that reduces the axial force that is required to install a fastening member.
  • Another object of an embodiment of the present invention is to provide a system that controls the amount of axial force that is required to obtain a desired clamp load when a fastener, such as a washer and bolt combination, a bolt or a flow bolt is installed.
  • Another object of an embodiment of the invention is to provide a reduction in clamp force range for a given torque, thereby requiring less axial force needed to properly install the fastener.
  • Yet another object of an embodiment of the present invention is to provide a system that reduces the clamp load required to obtain a seal when a flow bolt is installed, where the reduction in the clamp load is equal to or greater than the reduction in clamp load that can be accommodated due to either one or more external flutes being provided across the threads of the bolt or simply because the bolt is a flow bolt and is provided as having a reduced cross-section.
  • Still yet another object of an embodiment of the present invention is to provide a system that reduces the crush area of a deformable member.
  • Still yet another object of an embodiment of the present invention is to provide a system that provides a deformable fastening system that includes a sealing clinch feature.
  • a deformable fastening system comprises a deformable member; and a mating member that seals with the deformable member, wherein the deformable member requires a reduced clamp load to seal with the mating member than a clamp load required to seal a non-deformable member with a conventional mating member in a conventional fastening system.
  • the deformable member comprises: a fastener including at least one step having an inner portion having a first side and a second side opposing the first side, wherein the inner portion is bounded by an inner maximum dimension and at least one first outer portion integrally formed with and protruding outwardly from the inner portion first side defining a first outer surface bounded by a first outer maximum dimension less than the inner maximum dimension
  • the first axial force applied to the fastening member to reach the required axial force is less than a second axial force applied to a conventional fastener to seal the conventional fastening system.
  • the at least one outer portion has either a rectangular side profile or a first tapered portion defining a first tapered profile and a first planar portion defining the first outer portion.
  • the deformable member is a washer having a uniform middle portion defining the inner portion.
  • the washer either has at least one rectangular step or a taper on each side of the inner portion of the washer.
  • the at least one rectangular step or taper on the washer reduces the effective contact surface area when compared to a conventional shape.
  • a conventional washer is circular, has a hole in the middle, and is flat on both the top and the bottom.
  • a washer in accordance with an embodiment of the present invention provides either a stepped or tapered configuration, wherein both the top and the bottom of the washer are either stepped or tapered, thereby providing for a reduced contact surface area which effectively translates into less axial force being needed to properly install the fastener.
  • the washer has at least one second outer portion integrally formed with the uniform middle portion that protrudes outwardly from the uniform middle portion second side defining a second outer surface bounded by a second outer maximum dimension less than the inner maximum dimension.
  • the washer at least one outer portion comprises a first rectangular side profile.
  • the washer at least one second outer portion comprises: a second rectangular side profile.
  • the washer at least one first outer portion comprises a first tapered portion defining a first tapered profile and a first planar portion defining the first outer surface.
  • the washer at least one second outer portion comprises: a second tapered portion defining a second tapered profile and a second planar portion defining the second outer surface.
  • the mating member comprises: a non-deformable fastener having at least one outer portion, wherein the non- deformable fastener at least one outer portion contacts the deformable member to deform the deformable member.
  • the non-deformable fastener is a bolt having a shaft and head, the head including an underside including at least one step defining the outer portion, wherein the at least one step mates with the deformable member to deform the deformable member and continues to deform the deformable member until the outer portion contacts the deformable member at a desired clamp load.
  • the deformable member receives the bolt and may comprise a clamped component such as a workpiece or the like.
  • the non-deformable fastener comprises a clinch fastener that seals with the deformable member, wherein the deformable member is a staking or mating material.
  • the clinch fastener comprises: a bolt having a shaft and a head, the head including an undersurface including at least one step defining the at least one outer portion, wherein the at least one step mates with the mating material to deform and clinch, and seal with the mating material.
  • the clinch fastener comprises at least one retention groove, wherein when the bolt is staked through the mating material, a portion of the deformable mating material flows into the at least one retention groove.
  • the at least one step is not deformable and mates with the deformable member. In another embodiment of the invention, the at least one step is deformable and forms a seal with the mating member.
  • the bolt can be used in a system which also comprises a nut member and a clamped component between the bolt and the nut member, where preferably, the clamped component is formed of a material that is softer than both the bolt and the nut member and that deforms to seal with the bolt and nut member when the system is clamped together.
  • An embodiment of the present invention generally relates to fluid handling circuits that require tube or hose end fittings where clamp force is applied to form a leak-proof joint.
  • Clamp force is generated by applying torque to a mechanical fastener that brings two or more parts together, forming an intimate contact.
  • One or more of the parts in the joint will be softer than the others, usually a washer or clamped component, deforming under the clamp load to promote a leak-proof seal.
  • An embodiment of the present invention integrates geometric features that promote the deformation of the softer material thus creating a more effective seal.
  • the present invention also includes an embodiment that relates to indicating and thus, helping to control the clamp force in a bolted joint. Torque is normally used to achieve the desired clamp load, but there is typically a large variation in actual clamp load due to the variation in frictional forces.
  • An embodiment of the present invention integrates geometric features into a fastener to produce a visual clamp load indicator which functions to identify when the desired clamp load is achieved.
  • the present invention also includes an embodiment that relates to providing a seal in a clinched fastener system.
  • a fastening system including a non-deformable fastener having at least one outer portion, wherein the non-deformable fastener at least one outer portion contacts the deformable member to deform the deformable member.
  • a deformable fastening system includes a deformable member and a non-deformable mating member.
  • the non-deformable mating member is a fastener including a bolt having a shaft including a thread formed thereon, and a head having an undersurface including at least one inner step formed thereon.
  • the shaft of the bolt is inserted through a passage in the deformable member to engage a corresponding thread on a nut member and the head of the bolt is rotated to move the bolt into the nut member during a tightening cycle.
  • the at least one inner step of the bolt engages a mating surface of the deformable member to clamp the deformable member when the bolt is moved into the nut member causing an increase in axial load during the tightening cycle to deform the deformable member.
  • a deformable fastening system includes a clamped component and a fastener including a bolt having a shaft having a thread formed thereon and a head having an undersurface including at least one inner step formed thereon.
  • the undersurface of the head includes at least one inner step formed thereon defines at least one outer portion of the head.
  • the shaft of the bolt is inserted through a hole in the clamped component to engage a corresponding thread on a nut member and the head of the bolt is rotated to move the bolt into the nut member during a tightening cycle.
  • the at least one inner step of the bolt engages a mating surface of the clamped component to clamp the clamped component when the bolt is moved into the nut member causing an increase in axial load during the tightening cycle to deform the clamped component.
  • the non-deformable fastener is a bolt having a shaft and head, the head including an underside including at least one step defining the at least one outer portion, wherein the at least one step mates with the deformable member to deform the deformable member and continues to deform the deformable member until the outer portion contacts the deformable member at a desired clamp load.
  • the at least one step defining the at least one outer portion of the non-deformable fastener engages a mating surface of the deformable member to clamp the deformable member when the bolt is moved, causing a significant increase in torque during the tightening cycle as compared to a conventional head having a flat, non-stepped undersurface, which indicates that a predetermined clamp load has been reached.
  • the increasing axial load causes the deformable member to deform until a desired clamp load is reached.
  • torque and angle feedback installation equipment there will be a sudden rise in torque once the undersurface engages the clamped component. This feedback will enable the installation equipment to ensure that full contact and that the required clamp load has been achieved.
  • a deformable fastening system includes a clamped component and a fastener including a bolt having a shaft portion extending along a longitudinal axis of the fastener.
  • the shaft portion includes a securing portion formed thereon. The shaft portion of the bolt is inserted through a passage in the clamped component to engage a corresponding thread on a nut member and the head portion of the bolt is rotated to move the bolt into the nut member during a tightening cycle.
  • a head portion of the fastener includes a surface having at least one engagement portion and one or more projections formed on the at least one engagement portion.
  • the one or more projections are formed on the at least one engagement portion of the surface of the head portion generally proximate the shaft portion in a substantially circular and concentric arrangement with the longitudinal axis and shaft portion.
  • the one or more projections formed on the at least one engagement portion of the surface of the head of the bolt engage a mating surface of the clamped component to clamp the clamped component when the bolt is moved into the nut member causing an increase in axial load during the tightening cycle to deform the clamped component.
  • a fastener in an embodiment of the present invention, includes a bolt having a shaft portion extending along a longitudinal axis of the fastener, wherein the shaft portion including a securing portion formed thereon.
  • a head portion of the fastener includes a surface having at least one engagement portion integrally formed on the surface.
  • the at least one engagement portion includes one or more projections formed on the surface of the head portion generally proximate the shaft portion and in arrangement with the longitudinal axis and shaft portion.
  • the one or more projections include at least one first projection extending generally circumferentially about the surface of the head portion relative to the longitudinal axis.
  • the at least one first projection is formed with at least one geometric profile as part of the surface of the head portion of the fastener to provide a sealing arrangement between the fastener and a clamped component.
  • a fastener in another embodiment, includes a bolt having a head portion and a shaft portion extending along a longitudinal axis of the fastener, the shaft portion including a securing portion formed thereon.
  • the head portion includes a surface including at least one engagement portion integrally formed on the surface.
  • the at least one engagement portion includes one or more projections formed on the surface of the head portion generally proximate the shaft portion and in arrangement with the longitudinal axis and shaft portion.
  • the one or more projections includes at least one first projection extending generally circumferentially about the surface of the head portion relative to the longitudinal axis.
  • the at least one first projection is formed with at least one geometric profile as part of the surface of the head portion of the fastener to provide a sealing arrangement between the fastener and a clamped component.
  • a second projection extends generally circumferentially about the surface of the head portion relative to the longitudinal axis.
  • the second projection is formed as a plurality of discrete members cooperatively arranged to extend circumferentially around the surface of the head portion to provide continuous plurality of lines of contact between the one or more projections and the clamped component.
  • FIGS. 1 A, IB, 2A and 2B show a prior art fastening system having a deformable fastening member installed at the end of a brake hose.
  • FIG. 1 A shows an assembly view of the pre-installed state (in partial cross-section) and wherein, FIG. IB shows an enlarged cross-sectional view of FIG. 1 A, taken along the line A-A in FIG. 1 A.
  • FIG. 2 A shows an assembly view of the post-installed state (in partial crosssection) and wherein, FIG. 2B shows an enlarged cross-sectional view of FIG. 2 A, taken along the line B-B in FIG. 2A.
  • FIG. 3 provides a top view of a deformable washer that is in accordance with a first embodiment of the present invention, wherein the deformable washer has outer portions on both the top and the bottom where the outer portions each have a rectangular side profile;
  • FIG. 4 provides a side view of the deformable washer shown in FIG. 3.
  • FIGS. 5A, 5, B, 6A, and 6B show a deformable fastening system which is in accordance with an embodiment of the present invention being installed at the end of a brake hose, wherein the fastening system includes deformable members that are stepped washers, such as is shown in FIGS. 3 and 4.
  • FIG. 5A shows an assembly view of the pre-installed state (in partial cross-section) and wherein, FIG. 5B shows an enlarged cross-sectional view of FIG. 5 A, taken along the line C-C in FIG. 5A.
  • FIG. 6A shows an assembly view of the post-installed state (in partial crosssection) and wherein, FIG. 6B shows an enlarged cross-sectional view of FIG. 6B, taken along the line D-D in FIG. 6A.
  • FIG. 7 provides a top view of a deformable washer that is in accordance with a second embodiment of the present invention, wherein the deformable washer is tapered on both the top and the bottom;
  • FIG. 8 provides a side view of the deformable washer shown in FIG. 7;
  • FIGS. 9A, 9B, 10A and 10B show a deformable fastening system which is in accordance with another embodiment of the present invention being installed at the end of a brake hose, wherein the deformable fastening system includes deformable members that are tapered washers, such as is shown in FIGS. 7 and 8.
  • FIG. 9A shows an assembly view of the pre-installed state (in partial cross-section) and wherein, FIG. 9B shows an enlarged cross-sectional view of FIG. 9A, taken along the line E-E in FIG. 9A.
  • FIG. 10A shows an assembly view of the post-installed state (in partial cross-section) and wherein, FIG. 10B shows an enlarged cross-sectional view of FIG. 10B, taken along the line F-F in FIG. 10A.
  • FIG. 11 shows a top view of a non-deformable fastener of a fastening system defined by a bolt which is in accordance with an embodiment of the present invention
  • FIG. 12 shows a side, cross-sectional view of the bolt shown in FIG. 11, taken along line G-G of FIG. 11;
  • FIG. 13 shows a bottom view of the bolt shown in FIGS. 11 and 12.
  • FIG. 14 shows the fastening system in accordance with an embodiment of the present invention in a pre-installed state
  • FIG. 15 shows the fastening system in accordance with an embodiment of the present invention in a post-installed state
  • FIGS. 16, 17 and 18 show a deformable fastening system (in side, cross-section, and bottom view) which is in accordance with another embodiment of the present invention, wherein the fastening system includes a non-deformable fastener defined by a bolt, and wherein FIG. 16 shows the pre-installed state of the system, FIG. 17 shows a cross sectional view of Section H-H of FIG. 16, and FIG. 18 shows a bottom view of FIG. 16;
  • FIG. 19 shows the post-installed state of the bolt showed in FIGS. 16- 19 installed to form a sealed deformable fastening system with a deformable member;
  • FIG. 20 shows a perspective view of a fastening system in accordance with an embodiment of the present invention
  • FIG. 21 shows a bottom plan view of a fastening system in accordance with an embodiment of the present invention.
  • FIG. 22 shows a side plan view of a fastening system in accordance with an embodiment of the present invention
  • FIG. 23 shows a sectional side plan view of a portion of a head of a fastener of a fastening system in accordance with an embodiment of the present invention
  • FIG. 24 shows a top plan view of a fastener of a fastening system positioned proximate a workpiece or component in accordance with an embodiment of the present invention
  • FIG. 25 shows a sectional side plan view of a fastening system positioned proximate a workpiece or component in accordance with an embodiment of the present invention
  • FIG. 26 shows a sectional side plan view of a portion of a head of a fastener of a fastening system positioned proximate a workpiece or component in a pre-installed state in accordance with an embodiment of the present invention
  • FIG. 27 shows a sectional side plan view of a fastening system engaging a portion of a workpiece or component in a pre-installed state in accordance with an embodiment of the present invention
  • FIG. 28 shows a sectional side plan view of a portion of a head of a fastener of a fastening system engaging a portion of a workpiece or component in a post-installed state in accordance with an embodiment of the present invention
  • FIG. 29 shows a perspective view of another aspect of the fastening system in a post-installed state in accordance with an embodiment of the present invention.
  • the deformable fastening system includes a deformable member and a mating member that seals with the deformable member.
  • FIG. 3 provides a top view of the deformable member defined by a stepped washer 30 that is in accordance with an embodiment of the present invention
  • FIG. 4 provides a side view of the same washer 30.
  • the washer 30 includes at least one outer portion 32, shown as two outer portions 32 on both the top 34 and the bottom 36 of the washer 30 (while FIGS. 3 and 4 show one step 32 on both the top 34 and the bottom 36 of the washer, only one outer portion on only one side of the washer 30 may be provided.
  • the washer 30 can be provided as having more than one outer portions on each of the top 34 and bottom 36, or even an unequal number of outer portions on each of the top 34 and the bottom 36), and a hole 38 is provided in the center 40 of the washer.
  • the washer 30 has a uniform middle portion having an outer diameter 42 (FIG. 3) defined by the largest measurement, an inner maximum dimension, across the middle portion 44 of the washer 30 and an inner minimum diameter 46 defined by the hole 38 in the middle of the washer 30.
  • the washer has sides, a first and a second side, (top 34 and bottoms 38 shown in FIG. 4) wherein the first and second sides are bounded by a respective, first and second outer axial maximum dimensions, shown as outer diameters 48, 50 defined by at least one first and second outer portions (steps 32) of the washer 30.
  • the washer 30 is symmetrical such that the outer diameter 48, 50 of each of the steps 32 (i.e., respectively on both the top 34 and the bottom 36 of the washer 30) is generally equal.
  • the outer portions 32 on the top 34 and bottom 36, respectively, of the washer 30 are preferably formed using two opposing dies that have the step(s) shape formed in them.
  • a fixed stroke machine is preferably used to compress the washer material and form the steps using the dies.
  • the steps can be formed either during normal production of the washer using specially shaped tooling (with the stepped features), or as a secondary operation using similar tooling.
  • FIGS. 5A, 5B, 6A, and 6B show a deformable fastening system 52 being used to install a flow bolt 10 on a brake hose 12 where the deformable fastening system 52 employs the stepped deformable washer 30 shown in FIGS. 3 and 4, described previously.
  • FIGS. 5A and 5B show the pre-installed state while FIGS. 6A and 6B show the post-installed state.
  • two of the stepped washers 30 are used. Therefore, in FIGS. 5A, 5B, 6A and 6B, one washer is identified with reference numeral 30a and the other is identified with reference numeral 30b, to distinguish one from the other, yet both are preferably identical to washer 30 shown in FIGS. 3 and 4.
  • a deformable stepped washer 30a (identical to the stepped washer 30 shown in FIGS. 3 and 4) is slid onto the shaft 54 of the flow bolt 10 and then the shaft 54 of the flow bolt 10 is inserted through a bore 14 provided in a connector 16 at the end of the brake hose 12. At this point, the washer 30a is disposed between a head 22 of the flow bolt 10 and the connector 16. Then, another stepped washer 30b (also preferably identical to the stepped washer 30 shown in FIGS. 3 and 4) is slid onto the shaft 54 of the flow bolt 10 and then a securing member 26, such as a nut member, is threaded or otherwise engaged with the shaft 54 of the flow bolt 10.
  • a securing member 26 such as a nut member
  • the washer 30b is disposed between the connector 16 and the securing member 26, and the overall assembly looks as shown in FIG. 5. Then, the deformable fastener system 52 is tightened such as by rotating the head 22 of the flow bolt 10 and/or securing member 26, or the securing member 26 is crimped onto the shaft 54 of the flow bolt 10. Regardless, tightening of the fastening system 52 causes the stepped washers 30a, 30b to compress or crush against the connector 16 thereby forming a seal. During installation, the top 34 and bottom 36 of each of the washers 30a, 30b (see FIG. 6) can be crushed such that the thickness of each washer after installation equals the thickness of the middle portion 44 (shown in FIG. 4 for illustrative purposes) of each washer as it existed before installation (see FIGS. 5A, and 5B), but this is not imperative.
  • the washers 30a, 30b have at least outer portion 32 (see washer 30 shown in FIGS. 3 and 4, which is identical) on both the top 34 and the bottom 36, and was effectively pre-crushed before being used in the flow bolt installation process provides that the clamp force is reduced as a result of the contact area of the sealed joint being reduced compared to the contact area of a conventional, non-stepped washer. Processing the washer 30 shown in FIGS. 3 and 4 to give it one or more outer portions on both the top 34 and the bottom 36 reduces the force required to install, for example, a flow bolt, while still maintaining the radial strength of the washer.
  • the washer 30 has a first thickness 49 before installation into the deformable fastening system that equals the sum of a middle portion thickness 43a measured longitudinally across the inform middle portion and a step thickness 45 measured longitudinally across the at least one step (or across each step where there are a plurality of steps), wherein, when installed into the deformable fastening system, the washer has a second thickness 43b (shown in FIG. 6B) equal to the middle portion thickness 43 a due to the deformation of the washer.
  • conventional washers are of a single thickness and have more crush area than necessary to seal and to ensure sufficient radial strength.
  • the washer design is matched to compensate for reduced thread strength in that the crush area is reduced approximately by the amount of thread strength reduction.
  • the thread strength may be compromised in that the thread on either the flow bolt 10 or the nut member 26 may be susceptible to stripping if the flow bolt includes one or more external flutes 28 across the threads in order to provide a fluid flow path, such as is shown in FIGS. 5 and 6.
  • stepped washers 30a, 30b see FIGS. 3 and 4 which shows washer 30 which is identical
  • FIGS. 3 and 4 which shows washer 30 which is identical
  • FIG. 7 provides a top view of a deformable member defined by a tapered washer 60 that is in accordance with another embodiment of the present invention
  • FIG. 8 provides a side view of the same washer 60.
  • the washer 60 includes at least one outer portion having at least one taper 62 and at least one uniform middle portion 72 having an inner maximum dimension 71.
  • the top 64 first planer surface and bottom 66 second planer surface each respectively define a first outer maximum dimension 65, and a second outer maximum dimension 67 that is smaller than the first inner maximum dimension 71 of the uniform middle portion 72 of the washer 60.
  • the washer 60 is symmetrical such that each of the tapers 62 (i.e., on both the top 64 and the bottom 66 of the washer) are generally the same with regard to height and slope.
  • the washer 60 (shown in FIG. 8 has a first thickness 79 before installation into the deformable fastening system that equals the sum of a middle portion thickness 73a measured longitudinally across the inform middle portion and a step thickness 75 measured longitudinally across the at least one step (or across each step where there are a plurality of steps), wherein, when installed into the deformable fastening system, the washer has a second thickness 73b (shown in FIG. 10B) equal to the middle portion thickness 73 a due to the deformation of the washer.
  • the tapers 62 on the washer 60 are preferably formed using two opposing dies that are specifically shaped to form the tapers.
  • a fixed stroke machine is preferably used to compress the washer material and form the tapers 62 using the dies.
  • the tapers 62 can be formed either during normal production of the washer using specially shaped tooling (with the taper features), or as a secondary operation using similar tooling.
  • FIGS. 9A, 9B, 10A, and 10B show a fastening system 70 being used to install a flow bolt 10 on a brake hose 12.
  • the fastening system employs the tapered washer 60 shown in FIGS. 7 and 8, described previously.
  • FIG. 9A and 9B show the pre-installed state while FIGS. 10A and 10B show the post-installed state.
  • two of the tapered washers 60 are used. Therefore, in FIGS. 12 and 13, one washer is identified with reference numeral 60a and the other is identified with reference numeral 60b, to distinguish one from the other. Therefore, in FIGS. 9A, 9B, 10A and 10B, one washer is identified with reference numeral 60a and the other is identified with reference numeral 60b to distinguish one from the other, yet both are preferably identical to washer 60 shown in FIGS. 7 and 8.
  • a tapered washer 60a (identical to the tapered washer 60 shown in FIGS. 7 and 8) is slid onto the shaft 54 of the flow bolt 10 and then the shaft 54 of the flow bolt 10 is inserted through a bore 14 provided in a connector 16 at the end of the brake hose 12. At this point, the washer 60a is disposed between a head 22 of the flow bolt 10 and the connector 16. Then, another tapered washer 60b (also preferably identical to the tapered washer 60 shown in FIGS. 7 and 8) is slid onto the shaft 54 of the flow bolt 10. Then, a securing member 26, such as a nut member, is threaded or otherwise engaged with the shaft 54 of the flow bolt 10.
  • the washer 60b is disposed between the connector 16 and the securing member 26, and the overall assembly looks as shown in FIGS. 9 A and 9B.
  • the fastener system 70 is tightened such as by rotating the head 22 of the flow bolt 10 and/or securing member 26, or the securing member 26 is crimped onto the shaft 54 of the flow bolt 10. Regardless, tightening of the fastener system 70 causes the tapered washers 60a, 60b to compress or crush against the connector 16, thereby forming a seal as shown in FIGS. 10A and 10B.
  • the top 64 and bottom 66 of the washer 60 can be crushed such that the thickness of the washer 60 after installation substantially equals the thickness of the middle portion 72 (shown in FIG. 8) of the washer 60 as it existed before installation (see FIGS. 9A and 9B), but this is not imperative.
  • the washers 60a, 60b have at least one taper 62 (see washer 60 shown in FIGS. 7 and 8, which is identical), and was effectively precrushed before being used in the flow bolt installation process provides that the clamp force is reduced as a result of the contact area of the washer forming the sealed joint being reduced compared to that of the contact area of a conventional, non-tapered washer.
  • the fact that the washers 60a, 60b have at least one taper 62 on the top 64 and bottom 66 reduces the force required to install the washer to seal with the flow bolt 10 and to the connector assembly 16, for example, a flow bolt 10, while still maintaining the radial strength of the washers 60a, 60b.
  • the washer design is matched to compensate for reduced thread strength in that the crush area is reduced approximately by the amount of thread strength reduction.
  • the thread strength may be compromised in that the thread of either the bolt or the nut member may be susceptible to stripping if the flow bolt 10 includes one or more external flutes 28 (shown in FIGS. 9 A, 9B, 10 A, 10B) across the threads in order to provide a fluid flow path.
  • Using tapered washers 60a, 60b (see FIGS. 7 and 8 which shows washer 60 which is identical) compared to conventional washers provides that less axial force is required to crush and seal the washer to the flow bolt 10 and to both the connector assembly 16 and the securing member 26 due to the smaller crush area.
  • the stepped and tapered washers as shown in FIGS. 3-4 and 7-8, respectively, can be used to install standard, non-flow bolts as well as flow bolts, and specifically flow bolts having one or more external flutes running across the threads. Regardless, using the non-conventional washers disclosed herein provides for a reduced crush area which results in less clamp force being required for proper installation. Even standard flow bolts which do not have one or more external flutes cut or otherwise formed across the threads would benefit from a reduced clamp load due to the lower cross-sectional area of the bolt.
  • the increasing axial load causes the deformable fastening member (i.e., the stepped or tapered washers, as described above) to deform until a desired clamp load is reached.
  • the outer portions cause the contact area to be less than the contact area of a conventional non-deformable or non-stepped washer. Even though less material is in contact, the washer material that is loaded deforms more to better seal any voids in the joint. This seals the joint with a lower axial force (torque) than when a standard crush washer is used.
  • FIGS. 11, 12, and 13 provide a top view, side cross-sectional view, and bottom view, respectively, of a non-deformable fastener defined by a bolt 100 which is in accordance with an embodiment of the present invention.
  • the bolt 100 includes a head 102 (see FIGS. 11 and 12) and a shaft 104 (see FIGS. 12 and 13) having a thread 106 formed thereon.
  • Both the head 102 and the shaft 104 may be conventional except for the undersurface 108 under the head 102, which is provided as having at least one inner step or engagement portion 110 formed on a portion of the undersurface 108 of the head 102 of the bolt 100, wherein the at least one inner step 110 defines the at least one outer portion of the deformable fastening system.
  • the undersurface 108 may have at least one geometric feature formed thereon that may be a “torque robbing feature” such as adding texture or ribs to the undersurface 108 that provides high friction to the undersurface 108 when contacting a mating surface of a deformable member, such as a clamped component 124.
  • a clamped component 124 may be formed of various materials, including, but not limited to, polymers, metals, and the like. It is contemplated that a layer of material, such as paint, a coating, or the like, may be applied to the clamped component 124.
  • the layer of material may cooperate with the clamped component to provide additional features such as a decorative appearance, material protection or other physical function or aesthetic appearance.
  • the texture may be any geometry that transforms the undersurface 108 into a high friction surface.
  • One such feature preferably may be at least one geometric feature integrally formed on to the metal bolt 100 such as texture or ribs added to the undersurface 108 that makes the undersurface 108 a high friction surface and allows the required clamp load to be reached faster with less torque applied to seal the deformable fastening system.
  • FIGS. 14 and 15 provide cross-sectional views of a fastening system 120 that is in accordance with an embodiment of the present invention.
  • the fastening system 120 employs the bolt 100 shown in FIGS. 11-13, described previously, as well as a nut member 122 and a clamped component 124, such as a workpiece or the like, which is disposed between the nut member 122 and the undersurface 108 of the head 102 of the bolt 100.
  • the clamped component 124 is made of a softer material such as a metal, polymer, or composite, than both the metal bolt 100 and the nut member 122.
  • a deformable washer (not shown) may be utilized if the clamped component 124 is not deformable.
  • the bolt 100 is a non- deformable fastener and the clamped component is the deformable member.
  • the at least one step or engagement portion 110 may be a softer material than a mating surface and may deform to seal against the mating surface.
  • the at least one step is the deformable member, and the mating surface is the mating member.
  • each of the least one step 110 formed in the undersurface of the head 102 of the fastener 100 and the clamped component 124 are deformable when the at least one step 102 mates with the clamped component 124.
  • FIG. 14 shows the fastening system 120 before the bolt 100 is installed
  • FIG. 15 shows the fastening system 120 after the bolt 100 is installed.
  • initially the shaft 104 of the bolt 100 is inserted through a hole or passage 126 in the clamped component 124, and the thread 106 on the shaft 104 is engaged with a corresponding thread 128 in the nut member 122, causing the clamped component 124 or workpiece to be effectively captured between the head 102 of the bolt 100 and the nut member 122.
  • the bolt 100 is rotated using the head 102, in order for the bolt 100 to move more fully into the nut member 122 and clamp down on the clamped component 124.
  • the nut member 122 is rotated along the thread 106 of the shaft 104 of the bolt 100 to move the nut member 122 toward the head 102 of the bolt 100 and capture the clamped component 124 therebetween.
  • Providing one or more outer portions of the at least one inner step or engagement portion 110 under the head 102 causes a significant increase in torque during the tightening cycle as compared to a conventional head having a flat, nonstepped undersurface, which indicates that a predetermined clamp load has been reached.
  • the increasing axial load causes the clamped material (i.e., clamped component 124) to deform until a desired clamp load is reached.
  • the area of the outer portion 110 is calculated so that the required clamp load is reached once the undersurface 108 (i.e., the surface indicated with reference numeral 108 in FIG. 14) in the bolt 100 contacts the clamped component 124.
  • the undersurface 108 i.e., the surface indicated with reference numeral 108 in FIG. 14
  • the clamped component 124 verification of sufficient clamp load is visual.
  • torque & angle feedback installation equipment there will be a sudden rise in torque once the undersurface (i.e., the surface indicated with reference numeral 108 in FIG. 14) engages the clamped component 124. This feedback will enable the installation equipment to ensure that full contact and that the required clamp load has been achieved.
  • a non-deformable fastener comprises: a clinch fastener that seals with and clinches to the deformable member.
  • the deformable fastening system is in accordance with another embodiment of the present invention, wherein the deformable fastening system 220 (shown in FIG. 19) includes a non-deformable fastener defined by a bolt 200 having a clinch feature.
  • FIG. 16 shows the pre-installed state of the system;
  • FIG. 17 shows a cross sectional view of Section H-H of FIG. 16,
  • FIG. 18 shows a bottom view of FIG. 16, and
  • FIG. 19 shows the post-installed state of the system, wherein the deformable member is a staking or mating material 222.
  • the bolt 200 similar to the bolt 100 in FIGS.
  • 11-15 includes a head 202 (see FIGS. 16 and 19) and a shaft 204 (see FIGS. 16, 18, and 19). Both the head 202 and the shaft 204 may be conventional except for the undersurface 208 under the head 200, which is provided as having at least one inner step 210 thereon (shown in detail in FIG. 17), wherein the undersurface 208 and the at least one inner step 210 have similar features to the corresponding undersurface 108 and at least one inner step 210 associated with bolt 100.
  • additional features may be added such as ribs 232 to provide resistance to axial rotation.
  • the bolt 200 has a clinch feature, shown as retaining groove 230 that allows for flow and retention of retained material 222 (shown in FIG. 19) during a staking operation.
  • the retained staking material 222 is softer than the bolt material.
  • the at least one step 210 defining at least one outer portion mates with the staking material and acts as sealing feature and may include more than one step to further seal with the staked material 222.
  • FIG. 16 shows the fastening system 220 before the bolt 200 is installed
  • FIG. 19 shows the fastening system 220 after the bolt 200 is installed into staking material 222.
  • a programmable drive system can be utilized, preferably a drive system capable of performing a torque angle tightening strategy.
  • the bolt clamped component configuration disclosed herein provides for a reduced crush area that effectively translates into less axial force being needed to properly install the bolt.
  • additional sealing features are provided.
  • the fastening system 150 includes a fastener or bolt 100 having a head portion 102 defining a flanged portion 101 and an external drive profile 103.
  • the fastener 100 may be fabricated from one or more of the following materials: titanium, titanium alloys; nickel-chrome alloys, stainless steel, mild steel, cast iron, aluminum, aluminum alloys, etc., without limitation.
  • the external drive profile 103 of the head 102 includes a plurality of drive surfaces or drive walls 105 configured in a hexagonal or “hex” profile. It is understood that the drive surfaces or drive walls of the external drive profile of the head 102 may be formed with various other geometric shapes or profiles, including, for exemplary purposes, an internal hex profile, an internal multilobular profile, or an external multi-lobular profile.
  • the fastener 100 further defines a shaft portion 104 having a threaded or securing portion 106 formed thereon for mechanically coupling the fastener to a workpiece, clamped component, or the like.
  • the shaft portion 104 extends along and defines a longitudinal axis 107 of the fastener 100. As shown in the Figures, the diameter of the shaft portion 104 is smaller than the diameter of the flanged portion 101 of the head portion 102.
  • the flanged portion 101 of the head portion 102 projects generally radially outwardly from the longitudinal axis 107 and shaft portion 104.
  • the flanged portion 101 may have a generally circular shape orthogonal to the longitudinal axis 107, or, alternatively, a square shape, a hexagonal shape, or another shape depending upon the needs of the specific application.
  • the head portion 102 generally defines a surface 108 incorporating at least one inner step or engagement portion 110.
  • the at least one engagement portion 110 may include one or more projections 112, 114.
  • the one or more projections 112 may be formed on the surface 108 of the head portion 102 generally proximate the shaft portion 104 of the fastener 100 in a substantially circular and concentric arrangement with the longitudinal axis 107 and shaft 104 of the fastener 100. It is understood that other geometric configurations, including, without limitation, an ellipse, or the like, may be utilized with the one or more projections 112, 114. It is understood that the one or more projections 112, 114 of the at least one engagement portion 110 may be formed as one or more unitary rings extending circumferentially around the surface 108 of the head portion 102.
  • the at least one engagement portion 110 of the head portion 102 of the fastener 100 may include at least one first projection 112 extending generally circumferentially about the surface 108 of the head portion 102 relative to the longitudinal axis 107. It is also contemplated that the at least one first projection 112 may be formed as a sealing ring. In some embodiments, the at least one first projection 112 is integrally formed on the surface 108 of the head portion 102 of the fastener 100. The at least one first projection 112 may be provided on the at least one engagement portion 110 of the fastener 100 to provide a sealing arrangement when the fastener 100 is secured to the clamped component 124.
  • the at least one first projection 112 may be formed with a geometric profile, including without limitation, a multiple arcuate shaped profile or a plurality of progressively reduced diameter profiles or the like, as part of the surface 108 of the head portion 102 of the fastener 100.
  • the geometric profile of the at least one first projection 112 may include multiple cooperating profiles, such as redundant multiple arcuate shaped surfaces to engage and deform a workpiece or clamped component 124 at various depths to provide a sealing arrangement between the fastener 100 and clamped component 124, whereby the sealing ring 112 provides continuous plurality of lines of contact between the sealing ring 112 and a mating surface of the clamped component 124 and protects areas of the clamped component 124 exposed by one or more of the projections 112, 114 from corrosion. [00117] In some embodiments shown in FIGS.
  • the at least one first projection 112 may be formed with multiple geometrically shaped engagement surfaces 116, 118 to engage a workpiece or clamped component at various depths to provide a sealing arrangement between the fastener 100 and clamped component 124.
  • the at least one first projection 112 may include two or more projections, wherein the two or more projections are disposed adjacent to and in a cooperating arrangement to form two or more sealing rings.
  • the multiple engagement surfaces 116, 118 may include at least two engagement surfaces formed with a variety of geometric profiles, including, but not limited to, a generally arcuate shaped profile, a progressively reduced diameter profile or the like.
  • the engagement surface 116 of the at least one first projection 112 may be positioned a further distance from the longitudinal axis 107 relative to the engagement surface 118.
  • the engagement surface 116 may be positioned at an increased height or further distance from the surface 108 of the head portion 102 relative to the height of engagement surface 118 to form offset positions for the engagement surfaces 116 and 118 to provide distinct engagement depths and enhanced sealing features when the at least one first projection 112 is connected to the workpiece or clamped component 124.
  • the engagement surface 118 of the at least one first projection 112 may be positioned a further distance from the longitudinal axis 107 relative to the engagement surface 116. In some embodiments, the engagement surface 118 may be positioned at an increased height or further distance from the surface 108 of the head portion 102 relative to the height of the engagement surface 116 to form offset positions for the engagement surfaces 116 and 118 to provide distinct engagement depths and enhanced sealing features when the at least one first projection 112 is connected to the workpiece or clamped component 124.
  • the increased depth and offset position of the engagement surface 116 relative to the engagement surface 118, or the increased depth and offset position of the engagement surface 118 relative to the engagement surface 116 results in the engagement surface with an increased height or further distance from the surface 108 of the head portion 102 engaging the workpiece or clamped component 124 to provide a first sealing arrangement.
  • the engagement surfaces with increased depth and offset position shown as engagement surface 116 in the Figures, assists in protecting the engagement surface 118 with a reduced height relative to engagement surface 116 from damage during material and part handling prior to and during engagement of the fastener 100 to a clamped component 124.
  • the engagement surface shown as engagement surface 118 in the Figures, may be formed with a reduced height relative to engagement surface 116 to provide a second sealing arrangement.
  • the at least one engagement surface 110 of the fastener 100 may include three or more engagement surfaces or rings, wherein two or more engagement surfaces 116 may be formed with an increased height or positioned a further distance from the surface 108 of the head portion 102 relative to the height or position of the engagement surface 118 to protect the engagement surface 118 from damage during part handling, thereby ensuring the engagement surface 118 provides a sealing arrangement of the fastener 100 on the clamped component 124.
  • the one or more projections of the at least one engagement portion 110 of the head portion 102 of the fastener 100 includes a second projection 114 extending generally circumferentially about the surface 108 of the head portion 102 relative to the longitudinal axis 107. It is understood that the at least one engagement portion 110 may be formed with the second projection 114 extending generally circumferentially about the surface 108 of the head portion 102 relative to the longitudinal axis 107. The second projection 114 may be formed radially inward of the at least one first projection 112 relative to the longitudinal axis 107. It is also understood that the second projection 114 may be formed radially outward of the at least one first projection 112 relative to the longitudinal axis 107. It is also contemplated that the at least one engagement portion 110 of the fastener 100 may include only the at least one projection 112 on the at least one engagement portion 110 of the surface 108 of the fastener 100.
  • the second projection 114 may be formed with a geometric profile, including without limitation, a generally arcuate shaped profile, as part of the surface 108 of the head portion 102 of the fastener 100. It is understood that various geometric profiles, such as a progressively reduced diameter profile or the like, may be utilized to form the second projection 114 on the surface 108 of the head portion 102.
  • the second projection 114 extending from the surface 108 of the head portion 102 may be formed as a grounding ring.
  • the grounding ring 114 provides continuous plurality of lines of contact between the grounding ring 114 and a mating surface of the clamped component 124.
  • the grounding ring 114 is provided on the at least one engagement portion 110 of the fastener 100 to engage and penetrate a coating, such as paint or the like, applied to the engagement surface 126 of the clamped component 124.
  • the cooperation between the second projection as a grounding ring 114 and the at least one first projection as a sealing ring 112 allows the grounding ring 114 to be sealed from any outside corrosive elements and maintain connectivity while also trapping debris generated during the installation of the fastener 100 to the clamped component 124 where the grounding ring 114 penetrates and displace a coating and material of the clamped component 124.
  • use of the second projection 114 and the at least one first projection 112 of the at least one engagement portion 110 of the head portion 102 of the fastener 100 may significantly reduce or lower the torque requirements for sealing the fastener 100 a clamped component 124 relative to a standard fastener, reduce damage to the clamped component 124 or coatings applied thereto resulting from the engagement of the fastener 100 of the fastening system 150 relative to a standard fastener, and reduce or eliminate the use of chemical sealants or sealing washers in the fastening process.
  • various geometric profiles may be utilized to form the second projection 114 on the surface of the head portion 102.
  • a second projection 114 may be formed with multiple engagement surfaces, including, but not limited to one or more ramps or waveform shaped surfaces of varying heights as described above with the multiple engagement surfaces 116, 118 of the at least one first projection 112 to accomplish the objectives of the present invention, wherein the second projection 114 includes multiple engagement surfaces to reduce the torque required to deform and engage the engagement surface 126 of the clamped component 124 to provide a grounding arrangement for the fastener 100 around the second projection 114. It is also contemplated that the at least one second projection 114 may be formed as a sealing ring.
  • the second projection 114 may include two or more projections, wherein the two or more projections are disposed adjacent to and in a cooperating arrangement to form two or more sealing rings.
  • the one or more projections 112, 114 may be formed as a plurality of discrete members or projections cooperatively arranged to extend circumferentially around the surface 108 of the head portion 102 to provide a continuous plurality of lines of contact between the one or more projections 112, 114 and a mating surface of a workpiece or clamped component 124 as shown in FIGS. 24, 27 and 28.
  • the second projection 114 is formed as a grounding ring having a plurality of arcuate shaped discrete members or projections 117, wherein the plurality of discrete members or projections 117 extend generally circumferentially about the surface 108 of the head portion 102 relative to the longitudinal axis 107.
  • the plurality of discrete members or projections provide continuous plurality of lines of contact between the projections and a mating surface of the clamped component. It is understood that the quantity, position and geometric profile of the discrete members or projections 117 may be varied based upon the application associated with the fastener 100.
  • FIGS. 25 and 26 illustrate the fastening system 150, wherein the fastener 100 is shown prior to engagement with the workpiece 124.
  • FIG. 25 is a cross- sectional view of the fastening system 150, wherein the shaft portion 104 of the fastener 100 extends at least partially through an aperture 130 in a workpiece or clamped component 124 to position the surface 108 of the head portion 102 adjacent a receiving portion 126 of the clamped component 124.
  • the one or more projections 112, 114 of the at least one engagement portion 110 extending from the surface 108 of the head portion 102 are placed proximate the receiving surface 126 of the clamped component 124.
  • the second projection 114 is disposed on the surface 108 of the head portion 102 of the fastener 100 proximate the shaft portion 104, while the at least one first projection 112 is disposed radially outward of the second projection 114 on the surface 108 of the head portion 102. It is also contemplated that the at least one engagement portion 110 of the head portion 102 of the fastener 100 may be formed with only one of the at least one first projection 112 or the second projection 114 on the surface 108 of the head portion 102.
  • FIGS. 27 and 28 illustrate the fastening system 150 wherein the fastener 100 engages the workpiece or component 124.
  • the one or more projections 112, 114 of the at least one engagement portion 110 extending from the surface 108 of the head portion 102 engage and deform the receiving portion 126 of the clamped component 124 to create a sealing arrangement between the head portion 102 of the fastener 100 and the clamped component 100.
  • the cooperation between the second projection as a grounding ring 114 and the at least one first projection as a sealing ring 112 allows the grounding ring 114 to be sealed from any outside corrosive elements and maintain connectivity while also trapping debris generated during the installation of the fastener 100 to the clamped component 124 where the grounding ring 114 penetrates the coating.
  • first projection 112 and at least one second projection 114 of the at least one engagement portion 110 of the head portion 102 of the fastener 100 may significantly reduce or lower the torque requirements for sealing the fastener 100 a clamped component 124 relative to a standard fastener, reduce damage to the clamped component 124 or coatings applied thereto resulting from the engagement of the fastener 100 of the fastening system 150 relative to a standard fastener, and reduce or eliminate the use of chemical sealants or sealing washers in the fastening process.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Bolts, Nuts, And Washers (AREA)

Abstract

Un système de fixation déformable comprend un composant serré et un élément de fixation comprenant un boulon ayant une partie tige s'étendant le long d'un axe longitudinal de l'élément de fixation et une partie tête ayant une surface comprenant au moins une partie d'engagement et une ou plusieurs saillies formées sur la ou les parties d'engagement. La ou les saillies sont formées sur la ou les parties d'engagement généralement à proximité de la partie arbre. La ou les saillies formées sur la ou les parties d'engagement s'engagent avec une surface d'accouplement du composant serré pour serrer le composant serré lorsque le boulon est déplacé dans un élément écrou provoquant une augmentation de la charge axiale pendant le cycle de serrage pour déformer le composant serré.
PCT/US2023/079113 2022-11-09 2023-11-08 Système de fixation avec agencement d'étanchéité WO2024102828A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US202263423987P 2022-11-09 2022-11-09
US63/423,987 2022-11-09
US202318311591A 2023-05-03 2023-05-03
US18/311,591 2023-05-03

Publications (1)

Publication Number Publication Date
WO2024102828A1 true WO2024102828A1 (fr) 2024-05-16

Family

ID=91033570

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2023/079113 WO2024102828A1 (fr) 2022-11-09 2023-11-08 Système de fixation avec agencement d'étanchéité

Country Status (1)

Country Link
WO (1) WO2024102828A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030039527A1 (en) * 2000-01-18 2003-02-27 Volker Schatz Connecting element in the form of a screw, nut or washer for a screw connection, and method for the tightening thereof
US7258517B2 (en) * 2001-08-22 2007-08-21 Textron Verbindungstechnik Gmbh & Co. Ohg Self-punching fastener with radially positioned projections and an annular depression
US20140079510A1 (en) * 2011-04-05 2014-03-20 Iwata Bolt Kabushiki Kaisha Earth bolt
CN105201987A (zh) * 2015-11-11 2015-12-30 重庆青山工业有限责任公司 一种用于变速器上的防松密封螺栓结构
US20200217350A1 (en) * 2019-01-08 2020-07-09 Acument Intellectual Properties, Llc Clinch fastener

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030039527A1 (en) * 2000-01-18 2003-02-27 Volker Schatz Connecting element in the form of a screw, nut or washer for a screw connection, and method for the tightening thereof
US7258517B2 (en) * 2001-08-22 2007-08-21 Textron Verbindungstechnik Gmbh & Co. Ohg Self-punching fastener with radially positioned projections and an annular depression
US20140079510A1 (en) * 2011-04-05 2014-03-20 Iwata Bolt Kabushiki Kaisha Earth bolt
CN105201987A (zh) * 2015-11-11 2015-12-30 重庆青山工业有限责任公司 一种用于变速器上的防松密封螺栓结构
US20200217350A1 (en) * 2019-01-08 2020-07-09 Acument Intellectual Properties, Llc Clinch fastener

Similar Documents

Publication Publication Date Title
US9322424B2 (en) Nut with lug flare
US11168721B2 (en) Tapered lead-in for interference fit fasteners
EP1532373B1 (fr) Element d'attache femelle auto-fixant et procede d'installation associe
EP0540030B1 (fr) Vis de mise à la terre
US5743691A (en) Clinch-type fastener member
JPS6240564B2 (fr)
US20060204348A1 (en) Self-attaching fastener and fastener and panel assembly
CA2519654A1 (fr) Element d'assemblage resistant au couple
EP2787221B1 (fr) Écrou de perçage pour tôle d'acier à haute résistance
US10641307B2 (en) Radiused lead-in for interference fit fasteners
WO2024102828A1 (fr) Système de fixation avec agencement d'étanchéité
US7296957B2 (en) Methods and apparatus for coupling gas turbine engine components
US20200040935A1 (en) Low axial force sealing system
EP2238359B1 (fr) Élément de fixation de verrouillage
US12025170B2 (en) Apparatus for a burst-through torque indicator

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 23889656

Country of ref document: EP

Kind code of ref document: A1