• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a sealing nut comprising a nut and a deformable sealing ring, the nut comprising an annular body, a base comprising a chamber, a bore formed in the base, the bore comprising an annular bottom wall. having a length extending between a first inner radius and a second inner radius, the sealing ring comprising an annular body and an end face adapted to rest against the bottom wall, the end face having a length of extending between an inner radius and an outer radius. The ratio of the length of the bottom wall of the bore and the length of the end face of the ring is between 20% and 45%. The invention is applicable to assembly of aircraft structures.
    公开号:FR3042832A1
    申请号:FR1560075
    申请日:2015-10-22
    公开日:2017-04-28
    发明作者:Julien Goyer；Antoine Villet；Nicolas Naretto
    申请人:LISI Aerospace SAS；
    IPC主号:
    专利说明:

    NUT SEAL
    The present invention generally relates to sealed nuts, and more particularly to nuts having a sealing ring.
    Sealed nuts are used in the aeronautical industry to assemble structural members through which is inserted a screw or the like component including an external thread, said elements requiring a tight fluid and vapor seal.
    When assembling structural elements which work primarily in shear, tensile or a combination of the two, screws having a smooth, cylindrical or conical shaft portion having a length to completely traverse a range of thickness of the elements to be assembled. The length of the barrel makes it possible to assemble thicknesses varying between a minimum thickness ("grip min") and a maximum thickness ("grip max"), the difference being generally 1.6 mm (1/16 "of an inch in the system imperial). The thickness range is called in English terminology "grip capacity".
    The cylindrical or conical portion of the barrel of the screw used therefore exceeds the length of this range when the screw passes through elements having the minimum thickness that can assemble the screw. In contrast, the cylindrical or conical portion does not exceed when the screw passes through elements having the maximum thickness that can assemble the screw.
    Furthermore, the shear bolts generally comprise a barrel having an outside diameter greater than the maximum outside diameter of the thread.
    In order to assemble the structural elements, it is therefore necessary to use together with a shearing or pulling screw a nut 10 represented in FIG. 1 comprising a space 12 made in the bearing surface 14 intended to come into contact with a surface S of one of the elements to tighten. This space, made between the bearing surface 14 and the first thread of the nut, is conventionally called a chamber, and may have various shapes and dimensions. In the example given above, the chamber can receive up to 1.6 mm from the barrel of the screw which can protrude from the structure having a minimum thickness.
    In some cases, these nuts must also be waterproof. Such a nut is shown in FIG. 2. A deformable sealing ring 16, generally made of Teflon®, is disposed in a bore 18, made in the chamber 12. The ring 16 has an internal diameter greater than the diameter of the tapping and the diameter the barrel smooth so as not to interfere with the screw. The ring is interference mounted in the bore 18 to ensure its resistance in the nut during transport.
    The sealing ring has a conical shape which generally protrudes from the bearing surface of the nut. Thus, when the nut is tightened against a structural element, the sealing ring is both axially compressed and deformed radially towards the inside of the chamber and against the barrel and / or the threads of the screw, thus forming a tight seal.
    The Applicant has noted that in certain assembly configurations including a screw 20 and a tight nut 10 shown in FIG. 3, the ring 16 did not fully flow into the chamber 12 but flowed in part 22 between the bearing surface 14 of the nut and the surface S of the element to be tightened. This can occur when the screw is installed in a structure having a minimum thickness and the entire barrel length protruding from the structure is in the chamber.
    Such creep must be totally prevented, since it seriously compromises the mechanical strength of the screw / nut assembly. Indeed, the presence of a lubricating material between the bearing surface of the nut and the surface of the element to be clamped influences the coefficient of friction between these surfaces. When the coefficient of friction decreases, the tension of the screw increases above the allowable threshold by the screw, which can cause the rupture of the screw.
    The present invention relates to a sealing nut which prevents creep of the sealing ring between the nut and the structure, regardless of the assembly configuration, without reducing the strength, capacity or structural integrity of the assembly. or components of the assembly.
    More specifically, the sealing nut comprises a nut and a deformable sealing ring, the nut comprising an annular body extending in a direction of an axis of revolution, a base comprising a chamber and a bore formed in the base, the bore comprising an annular bottom wall having a width extending between a first inner radius and a second radius. The sealing ring comprises an annular body and an end face adapted to rest against the bottom wall, the end face having a width extending between an inner radius and an outer radius. The sealing nut is such that the ratio of the width of the bottom wall of the bore and the length of the end face of the ring is between 20 and 45%.
    Such a configuration allows the sealing ring to always be guided towards the inside of the chamber, whatever the configuration of the assembly, without flowing beyond the chamber or out of the bore.
    Furthermore, the nut according to the invention may comprise one or more of the following characteristics: the sealing nut comprises a chamfer between the bottom wall of the bore and a wall of the chamber of the nut, the chamfer makes an angle with the axis of revolution between 45 ° to 60 °, - the bottom wall and the end face have complementary shapes, - the bottom wall and the end face each comprise a portion disposed substantially perpendicularly to the axis of revolution, a wall of the bore comprises a groove extending radially inside the base, and an outer wall of the ring comprises a projection complementary in shape to that of the groove, the ring has an outer radius greater than an inner radius of the bore. the ratio between the outside radius of the ring and the inside radius of the bore is between 1.010 and 1.016; the volume of the ring compared with the available volume of the nut is between 70% and 85%; available being the smallest hollow volume inside the nut between a bearing surface and a first thread of the nut, at one end of the tapping located on the side of the base, once a screw placed in the 'nut, when the screw occupies a maximum volume. The invention will be better understood on reading the description which follows, in connection with the drawings illustrating by way of example embodiments of the invention.
    FIG. 1 (already described) is a section of a chamber nut of the prior art,
    FIG. 2 (already described) is a section of a sealing nut of the prior art,
    FIG. 3 (already described) is a partial sectional view of an assembly comprising a screw and a sealing nut of the prior art,
    FIG. 4 is a side view of a sealing nut according to one embodiment of the invention,
    FIG. 5 is an exploded section of the sealing nut of FIG. 4,
    FIG. 6 is a section of a sealing nut according to a second embodiment,
    FIG. 7 is a partial sectional view of an assembly comprising a screw and a sealing nut according to one embodiment of the invention,
    Figure 8 is a section of a sealing nut according to a third embodiment.
    A sealing nut 100, shown in FIGS. 4 and 5, comprises a nut 101 and a sealing ring 130. The nut 101 extends in the direction of an axis of revolution A of said nut and comprises a key grip 102. and a base 104. The key socket 102 is here a hexagon. The base, of enlarged outer diameter relative to the largest dimension of the hexagon, has a frustoconical upper surface 106 which has six recessed sides relative to this frustoconical surface, such as those described in patent application FR 2937386 to name of the plaintiff. Each recess is aligned with a flat surface of the hex key socket.
    FIG. 5 shows more precisely that the base 104 comprises a bearing surface 108 opposite to the frustoconical surface, and a chamber 110 having a cylindrical wall 112 and an end wall 114 connecting the cylindrical wall 112 and the first thread. In this example, the end wall 114 is a frustoconical surface.
    The tapping 116 extends on the inner surface of the nut, between the end of the end wall 114 and the upper end 118 of the nut, opposite the bearing surface 108. The base 104 comprises also a cylindrical bore 120 formed in the chamber 110, opening on the bearing surface 108, and having a first inner radius R1 greater than the radius of the chamber 110. The bore 120 comprises a cylindrical wall 122 and a bottom wall 124 plane. In this example, the bottom wall is substantially perpendicular to the axis A. It is understood by substantially that the angle may vary by a few degrees.
    A chamfer 126 connects the bottom wall 124 of the bore 120 to the cylindrical wall 112 of the chamber 110.
    The bottom wall 124 is an annular surface A1 extending between the first inner radius R1 of the cylindrical wall 122, and a second inner radius r1, defined by the distance between the axis A and the distance at which the chamfer 126 intersects. the end wall 124. The annular surface A1 has the value A1 = (R12-r12). π
    In two dimensions, the bottom wall 124 has a width L1 defined by the radius difference (R1-r1). The bore 120 is intended to receive a sealing ring 130. A chamfer 128 is formed on the perimeter opening of the bore to guide the insertion of the ring into the bore.
    The ring 130 is an annular ring of axis of revolution A, comprising an upper end face 132 intended to rest against the bottom wall 124 of the bore 120. Preferably, the upper end face comprises at least one surface of complementary shape of the bottom wall 124 of the nut. In the example illustrated in FIG. 3, the upper end surface 132 is entirely flat and substantially perpendicular to the axis A.
    The sealing ring 130 has a bore 134 whose diameter, equal to twice the inner radius r 2 indicated in FIG. 3, is greater than the diameter of the screw barrel so as not to interfere with the threads and the barrel of the screw on which the nut will be screwed. The ring can be brought into contact with the screw barrel if a larger diameter screw called "oversize" is used in a maintenance operation instead of a screw of nominal diameter, but the function of the ring it is not to brake the screw and / or to limit the impermeability of the nut.
    A lower end face 136 of the sealing ring opposite the upper end face 132 is frustoconical, the wall of the bore 134 being longer in the axial direction A than the outer wall 138 intended to come into contact with the cylindrical wall 122 of the bore.
    The outer radius R2 of the ring 130 is greater than that of the first inner radius R1 of the bore, so that the ring must be inserted into the bore. The interference created keeps the ring in the bore, especially during its transport, storage and during the installation of the nut. Preferably, the interference ratio between the outer radius R2 of the ring and the radius R1 of the bore is between 1.010 and 1.016. The larger the nominal diameter - diameter measured at the bottom of the threads - of the nut, the lower the interference ratio.
    The bearing surface 132 of the ring is also an annular surface A2, extending between the outer radius R2 and the inner radius d2, having the value A2 = (R22-r22). π
    In two dimensions, the bearing surface 132 of the ring has a width L2 defined by the radius difference (R2-r2).
    To avoid unwanted creep of the ring, the ratio between the bearing widths L1 and L2 must be greater than or equal to 20%, and less than or equal to 45%, ie: 20% <L1 / L2 <45%
    This relationship defines the contact width ratio between the upper end face 132 of the ring 130 and the bottom wall 124 of the nut 101 in a plane substantially perpendicular to the axis A.
    If the ratio of the contact width between the ring and the nut is less than 20%, the ring may rather flow during its installation in the chamber 110 into the threads of the tapping 116: the creep of the ring during its insertion into the nut is not controlled. If the material of the ring is in the threads, the coefficient of friction between the threads of the screw and the nut will decrease, the tension in the screw may rise well above the allowable limit, which may cause breaking of the screw.
    If the contact width ratio between the ring and the nut is greater than 45%, then the ring 130 is likely to flow between the bearing surface 108 of the nut and the surface of the structure when the nut 130 is installed on a screw. The risk is also to induce an uncontrolled tension in the screw, because of the decrease in the coefficient of friction between the surfaces in contact.
    Table 1 below gives examples by diameter of the relationships between the bearing widths L1 and L2 of a nut range tested by the applicant for different diameters:
    Table 1
    As previously described, a chamfer 126 connects the bottom wall 124 of the bore 120 to the cylindrical wall 112 of the chamber 110. The chamfer 126 here makes it possible to guide the material towards the chamber 110. It increases the space available in the chamber without removing too much material from the base to ensure the integrity of the base when it works in compression.
    The chamfer 126 may have different angles measured relative to the axis of revolution A according to the nominal diameter of the nut. Table 2 indicates the preferred angle of the chamfer 126 by nut diameter.
    Table 2
    In certain configurations, the chamber 110 may be completely conical: as shown in FIG. 6, the end wall 114 of the chamber and the chamfer 126 are combined in one and the same wall having a single angle. In the example of Figure 6, the angle is 60 ° with the axis of revolution A.
    The applicant has carried out several assembly tests, and simulated by two-dimensional finite elements these same assemblies, each comprising a screw whose barrel diameter is at the maximum of the tolerance, a structure having a minimum thickness, a nut of which a volume of the room is at least of the tolerance, and a ring of which all the dimensions are at the maximum of the matter.
    In the first assembly of the prior art, represented in FIG. 3, the nut is a nut of the prior art, with a contact width of between 78% and 96%. In a second assembly, shown in FIG. 7, the nut comprises a contact width of between 20% and 45%. The screws 20 are identical in the two assemblies comprising the same thicknesses of structure.
    As indicated previously, in the assembly of FIG. 3, the material of the ring 16 does not entirely flow into the chamber 12 but flows partly between the bearing surface 14 of the nut and the surface S of the element to be tightened.
    In the assembly of FIG. 7 comprising the nut of FIG. 5, no material of the ring has flowed between the nut and the structure, and there is no space between the wall of the chamber and the barrel of the screw. The seal is better, and the risk of exceeding the UTS of the screw is canceled.
    Preferably, a volume of the ring 130 constituted by the volume of the material of the ring 130, compared to the available volume of the nut 101, is in a range between 70% and 85%. The available volume considered here is the smallest hollow volume inside the nut 101 between the bearing surface 108 and the first thread of the tapping 116 once the screw is placed in the nut, when the screw occupies a volume maximum. By convention, the maximum volume of the screw in the available space is calculated as a height of the chamber 110 between the bearing surface 108 and the first thread of the tapping 116, on the side of said chamber, multiplied by a surface of a section, perpendicular to the axis of revolution A, of the smooth drum of the screw. Below 70%, the volume of the ring is too small compared to the volume of the chamber, and the nut can not be sealed. Above 85%, the ring may flow beyond the chamber to the threads or under the base and compromise the integrity of the nut during installation. The nut is preferably made of titanium alloy, and the ring is for example made of PTFE (also sold under the trade name Teflon ™, from Dupont de Nemours), in order to keep a light nut. Of course, the nut and the ring can be made in another material if the weight is not a major criterion.
    The keyhole comprises in a known manner a braking means, such as an elliptical deformation or a deformation at three points of the tapping, made on an outer surface of the nut near the upper end 118. If the nut is alloy titanium, braking will preferably be carried out according to the method described in patent FR2947597 in the name of the applicant. The invention is not limited to the single example described above. Thus, the nut may comprise a frustoconical base without recesses with respect to the frustoconical upper surface.
    The wall of the bore 120 may be conical, with an angle β between 2 ° and 5 ° and opening from the appii surface 108 to the bottom wall 124, between the wall 122 and the axis A of the nut 101, to improve the maintenance of the ring 130 in the bore, especially at low temperature (Figure 8). The ring 130 itself has the same angle β between 2 ° and 5 °, between the outer wall 138 and the axis A. Beyond an angle of 5 °, the ring can no longer be inserted into the ring. 120 tapered bore. Below 2 °, the difference in angle is not sufficient to improve the maintenance of the ring relative to a cylindrical wall. The interference ratio between an outer radius R2 of the ring and a radius R1 of the bore, said spokes being positioned at the same axial distance respectively from the bottom wall 124 and the upper end surface 132, is also between 1.010 and 1.016.
    Another surface that the chamfer 126 may be adopted to connect the end wall 124 of the bore and the cylindrical wall 112 of the chamber, such as a radiated or multi-radiated surface.
    Similarly, the bottom wall of the chamber may be conical, or may comprise from the cylindrical wall of the bore a conical portion and a portion perpendicular to the axis of revolution A. In these cases, the end face of the ring which is in contact with the bottom wall will respectively be conical, or comprise a conical portion complementary to that of the bottom wall, and a portion perpendicular to the axis of revolution. The width measurements L1 and L2 may be made in the angular direction or projected in a direction substantially perpendicular to the axis of revolution. Since the two surfaces have the same angle with respect to the axis of revolution, the ratio of the two projected widths will be equal to the ratio of the widths measured in the angular direction.
    In another variant, the bore may comprise a groove extending radially inside the wall 122 of the bore - whether the wall is cylindrical or conical - with a radius greater than the radius R 1 of the bore. The ring may comprise a projection extending radially outside the wall 138, shapes and dimensions complementary to that of the groove, that is to say, allowing the engagement of said projection in said groove. The groove / projection assembly improves the retention of the ring in the nut. In this case, the additional dimensions of the grooves and projections are not taken into account for the measurements of the lengths L1 and L2. The grooves and projections may be circular, or extend only partially around the periphery of the bore and the ring.
    权利要求:
    Claims (9)
    [1" id="c-fr-0001]
    1. A sealing nut (100) comprising a nut (101) and a deformable sealing ring (130), the nut having an annular body extending in a direction of an axis of revolution (A), an erbase ( 104) having a chamber (110) and a bore (120) formed in said base, the bore (120) comprising an annular bottom wall (124) having a width extending between a first interior radius (RI) and a second inner radius (r1), the sealing ring (130) comprising an annular body and an upper end face (132) adapted to rest against the bottom wall (124) of the bore, said end face having a width extending between an inner radius (r2) and an outer radius (R2), characterized in that the ratio of the width (L1) of the bottom wall (124) of the bore to the width ( L2) of the upper end face (132) of the ring is between 20% and 45%.
    [2" id="c-fr-0002]
    The seal nut of claim 1, wherein the nut (100) has a chamfer (126) between the bottom wall (124) of the bore and a wall of the chamber (110) of said nut.
    [3" id="c-fr-0003]
    3. Waterproof nut according to claim 2, wherein the chamfer (126) makes an angle (a) with the axis of revolution (A) between 45 ° to 60 °.
    [4" id="c-fr-0004]
    4. Sealing nut according to one of the preceding claims, such that the bottom wall (124) of the bore and the upper end face (132) of the ring have complementary shapes.
    [5" id="c-fr-0005]
    5. Sealing nut according to claim 4, such that the bottom wall (124) and the upper end face (132) each comprise a portion disposed substantially perpendicular to the axis of revolution (A).
    [6" id="c-fr-0006]
    6. Sealing nut according to one of the preceding claims, such that the ring (130) has an outer radius (R2) greater than a first inner radius (R1) of the bore.
    [7" id="c-fr-0007]
    7. Waterproof nut according to claim 7 such that a ratio between the outer radius (R2) of the ring and the first inner radius (R1) of the bore is between 1.010 and 1.016.
    [8" id="c-fr-0008]
    8. Watertight nut according to one of the preceding claims, such that a wall (122) of the bore (120) comprises a groove extending radially inside the base (104), and an outer wall (138) of the ring (130) comprises a projection complementary shape of said groove.
    [9" id="c-fr-0009]
    9. Waterproof nut according to one of the preceding claims, such that a volume of the ring (130) is between 70% and 85% of an available volume of the nut (101), said available volume being the most small hollow volume inside the nut between a bearing surface (108) and a first thread of said nut, at one end of a tapping (116) located on the side of the base (104), once a screw placed in the nut, when the screw occupies a maximum volume.
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    同族专利:
    公开号 | 公开日
    CN107061467A|2017-08-18|
    TR201817857T4|2019-01-21|
    EP3159556A1|2017-04-26|
    MA41366B1|2018-12-31|
    BR102016024661A2|2018-05-02|
    RU2706452C2|2019-11-19|
    US20170114823A1|2017-04-27|
    US10190619B2|2019-01-29|
    EP3159556B1|2018-08-29|
    RU2016141487A3|2019-09-27|
    CA2945762A1|2017-04-22|
    CN107061467B|2020-04-17|
    JP6846158B2|2021-03-24|
    JP2017083013A|2017-05-18|
    MA41366A|2017-04-26|
    FR3042832B1|2017-12-22|
    RU2016141487A|2018-04-23|
    ES2700108T3|2019-02-14|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3316952A|1966-03-14|1967-05-02|Eaton Yale & Towne|Sealing lock nut|
    US5454675A|1994-04-26|1995-10-03|Abbott-Interfast Corporation|Sealing nut and method of making same|
    EP2682615A1|2012-07-03|2014-01-08|NEDSCHROEF PLETTENBERG GmbH|Nut|
    US20140086702A1|2012-09-25|2014-03-27|Kanai Co., Ltd.|Nut|
    WO2014087108A1|2012-12-05|2014-06-12|Lisi Aerospace|Self-braking ring nut and method for producing such a nut|CN110439904A|2019-07-19|2019-11-12|苏州中新精密工业有限公司|A kind of nut and its production technology|US3399589A|1965-12-29|1968-09-03|Lamson & Sessions Co|Sealing fastener|
    DE1750702A1|1968-05-27|1971-02-18|Boellhoff & Co|Screw piece, in particular nut, with a sealing and locking ring made of thermoplastic material|
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    US5033924A|1989-12-12|1991-07-23|Vsi Corporation|Lock nut having a deformablel threaded bore|
    US5393182A|1993-10-25|1995-02-28|Microdot Inc.|Seal nut|
    US5388941A|1994-02-09|1995-02-14|Trw Inc.|Seal nut for power steering assembly|
    AU7008301A|2000-06-23|2002-01-08|Hi Shear Corp|Swage collar with internal sealing insert|
    US6966736B2|2002-03-04|2005-11-22|The Dyson Corporation|Method and structure for locking nut with deformable member|
    US6881019B2|2002-03-04|2005-04-19|The Dyson Corporation|Method and structure for locknut with substantially rigid locking member|
    DE102008015711A1|2008-02-29|2009-09-03|Profil Verbindungstechnik Gmbh & Co. Kg|Assembly component consisting of a sheet metal part and an attached nut member and method for producing such a component assembly|
    CN104121267B|2014-08-08|2017-01-18|贵州航天精工制造有限公司|Sealing self-locking nut assembly and manufacturing method|CN107461392A|2017-08-22|2017-12-12|苏州威富达精密机械制造有限公司|It is a kind of can oblique angle fix coupling nut|
    AU2018353120A1|2017-10-19|2020-05-07|Security Locknut, LLC|Fastener systems and methods|
    US10954991B2|2018-03-30|2021-03-23|The Boeing Company|Electromagnetic effect protective fastener with swageable termination body|
    CN109083918A|2018-11-07|2018-12-25|嘉兴海缙五金科技有限公司|A kind of locking nut|
    CN110131277B|2019-06-10|2021-11-09|嘉兴三喜新材料有限公司|Oil drilling platform is with fixed firm double-screw bolt|
    FR3097601B1|2019-06-24|2021-07-09|Airbus Operations Sas|Nut of a fastening system comprising a conical section|
    CN110725846A|2019-09-11|2020-01-24|河南航天精工制造有限公司|Sealing nut assembly|
    法律状态:
    2016-10-28| PLFP| Fee payment|Year of fee payment: 2 |
    2017-04-28| PLSC| Publication of the preliminary search report|Effective date: 20170428 |
    2017-10-27| PLFP| Fee payment|Year of fee payment: 3 |
    2018-10-31| PLFP| Fee payment|Year of fee payment: 4 |
    2020-10-16| ST| Notification of lapse|Effective date: 20200906 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1560075A|FR3042832B1|2015-10-22|2015-10-22|NUT SEAL|FR1560075A| FR3042832B1|2015-10-22|2015-10-22|NUT SEAL|
    CA2945762A| CA2945762A1|2015-10-22|2016-10-19|Sealed nut|
    MA41366A| MA41366B1|2015-10-22|2016-10-21|Waterproof nut|
    RU2016141487A| RU2706452C2|2015-10-22|2016-10-21|Sealing nut|
    BR102016024661-0A| BR102016024661B1|2015-10-22|2016-10-21|SEAL NUT|
    CN201610919595.XA| CN107061467B|2015-10-22|2016-10-21|Sealing nut|
    TR2018/17857T| TR201817857T4|2015-10-22|2016-10-21|Sealing Nut|
    EP16195114.0A| EP3159556B1|2015-10-22|2016-10-21|Sealed nut|
    ES16195114T| ES2700108T3|2015-10-22|2016-10-21|Watertight nut|
    JP2016206586A| JP6846158B2|2015-10-22|2016-10-21|Sealing nut|
    US15/331,854| US10190619B2|2015-10-22|2016-10-22|Sealing nut|
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