JP4072832B1 - Locking nut - Google Patents

Locking nut Download PDF

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JP4072832B1
JP4072832B1 JP2007155705A JP2007155705A JP4072832B1 JP 4072832 B1 JP4072832 B1 JP 4072832B1 JP 2007155705 A JP2007155705 A JP 2007155705A JP 2007155705 A JP2007155705 A JP 2007155705A JP 4072832 B1 JP4072832 B1 JP 4072832B1
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washer
nut
bolt
cylindrical portion
screw
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JP2008309202A (en
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宣彦 二川
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宣彦 二川
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Priority to PCT/JP2008/060298 priority patent/WO2008152963A1/en
Priority to TW97121747A priority patent/TW200916667A/en
Publication of JP2008309202A publication Critical patent/JP2008309202A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • 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
    • F16B39/36—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 with conical locking parts, which may be split, including use of separate rings co-operating therewith
    • 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
    • F16B37/00—Nuts or like thread-engaging members
    • F16B37/005—Nuts or like thread-engaging members into which threads are cut during screwing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B39/00—Locking of screws, bolts or nuts
    • F16B39/02—Locking of screws, bolts or nuts in which the locking takes place after screwing down
    • F16B39/12—Locking of screws, bolts or nuts in which the locking takes place after screwing down by means of locknuts
    • F16B39/16—Locking of screws, bolts or nuts in which the locking takes place after screwing down by means of locknuts in which the screw-thread of the locknut differs from that of the nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • 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
    • F16B39/284—Locking by means of elastic deformation
    • F16B39/286—Locking by means of elastic deformation caused by saw cuts

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

Abstract

【課題】 この発明は、ボルトとナットとのゆるみ止めをより確実且強固に達成することが出来、しかも大量生産に適した構造のゆるみ止めナットを提供せんとするものである。
【解決手段】 ボルトに螺合して締結されるナットと、このナットと該ボルトとの間に介在されるワッシャとを備え、ワッシャは前記ボルトを挿入する筒状の挿入部を有し、且、軸方向に一端から他端まで伸びるスリットが形成されており、ナットとワッシャとを台頭円錐形の斜面を介して当接させ、締結時に台頭円錐形のテーパー面との当接によるナットの締め付けによって、ワッシャを縮径させ、ワッシャをボルトに圧着させて、ナットのゆるみ止めを果たすようにしたことを特徴とするゆるみ止めナット。
【選択図】図１PROBLEM TO BE SOLVED: To provide a locking nut having a structure capable of more reliably and firmly achieving locking between a bolt and a nut and suitable for mass production.
SOLUTION: A nut screwed to a bolt and a washer, and a washer interposed between the nut and the bolt, the washer has a cylindrical insertion portion for inserting the bolt, and A slit that extends from one end to the other in the axial direction is formed, and the nut and washer are brought into contact with each other via a truncated conical slope, and the nut is tightened by contact with the tapered surface of the truncated cone during fastening The lock nut is characterized in that the diameter of the washer is reduced and the washer is crimped to the bolt to prevent the nut from loosening.
[Selection] Figure 1

Description

この発明は、ボルトに螺合して物体を締結するナットに関し、より詳細には、ネジのゆるみを防止し得るようにしたゆるみ止めナットに関する。   The present invention relates to a nut that is screwed into a bolt to fasten an object, and more particularly to a locking nut that can prevent the screw from loosening.

従来、雄ネジを有するボルトと、該ボルトに螺合する雌ネジを有するナットで、物体を締め付けて固定する固定手段は公知であり、多様な用途、分野において広く利用されている。ボルトとナットは、雄ネジと雌ネジの螺合により締め付けが行なわれるが、ボルトやナットに付加される振動、回転、衝撃等によって、締め付けがゆるんで来るおそれがあった。ネジのゆるみは、物体の固定状態を不安定にし、ときとして重大な事故を招来するおそれがある。そこで、ネジのゆるみを防止するために従来種々の方法、構造が提案されてきている。   Conventionally, fixing means for tightening and fixing an object with a bolt having a male screw and a nut having a female screw screwed to the bolt are known and widely used in various applications and fields. The bolt and the nut are tightened by screwing the male screw and the female screw, but the tightening may be loosened by vibration, rotation, impact, or the like applied to the bolt or nut. Loose screws can destabilize the object and can cause serious accidents. Therefore, various methods and structures have been proposed in the past in order to prevent the screws from loosening.

ネジは、締め付け部からの応力により、ボルトとナットが互いに軸方向反対方向に変位させられてネジ溝が消失し、雄ネジと雌ネジのネジ山が軸方向において当接して締付力の保持と固定状態の維持が図れるようになっている。ネジのゆるみ止めは、通常、雄ネジと雌ネジの軸方向へのもどりを防止する手段、例えばロックナット、バネ座金などにより、ネジのもどりを防止している。しかしながら、かかる従来のロックナットやバネ座金の如きネジのもどり防止手段では、雄ネジと雌ネジは軸方向に片寄せられてネジ山を密着させた状態を、もどり防止手段で維持するようにしたにすぎず、密着側と反対の側では、雄ネジと雌ネジの間隔は大きくなっており、ネジ溝が消失しているわけではないため、衝撃や振動を受けて密着した状態が容易に解消されるおそれがあり、ネジのゆるみを十分には防止することが出来なかった。   The bolts and nuts are displaced in the axial direction opposite to each other due to the stress from the tightening part, and the screw grooves disappear, and the thread of the male and female threads abut in the axial direction to maintain the tightening force. And the fixed state can be maintained. In order to prevent the screws from loosening, the screws are usually prevented from returning by means for preventing the male and female screws from returning in the axial direction, such as a lock nut and a spring washer. However, in the conventional screw return prevention means such as a lock nut and a spring washer, the male screw and the female screw are shifted in the axial direction so that the thread is brought into close contact with the return prevention means. However, on the side opposite to the close contact side, the space between the male screw and the female screw is large, and the screw groove is not lost, so the contact state due to impact or vibration is easily eliminated. As a result, the loosening of the screws could not be prevented sufficiently.

そこで、ナットの一部を変形させてボルトに当接させることにより、ネジ溝を消失させてネジのもどりを防止するようにしたものが、特許文献１及び特許文献２に開示されている。特許文献１に開示されている技術は、止めナットと締付けナットのダブルナットからなり、止めナットに外周面をテーパー面とした締付筒体を一体に連結し、該締付筒体に複数のスリットを入れて、締付けナットでテーパー面を押圧して締付筒体を変形させるようにしたものであり、特許文献２に開示されている技術は、ナットの座面間で変形する突起をナットに一体に形成し、該突起をナットとボルトのネジ溝にクサビ状に嵌入して変形させ、ナットのゆるみを防止するようにしたものである。   Therefore, Patent Document 1 and Patent Document 2 disclose that a part of a nut is deformed and brought into contact with a bolt so that a screw groove disappears to prevent the screw from returning. The technology disclosed in Patent Document 1 is composed of a double nut of a lock nut and a tightening nut, and a tightening cylinder body having an outer peripheral surface as a tapered surface is integrally connected to the lock nut, and a plurality of the tightening cylinder bodies are connected to the tightening cylinder body. A slit is inserted and the tapered surface is deformed by pressing the taper surface with a tightening nut, and the technique disclosed in Patent Document 2 is a method in which a protrusion that deforms between the seating surfaces of the nut The protrusion is inserted into the thread groove of the nut and bolt in a wedge shape and deformed to prevent loosening of the nut.

しかしながら、このようなナットの一部を変形させる構造では、締付筒体や突起の基部がナットに一体となっているため、変形させたとき先端部分が傾斜して小さな面積で雄ネジと雌ネジが接触しているにすぎず、十分なゆるみ止め効果を期待することが出来ないという問題があった。また、変形した締付筒体や突起による固定を解除することが極めて困難で、特別な治具を必要とするという問題があった。さらに、固定が長期に亘る場合にはその解除が不可能となるおそれがあった。特に、突起の形成は、鍛造方法のような大量生産方式での製造が困難であり、大量生産物品であるナットの製造には適していない構造であった。
実開昭５５−１１５４２２号公報 特開平１０−６１６４５号公報 However, in such a structure in which a part of the nut is deformed, the tightening cylinder and the base of the protrusion are integrated with the nut, so that when deformed, the tip portion is inclined and the male screw and the female have a small area. There is a problem that the screws are only in contact with each other and a sufficient locking effect cannot be expected. Further, it is extremely difficult to release the fixing by the deformed tightening cylinder or the protrusion, and there is a problem that a special jig is required. Furthermore, when the fixing is performed for a long period of time, it may not be possible to release it. In particular, the formation of protrusions is a structure that is difficult to manufacture in a mass production system such as a forging method and is not suitable for manufacturing nuts that are mass-produced articles.
Japanese Utility Model Publication No. 55-115422 Japanese Patent Laid-Open No. 10-61645

この発明は、ボルトとナットとのゆるみ止めをより確実且強固に達成することが出来、しかも大量生産に適した構造のゆるみ止めナットを提供せんとするものである。   The present invention is intended to provide a locking nut having a structure that can more reliably and firmly achieve the locking between the bolt and the nut and is suitable for mass production.

本発明は、ボルトに螺合して締結されるナットと、このナットと該ボルトとの間に介在されるワッシャとを備え、ワッシャは前記ボルトを挿入する筒状の挿入部を有し、且、軸方向に一端から他端まで伸びるスリットが形成され、ワッシャの筒状部内面に、前記ボルトと逆方向のネジが形成されており、ナットとワッシャとを台頭円錐形の斜面を介して当接させ、締結時に台頭円錐形のテーパー面との当接によるナットの締め付けによって、ワッシャを縮径させ、ワッシャをボルトに圧着させて、ナットのゆるみ止めを果たすようにしたことを特徴とするゆるみ止めナットである。 The present invention comprises a nut screwed and fastened to a bolt, and a washer interposed between the nut and the bolt, the washer having a cylindrical insertion portion for inserting the bolt, and A slit extending in the axial direction from one end to the other end is formed, and a screw in a direction opposite to the bolt is formed on the inner surface of the cylindrical portion of the washer. The nut and the washer are pressed against each other via a truncated conical slope. The looseness is characterized in that the nut is tightened by abutting with the tapered surface of the conical cone at the time of fastening and the washer is reduced in diameter and the washer is crimped to the bolt to prevent the nut from loosening. It is a lock nut.

ナットは、ボルトの雄ネジに螺合する雌ネジを形成した雌ネジ部と、この雌ネジ部に連続する筒状部とを有し、ワッシャは、ボルトの軸心に対して直角方向に延びるフランジ部と、このフランジ部からボルト軸方向に筒状に立ち上がる筒状部とを有し、筒状部の外周面はフランジ部を基部として先端に向かって径が漸減する台頭円錐形のテーパー面に形成され、ナットの筒状部の内径はワッシャのテーパー面の最大外径よりも小さく形成され、ワッシャには一端から他端まで延びるスリットが形成され、ボルトにワッシャを挿通し、ナットの筒状部をワッシャの筒状部に挿入しつつボルトに螺合し、ワッシャのテーパ面とナットの筒状部との当接により、ワッシャを縮径してワッシャの筒状部内面をボルトに圧着して逆方向のネジをボルトのネジに噛み込ませつつ締結するようにしたことを特徴としている。 The nut has a female screw portion that forms a female screw that is screwed into a male screw of the bolt, and a cylindrical portion that is continuous to the female screw portion, and the washer extends in a direction perpendicular to the axis of the bolt. A tapered cone surface having a flange portion and a cylindrical portion that rises in a cylindrical shape from the flange portion in the bolt axis direction, and the outer peripheral surface of the cylindrical portion gradually decreases in diameter toward the tip with the flange portion as a base. The inner diameter of the cylindrical portion of the nut is formed smaller than the maximum outer diameter of the tapered surface of the washer. The washer has a slit extending from one end to the other end, the washer is inserted into the bolt, and the nut cylinder The washer is screwed into the bolt while being inserted into the cylindrical part of the washer. to the opposite direction of the screw bolt of It is characterized in that as fastening while meshed with the di.

フランジ部と筒状部のテーパー面との間に、フランジ部からボルト軸方向に平行に立ち上がった非テーパー状の基端部を有し、ナット締め付け時に非テーパー状の基端部に、ナットの筒状部を当接、係入させて、該非テーパー状の基端部内にナットが当接している限り、ナットのゆるみが生じないようにして、緩み止めの安全度を向上させることが出来る。ワッシャの筒状部内径は、円形断面若しくは三角形、四角形、五角形、六角形等の非円形断面のいずれであっても良い。更に、台頭円錐形の筒状部は、フランジ部を介して軸方向対称に形成しても良い。この場合には、両方の筒状部に夫々ナットの筒状部が係合し、ワッシャを縮径させる。   Between the flange part and the tapered surface of the cylindrical part, it has a non-tapered base end that rises parallel to the bolt axis direction from the flange part. As long as the cylindrical portion is abutted and engaged and the nut is in contact with the non-tapered base end portion, the nut can be prevented from loosening, and the safety of the locking can be improved. The inner diameter of the cylindrical portion of the washer may be a circular cross section or a non-circular cross section such as a triangle, a quadrangle, a pentagon, or a hexagon. Furthermore, the cylindrical part of the conical cone may be formed symmetrically in the axial direction via the flange part. In this case, the cylindrical portions of the nut are engaged with both the cylindrical portions, respectively, and the diameter of the washer is reduced.

本発明のゆるみ止めナットによれば、実施例１に示すように、米国航空機規格に準じた振動試験において、１７分間以上の耐振性を示すという格別の結果を得ることが可能であって、確実にゆるみを防止出来、強固な締結状態を長期間にわたって保持することが出来るという効果がある。   According to the loosening prevention nut of the present invention, as shown in Example 1, it is possible to obtain a special result of exhibiting vibration resistance of 17 minutes or more in a vibration test in accordance with the US aircraft standard. It is possible to prevent loosening and to maintain a strong fastening state over a long period of time.

当該発明のゆるみ止めナットは、構造が単純であり、製造コストを十分安価に抑えることが可能であって、大量生産にも適するという効果がある。   The loosening prevention nut of the present invention has a simple structure, can suppress the manufacturing cost sufficiently low, and has an effect of being suitable for mass production.

この発明の好ましい実施の形態を以下に図面を参照しながら詳細に説明する。図１は、本実施態様のゆるみ止めナット(１)を、ボルト(２)に締結し、被締結体(３)を固定した状態を示す断面図である。図２は、図１に示すゆるみ止めナット(１)の構成を示す部分断面斜視図であり、図３は図１に示すゆるみ止めナット(１)におけるワッシャ(５)の構成を示す部分断面斜視図である。図４Ａは、ナット(１)の締め付けによるワッシャ(５)の変形の様子を模式的に示す模式図であり、図４Ｂは図４Ａの部分拡大図である。図５は、ワッシャ(５)の一変形例を示す部分断面斜視図であり、図６は図５に示すワッシャ(５)の締結状態を模式的に示す図である。図７は、ワッシャ(５)の他の変形例を示す一部断面斜視図であり、図８は図７に示すワッシャ(５)の締結状態を模式的に示す図である。   Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a cross-sectional view showing a state in which the locking nut (1) of the present embodiment is fastened to the bolt (2) and the fastened body (3) is fixed. 2 is a partial cross-sectional perspective view showing the configuration of the locking nut (1) shown in FIG. 1, and FIG. 3 is a partial cross-sectional perspective view showing the configuration of the washer (5) in the locking nut (1) shown in FIG. FIG. FIG. 4A is a schematic view schematically showing a state of deformation of the washer (5) by tightening the nut (1), and FIG. 4B is a partially enlarged view of FIG. 4A. FIG. 5 is a partial cross-sectional perspective view showing a modified example of the washer (5), and FIG. 6 is a diagram schematically showing a fastening state of the washer (5) shown in FIG. FIG. 7 is a partially sectional perspective view showing another modified example of the washer (5), and FIG. 8 is a diagram schematically showing a fastening state of the washer (5) shown in FIG.

図１に示すように、本実施態様のゆるみ止めナットは、ボルト(２)に螺合して締結されるナット(１)と、このナット(１)と該ボルト(２)との間に介在するワッシャ(５)とを備え、前記ナット(１)の締結時において、該ナット(１)の螺合による締め付けによって前記ワッシャ(５)が縮径し、該ワッシャ(５)と前記ボルト(２)とが強固に当接することによってゆるみ止め効果がもたらされる。   As shown in FIG. 1, the locking nut according to the present embodiment includes a nut (1) that is screwed to and fastened to a bolt (2), and is interposed between the nut (1) and the bolt (2). A washer (5), and when the nut (1) is fastened, the washer (5) is reduced in diameter by screwing of the nut (1), and the washer (5) and the bolt (2) ) Are brought into firm contact with each other, thereby providing a locking effect.

本実施態様のナット(１)は、図２に示すように、前記ボルト(２)の雄ネジ(2b)に螺合する雌ネジ(1a)を形成した雌ネジ部(1b)と、この雌ネジ(1a)に連続する円筒状の筒状部(1c)とを有する。このナット(１)の外形は、略正六角柱であるが勿論これに限らず、従来公知のナット外形を採用することが出来る。   As shown in FIG. 2, the nut (1) of this embodiment includes a female screw portion (1 b) having a female screw (1 a) that is screwed into the male screw (2 b) of the bolt (2), and the female screw portion (1 b). And a cylindrical tubular portion (1c) continuous to the screw (1a). The outer shape of the nut (1) is a substantially regular hexagonal column, but is not limited to this, and a conventionally known nut outer shape can be adopted.

本実施態様のワッシャ(５)は、図３に示すように、ボルトの軸方向と直交する方向に延びる平坦な円板状のフランジ部(5a)と、このフランジ部(5a)からボルト軸方向に沿って筒状に立ち上がった筒状部(5b)とを有し、筒状部(5b)の外周面がフランジ部(5a)から外方に向かって狭まる台頭円錐形のテーパー面に形成されている。該筒状部(5b)は、その頂部(5c)の最大外径はナット(１)の筒状部(1c)の内径よりも小さく、ワッシャ(５)の筒状部(5b)の最大外径はナット(１)の筒状部(1c)の内径よりも大径に形成され、ナットによりワッシャをテーパー面のくさび効果により、縮径することが出来る。縮径のために、ワッシャ(５)には、該ワッシャ(５)の一端から他端まで連続して切り込まれたスリット(5e)が形成される。フランジ部(5a)から立ち上がったテーパー状の外周面を有するワッシャ(５)の筒状部(5b)は、好ましくはフランジ部(5a)との間に、ボルトの軸方向に対して平行に若干立ち上がった非テーパー状、すなわち筒状の基端部(5f)を有し、ナット(１)締め付け時に、この基端部(5f)にナット(１)の筒状部(1c)の内周面が当接、係入して、より確かな緩み止めが図られるようになっている。   As shown in FIG. 3, the washer (5) of this embodiment includes a flat disk-shaped flange portion (5a) extending in a direction perpendicular to the axial direction of the bolt, and the axial direction of the bolt from the flange portion (5a). And a cylindrical portion (5b) rising in a cylindrical shape along the outer peripheral surface of the cylindrical portion (5b) is formed into a tapered cone-shaped tapered surface that narrows outward from the flange portion (5a). ing. The cylindrical portion (5b) has a maximum outer diameter of the top portion (5c) smaller than the inner diameter of the cylindrical portion (1c) of the nut (1), and the maximum outer diameter of the cylindrical portion (5b) of the washer (5). The diameter is formed larger than the inner diameter of the cylindrical portion (1c) of the nut (1), and the washer can be reduced in diameter by the wedge effect of the tapered surface. In order to reduce the diameter, the washer (5) is formed with a slit (5e) continuously cut from one end to the other end of the washer (5). The cylindrical part (5b) of the washer (5) having a tapered outer peripheral surface rising from the flange part (5a) is preferably slightly parallel to the axial direction of the bolt between the flange part (5a). It has a raised non-tapered, that is, cylindrical base end (5f), and when tightening the nut (1), the base end (5f) is connected to the inner peripheral surface of the cylindrical portion (1c) of the nut (1). Are brought into contact with and engaged with each other, so that more reliable locking can be achieved.

本発明のゆるみ止めナット(１)は、従来公知の一般的なボルト(２)に対して螺合して締結することが可能であるが、本実施態様におけるボルト(２)は、略六角柱の頭部(2a)（埋め込みボルトのような場合には、必ずしも頭部を必要としない）と、雄ねじが形成されたボルト本体(2b)を有する。被締結体(３)は、ボルト本体(2b)が挿通する貫通孔(3a)を有する（図１参照）。   The loosening prevention nut (1) of the present invention can be screwed and fastened to a conventionally known general bolt (2), but the bolt (2) in this embodiment is a substantially hexagonal column. Head (2a) (in the case of an embedded bolt, the head is not necessarily required) and a bolt body (2b) formed with a male screw. The fastened body (3) has a through hole (3a) through which the bolt body (2b) is inserted (see FIG. 1).

本実施態様のゆるみ止めナット(１)を前記ボルト(２)に締結する際には、該ボルト(２)の頭部(2a)とフランジ部(5a)との間に被締結体(３)を挟んでワッシャ(５)を挿通し、その後、ナット(１)の筒状部(1c)をワッシャ(５)の筒状部(5b)に挿入しつつボルト(２)に螺合する。ナット(１)の螺進により、ワッシャ(５)のテーパ状の筒状部(5b)に、ナット(１)の筒状部(1c)が係合して、テーパー面に沿ったくさび効果により、図４に示すようにワッシャ(５)が変形しつつ縮径し、該ワッシャ(５)の筒状部(5b)の内周面が局部的にボルト本体(2b)に圧着し締結される。このワッシャ(５)の縮径の様子を模式的に示したのが図４Ａ及び図４Ｂである。図４Ａ及び図４Ｂに二点鎖線で示すように、ワッシャ(５)は、略卵形に変形しつつ縮径し、内径が狭小に変形した部分が局部的にボルトに圧着する。   When the locking nut (1) of this embodiment is fastened to the bolt (2), the fastened body (3) is interposed between the head (2a) and the flange (5a) of the bolt (2). Then, the washer (5) is inserted, and the cylindrical portion (1c) of the nut (1) is inserted into the cylindrical portion (5b) of the washer (5) and screwed into the bolt (2). Due to the screwing of the nut (1), the tubular portion (1c) of the nut (1) is engaged with the tapered tubular portion (5b) of the washer (5), and the wedge effect along the tapered surface is obtained. 4, the washer (5) is deformed and reduced in diameter, and the inner peripheral surface of the cylindrical portion (5b) of the washer (5) is locally crimped and fastened to the bolt body (2b). . FIGS. 4A and 4B schematically show the diameter of the washer (5). As shown by a two-dot chain line in FIGS. 4A and 4B, the washer (5) is reduced in diameter while being deformed into a substantially oval shape, and a portion whose inner diameter is deformed to be narrow is locally pressed onto the bolt.

また、ワッシャ(５)の筒状部(5b)の内部形状は、必ずしも円形でなければならないというものではなく、例えば、図５に示すように、ワッシャ(50)の筒状部(50b)の形状は、断面三角形、若しくは図７に示すような断面五角形等の非円形断面とすることが出来る。図５Ａの断面三角形の場合、図６Ａに示すように、スリット(50e)が狭まり、三角形の三辺が三角形の中心に向かって収縮して、ボルト(２)に三方向から圧着するようになる。尚、この三角形断面を採用する場合、縮径時における狭部(50f)の折曲げ強度を向上させるため、図５Ｂ、図６Ｂに示すように、その端部形状を円弧状に形成するのが好ましい。   Moreover, the internal shape of the cylindrical part (5b) of the washer (5) does not necessarily have to be circular, and for example, as shown in FIG. 5, the cylindrical part (50b) of the washer (50) The shape may be a non-circular cross section such as a triangular cross section or a pentagonal cross section as shown in FIG. In the case of the cross-sectional triangle of FIG. 5A, as shown in FIG. 6A, the slit (50e) is narrowed, the three sides of the triangle contract toward the center of the triangle, and the bolt (2) is crimped from three directions. . When this triangular cross section is adopted, in order to improve the bending strength of the narrow portion (50f) when the diameter is reduced, as shown in FIGS. 5B and 6B, the end shape is formed in an arc shape. preferable.

また、図７に示す断面五角形の場合、図８に示すように、スリット(51e)が狭まり、五角形の五辺が該五角形の中心に向かって収縮して、ボルト(２)に五方向から締め付けるよう圧着する。これら図５或いは図７に示す形状は単なる例示であり、三角形、五角形に限られるものではなく、所望の非円形断面形状とすることが出来る。例えば、図９，１０に示すような四角形、若しくは図１１，１２に示す六角形或いはその他の多角形状、楕円形状とすることが出来る。すなわち、図９，１０においては、ワッシャ(52)の筒状部(52b)の内周面が四角形に形成され、図１１，１２においては、ワッシャ(53)の筒状部(53b)の内周面が六角形に形成されている。その他の点は、前述した構造と実質的に同じである。   Further, in the case of the pentagonal cross section shown in FIG. 7, as shown in FIG. 8, the slit (51e) narrows, the pentagonal five sides contract toward the center of the pentagon, and tightens the bolt (2) from five directions. Crimp so that. These shapes shown in FIG. 5 or FIG. 7 are merely examples, and are not limited to triangles and pentagons, and may have a desired noncircular cross-sectional shape. For example, a quadrangle as shown in FIGS. 9 and 10, a hexagon as shown in FIGS. 11 and 12, other polygonal shapes, or an elliptical shape can be used. That is, in FIGS. 9 and 10, the inner peripheral surface of the cylindrical portion (52b) of the washer (52) is formed in a square shape, and in FIGS. 11 and 12, the inner surface of the cylindrical portion (53b) of the washer (53) is formed. The peripheral surface is formed in a hexagon. Other points are substantially the same as the structure described above.

図１３〜１５は、更に他の変形を示し、ワッシャ(500)に、フランジ部(500a)を介して軸方向対称に筒状部(500b)(500b)を形成し、該二つの筒状部(500b)に夫々ナット(１)を挿着し、筒状部の縮径を行い、より強固にボルト(２)に筒状部内周面を圧着するようにしたものである。スリット(500e)は、上部の筒状部からフランジ部を越えて下部の筒状部まで連続して形成され、スリットにより、ワッシャは軸方向に分断された状態になる。その他の点は、前記図１〜１２に示すものと実質的に同じである。   FIGS. 13 to 15 show still another modification, in which a cylindrical portion (500b) (500b) is formed in the washer (500) symmetrically in the axial direction via the flange portion (500a), and the two cylindrical portions are formed. The nut (1) is inserted into each (500b), the diameter of the cylindrical portion is reduced, and the inner peripheral surface of the cylindrical portion is more firmly bonded to the bolt (2). The slit (500e) is continuously formed from the upper cylindrical portion to the lower cylindrical portion beyond the flange portion, and the washer is divided in the axial direction by the slit. The other points are substantially the same as those shown in FIGS.

図１６〜１８はワッシャの変形例を示し、筒状部内面に回り止め用の加工を施したものである。図１６に示すものは、円筒部内面にボルト(２)の雄ネジ(2b)と逆方向の逆ネジ(61)を形成したものである。この逆ネジ(61)の存在によりナット(１)による締結によって縮径した際に、ボルト(２)の雄ネジ(2b)に逆ネジ(61)が局部的に噛み込み、ワッシャの回転が抑止され、振動等によるナットの滑落を防止できる。尚、形成する逆ネジ(61)は、雄ネジ(2b)とはネジピッチに関係なく両者が合致することは無い為、雄ネジ(2b)と同じピッチで形成しても、異なるピッチで形成しても良く、所望のピッチを採用することができる。   FIGS. 16 to 18 show modified examples of the washer, in which the inner surface of the cylindrical portion is processed to prevent rotation. FIG. 16 shows an example in which a reverse screw (61) in the opposite direction to the male screw (2b) of the bolt (2) is formed on the inner surface of the cylindrical portion. When the diameter is reduced by fastening with the nut (1) due to the presence of the reverse screw (61), the reverse screw (61) is locally engaged with the male screw (2b) of the bolt (2), and the rotation of the washer is suppressed. Thus, the nut can be prevented from sliding off due to vibration or the like. Note that the reverse screw (61) to be formed does not match the male screw (2b) regardless of the screw pitch, so even if they are formed at the same pitch as the male screw (2b), they must be formed at a different pitch. The desired pitch may be employed.

図１７に示すものは他の変形例を示し、円筒部内面に円筒部内面にボルト(２)の雄ネジ(2b)と同方向で、且、雄ネジ(2b)と異なるネジピッチの正ネジ(62)を形成したものである。例えば、ボルトの雄ネジが１.７５mmピッチの右ネジである時、１.５mmピッチの右ネジで形成する。これにより両ネジが合致することはなく、ワッシャの縮径時、雄ネジ(2b)と正ネジ(62)は局部的に噛み合い、回転を抑止することができる。尚、正ネジ(62)のネジピッチはこれに限られるものではなく、２mm、１.８mm等、ボルトの雄ネジのピッチと異なるものであればよい。   FIG. 17 shows another modified example. A positive screw (in the same direction as the male screw (2b) of the bolt (2) on the inner surface of the cylindrical portion and a different screw pitch from the male screw (2b)) 62). For example, when the male screw of the bolt is a right-hand screw with a pitch of 1.75 mm, the right-hand screw with a pitch of 1.5 mm is formed. As a result, the screws do not coincide with each other, and when the washer is reduced in diameter, the male screw (2b) and the positive screw (62) are locally engaged to prevent rotation. The screw pitch of the positive screw (62) is not limited to this, and may be any pitch that is different from the pitch of the male screw of the bolt, such as 2 mm and 1.8 mm.

図１８に示すものは更に他の変形例を示し、円筒部内面に断面台形の縦溝(63)を形成したものである。ナット(１)の締結によって縮径した際、ボルト(２)の雄ネジ(2b)に縦溝(63)が直行するように喰い込み、ワッシャの回転が強固に抑止される。尚、前述の逆ネジ(61)、正ネジ(62)を形成したものと同様に、円筒部の内径はボルトの外径よりも若干大きく設計されているため、縦溝(63)の存在にかかわらず、ボルトへの挿着に支障はない。尚、内面形状は前記台形に限られるものではなく、矩形、波形等の形状であってもよい。   FIG. 18 shows still another modified example in which a longitudinal groove (63) having a trapezoidal cross section is formed on the inner surface of the cylindrical portion. When the diameter is reduced by fastening the nut (1), the vertical groove (63) bites into the male screw (2b) of the bolt (2) so that the rotation of the washer is firmly suppressed. Note that, as in the case where the reverse screw (61) and the normal screw (62) are formed, the inner diameter of the cylindrical portion is designed to be slightly larger than the outer diameter of the bolt. Regardless, there is no hindrance to the bolt. The inner surface shape is not limited to the trapezoidal shape, and may be a rectangular shape, a corrugated shape, or the like.

前述の溝のないワッシャを含め、全てのワッシャの円筒部の内径は、ボルトの外径に比べ若干大きく設計されている。すなわち、ボルトの直径が１１.８mmとしたとき、円筒部の内径は１２mmとし、０.２mmのクリアランスを確保している。これにより、逆ネジ(61)、正ネジ(62)及び縦溝(63)の存在にかかわらず、ボルトの雄ネジ(2b)に引っかかるような支障はなく、簡単に挿着することが出来るようになっている。   The inner diameter of the cylindrical portion of all the washers including the washer without the groove is designed to be slightly larger than the outer diameter of the bolt. That is, when the bolt diameter is 11.8 mm, the inner diameter of the cylindrical portion is 12 mm, and a clearance of 0.2 mm is secured. As a result, regardless of the presence of the reverse screw (61), normal screw (62), and vertical groove (63), there is no hindrance to the male screw (2b) of the bolt so that it can be easily inserted and attached. It has become.

本実施態様のゆるみ止めナットを、ボルトに締結し、被締結体に固定した状態を示す断面図Sectional drawing which shows the state which fastened the locking nut of this embodiment to the volt | bolt, and was fixed to the to-be-fastened body 図１に示すゆるみ止めナットにおけるナットの構成を示す部分断面斜視図The partial cross-section perspective view which shows the structure of the nut in the locking nut shown in FIG. 図１に示すゆるみ止めナットにおけるワッシャの構成を示す部分断面斜視図The partial cross-section perspective view which shows the structure of the washer in the locking nut shown in FIG. ナットの締め付けによるワッシャの変形の様子を模式的に示すワッシャの一端面を平面視した模式図Schematic view of one end face of the washer schematically showing how the washer is deformed by tightening the nut 図４Ａの部分拡大図Partial enlarged view of FIG. 4A ワッシャの一変形例を示す一部を断面した斜視図The perspective view which cut down a part showing one modification of a washer 図５に示すワッシャの締結状態を模式的に示す図The figure which shows typically the fastening state of the washer shown in FIG. ワッシャの他の変形例を示す一部を断面した斜視図The perspective view which carried out the cross section of a part which shows other modifications of a washer 図７に示すワッシャの締結状態を模式的に示す図The figure which shows typically the fastening state of the washer shown in FIG. ワッシャの更に他の変形を示す一部を断面した斜視図The perspective view which carried out the cross section of the part which shows other deformation | transformation of a washer. 図９に示すワッシャの締結状態を模式的に示す図The figure which shows typically the fastening state of the washer shown in FIG. ワッシャの更に他の変形を示す一部を断面した斜視図The perspective view which carried out the cross section of the part which shows other deformation | transformation of a washer. 図１１に示すワッシャの締結状態を模式的に示す図The figure which shows typically the fastening state of the washer shown in FIG. 更に他の変形にかかるワッシャをナットと組み合わせて、ボルトに締結し、被締結体を固定した状態を示す断面図Sectional drawing which shows the state which combined the washer concerning other deformation | transformation with the nut, fastened to the volt | bolt, and fixed the to-be-fastened body. 図１３のナットの一部を断面した斜視図FIG. 13 is a perspective view of a part of the nut in FIG. 図１３のワッシャの一部を断面した斜視図FIG. 13 is a perspective view of a part of the washer of FIG. ワッシャの円筒部内面に逆ネジを形成した例を示す図The figure which shows the example which formed the reverse screw in the cylindrical part inner surface of a washer 同、正ネジを形成した例を示す図The figure which shows the example which formed the same screw 同、縦溝を形成した例を示す図The figure which shows the example which formed the vertical groove

符号の説明Explanation of symbols

１ ゆるみ止めナット
1a 雌ネジ
1b 雌ネジ部
1c 筒状部
２ ボルト
2a 頭部
2b 雄ネジ
2c 雄ネジ部
2d ボルト本体
2e 円柱部
３ 被締結体
3a 貫通孔
５ ワッシャ
5a フランジ部
5b 筒状部
5c 頂部
5d 下端部
5e スリット
5f 基端部
50 ワッシャ
50a フランジ部
50b 筒状部
50c 頂部
50d 下端部
50e スリット
50f 狭部
51 ワッシャ
51a フランジ部
51b 筒状部
51c 頂部
51d 下端部
51e スリット
52 ワッシャ
52a フランジ部
52b 筒状部
52c 頂部
52d 下端部
52e スリット
53 ワッシャ
53a フランジ部
53b 筒状部
53c 頂部
53d 下端部
53e スリット
500 ワッシャ
500a フランジ部
500b 筒状部
500e スリット
61 逆ネジ
62 正ネジ
63 縦溝
1 Locking nut
1a Female thread
1b Female thread
1c Cylindrical part 2 bolt
2a head
2b Male thread
2c Male thread
2d bolt body
2e Cylindrical part 3 Fastened object
3a Through hole 5 Washer
5a Flange
5b Tube
5c top
5d bottom edge
5e slit
5f Base end
50 washers
50a Flange
50b Tube
50c top
50d bottom edge
50e slit
50f Narrow part
51 washer
51a Flange
51b Tube
51c top
51d bottom edge
51e slit
52 washer
52a Flange
52b Tube
52c top
52d bottom edge
52e slit
53 Washer
53a Flange
53b Tube
53c top
53d bottom edge
53e slit
500 washers
500a Flange
500b Tube
500e slit
61 Reverse screw
62 Positive screw
63 Vertical groove

Claims (6)

ボルトに螺合して締結されるナットと、このナットと該ボルトとの間に介在されるワッシャとを備え、ワッシャは前記ボルトが挿入される筒状の挿入部を有し、且、軸方向に一端から他端まで伸びる１本のスリットにより分断されており、ワッシャの外周面は台頭円錐形に形成され、ナットとワッシャとを台頭円錐形のテーパー面を介して当接させ、締結時に台頭円錐形のテーパー面との当接によるナットの締め付けによって、ワッシャをスリットにおいて縮径させ、ワッシャ内周面をボルトに圧着させて、ナットのゆるみ止めを果たすようにしたゆるみ止めナットであって、ワッシャの筒状部内面に、前記ボルトと逆方向のネジを形成したことを特徴とするゆるみ止めナット。 A nut screwed and fastened to the bolt, and a washer interposed between the nut and the bolt, the washer having a cylindrical insertion portion into which the bolt is inserted, and in the axial direction The washer is divided by a single slit extending from one end to the other, and the outer peripheral surface of the washer is formed in a truncated cone shape. The nut and washer are brought into contact with each other via a tapered surface of the truncated cone, and are A locking nut that tightens the nut by contact with the conical tapered surface to reduce the diameter of the washer at the slit and presses the inner peripheral surface of the washer to the bolt to prevent the nut from loosening . A loosening prevention nut characterized in that a screw in a direction opposite to that of the bolt is formed on the inner surface of the cylindrical portion of the washer . ナットは、ボルトの雄ネジに螺合する雌ネジを形成した雌ネジ部と、この雌ネジ部に連続する筒状部とを有し、ワッシャは、ボルトの軸心に対して直角方向に延びるフランジ部と、このフランジ部からボルト軸方向に筒状に立ち上がる筒状部とを有し、筒状部の外周面はフランジ部を基部として先端に向かって径が漸減する台頭円錐形のテーパー面に形成され、ナットの筒状部の内径はワッシャのテーパー面の最大外径よりも小さく形成され、ワッシャは一端から他端まで延びるスリットにより分断され、ボルトにワッシャを挿通し、ナットの筒状部をワッシャの筒状部に挿入しつつボルトに螺合し、ワッシャのテーパ面とナットの筒状部との当接により、ワッシャを縮径してワッシャの筒状部内面をボルトに圧着して逆方向のネジをボルトのネジに噛み込ませつつ締結するようにしたことを特徴とする請求項１記載のゆるみ止めナット。 The nut has a female screw portion that forms a female screw that is screwed into a male screw of the bolt, and a cylindrical portion that is continuous to the female screw portion, and the washer extends in a direction perpendicular to the axis of the bolt. A tapered cone surface having a flange portion and a cylindrical portion that rises in a cylindrical shape from the flange portion in the bolt axis direction, and the outer peripheral surface of the cylindrical portion gradually decreases in diameter toward the tip with the flange portion as a base. The inner diameter of the cylindrical portion of the nut is formed smaller than the maximum outer diameter of the tapered surface of the washer, the washer is divided by a slit extending from one end to the other end, the washer is inserted into the bolt, and the cylindrical shape of the nut Is inserted into the cylindrical part of the washer and screwed into the bolt. bolt in the opposite direction of the screw Te Locking nut according to claim 1, characterized in that as fastening while meshed with the screw. フランジ部と筒状部のテーパー面との間に、フランジ部からボルト軸方向に平行に立ち上がった非テーパー状の基端部を有し、ナット締め付け時に非テーパー状の基端部に、ナットの筒状部が当接、係入するようにしたことを特徴とする請求項１又は２に記載のゆるみ止めナット。   Between the flange part and the tapered surface of the cylindrical part, it has a non-tapered base end that rises parallel to the bolt axis direction from the flange part. The loosening prevention nut according to claim 1 or 2, wherein the cylindrical portion is abutted and engaged. ワッシャの筒状部内径が、円形断面であることを特徴とする請求項１乃至３のいずれかに記載のゆるみ止めナット。   4. The loosening prevention nut according to claim 1, wherein an inner diameter of the cylindrical portion of the washer has a circular cross section. ワッシャの筒状部内径が、非円形断面であることを特徴とする請求項１乃至３のいずれかに記載のゆるみ止めナット。   The loosening prevention nut according to any one of claims 1 to 3, wherein the inner diameter of the cylindrical portion of the washer has a non-circular cross section. ワッシャの筒状部を、フランジ部を介して軸方向対称に形成したことを特徴とする請求項１乃至５のいずれかに記載のゆるみ止めナット。   6. The locking nut according to claim 1, wherein the cylindrical portion of the washer is formed symmetrically in the axial direction via the flange portion.
JP2007155705A 2007-06-12 2007-06-12 Locking nut Expired - Fee Related JP4072832B1 (en)

Priority Applications (3)

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JP2007155705A JP4072832B1 (en) 2007-06-12 2007-06-12 Locking nut
PCT/JP2008/060298 WO2008152963A1 (en) 2007-06-12 2008-06-04 Loosening preventive nut
TW97121747A TW200916667A (en) 2007-06-12 2008-06-11 Nut contrived for screws not to slacken

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JP2008309202A JP2008309202A (en) 2008-12-25

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JP2008309202A (en) 2008-12-25
WO2008152963A1 (en) 2008-12-18

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