JP7126209B2

JP7126209B2 - pipe joint

Info

Publication number: JP7126209B2
Application number: JP2019121338A
Authority: JP
Inventors: 秋生保田
Original assignee: Daikin Industries Ltd; Higashio Mech Co Ltd
Current assignee: Daikin Industries Ltd; Higashio Mech Co Ltd
Priority date: 2019-06-28
Filing date: 2019-06-28
Publication date: 2022-08-26
Anticipated expiration: 2039-06-28
Also published as: JP2021008888A

Description

本発明は、管継手に関する。 The present invention relates to pipe joints.

管継手の一種として、フレア継手が広く知られている。一般に、このフレア継手は、図15に示すように、パイプｐの端部にフレア加工部ｆを特別な治具にて塑性加工して形成し、このフレア加工部ｆを、フレア継手本体ｈのテーパ部ａに当てて袋ナットｎにて締付けて、袋ナットｎのテーパ面ｔとフレア継手本体ｈのテーパ部ａにて挟圧し、金属面の相互圧接にて密封性を確保する構成である（例えば特許文献１参照）。
しかしながら、図15に示した管継手は、作業現場にて、被接続パイプｐの端部に、専用工具を使用して、フレア加工部ｆを形成する必要があり、作業能率が悪く、品質のバラツキも生じる。さらに、パイプｐのフレア加工部ｆの小径端縁ｆ₁ に亀裂を生じ易い。また、袋ナットｎを締付けた際にパイプｐが減肉して、その結果、密封性の低下や袋ナットｎに緩みを発生し易いという問題もあった。
そこで、本出願人等は、図15に示すフレア加工部ｆを全く省略したパイプｐを、接続できる管継手を提案した。 A flare joint is widely known as one type of pipe joint. In general, as shown in FIG. 15, this flared joint is formed by forming a flared portion f at the end of a pipe p by plastic working with a special jig, and this flared portion f is formed on the flared joint main body h. The cap nut n is applied to the tapered portion a and tightened, and the tapered surface t of the cap nut n and the tapered portion a of the flare joint main body h are pressed against each other, and the metal surfaces are pressed against each other to ensure the sealing performance. (See Patent Document 1, for example).
However, with the pipe joint shown in FIG. 15, it is necessary to use a special tool to form the flared portion f at the end of the pipe to be connected p at the work site, resulting in poor work efficiency and poor quality. Variation also occurs. Furthermore, the small diameter edge f ₁ of the flared portion f of the pipe p is likely to crack. Moreover, when the cap nut n is tightened, the thickness of the pipe p is reduced, and as a result, there is a problem that the sealing performance is deteriorated and the cap nut n is easily loosened.
Therefore, the present applicants have proposed a pipe joint capable of connecting a pipe p in which the flared portion f shown in FIG. 15 is completely omitted.

即ち、図16に示すような構造の管継手である（特許文献２参照）。この図16（特許文献２）に記載の管継手は、雄ネジ部52とテーパ部53を有するフレア継手本体51に対し、袋ナット54を螺着するが、内部の収納空間部55には、ストップリング56を内装保持する。
このストップリング56は、シール凹溝57を有し、Ｏリング58が内装され、挿入されるパイプＰとの間の密封作用は、このＯリング58によって行われる。特に、ストップリング56は、継手本体51のテーパ部53に圧接する圧接勾配面59を有する。また、先端側には薄肉円筒部60が同一径をもって延設され、この薄肉円筒部60の最先端には、断面三角形のパイプ外周面食い込み用爪部61が付設されている。
この爪部61は、袋ナット54の螺進に伴って、パイプＰの外周面に食い込ませる構成である（特許文献２参照）。 That is, it is a pipe joint having a structure as shown in FIG. 16 (see Patent Document 2). The pipe joint described in FIG. 16 (Patent Document 2) has a flare joint main body 51 having a male screw portion 52 and a tapered portion 53, and a cap nut 54 is screwed thereon. The stop ring 56 is internally held.
This stop ring 56 has a seal recessed groove 57, and an O-ring 58 is installed therein, and the sealing action between the stop ring 56 and the pipe P into which it is inserted is performed by this O-ring 58. As shown in FIG. In particular, the stop ring 56 has a pressure sloped surface 59 that presses against the tapered portion 53 of the joint body 51 . Further, a thin cylindrical portion 60 extends with the same diameter on the tip end side, and at the tip of the thin cylindrical portion 60, a pawl portion 61 for biting into the outer peripheral surface of the pipe having a triangular cross section is attached.
The claw portion 61 is configured to bite into the outer peripheral surface of the pipe P as the cap nut 54 is screwed (see Patent Document 2).

特開２００５－４２８５８号公報JP-A-2005-42858 特許第５０９１１９１号公報Japanese Patent No. 5091191

しかしながら、図16（特許文献２）に示した管継手を、冷媒配管用として現実に市場へ提供するうえで、次の３点が、未解決であり、又は、技術的に不十分であることが、判明してきた。
（ｉ）袋ナット54を螺進してゆくとストップリング56が共廻りを生じ、テーパ部53と圧接勾配面59の間で相対的スリップを発生し、これによって、その金属圧接シールが破壊される。これを防ぐために、爪部61を、特別な治具を使用して、パイプＰの外周面に、予め、食い込ませておく「予備加工」を必要とする点。
このような「予備加工」は配管接続現場での作業能率を著しく低下させる。
（ii）現実のパイプＰは、その肉厚が、薄肉円筒部60の肉厚と同程度であり、図16に示した肉厚Ｔｐの約１／３の場合もあり得る。従って、三角形断面の爪部61といえども、Ｃｕ製パイプＰの表面に食い込まず、パイプＰを局部的に内径方向に塑性変形させるのみで、パイプ耐引抜力が小さい点。
(iii) 上記（ii）に記述したように爪部61がパイプＰに食い込まず、配管工事完了後、パイプＰをその軸心廻りに回転させる外力が作用すると、簡単に回転を起こす。これに伴って、爪部61とパイプ外周面との間のメタルシール性が破壊される。従って、Ｏリング58を省略できない点。 However, the following three points remain unsolved or are technically inadequate in order to actually provide the pipe joint shown in FIG. 16 (Patent Document 2) to the market for use in refrigerant pipes. But it became clear.
(i) As the cap nut 54 is screwed, the stop ring 56 rotates together, causing a relative slip between the tapered portion 53 and the pressure gradient surface 59, thereby destroying the metal pressure contact seal. be. In order to prevent this, "preliminary processing" is required in which the claw portion 61 is made to bite into the outer peripheral surface of the pipe P in advance using a special jig.
Such "preliminary work" significantly reduces work efficiency at the piping connection site.
(ii) The thickness of the actual pipe P is approximately the same as the thickness of the thin cylindrical portion 60, and may be about 1/3 of the thickness Tp shown in FIG. Therefore, even the claw portion 61 having a triangular cross section does not bite into the surface of the Cu pipe P, but only locally plastically deforms the pipe P in the inner diameter direction, and the pipe pull-out resistance is small.
(iii) As described in (ii) above, the claws 61 do not bite into the pipe P, and when an external force acts to rotate the pipe P around its axis after the completion of piping work, the pipe P easily rotates. Along with this, the metal seal between the claw portion 61 and the outer peripheral surface of the pipe is destroyed. Therefore, the O-ring 58 cannot be omitted.

そこで、本発明は、雄ネジ部と先端縮径勾配面を有するフレア継手本体と、上記雄ネジ部に螺着される雌ネジ部を孔部の基端に有し、かつ、該孔部の中間には同一径部と段付部と先端縮径テーパ部とを有する収納空間部を形成した袋ナットと、該収納空間部に内装されると共に、上記先端縮径勾配面に圧接する基端側圧接勾配面を有すると共に、先端側には塑性変形可能な薄肉略円筒部とその先端頭部のパイプ引抜阻止用爪部とを有するストップリングと、を具備した管継手に於て、上記爪部は、微小間隔をもって配設された後爪と前爪にて構成され、上記後爪の断面形状は、直線状第１先端辺を上辺として有する台形乃至略台形であり、上記前爪の断面形状は、直線状第２先端辺を上辺として有する台形乃至略台形であり、被接続パイプのストレート状先端部の外周面に対し、上記ストップリングの上記後爪の第１先端辺と、上記前爪の第２先端辺が、上記袋ナットの螺進に伴って、強力圧接状態となって、パイプ引抜抵抗力を発生するよう構成し、上記袋ナットの上記孔部において、先端縮径テーパ部が、基端側急勾配テーパ部と先端側緩勾配テーパ部をもって、構成されている。 Accordingly, the present invention provides a flare joint main body having a male threaded portion and a tapered surface with a reduced diameter at the tip end, and a female threaded portion screwed to the male threaded portion at the base end of the hole. A cap nut having a storage space formed in the middle thereof, which has a portion of the same diameter, a stepped portion, and a tapered portion with reduced diameter at the tip; A pipe joint comprising a stop ring having a side pressure contact gradient surface, and having a plastically deformable thin-walled substantially cylindrical portion on the tip end side and a pipe pull-out preventing pawl portion at the top of the stop ring, wherein: The part is composed of a rear claw and a front claw arranged with a minute interval therebetween, the cross-sectional shape of the rear claw being a trapezoid or substantially a trapezoid having a linear first tip side as an upper side, and the cross section of the front claw. The shape is a trapezoidal or substantially trapezoidal shape having a linear second tip side as an upper side, and the first tip side of the rear claw of the stop ring and the front claw of the stop ring with respect to the outer peripheral surface of the straight tip portion of the pipe to be connected. The second tip side of the pawl comes into a strong pressure contact state as the cap nut is screwed to generate a pipe pull-out resistance force, and the hole portion of the cap nut has a tapered portion with a reduced diameter at the tip. is configured with a proximal steep taper and a distal gentle taper.

また、雄ネジ部と先端縮径勾配面を有するフレア継手本体と、上記雄ネジ部に螺着される雌ネジ部を孔部の基端に有し、かつ、該孔部の中間には同一径部と段付部と先端縮径テーパ部とを有する収納空間部を形成した袋ナットと、該収納空間部に内装されると共に、上記先端縮径勾配面に圧接する基端側圧接勾配面を有すると共に、先端側には塑性変形可能な薄肉略円筒部とその先端頭部のパイプ引抜阻止用爪部とを有するストップリングと、を具備した管継手に於て、上記爪部は、微小間隔をもって配設された後爪と前爪にて構成され、上記後爪の断面形状は、直線状第１先端辺を上辺として有する台形乃至略台形であり、上記前爪の断面形状は、直線状第２先端辺を上辺として有する台形乃至略台形であり、被接続パイプのストレート状先端部の外周面に対し、上記ストップリングの上記後爪の第１先端辺と、上記前爪の第２先端辺が、上記袋ナットの螺進に伴って、強力圧接状態となって、パイプ引抜抵抗力を発生するよう構成し、上記ストップリングの自由状態において、上記後爪の上記第１先端辺と、上記前爪の上記第２先端辺を、相互に平行として、かつ、上記第１先端辺を上記第２先端辺よりもラジアル内方として、配設し、さらに、上記強力圧接状態において、上記第２先端辺が上記第１先端辺よりもラジアル内方向に突出状、又は、上記第２先端辺と上記第１先端辺がラジアル方向同一位置となるように、上記先端縮径テーパ部の先端側の傾斜角度と、上記先端頭部の形状と寸法を、設定した。 A flare joint main body having a male screw portion and a tapered surface with a reduced diameter at the tip; a female screw portion screwed onto the male screw portion; A cap nut forming a storage space having a diametrical portion, a stepped portion, and a tapered portion with a reduced diameter at the tip; and a stop ring having a plastically deformable thin-walled substantially cylindrical portion on the tip end side and a claw portion for preventing the pipe from being pulled out at the top of the stop ring, wherein the claw portion has a minute The cross-sectional shape of the rear claw is a trapezoid or substantially trapezoid having a linear first tip side as an upper side, and the cross-sectional shape of the front claw is a straight line. The first tip side of the rear claw of the stop ring and the second tip side of the front claw of the stop ring are formed with respect to the outer peripheral surface of the straight tip portion of the pipe to be connected. As the cap nut is screwed, the tip side is in a strong pressure contact state to generate a pipe pull-out resistance, and in the free state of the stop ring, the first tip side of the rear claw and the first tip side. the second tip sides of the front claws are parallel to each other, and the first tip sides are arranged radially inward of the second tip sides; The tip of the tapered portion with reduced diameter at the tip so that the second tip side protrudes radially inward from the first tip side, or the second tip side and the first tip side are at the same position in the radial direction. The angle of inclination of the side and the shape and size of the tip head were set.

また、雄ネジ部と先端縮径勾配面を有するフレア継手本体と、上記雄ネジ部に螺着される雌ネジ部を孔部の基端に有し、かつ、該孔部の中間には同一径部と段付部と先端縮径テーパ部とを有する収納空間部を形成した袋ナットと、該収納空間部に内装されると共に、上記先端縮径勾配面に圧接する基端側圧接勾配面を有すると共に、先端側には塑性変形可能な薄肉略円筒部とその先端頭部のパイプ引抜阻止用爪部とを有するストップリングと、を具備した管継手に於て、上記爪部は、微小間隔をもって配設された後爪と前爪にて構成され、上記後爪の断面形状は、直線状第１先端辺を上辺として有する台形乃至略台形であり、上記前爪の断面形状は、直線状第２先端辺を上辺として有する台形乃至略台形であり、被接続パイプのストレート状先端部の外周面に対し、上記ストップリングの上記後爪の第１先端辺と、上記前爪の第２先端辺が、上記袋ナットの螺進に伴って、強力圧接状態となって、パイプ引抜抵抗力を発生するよう構成し、受圧状態下で、上記薄肉略円筒部が、過大拡径変形するのを阻止するための小突起を、上記薄肉略円筒部の外周面に付設して、上記小突起を上記袋ナットの上記孔部の内面に当接するように構成した。 A flare joint main body having a male screw portion and a tapered surface with a reduced diameter at the tip; a female screw portion screwed onto the male screw portion; A cap nut forming a storage space having a diametrical portion, a stepped portion, and a tapered portion with a reduced diameter at the tip; and a stop ring having a plastically deformable thin-walled substantially cylindrical portion on the tip end side and a claw portion for preventing the pipe from being pulled out at the top of the stop ring, wherein the claw portion has a minute The cross-sectional shape of the rear claw is a trapezoid or substantially trapezoid having a linear first tip side as an upper side, and the cross-sectional shape of the front claw is a straight line. The first tip side of the rear claw of the stop ring and the second tip side of the front claw of the stop ring are formed with respect to the outer peripheral surface of the straight tip portion of the pipe to be connected. When the cap nut is screwed, the tip side is strongly pressed against the pipe and generates resistance to pull out of the pipe . A small projection for preventing the slippage is attached to the outer peripheral surface of the thin-walled substantially cylindrical portion, and the small projection is configured to abut against the inner surface of the hole of the cap nut.

また、雄ネジ部と先端縮径勾配面を有するフレア継手本体と、上記雄ネジ部に螺着される雌ネジ部を孔部の基端に有し、かつ、該孔部の中間には同一径部と段付部と先端縮径テーパ部とを有する収納空間部を形成した袋ナットと、該収納空間部に内装されると共に、上記先端縮径勾配面に圧接する基端側圧接勾配面を有すると共に、先端側には塑性変形可能な薄肉略円筒部とその先端頭部のパイプ引抜阻止用爪部とを有するストップリングと、を具備した管継手に於て、上記爪部は、微小間隔をもって配設された後爪と前爪にて構成され、上記後爪の断面形状は、直線状第１先端辺を上辺として有する台形乃至略台形であり、上記前爪の断面形状は、直線状第２先端辺を上辺として有する台形乃至略台形であり、被接続パイプのストレート状先端部の外周面に対し、上記ストップリングの上記後爪の第１先端辺と、上記前爪の第２先端辺が、上記袋ナットの螺進に伴って、強力圧接状態となって、パイプ引抜抵抗力を発生するよう構成し、上記ストップリングのパイプ挿入孔部の少なくとも奥方部位を、奥方縮径テーパ状に形成し、パイプ挿入完了状態で上記ストレート状先端部が上記パイプ挿入孔部の内周面に圧接するよう構成した。 A flare joint main body having a male screw portion and a tapered surface with a reduced diameter at the tip; a female screw portion screwed onto the male screw portion; A cap nut forming a storage space having a diametrical portion, a stepped portion, and a tapered portion with a reduced diameter at the tip; and a stop ring having a plastically deformable thin-walled substantially cylindrical portion on the tip end side and a claw portion for preventing the pipe from being pulled out at the top of the stop ring, wherein the claw portion has a minute The cross-sectional shape of the rear claw is a trapezoid or substantially trapezoid having a linear first tip side as an upper side, and the cross-sectional shape of the front claw is a straight line. The first tip side of the rear claw of the stop ring and the second tip side of the front claw of the stop ring are formed with respect to the outer peripheral surface of the straight tip portion of the pipe to be connected. As the cap nut is screwed, the tip side is in a strong pressure contact state to generate a pipe pull-out resistance force, and at least the inner portion of the pipe insertion hole portion of the stop ring is formed into a tapered portion with a reduced inner diameter. When the pipe is completely inserted, the straight end portion is pressed against the inner peripheral surface of the pipe insertion hole.

また、上記爪部の上記後爪・前爪が上記袋ナットの螺進に伴って上記外周面に強力圧接状態で、上記後爪と前爪が密封機能を発揮して、ストップリングの内周面と外周面にシール材が省略されている。
また、上記パイプの外周面に対し、上記後爪及び前爪が、上記強力圧接状態において、パイプ引抜抵抗力を略相等しく分担するよう構成した。
また、上記後爪と上記前爪を先端に有する上記薄肉略円筒部は、先端方向に拡径状の円錐筒型とした。
また、上記継手本体の上記先端縮径勾配面の先端と、継手本体孔部とによって形成される円環状先端エッジ部に対し、内径側から引掛ける円環状小突条を、上記ストップリングの基端側圧接勾配面の内周端縁に付設し、該ストップリングの基端部が、過大にラジアル外方へ変形することを阻止するよう構成した。 Further, the rear claws and front claws of the claw portion are strongly pressed against the outer peripheral surface as the cap nut is screwed, and the rear claws and the front claws exhibit a sealing function, and the inner circumference of the stop ring is The sealing material is omitted on the surface and the outer peripheral surface.
Further, the rear claw and the front claw share the pipe pull-out resistance substantially equally in the strong pressure contact state with respect to the outer peripheral surface of the pipe.
Further, the thin-walled substantially cylindrical portion having the rear claw and the front claw at the tip has a conical cylindrical shape whose diameter expands in the tip direction.
In addition, an annular small ridge that is hooked from the inner diameter side is attached to the annular tip edge portion formed by the tip of the tip diameter decreasing slope surface of the joint body and the joint body hole portion at the base of the stop ring. The stop ring is attached to the inner peripheral edge of the end-side pressure contact gradient surface, and is configured to prevent the base end portion of the stop ring from being excessively deformed radially outward.

本発明によれば、従来必要であった前記「予備加工」を全く省略できて、配管作業が著しく容易かつ迅速に行い得る。しかも、安定して冷媒等の洩れを防止できる。
さらに、パイプの耐引抜力、及び、パイプ軸心廻りの耐回転トルクが、いずれも、大きい。特に、硬度が低く、縮径方向へ塑性変形し易い材質のパイプであっても、平面による強力圧接状態を保つ、２個の後爪・前爪によって、パイプ耐引抜力と耐回転トルクが安定して大きい。 According to the present invention, the above-mentioned "preliminary processing" that has been required in the conventional art can be completely omitted, and the piping work can be carried out remarkably easily and quickly. Moreover, leakage of refrigerant or the like can be stably prevented.
Furthermore, the pull-out force of the pipe and the rotational torque around the pipe axis are both large. In particular, even for pipes with low hardness and easy plastic deformation in the diameter contraction direction, the two rear and front claws maintain a strong pressure contact state on the flat surface, and the pipe pull-out resistance and rotational torque resistance are stable. and big.

本発明の実施の一形態を示しパイプ接続中の状態を示した断面図である。It is a sectional view showing an embodiment of the present invention and showing a state during pipe connection. パイプ接続完了状態を示す断面図である。It is a sectional view showing a pipe connection completion state. 袋ナットの一例を示す断面図であって、（Ａ）は全体断面図、（Ｂ）は要部拡大断面図である。It is sectional drawing which shows an example of a cap nut, Comprising: (A) is general sectional drawing, (B) is principal part enlarged sectional drawing. ストップリングの一例を示す断面図である。It is a sectional view showing an example of a stop ring. ストップリングの要部拡大断面図である。FIG. 4 is an enlarged cross-sectional view of a main part of the stop ring; 他の例を示したストップリングの要部拡大断面図である。FIG. 6 is an enlarged cross-sectional view of a main part of a stop ring showing another example; 後爪の断面形状を例示した説明図である。It is explanatory drawing which illustrated the cross-sectional shape of the back nail|claw. 前爪の断面形状を例示した説明図である。It is explanatory drawing which illustrated the cross-sectional shape of the front nail|claw. 袋ナットのストレート部及び急勾配テーパ部に薄肉略円筒部の先端頭部が対応している状態を示した要部拡大断面図である。FIG. 4 is an enlarged cross-sectional view of essential parts showing a state in which the tip head portion of the thin-walled substantially cylindrical portion corresponds to the straight portion and the steeply tapered portion of the cap nut. 袋ナットの急勾配テーパ部と緩勾配テーパ部の境目近傍に、薄肉略円筒部の先端頭部が対応している状態を示した要部拡大断面図である。FIG. 4 is an enlarged cross-sectional view of a main part showing a state in which the tip head portion of the thin-walled substantially cylindrical portion corresponds to the vicinity of the boundary between the steep tapered portion and the gentle tapered portion of the cap nut. 袋ナットの緩勾配テーパ部にまで先端頭部が侵入した状態の要部拡大断面図である。FIG. 4 is an enlarged cross-sectional view of a main part in a state in which the tip head has entered the gently tapered portion of the cap nut. さらに侵入した状態の要部拡大断面図である。It is an enlarged cross-sectional view of a main part in a state of further intrusion. 先端頭部が最終侵入位置に到達した接続完了状態を示す要部拡大断面図である。FIG. 10 is an enlarged cross-sectional view of a main part showing a connection completion state in which the tip head has reached the final entry position; 作用説明のための、図13の要部拡大図である。FIG. 14 is an enlarged view of a main part of FIG. 13 for explaining the operation; 従来例を示す断面図である。FIG. 10 is a cross-sectional view showing a conventional example; 別の従来例を示す断面図である。FIG. 10 is a sectional view showing another conventional example;

以下、図示の実施の形態に基づき本発明を詳説する。
図１～図５に示す実施の形態に於て、本発明に係る管継手Ｊは、フレア継手本体１と袋ナット２とストップリング３を具備し、さらに、被接続用パイプＰの先端には（従来のフレア加工を全く省略して）ストレート状先端部10を有している。 BEST MODE FOR CARRYING OUT THE INVENTION The present invention will be described in detail below based on the illustrated embodiments.
In the embodiment shown in FIGS. 1 to 5, a pipe joint J according to the present invention comprises a flare joint body 1, a cap nut 2 and a stop ring 3. It has a straight tip 10 (omitting the conventional flaring altogether).

フレア継手本体１は、古くから使用されてきたものであって、図15に示したフレア継手本体ｈと同様のものであって、先端縮径勾配面５を有する。つまり、流路孔６が貫設された接続筒部７の先端に先端縮径勾配面５が形成されている。
また、全体形状は、ストレート状、Ｔ字型、Ｙ字型、十字型等自由であるが、図１，図２の図外に存在する他の接続端部の形状は、図１，図２と同様の接続筒部７を有していても、あるいは、テーパ雄ネジ，平行雌ネジ，溶接用筒部等を有していても、自由である。
要するに、図１，図２に示すように少なくとも１個の接続筒部７を備え、また、図１，図２の図例では、上記勾配面５の基端縁に連設した短いストレート部８を介して、平行ネジの雄ネジ部９を、上記接続筒部７が有している。このフレア継手本体１の材質としては、黄銅（真鍮）が好適である。 The flare joint main body 1 has been used for a long time, and is similar to the flare joint main body h shown in FIG. In other words, the leading end diameter reducing slope surface 5 is formed at the leading end of the connecting tube portion 7 through which the passage hole 6 is provided.
The overall shape may be straight, T-shaped, Y-shaped, cross-shaped, or the like. It is free to have the same connection tube portion 7 as in the above, or to have a tapered male thread, a parallel female thread, a welding tube portion, or the like.
In short, as shown in FIGS. 1 and 2, at least one connecting tube portion 7 is provided, and in the examples of FIGS. The connection tube portion 7 has a male screw portion 9 of a parallel screw through. A suitable material for the flare joint main body 1 is brass.

袋ナット２は、（図１～図３に示すように、）軸心方向に孔部11が貫設され、この孔部11の基端には、上記雄ネジ部９が螺着される雌ネジ部12を有し、その雌ネジ部12から先端に向かって、順次、軸心方向に小さな幅寸法Ｗ₁₃のシール溝13、第１同一径部（第１ストレート部）14Ａ、第２同一径部（第２ストレート部）14Ｂ、段付部15、小幅寸法Ｗ₁₆の短ストレート部16、先端縮径テーパ部17、及び、（被接続パイプＰの外径よりも僅かに大きい内径寸法の）ストレート部18が、形成される。 The cap nut 2 has a hole 11 extending axially (as shown in FIGS. 1 to 3), and the proximal end of the hole 11 is a female screw into which the male threaded portion 9 is screwed. A seal groove ₁₃ having a small width dimension W13, a first same diameter portion (first straight portion) 14A, a second same diameter portion (first straight portion) 14A, and a second same A diameter portion (second straight portion) 14B, a stepped portion 15, a short straight portion 16 with a small width dimension W ₁₆ , a tapered portion 17 with a reduced diameter at the tip, and an inner diameter dimension slightly larger than the outer diameter of the connected pipe P ) a straight portion 18 is formed.

ストレート部18には、凹溝部19が形成され、Ｏリング等のシール48が装着される。また、シール溝13には別のＯリング等のシール46が装着される。前記第１同一径部14Ａは第２同一径部14Ｂよりも、僅かに大きい内径寸法に設定する。
上記孔部11の同一径部14Ａ，14Ｂ、段付部15、短ストレート部16と先端縮径テーパ部17をもって、ストップリング３を収納するための収納空間部Ｅを形成している。この袋ナット２の材質は、黄銅（真鍮）、又は、アルミニウムとする。 A groove portion 19 is formed in the straight portion 18, and a seal 48 such as an O-ring is attached. Also, another seal 46 such as an O-ring is mounted in the seal groove 13 . The first same-diameter portion 14A is set to have an inner diameter slightly larger than that of the second same-diameter portion 14B.
The same diameter portions 14A and 14B of the hole portion 11, the stepped portion 15, the short straight portion 16 and the tapered portion 17 with reduced diameter at the tip form a storage space portion E for storing the stop ring 3. As shown in FIG. The cap nut 2 is made of brass or aluminum.

そして、図３（Ｂ）に示すように、袋ナット２の孔部11に於て、先端縮径テーパ部17が、基端側急勾配テーパ部17Ａと先端側緩勾配テーパ部17Ｂ等をもって、構成されている。また、最奥当り勾配部17Ｃを付加するも好ましい。
なお、図３（Ｂ）に示したように、段付部15と短ストレート部16の角部を、アール状面取りｒとする。
なお、僅かに内径寸法を相違した前記第１・第２同一径部14Ａ，14Ｂをもって、同一径部（ストレート部）14とした場合を、図３に於て、説明したが、所望により、第１同一径部14Ａと第２同一径部14Ｂとを全く同一内径としても良い場合もある。 Then, as shown in FIG. 3(B), in the hole 11 of the cap nut 2, the tapered portion 17 with reduced diameter at the tip has a steep tapered portion 17A on the proximal side and a gentle tapered portion 17B on the distal end side. It is configured. Also, it is preferable to add the deepest contact slope portion 17C.
As shown in FIG. 3B, the corners of the stepped portion 15 and the short straight portion 16 are chamfered in a rounded shape r.
In FIG. 3, the case where the first and second same diameter portions 14A and 14B having slightly different inner diameters are used as the same diameter portion (straight portion) 14 has been described. In some cases, the first same diameter portion 14A and the second same diameter portion 14B may have exactly the same inner diameter.

次に、ストップリング３について説明する。図４、及び、図１～３に示すように、ストップリング３は、袋ナット２の収納空間部Ｅに内装される。このストップリング３は略短円筒型であって、外周面が、基端から中間域までは、袋ナット２の孔部11のストレート部14に摺動可能に嵌合する基本外径部24と、段付部25を介して先端側に連設された小径かつ先端へ緩やかに拡径テーパ状の薄肉略円筒部35とを、有する。
また、内周面27は、軸心方向中間に基本内径部28を有し、パイプＰは、（図１に示すように）この基本内径部28に挿入される。 Next, the stop ring 3 will be explained. As shown in FIG. 4 and FIGS. 1 to 3, the stop ring 3 is installed inside the storage space E of the cap nut 2. As shown in FIG. The stop ring 3 has a substantially short cylindrical shape, and has a basic outer diameter portion 24 that is slidably fitted in the straight portion 14 of the hole portion 11 of the cap nut 2 from the base end to the intermediate region of the outer peripheral surface. , and a tapered thin-walled substantially cylindrical portion 35 having a small diameter and gradually increasing in diameter toward the distal end, connected to the distal end side via the stepped portion 25 .
The inner peripheral surface 27 also has a basic inner diameter 28 in the middle in the axial direction, into which the pipe P is inserted (as shown in FIG. 1).

さらに、基本内径部28の基端部は、小径内周面部29Ａを有する内突隆部29が連設される。この内突隆部29の（軸心直交面状の）一端面が段付面30となる。
32は、アール（凸）状圧接勾配面であり、ストップリング３の基端に形成され、図１，図２に示す如く、継手本体１の先端縮径勾配面５に圧接して、メタルタッチで密封作用をなす。 Further, the base end portion of the basic inner diameter portion 28 is continuously provided with an inner protruding portion 29 having a small diameter inner peripheral surface portion 29A. One end surface of the inner protruding portion 29 (on a surface orthogonal to the axis) serves as a stepped surface 30 .
Reference numeral 32 denotes a radiused (convex) pressure contact gradient surface, which is formed at the proximal end of the stop ring 3 and, as shown in FIGS. to provide a sealing effect.

ところで、アール状圧接勾配面32の内周端縁と、前記小径内周面部29Ａとの交叉部位に於て、円環状小突条40が設けられている。
具体的に説明すれば、図１，図２に示したように、継手本体１の先端縮径勾配面５の先端と、継手本体孔部６とによって形成された円環状先端エッジ部20に対し、内径側から引掛ける円環状小突条40を、ストップリング３が有する。 By the way, an annular small ridge 40 is provided at the intersection of the inner peripheral edge of the radius pressure contact gradient surface 32 and the small diameter inner peripheral surface portion 29A.
Specifically, as shown in Figs. , the stop ring 3 has an annular small projection 40 hooked from the inner diameter side.

図４から明らかなように、この小突条40は、その断面形状が横倒三角形であり、しかも、アール（凸）状の圧接勾配面32の内端縁を、小アール凹部21を介して外方へ反転した小斜辺と、小径内周面部29Ａとによって、横倒三角形に構成している。
このように、継手本体１の円環状先端エッジ部20に対し、円環状小突条40を、内径側から、図１，図２に示すように、引掛け状とすることで、ストップリング３の基端部が、過大にラジアル外方へ変形することを阻止できる。 As is clear from FIG. 4, the small ridge 40 has a cross-sectional shape of an inverted triangle, and furthermore, the inner edge of the rounded (convex) pressure contact gradient surface 32 is pushed through the small rounded concave portion 21. The outwardly inverted small oblique side and the small-diameter inner peripheral surface portion 29A form a laterally inverted triangle.
As shown in FIGS. 1 and 2, the annular small ridge 40 is hooked from the annular distal end edge portion 20 of the joint body 1 from the inner diameter side in this way, so that the stop ring 3 can be can be prevented from deforming excessively radially outward.

そして、図４に示すように、ストップリング３のパイプ挿入孔部３Ａの少なくとも奥方部位31を、奥方縮径テーパ状に形成する。つまり、図４に於て、極めて小さな勾配角度θ───例えば、０．５°≦θ≦２°───をもって、少なくとも奥方部位31をテーパ状に形成し、図２に示したパイプ挿入完了状態で、パイプＰの先端部10が、パイプ挿入孔部３Ａの内周面27の奥方部位31にて圧接するよう構成する。 Then, as shown in FIG. 4, at least the inner portion 31 of the pipe insertion hole portion 3A of the stop ring 3 is formed in a tapered shape with a reduced inner diameter. That is, in FIG. 4, at least the inner portion 31 is tapered with a very small inclination angle .theta.--for example, 0.5.degree. In the completed state, the distal end portion 10 of the pipe P is configured to press against the deep portion 31 of the inner peripheral surface 27 of the pipe insertion hole portion 3A.

そして、ストップリング３は、先端側に塑性変形可能な薄肉略円筒部35を一体に有する。かつ、この薄肉略円筒部35の先端頭部37には、パイプ引抜阻止用爪部36が設けられる。
図５又は図６に、拡大断面をもって示すように、この爪部36は、微小間隔Ｗ₃₆をもって配設された後爪36Ｂと前爪36Ｆにて、構成される。
なお、薄肉略円筒部35は、先端方向へ拡径状の円錐筒型とする（図４，図５，図６参照）。 The stop ring 3 integrally has a plastically deformable thin substantially cylindrical portion 35 on the distal end side. In addition, a tip portion 37 of the thin-walled substantially cylindrical portion 35 is provided with a claw portion 36 for preventing pipe withdrawal.
As shown in the enlarged cross section of FIG. 5 or 6, the claw portion ₃₆ is composed of a rear claw 36B and a front claw 36F which are arranged with a minute gap W36.
In addition, the thin-walled substantially cylindrical portion 35 has a conical cylindrical shape whose diameter expands toward the distal end (see FIGS. 4, 5, and 6).

また、図１，図２，図４に於ける先端（右）方向を、「前方」と見ることによって、後爪36Ｂ・前爪36Ｆと呼称する。
そして、図７と図５に示すように、後爪36Ｂの断面形状は、直線状第１先端辺41を上辺として有する台形乃至略台形である。なお、図７は、図４のＸ部を拡大して示した拡大断面図であると、見ることができる。 1, 2 and 4 are referred to as rear claws 36B and front claws 36F by viewing the direction of the leading end (right) as "forward".
As shown in FIGS. 7 and 5, the cross-sectional shape of the rear claw 36B is trapezoidal or substantially trapezoidal having the linear first tip side 41 as its upper side. 7 can be viewed as an enlarged cross-sectional view showing the X portion of FIG. 4 in an enlarged manner.

図７（ａ）は後爪36Ｂの断面形状が台形の場合を示し、図７（ｂ）では左右斜辺が凹状弯曲状の略台形を示し、図７（ｃ）では台形の左右斜辺の内の後方斜辺が急峻であり、前方斜辺は凹状弯曲状である場合を例示している。 FIG. 7(a) shows a case where the cross-sectional shape of the rear claw 36B is trapezoidal, FIG. 7(b) shows a substantially trapezoid with concavely curved left and right oblique sides, and FIG. A case is illustrated in which the rear oblique side is steep and the front oblique side is concavely curved.

また、図８と図５に示すように、前爪36Ｆの断面形状は、直線状第２先端辺42を上辺として有する台形乃至略台形である。なお、図８は、図４のＸ部を拡大して示した拡大断面図であると言える。 As shown in FIGS. 8 and 5, the cross-sectional shape of the front claw 36F is trapezoidal or substantially trapezoidal having the linear second tip side 42 as its upper side. In addition, it can be said that FIG. 8 is an enlarged cross-sectional view showing the X section of FIG. 4 in an enlarged manner.

図８（ａ）は前爪36Ｆの断面形状が台形の場合を示し、図８（ｂ）では台形の内の前方斜辺が急峻な台形を示す。図８（ｃ）では台形の左右斜辺の内の前方斜辺が急峻であり、後方斜辺は凹状弯曲状の場合を例示する。
いずれにせよ、後爪36Ｂと前爪36Ｆのいずれも、その断面形状は、上辺が直線状であり、いわば「テーブルマウンティン型」と呼ぶことも可能である。 FIG. 8(a) shows a case where the cross-sectional shape of the front claw 36F is trapezoidal, and FIG. 8(b) shows a trapezoid with a steep front oblique side. FIG. 8C illustrates a case where the front oblique side of the left and right oblique sides of the trapezoid is steep and the rear oblique side is concavely curved.
In any case, both the rear claw 36B and the front claw 36F have a cross-sectional shape with a linear upper side, and can be called a "table mounting type".

（既に述べたが）後爪36Ｂと前爪36Ｆを、先端に有する薄肉略円筒部35は、全体として、先端方向に拡径状の円錐筒型であるが、その円筒部35の先端に付設された、後爪36Ｂの第１先端辺41と、前爪36Ｆの第２先端辺42は、相互に平行に形成され、自由状態下で、図５のように、前爪36Ｆの第２先端辺42よりも後爪36Ｂの第１先端辺41を微小寸法ΔＨだけ、ラジアル内方向となるように設定する。（いわば、平行段違いに配設している。） (Already described) The thin substantially cylindrical portion 35 having the rear claw 36B and the front claw 36F at the tip thereof has a conical cylindrical shape with a diameter expanding toward the tip as a whole. The first tip side 41 of the rear claw 36B and the second tip side 42 of the front claw 36F are formed parallel to each other, and under the free state, as shown in FIG. The first tip side 41 of the rear claw 36B is set radially inward from the side 42 by a minute dimension ΔH. (In other words, they are arranged parallel to each other.)

また、図６に示すように、前述の微小寸法ΔＨを極微小乃至零とすることも、好ましい場合がある。
なお、図５の先端頭部37の最先端ラジアル外方部38は丸味のあるアール形状としている。また、図６の先端頭部37は、先端縮径状斜面部43を有する。 Also, as shown in FIG. 6, it may be preferable to set the aforementioned minute dimension ΔH to be extremely small or zero.
Note that the distal end radial outer portion 38 of the tip head portion 37 in FIG. 5 has a rounded arc shape. Also, the tip head portion 37 of FIG.

図６に示した自由状態の薄肉略円筒部35は、袋ナット２の螺進に伴って、順次、図９，図10，図11，図12及び図13・図14のように、変形してゆく。
即ち、被接続パイプＰのストレート状先端部10の外周面10Ａに対し、ストップリング３の後爪36Ｂの第１先端辺41と、前爪36Ｆの第２先端辺42が、縮径方向（ラジアル内方向）に、移動して、最終の接続完了状態では、図13と図14に示す如く、矢印Ｐ₄₁，Ｐ₄₂をもって示した大きな圧接面圧力をもって、強力圧接状態となって、大きなパイプ引抜抵抗力Ｚを発生する。 As the cap nut 2 is screwed, the thin cylindrical portion 35 in the free state shown in FIG. 6 is deformed sequentially as shown in FIGS. to go
That is, the first tip side 41 of the rear claw 36B of the stop ring 3 and the second tip side 42 of the front claw 36F of the stop ring 3 are aligned in the radial direction with respect to the outer peripheral surface 10A of the straight tip portion 10 of the connected pipe P. 13 and 14. In the final connection state, as shown in FIG. 13 and FIG. 14, a strong pressure contact state is created with a large pressure contact surface pressure indicated by arrows P ₄₁ and P ₄₂ , and a large pipe is pulled out. Generates resistance Z.

そして、後爪36Ｂ・前爪36Ｆがパイプ外周面10Ａに対し強力圧接状態では、この後爪36Ｂ・前爪36Ｆから成る爪部36が、冷媒等の流体に対する密封機能を十分に発揮して、図２に示したように、ストップリング３の内周面とパイプ外周面10Ａとの間、及び、ストップリング３の外周面と袋ナット２の孔部11の内周面との間に、シール材が省略される。即ち、従来例を示した図16におけるＯリング58が省略されている。 When the rear claws 36B and the front claws 36F are strongly pressed against the outer peripheral surface 10A of the pipe, the claw portion 36 consisting of the rear claws 36B and the front claws 36F sufficiently exerts a sealing function against fluid such as refrigerant. As shown in FIG. 2, seals are provided between the inner peripheral surface of the stop ring 3 and the pipe outer peripheral surface 10A and between the outer peripheral surface of the stop ring 3 and the inner peripheral surface of the hole 11 of the cap nut 2. material is omitted. That is, the O-ring 58 in FIG. 16 showing the conventional example is omitted.

ところで、（既に述べたように）袋ナット２の孔部11の先端縮径テーパ部17は、（短ストレート部16につづく）基端側急勾配テーパ部17Ａと、先端側緩勾配テーパ部17Ｂをもって、構成されている。図６に示した自由状態の薄肉略円筒部35の先端頭部37の最外径部37Ａは、短ストレート部16の内径寸法と同一径、乃至、僅かに小さく設定しておく。しかも、斜面部43が形成されているので、図９の状態まで容易に先端頭部37を侵入させることができる。つまり、先端頭部37の最先端アール部38Ａが、（図９に示したように）急勾配テーパ部17Ａに当る。 By the way, (as already described), the tapered portion 17 of the hole portion 11 of the cap nut 2 has a steep taper portion 17A on the proximal end side (following the short straight portion 16) and a gently tapered portion 17B on the distal end side. It is composed of The outermost diameter portion 37A of the tip head portion 37 of the thin-walled substantially cylindrical portion 35 in the free state shown in FIG. Moreover, since the inclined surface portion 43 is formed, the tip head portion 37 can be easily inserted into the state shown in FIG. That is, the distal radius 38A of the tip head 37 abuts the steep taper 17A (as shown in FIG. 9).

引続き袋ナット２を螺進させれば、アール部38Ａは、急勾配テーパ部17Ａと緩勾配テーパ部17Ｂの境目に到達し（図10参照）、このとき、パイプＰの外周面10Ａに対して、後爪36Ｂの第１先端辺41と、前爪36Ｆの第２先端辺42が、接触を開始する。
引続き袋ナット２を螺進させてゆけば、図11及び図12に示すように、斜面部43が、緩勾配テーパ部17Ｂに摺接しつつ、かつ、同一勾配（傾斜角度）を保持しつつ、先端頭部37は、ラジアル内方向に動き、パイプＰが局部的に縮径変形を起こす。さらに、袋ナット２を螺進させてゆけば、図13と図14に示した最終締付状態となる。 If the cap nut 2 is continued to be screwed, the rounded portion 38A reaches the boundary between the steep taper portion 17A and the gently taper portion 17B (see FIG. 10). , the first tip side 41 of the rear claw 36B and the second tip side 42 of the front claw 36F start to come into contact with each other.
As the cap nut 2 is continued to be screwed, as shown in FIGS. 11 and 12, the slope portion 43 is brought into sliding contact with the gently sloped tapered portion 17B while maintaining the same slope (inclination angle). The tip head 37 moves radially inward, causing the pipe P to locally shrink in diameter. Further screwing the cap nut 2 results in the final tightening state shown in FIGS.

銅（Ｃｕ）等の比較的柔らかいパイプＰは、局部的に縮径変形を起こして、（図11から）図12を経て図13・図14のような形状となるが、第１先端辺41と第２先端辺42は相互に平行を保ちつつ（図６参照）、パイプＰの外周面10Ａに対して、強力圧接状態となって、大きなパイプ引抜抵抗力Ｚを発揮する。
図13と図14に於て、破線Ｙは、パイプＰの軸心と平行な基準線を示す。即ち、この基準線（破線）Ｙを基準として、パイプＰの外周面10Ａが如何に変形しているか、及び、後爪36Ｂと前爪36Ｆの傾斜姿勢と相対的位置関係を明らかに示すためのものである。 A relatively soft pipe P made of copper (Cu) or the like is locally deformed to reduce its diameter, and becomes a shape as shown in FIGS. 13 and 14 through FIG. and the second tip side 42 are kept parallel to each other (see FIG. 6), and are strongly pressed against the outer peripheral surface 10A of the pipe P, exhibiting a large pipe pull-out resistance Z. As shown in FIG.
13 and 14, dashed line Y indicates a reference line parallel to the axis of pipe P. In FIG. That is, using this reference line (broken line) Y as a reference, it is possible to clearly show how the outer peripheral surface 10A of the pipe P is deformed, and the tilted attitude and relative positional relationship between the rear claw 36B and the front claw 36F. It is.

図13と図14に示した接続完了状態に於て、後爪36Ｂ及び前爪36Ｆは、略等しい圧接面圧力Ｐ₄₁，Ｐ₄₂をもってパイプ外周面10Ａに対して強力圧接状態となり、（図14に示した）後爪36Ｂによる引抜抵抗力Ｚ₄₁と、前爪36Ｆによる引抜抵抗力Ｚ₄₂は、略相等しくなる。
即ち、図14に於て、次式が成立する。
Ｚ＝Ｚ₄₁＋Ｚ₄₂
Ｚ₄₁≒Ｚ₄₂
さらに、言い換えれば、（図14に示すように、）全体パイプ引抜抵抗力を示すベクトルＺに関して、後爪36Ｂと前爪36Ｆは、各々、ベクトルＺ₄₁とベクトルＺ₄₂をもって示すように、相等しく分担する。 13 and 14, the rear claw 36B and the front claw 36F are strongly pressed against the outer peripheral surface 10A of the pipe with substantially equal pressing surface pressures _P41 and _P42 (Fig. 14). ) are approximately equal to the pull-out resistance Z ₄₁ by the rear claw 36B and the pull-out resistance Z ₄₂ by the front claw 36F.
That is, in FIG. 14, the following formula holds.
Z = _Z41 + _Z42
_Z41 ≒ _Z42
Further, in other words, with respect to vector Z representing the overall pipe pull resistance force (as shown in FIG. 14), rear pawl 36B and front pawl 36F are equivalent, as indicated by vectors Z ₄₁ and Z ₄₂ , respectively. to share the load.

具体的に、後爪36Ｂの引抜抵抗力（ベクトル）Ｚ₄₁と、前爪36Ｆの引抜抵抗力（ベクトル）Ｚ₄₂を、略等しくするための構成を、以下、説明すると、自由状態では、図６に示したように、後爪36Ｂの第１先端辺41と、前爪36Ｆの第２先端辺42を、微小（段差）寸法ΔＨをもって相互平行として、さらに、第１先端辺41を第２先端辺42よりもラジアル内方として、配設しておく。
そして、強力圧接状態（接続完了状態）においては、図13と図14に示す如く、第２先端辺42が第１先端辺41よりもラジアル内方向に突出状とさせ、又は、両先端辺42，41をラジアル方向同一位置となるように、袋ナット２の先端縮径テーパ部17の先端側の傾斜角度───つまり、図９～図14では、緩勾配テーパ部17Ｂの傾斜角度───と、先端頭部37の形状と寸法を、決定する。 Specifically, a configuration for making the pull-out resistance (vector) Z41 of the rear claw 36B and the pull-out resistance (vector) _Z42 of the front claw _36F substantially equal will be described below. 6, the first tip side 41 of the rear claw 36B and the second tip side 42 of the front claw 36F are parallel to each other with a small (step) dimension ΔH, and the first tip side 41 is set to the second tip side. It is arranged radially inward of the tip side 42 .
13 and 14, in the strong press-contact state (connection completed state), the second tip side 42 projects radially inward from the first tip side 41, or both tip sides 42 , 41 at the same position in the radial direction, the angle of inclination of the leading end side of the tapered portion 17 with reduced diameter at the tip of the cap nut 2—that is, the angle of inclination of the gentle taper portion 17B in FIGS. - and the shape and dimensions of the tip head 37 are determined.

特に、先端頭部37の形状と寸法について、さらに具体的に説明すれば、先端頭部37の外周面（斜面部）43は、緩勾配テーパ部17Ｂに圧接して安定姿勢を維持するに十分なアキシャル方向寸法をもってストレート傾斜状に形成する。そして、後爪36Ｂと前爪36Ｆを結ぶ直線（図示省略）が、図14（図13）に示した破線Ｙと平行状として、乃至、先端方向（前方）へゆくにしたがって、破線Ｙにしだいに接近するように、後爪36Ｂと前爪36Ｆのラジアル方向位置を、設定する。
なお、図５に示す形状の場合には、先端頭部37が、ラジアル内方へやや大き目に、首を振るように、先端縮径テーパ部17の緩勾配テーパ部17Ｂ、及び、最奥当り勾配部17Ｃの寸法と形状を設定する。 In particular, the shape and dimensions of the tip head portion 37 will be explained in more detail. It is formed in a straight slant shape with an axial dimension. A straight line (not shown) connecting the rear claw 36B and the front claw 36F is parallel to the dashed line Y shown in FIG. The radial positions of the rear claw 36B and the front claw 36F are set so as to approach .
In addition, in the case of the shape shown in FIG. 5, the tip head portion 37 swings slightly radially inward, and the gently sloped tapered portion 17B of the tip diameter reduction taper portion 17 and the deepest contact Set the size and shape of the sloped portion 17C.

そして、ストップリング３の薄肉略円筒部35に於て、その外周面に小突起33が付設されている。図例では、小突起33は略台形状である。
この小突起33は、図12、及び、図13に示すように、袋ナット２の短ストレート部16に対応し、受圧状態下で、薄肉略円筒部35が過大に拡径変形しようとした際、小突起33が袋ナット２の孔部11の内面に当接して、それを阻止する。特に、小突起33は、孔部11の短ストレート部16に対応している（図13参照）。 A small protrusion 33 is attached to the outer peripheral surface of the thin-walled substantially cylindrical portion 35 of the stop ring 3 . In the illustrated example, the small protrusion 33 is substantially trapezoidal.
12 and 13, this small projection 33 corresponds to the short straight portion 16 of the cap nut 2, and when the thin approximately cylindrical portion 35 tries to expand and deform excessively under pressure, , the small projection 33 contacts the inner surface of the hole 11 of the cap nut 2 to block it. In particular, the small protrusion 33 corresponds to the short straight portion 16 of the hole 11 (see FIG. 13).

図９，図10，図11に示した挿入初期から中期までは、薄肉略円筒部35は、孔部11の内周面に対して先端頭部37のみが摺接するので、特に、袋ナット２を作業工具で回転させるときの回転トルクは小さく、軽快に作業できる利点がある。
そして、図12及び図13に示した最終近く、及び、最終締付状態下では、小突起33が短ストレート部16に当接して、薄肉略円筒部35のセンタリングを行うという利点もある。 9, 10, and 11, from the initial stage to the middle stage of insertion shown in FIGS. There is an advantage that the rotation torque is small when the is rotated by the work tool, and the work can be performed lightly.
12 and 13, and in the final tightening state, there is also the advantage that the small projection 33 abuts against the short straight portion 16 to center the thin substantially cylindrical portion 35. As shown in FIG.

なお、図１，図２に於て、Ｏリング等のシール46，48が設けられているが、冷媒等の流体の外部漏洩阻止のためではなく、本発明における圧接部位や塑性変形部位等の応力腐食を防止するためのものであり、耐酸素性ゴムが望ましい。また、本発明は、図示の実施の形態に限らず、設計変更自由であって、例えば、袋ナット２の短ストレート部16を省略し、あるいは、緩やかなテーパ状とするも、自由である。 In FIGS. 1 and 2, seals 46 and 48 such as O-rings are provided. It is intended to prevent stress corrosion, and oxygen-resistant rubber is desirable. Moreover, the present invention is not limited to the illustrated embodiment, and the design can be freely changed. For example, the short straight portion 16 of the cap nut 2 can be omitted or gently tapered.

本発明は、以上詳述したように、雄ネジ部９と先端縮径勾配面５を有するフレア継手本体１と、上記雄ネジ部９に螺着される雌ネジ部12を孔部11の基端に有し、かつ、該孔部11の中間には同一径部14と段付部15と先端縮径テーパ部17とを有する収納空間部Ｅを形成した袋ナット２と、該収納空間部Ｅに内装されると共に、上記先端縮径勾配面５に圧接する基端側圧接勾配面32を有すると共に、先端側には塑性変形可能な薄肉略円筒部35とその先端頭部37のパイプ引抜阻止用爪部36とを有するストップリング３と、を具備した管継手に於て、上記爪部36は、微小間隔Ｗ₃₆をもって配設された後爪36Ｂと前爪36Ｆにて構成され、上記後爪36Ｂの断面形状は、直線状第１先端辺41を上辺として有する台形乃至略台形であり、上記前爪36Ｆの断面形状は、直線状第２先端辺42を上辺として有する台形乃至略台形であり、被接続パイプＰのストレート状先端部10の外周面10Ａに対し、上記ストップリング３の上記後爪36Ｂの第１先端辺41と、上記前爪36Ｆの第２先端辺42が、上記袋ナット２の螺進に伴って、強力圧接状態となって、パイプ引抜抵抗力Ｚを発生するよう構成したので、袋ナット２を螺進してゆく際にストップリング３は共廻りせず、ストップリング３はパイプＰと一体状に静止を続ける。従って、継手本体１の勾配面５と、アール状圧接勾配部32の間での相対的スリップの発生を防止できる。従来の（図16に示した）管継手における未解決の課題（ｉ）として述べた、特別な治具を使用した「予備加工」が省略できる。
これに伴って、配管接続現場での作業能率が飛躍的に改善される。
さらに、パイプ耐引抜力は、台形乃至略台形の第１先端辺41と第２先端辺42による面的な強力圧接状態が得られるため、従来の管継手（図16参照）における三角形断面の爪部61よりも、十分に強力となった。
配管工事完了後、パイプＰをその軸心廻りに回転させる外力が作用した際、（線圧接ではなく）面的圧接であるため、しかも、後爪36Ｂと前爪36Ｆのダブル強力圧接であるため、爪部36とパイプ外周面10Ａとの間のメタルシール性が確実に維持される。 As described in detail above, the present invention comprises a flare joint main body 1 having a male threaded portion 9 and a tapered tip surface 5, and a female threaded portion 12 screwed onto the male threaded portion 9 at the base of a hole portion 11. a cap nut 2 formed at an end thereof and formed with a storage space E having a same diameter portion 14, a stepped portion 15 and a reduced diameter taper portion 17 in the middle of the hole portion 11; E and has a base-side pressure-contact sloped surface 32 that presses against the tip diameter-reducing sloped surface 5, and a plastically deformable thin-walled substantially cylindrical portion 35 and its tip head portion 37 on the tip side to pull out the pipe. In a pipe joint provided with a stop ring 3 having a blocking pawl portion 36, the pawl portion ₃₆ is composed of a rear pawl 36B and a front pawl 36F arranged with a minute gap W36 therebetween. The cross-sectional shape of the rear claw 36B is trapezoidal or substantially trapezoidal having the linear first tip side 41 as its upper side, and the cross-sectional shape of the front claw 36F is trapezoidal or substantially trapezoidal having the linear second tip side 42 as its upper side. The first tip side 41 of the rear claw 36B of the stop ring 3 and the second tip side 42 of the front claw 36F of the stop ring 3 are aligned with the outer peripheral surface 10A of the straight tip portion 10 of the pipe P to be connected. As the cap nut 2 is screwed, it becomes a strong pressure contact state to generate a pipe pull-out resistance Z, so that the stop ring 3 does not rotate together when the cap nut 2 is screwed. The stop ring 3 remains stationary together with the pipe P. Therefore, it is possible to prevent the occurrence of relative slippage between the sloped surface 5 of the joint body 1 and the radius pressure contact sloped portion 32 . It is possible to omit the "preliminary processing" using a special jig described as the unsolved problem (i) in the conventional pipe joint (shown in FIG. 16).
Along with this, the work efficiency at the piping connection site is dramatically improved.
Furthermore, as for the pipe pull-out resistance, since a planar strong pressure contact state is obtained by the trapezoidal or substantially trapezoidal first tip side 41 and the second tip side 42, it is superior to the conventional pipe joint (see FIG. 16) with triangular cross-section nails. More powerful than Part 61.
After completion of the piping work, when an external force acts to rotate the pipe P around its axis, it is surface pressure contact (rather than line pressure contact) and double strong pressure contact of the rear claws 36B and front claws 36F. , the metal sealing property between the claw portion 36 and the outer peripheral surface 10A of the pipe is reliably maintained.

また、上記爪部36の上記後爪36Ｂ・前爪36Ｆが上記袋ナット２の螺進に伴って上記外周面10Ａに強力圧接状態で、上記後爪36Ｂと前爪36Ｆが密封機能を発揮して、ストップリング３の内周面と外周面にシール材が省略されている構成であるので、特に耐冷媒用の高価なシール材（従来の図16に示したＯリング58）が省略できることとなり、さらに、ストップリング３に面倒なシール用凹溝の加工も省略できる。 Further, the rear claw 36B and the front claw 36F of the claw portion 36 are strongly pressed against the outer peripheral surface 10A as the cap nut 2 is screwed, and the rear claw 36B and the front claw 36F perform a sealing function. In addition, since the seal material is omitted from the inner peripheral surface and the outer peripheral surface of the stop ring 3, it is possible to omit the expensive seal material (conventional O-ring 58 shown in FIG. 16) for refrigerant resistance. Furthermore, the troublesome processing of grooves for sealing in the stop ring 3 can be omitted.

また、上記袋ナット２の上記孔部11において、先端縮径テーパ部17が、基端側急勾配テーパ部17Ａと先端側緩勾配テーパ部17Ｂをもって、構成されているので、袋ナット２の螺進回数を減少して、配管接続作業の能率向上を図り得る。即ち、薄肉略円筒部35が小さい力で縮径できる袋ナット２の螺進初期（図９から図10までの状態参照）にあっては、僅かな袋ナット２の回転で縮径させて、袋ナット２の螺進全回数を減らすことが可能となる。
その後、後爪36Ｂと前爪36Ｆがパイプ外周面10Ａに接触した後（図11～図13参照）は、先端側緩勾配テーパ部17Ｂにてゆっくりと縮径させることができて、合理的に螺進作業を行い得る。 Further, in the hole portion 11 of the cap nut 2, the tapered portion 17 with reduced diameter at the distal end is composed of the steep taper portion 17A on the proximal end side and the gentle taper portion 17B on the distal end side. By reducing the number of advances, the efficiency of pipe connection work can be improved. That is, at the initial stage of threading of the cap nut 2 (see the states of FIGS. 9 and 10), in which the diameter of the thin cylindrical portion 35 can be reduced with a small force, the diameter is reduced by a slight rotation of the cap nut 2. It is possible to reduce the total number of times the cap nut 2 is screwed.
After that, after the rear claw 36B and the front claw 36F come into contact with the outer peripheral surface 10A of the pipe (see FIGS. 11 to 13), the diameter can be gradually reduced at the tip-side gently sloping tapered portion 17B, and rationally Able to do spiral work.

また、上記パイプＰの外周面10Ａに対し、上記後爪36Ｂ及び前爪36Ｆが、上記強力圧接状態において、パイプ引抜抵抗力Ｚを略相等しく分担するよう構成したので、図14に示したように、パイプ引抜抵抗力Ｚは、（Ｚ₄₁＋Ｚ₄₂）として十分大きな値となり、実用上、優れた耐引抜力を発揮する。特に、パイプＰの材質が塑性変形し易い軟らかい場合には、爪部が突き挿さらず、図12から図13，図14のように逃げてしまうが、このような悪条件下であっても、実用上、十分に大きい耐引抜力が得られる。 Further, since the rear claw 36B and the front claw 36F are configured to share the pipe pull-out resistance force Z substantially equally with respect to the outer peripheral surface 10A of the pipe P in the strong pressure contact state, as shown in FIG. In addition, the pipe pull-out resistance Z becomes a sufficiently large value as (Z ₄₁ +Z ₄₂ ), and practically exhibits excellent pull-out resistance. In particular, if the material of the pipe P is soft and easily plastically deformed, the claws will not penetrate and escape as shown in Figs. 12 to 13 and 14. , Practically, a sufficiently large pull-out resistance can be obtained.

また、上記ストップリング３の自由状態において、上記後爪36Ｂの上記第１先端辺41と、上記前爪36Ｆの上記第２先端辺42を、相互に平行として、かつ、上記第１先端辺41を上記第２先端辺42よりもラジアル内方として、配設し、さらに、上記強力圧接状態において、上記第２先端辺42が上記第１先端辺41よりもラジアル内方向に突出状、又は、上記第２先端辺42と上記第１先端辺41がラジアル方向同一位置となるように、上記先端縮径テーパ部17の先端側の傾斜角度と、上記先端頭部37の形状と寸法を、設定したので、後爪36Ｂと前爪36Ｆのいずれか一方が「遊ぶ」ことがなく、各々が略相等しい引抜抵抗力Ｚ₄₁，Ｚ₄₂を、発揮し、全体のパイプ引抜抵抗力Ｚは十分大となって、実用上、優秀な耐引抜力が得られる。特に、パイプＰの材質が塑性変形し易い軟らかい場合には、爪部が突き挿さらず、塑性変形しつつパイプ外周面10Ａが弯曲凹状に逃げてしまう（図12から図13，図14参照）。このような悪条件下であっても、十分に大きい耐引抜力が得られる。 In the free state of the stop ring 3, the first tip side 41 of the rear claw 36B and the second tip side 42 of the front claw 36F are parallel to each other, and the first tip side 41 is radially inward of the second tip side 42, and furthermore, the second tip side 42 protrudes radially inward from the first tip side 41 in the strong pressure contact state, or The angle of inclination of the tapered portion 17 with reduced diameter on the tip side and the shape and dimensions of the tip head portion 37 are set so that the second tip side 42 and the first tip side 41 are at the same position in the radial direction. Therefore, either one of the rear claw 36B and the front claw 36F does not "play", and each exerts substantially equal pull-out resistance Z ₄₁ , Z ₄₂ , and the overall pipe pull-out resistance Z is sufficiently large. As a result, practically excellent pull-out resistance can be obtained. In particular, when the pipe P is made of a soft material that is easily plastically deformed, the claw portion does not penetrate, and the outer peripheral surface 10A of the pipe escapes in a curved concave shape while being plastically deformed (see FIGS. 12 to 13 and 14). . Even under such adverse conditions, a sufficiently high pull-out resistance can be obtained.

また、上記後爪36Ｂと上記前爪36Ｆを先端に有する上記薄肉略円筒部35は、先端方向に拡径状の円錐筒型としたので、袋ナット２の先端縮径テーパ部17に対する、薄肉略円筒部35の外周面の接触面積が、（同一径の円筒型に比較して）少なく、袋ナット２の回転トルクも小さくて済むと共に、回転に要する仕事量（エネルギー）も少なく、袋ナット２の螺進作業性が優れる。さらに、ストップリング３を共回りさせるトルクも減少する。 Further, since the thin-walled substantially cylindrical portion 35 having the rear claw 36B and the front claw 36F at the tip thereof is formed into a conical cylinder shape with a diameter expanding in the tip direction, the tip of the cap nut 2 has a thin thickness with respect to the tapered portion 17 with the reduced diameter at the tip. The contact area of the outer peripheral surface of the substantially cylindrical portion 35 is small (compared to a cylindrical shape with the same diameter), the rotational torque of the cap nut 2 is small, and the amount of work (energy) required for rotation is small. 2 is excellent in spiraling workability. Furthermore, the torque that co-rotates the stop ring 3 is also reduced.

また、受圧状態下で、上記薄肉略円筒部35が、過大拡径変形するのを阻止するための小突起33を、上記薄肉略円筒部35の外周面に付設して、上記小突起33を上記袋ナット２の上記孔部11の内面に当接するように構成したので、受圧状態下で薄肉略円筒部35が異常拡径変形させることなく、薄肉略円筒部35の肉厚を十分に薄くできる。この肉厚が十分に薄いことによって、袋ナット２の回転トルクも小さくて済み、回転に要する仕事量（エネルギー）も減少できて、袋ナット２の螺進作業性が向上する。 In addition, a small projection 33 is provided on the outer peripheral surface of the thin approximately cylindrical portion 35 to prevent the thin approximately cylindrical portion 35 from being deformed to excessively expand its diameter under pressure. Since the cap nut 2 is configured to abut on the inner surface of the hole 11, the thickness of the thin substantially cylindrical portion 35 is made sufficiently thin without causing the thin substantially cylindrical portion 35 to be abnormally expanded and deformed under pressure. can. Since the wall thickness is sufficiently thin, the rotational torque of the cap nut 2 can be reduced, the amount of work (energy) required for rotation can be reduced, and the screwing workability of the cap nut 2 is improved.

また、上記継手本体１の上記先端縮径勾配面５の先端と、継手本体孔部６とによって形成される円環状先端エッジ部20に対し、内径側から引掛ける円環状小突条40を、上記ストップリング３の基端側圧接勾配面32の内周端縁に付設し、該ストップリング３の基端部が、過大にラジアル外方へ変形することを阻止するよう構成したので、継手本体１の勾配面５と、ストップリング３の圧接勾配面32の相互の姿勢が安定し、このメタルタッチ部位の密封性能が安定して確保される。
また、ストップリング３の基端外周面が局部的に拡径して、袋ナット２の螺進を妨げることを、防止できる。 Further, an annular small ridge 40 is hooked from the inner diameter side to an annular tip end edge portion 20 formed by the tip of the tip diameter reducing gradient surface 5 of the joint body 1 and the joint body hole portion 6, Since the stop ring 3 is attached to the inner peripheral edge of the base-side pressure contact sloped surface 32 of the stop ring 3 to prevent the base end portion of the stop ring 3 from being excessively deformed radially outward, the joint body The mutual postures of the sloped surface 5 of the stop ring 3 and the pressing sloped surface 32 of the stop ring 3 are stabilized, and the sealing performance of this metal touch portion is stably ensured.
In addition, it is possible to prevent the outer peripheral surface of the proximal end of the stop ring 3 from locally expanding in diameter and hindering the screwing of the cap nut 2 .

また、上記ストップリング３のパイプ挿入孔部３Ａの少なくとも奥方部位31を、奥方縮径テーパ状に形成し、パイプ挿入完了状態で上記ストレート状先端部10が上記パイプ挿入孔部３Ａの内周面27に圧接するよう構成したので、パイプＰを振らせる方向の外力が作用したとしても、パイプＰはストップリング３に対して、両軸心相互を完全に一致するように維持される。従って、そのような外力がパイプＰに作用した際に、パイプＰを強力に保持している薄肉略円筒部35の先端頭部37を中心として、揺動運動を起こし、後爪36Ｂと前爪36Ｆによる強力圧接状態（掴持状態）が、破壊されることを、防止できる。 Further, at least the inner portion 31 of the pipe insertion hole portion 3A of the stop ring 3 is formed in a tapered shape with a reduced inner diameter, and when the pipe is completely inserted, the straight tip portion 10 tapers to the inner peripheral surface of the pipe insertion hole portion 3A. 27, even if an external force acts to swing the pipe P, the pipe P is maintained with the stop ring 3 so that both axial centers are completely aligned with each other. Therefore, when such an external force acts on the pipe P, the thin cylindrical portion 35 that strongly holds the pipe P causes a rocking motion around the tip head portion 37, causing the rear claw 36B and the front claw to move. It is possible to prevent the strong pressure contact state (gripping state) by 36F from being destroyed.

１フレア継手本体
２袋ナット
３ストップリング
３Ａパイプ挿入孔部
５先端縮径勾配面
６継手本体孔部
９雄ネジ部
10 ストレート状先端部
10Ａ外周面
11 孔部
12 雌ネジ部
14 同一径部
15 段付部
16 短ストレート部
17 先端縮径テーパ部
17Ａ急勾配テーパ部
17Ｂ緩勾配テーパ部
20 先端エッジ部
27 内周面
31 奥方部位
32 基端側圧接勾配面
33 小突起
35 薄肉略円筒部
36 爪部
36Ｂ後爪
36Ｆ前爪
37 先端頭部
40 円環状小突条
41 第１先端辺
42 第２先端辺
Ｅ収納空間部
Ｐパイプ
Ｗ₃₆ 微小間隔
Ｚパイプ引抜抵抗力 REFERENCE SIGNS LIST 1 Flare joint body 2 Cap nut 3 Stop ring 3A Pipe insertion hole 5 Tip diameter reduction slope surface 6 Joint body hole 9 Male screw
10 straight tip
10A outer circumference
11 hole
12 female thread
14 same diameter
15 Stepped part
16 Short straight section
17 Tip reduced diameter taper
17A steep taper
17B gentle taper
20 tip edge
27 Inner surface
31 deep part
32 Proximal pressure slope surface
33 small protrusion
35 Thin almost cylindrical part
36 Claw
36B rear claw
36F front claw
37 tip head
40 Annular ridge
41 1st edge
42 Second tip side E Storage space P Pipe W ₃₆ Minute interval Z Pipe pulling resistance

Claims

a flare joint body (1) having a male threaded portion (9) and a tapered surface (5) with a reduced diameter at the tip;
A female threaded portion (12) screwed onto the male threaded portion (9) is provided at the proximal end of the hole (11), and a portion (14) of the same diameter is provided in the middle of the hole (11). a cap nut (2) forming a storage space (E) having a stepped portion (15) and a reduced diameter tapered portion (17);
A plastically deformable thin substantially cylindrical portion on the distal end side, which is housed in the storage space (E) and has a base end pressure contact gradient surface (32) in pressure contact with the tip diameter reduction gradient surface (5). a stop ring (3) having a (35) and a pipe pull-out prevention claw (36) on its tip head (37);
In a pipe joint equipped with
The claw portion ( ₃₆ ) is composed of a rear claw (36B) and a front claw (36F) spaced apart by a minute distance (W36). The cross-sectional shape of the front claw (36F) is a trapezoid or approximately trapezoid having the top side of the tip side (41), and the top side is the linear second tip side (42),
The first tip side (41) of the rear claw (36B) of the stop ring (3) and the front claw ( 36F), as the cap nut (2) is screwed, the second tip side (42) of the pipe nut (2) is brought into a strong pressure contact state to generate a pipe pull-out resistance (Z) ,
In the hole (11) of the cap nut (2), the tapered portion (17) with reduced diameter at the tip is composed of a steep tapered portion (17A) on the proximal end side and a gentle tapered portion (17B) on the distal end side. A pipe joint characterized by:

a flare joint body (1) having a male threaded portion (9) and a tapered surface (5) with a reduced diameter at the tip;
A female threaded portion (12) screwed onto the male threaded portion (9) is provided at the proximal end of the hole (11), and a portion (14) of the same diameter is provided in the middle of the hole (11). a cap nut (2) forming a storage space (E) having a stepped portion (15) and a reduced diameter tapered portion (17);
A plastically deformable thin substantially cylindrical portion on the distal end side, which is housed in the storage space (E) and has a base end pressure contact gradient surface (32) in pressure contact with the tip diameter reduction gradient surface (5). a stop ring (3) having a (35) and a pipe pull-out prevention claw (36) on its tip head (37);
In a pipe joint equipped with
The claw portion (36) is composed of a rear claw (36B) and a front claw (36F) spaced apart by a minute distance ( _W36 ). The cross-sectional shape of the front claw (36F) is a trapezoid or approximately trapezoid having the top side of the tip side (41), and the top side is the linear second tip side (42),
The first tip side (41) of the rear claw (36B) of the stop ring (3) and the front claw ( 36F), as the cap nut (2) is screwed, the second tip side (42) of the pipe nut (2) is brought into a strong pressure contact state to generate a pipe pull-out resistance (Z),
In the free state of the stop ring (3), the first tip side (41) of the rear claw (36B) and the second tip side (42) of the front claw (36F) are parallel to each other, and the first tip side (41) is arranged radially inward of the second tip side (42),
Further, in the strong pressure contact state, the second tip side (42) protrudes radially inward from the first tip side (41), or the second tip side (42) and the first tip side (42) protrude radially inward. So that (41) is at the same position in the radial direction,
A pipe joint characterized by setting the inclination angle of the distal end side of the reduced diameter tapered portion (17) and the shape and dimensions of the distal head portion (37) .

a flare joint body (1) having a male threaded portion (9) and a tapered surface (5) with a reduced diameter at the tip;
A female threaded portion (12) screwed onto the male threaded portion (9) is provided at the proximal end of the hole (11), and a portion (14) of the same diameter is provided in the middle of the hole (11). a cap nut (2) forming a storage space (E) having a stepped portion (15) and a reduced diameter tapered portion (17);
A plastically deformable thin substantially cylindrical portion on the distal end side, which is housed in the storage space (E) and has a base end pressure contact gradient surface (32) in pressure contact with the tip diameter reduction gradient surface (5). a stop ring (3) having a (35) and a pipe pull-out prevention claw (36) on its tip head (37);
In a pipe joint equipped with
The claw portion (36) is composed of a rear claw (36B) and a front claw (36F) spaced apart by a minute distance ( _W36 ). The cross-sectional shape of the front claw (36F) is a trapezoid or approximately trapezoid having the top side of the tip side (41), and the top side is the linear second tip side (42),
The first tip side (41) of the rear claw (36B) of the stop ring (3) and the front claw ( 36F), as the cap nut (2) is screwed, the second tip side (42) of the pipe nut (2) is brought into a strong pressure contact state to generate a pipe pull-out resistance (Z),
A small protrusion (33) is attached to the outer peripheral surface of the thin approximately cylindrical portion (35) to prevent the thin approximately cylindrical portion (35) from being deformed to excessively expand its diameter under pressure. A pipe joint characterized by comprising a small protrusion (33) configured to abut against the inner surface of the hole (11) of the cap nut (2) .

a flare joint body (1) having a male threaded portion (9) and a tapered surface (5) with a reduced diameter at the tip;
A female threaded portion (12) screwed onto the male threaded portion (9) is provided at the proximal end of the hole (11), and a portion (14) of the same diameter is provided in the middle of the hole (11). a cap nut (2) forming a storage space (E) having a stepped portion (15) and a reduced diameter tapered portion (17);
A plastically deformable thin substantially cylindrical portion on the distal end side, which is housed in the storage space (E) and has a base end pressure contact gradient surface (32) in pressure contact with the tip diameter reduction gradient surface (5). a stop ring (3) having a (35) and a pipe pull-out prevention claw (36) on its tip head (37);
In a pipe joint equipped with
The claw portion (36) is composed of a rear claw (36B) and a front claw (36F) spaced apart by a minute distance ( _W36 ). The cross-sectional shape of the front claw (36F) is a trapezoid or approximately trapezoid having the top side of the tip side (41), and the top side is the linear second tip side (42),
The first tip side (41) of the rear claw (36B) of the stop ring (3) and the front claw ( 36F), as the cap nut (2) is screwed, the second tip side (42) of the pipe nut (2) is brought into a strong pressure contact state to generate a pipe pull-out resistance (Z),
At least the rear part (31) of the pipe insertion hole (3A) of the stop ring (3) is formed in a tapered shape with a reduced diameter in the rear, and when the pipe is completely inserted, the straight tip part (10) extends into the pipe insertion hole. A pipe joint characterized by being configured to press against the inner peripheral surface (27) of the portion (3A) .

The rear claw (36B) and the front claw (36F) of the claw portion (36) are strongly pressed against the outer peripheral surface (10A) as the cap nut (2) is screwed, and the rear claw (36B) is pressed against the outer peripheral surface (10A). 5. A pipe joint according to claim 1, 2, 3 or 4 , wherein the front claw (36F) exerts a sealing function and sealing material is omitted from the inner and outer peripheral surfaces of the stop ring (3) .

The rear claw (36B) and the front claw (36F) share the pipe pull-out resistance (Z) substantially equally in the strong pressure contact state with respect to the outer peripheral surface (10A) of the pipe (P). A pipe joint according to claim 1, 2, 3 or 4 .

5. The thin cylindrical portion (35) having the rear claw (36B) and the front claw (36F) at its distal end has a conical cylindrical shape with a diameter expanding toward the distal end. pipe fittings.

An annular ring that is hooked from the inner diameter side to an annular tip edge portion (20) formed by the tip of the tip diameter reducing gradient surface (5) of the joint body (1) and the joint body hole portion (6). small ridges (40),
Attached to the inner peripheral edge of the base end pressure contact gradient surface (32) of the stop ring (3) to prevent the base end of the stop ring (3) from being deformed radially outward excessively. 5. The pipe joint according to claim 1, 2, 3 or 4 constructed .