JP4103777B2 - Pipe joint seal structure - Google Patents

Pipe joint seal structure Download PDF

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JP4103777B2
JP4103777B2 JP2003374598A JP2003374598A JP4103777B2 JP 4103777 B2 JP4103777 B2 JP 4103777B2 JP 2003374598 A JP2003374598 A JP 2003374598A JP 2003374598 A JP2003374598 A JP 2003374598A JP 4103777 B2 JP4103777 B2 JP 4103777B2
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peripheral surface
pipe
male
annular elastic
double ring
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JP2005140164A (en
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誠 吉野
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Denso Corp
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Description

本発明は、オス側配管のオス継手部をメス側配管のメス継手部に嵌め合わせることにより、配管部材を結合する配管継手のシール構造に関し、車両用空調装置の冷媒の配管継手に用いて好適である。   The present invention relates to a seal structure of a pipe joint for connecting pipe members by fitting a male joint part of a male side pipe to a female joint part of a female side pipe, and is suitable for use as a refrigerant pipe joint of a vehicle air conditioner. It is.

従来、配管の継手におけるシール構造として、図１０の特許文献１のように環状弾性シール部材であるＯリング５１を使用したものが知られている。この従来例では、オス側配管１４のオス継手部１４ａとメス側配管１５のメス継手部１５ａを嵌め合わせることにより、オス側配管１４とメス側配管１５を結合している。さらに、オス継手部１４ａの外周面にはＯリング５１を取り付ける溝１４ｂが形成されており、この溝１４ｂにＯリング５１が取付け配置される。   2. Description of the Related Art Conventionally, as a seal structure in a joint of a pipe, one using an O-ring 51 that is an annular elastic seal member as in Patent Document 1 in FIG. 10 is known. In this conventional example, the male side pipe 14 and the female side pipe 15 are combined by fitting the male joint part 14 a of the male side pipe 14 and the female joint part 15 a of the female side pipe 15. Further, a groove 14b for attaching the O-ring 51 is formed on the outer peripheral surface of the male joint portion 14a, and the O-ring 51 is attached and disposed in the groove 14b.

これによると、オス継手部１４ａとメス継手部１５ａの嵌め合い時にＯリング５１がメス継手部１５ａの内周面１５ｂとオス継手部１４ａの溝１４ｂに圧接するため、配管１４、１５内の流体が配管１４、１５外に漏れ出すことを防止（シール）できる。また、従来例ではオス側配管１４のオス継手部１４ａに溝１４ｂを２つ形成したため、溝１４ｂが１つの場合に比べて、より確実に配管１４、１５内の流体が配管１４、１５外に漏れ出すことを防止できる。   According to this, when the male joint portion 14a and the female joint portion 15a are fitted, the O-ring 51 is pressed against the inner peripheral surface 15b of the female joint portion 15a and the groove 14b of the male joint portion 14a. Can be prevented (seal) from leaking out of the pipes 14 and 15. Further, in the conventional example, since the two grooves 14b are formed in the male joint portion 14a of the male side pipe 14, the fluid in the pipes 14 and 15 is more reliably transferred to the outside of the pipes 14 and 15 than in the case of one groove 14b. Leakage can be prevented.

さらに、本発明者は従来例と同等の効果を有する配管継手のシール構造として、図１１に示すように、環状弾性シール部材に配管１４、１５の中心軸Ａ方向に２つの頂部を有する二山リング１６を使用した比較例１について検討した。   Furthermore, as shown in FIG. 11, the present inventor, as a pipe joint seal structure having an effect equivalent to that of the conventional example, has two crests having two apexes in the direction of the central axis A of the pipes 14 and 15 as shown in FIG. 11. Comparative Example 1 using the ring 16 was examined.

これによると、オス継手部１４ａとメス継手部１５ａの嵌め合い時に、二山リング１６の外側面１６ａに形成された２つの頂部１６ｂがメス継手部１５ａの内周面１５ｂに圧接する。したがって、Ｏリングを２つ配置した従来例と同様に配管１４、１５内の流体が配管１４、１５外に漏れ出すことを防止（シール）できる。
特開２００２−２１４０６７号公報 According to this, at the time of fitting the male joint portion 14a and the female joint portion 15a, the two top portions 16b formed on the outer side surface 16a of the double ring 16 are pressed against the inner peripheral surface 15b of the female joint portion 15a. Therefore, it is possible to prevent (seal) the fluid in the pipes 14 and 15 from leaking out of the pipes 14 and 15 as in the conventional example in which two O-rings are arranged.
JP 2002-214067 A

しかし、特許文献１の配管継手のシール構造ではＯリング５１を２個使用するため部品点数が増えてしまう。また、オス継手部１４ａにはＯリング５１の取り付ける溝１４ｂの加工が２ヶ所必要となる。さらに、２つのＯリング５１を溝１４ｂに組み付けなければならない。以上が相まって、コストが増加してしまう。   However, in the pipe joint seal structure disclosed in Patent Document 1, two O-rings 51 are used, which increases the number of parts. In addition, the male joint portion 14a requires two machining of the groove 14b to which the O-ring 51 is attached. Furthermore, the two O-rings 51 must be assembled in the groove 14b. Combined with the above, the cost increases.

また、図１１の比較例１では環状弾性シール部材である二山リング１６が１つのため上述したコストの増加を防止できる。しかし、二山リング１６を成型加工するには二山リング１６の軸中心Ａ側（内側）の面１６ｃを形成する金型をスライドさせるため、内側面１６ｃが平滑な形状となる場合がある。このような場合には、特に二山リング１６を取り付ける溝１４ｂと二山リング１６の内側面１６ｃとの間のシール性能が低いという問題がある。   Moreover, in the comparative example 1 of FIG. 11, since there is one double ring 16 which is an annular elastic seal member, the above-described increase in cost can be prevented. However, in order to mold the double ring 16, the inner surface 16c may have a smooth shape because the mold forming the surface 16c on the axis center A side (inside) of the double ring 16 is slid. In such a case, there is a problem that the sealing performance between the groove 14b for attaching the double ring 16 and the inner side surface 16c of the double ring 16 is low.

本発明は、上記点に鑑み、配管継手において環状弾性シール部材と継手部の環状弾性シール部材が取り付けられる面との間のシール性能の向上を目的とし、特に環状弾性シール部材の内側面および外側面のうち、継手部に接する面が平滑な形状の場合のシール性能の向上を目的とする。   In view of the above points, the present invention aims to improve the sealing performance between the annular elastic seal member and the surface to which the annular elastic seal member of the joint portion is attached in the pipe joint, and in particular, the inner surface and the outer surface of the annular elastic seal member. It aims at the improvement of the sealing performance in the case where the surface which contacts a joint part is a smooth shape among side surfaces.

上記目的を達成するため、請求項１に記載の発明では、オス継手部（１４ａ）を有するオス側配管部材（１４）と、メス継手部（１５ａ）を有するメス側配管部材（１５）と、オス継手部（１４ａ）の外周面、またはメス継手部（１５ａ）の内周面（１５ｂ）に配置される環状弾性シール部材（１６、１９）とを備え、
オス継手部（１４ａ）とメス継手部（１５ａ）の内周面（１５ｂ）を嵌め合わせることにより、両配管部材（１４、１５）を結合し、
オス継手部（１４ａ）とメス継手部（１５ａ）が結合した状態において、環状弾性シール部材（１６、１９）が外周面と内周面（１５ｂ）との間で、外周面および内周面（１５ｂ）に圧接し、
外周面または内周面（１５ｂ）には、環状弾性シール部材（１６、１９）に凹凸を形成する少なくとも１つの凹凸形状（１４ｃ、１４ｆ、１５ｅ）が形成され、
オス側配管部材（１４）には、環状弾性シール部材（１６、１９）が流体から圧力を受けた状態で、環状弾性シール部材（１６、１９）のずれを規制する規制面（１４ｅ）が備えられており、
規制面（１４ｅ）には、環状弾性シール部材（１６、１９）に凹凸を形成する少なくとも１つの別の凹凸形状（１４ｈ）が形成されていることを特徴としている。 In order to achieve the above object, in the invention according to claim 1, a male pipe member (14) having a male joint part (14a), a female pipe member (15) having a female joint part (15a), An annular elastic seal member (16, 19) disposed on the outer peripheral surface of the male joint portion (14a) or the inner peripheral surface (15b) of the female joint portion (15a);
By fitting both the male joint part (14a) and the inner peripheral surface (15b) of the female joint part (15a), the both pipe members (14, 15) are combined,
In a state where the male joint portion (14a) and the female joint portion (15a) are coupled, the annular elastic seal member (16, 19) is between the outer peripheral surface and the inner peripheral surface (15b). 15b),
On the outer peripheral surface or the inner peripheral surface (15b), at least one concavo-convex shape (14c, 14f, 15e) that forms the concavo-convex shape on the annular elastic seal member (16, 19) is formed .
The male piping member (14) includes a regulation surface (14e) that regulates the displacement of the annular elastic seal member (16, 19) in a state where the annular elastic seal member (16, 19) receives pressure from the fluid. And
The restriction surface (14e) is characterized in that at least one other uneven shape (14h) that forms unevenness on the annular elastic seal member (16, 19) is formed .

これによると、オス継手部（１４ａ）とメス継手部（１５ａ）が結合した状態において、外周面または内周面（１５ｂ）に少なくとも１つの凹凸形状（１４ｃ、１４ｆ、１５ｅ）を形成したため、環状弾性シール部材（１６、１９）が凹凸形状に対応して変形する。   According to this, at least one uneven shape (14c, 14f, 15e) is formed on the outer peripheral surface or the inner peripheral surface (15b) in a state where the male joint portion (14a) and the female joint portion (15a) are combined, The elastic seal members (16, 19) are deformed corresponding to the uneven shape.

この凹凸形状（１４ｃ、１４ｆ、１５ｅ）が凹形状の場合には、環状弾性シール部材（１６、１９）が凹形状に押し込まれるように変形する。この時、凹形状が形成される外周面、または内周面（１５ｂ）と凹形状の境目（後述する図６中の記号Ｂ。中心軸Ａ方向に２ヶ所ある）では、環状弾性シール部材（１６、１９）が外周面または内周面（１５ｂ）に与える圧力が局所的に高くなる。   When the uneven shape (14c, 14f, 15e) is a concave shape, the annular elastic seal member (16, 19) is deformed so as to be pushed into the concave shape. At this time, at the outer peripheral surface where the concave shape is formed, or at the boundary between the inner peripheral surface (15b) and the concave shape (symbol B in FIG. 6 described later, there are two places in the direction of the central axis A), an annular elastic sealing member ( 16, 19) locally increases the pressure applied to the outer peripheral surface or the inner peripheral surface (15b).

これにより、環状弾性シール部材（１６、１９）と凹形状が形成される外周面または内周面（１５ｂ）を、より密着させることができる。したがって、凹形状が形成される外周面または内周面（１５ｂ）と環状弾性シール部材（１６、１９）との間のシール性能を高めることができる。   Thereby, an annular elastic sealing member (16, 19) and the outer peripheral surface or inner peripheral surface (15b) in which a concave shape is formed can be made to adhere more closely. Therefore, the sealing performance between the outer peripheral surface or inner peripheral surface (15b) in which the concave shape is formed and the annular elastic seal member (16, 19) can be enhanced.

一方、凹凸形状（１４ｃ、１４ｆ、１５ｅ）が凸形状の場合には、凸形状により環状弾性シール部材（１６、１９）と凸形状が形成される外周面または内周面（１５ｂ）との間の圧力を局所的に高くすることができる。これにより、環状弾性シール部材（１６、１９）と凸形状が形成される外周面または内周面（１５ｂ）を、より密着させることができる（後述の図５参照）。したがって、凸形状が形成される外周面または内周面（１５ｂ）と環状弾性シール部材（１６、１９）との間のシール性能を高めることができる。   On the other hand, when the concavo-convex shape (14c, 14f, 15e) is a convex shape, between the annular elastic seal member (16, 19) and the outer peripheral surface or the inner peripheral surface (15b) where the convex shape is formed by the convex shape. Can be locally increased. Thereby, an annular elastic sealing member (16, 19) and the outer peripheral surface or inner peripheral surface (15b) in which a convex shape is formed can be made to adhere more closely (refer to Drawing 5 mentioned below). Therefore, the sealing performance between the outer peripheral surface or inner peripheral surface (15b) on which the convex shape is formed and the annular elastic seal member (16, 19) can be enhanced.

さらに、オス側配管部材（１４）が、環状弾性シール部材（１６、１９）のずれを規制する規制面（１４ｅ）を備えているので、環状弾性シール部材（１６、１９）は流体からの圧力により、規制面（１４ｅ）に押し付けられる。この時、上述した環状弾性シール部材（１６、１９）と外周面または内周面（１５ｂ）の凹凸形状（１４ｃ、１４ｆ、１５ｅ）との間と同様の関係が、環状弾性シール部材（１６、１９）と規制面（１４ｅ）の別の凹凸形状（１４ｈ）との間に生じる。したがって、環状弾性シール部材（１６、１９）と規制面（１４ｅ）との間のシール性能を高めることができる。 Furthermore, since the male side piping member (14) includes a regulating surface (14e) that regulates the displacement of the annular elastic seal member (16, 19) , the annular elastic seal member (16, 19) is pressured from the fluid. Thus, it is pressed against the regulation surface (14e). At this time, the irregular shape of the outer peripheral surface or inner peripheral surface with annular elastic seal member described above (16,19) (15b) (14c , 14f, 15e) is same relationship as between the annular elastic seal member (16, 19) and another irregular shape (14h) of the regulating surface (14e). Therefore, the sealing performance between the annular elastic sealing member (16, 19) and the regulating surface (14e) can be enhanced.

また、請求項２に記載の発明では、請求項１において、環状弾性シール部材は、内側面（１６ｃ、１９ａ）および外側面（１６ａ、１９ｃ）のうち、凹凸形状（１４ｃ、１４ｆ、１５ｅ）に接していない面に、両配管部材（１４、１５）の中心軸Ａ方向に複数の頂部（１６ｂ、１９ｂ）を形成した複数山リング（１６、１９）であるシール構造を特徴としている。 Further, in the invention according to claim 2, Oite to claim 1, the annular elastic seal member has an inner surface (16c, 19a) and an outer surface (16a, 19c) of the concavo-convex shape (14c, 14f, 15e ) Is characterized by a seal structure that is a plurality of crest rings (16, 19) in which a plurality of top portions (16b, 19b) are formed in the direction of the central axis A of both piping members (14, 15) on the surface not in contact with.

これによると、流体が配管部材（１４、１５）から漏れ出そうとする方向（両配管部材（１４，１５）の中心軸Ａ方向）に複数の頂部（１６ｂ、１９ｂ）が形成されているため、頂部（１６ｂ、１９ｂ）の数と同数のＯリングを配置した場合（図１０の従来例はＯリングが２つの例）と同等のシール性能を発揮することができる。さらに、この複数山リング（１６、１９）は１つの部品であるため、従来例のようにＯリングが複数の場合に生じる部品点数（Ｏリングの数）の増加、複数のＯリング取付部の加工および複数のＯリングの組み付けによるコストの増加を防ぐことができる。   According to this, a plurality of top portions (16b, 19b) are formed in the direction in which the fluid leaks from the piping members (14, 15) (the direction of the central axis A of both the piping members (14, 15)). The same number of O-rings as the tops (16b, 19b) are arranged (the conventional example of FIG. 10 can exhibit sealing performance equivalent to that of two O-rings). Furthermore, since the multiple ring (16, 19) is a single part, the number of parts (number of O-rings) generated when there are a plurality of O-rings as in the conventional example, Cost increase due to processing and assembly of a plurality of O-rings can be prevented.

また、請求項３に記載の発明のように、請求項２において、単体状態において複数山リング（１６、１９）の内側面（１６ｃ、１９ａ）および外側面（１６ａ、１９ｃ）のうち、凹凸形状（１４ｃ、１４ｆ、１５ｅ）に接する面を平滑な円周面として、複数山リング（１６、１９）と凹凸形状が形成される外周面または内周面（１５ｂ）との間のシール性能を高めてもよい。 It is preferable as defined in claim 3, in claim 2, the inner surfaces of the plurality mountain rings (16, 19) in a single state (16c, 19a) and an outer surface (16a, 19c) of the concavo-convex shape The surface in contact with (14c, 14f, 15e) is a smooth circumferential surface, and the sealing performance between the multiple ridge rings (16, 19) and the outer peripheral surface or inner peripheral surface (15b) on which the concavo-convex shape is formed is enhanced. May be.

なお、内側面（１６ｃ、１９ａ）および外側面（１６ａ、１９ｃ）のうち、凹凸形状が形成される外周面または内周面（１５ｂ）が平滑な円周面であれば、その面を金型の型抜き（スライド）方向にすることができる。これにより、加工時の型設計の自由度が高くなり、複数山リング（１６、１９）の製造コストを低減できる。   Of the inner side surface (16c, 19a) and outer side surface (16a, 19c), if the outer peripheral surface or inner peripheral surface (15b) on which the concavo-convex shape is formed is a smooth circumferential surface, that surface is a mold. It can be in the direction of die cutting (sliding). Thereby, the freedom degree of the die design at the time of a process becomes high, and the manufacturing cost of a multiple mountain ring (16, 19) can be reduced.

また、請求項４に記載の発明のように、請求項２または３において、単体状態の複数山リング（１６、１９）の幅方向側面（１６ｄ、１９ｄ）のうち、少なくとも規制面（１４ｅ）に形成された別の凹凸形状（１４ｈ）に接する面を平坦な形状として、請求項２または３と同様の理由により複数山リング（１６、１９）と規制面（１４ｅ）との間のシール性能を高めてもよい。さらに、別の凹凸形状（１４ｈ）に接する面が平坦な形状であるため、その面を金型の型抜き（スライド）方向にすることができる。これにより、加工時の型設計の自由度が高くなり、複数山リング（１６、１９）の製造コストを低減できる。
請求項５に記載の発明では、オス継手部（１４ａ）を有するオス側配管部材（１４）と、
メス継手部（１５ａ）を有するメス側配管部材（１５）と、
オス継手部（１４ａ）の外周面、またはメス継手部（１５ａ）の内周面（１５ｂ）に配置される環状弾性シール部材（１６、１９）とを備え、
オス継手部（１４ａ）とメス継手部（１５ａ）の内周面（１５ｂ）を嵌め合わせることにより、両配管部材（１４、１５）を結合し、
オス継手部（１４ａ）とメス継手部（１５ａ）が結合した状態において、環状弾性シール部材（１６、１９）が外周面と内周面（１５ｂ）との間で、外周面および内周面（１５ｂ）に圧接し、
外周面または内周面（１５ｂ）には、環状弾性シール部材（１６、１９）に凹凸を形成する少なくとも１つの凹凸形状（１４ｃ、１４ｆ、１５ｅ）が形成され、
環状弾性シール部材は、内側面（１６ｃ、１９ａ）および外側面（１６ａ、１９ｃ）のうち、凹凸形状（１４ｃ、１４ｆ、１５ｅ）に接していない面において、両配管部材（１４、１５）の中心軸Ａ方向に複数の頂部（１６ｂ、１９ｂ）を形成した複数山リング（１６、１９）であり、
複数山リング（１６、１９）は単体状態において、内側面（１６ｃ、１９ａ）および外側面（１６ａ、１９ｃ）のうち、凹凸形状（１４ｃ、１４ｆ、１５ｅ）に接する面が平滑な円周面であることを特徴としている。
これにより、上記した請求項１と同様に外周面または内周面（１５ｂ）と環状弾性シール部材（１６、１９）との間のシール性能を高めることができ、さらに上記した請求項２、３と同様の作用効果を得ることができる。 Further, as in the invention described in claim 4 , in claim 2 or 3 , at least the regulating surface (14 e) among the side surfaces (16 d, 19 d) in the width direction of the multiple mountain rings (16, 19) in a single state. For the same reason as in claim 2 or 3 , the sealing performance between the multiple crest rings (16, 19) and the restricting surface (14e) is improved by making the surface in contact with the other uneven shape (14h) formed flat. May be raised. Furthermore, since the surface in contact with the other concavo-convex shape (14h) is a flat shape, the surface can be set in the die cutting (sliding) direction of the mold. Thereby, the freedom degree of the die design at the time of a process becomes high, and the manufacturing cost of a multiple mountain ring (16, 19) can be reduced.
In invention of Claim 5, male side piping member (14) which has a male joint part (14a),
A female pipe member (15) having a female joint part (15a);
An annular elastic seal member (16, 19) disposed on the outer peripheral surface of the male joint portion (14a) or the inner peripheral surface (15b) of the female joint portion (15a);
By fitting both the male joint part (14a) and the inner peripheral surface (15b) of the female joint part (15a), the both pipe members (14, 15) are combined,
In a state where the male joint portion (14a) and the female joint portion (15a) are coupled, the annular elastic seal member (16, 19) is between the outer peripheral surface and the inner peripheral surface (15b). 15b),
On the outer peripheral surface or the inner peripheral surface (15b), at least one concavo-convex shape (14c, 14f, 15e) that forms the concavo-convex shape on the annular elastic seal member (16, 19) is formed.
The annular elastic seal member is the center of both the pipe members (14, 15) on the inner surface (16c, 19a) and the outer surface (16a, 19c) that are not in contact with the concavo-convex shape (14c, 14f, 15e). A plurality of crest rings (16, 19) formed with a plurality of peaks (16b, 19b) in the direction of the axis A,
In the single state, the multiple crest rings (16, 19) have a smooth circumferential surface that is in contact with the concavo-convex shape (14c, 14f, 15e) among the inner surface (16c, 19a) and the outer surface (16a, 19c). It is characterized by being.
As a result, the sealing performance between the outer peripheral surface or the inner peripheral surface (15b) and the annular elastic sealing member (16, 19) can be enhanced in the same manner as in the first aspect. The same effect can be obtained.

なお、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示すものである。   In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

（第１実施形態）
図１は、本発明の第１実施形態に係る配管継手１０のシール構造を車両用空調装置の冷媒配管に適用したものである。車両用空調装置の冷媒配管は、機能部品（例えば、圧縮機１１、蒸発器１２、凝縮器１３）の間を接続して冷媒経路を形成するものである。冷媒配管には継ぎ目（継手１０）が無いのが望ましいが、一般的には車両用空調装置の製造、設計レイアウトおよびサービス上の理由により、冷媒経路の延長、分岐、合流を行う継ぎ目（継手部１０）が設けられる。 (First embodiment)
FIG. 1 shows an application of the seal structure of the pipe joint 10 according to the first embodiment of the present invention to the refrigerant pipe of the vehicle air conditioner. The refrigerant piping of the vehicle air conditioner connects functional components (for example, the compressor 11, the evaporator 12, and the condenser 13) to form a refrigerant path. It is desirable that the refrigerant pipe does not have a joint (joint 10), but generally, the joint (joint part) that extends, branches, and merges the refrigerant path for reasons of manufacture, design layout, and service of the vehicle air conditioner. 10).

図２は継手部１０の断面を示しており、オス側配管１４のオス継手部１４ａとメス側配管１５のメス継手部１５ａを嵌め合わせることにより、オス側配管１４とメス側配管１５を結合し、配管１４、１５内の流体経路を延長している。ここで、図２中の点線Ａは配管１４、１５の中心軸を示し、矢印Ｒは断面における中心軸Ａからの放射方向を示している。なお、冷媒の流れ方向は中心軸Ａ方向となる。以下、配管継手１０を構成するオス側配管１４、メス側配管１５および環状弾性シール部材１６について説明する。   FIG. 2 shows a cross section of the joint part 10, and the male side pipe 14 and the female side pipe 15 are joined by fitting the male joint part 14 a of the male side pipe 14 and the female joint part 15 a of the female side pipe 15. The fluid paths in the pipes 14 and 15 are extended. Here, the dotted line A in FIG. 2 indicates the central axis of the pipes 14 and 15, and the arrow R indicates the radial direction from the central axis A in the cross section. The refrigerant flow direction is the direction of the central axis A. Hereinafter, the male side pipe 14, the female side pipe 15 and the annular elastic seal member 16 constituting the pipe joint 10 will be described.

図３に示すようにオス側配管１４は略円筒形状の管であり、φＤ１の外径を持つオス継手部１４ａを備えている。このオス継手部１４ａの外周面には環状弾性シール材である二山リング１６を取り付ける溝１４ｂが形成されている。ここで、溝１４ｂは特許請求の範囲における外周面に含まれている。   As shown in FIG. 3, the male side pipe 14 is a substantially cylindrical pipe, and includes a male joint portion 14a having an outer diameter of φD1. A groove 14b for attaching a double ring 16 that is an annular elastic sealing material is formed on the outer peripheral surface of the male joint portion 14a. Here, the groove 14b is included in the outer peripheral surface in the claims.

溝１４ｂには、溝１４ｂから外方（放射方向Ｒ）へ向かって突き出す突起部１４ｃが形成されている。また、オス側配管１４のうちオス継手部１４ａとの境目の部位には、段付部１４ｄが形成されている。なお、溝１４ｂでのオス側配管１４の外径はφＤ２である。   The groove 14b is formed with a protrusion 14c that protrudes outward (radial direction R) from the groove 14b. Further, a stepped portion 14d is formed at the boundary between the male side pipe 14 and the male joint portion 14a. The outer diameter of the male side pipe 14 in the groove 14b is φD2.

オス側配管１４の材料は、冷媒および配管が設置される環境に対する耐食性等を考慮して決定される。本実施形態では材料としてアルミ材を使用し、このアルミ材に切削、プレス、転造等の加工を施してオス側配管１４を成形している。   The material of the male side pipe 14 is determined in consideration of the corrosion resistance to the environment where the refrigerant and the pipe are installed. In the present embodiment, an aluminum material is used as a material, and the male side pipe 14 is formed by performing processing such as cutting, pressing, and rolling on the aluminum material.

また、溝１４ｂに取付けられる二山リング１６は略リング形状をしており、放射方向Ｒの断面が二山形状（Ｂ字形状）である。本実施形態の二山リング１６は、略リング形状の最大外径、つまりリング１６の外側面１６ａのうち二山の頂部１６ｂでの直径がφＤ３であり、また、略リング形状の内側面１６ｃでの直径φがＤ４である。   Moreover, the double ring 16 attached to the groove 14b has a substantially ring shape, and the cross section in the radial direction R has a double shape (B-shape). The double ring 16 of this embodiment has a substantially ring-shaped maximum outer diameter, that is, the diameter at the top 16b of the two peaks of the outer surface 16a of the ring 16 is φD3, and the inner surface 16c of the substantially ring shape. Has a diameter φ of D4.

二山リング１６の内側面１６ｃは、成型加工時に金型を図３中の中心軸Ａ方向（矢印Ｙ方向）にスライドさせるため、平滑な円周面になる。以下、矢印Ｙ方向を二山リング１６の幅方向と称す。さらに、本実施形態では二山リング１６の幅方向（矢印Ｙ方向）に位置する側面１６ｄも平坦な形状となっている。なお、二山リング１６の材料は温度に対する耐性、冷媒の透過性、弾性等を考慮して決定され、本実施形態ではＥＰＤＭ（エチレンプロピレンジエン三元共重合体、エチレンプロピレンゴム）を使用している。   The inner surface 16c of the double ring 16 has a smooth circumferential surface because the mold is slid in the direction of the central axis A (arrow Y direction) in FIG. Hereinafter, the arrow Y direction is referred to as the width direction of the double ring 16. Furthermore, in this embodiment, the side surface 16d located in the width direction (arrow Y direction) of the double ring 16 has a flat shape. The material of the double ring 16 is determined in consideration of temperature resistance, refrigerant permeability, elasticity, etc. In this embodiment, EPDM (ethylene propylene diene terpolymer, ethylene propylene rubber) is used. Yes.

ところで、メス側配管１５は図４に示すように略円筒形状の管であり、オス側配管１４のオス継手部１４ａが挿入されるメス継手部１５ａを有している。このメス継手部１５ａの内周面１５ｂでの径はφＤ５である。内径φＤ５は、オス継手部１４ａの外径φＤ１よりも大きく二山リング１６の外径φＤ３よりも小さい値となっている。なお、このメス側配管１５もオス側配管１４と同様にアルミを材料として形成されている。   By the way, the female side pipe 15 is a substantially cylindrical pipe as shown in FIG. 4, and has a female joint part 15 a into which the male joint part 14 a of the male side pipe 14 is inserted. The diameter of the female joint portion 15a on the inner peripheral surface 15b is φD5. The inner diameter φD5 is larger than the outer diameter φD1 of the male joint portion 14a and smaller than the outer diameter φD3 of the double ring 16. The female side pipe 15 is also made of aluminum as a material, like the male side pipe 14.

次に、二山リング１６、オス側配管１４およびメス側配管１５の組付けについて説明すると、まず弾性を有する二山リング１６の内径φＤ４をオス継手部１４ａの外径φＤ１よりも大きく押し広げて溝１４ｂに取付ける（図３）。なお、溝１４ｂでの外径φＤ２は二山リング１６の内径φＤ４よりもわずかに大きい値となっており、二山リング１６の内側面１６ｃがその弾性力により中心軸Ａ側に押し付けられるようになっている。   Next, the assembly of the double ring 16, the male side pipe 14, and the female side pipe 15 will be described. First, the inner diameter φD4 of the elastic double ring 16 is pushed larger than the outer diameter φD1 of the male joint portion 14a. It is attached to the groove 14b (FIG. 3). The outer diameter φD2 of the groove 14b is slightly larger than the inner diameter φD4 of the double ring 16 so that the inner surface 16c of the double ring 16 is pressed against the central axis A side by its elastic force. It has become.

その後、二山リング１６が取付けられたオス側配管１４のオス継手部１４ａをメス側配管１５のメス継手部１５ａに挿入する（図４）。この時、メス継手部１５ａの内周面１５ｂの内径φＤ５が二山リング１６の外径φＤ３よりも小さいため、弾性を持つ二山リング１６が押しつぶされる。押しつぶされることにより二山リング１６には応力が発生し、この応力により二山リング１６の二山の頂部１６ａはメス継手部１５ａの内周面１５ｂに圧接し、二山リング１６の内側面１６ｃは溝１４ｂおよび溝１４ｂに形成された突起部１４ｃに圧接する。   Then, the male joint part 14a of the male side pipe 14 to which the double ring 16 is attached is inserted into the female joint part 15a of the female side pipe 15 (FIG. 4). At this time, since the inner diameter φD5 of the inner peripheral surface 15b of the female joint portion 15a is smaller than the outer diameter φD3 of the double ring 16, the elastic double ring 16 is crushed. As a result of the crushing, a stress is generated in the double ring 16, and the two peaks 16 a of the double ring 16 are pressed against the inner peripheral surface 15 b of the female joint 15 a due to this stress, and the inner surface 16 c of the double ring 16. Is in pressure contact with the groove 14b and the protrusion 14c formed in the groove 14b.

また、二山リング１６は冷媒の圧力を受けて冷媒の経路とは反対側方向（図２〜４では左方向）にずれようとするため、オス継手部１４ａには二山リング１６のずれを規制する規制面１４ｅが備えられている。したがって、二山リング１６の幅方向（図３中Ｙ方向）の側面１６ｄは冷媒の圧力により規制面１４ｅに押し付けられている。   In addition, the double ring 16 receives the pressure of the refrigerant and tends to shift in the direction opposite to the refrigerant path (leftward in FIGS. 2 to 4). Therefore, the double ring 16 is displaced in the male joint portion 14a. A restriction surface 14e for restriction is provided. Therefore, the side surface 16d in the width direction (Y direction in FIG. 3) of the double ring 16 is pressed against the regulating surface 14e by the pressure of the refrigerant.

これらにより、図２に示すように配管１４、１５内の冷媒が配管１４、１５外に漏れ出すことを防止しつつ、冷媒経路を延長している。なお、オス継手部１４ａの挿入はオス側配管１４の段付部１４ｄがメス側配管１５の端部１５ｃに突き当たる位置まで行われる。さらに、配管１４、１５は、配管１４、１５の外周に配置されたボルト１７およびナット１８により外れないように結合されている（図１参照）。   As a result, the refrigerant path is extended while preventing the refrigerant in the pipes 14 and 15 from leaking out of the pipes 14 and 15 as shown in FIG. The male joint portion 14a is inserted to a position where the stepped portion 14d of the male side pipe 14 abuts against the end portion 15c of the female side pipe 15. Further, the pipes 14 and 15 are coupled so as not to be detached by bolts 17 and nuts 18 arranged on the outer periphery of the pipes 14 and 15 (see FIG. 1).

次に、第１実施形態による作用効果を列挙すると、（１）二山リング１６が取り付けられるオス継手部１４ａの溝１４ｂに、二山リング１６へ向かって突き出す突起部１４ｃを形成したため、溝１４ｂと二山リング１６の内側面１６ｃとの間のシール性能を高めることができる。   Next, the effects of the first embodiment are listed. (1) Since the protrusion 14c protruding toward the double ring 16 is formed in the groove 14b of the male joint part 14a to which the double ring 16 is attached, the groove 14b And the inner surface 16c of the double ring 16 can be improved in sealing performance.

ところで、図５は比較例１（図中（ａ））および本実施形態（図中（ｂ））において、オス継手部１４ａが二山シール１６から受ける応力を比較したものである。本実施形態のオス継手部１４ａは、突起部１４ｃにおいて二山シール１６から受ける圧力が局所的に高くなっている。これは二山シール１６の内側面１６ｃと溝１４ｂの突起部１４ｃが、より密着していることを示している。   By the way, FIG. 5 compares the stress which the male joint part 14a receives from the double seal 16 in the comparative example 1 ((a) in a figure) and this embodiment ((b) in a figure). In the male joint portion 14a of the present embodiment, the pressure received from the double seal 16 at the protrusion 14c is locally high. This indicates that the inner surface 16c of the double seal 16 and the protrusion 14c of the groove 14b are more closely attached.

これにより、溝１４ｂと二山リング１６の内側面１６ｃとの間のシール性能を高めることができる。なお、この効果は二山リング１６のように幅方向（図３中Ｙ方向）に長さがあり、取り付けられる面（溝１４ｂ）に接する内側面１６ｃが平滑な円周面をしているシール部材の場合に特に顕著に現れる。   Thereby, the sealing performance between the groove | channel 14b and the inner surface 16c of the double ring 16 can be improved. In addition, this effect has a length in the width direction (Y direction in FIG. 3) like the double ring 16, and the inner side surface 16c in contact with the surface (groove 14b) to be attached has a smooth circumferential surface. This is particularly noticeable in the case of members.

さらに、二山リング１６が取付けられる溝１４ｂに突起部１４ｃを形成したため、配管１４、１５の結合時に二山リング１６の内側面１６ｃが突起部１４ｃに対応して変形する。内側面１６ｃの変形により、溝１４ｂおよび突起部１４ｃと二山リング１６の内側面１６ｃとの間の中心軸Ａ方向のシール長さ（接している距離）が長くなるため、溝１４ｂと二山リング１６の内側面１６ｃとの間のシール性能を高めることができる。   Furthermore, since the protrusion 14c is formed in the groove 14b to which the double ring 16 is attached, the inner side surface 16c of the double ring 16 is deformed corresponding to the protrusion 14c when the pipes 14 and 15 are joined. Due to the deformation of the inner surface 16c, the seal length (distance in contact) between the groove 14b and the protrusion 14c and the inner surface 16c of the double ring 16 in the direction of the central axis A is increased. The sealing performance between the inner surface 16c of the ring 16 can be enhanced.

（２）環状弾性シール部材として１個の部品である二山リング１６を使用したため、配管継手１０のシール構造全体での部品点数を従来例（図１０）のシール構造よりも少なくできる。また、二山リング１６が取り付けられるオス継手部１４ａの溝１４ｂの加工が１ヶ所で済む。さらに、溝１４ｂへの二山リング１６の組み付けが１回で済む。これらが相まって、従来例のように弾性シール部材（Ｏリング５１）を２つ使用した場合と比較してコストを低くすることができる。   (2) Since the double ring 16 which is one part is used as the annular elastic seal member, the number of parts in the entire seal structure of the pipe joint 10 can be reduced as compared with the seal structure of the conventional example (FIG. 10). Further, the machining of the groove 14b of the male joint portion 14a to which the double ring 16 is attached is completed at one place. Further, the double ring 16 can be assembled to the groove 14b only once. Together, the cost can be reduced compared to the case where two elastic seal members (O-rings 51) are used as in the conventional example.

（３）環状弾性シール部材として２つの頂部１６ｂがメス継手部１５ａの内周面１５ｂに圧接する二山リング１６を使用したため、Ｏリング５１を２つ使用した従来例と同等のシール性能を発揮することができる。   (3) Since the double ring 16 in which the two top portions 16b are pressed against the inner peripheral surface 15b of the female joint portion 15a is used as the annular elastic seal member, the sealing performance equivalent to the conventional example using two O-rings 51 is exhibited. can do.

従来例（図１０）の配管継手のシール構造では、冷媒が配管１４、１５から漏れ出そうとする方向にシール部材であるＯリング５１を２つ配置してシール性能（配管１４、１５内の冷媒を漏らさない性能）を高めている。一方、本実施形態の二山リング１６には、冷媒が配管１４、１５から漏れ出そうとする方向に２つの頂部１６ｂが形成されているため、従来例と同等のシール性能を発揮することができる。   In the pipe joint seal structure of the conventional example (FIG. 10), two O-rings 51, which are seal members, are arranged in the direction in which the refrigerant leaks from the pipes 14 and 15, and the sealing performance (in the pipes 14 and 15). (Performance that does not leak refrigerant). On the other hand, in the double ring 16 of the present embodiment, the two top portions 16b are formed in the direction in which the refrigerant is about to leak from the pipes 14 and 15, so that the sealing performance equivalent to the conventional example can be exhibited. it can.

（４）環状弾性シール部材として、幅方向（図３中Ｙ方向）に長さのある二山リング１６を使用したため、冷媒が二山リング１６を透過して配管外に漏れ出してしまうことを防止できる。二山リング１６の幅方向の長さが長いとは、透過しようとする冷媒から見て二山リング１６の材料厚さが厚いという事である。したがって、冷媒が二山リング１６を透過して配管１４、１５外に漏れ出してしまうことを防止でき、経時による冷媒量の不足などの不具合を防止することができる。   (4) Since the double ring 16 having a length in the width direction (Y direction in FIG. 3) is used as the annular elastic seal member, the refrigerant permeates the double ring 16 and leaks out of the pipe. Can be prevented. The long length in the width direction of the double ring 16 means that the material thickness of the double ring 16 is thick as viewed from the refrigerant to be transmitted. Therefore, it is possible to prevent the refrigerant from leaking out of the pipes 14 and 15 through the double ring 16 and to prevent problems such as a shortage of the refrigerant amount over time.

（５）環状弾性シール部材として、幅方向（図３中Ｙ方向）に長さのある二山リング１６を使用したため、二山リング１６取付け後のオス継手部１４ａをメス継手部１５ａに挿入する時（図４）に二山リング１６の形状が崩れてオス継手部１４ａとメス継手部１５ａに挟まることを減少させることができる。   (5) Since the double ring 16 having a length in the width direction (Y direction in FIG. 3) is used as the annular elastic seal member, the male joint portion 14a after the double ring 16 is attached is inserted into the female joint portion 15a. At this time (FIG. 4), it is possible to reduce the shape of the double ring 16 from collapsing between the male joint portion 14a and the female joint portion 15a.

ところで、環状弾性シール部材取付け後のオス継手部１４ａをメス継手部１５ａに挿入する時（図４）に、シール部材が従来例（図１０）のようなＯリング５１では、Ｏリング５１がねじれてオス継手部１４ａとメス継手部１５ａに挟まる、いわゆる咬み込み状態になる場合がある。   By the way, when the male joint portion 14a after the annular elastic seal member is attached is inserted into the female joint portion 15a (FIG. 4), the O-ring 51 is twisted in the O-ring 51 as in the conventional example (FIG. 10). Thus, there is a case where a so-called bite state is reached between the male joint portion 14a and the female joint portion 15a.

しかし、本実施形態の二山リング１６は幅方向（図３中Ｙ方向）に長さがあるため、ねじれにくい。したがって、組み付け時に咬み込み状態となることを防止することができ、配管継手１０のシール構造における組み付け不良（シール不良）を防止することができる。   However, since the double ring 16 of this embodiment has a length in the width direction (Y direction in FIG. 3), it is difficult to twist. Therefore, it is possible to prevent a state of being bitten at the time of assembly, and it is possible to prevent an assembly failure (seal failure) in the seal structure of the pipe joint 10.

（６）二山リング１６の内側面１６ｃおよび幅方向側面１６ｄが平滑な形状であるため、二山リング１６の成型加工にかかるコストを低減することができる。   (6) Since the inner side surface 16c and the width direction side surface 16d of the double ring 16 have a smooth shape, the cost required for molding the double ring 16 can be reduced.

ところで、二山リング１６の内側面１６ｃが平滑な円周面であると、その面を金型の型抜き（スライド）方向にすることができるようになる。これにより、加工時の型設計の自由度が高くなり、二山リング１６の製造コストを低減することができる。同様に、幅方向側面１６ｄも平坦な形状となっているため、さらに製造コストを低減することができる。   By the way, when the inner side surface 16c of the double ring 16 is a smooth circumferential surface, the surface can be set in a die-cutting (sliding) direction of the mold. Thereby, the freedom degree of the die design at the time of a process becomes high, and the manufacturing cost of the double ring 16 can be reduced. Similarly, since the width-direction side surface 16d has a flat shape, the manufacturing cost can be further reduced.

（第２実施形態）
第１実施形態では、溝１４ｂに取り付けられた二山リング１６に向かって突き出す突起部１４ｃが形成されていたが、図６に示す第２実施形態では二山リング１６から窪む窪み部１４ｆが形成されている。 (Second Embodiment)
In the first embodiment, the protruding portion 14c protruding toward the double ring 16 attached to the groove 14b is formed. However, in the second embodiment shown in FIG. 6, the concave portion 14f recessed from the double ring 16 is formed. Is formed.

これによると、二山リング１６が取付けられたオス側配管１４のオス継手部１４ａをメス側配管１５のメス継手部１５ａに挿入する時に、メス継手部１５ａの内周面１５ｂにより弾性を持つ二山リング１６が押しつぶされる。押しつぶされることにより二山リング１６には応力が発生する。この応力により二山リング１６の二山の頂部１６ａはオス継手部１５の内周面１５ｂに圧接し、一方、二山リング１６の内側面１６ｃは窪み部１４ｆに対応した形状に変形して溝１４ｂおよび窪み部１４ｆに圧接する。   According to this, when the male joint part 14a of the male side pipe 14 to which the double ring 16 is attached is inserted into the female joint part 15a of the female side pipe 15, the inner peripheral surface 15b of the female joint part 15a is more elastic. The mountain ring 16 is crushed. Stress is generated in the double ring 16 by being crushed. Due to this stress, the top 16a of the double ring 16 is pressed against the inner peripheral surface 15b of the male joint 15, while the inner side 16c of the double ring 16 is deformed into a shape corresponding to the recess 14f. 14b and the depression 14f are in pressure contact.

この時、二山リング１６が窪み部１４ｆに押し込まれるように変形するため、溝１４ｂと窪み部１４ｆとの境目Ｂ（中心軸Ａ方向に２ヶ所ある）と二山リング１６との間の圧力が局所的に高くなる。これは二山シール１６の内側面１６ｃと、溝１４ｂと窪み部１４ｆの境目Ｂとが、より密着していることを示している。   At this time, since the double ring 16 is deformed so as to be pushed into the recess 14f, the pressure between the boundary B (there are two places in the direction of the central axis A) between the groove 14b and the recess 14f and the double ring 16 Is locally high. This indicates that the inner surface 16c of the double seal 16 and the boundary B between the groove 14b and the recessed portion 14f are more closely attached.

したがって、溝１４ｂと二山リング１６の内側面１６ｃとの間のシール性能を高めることができる。この効果は二山リング１６のように幅方向（図３中Ｙ方向）に長さがあり、取り付けられる面（溝１４ｂ）に接する内側面１６ｃが平滑な円周面をしているシール部材の場合に特に顕著に現れる。   Therefore, the sealing performance between the groove 14b and the inner surface 16c of the double ring 16 can be enhanced. This effect is the effect of the seal member having a length in the width direction (Y direction in FIG. 3) like the double ring 16 and the inner side surface 16c in contact with the surface to be attached (groove 14b) having a smooth circumferential surface. Especially when it appears.

さらに、二山リング１６が取付けられる溝１４ｂに窪み部１４ｆを形成したため、配管１４、１５の結合時に二山リング１６の内側面１６ｃが窪み部１４ｆに対応して変形する。内側面１６ｃの変形により、溝１４ｂおよび窪み部１４ｆと二山リング１６の内側面１６ｃとの間の中心軸Ａ方向のシール長さ（接している距離）が長くなるため、溝１４ｂと二山リング１６の内側面１６ｃとの間のシール性能を高めることができる。   Furthermore, since the recess 14f is formed in the groove 14b to which the double ring 16 is attached, the inner side surface 16c of the double ring 16 is deformed corresponding to the recess 14f when the pipes 14 and 15 are joined. Due to the deformation of the inner surface 16c, the seal length in the direction of the central axis A (distance in contact) between the groove 14b and the recessed portion 14f and the inner surface 16c of the double ring 16 is increased. The sealing performance between the inner surface 16c of the ring 16 can be enhanced.

なお、本実施形態においても第１実施形態で述べた作用効果（２）〜（６）を発揮することができる。   In the present embodiment, the effects (2) to (6) described in the first embodiment can be exhibited.

（第３実施形態）
第１、第２実施形態では、オス継手部１４ａの外周面に環状弾性シール部材である二山リング１６が取り付けられる溝１４ｂを形成していたが、図７の第３実施形態のオス継手部１４ａは、規制面１４ｅが段付形状となっており、端部側（メス側配管１５側）に一定の外径φＤ２を有する形状になっている。なお、本実施形態では凸継手部の外周面において、二山リング１６が取り付けられる部分は規制面１４ｅから二山リング１６の幅（図３中Ｙ方向の長さ）分の領域１４ｇとなる。 (Third embodiment)
In 1st, 2nd embodiment, although the groove | channel 14b to which the double ring 16 which is a cyclic | annular elastic seal member is attached was formed in the outer peripheral surface of the male joint part 14a, the male joint part of 3rd Embodiment of FIG. In 14a, the regulation surface 14e has a stepped shape, and has a shape having a constant outer diameter φD2 on the end side (female side pipe 15 side). In the present embodiment, on the outer peripheral surface of the convex joint portion, the portion to which the double ring 16 is attached is a region 14g corresponding to the width (length in the Y direction in FIG. 3) of the double ring 16 from the regulating surface 14e.

図３の第１実施形態では、弾性を有する二山リング１６の内径φＤ４をオス側配管１４のオス継手部１４ａの外径φＤ１よりも大きく押し広げて溝１４ｂに取付けなければならなかった。しかし、本実施形態によると二山リング１６をオス継手部１４ａに組付ける時に、弾性を有する二山リング１６の内径φＤ４を押し広げること無く溝１４ｂに取付けることができる。そのため、より簡単に二山リング１６をオス継手部１４ａに組み付けることができ、組み付け時間の短縮や確実な組み付けを行うことができる。   In the first embodiment of FIG. 3, the inner diameter φD4 of the elastic double ring 16 has to be expanded to be larger than the outer diameter φD1 of the male joint portion 14a of the male side pipe 14 and attached to the groove 14b. However, according to this embodiment, when the double ring 16 is assembled to the male joint portion 14a, it can be attached to the groove 14b without expanding the inner diameter φD4 of the elastic double ring 16. Therefore, the double ring 16 can be more easily assembled to the male joint portion 14a, and the assembling time can be shortened or surely assembled.

なお、本実施形態においても第１、第２実施形態で述べた作用効果（１）〜（６）を発揮することができる。   In this embodiment, the effects (1) to (6) described in the first and second embodiments can be exhibited.

（第４実施形態）
本実施形態は、図８に示すように第１実施形態とほぼ同様の構造であるが、オス継手部１４ａの規制面１４ｅに二山リング１６方向（メス側配管１５方向）へ突き出す横突起部１４ｈが形成されている。 (Fourth embodiment)
As shown in FIG. 8, the present embodiment has substantially the same structure as that of the first embodiment, but a lateral protrusion that protrudes in the double ring 16 direction (female-side piping 15 direction) on the regulating surface 14e of the male joint portion 14a. 14h is formed.

ところで、二山リング１６は冷媒の圧力により図中左方向への力を受け、規制面１４ｅに押し付けられる。この時、第１実施形態で述べた二山シール１６と突起部１４ｃの関係（図５）と同様に規制面１４ｅの横突起部１４ｈでは二山シール１６から受ける圧力が高くなっている。これは、二山リング１６の幅方向（図３中Ｙ方向）の側面１６ｄとオス継手部１４ａの規制面１４ｅが、より密着していることを示している。   By the way, the double ring 16 receives a force in the left direction in the figure due to the pressure of the refrigerant and is pressed against the regulating surface 14e. At this time, similarly to the relationship between the double seal 16 and the protrusion 14c described in the first embodiment (FIG. 5), the pressure received from the double seal 16 is high at the lateral protrusion 14h of the regulating surface 14e. This indicates that the side surface 16d in the width direction (Y direction in FIG. 3) of the double ring 16 and the regulating surface 14e of the male joint portion 14a are more closely attached.

これにより、規制面１４ｅと二山リング１６の幅側面１６ｄとの間のシール性能を高めることができる。この効果は二山リング１６のように、規制面１４ｅに接する幅方向（図３中Ｙ方向）の側面１６ｄが平坦な形状をしているシール部材の場合に特に顕著に現れる。   Thereby, the sealing performance between the control surface 14e and the width side surface 16d of the double ring 16 can be improved. This effect is particularly prominent in the case of a sealing member having a flat side surface 16d in the width direction (Y direction in FIG. 3) in contact with the regulating surface 14e, such as the double ring 16.

なお、本実施形態においても第１〜第３実施形態で述べた作用効果（１）〜（６）を発揮することができる。   In this embodiment, the operational effects (1) to (6) described in the first to third embodiments can be exhibited.

（第５実施形態）
第１〜第４実施形態では、オス側配管１４のオス継手部１４ａに二山リング１６を取り付けた例を示したが、図９に示す第５実施形態では、メス継手部１５ａの内周部１６ｂに環状弾性シール部材である内二山リング１９を取り付ける取り付け領域１５ｄが配置されている。 (Fifth embodiment)
In 1st-4th embodiment, although the example which attached the double ring 16 to the male joint part 14a of the male side piping 14 was shown, in 5th Embodiment shown in FIG. 9, the inner peripheral part of the female joint part 15a An attachment region 15d for attaching the inner double ring 19 which is an annular elastic seal member is disposed at 16b.

内二山リング１９は、第１〜第４実施形態で述べた二山リング１６の内側面１６ｃと外側面１６ａが逆になった形状をしており、内側面１９ａに２つの頂部１９ｂを備えている。なお、内二山リング１９の外側面１９ｃは平滑な円周面になっている。また、内周部１５ｂの取り付け領域１５ｄには内二山リング１９（中心軸Ａ方向）へ向かって突き出す内突起部１５ｅが形成されている。   The inner double ring 19 has a shape in which the inner side surface 16c and the outer side surface 16a of the double ring 16 described in the first to fourth embodiments are reversed, and includes two top portions 19b on the inner side surface 19a. ing. The outer surface 19c of the inner double ring 19 is a smooth circumferential surface. In addition, an inner projection 15e protruding toward the inner double ring 19 (in the direction of the central axis A) is formed in the attachment region 15d of the inner peripheral portion 15b.

内二山リング１９のメス継手部１５ａへの組み付け時には、内二山リング１９を幅方向側面１９ｄがメス継手部１５ａの段付部１５ｆに突き当たるまで挿入する。その後、オス継手部１４ａを挿入すると、オス継手部１４ａの外径が内二山リング１９の内径よりも大きいため、弾性を持つ内二山リング１９が押しつぶされる。押しつぶされることにより内二山リング１９には応力が発生し、この応力により内二山リング１９の二山の頂部１９ａはオス継手部１４ａの外周面に圧接し、内二山リング１９の外側面１９ｃは取り付け領域１５ｄおよび取り付け領域１５ｄに形成された内突起部１５ｅに圧接する。   When the inner double ring 19 is assembled to the female joint portion 15a, the inner double ring 19 is inserted until the side surface 19d in the width direction hits the stepped portion 15f of the female joint portion 15a. Thereafter, when the male joint portion 14a is inserted, the outer diameter of the male joint portion 14a is larger than the inner diameter of the inner double ring 19 so that the elastic inner ring 19 is crushed. By being crushed, a stress is generated in the inner double ring 19, and by this stress, the top 19 a of the two peaks of the inner double ring 19 is pressed against the outer peripheral surface of the male joint portion 14 a, and the outer surface of the inner double ring 19 is 19c press-contacts to the attachment area | region 15d and the inner projection part 15e formed in the attachment area | region 15d.

本実施形態では、第１実施形態の図５と同様の関係により、取り付け領域１５ｄの内突起部１５ｅと内二山シール１９の外側面１９ｃとの間の圧力が局所的に高くなっている。そのため、取り付け領域１５ｄと内二山リング１９の外側面１６ｃとの間のシール性能を高めることができる。   In the present embodiment, the pressure between the inner protrusion 15e of the attachment region 15d and the outer surface 19c of the inner double seal 19 is locally high due to the same relationship as in FIG. 5 of the first embodiment. Therefore, the sealing performance between the attachment region 15d and the outer surface 16c of the inner double ring 19 can be enhanced.

また、内二山リング１９の幅側面１９ｄは冷媒の圧力により図９中左方向への力を受け、規制面１４ｅに押し付けられる。この時、第１実施形態で述べた内二山シール１９と突起部１４ｃの関係（図５）と同様に規制面１４ｅの横突起部１４ｈと二山シール１６の幅側面１６ｄとの間の圧力が局所的に高くなっている。そのため、第４実施形態と同様に規制面１４ｅと内二山リング１９の幅側面１９ｄとの間のシール性能を高めることができる。   Further, the width side surface 19d of the inner double ring 19 receives a force in the left direction in FIG. 9 due to the pressure of the refrigerant and is pressed against the regulating surface 14e. At this time, the pressure between the lateral protrusion 14h of the restricting surface 14e and the width side surface 16d of the double seal 16 is similar to the relationship between the inner double seal 19 and the protrusion 14c described in the first embodiment (FIG. 5). Is locally high. Therefore, the sealing performance between the regulation surface 14e and the width side surface 19d of the inner double ring 19 can be enhanced as in the fourth embodiment.

さらに、第１実施形態と同様の関係により、規制面１４ｅおよび横突起部１４ｈと二山リング１６の幅側面１６ｄとの間の中心軸Ａ方向のシール長さ（接している距離）が長くなるため、規制面１４ｅと二山リング１６の幅方向側面１６ｄとの間のシール性能を高めることができる。   Further, due to the same relationship as in the first embodiment, the seal length (contact distance) in the central axis A direction between the regulating surface 14e and the lateral protrusion 14h and the width side surface 16d of the double ring 16 is increased. Therefore, the sealing performance between the regulation surface 14e and the width direction side surface 16d of the double ring 16 can be enhanced.

なお、本実施形態では規制面１４ｅに横突起部１４ｈを形成した例を示したが、この横突起部１４ｈは窪み形状、または凹凸が無い形状であってもよい。そして、本実施形態においても第１〜第３実施形態で述べた作用効果（２）〜（６）を発揮することができる。ただし、二山リング１６の内側面１６ｃは、内二山リング１９の外側面１９ｃに、外側面１６ａは内側面１９ａに、頂部１６ｂは頂部１９ｂに幅方向側面１６ｄは幅方向側面１９ｄにそれぞれ該当する。   In the present embodiment, an example in which the lateral protrusion 14h is formed on the regulation surface 14e has been described. However, the lateral protrusion 14h may have a recessed shape or a shape without unevenness. And also in this embodiment, the effect (2)-(6) described in the 1st-3rd embodiment can be exhibited. However, the inner side surface 16c of the double ring 16 corresponds to the outer side surface 19c of the inner double ring 19, the outer side surface 16a corresponds to the inner side surface 19a, the top portion 16b corresponds to the top portion 19b, and the width direction side surface 16d corresponds to the width direction side surface 19d. To do.

（他の実施形態）
上述の実施形態では、車両用空調装置の冷媒配管１４、１５に本発明を適用した例を示したが、車両用に限られるものではなく空調装置の冷媒配管であってもよい。また、本発明は冷媒配管に限られるものではなく流体の経路を形成する配管に適用可能である。 (Other embodiments)
In the above-mentioned embodiment, although the example which applied this invention to the refrigerant | coolant piping 14 and 15 of a vehicle air conditioner was shown, it is not restricted to vehicles, The refrigerant | coolant piping of an air conditioner may be sufficient. Further, the present invention is not limited to the refrigerant pipe, and can be applied to a pipe that forms a fluid path.

また、上述の実施形態では配管部材１４、１５が略円筒形状の管の例を示したが、オス継手部１４ａとメス継手部１５ａが嵌め合い形状で、両継手部１４ａ、１５ａの間に環状弾性シール部材１６、１９が配置されていれば管の形状は楕円、角管等種々変更可能である。   Moreover, although the piping members 14 and 15 showed the example of the substantially cylindrical pipe | tube in the above-mentioned embodiment, the male joint part 14a and the female joint part 15a are fitting shape, and it is cyclic | annular between both joint parts 14a and 15a. If the elastic seal members 16 and 19 are disposed, the shape of the tube can be variously changed such as an ellipse or a square tube.

また、上述の実施形態では、配管１４、１５の材料としてアルミを使用した例を示したが使用条件、例えば前述の耐食性等を満たす材料、一例としてアルミ以外の金属、または非金属、一例として樹脂の成形品であってもよい。   Moreover, in the above-mentioned embodiment, although the example which used aluminum as a material of the piping 14 and 15 was shown, the material which satisfy | fills use conditions, for example, the above-mentioned corrosion resistance etc., as an example, metals other than aluminum, or nonmetal, as an example resin It may be a molded article.

また、上述の実施形態では、二山リング１６の内側面１６ｃ、内二山リング１９の外側面１９ｃおよび幅方向側面１６ｄ、１９が平坦な形状の例を示したが、本発明では内側面１６ｃ、外側面１９ｃおよび幅方向側面１６ｄが平坦な形状でなくても凹凸形状１４ｃ、１４ｆ、１４ｈ、１５ｅによりシール性を向上することができる。さらに、環状弾性シール部材１６、１９は山の頂部１６ｂ、１９ｂが２個以上のものでもよく、頂部１６ｂ、１９ｂが１つのものであってもよい。   In the above-described embodiment, the inner side surface 16c of the double ring 16 and the outer side surface 19c and the width direction side surfaces 16d, 19 of the inner double ring 19 are flat. Even if the outer side surface 19c and the side surface 16d in the width direction are not flat, the unevenness 14c, 14f, 14h, and 15e can improve the sealing performance. Further, the annular elastic seal members 16 and 19 may have two or more crests 16b and 19b, and may have one crest 16b and 19b.

また、上述の第４、第５実施形態では、二山リング１６、１９の幅方向側面１６ｄ、１９ｄの両方が平坦な形状の例を示したが、規制面１４ｅに接する側面１６ｄ、１９ｄのみが平坦な形状であってもよい。しかし、環状弾性シール部材１６、１９の規制面１４ｅに接する側面１６ｄ、１９ｄのみが平坦な形状であると組み付け方向が決まってしまい組付け性が悪くなってしまう。したがって、組み付け方向に指定がない幅方向側面１６ｄ、１９ｄの両方が平坦な形状、つまり幅方向に対称な形状が一般的である。   In the fourth and fifth embodiments described above, both the width direction side surfaces 16d and 19d of the double rings 16 and 19 are flat. However, only the side surfaces 16d and 19d in contact with the regulating surface 14e are provided. It may be a flat shape. However, if only the side surfaces 16d and 19d in contact with the regulating surface 14e of the annular elastic seal members 16 and 19 have a flat shape, the assembling direction is determined and the assembling property is deteriorated. Therefore, a shape in which both of the side surfaces 16d and 19d in the width direction that are not specified in the assembling direction are flat, that is, a shape that is symmetrical in the width direction is common.

また、上述の実施形態では、二山リング１６、１９の材料としてＥＰＤＭを使用した例を示したが、二山リング１６、１９の材料はＥＰＤＭに限られるものではなく他のゴム材料、熱可塑性エラストマ、弾性を有する樹脂等様々に変更可能である。   In the above-described embodiment, the example in which EPDM is used as the material of the double rings 16 and 19 is shown. However, the material of the double rings 16 and 19 is not limited to EPDM, and other rubber materials and thermoplastics. Various changes such as elastomer and elastic resin can be made.

また、上述の実施形態では、二山リング１６、１９が略リング形状の例を示したが、略リング形状とは弾性シール部材が閉ループ形状であることを意味しており、楕円形状等も含まれる。この時、請求項３、５中の凹凸形状（１４ｃ、１４ｆ、１５ｅ）に接する内側面（１６ｃ）または外側面（１９ｃ）の平滑な円周面とは、当然にループ形状に対応した面形状となる。

Moreover, in the above-mentioned embodiment, although the double ring 16 and 19 showed the example of substantially ring shape, substantially ring shape means that an elastic seal member is closed loop shape, and elliptical shape etc. are also included. It is. At this time, the smooth circumferential surface of the inner surface ( 16c ) or the outer surface ( 19c ) in contact with the uneven shape (14 c, 14 f, 15 e) in claims 3 and 5 is naturally a surface shape corresponding to the loop shape. It becomes.

また、上述の実施形態では管形状の配管部材１４、１５同士を継いで、流体（冷媒）経路を延長した例を示したが、配管部材には部材内で流体経路を分岐・合流させる部材も含まれる。したがって、オス継手部とメス継手部を有する一組の管と分岐・合流部材、または分岐・合流部材同士を継いで流体経路を延長、分岐させてもよい。   Moreover, although the pipe-shaped piping members 14 and 15 were connected in the above-mentioned embodiment, the example which extended the fluid (refrigerant) path | route was shown, The member which branches and joins a fluid path | route within a member is also included in a piping member. included. Therefore, the fluid path may be extended or branched by connecting a pair of pipes having a male joint part and a female joint part and a branch / merge member, or branch / merge members.

また、上述の実施形態では規制面と段付き面が別になっている例を示したが、規制面のみを形成し、規制面に段付き面としての機能を持たせてもよい。   In the above-described embodiment, an example in which the regulation surface and the stepped surface are separate from each other is shown, but only the regulation surface may be formed, and the regulation surface may have a function as a stepped surface.

本発明を車両用空調装置に適用した第１実施形態を示す斜視図である。1 is a perspective view showing a first embodiment in which the present invention is applied to a vehicle air conditioner. 第１実施形態に係る配管継手のシール構造を示す半断面図である。It is a half sectional view showing a seal structure of a pipe joint concerning a 1st embodiment. 第１実施形態に係るオス側配管の形状、環状弾性シール部材の形状およびこれらの組付け方法を示す半断面図である。It is a half sectional view showing the shape of male side piping concerning the 1st embodiment, the shape of an annular elastic seal member, and these assembly methods. 第１実施形態に係るメス側配管の形状およびメス側配管とオス側配管との組付け方法を示す半断面図である。It is a half sectional view showing the method of assembling the shape of the female pipe and the female pipe and the male pipe according to the first embodiment. （ａ）比較例１において二山シールからオス継手部が受ける圧力の分布、（ｂ）第１実施形態において二山シールからオス継手部が受ける圧力の分布をそれぞれ示した図である。(A) It is the figure which showed distribution of the pressure which a male joint part receives from a double seal in the comparative example 1, and (b) Distribution of the pressure which a male joint part receives from a double seal in 1st Embodiment, respectively. 第２実施形態に係る配管継手のシール構造を示す半断面図である。It is a half sectional view showing a seal structure of a pipe joint concerning a 2nd embodiment. 第３実施形態に係る配管継手のオス継手部を示す半断面図である。It is a half sectional view showing a male joint part of a pipe joint concerning a 3rd embodiment. 第４実施形態に係る配管継手のシール構造を示す半断面図である。It is a half sectional view showing a seal structure of a pipe joint concerning a 4th embodiment. 第５実施形態に係る配管継手のシール構造を示す半断面図である。It is a half sectional view showing a seal structure of a pipe joint concerning a 5th embodiment. 特許文献１（従来例）に係る配管継手のシール構造を示す断面図である。It is sectional drawing which shows the seal structure of the piping joint which concerns on patent document 1 (conventional example). 比較例１に係る配管継手のシール構造を示す半断面図である。6 is a half cross-sectional view showing a seal structure of a pipe joint according to Comparative Example 1. FIG.

符号の説明Explanation of symbols

１４…オス側配管部材、１４ａ…オス継手部、１４ｃ…突起部（凹凸形状）、
１４ｅ…規制面、１４ｆ…窪み部（凹凸形状）、１４ｈ…横突起部（凹凸形状）、
１５…メス側配管部材、１５ａ…メス継手部、１５ｂ…内周面、
１５ｅ…内突起部（凹凸形状）、１６…二山リング（環状弾性シール部材）、
１６ａ…外側面、１６ｂ…頂部、１６ｃ…内側面、１６ｄ…幅方向側面、
１９…内二山リング（環状弾性シール部材）、１９ａ…内側面、１９ｂ…頂部、
１９ｃ…外側面、１９ｄ…幅方向側面。 14 ... male-side piping member, 14a ... male joint part, 14c ... projection part (uneven shape),
14e ... restriction surface, 14f ... depression (uneven shape), 14h ... lateral protrusion (uneven shape),
15 ... Female piping member, 15a ... Female joint, 15b ... Inner peripheral surface,
15e ... inner protrusion (uneven shape), 16 ... double ring (annular elastic seal member),
16a ... outer side surface, 16b ... top, 16c ... inner side surface, 16d ... width side surface,
19 ... Inner ring ring (annular elastic seal member), 19a ... Inner side surface, 19b ... Top,
19c ... Outer side surface, 19d ... Side surface in the width direction.

Claims (5)

オス継手部（１４ａ）を有するオス側配管部材（１４）と、
メス継手部（１５ａ）を有するメス側配管部材（１５）と、
前記オス継手部（１４ａ）の外周面、または前記メス継手部（１５ａ）の内周面（１５ｂ）に配置される環状弾性シール部材（１６、１９）とを備え、
前記オス継手部（１４ａ）と前記メス継手部（１５ａ）の前記内周面（１５ｂ）を嵌め合わせることにより、前記両配管部材（１４、１５）を結合し、
前記オス継手部（１４ａ）と前記メス継手部（１５ａ）が結合した状態において、前記環状弾性シール部材（１６、１９）が前記外周面と前記内周面（１５ｂ）との間で、前記外周面および前記内周面（１５ｂ）に圧接し、
前記外周面または前記内周面（１５ｂ）には、前記環状弾性シール部材（１６、１９）に凹凸を形成する少なくとも１つの凹凸形状（１４ｃ、１４ｆ、１５ｅ）が形成され、
前記オス側配管部材（１４）には、前記環状弾性シール部材（１６、１９）が前記流体から圧力を受けた状態において、前記環状弾性シール部材（１６、１９）のずれを規制する規制面（１４ｅ）が備えられており、
前記規制面（１４ｅ）には、前記環状弾性シール部材（１６、１９）に凹凸を形成する少なくとも１つの別の凹凸形状（１４ｈ）が形成されていることを特徴とする配管継手のシール構造。 A male pipe member (14) having a male joint part (14a);
A female pipe member (15) having a female joint part (15a);
An annular elastic seal member (16, 19) disposed on the outer peripheral surface of the male joint portion (14a) or the inner peripheral surface (15b) of the female joint portion (15a);
By fitting the male joint part (14a) and the inner peripheral surface (15b) of the female joint part (15a), the pipe members (14, 15) are combined,
In a state where the male joint portion (14a) and the female joint portion (15a) are coupled, the annular elastic seal member (16, 19) is disposed between the outer peripheral surface and the inner peripheral surface (15b). The surface and the inner peripheral surface (15b),
The outer peripheral surface or the inner peripheral surface (15b) is formed with at least one uneven shape (14c, 14f, 15e) that forms unevenness on the annular elastic seal member (16, 19) .
The male side piping member (14) is provided with a regulating surface for restricting the displacement of the annular elastic seal member (16, 19) in a state where the annular elastic seal member (16, 19) receives pressure from the fluid. 14e) is provided,
A pipe joint seal structure, wherein the regulating surface (14e) is formed with at least one other irregular shape (14h) that forms irregularities on the annular elastic seal member (16, 19) . 前記環状弾性シール部材は、前記内側面（１６ｃ、１９ａ）および前記外側面（１６ａ、１９ｃ）のうち、前記凹凸形状（１４ｃ、１４ｆ、１５ｅ）に接していない面において、前記両配管部材（１４、１５）の中心軸Ａ方向に複数の頂部（１６ｂ、１９ｂ）を形成した複数山リング（１６、１９）であることを特徴とする請求項１に記載の配管継手のシール構造。 The annular elastic sealing member is formed on the inner surface (16c, 19a) and the outer surface (16a, 19c) on the pipe member (14) on the surface not in contact with the concavo-convex shape (14c, 14f, 15e). 15) The pipe joint seal structure according to claim 1 , wherein the ring joint is a plurality of crest rings (16, 19) formed with a plurality of top portions (16b, 19b) in the direction of the central axis A. 前記複数山リング（１６、１９）は単体状態において、前記内側面（１６ｃ、１９ａ）および前記外側面（１６ａ、１９ｃ）のうち、前記凹凸形状（１４ｃ、１４ｆ、１５ｅ）に接する面が平滑な円周面であることを特徴とする請求項２に記載の配管継手のシール構造。 In the single state, the plurality of mountain rings (16, 19) have a smooth surface in contact with the concavo-convex shape (14c, 14f, 15e) among the inner surface (16c, 19a) and the outer surface (16a, 19c). The pipe joint seal structure according to claim 2 , wherein the seal structure is a circumferential surface. 前記複数山リング（１６、１９）は単体状態において、前記複数山リング（１６、１９）の幅方向側面（１６ｄ、１９ｄ）のうち、少なくとも前記別の凹凸形状（１４ｈ）に接する面が平坦な形状であることを特徴とする請求項２または３に記載の配管継手のシール構造。 When the plurality of mountain rings (16, 19) are in a single state, at least one of the side surfaces (16d, 19d) in the width direction of the plurality of mountain rings (16, 19) in contact with the other uneven shape (14h) is flat. The pipe joint seal structure according to claim 2 , wherein the pipe joint has a shape. オス継手部（１４ａ）を有するオス側配管部材（１４）と、
メス継手部（１５ａ）を有するメス側配管部材（１５）と、
前記オス継手部（１４ａ）の外周面、または前記メス継手部（１５ａ）の内周面（１５ｂ）に配置される環状弾性シール部材（１６、１９）とを備え、
前記オス継手部（１４ａ）と前記メス継手部（１５ａ）の前記内周面（１５ｂ）を嵌め合わせることにより、前記両配管部材（１４、１５）を結合し、
前記オス継手部（１４ａ）と前記メス継手部（１５ａ）が結合した状態において、前記環状弾性シール部材（１６、１９）が前記外周面と前記内周面（１５ｂ）との間で、前記外周面および前記内周面（１５ｂ）に圧接し、
前記外周面または前記内周面（１５ｂ）には、前記環状弾性シール部材（１６、１９）に凹凸を形成する少なくとも１つの凹凸形状（１４ｃ、１４ｆ、１５ｅ）が形成され、
前記環状弾性シール部材は、前記内側面（１６ｃ、１９ａ）および前記外側面（１６ａ、１９ｃ）のうち、前記凹凸形状（１４ｃ、１４ｆ、１５ｅ）に接していない面において、前記両配管部材（１４、１５）の中心軸Ａ方向に複数の頂部（１６ｂ、１９ｂ）を形成した複数山リング（１６、１９）であり、
前記複数山リング（１６、１９）は単体状態において、前記内側面（１６ｃ、１９ａ）および前記外側面（１６ａ、１９ｃ）のうち、前記凹凸形状（１４ｃ、１４ｆ、１５ｅ）に接する面が平滑な円周面であることを特徴とする配管継手のシール構造。 A male pipe member (14) having a male joint part (14a);
A female pipe member (15) having a female joint part (15a);
An annular elastic seal member (16, 19) disposed on the outer peripheral surface of the male joint portion (14a) or the inner peripheral surface (15b) of the female joint portion (15a);
By fitting the male joint part (14a) and the inner peripheral surface (15b) of the female joint part (15a), the pipe members (14, 15) are combined,
In a state where the male joint portion (14a) and the female joint portion (15a) are coupled, the annular elastic seal member (16, 19) is disposed between the outer peripheral surface and the inner peripheral surface (15b). The surface and the inner peripheral surface (15b),
The outer peripheral surface or the inner peripheral surface (15b) is formed with at least one uneven shape (14c, 14f, 15e) that forms unevenness on the annular elastic seal member (16, 19) .
The annular elastic sealing member is formed on the inner surface (16c, 19a) and the outer surface (16a, 19c) on the pipe member (14) on the surface not in contact with the concavo-convex shape (14c, 14f, 15e). 15) a plurality of mountain rings (16, 19) formed with a plurality of top portions (16b, 19b) in the direction of the central axis A.
In the single state, the plurality of mountain rings (16, 19) have a smooth surface in contact with the concavo-convex shape (14c, 14f, 15e) among the inner surface (16c, 19a) and the outer surface (16a, 19c). A pipe joint seal structure characterized by a circumferential surface .
JP2003374598A 2003-11-04 2003-11-04 Pipe joint seal structure Expired - Fee Related JP4103777B2 (en)

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