JPS6339371Y2 - - Google Patents
Info
- Publication number
- JPS6339371Y2 JPS6339371Y2 JP1980102602U JP10260280U JPS6339371Y2 JP S6339371 Y2 JPS6339371 Y2 JP S6339371Y2 JP 1980102602 U JP1980102602 U JP 1980102602U JP 10260280 U JP10260280 U JP 10260280U JP S6339371 Y2 JPS6339371 Y2 JP S6339371Y2
- Authority
- JP
- Japan
- Prior art keywords
- tube
- seal ring
- pipe
- tip
- receiving hole
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 238000002485 combustion reaction Methods 0.000 claims description 9
- 239000002184 metal Substances 0.000 claims description 7
- 229910052751 metal Inorganic materials 0.000 claims description 7
- 238000007789 sealing Methods 0.000 description 16
- 230000008602 contraction Effects 0.000 description 4
- 229910001018 Cast iron Inorganic materials 0.000 description 3
- 239000013013 elastic material Substances 0.000 description 3
- 229910001220 stainless steel Inorganic materials 0.000 description 3
- 239000010935 stainless steel Substances 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 239000007769 metal material Substances 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 230000002542 deteriorative effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 229910002804 graphite Inorganic materials 0.000 description 1
- 239000010439 graphite Substances 0.000 description 1
- 239000003779 heat-resistant material Substances 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000006116 polymerization reaction Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 229910000859 α-Fe Inorganic materials 0.000 description 1
Landscapes
- Exhaust Silencers (AREA)
- Joints With Pressure Members (AREA)
- Joints With Sleeves (AREA)
Description
【考案の詳細な説明】
本考案は内燃機関の排気マニホールド、ターボ
過給機のタービン側及びこれらを連結する管、あ
るいは排気マニホールドと消音器（マフラー）間
を連結する管等（これらを排気管と総称する）の
接続装置に関するものである。[Detailed description of the invention] This invention is applicable to the exhaust manifold of an internal combustion engine, the turbine side of a turbocharger, and the pipe connecting these, or the pipe connecting the exhaust manifold and a muffler (these are exhaust pipes). (collectively referred to as ) connection devices.
前記の如き排気管の接続装置は、高温高圧が通
過し、しかも振動をうけるので各管の間のシール
が非常に難しい。 The above-mentioned exhaust pipe connecting device passes high temperature and high pressure and is subject to vibration, making it very difficult to seal between the pipes.
従来例えば第３図に示すように、接続すべき一
方の管Ａの端部を他方の管Ｂの端部に形成した受
け穴Ｃ内に挿入し、前記管Ａの外径部に形成した
溝内に耐熱材料からなるシールリングＤを嵌め込
んで該シールリングＤの外周を他方の管Ｂの内周
に接触させ前記管Ａ，Ｂ間のシールを行うように
したものが知られているが、このような装置で
は、管Ａ，Ｂ内を流れる高温ガスによつて管Ａ，
Ｂが膨張収縮をくり返すため、前記シールリング
Ｄの接触面が摩耗して気密保持作用が劣化しガス
洩れが生ずることが多かつた。又、前記構造では
曲管になじみ難く、密封性をよくしようとして圧
入すると亀裂を生ずる等の欠点を有していた。 Conventionally, for example, as shown in FIG. 3, the end of one pipe A to be connected is inserted into a receiving hole C formed at the end of the other pipe B, and a groove is formed on the outer diameter of said pipe A. It is known that a seal ring D made of a heat-resistant material is fitted inside the tube, and the outer periphery of the seal ring D is brought into contact with the inner periphery of the other tube B to seal between the tubes A and B. , in such a device, the tubes A, B are heated by high temperature gas flowing in the tubes A, B.
Since B repeats expansion and contraction, the contact surface of the seal ring D wears out, deteriorating its airtightness and often causing gas leakage. In addition, the structure described above has the disadvantage that it is difficult to fit into a curved pipe, and cracks occur when press-fitted to improve sealing performance.
上記のシールリングＤが摩耗するという欠点は
他方の管の受け穴Ｃに挿入される一方の管Ａの先
端外径部を球面状とした装置においては、シール
リングが一本しか使用できないことから甚しく、
シールリングの耐久性を著しく欠いていた。 The drawback that the seal ring D wears out is that only one seal ring can be used in a device in which the outer diameter of the tip of one tube A that is inserted into the receiving hole C of the other tube is spherical. seriously,
The durability of the seal ring was significantly lacking.
このため実公昭51−13632号公報に示される分
割型エキゾーストマニホルドの接続構造の如く、
エキゾーストマニホルドの継目部に、耐熱金属材
より成り中央部に熱膨張を吸収する環状湾曲部を
形成した接続部材を嵌合して気密接続してなるも
のもあるが、気密は接続部材におけるエキゾース
トマニホルドの継目部に接する両側面で行うのみ
であるから、前記接続部材の軸心方向の弾性及び
エキゾーストマニホルドの熱膨張力による密着力
は利用できても、前記環状湾曲部への半径方向の
弾性力やマニホルド内に作用するガス圧力は利用
できずシール性が充分でない。又前記接続部材の
環状湾曲部にかゝる力やガス圧のくり返しによつ
て該湾曲部が必要以上に撓んで接続部材のフラン
ジがマニホルド内径面への密着と剥離をくり返
し、上記フランジがマニホルド内径に密着したと
きは、密封性はよくなつてもマニホルドの膨張、
収縮に際して摩擦力が大となり、各部に無用の応
力を発生させるとともに、前記フランジがマニホ
ルド内径から剥離したときは密封性が悪くなるな
ど温度等によつてその密封性が変化する欠点があ
る。 For this reason, as in the connection structure of the split type exhaust manifold shown in Japanese Utility Model Publication No. 13632/1983,
Some exhaust manifolds are airtightly connected by fitting a connecting member made of a heat-resistant metal material and having an annular curved part in the center that absorbs thermal expansion into the joint of the exhaust manifold. Since this is done only on both sides that contact the joint of the connecting member, even though the elasticity in the axial direction of the connecting member and the adhesion force due to the thermal expansion force of the exhaust manifold can be used, the elastic force in the radial direction on the annular curved portion can be used. The gas pressure acting inside the manifold cannot be used and the sealing performance is insufficient. Further, due to the repeated force and gas pressure applied to the annular curved portion of the connecting member, the curved portion is bent more than necessary, and the flange of the connecting member repeatedly comes into close contact with and peels off from the inner diameter surface of the manifold. If it is in close contact with the inner diameter, the sealing performance may be good, but the manifold may expand,
Frictional force becomes large during contraction, generating unnecessary stress in various parts, and there is a drawback that the sealing performance changes depending on temperature etc., such as poor sealing performance when the flange peels off from the inner diameter of the manifold.
また、実開昭54−142712号公報にはシリンダヘ
ツドへの排気マニホルドの取付部として断面Ｃ形
Ｏリングをマニホルドの取付部フランジ端面に設
けた凹部に介挿し、シリンダヘツドに押付けるも
のが示されているが、これは単にＯリングをフラ
ンジの凹部に介挿してシリンダヘツド平面に押し
つけたもので、一方の管の穴の中に他方の管端を
挿入した部分を密封しようとするものではなく、
又前記Ｏリングは前記凹部円で保持され２乃至３
箇所当接しているが、一方シリンダヘツド側は１
箇所でその当接のバランス及び安定性が悪く、又
線状に接するので密着性もよくないという欠点が
ある。 Furthermore, Japanese Utility Model Application Publication No. 54-142712 discloses a method for attaching an exhaust manifold to the cylinder head by inserting an O-ring with a C-shaped cross section into a recess provided on the end face of the flange of the attachment part of the manifold and pressing it against the cylinder head. However, this is simply an O-ring inserted into a recess in the flange and pressed against the cylinder head plane, and is not intended to seal the part where the end of one tube is inserted into the hole of the other tube. Without,
Further, the O-ring is held in the recessed circle and has a diameter of 2 to 3.
The parts are in contact with each other, but on the other hand, there is 1 on the cylinder head side.
There are disadvantages in that the balance and stability of the contact is poor at certain points, and the adhesion is also poor because of the linear contact.
また、米国特許第3550987号明細書には、一方
の管の先端及びこれが嵌入される他方の管の受け
穴と内径部管に形成された空間に、弾性物質製シ
ールリングを配設した構造が示されているが、こ
のシールリングは弾性物質製故、管内を排気ガス
が流れる場合劣化が激しく、また半径方向にはふ
くらみの外周が前記一方の管の溝の底に接してな
いので半径方向のシールは期待できないほか、２
本の管を屈曲させる力がかかつたとき順応できな
い。 Further, US Pat. No. 3,550,987 discloses a structure in which a seal ring made of an elastic material is provided in the space formed in the receiving hole and the inner diameter tube of the tip of one tube and the other tube into which it is inserted. As shown in the figure, since this seal ring is made of an elastic material, it deteriorates rapidly when exhaust gas flows inside the pipe, and the outer circumference of the bulge does not contact the bottom of the groove of the one pipe in the radial direction. In addition to not expecting a sticker of 2
When a force is applied to a book tube to bend it, it cannot adapt.
また、実開昭52−156318号公報には管継手のシ
ールリングとして外径方向にふくらみをもつたシ
ールリングの構成が示されているが、このシール
リングも弾性物質製故、管内を排気ガスが流れる
場合劣化が激しく耐久性の点で排気管の接続装置
として使用出来ないほか、２本の管を屈曲させる
力がかかつたとき順応できない。 Furthermore, Japanese Utility Model Application Publication No. 52-156318 discloses a structure of a seal ring that bulges in the outer diameter direction as a seal ring for a pipe joint, but this seal ring is also made of an elastic material, so that the exhaust gas cannot be It deteriorates severely when water flows through it, making it unusable as a connecting device for exhaust pipes due to its durability, and it also cannot adapt when a force is applied to bend the two pipes.
更に、特公昭48−38659号公報には、全体的に
Ｕ字状横断面を有し、且つ取付られる管より熱膨
脹係数が小さいシート状金属よりなる２つの層よ
り形成された環状部材と、前記２つの層が相対的
に変位運動しないようにそれらの層を一体にする
手段とよりなり、前記２つの層は内側層の方が外
側層よりも大きい熱膨脹係数を有しており、温度
上昇により前記Ｕ字状横断面を有する部材の脚が
散開するようにされた管継手のフランジ間に使用
される流体シール構造が示されているが、これは
繁ぐべき２つの管の軸方向又は半径方向のいずれ
かに前記脚が散開する力を付勢させるのみで、軸
方向及び半径方向の両方向に付勢してシール性を
向上させるものではなく、また上記両管は屈曲へ
の順応性を欠いている。 Furthermore, Japanese Patent Publication No. 48-38659 discloses an annular member formed of two layers of sheet metal having an overall U-shaped cross section and a coefficient of thermal expansion smaller than that of the pipe to which it is attached; The two layers have a means of uniting them so that there is no relative displacement movement, the inner layer having a larger coefficient of thermal expansion than the outer layer, and the inner layer having a higher coefficient of thermal expansion than the outer layer. A fluid seal structure is shown for use between the flanges of a pipe fitting in which the legs of the member having a U-shaped cross-section are spread apart, but this is not limited to the axial or radial direction of the two pipes to be joined. It only applies the force for the legs to spread out in one of the directions, but does not apply the force in both the axial and radial directions to improve sealing performance, and both tubes have good adaptability to bending. Lacking.
また、実開昭54−183519号に係る明細書及び図
面には、複数に分割された鋳鉄製マニホルド部材
を接続して一体化される排気マニホルドにおい
て、相接続する一方の排気マニホルド部材の端部
外周面と、これより大径に形成された他方のマニ
ホルド部材の端部内周面とを、これらの間にマニ
ホルド部材とは異質金属材料（ステンレス等）か
らなる中間スリーブを介して重合接続し、該中間
スリーブをいずれか一方のマニホルド部材に嵌着
し、他方のマニホルド部材と摺動自由に密接して
介装した機構が示されている。 Furthermore, in the specification and drawings of Utility Model Application Publication No. 54-183519, in an exhaust manifold in which a plurality of divided cast iron manifold members are connected and integrated, the end of one exhaust manifold member that is connected to each other is described. The outer circumferential surface and the inner circumferential surface of the end of the other manifold member formed to have a larger diameter are connected by polymerization between them via an intermediate sleeve made of a metal material (such as stainless steel) different from that of the manifold member, A mechanism is shown in which the intermediate sleeve is fitted onto one of the manifold members and is slidably and closely interposed with the other manifold member.
しかし、例えば上記図面第４図に示された中間
スリーブも、排気マニホルドの軸方向にのみスプ
リング効果を発揮するのみで、軸方向及び半径方
向の両方向に付勢してシール性を向上させるもの
ではなく、また上記両マニホルドの屈曲への順応
性はない。 However, for example, the intermediate sleeve shown in FIG. 4 above only exerts a spring effect in the axial direction of the exhaust manifold, and does not improve the sealing performance by applying pressure in both the axial and radial directions. There is no bending flexibility in both manifolds.
本考案は以上のような従来装置のもつ欠点を除
去し、密封性及び密封すべき管の膨脹収縮に対す
る順応性を優れたしかも耐久性のある排気管の接
続装置を提供することを目的としてなされたもの
で、その要旨とするところは、一方の管における
軸心を含む断面が球面状をなす先端及びこれが嵌
入される他方の管の直管状の受け穴と内径部間に
形成された肩の間に、外径方向にふくらみをも
ち、前記両管の熱膨脹率より小さい熱膨脹率の耐
熱金属板製シールリングを、その両側部が前記肩
と一方の管の先端に、また前記ふくらみの外径部
が受け穴の内径面に、それぞれ当接するよう配設
してなる内燃機関の排気管の接続装置にある。 The present invention has been made for the purpose of eliminating the above-mentioned drawbacks of conventional devices and providing an exhaust pipe connecting device that has excellent sealing performance and adaptability to the expansion and contraction of the pipe to be sealed, and is also durable. The gist of this is that the tip of one tube has a spherical cross section including the axis, and the shoulder formed between the straight receiving hole and the inner diameter of the other tube into which the tip is inserted. In between, there is a seal ring made of a heat-resistant metal plate having a bulge in the outer diameter direction and having a coefficient of thermal expansion smaller than that of both tubes, and its both sides are attached to the shoulder and the tip of one of the tubes, and the outer diameter of the bulge is A connecting device for an exhaust pipe of an internal combustion engine is provided, in which two portions are disposed so as to abut on the inner diameter surface of a receiving hole.
以下その実施例を図面により説明すると、第１
図において、１は例えばガス流の上流側に位置す
る一方の管であつて、その端部外径部には縦断面
においてほゞ球面状の外径面１１が形成されてい
る。３は他方の管であつて、その端部には、前記
一方の管１の内径と同径の内径３１より大きな径
の受け穴３２が形成され、該受け穴３２内に、前
記一方の管１の球面状の外径面１１がスキマバメ
にて差し込まれる。 The following examples will be explained with reference to the drawings.
In the figure, reference numeral 1 denotes, for example, one tube located on the upstream side of the gas flow, and an outer diameter surface 11 having a substantially spherical shape in longitudinal section is formed at the outer diameter portion of the end thereof. Reference numeral 3 designates the other tube, and a receiving hole 32 having a diameter larger than the inner diameter 31, which is the same as the inner diameter of the one tube 1, is formed at the end of the tube. The spherical outer diameter surface 11 of No. 1 is inserted with a clearance fit.
前記他方の管３の受け穴３２と内径３１間には
肩３３が形成され、該肩３３と一方の管１の端部
（面）間にはスキマが設けられ、同スキマにシー
ルリング２が挿入されている。 A shoulder 33 is formed between the receiving hole 32 and the inner diameter 31 of the other tube 3, and a gap is provided between the shoulder 33 and the end (surface) of the one tube 1, and the seal ring 2 is installed in the gap. It has been inserted.
上記シールリング２は、外径方向にふくらみの
ある断面形状を有する耐熱金属板製のリングであ
つて、上記断面形状は、この例では上記ふくらみ
がＵ字形をなしているがこれはＶ字形でもよく、
またその寸法は、前記両管１，３の組付時の軸方
向の力により、シールリング２の両側部が、前記
肩３３と前記管１の端面に当接（圧接）して外径
方向に広がつた際、その外径部（頂部）が前記受
け穴３２の内径面に圧接されるよう且つ、内径面
は前記管１，３の内径と同一となるよう定められ
る。 The seal ring 2 is a ring made of a heat-resistant metal plate and has a cross-sectional shape that bulges in the outer diameter direction, and the cross-sectional shape is such that the bulge is U-shaped in this example, but it can also be V-shaped. often,
In addition, the dimensions are such that due to the axial force when the two pipes 1 and 3 are assembled, both sides of the seal ring 2 come into contact (pressure contact) with the shoulder 33 and the end surface of the pipe 1, and the outer diameter direction When expanded, the outer diameter portion (top) is set in pressure contact with the inner diameter surface of the receiving hole 32, and the inner diameter surface is determined to be the same as the inner diameter of the tubes 1 and 3.
前記管１及び３は一般に鋳鉄製であるのに対
し、前記シールリング２は、それよりも熱膨張率
が小さい耐熱性金属、例えばフエライト系の
SUS材（ステンレス鋼管）から成るものである。 While the tubes 1 and 3 are generally made of cast iron, the seal ring 2 is made of a heat-resistant metal with a smaller coefficient of thermal expansion, such as ferrite.
It is made of SUS material (stainless steel pipe).
上記のような本案装置は第２図に示す如き排気
系に実施される。即ち、第２図は上述した本考案
をＶ型内燃機関の排気系に実施した例を概略的に
示すもので、４及び５は上記内燃機関の各バンク
のシリンダヘツド、６はターボチヤージヤー、４
１，４２及び５１，５２は前記バンク４，５の排
気マニホールド、６１はターボチヤージヤー６の
コンプレツサ、６２はタービン、６３は該タービ
ン６２に連通する分岐管、４３，４４及び５３，
５４はタービンの分岐管６３と前記マニホールド
４２，５２間を連通する接続管、７は噴射ポン
プ、８は冷却フアンを示す。なお同図において、
円で囲まれた部分は、各管の接続部であつて第１
図の実施例に示す装置が使用されている。 The device of the present invention as described above is implemented in an exhaust system as shown in FIG. That is, FIG. 2 schematically shows an example in which the above-described present invention is implemented in the exhaust system of a V-type internal combustion engine, where 4 and 5 are cylinder heads of each bank of the internal combustion engine, and 6 is a turbocharger. , 4
1, 42 and 51, 52 are exhaust manifolds of the banks 4, 5, 61 is a compressor of the turbocharger 6, 62 is a turbine, 63 is a branch pipe communicating with the turbine 62, 43, 44, and 53,
54 is a connecting pipe that communicates between the branch pipe 63 of the turbine and the manifolds 42, 52, 7 is an injection pump, and 8 is a cooling fan. In addition, in the same figure,
The part surrounded by a circle is the connection part of each pipe and is the first
The apparatus shown in the illustrated embodiment is used.
本考案装置を構成するには、例えば前記接続管
４４に相当する他方の管３の受け穴３２内の肩３
３に当接するよう耐熱金属抜製のシールリング２
を挿入し、ふくらみの外径部で受け穴３２内に固
定するとともに、接続管４３に相当する球面状の
外径面１１を形成した一方の管１を上記受け穴３
２内に挿入し、その先端をシールリング２の側面
に押し当て該リングを押圧する。これにより、シ
ールリング２は前記肩３３と一方の管１の先端に
圧接すると同時にふくらみ外径部が受け穴３２内
面に圧接して３点でシールされる。 To construct the device of the present invention, for example, a shoulder 3 in the receiving hole 32 of the other pipe 3 corresponding to the connecting pipe 44 is required.
Seal ring 2 made of heat-resistant metal so as to come into contact with 3.
is inserted and fixed in the receiving hole 32 by the outer diameter part of the bulge, and one tube 1 having a spherical outer diameter surface 11 corresponding to the connecting pipe 43 is inserted into the receiving hole 3.
2 and press its tip against the side surface of the seal ring 2 to press the ring. As a result, the seal ring 2 is brought into pressure contact with the shoulder 33 and the tip of one of the tubes 1, and at the same time, the swollen outer diameter portion is brought into pressure contact with the inner surface of the receiving hole 32, creating a seal at three points.
ここで前記管１及び管３内に高温高圧のガス、
例えば内燃機関の排気ガス（一例として温度は
700℃前後、圧力は3.5〜６Kg／cm2にもなる）が流
れた場合、上記接続部においては、シールリング
２の両側部は前記管３の肩３３と前記管１の先端
部に、またそのふくらみの外径部は受け穴３２の
内径面にそれぞれ圧接され、３点でシールされて
おり、又上記ガス圧によつてもシールリング２は
受け穴３２内面、肩３３及び管１の先端部に押圧
されるので、この部分からのガス洩れは確実に防
止される。 Here, high temperature and high pressure gas is present in the pipes 1 and 3.
For example, the exhaust gas of an internal combustion engine (for example, the temperature is
When a temperature of around 700°C and a pressure of 3.5 to 6 kg/cm 2 flows, both sides of the seal ring 2 will contact the shoulder 33 of the pipe 3 and the tip of the pipe 1 at the above connection. The outer diameter portion of the bulge is pressed against the inner diameter surface of the receiving hole 32 and sealed at three points, and the seal ring 2 is also pressed against the inner surface of the receiving hole 32, the shoulder 33, and the tip of the tube 1 due to the gas pressure. Gas leakage from this part is reliably prevented.
又、管内を流れる排気ガスの温度が内燃機関の
運転条件の変化に伴ない上下を繰り返す、いわゆ
る熱サイクルの影響により、前記両管及びシール
リング２は、径方向及び軸方向の膨張・収縮を繰
り返すが、前記の如く、シールリング２は前記管
３，１より熱膨張率が小さいSUS材で形成する
ことにより、径方向の膨張が小さく、従つて前記
管１，３に対し過大な力を及ぼして遂には亀裂を
生ずるなどの上記トラブルもなく、しかも両管
１，３にて押圧されること及び前記ガス圧により
ふくらみの外径部の受け穴３２内径面への圧接は
充分保たれる。また、前記管３と管１の軸方向の
伸び（熱サイクルによる伸びと、鋳鉄製の場合内
部組織の変化即ち黒鉛の成長による伸びと両方あ
る）に対しても、シールリング２のもつ弾性力に
より十分吸収され、シール機能は確実に保持され
る。 Furthermore, due to the effect of a so-called thermal cycle, in which the temperature of the exhaust gas flowing inside the pipes repeatedly rises and falls as the operating conditions of the internal combustion engine change, both the pipes and the seal ring 2 expand and contract in the radial and axial directions. To repeat, as mentioned above, the seal ring 2 is made of SUS material whose coefficient of thermal expansion is smaller than that of the tubes 3 and 1, so that the expansion in the radial direction is small, and therefore, excessive force is not applied to the tubes 1 and 3. Finally, there is no problem such as cracking, and the pressure between the tubes 1 and 3 and the gas pressure keep the outer diameter of the bulge in sufficient contact with the inner diameter of the receiving hole 32. . In addition, the seal ring 2 has an elastic force against elongation in the axial direction of the tubes 3 and 1 (both elongation due to thermal cycles and elongation due to changes in internal structure, i.e., growth of graphite in the case of cast iron). It is fully absorbed and the sealing function is reliably maintained.
また、管１又は管３が曲管である場合、高温の
ガスは管の曲率半径の外側寄りに沿つて流れる傾
向を有するから、この部分の外側の伸びが大き
く、管１又は管３は全体として更に折れ曲がる方
向に変形するが、この変形は、管１の端部球面１
１とシールリング２の変形により十分吸収され
る。 In addition, if the tube 1 or tube 3 is a curved tube, the high temperature gas tends to flow along the outer side of the radius of curvature of the tube, so the outer elongation of this part is large, and the tube 1 or tube 3 as a whole However, this deformation is caused by the spherical surface 1 at the end of the tube 1.
This is sufficiently absorbed by the deformation of seal ring 1 and seal ring 2.
尚、前記シールリング２は、前記のようにステ
ンレス鋼管がこの例では使用されているが、その
肉厚が薄いほど（例えば0.5mm前後）上記変形に
対するフレキシビリテイーが増すので、管内を流
れるガス圧によりシールリング２の両側部と頂部
のシール点は接触圧がせられ、過酷な運転条件に
おいて却つてシール機能は高くなる。 In this example, the seal ring 2 is made of a stainless steel pipe as described above, but the thinner the wall thickness (for example, around 0.5 mm), the more flexible it is against deformation, so the gas flowing inside the pipe is more flexible. Due to the pressure, contact pressure is applied to the sealing points on both sides and the top of the seal ring 2, and the sealing function becomes even higher under severe operating conditions.
本考案は以上のように、一方の管における軸心
を含む断面が球面状をなす先端及びこれが嵌入さ
れる他方の管の直管状の受け穴と内径部間に形成
された肩の間に、外径方向にふくらみをもち、前
記両管の熱膨脹率より小さい熱膨脹率の耐熱金属
板製シールリングを、その両側部が前記肩と一方
の管の先端に、また前記ふくらみの外径部が受け
穴の内径面に、それぞれ当接するよう配設してな
るので、一方の管における軸心を含む断面が球面
状をなす先端とこれが嵌入される他方の管の前記
肩の間に前記シールリングを配設することによ
り、上記シールリングはその弾性で前記他方の管
の肩と一方の管の先端に圧接されるのみならず、
ふくらみの外径部が前記他方の管の受け穴内面に
圧接され、結局３点において密封作用がなされる
ので、前記従来装置に比較して密封性が向上す
る。また、前記２本の管にこれを屈曲する力がか
かつたときも、一方の管における球面状外径面を
形成した先端が他方の直管状受け穴内で適当な隙
間を保ちつつ円滑に屈曲し、前記シールリングも
これに追随してシール作用を継続させることがで
きる。 As described above, the present invention has a shoulder formed between the tip of one tube, which has a spherical cross section including the axis, and the straight receiving hole of the other tube into which the tip is inserted, and the inner diameter portion. A seal ring made of a heat-resistant metal plate having a bulge in the outer diameter direction and having a coefficient of thermal expansion smaller than that of both tubes is provided, with both sides of the seal ring positioned at the shoulder and the tip of one of the tubes, and the outer diameter portion of the bulge being received. The seal ring is arranged so as to abut on the inner diameter surface of the hole, so that the seal ring is placed between the tip of one tube, which has a spherical cross section including the axis, and the shoulder of the other tube into which it is inserted. Due to this arrangement, the seal ring is not only brought into pressure contact with the shoulder of the other pipe and the tip of the one pipe by its elasticity, but also
The outer diameter portion of the bulge is pressed against the inner surface of the receiving hole of the other tube, and the sealing action is ultimately performed at three points, so that the sealing performance is improved compared to the conventional device. Furthermore, even when a force is applied to the two tubes to bend them, the tip of one tube, which has a spherical outer diameter surface, bends smoothly while maintaining an appropriate gap within the straight receiving hole of the other tube. However, the seal ring can also follow this and continue its sealing action.
更に一方の管と他方の管内を流れる高圧ガス圧
力によつてシールリングによる前記軸方向及び半
径方向の圧力が増大され、密着度が一層良好とな
る。従つて内燃機関の高速時高負荷時など排気圧
力が上昇する過酷な運転条件となる程、密封性が
良くなる効果がある。 Furthermore, the pressure in the axial and radial directions due to the seal ring is increased by the high pressure gas flowing in one tube and the other tube, resulting in even better adhesion. Therefore, the more severe the operating conditions are such that the exhaust pressure increases, such as when the internal combustion engine is running at high speed and under high load, the better the sealing performance becomes.
出願人におけるデイーゼル機関を備えた大型車
を例にとると、その排気圧力は通常使用時の圧力
変動を考慮すると約４Kg／cm2、また排気ブレーキ
作動時には約６Kg／cm2にまで上昇し、また排気ガ
スの温度は700℃にも達するのであるが、本考案
装置によれば、このような過酷な条件において
も、確実にガス洩れを防ぐことが確認された。 Taking the applicant's large vehicle equipped with a diesel engine as an example, its exhaust pressure rises to approximately 4 kg/cm 2 when pressure fluctuations during normal use are taken into account, and to approximately 6 kg/cm 2 when the exhaust brake is activated. Furthermore, the temperature of the exhaust gas reaches as high as 700°C, and it has been confirmed that the device of the present invention reliably prevents gas leakage even under such harsh conditions.
特にターボチヤージヤー付の場合には、ガス洩
れは性能に大きく影響し、低速域では殊にその性
能を低下させるが、本考案によりこの問題が解消
され、ターボチヤージヤーの性能を十分発揮させ
ることができる。 Particularly in the case of a turbocharger, gas leakage greatly affects the performance, especially in the low speed range, but this invention solves this problem and fully demonstrates the performance of the turbocharger. can be done.
また、前記熱サイクル発生時において、前記排
気管接続部における一方及び他方の管の膨脹収縮
にもシールリングはその弾性によつてよく追随し
高い密封性を保持するとともに、長時間の熱サイ
クルによる形状変化に対してもこれを吸収するフ
レキシビリテイーを有するから、前記接続部の亀
裂やガス洩れを確実に防ぐことができ、この際シ
ールリングは管より熱膨脹率が小さいので径方向
の膨脹によつて排気管に前記亀裂を生ずることも
なく、耐久性も充分確保できる効果がある。 In addition, when the heat cycle occurs, the seal ring closely follows the expansion and contraction of one and the other pipes at the exhaust pipe connection part due to its elasticity, and maintains high sealing performance. Since it has the flexibility to absorb changes in shape, it is possible to reliably prevent cracks and gas leaks at the connection.In this case, the seal ring has a smaller coefficient of thermal expansion than the pipe, so it is flexible enough to absorb changes in shape. Therefore, the exhaust pipe is free from cracks and sufficient durability can be ensured.
更に本案装置は構造が簡単で製作費が安く、ま
た本実施例では締付ボルト等を一切使用せず、単
に差し込むだけの作業ですむので、接続作業がき
わめて簡単であるという効果もある。 Furthermore, the device of the present invention has a simple structure and low manufacturing cost, and the present embodiment does not use any tightening bolts, and all that is required is simply inserting them, so the connection work is extremely simple.
第１図は本考案の実施例を示す断面図、第２図
は本考案装置をターボチヤージヤー付内燃機関の
排気系に使用した例を示す概略、第３図は従来の
この種の装置の一例を示す部分的断面図である。
符号１……一方の管、１１……球面状外径面、
２……シールリング、３……他方の管、３２……
受け穴、３３……肩、４，５……Ｖ型エンジンの
シリンダヘツド、６……ターボチヤージヤー。
Fig. 1 is a sectional view showing an embodiment of the present invention, Fig. 2 is a schematic diagram showing an example in which the inventive device is used in an exhaust system of a turbocharged internal combustion engine, and Fig. 3 is a conventional device of this type. It is a partial sectional view showing an example. Code 1... One tube, 11... Spherical outer diameter surface,
2... Seal ring, 3... Other tube, 32...
Receiving hole, 33... shoulder, 4, 5... cylinder head of V-type engine, 6... turbo charger.
Claims (1)
す先端及びこれが嵌入される他方の管の直管状の
受け穴と内径部間に形成された肩の間に、外径方
向にふくらみをもち、前記両管の熱膨脹率より小
さい熱膨脹率の耐熱金属板製シールリングを、そ
の両側部が前記肩と一方の管の先端に、また前記
ふくらみの外径部が受け穴の内径面に、それぞれ
当接するよう配設してなる内燃機関の排気管の接
続装置。 A bulge in the outer radial direction between the tip of one tube whose cross section including the axis is spherical and the shoulder formed between the straight receiving hole and the inner diameter of the other tube into which this tip is inserted; A seal ring made of a heat-resistant metal plate having a coefficient of thermal expansion smaller than that of both tubes is placed so that both sides of the ring are in contact with the shoulder and the tip of one of the tubes, and the outer diameter of the bulge is in contact with the inner diameter of the receiving hole. A connecting device for the exhaust pipes of an internal combustion engine, which are arranged so that they touch each other.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980102602U JPS6339371Y2 (en) | 1980-07-18 | 1980-07-18 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1980102602U JPS6339371Y2 (en) | 1980-07-18 | 1980-07-18 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5725283U JPS5725283U (en) | 1982-02-09 |
| JPS6339371Y2 true JPS6339371Y2 (en) | 1988-10-17 |
Family
ID=29464023
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1980102602U Expired JPS6339371Y2 (en) | 1980-07-18 | 1980-07-18 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6339371Y2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07116934B2 (en) * | 1986-05-23 | 1995-12-18 | テレダイン・インダストリーズ・インコーポレーテッド | Exhaust manifold for cylinder-opposed engines |
| JPH0273904U (en) * | 1988-11-21 | 1990-06-06 |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3550987A (en) * | 1968-04-16 | 1970-12-29 | G C Dickey Corp | Resilient sealing apparatus |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52156318U (en) * | 1976-05-24 | 1977-11-28 |
-
1980
- 1980-07-18 JP JP1980102602U patent/JPS6339371Y2/ja not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3550987A (en) * | 1968-04-16 | 1970-12-29 | G C Dickey Corp | Resilient sealing apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5725283U (en) | 1982-02-09 |
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