JPS621378Y2 - - Google Patents
Info
- Publication number
- JPS621378Y2 JPS621378Y2 JP9164480U JP9164480U JPS621378Y2 JP S621378 Y2 JPS621378 Y2 JP S621378Y2 JP 9164480 U JP9164480 U JP 9164480U JP 9164480 U JP9164480 U JP 9164480U JP S621378 Y2 JPS621378 Y2 JP S621378Y2
- Authority
- JP
- Japan
- Prior art keywords
- pipe
- sealing
- bulge
- outer diameter
- tube
- 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
- 238000007789 sealing Methods 0.000 claims description 48
- 239000002184 metal Substances 0.000 claims description 7
- 229910052751 metal Inorganic materials 0.000 claims description 7
- 239000007789 gas Substances 0.000 description 18
- 238000002485 combustion reaction Methods 0.000 description 6
- 229910001018 Cast iron Inorganic materials 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 230000008602 contraction Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000012010 growth Effects 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000005336 cracking Methods 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
- 230000007774 longterm Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000008467 tissue growth Effects 0.000 description 1
- 229910000859 α-Fe Inorganic materials 0.000 description 1
Landscapes
- Joints With Sleeves (AREA)
- Exhaust Silencers (AREA)
Description
【考案の詳細な説明】
本考案は、例えば内燃機関の排気マニホールド
とターボチヤージヤー間、あるいは排気マニホー
ルドと排気管等、比効的高温高圧のガスに適した
管の接続装置に関するものである。[Detailed description of the invention] The present invention relates to a pipe connection device suitable for gases having a specific high temperature and high pressure, such as between an exhaust manifold and a turbocharger of an internal combustion engine, or between an exhaust manifold and an exhaust pipe. .
前記の如き管の接続装置としては、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。 Conventionally, as shown in FIG. 3, the above-mentioned pipe connecting device has been used, for example, by inserting the end of one pipe A to be connected into a receiving hole C formed at the end of the other pipe B, and A seal ring D made of a heat-resistant material is fitted into a groove formed on the outer diameter of the tube A, and the outer circumference of the seal ring D is brought into contact with the inner circumference of the other tube B to seal between the tubes A and B. It is known that this was done.
しかしながら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が膨脹収縮を
くり返すため、材料自体の耐久性がないこととも
相俟つて、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じていた。
また、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。 However, in such a device, the tubes A and B repeatedly expand and contract due to the high-temperature gas flowing inside them, and this combined with the lack of durability of the material itself, causes the contact of the seal ring D. The surfaces were worn and the airtightness deteriorated, causing gas leaks.
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 in an attempt to improve sealing performance.
シールリングＤが摩耗するという上記欠点は他
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１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 above-mentioned disadvantage of the seal ring D being worn out is extremely serious because only one seal ring can be used in a device in which the outer diameter portion of the tip of one tube A inserted into the receiving hole C of the other tube is spherical. However, 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脹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脹力による密着力
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たわ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脹、
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 in contact with the joint, even though the adhesion force due to the axial elasticity of the connecting member and the thermal expansion force of the exhaust manifold can be used, the elastic force in the radial direction to the annular curved portion and the adhesion force due to the thermal expansion force of the exhaust manifold are The gas pressure acting inside cannot be used and the sealing performance is insufficient. Further, due to the repeated application of force and gas pressure 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 adheres to and peels off from the inner diameter surface of the manifold, causing the flange to become attached to the manifold. If it is in close contact with the inner diameter, even if the sealing performance is good, the manifold may expand or
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.
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、安定性及び密封すべき管の膨脹
収縮に対する順応性に優れたしかも耐久性のある
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の先
端及びこれが嵌入する他方の管の受け穴と内径間
に形成された肩の間に、耐熱金属板製シーリング
パイプの一端に形成した外径方向へのふくらみを
配置せしめ、前記ふくらみの両側部が前記肩と一
方の管の先端に、また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且つ前記シー
リングパイプの他端側を前記一方の管の内径端部
に嵌合固定せしめたことにある。 The present invention aims to eliminate the drawbacks of the conventional devices as described above, and to provide a durable pipe connecting device that has excellent sealing performance, stability, and adaptability to the expansion and contraction of the pipe to be sealed. It was created for this purpose, and its gist is that it is formed at one end of a heat-resistant metal plate sealing pipe between the shoulder formed between the tip of one pipe and the receiving hole of the other pipe into which it fits, and the inner span. and a bulge extending in the outer diameter direction of the sealing pipe, such that both sides of the bulge are in contact with the shoulder and the tip of one of the pipes, and the outer diameter of the bulge is in contact with the inner diameter surface of the receiving hole. The other end is fitted and fixed to the inner diameter end of the one tube.
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は一方の管であつて、その端部外
径部には、ほゞ球面状の外径面１１が形成され、
同内径端部側には、同管１の内径１２よりもやゝ
径の大きな取付穴１３が形成されている。内径１
２と取付穴１３との間には肩（段部）１４が形成
される。 The following examples will be explained with reference to the drawings.
In the figure, reference numeral 1 denotes one tube, and an approximately spherical outer diameter surface 11 is formed on the outer diameter portion of the end thereof.
A mounting hole 13 having a diameter slightly larger than the inner diameter 12 of the tube 1 is formed on the inner diameter end side. Inner diameter 1
A shoulder (step) 14 is formed between the mounting hole 13 and the mounting hole 13 .
２は耐熱金属板製シーリングパイプであつて、
一端側に外径方向へのふくらみ２０が全周にわた
つて形成されており、その他端側の円筒部は、前
記一方の管１の取付穴１３内にシマリバメで嵌合
固定され、ふくらみ２０が管１の端部から突出す
るよう、且つ端部と前記肩１４の間にスキマが残
るようにその取付位置が定められている。上記ふ
くらみ２０の断面形状は、この例ではほゞＵ字形
をなしているがＶ字形でもよい。 2 is a sealing pipe made of a heat-resistant metal plate,
A bulge 20 in the outer diameter direction is formed on one end side over the entire circumference, and the cylindrical portion on the other end side is fitted and fixed in the mounting hole 13 of the one pipe 1 with a tight fit, so that the bulge 20 Its attachment position is determined so that it protrudes from the end of the tube 1 and leaves a gap between the end and the shoulder 14. Although the cross-sectional shape of the bulge 20 is approximately U-shaped in this example, it may be V-shaped.
３は他方の管であつて、その端部には受け穴３
３と内径３１が肩３６を介して連続して形成され
ている。上記受け穴３３は、シーリングパイプ２
の前記ふくらみ２０の外径部及び一方の管１の端
部外径面１１の最大外径よりわずかに大きな径を
有している。 3 is the other tube with a receiving hole 3 at its end.
3 and the inner diameter 31 are formed continuously via a shoulder 36. The receiving hole 33 is connected to the sealing pipe 2
It has a diameter slightly larger than the outer diameter of the bulge 20 and the maximum outer diameter of the end outer diameter surface 11 of one tube 1.
シーリングパイプ２は後記のようにセツトした
とき、前記両管３，１の軸方向の力により、前記
ふくらみ２０の両側部は、それぞれ前記肩３６と
一方の管１の開口端により当接（圧接）され、こ
れによりふくらみ２０は外径方向に、わずかに拡
がつて同外径部は受け穴３３の内径に押圧される
よう構成する。 When the sealing pipe 2 is set as described below, both sides of the bulge 20 are brought into contact (pressure contact) by the shoulder 36 and the open end of one of the pipes 1 due to the axial force of the two pipes 3 and 1. ), whereby the bulge 20 expands slightly in the outer diameter direction, and the outer diameter portion is pressed against the inner diameter of the receiving hole 33.
前記管１（及び３）は一般に鋳鉄製であるのに
対し、前記シーリングパイプ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）が好ましい。 While the pipes 1 (and 3) are generally made of cast iron, the sealing pipe 2 is preferably made of a heat-resistant metal with a smaller coefficient of thermal expansion, such as a ferrite-based 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は各バンクのシリンダヘツ
ド、６はターボチヤージヤー、４１，４２及び５
１，５２は前記バンクの排気マニホールド、６１
はターボチヤージヤーのコンプレツサ、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と各マニホールド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。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、それぞれ第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 present invention described above is implemented in the exhaust system of a V-type internal combustion engine, where 4 and 5 are cylinder heads of each bank, 6 is a turbocharger, and 41, 42 are cylinder heads of each bank. and 5
1, 52 is the exhaust manifold of the bank, 61
62 is a turbocharger compressor; 62 is a turbine; 63 is a branch pipe communicating with the turbine 62; 43, 44 and 53, 54 are connection pipes communicating between the turbine branch pipe 63 and each manifold 42, 52; 7 indicates an injection pump, and 8 indicates a cooling fan. In the same figure, the circled parts are the connection parts of the respective pipes, and the apparatus shown in the embodiment of FIG. 1 is used in each case.
本考案装置を構成するには、例えば第２図の接
続管４３に相当する一方の管１の取付穴１３にシ
ーリングパイプ２の前記他端側の円筒部をシマリ
バメにて嵌合固定した後、このように一方の管１
に固定したシーリングパイプ２の前記ふくらみ２
０を他方の管３の受け穴３３に遊嵌し、ふくらみ
２０の一側を肩３６に当接させ、他側を一方の管
１の端面で押すように装着せしめる。 To configure the device of the present invention, for example, after fitting and fixing the cylindrical portion of the other end of the sealing pipe 2 into the mounting hole 13 of one pipe 1 corresponding to the connecting pipe 43 in FIG. 2 with a tight fit, In this way, one tube 1
The bulge 2 of the sealing pipe 2 fixed to
0 is loosely fitted into the receiving hole 33 of the other tube 3, one side of the bulge 20 is brought into contact with the shoulder 36, and the other side is pressed by the end surface of the one tube 1.
ここで前記管１及び３内に高温高圧のガス、例
えば内燃機関の排気ガス（１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、シーリングパイ
プ２と管１の取付穴１３間はシマリバメされてお
り、またふくらみ２０の両側部はそれぞれ管１の
端部と管３の肩３６に当接され、更にふくらみ２
０の外径部は受け穴３３の内径面に圧接している
ため、これらの部分によりガス洩れを確実に防ぐ
ことができる。 Here, a high-temperature, high-pressure gas, such as exhaust gas from an internal combustion engine (for example, the temperature is 700
℃, and the pressure is as high as 3.5 to 6 kg/cm 2 ), in the above connection, there is a tight fit between the sealing pipe 2 and the mounting hole 13 of the pipe 1, and both sides of the bulge 20 are abut the ends of tube 1 and shoulders 36 of tube 3, respectively, and further bulges 2
Since the outer diameter portion of 0 is in pressure contact with the inner diameter surface of the receiving hole 33, gas leakage can be reliably prevented by these portions.
又管内を流れる排気ガスの温度は、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リン
グパイプは、径方向及び軸方向の膨張・収縮を繰
り返すが、前記の如くシーリングパイプ２と管１
のシマリバメ部分においては、管１は鋳鉄製であ
り、シーリングパイプ２はそれよりも熱膨張率の
小さな、例えばSUS材であるため、高温のガスに
直接されされるシーリングパイプ２の径方向の膨
張率が管１の同シマリバメ部分の内径の膨張量を
上まわることはなく、また、管１の取付穴１３の
内径寸法は、膨張時においても、シーリングパイ
プ２に対するシマリバメを保持するように、あら
かじめ規定されているので、同部分のシール機能
は保持されるとともに、亀裂が生ずるといつた問
題もない。 Furthermore, the temperature of the exhaust gas flowing inside the pipes repeatedly rises and falls as the operating conditions of the internal combustion engine change, which is the effect of a so-called thermal cycle, which causes the above-mentioned two pipes and the sealing pipe to repeatedly expand and contract in the radial and axial directions. , sealing pipe 2 and pipe 1 as described above.
In the snug fit part, the pipe 1 is made of cast iron, and the sealing pipe 2 is made of a material with a smaller coefficient of thermal expansion, for example, SUS, so that the radial expansion of the sealing pipe 2 when exposed directly to high-temperature gas occurs. The rate of expansion does not exceed the amount of expansion of the inner diameter of the same snugly fit portion of the pipe 1, and the inner diameter of the mounting hole 13 of the tube 1 is set in advance so as to maintain the snug fit against the sealing pipe 2 even when expanded. Since it is specified, the sealing function of the same part is maintained and there is no problem such as cracking.
又、前記管３の受け穴３３とふくらみ２０の外
径部との接続部においても、一般に管３は鋳鉄、
シーリングパイプ２はこの例ではSUS材であり、
熱膨張率がパイプ２が低いが、受け穴３３の膨張
に対し、充分追従し、スキマが生じないようにふ
くらみ２０の密着度（圧接度）及び、その肉厚を
定めておけば、ガス洩れに対するシール機能を保
持することができる。シーリングパイプの肉厚が
薄いと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、ふくらみ２０の両側部と頂部
のシール点は、その接触圧が増大させられ、過酷
な運転条件において、かえつてシール機能が高く
なるという効果を生ずる。 Also, at the connection part between the receiving hole 33 of the pipe 3 and the outer diameter part of the bulge 20, the pipe 3 is generally made of cast iron,
The sealing pipe 2 is made of SUS material in this example,
Although the coefficient of thermal expansion of the pipe 2 is low, if the degree of adhesion (degree of pressure contact) and the wall thickness of the bulge 20 are determined so that it sufficiently follows the expansion of the receiving hole 33 and does not create a gap, gas leakage can be prevented. It is possible to maintain the sealing function against. Since the thin wall thickness of the sealing pipe increases its flexibility, the gas pressure flowing inside the pipe increases the contact pressure at the sealing points on both sides and the top of the bulge 20, and in harsh operating conditions, it becomes more flexible. This has the effect of increasing the sealing function.
管１と３はこの例では鋳鉄であるから、長時間
の熱サイクルの影響で内部組織が変化（黒鉛の成
長）し、特に軸方向の成長が大きい。しかし上記
実施例においては、シーリングパイプ２と管１の
肩１４間にスキマが設けてあり、ふくらみ２０は
軸方向にたわむことができるので、組織の成長及
び熱サイクルにおける膨張に対しても充分吸収す
ることができる。ふくらみ２０と管との間の密着
圧力は前述の通り増大し、シール性はむしろ向上
するものである。 Since the tubes 1 and 3 are made of cast iron in this example, the internal structure changes (graphite growth) under the influence of long-term thermal cycles, and the growth in the axial direction is particularly large. However, in the above embodiment, a gap is provided between the sealing pipe 2 and the shoulder 14 of the tube 1, and the bulge 20 can be bent in the axial direction, so it can sufficiently absorb tissue growth and expansion due to thermal cycles. can do. The contact pressure between the bulge 20 and the pipe increases as described above, and the sealing performance is rather improved.
また、管１又は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１１とシ
ーリングパイプ２の変形により充分吸収される。
尚シーリングパイプ２は、前記したようにステン
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は良好となる。 Furthermore, if the tube 1 or 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 portion is large;
Although the tube 1 or 3 as a whole is further deformed in the bending direction, this deformation is sufficiently absorbed by the deformation of the spherical end surface 11 of the tube 1 and the sealing pipe 2.
As described above, the sealing pipe 2 is a stainless steel pipe in this example, and the thinner the wall thickness (for example, around 0.5 mm), the better the flexibility against the above deformation.
本考案は上記の如く、一方の管の先端及びこれ
が嵌入する他方の管の大径の受け穴と該受け穴よ
り小径の穴間に形成された肩の間に、耐熱金属板
製シーリングパイプの一端側に形成した外径方向
へのふくらみを配置せしめ、前記ふくらみの両側
部が前記肩と一方の管の先端に、またふくらみの
外径部が大径の受け穴の内径面に、それぞれ当接
するよう且つ前記シーリングパイプの他端側を前
記一方の管の内径端部に嵌合固定せしめてなるの
で、一方の管の先端及びこれが嵌入する他方の管
の大径の受け穴と内径間に形成された肩の間に、
耐熱金属板製シーリングパイプの一端側に形成し
た外径方向へのふくらみを配置せしめ、前記ふく
らみの両側部が前記肩と一方の管の先端に、また
ふくらみの外径部が受け穴の内径面にそれぞれ当
接することによつて、上記シーリングパイプはそ
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
てバランスよく密封作用がなされて前記従来装置
に比較して密封性が一段と向上する。 As described above, the present invention provides a sealing pipe made of a heat-resistant metal plate between the shoulder formed between the tip of one pipe and the large-diameter receiving hole of the other pipe into which it is inserted, and a hole smaller in diameter than the receiving hole. A bulge formed on one end side is arranged in the outer diameter direction, and both sides of the bulge are in contact with the shoulder and the tip of one of the tubes, and the outer diameter part of the bulge is in contact with the inner diameter surface of the large diameter receiving hole. Since the other end of the sealing pipe is fitted and fixed to the inner diameter end of the one pipe, there is no space between the tip of one pipe and the large diameter receiving hole of the other pipe into which it is fitted. Between the formed shoulders,
A bulge formed in the outer diameter direction on one end side of a sealing pipe made of a heat-resistant metal plate is arranged, and both sides of the bulge are connected to the shoulder and the tip of one pipe, and the outer diameter part of the bulge is connected to the inner diameter surface of the receiving hole. By abutting on each of the above, the sealing pipe is not only pressed against the shoulder of the other pipe and the tip of the one pipe due to its elasticity, but also the outer diameter of the bulge is brought into contact with the inner surface of the receiving hole of the other pipe. As a result, a well-balanced sealing action is achieved at the three points, and the sealing performance is further improved compared to the conventional device.
更に一方の管と他方の管内を流れる高圧ガス圧
力によつてシーリングパイプ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 sealing pipe is increased by the high pressure gas flowing in one pipe and the other pipe, so that the degree of adhesion becomes even better. 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４Kg／cm2ほど、また排気ブレー
キ作動時には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。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、特に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充分発揮させる
ことができる。 Taking the applicant's large vehicle equipped with a diesel engine as an example, its exhaust pressure rises to about 4 Kg/cm 2 when pressure fluctuations during normal use are considered, and as high as 6 Kg/cm 2 when the exhaust brake is activated. The temperature of the gas reaches as high as 700°C, and with the device of this invention, even under such harsh conditions,
It was confirmed that it reliably prevents gas leaks. 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 improves the performance of the turbocharger. It can be demonstrated.
また、前記熱サイクル発生時において、前記排
気系の管の接続部における一方及び他方の管の膨
張収縮にもシーリングパイプ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
る。 In addition, when the heat cycle occurs, the sealing pipe closely follows the expansion and contraction of one pipe and the other pipe at the connection part of the pipes of the exhaust system due to its elasticity, maintains high sealing performance, and maintains a high sealing property over a long period of time. Since it has the flexibility to absorb changes in shape due to thermal cycles, it is possible to reliably prevent cracks and gas leaks in the connection portion.
また、シーリングパイプの他端側を前記一方の
管の内径端部に嵌合固定せしめることにより、こ
の部分でも密封が行われるとともに、上記パイプ
の他端側と両管１の肩１４の間はスキマがあるの
で、熱膨脹による軸方向への移動はもとより、エ
ンジン等の振動などに際しても支障ない。 Further, by fitting and fixing the other end of the sealing pipe to the inner diameter end of the one pipe, sealing is achieved also in this part, and the space between the other end of the pipe and the shoulders 14 of both pipes 1 is Since there is a gap, there is no problem not only with movement in the axial direction due to thermal expansion but also with vibrations of the engine, etc.
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図は本考案の一実施例を示す断面図、第２
図は本考案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図、第３図は従来装
置の一例を示す部分的断面図である。
符号１……一方の管、１１……外径面、１３…
…取付孔、１４……肩、２……シーリングパイ
プ、３……他方の管、３１……内径、３３……受
け穴、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 one embodiment of the present invention;
The figure is a schematic view showing an example in which the present invention is used in an exhaust system of an internal combustion engine with a turbocharger, and FIG. 3 is a partial sectional view showing an example of a conventional device. Code 1...One tube, 11...Outer diameter surface, 13...
...Mounting hole, 14...Shoulder, 2...Sealing pipe, 3...Other pipe, 31...Inner diameter, 33...Socket hole, 4, 5...Cylinder head of V-type engine, 6...Turbocharger Jiya.
Claims (1)
の受け穴と内径間に形成された肩の間に、耐熱
金属板製シーリングパイプの一端側に形成した
外径方向へのふくらみを配置せしめ、前記ふく
らみの両側部が前記肩と一方の管の先端に、ま
たふくらみの外径部が受け穴の内径面に、それ
ぞれ当接するよう且つ前記シーリングパイプの
他端側を前記一方の管の内径端部に嵌合固定せ
しめてなる管の接続装置。 ２ 前記シーリングパイプを、管の熱膨張率より
小さい熱膨脹率をもつ耐熱性金属により形成せ
しめてなる実用新案登録請求の範囲第１項記載
の管の接続装置。 ３ 前記一方の管の先端部外径が軸心を含む断面
においてふくらみをもつ実用新案登録請求の範
囲第１項記載の管の接続装置。[Claims for Utility Model Registration] 1. An outer diameter formed on one end side of a sealing pipe made of a heat-resistant metal plate between the shoulder formed between the tip of one pipe and the receiving hole of the other pipe into which it is inserted and the inner span. a bulge in the direction of the sealing pipe, so that both sides of the bulge are in contact with the shoulder and the tip of one of the pipes, and the outer diameter of the bulge is in contact with the inner diameter of the receiving hole, and the other end of the sealing pipe is A pipe connecting device, which is fitted and fixed to the inner diameter end of one of the pipes. 2. The pipe connecting device according to claim 1, wherein the sealing pipe is made of a heat-resistant metal having a coefficient of thermal expansion smaller than that of the pipe. 3. The pipe connecting device according to claim 1, wherein the outer diameter of the tip end of the one pipe is bulged in a cross section including the axis.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9164480U JPS621378Y2 (en) | 1980-06-30 | 1980-06-30 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9164480U JPS621378Y2 (en) | 1980-06-30 | 1980-06-30 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5716077U JPS5716077U (en) | 1982-01-27 |
| JPS621378Y2 true JPS621378Y2 (en) | 1987-01-13 |
Family
ID=29453616
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9164480U Expired JPS621378Y2 (en) | 1980-06-30 | 1980-06-30 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS621378Y2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0338404Y2 (en) * | 1985-12-06 | 1991-08-14 | ||
| JP2006316760A (en) * | 2005-05-16 | 2006-11-24 | Honda Motor Co Ltd | Assembly structure of oil pump |
-
1980
- 1980-06-30 JP JP9164480U patent/JPS621378Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5716077U (en) | 1982-01-27 |
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