JP2005331217A - Gas cooling device - Google Patents

Gas cooling device Download PDF

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Publication number
JP2005331217A
JP2005331217A JP2004169470A JP2004169470A JP2005331217A JP 2005331217 A JP2005331217 A JP 2005331217A JP 2004169470 A JP2004169470 A JP 2004169470A JP 2004169470 A JP2004169470 A JP 2004169470A JP 2005331217 A JP2005331217 A JP 2005331217A
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gas
heat transfer
cooling
pipe
cooling device
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JP4544575B2 (en
Inventor
Tadahiro Goto
忠弘 後藤
Yuji Miyauchi
祐治 宮内
Masayoshi Usui
正佳 臼井
Shoichiro Usui
正一郎 臼井
Kazuyoshi Takigawa
一儀 滝川
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Usui Kokusai Sangyo Kaisha Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1615—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium
    • F28D7/1623—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits being inside a casing and extending at an angle to the longitudinal axis of the casing; the conduits crossing the conduit for the other heat exchange medium with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/26—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being integral with the element
    • F28F1/28—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being integral with the element the element being built-up from finned sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/02—Streamline-shaped elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/02—Flexible elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gas cooling device capable of efficiently cooling gas such as EGR gas. <P>SOLUTION: In this gas cooling device, a gas pipe for the EGR gas or the like is provided with a large number of cooling pipes vertically crossing a gas flow direction of the pipe such that the cooling pipes penetrate the peripheral wall of the gas pipe, the outer face of the gas pipe on both sides of a pipe axial direction of a refrigerant pipe group thereof or the whole outer face of the gas pipe is provided with a cooling jacket, and the gas inside the gas pipe is cooled by a refrigerant flowing through the cooling pipe. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、ガス冷却装置に係り、より詳しくはディーゼルエンジンの排気系から排気ガスの一部を取出し、ＥＧＲ配管を介してエンジンの吸気系に戻し、混合気に加える排気再循環（以下ＥＧＲという）に際して、ＥＧＲ配管内のＥＧＲガスを冷却する装置に関するものである。   The present invention relates to a gas cooling device, and more specifically, a part of exhaust gas is taken out from an exhaust system of a diesel engine, returned to an engine intake system through an EGR pipe, and added to an air-fuel mixture (hereinafter referred to as EGR). ), An apparatus for cooling the EGR gas in the EGR pipe.

排気系から排気ガスの一部を取出して、再びエンジンの吸気系に戻し、混合気に加える方法は、ＥＧＲ（Ｅｘｈａｕｓｔ Ｇａｓ Ｒｅｃｉｒｃｕｌａｔｉｏｎ：排気再循環）と称される。ＥＧＲはＮＯｘ（窒素酸化物）の発生抑制、ポンプ損失の低減、燃焼ガスの温度低下に伴う冷却液への放熱損失の低減、作動ガス量・組成の変化による比熱比の増大と、これに伴うサイクル効率の向上など、多くの効果が得られることから、エンジンの排気ガス浄化、熱効率を改善するには有効な方法とされている。   A method of taking a part of the exhaust gas from the exhaust system, returning it to the engine intake system again, and adding it to the air-fuel mixture is called EGR (Exhaust Gas Recirculation). EGR suppresses the generation of NOx (nitrogen oxide), reduces pump loss, reduces heat dissipation loss to the coolant due to lowering of combustion gas temperature, and increases specific heat ratio due to changes in working gas amount / composition. Since many effects such as improvement of cycle efficiency can be obtained, it is considered to be an effective method for purifying engine exhaust gas and improving thermal efficiency.

しかるに、ＥＧＲガスの温度が高くなりかつＥＧＲガス量が増大すると、その熱作用によりＥＧＲバルブの耐久性が劣化し、早期破損を招く場合があったり、その防止のために水冷構造とする必要があることや吸気温度の上昇に伴い充填効率の低下による燃費の低下等が認識されている。このような事態を避けるため、エンジンの冷却液、カーエアコン用冷媒または、冷却風等によってＥＧＲガスを冷却する装置が用いられている。   However, when the temperature of the EGR gas is increased and the amount of EGR gas is increased, the durability of the EGR valve is deteriorated due to its thermal action, which may cause premature breakage, and a water cooling structure is necessary to prevent this. It is recognized that there is a decrease in fuel consumption due to a decrease in charging efficiency as the intake air temperature increases. In order to avoid such a situation, an EGR gas cooling device is used with an engine coolant, a car air conditioner refrigerant, cooling air, or the like.

従来のＥＧＲガスの冷却装置としては、熱交換器形の各種冷却器が提案されている。
例えば、ガスを通す内管の外側に、液体を通す外管を配設し、ガスと液体間で熱交換を行う交換器において、内管内に金属コルゲート板がフィンとして挿入されている２重管式熱交換器（特許文献１参照）、内管と外管とを備え、内管側および外管側にそれぞれ高温側流体通路および低温側流体通路のどちらか一方ずつを備えた２重管式熱交換器（特許文献２参照）、内側に被冷却媒体を流通させる内管と、内管の外周を離間して囲むように設けられた外管と、内管の内部に配設された熱応力緩和機能を有する放熱フィンとから構成された２重管式熱交換器（特許文献３参照）、内側に被冷却媒体を流通させる内管と、内管の外周を離間して囲むように設けられた外管と、内管の内部に配設されたクロスフィンとから構成された２重管式熱交換器（特許文献４参照）、ＥＧＲガス配管の外周面に、冷却配管（伝熱管）がスパイラル状に対接巻装されたＥＧＲガス冷却装置（特許文献５参照）および、ＥＧＲガス配管の外周壁を貫通して、冷却配管（伝熱管）が当該ＥＧＲガス配管の内部に挿入された構造のＥＧＲガス冷却装置（特許文献６参照）等がある。
特開平１１−２３１８１号公報 特開２００２−３５００７１号公報 特開２０００−１１１２７７号公報 特開２００３−２１４７８号公報 特開平９−８８７３０号公報 特開平９−８８７３１号公報 As a conventional EGR gas cooling device, various heat exchanger type coolers have been proposed.
For example, a double pipe in which a metal corrugated plate is inserted as a fin in the inner pipe in an exchanger in which an outer pipe through which a liquid passes is arranged outside the inner pipe through which the gas passes and heat exchange is performed between the gas and the liquid. -Type heat exchanger (refer to Patent Document 1), a double pipe type comprising an inner pipe and an outer pipe, each having either a high-temperature side fluid passage or a low-temperature side fluid passage on the inner pipe side and the outer pipe side, respectively A heat exchanger (see Patent Document 2), an inner pipe for circulating a medium to be cooled, an outer pipe provided so as to surround and surround the outer circumference of the inner pipe, and heat disposed in the inner pipe A double-pipe heat exchanger composed of heat dissipating fins having a stress relieving function (see Patent Document 3), an inner tube through which a medium to be cooled is circulated, and an outer periphery of the inner tube are provided so as to be spaced apart A double pipe type heat exchanger composed of an outer tube and a cross fin disposed inside the inner tube (See Patent Document 4), EGR gas cooling device (see Patent Document 5) in which a cooling pipe (heat transfer pipe) is spirally wound around the outer peripheral surface of the EGR gas pipe, and the outer peripheral wall of the EGR gas pipe And an EGR gas cooling device (see Patent Document 6) having a structure in which a cooling pipe (heat transfer pipe) is inserted into the EGR gas pipe.
Japanese Patent Laid-Open No. 11-23181 JP 2002-350071 A JP 2000-1111277 A JP 2003-21478 A JP-A-9-88730 JP-A-9-88731

しかしながら、特許文献１〜４に開示されている従来の２重管タイプのＥＧＲガス冷却器の場合は、ＥＧＲガス流路を構成するパイプ内面は、長さ方向全長にわたって内周面が平滑となっているものが多く、パイプ中心付近の熱伝達が十分でなく、ＥＧＲガスの冷却効率が低いという問題があった。
また、特許文献５〜６に開示されているＥＧＲガス冷却装置の場合は、製作が容易でコストが安くつくという利点を有するが、伝熱面積が狭いため伝熱性能を確保するためには特に軸方向長さを長くする必要があり、大きなスペースを占めて自動車に搭載するにはレイアウト上の問題が発生すること、さらにガス流がＥＧＲガス配管に沿って流れるためガス流の乱流化の程度が低く、伝熱面の境界層が十分に薄くならず伝熱性能が若干劣るという問題があった。
本発明はかかる課題を解決するためになされたもので、簡略な構造であるにもかかわらず冷却効率が優れ、しかも限られたスペースに容易に設置が可能なガス冷却装置を提供することを目的とするものである。 However, in the case of the conventional double pipe type EGR gas cooler disclosed in Patent Documents 1 to 4, the inner peripheral surface of the pipe inner surface constituting the EGR gas flow path is smooth over the entire length in the length direction. However, there is a problem that the heat transfer around the center of the pipe is not sufficient and the cooling efficiency of the EGR gas is low.
In addition, the EGR gas cooling device disclosed in Patent Documents 5 to 6 has an advantage that it is easy to manufacture and is inexpensive, but in order to ensure heat transfer performance because the heat transfer area is narrow. It is necessary to lengthen the axial direction, and a layout problem arises when it takes up a large space and is mounted on a car. Furthermore, since the gas flow flows along the EGR gas pipe, There is a problem that the degree is low and the boundary layer of the heat transfer surface is not sufficiently thin and the heat transfer performance is slightly inferior.
The present invention has been made to solve such a problem, and an object of the present invention is to provide a gas cooling device that has excellent cooling efficiency despite being a simple structure and can be easily installed in a limited space. It is what.

本発明に係るガス冷却装置は、基本的にはガス流路のガス流れ方向に対して直角に交差する多数の冷却媒体流路を設けることによって熱交換性能の向上をはかったもので、その第１発明は、ガス配管に、該配管のガス流れ方向に対して直角に交差する多数の冷却配管が、該各配管の両管端が外部に開口するごとく当該ガス配管の外周壁を貫通して固着配列され、さらに前記冷却媒体配管群の管軸方向両側のガス配管外面またはガス配管外面全体に、冷却媒体の流入出口を有する冷却ジャケットが固着され、前記冷却配管内を通流する冷却媒体によって前記ガス配管内のガスが冷却される構成となしたことを特徴とするものである。
又、このガス冷却装置における前記冷却配管は、その外周にスパイラル状もしくはディスク状のフィンを有したり、前記冷却配管が固着配列された熱交換領域のガス配管内に、当該ガス配管内のガス流に平行で前記冷却配管に直角なプレートフィンを少なくとも１枚設けたり、さらに前記プレートフィンの冷却配管が挿入される貫孔には、バーリング壁を設けたり、さらに又、前記プレートフィンにはルーバー、貫孔、ピンフィン、凹凸のうち、少なくとも一つを設けたりするものである。 The gas cooling device according to the present invention basically improves the heat exchange performance by providing a large number of coolant flow paths that intersect at right angles to the gas flow direction of the gas flow path. 1 In the invention, a number of cooling pipes intersecting a gas pipe at right angles to the gas flow direction of the pipe pass through the outer peripheral wall of the gas pipe as both ends of the pipe open to the outside. A cooling jacket having a cooling medium inflow / outlet is fixed to the outer surface of the gas pipe on the both sides in the axial direction of the cooling medium pipe group or the entire outer surface of the gas pipe, and the cooling medium flowing through the cooling pipe. The gas in the gas pipe is cooled.
Further, the cooling pipe in the gas cooling apparatus has spiral or disk-shaped fins on the outer periphery, or the gas pipe in the heat exchange area in which the cooling pipe is fixedly arranged. At least one plate fin parallel to the flow and perpendicular to the cooling pipe is provided, a burring wall is provided in a through hole into which the cooling pipe of the plate fin is inserted, and a louver is provided on the plate fin. At least one of a through hole, a pin fin, and an unevenness is provided.

同じく第２発明は、ガス配管に、一枚の板にバーリング加工を施して多数の突出筒体を同一位相で形成したプレートフィンを複数枚重ねて前記各突出筒体部を溶接又はろう付けにて接合することにより多数のチューブ状冷却媒体流路が形成されたコアが、該コアのチューブ状冷却媒体流路が該配管のガス流れ方向に対して直角に交差し、かつ各チューブ状冷却媒体流路の端部が外部に開口するごとく当該ガス配管の外周壁を貫通して固着配列され、さらに前記チューブ状冷却媒体流路群の両開口端側のガス配管外面又はガス配管外面全体に、冷却媒体の流入出口を有する冷却ジャケットが固着され、前記チューブ状冷却媒体流路内を通流する冷却媒体によって前記ガス配管内のガスが冷却される構成となしたことを特徴とするものである。   Similarly, in the second invention, a plurality of plate fins in which a plurality of projecting cylindrical bodies are formed in the same phase by performing burring processing on a single plate on a gas pipe are welded or brazed. The cores in which a large number of tubular cooling medium flow paths are formed by joining together, the tubular cooling medium flow paths of the cores intersect at right angles to the gas flow direction of the piping, and each tubular cooling medium As the end of the flow path opens to the outside, it is fixedly arranged through the outer peripheral wall of the gas pipe, and further on the gas pipe outer surface or the entire gas pipe outer surface on both ends of the tubular cooling medium flow path group, A cooling jacket having an inlet / outlet for the cooling medium is fixed, and the gas in the gas pipe is cooled by the cooling medium flowing through the tubular cooling medium flow path. .

同じく第３発明は、冷却媒体の流入口もしくは流出口のいずれかを有し、相対する冷却ジャケットの間にあって、ガスの流れ方向に対して直角に交差する伝熱管を、間隔を保持して複数配置したガス冷却装置において、前記冷却ジャケットによって覆われている部分を除く隣接する壁面に、ガスの流れ方向に対して平行に、もしくは交差して複数のフレキ成形部及び／又は複数の放熱用フィンを有することを特徴とするものである。
又、このガス冷却装置においては、前記間隔を保持して複数配置される伝熱管の外周面に、ガスの流れ方向に対して平行に、複数のプレートフィンを接合したり、前記伝熱管に接合されるプレートフィンの他端を、前記フレキ成形部に挿入し、挟持させたりすることを好ましい態様とし、さらに前記プレートフィンには、波形、うねりを有した矩形の波形、貫孔、凹凸、ルーバー等の加工が施されていること、前記ガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付けであることを好ましい態様とするものである。 Similarly, in the third invention, a plurality of heat transfer tubes having either a cooling medium inflow port or an outflow port and intersecting at right angles to the gas flow direction between the opposed cooling jackets are maintained at intervals. In the arranged gas cooling apparatus, a plurality of flexible molding portions and / or a plurality of heat radiation fins are arranged on an adjacent wall surface excluding a portion covered by the cooling jacket in parallel or intersecting with the gas flow direction. It is characterized by having.
Further, in this gas cooling apparatus, a plurality of plate fins are joined to the outer peripheral surface of the plurality of heat transfer tubes arranged while maintaining the interval in parallel to the gas flow direction, or joined to the heat transfer tubes. It is preferable that the other end of the plate fin is inserted into the flexible molding portion and sandwiched, and the plate fin has a corrugated shape, a corrugated rectangular corrugated shape, a through hole, an unevenness, and a louver. It is preferable that the processing such as the above is performed and the joining means of each part constituting the gas cooling device is welding and / or brazing.

同じく第４発明は、冷却媒体の流入口若しくは流出口のいずれかを有し、相対する冷却ジャケットの間にあって、ガスの流れ方向に対して直角に交差する複数の偏平伝熱管を、間隔を保持して配置したガス冷却装置であって、前記偏平伝熱管の偏平した外表面に、ガスの流れ方向に対して平行に、多数のチャンネル形状のフィンを設けたことを特徴とするものである。
又、このガス冷却装置においては、前記フィンが前記偏平伝熱管の全長にわたりもしくは長さ方向に小型分割形状、切り起こし付き帯状フィンであることを特徴とし、さらに前記フィンには、ルーバー、貫孔、凹凸、波形等が設けられたり、又、前記フィンを偏平伝熱管同士若しくは偏平伝熱管と冷却装置外壁との間において圧接せしめたのち、接合したり、さらに前記フィンを含むガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付であることを好ましい態様とするものである。 Similarly, in the fourth invention, a plurality of flat heat transfer tubes that have either an inlet or an outlet for the cooling medium and that intersect between the opposing cooling jackets and intersect at right angles to the gas flow direction are maintained at intervals. In the gas cooling device arranged in this manner, a large number of channel-shaped fins are provided on the flat outer surface of the flat heat transfer tube in parallel with the gas flow direction.
Further, in this gas cooling device, the fin is a strip-shaped fin with a small divided shape and cut and raised over the entire length of the flat heat transfer tube or in the length direction. , Irregularities, corrugations, etc. are provided, and the fins are joined between flat heat transfer tubes or between the flat heat transfer tubes and the outer wall of the cooling device, and then joined, and further constitute a gas cooling device including the fins It is preferable that the joining means of each part to be performed is welding and / or brazing.

同じく第５発明は、冷却媒体の流入口若しくは流出口のいずれかを有し、相対する冷却ジャケットの間にあって、ガスの流れ方向に対して直角に交差する複数の偏平伝熱管を、間隔を保持して複数配置したガス冷却装置であって、前記間隔を保持して配置した偏平伝熱管の偏平した外表面に、略直角でかつガスの流れ方向に対して平行に多数のフィンを設け、これを交互に介装させて固定することによってコアを形成せしめたことを特徴とするものである。
又、このガス冷却装置においては、前記コアのアスペクト比が、偏平伝熱管長さ／ＥＧＲガス流路の長さ比において、１：１．５〜１：７、または１：２．５〜１：５であること、前記偏平伝熱管単体が、一体もの、若しくは複数の偏平管で構成されていること、前記一体ものの偏平伝熱管単体は、内部に１〜複数個の補強用リブを有すること、前記偏平伝熱管の偏平した外表面に固定されるフィンが、ガスの流れ方向に蛇行するように固定されていること、前記偏平伝熱管単体は、ガスの流れ方向に波型に変形して形成され、その外表面に固定されるフィンも同様に波型に形成されること、前記フィンが、コルゲートフィンであること、前記フィンには、ルーバー、貫孔、ピンフィン等が設けられること、ガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付であることを好ましい態様とするものである。 Similarly, in the fifth invention, a plurality of flat heat transfer tubes that have either an inlet or an outlet for the cooling medium and that intersect between the opposing cooling jackets and intersect at right angles to the gas flow direction are maintained at intervals. A plurality of gas cooling devices provided on the flat outer surface of the flat heat transfer tubes arranged with the gap therebetween, provided with a plurality of fins substantially perpendicular to and parallel to the gas flow direction. The core is formed by alternately interposing and fixing the cores.
In this gas cooling apparatus, the aspect ratio of the core is 1: 1.5 to 1: 7 or 1: 2.5 to 1 in the ratio of the flat heat transfer tube length / EGR gas flow path. : 5, the flat heat transfer tube itself is composed of one or a plurality of flat tubes, and the single flat heat transfer tube has one to a plurality of reinforcing ribs inside. The fin fixed to the flat outer surface of the flat heat transfer tube is fixed to meander in the gas flow direction, and the flat heat transfer tube itself is deformed into a wave shape in the gas flow direction. The fins formed and fixed to the outer surface thereof are also formed in a corrugated shape, the fins are corrugated fins, the fins are provided with louvers, through holes, pin fins, etc., gas Connection of each part of the cooling device Means, it is an preferred embodiment that the welding and / or brazing.

同じく第６発明は、冷却媒体の流入口若しくは流出口のいずれかを有し、相対する冷却ジャケットの間にあって、ガスの流れ方向に対して直角に交差する伝熱管を、間隔を保持して複数配置したガス冷却装置において、該伝熱管の断面形状をガスの流れ方向後方に向かって、その幅を次第に拡張せしめた楔形形状とし、該楔形形状の伝熱管内を通流する冷却媒体によってガスを冷却することを特徴とするものである。
又、このガス冷却装置においては、前記楔形形状の伝熱管同士、若しくは該伝熱管とガス配管との間隙に、ガスの流れ方向と平行してプレートフィンが固着されてなること、前記プレートフィンには貫孔、ルーバー、ピンフィン、凹凸等が設けられること、前記プレートフィンを含む前記ガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付であることを好ましい態様とするものである。 Similarly, according to the sixth aspect of the present invention, a plurality of heat transfer tubes that have either an inlet or an outlet for the cooling medium and that intersect between the opposing cooling jackets and intersect at right angles to the gas flow direction are spaced apart. In the arranged gas cooling device, the cross-sectional shape of the heat transfer tube is a wedge shape whose width is gradually expanded toward the rear of the gas flow direction, and the gas is supplied by the cooling medium flowing through the heat transfer tube of the wedge shape. It is characterized by cooling.
In this gas cooling device, plate fins are fixed in parallel to the gas flow direction between the wedge-shaped heat transfer tubes or between the heat transfer tubes and the gas pipes. Is preferably provided with through-holes, louvers, pin fins, irregularities, etc., and the joining means of each part constituting the gas cooling device including the plate fins is welding and / or brazing. .

同じく第７発明は、ガス配管内を流れるガスの流れ方向に対して直角に交差する伝熱管が、間隔を保持して複数配置されたガス冷却装置において、該伝熱管はその両管端を開口した状態で前記ガス配管の外周壁を貫通して固着配列され、該固着配列された伝熱管列群の管軸方向両端におけるガス配管の上下若しくは両側面又は全周に渡るガス配管外周面に、冷却媒体の流入口若しくは流出口のいずれかを有する冷却ジャケットが固着され、該冷却ジャケットの流入口から流入した冷却媒体が、前記伝熱管列群を経由して他の冷却ジャケット流出口から系外に流去する冷却媒体流路にあって、隣接する前記伝熱管列群境界の冷却媒体の流れ方向交互に堰を設け、該伝熱管内を通流する冷却媒体の流路と流速とを任意に制御しながら、該伝熱管列群を通流する冷却媒体によってガスを冷却することを特徴とするものである。
又、このガス冷却装置においては、前記伝熱管列群を形成する複数の伝熱管の形状が円筒状チューブ管、長円形の偏平管、断面楔形形状に加工された金属管等であること、前記伝熱管列群を形成するそれぞれの伝熱管同士、若しくは該伝熱管とガス配管外壁の内周面との間隙に、ガスの流れ方向に平行して、プレートフィンを固着してなること、前記プレートフィンには貫孔、ルーバー、ピンフィン、凹凸等が設けられること、前記プレートフィンを含むガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付であることを好ましい態様とするものである。 Similarly, according to a seventh aspect of the present invention, there is provided a gas cooling apparatus in which a plurality of heat transfer tubes intersecting at right angles to a flow direction of a gas flowing in a gas pipe are arranged at intervals, and the heat transfer tubes are opened at both ends. In such a state, the gas pipe is fixedly arranged through the outer peripheral wall of the gas pipe, and the gas pipe outer peripheral surface over the entire upper and lower sides or both sides or the entire circumference of the gas pipe at both ends in the tube axis direction of the heat transfer tube row group fixedly arranged. A cooling jacket having either an inlet or an outlet for the cooling medium is fixed, and the cooling medium flowing in from the inlet of the cooling jacket passes from the other cooling jacket outlet through the heat transfer tube array group. In which the weirs are alternately arranged in the flow direction of the cooling medium at the boundary between adjacent heat transfer tube groups, and the flow path and flow velocity of the cooling medium flowing through the heat transfer tubes are arbitrarily set. While controlling the heat transfer tube row It is characterized in that the gas is cooled by a cooling medium flowing through the.
Further, in this gas cooling device, the shape of the plurality of heat transfer tubes forming the heat transfer tube row group is a cylindrical tube tube, an oblong flat tube, a metal tube processed into a wedge-shaped cross section, etc. A plate fin fixed to each heat transfer tube forming the heat transfer tube row group or in a gap between the heat transfer tube and the inner peripheral surface of the gas pipe outer wall in parallel with the gas flow direction; The fins are preferably provided with through holes, louvers, pin fins, irregularities, etc., and the joining means of each part constituting the gas cooling device including the plate fins is welding and / or brazing. is there.

本発明に係るガス冷却装置は、以下に記載する効果を奏する。
第１発明及びに第２発明に係るガス冷却装置は、ガス配管内を流れるガスの流れに対し直角方向に交差するごとく配列した多数の冷却媒体流路、すなわちストレートパイプやフィン付きチューブからなる冷却配管、さらにこの冷却配管とフィンプレートの作用により、ガス流れの乱流化と伝熱面積の増大がはかられ、高い熱交換性能が得られるという優れた効果を奏する。 The gas cooling device according to the present invention has the effects described below.
The gas cooling device according to the first and second aspects of the present invention is a cooling system comprising a plurality of cooling medium flow paths arranged in a direction perpendicular to the flow of gas flowing in the gas pipe, that is, straight pipes and finned tubes. Due to the action of the piping, and the cooling piping and the fin plate, the gas flow is turbulent and the heat transfer area is increased, and an excellent effect is obtained in that high heat exchange performance is obtained.

第３発明に係るガス冷却装置は、冷却ジャケットによって覆われている部分を除く隣接する壁面に、ガスの流れ方向に対して平行に、もしくは交差して複数のフレキ成形を施すことにより、壁面に微妙な凹部が形成され、それによってガスの流れに乱流を生起せしめ、かつ拡張された接触面積によって外気との接触を促進させて、その冷却効率を上昇させることができ、さらに、上記のフレキ成形に替えて前記冷却ジャケットに覆われた部分を除く壁面や、その外側の壁面もしくは伝熱管の外周面に、ガスの流れ方向に対して平行に、もしくは交差して複数の放熱用プレートフィンを接合したり、又は該伝熱管に接合したプレートフィンの他端を、前記フレキ成形部に挿入して挟持させたり、あるいは該プレーフィンに波形、うねりを有した矩形の波形、貫孔、凹凸、ルーバー等の加工を施すことによって、同様平滑なガスの流れを妨げると共に、その流れに乱流や渦流を生ぜしめ、冷却ジャケットや伝熱管への接触を促進させて熱交換をはかり、その冷却効率を最大限に高めることが可能であり、その構造の簡略化と小型軽量化がはかられるため、得られたＥＧＲガス冷却装置は限られたスペースに容易に設置することができる。   A gas cooling device according to a third aspect of the present invention is provided on a wall surface by performing a plurality of flexible moldings on an adjacent wall surface excluding a portion covered by a cooling jacket in parallel or intersecting with a gas flow direction. A subtle recess is formed, thereby creating a turbulent flow in the gas flow and promoting contact with the outside air by the expanded contact area to increase its cooling efficiency. Instead of molding, a plurality of heat dissipating plate fins are provided on the wall surface excluding the portion covered by the cooling jacket, on the outer wall surface or on the outer peripheral surface of the heat transfer tube, in parallel or intersecting with the gas flow direction. The other end of the plate fin joined to the heat transfer tube is inserted into the flexible molded portion to be sandwiched, or the play fin has a waveform and a wave By processing the corrugated shape, through-holes, irregularities, louvers, etc., the same smooth flow of gas is prevented, and turbulence and vortex flow are generated in the flow to promote contact with the cooling jacket and heat transfer tube. Therefore, the EGR gas cooling system can be easily installed in a limited space because the structure can be simplified and the size and weight can be reduced. Can be installed.

第４発明に係るガス冷却装置は、ガスの流れに対して直交する主としてエンジン冷却水が用いられる冷却媒体が、前記偏平伝熱管によって流路を狭められ、その流速を増加させて該管内を通過すると共に、伝熱面積を広げて冷却効率の上昇をはかり、加えて該偏平伝熱管の外表面同士、もしくは該偏平伝熱管と前記ガス配管外壁との間に設けられた前記多数のチャンネル型フィンにも熱伝達されてこれを冷却し、その伝熱面積の拡大を一層促進する。一方、該偏平伝熱管およびチャンネル型フィンによってその流路を妨げられたＥＧＲガスは、不規則なガス流路内を乱流や渦流を伴いながら時間をかけて通過する。従って、ＥＧＲガスの熱はこの間に多数のチャンネル型フィン並びに前記偏平伝熱管内を高速で通過する冷却媒体に確実に熱伝達されて効率的に熱交換される。   According to a fourth aspect of the present invention, there is provided the gas cooling device according to the fourth aspect of the present invention, wherein the cooling medium mainly using the engine coolant orthogonal to the gas flow is narrowed by the flat heat transfer tube, and the flow rate is increased to pass through the tube. In addition, the cooling efficiency is increased by expanding the heat transfer area, and in addition, the multiple channel fins provided between the outer surfaces of the flat heat transfer tubes or between the flat heat transfer tubes and the outer wall of the gas pipe The heat is also transferred to cool this, and the expansion of the heat transfer area is further promoted. On the other hand, the EGR gas whose flow path is blocked by the flat heat transfer tube and the channel type fin passes through the irregular gas flow path with turbulent flow and vortex flow over time. Therefore, the heat of the EGR gas is surely transferred to the cooling medium passing at a high speed through the many channel-type fins and the flat heat transfer tube during this time, and efficiently exchanged heat.

又、前記チャンネル型フィンの形状を小型の分割形状とすることにより、偏平伝熱管同士および偏平伝熱管とガス配管の外壁との間に配列して固定する際、任意の位置に任意のピッチで配列することが可能となり、ＥＧＲガス流に対応した形で配列することによって、その放熱を促進することができる。さらに、分割方式としたことによって組み付けに際して、偏平伝熱管とチャンネル型フィンとの間での組み付け用穴ピッチが合わずに、組み付けに困難を生ずるという問題は未然に解消される上、該チャンネル型フィンを小割の断面略コの字形状としたことにより、該フィンと偏平伝熱管の平坦部との接合の密着性とその確実性が保障され、熱交換性能の一層の向上をはかることができる。   In addition, by making the shape of the channel type fin into a small divided shape, when arranging and fixing between the flat heat transfer tubes and between the flat heat transfer tubes and the outer wall of the gas pipe, at an arbitrary pitch at an arbitrary position. It becomes possible to arrange, and by arranging in a form corresponding to the EGR gas flow, the heat dissipation can be promoted. Furthermore, the problem that the assembly hole pitch between the flat heat transfer tube and the channel type fins does not match and causes difficulty in the assembly is solved by the division method, and the channel type By making the fin a substantially U-shaped with a small cross section, it is possible to ensure the adhesion and reliability of the junction between the fin and the flat portion of the flat heat transfer tube, and to further improve the heat exchange performance. it can.

さらに、偏平伝熱管どうしもしくは該偏平伝熱管とガス配管との間に、前記チャンネル型フィンを密着させて固定することにより強固な支持体となって作用し、補強効果を発揮するため、過酷な運転条件の中で配設される当該ガス冷却装置として、そのまま用いることが可能なために装置の小型軽量化が可能となり、冷却装置のコンパクト化がはかられ、限られたスペースに容易に設置することができる。   Furthermore, since the channel-type fins are closely attached and fixed between the flat heat transfer tubes or between the flat heat transfer tubes and the gas pipe, it acts as a strong support and exerts a reinforcing effect. As the gas cooling device installed in the operating conditions, it can be used as it is, making it possible to reduce the size and weight of the device, making the cooling device more compact and easily installing it in a limited space. can do.

第５発明に係るガス冷却装置は、偏平伝熱管の外表面に対して略直角で、かつガスの流れ方向に対してほぼ平行に、多数のフィンを交互に介装させて固定することによってコアの１セグメントを形成せしめる構成としたことにより、ガスの流れに対して直交する主としてエンジン冷却水が用いられる冷却媒体が、前記偏平伝熱管によって流路を狭められ、その流速を増加させて該管内を通過し、一方、ガス流は、該偏平伝熱管の外表面に多数のフィンを介装・固定することにより、偏平伝熱管と偏平伝熱管との間隔の交互の積層において多数のセグメントによりコアが形成され、該コア内の長いガス流路を時間をかけて通過することとなり、ガスの熱はこの間に偏平伝熱管の外表面と多数のフィンに熱伝達され、該ガス流に対して直交して、前記偏平伝熱管内を高速で通過する冷却媒体に確実に熱伝達されて効率的に熱交換される。   According to a fifth aspect of the present invention, there is provided a gas cooling device comprising: a core by alternately interposing and fixing a plurality of fins substantially perpendicular to the outer surface of the flat heat transfer tube and substantially parallel to the gas flow direction. Therefore, the cooling medium that mainly uses engine cooling water orthogonal to the gas flow is narrowed by the flat heat transfer tube, and the flow rate is increased to increase the flow rate in the tube. On the other hand, the gas flow is cored by a number of segments in an alternating stack of flat heat transfer tubes and flat heat transfer tubes by interposing and fixing a large number of fins on the outer surface of the flat heat transfer tubes. And the gas heat is transferred to the outer surface of the flat heat transfer tube and a large number of fins in the meantime, and is orthogonal to the gas flow. do it, Serial The flat heat transfer tube is securely heat transfer to the cooling medium passing through at high speed is effectively heat exchanger.

又、前記偏平伝熱管及びこれに固定されるフィンによって形成される前記コアのアスペクト比、即ち偏平伝熱管長さ／ＥＧＲガス流路長さの比を、１：１．５〜１：７、好ましくは１：２．５〜１：５としたことにより、その熱伝達性能を一層向上させ、ＥＧＲガスの冷却効率をさらに高めることが可能となる。さらに、偏平伝熱管の外表面に固定する前記フィンを、ガスの流れ方向に対して蛇行するように設けたり、または形成されるコアを同様ガスの流れ方向に蛇行させたり、固定するフィンの形状をコルゲートフィンとしたり、あるいはプレートフィンに対してルーバー、貫孔、ピンフィン等を設けることによって、ガスの流路を長くせしめるのみならず、適宜に乱流や渦流を生起せしめて、フィンとの接触をさらに促し、該フィンを介して偏平伝熱管への熱伝達を効果的に促進して、その冷却効率を最大限に高めることが可能である。   The aspect ratio of the core formed by the flat heat transfer tubes and the fins fixed thereto, that is, the ratio of the flat heat transfer tube length / EGR gas flow path length is 1: 1.5 to 1: 7, Preferably, the ratio of 1: 2.5 to 1: 5 can further improve the heat transfer performance and further enhance the cooling efficiency of the EGR gas. Further, the shape of the fin for fixing the fin fixed to the outer surface of the flat heat transfer tube so as to meander with respect to the gas flow direction, or to meander or fix the core to be formed in the same direction of gas flow. Corrugated fins, or by providing louvers, through holes, pin fins, etc. to the plate fins, not only lengthen the gas flow path but also cause turbulence and vortices as appropriate, and contact with the fins It is possible to further enhance the cooling efficiency by effectively promoting the heat transfer to the flat heat transfer tubes via the fins.

さらに、偏平伝熱管どうしもしくは該偏平伝熱管とガス配管との間に、前記コルゲートフィンを介装させて固定することによって形成されるコアが、強固な支持体となって作用し、補強効果を発揮するため、過酷な運転条件の中で配設される当該ガス冷却装置として、そのまま用いることが可能なために装置の小型軽量化が可能となり、冷却装置のコンパクト化がはかられ、限られたスペースに容易に設置することができる。   Further, the core formed by interposing and fixing the corrugated fins between the flat heat transfer tubes or between the flat heat transfer tubes and the gas pipe acts as a strong support, and has a reinforcing effect. Because it can be used as the gas cooling device installed under severe operating conditions, it can be used as it is, making it possible to reduce the size and weight of the device, making the cooling device more compact and limited. It can be installed easily in an open space.

第６発明に係るガス冷却装置は、伝熱管の断面形状をガスの流れ方向上流側（先端部）から下流方向（後端部）に向かうに従って、その幅を次第に拡張せしめた楔形形状とし、該楔形形状の伝熱管内を通流する冷却媒体によってガスを冷却する構成となしたことにより、ガスのガス流は冷却された伝熱管の傾斜した伝熱面の全てに対して衝突を繰り返しながら下流側に進行するが、この際、該ガス流は傾斜した伝熱面への衝突と同時に境界層を徐々に剥離しながら進行するため、該伝熱面における表面状態が改善され、ガス流は境界層の厚みを増すことなく下流方向に進み、全ての伝熱面での効果的な熱交換が進行して、優れた冷却効率が保障される。又、断面楔形形状の伝熱管の外周面を下流側に進行するガス流は、該伝熱管の後方側における急激な断面変化を受けていわゆる「カルマンの渦列」を生じ、流速を高めて伝熱管の背面や下流側に配置された伝熱面を含め、該伝熱管の全ての伝熱面において効果的な熱交換が促進され、優れた冷却性能を発揮することができる。一方、楔形形状の伝熱管内を通流する冷却媒体は、前記伝熱管の幅の狭い先端面ではその流路を狭められ、流速を増加させて該管内を通過することにより冷却効率の上昇をはかり、幅の拡張された下流側においては多量の冷却水が少ない流過抵抗により流れて沸騰を制御して、その拡張された表面積と共に効果的な熱交換がはかられ、冷却性能の一層の向上に寄与する。   A gas cooling device according to a sixth aspect of the present invention has a wedge-shaped shape in which the cross-sectional shape of the heat transfer tube is gradually expanded in width from the upstream side (front end portion) to the downstream direction (rear end portion) in the gas flow direction. Since the gas is cooled by the cooling medium that flows in the wedge-shaped heat transfer tube, the gas flow of the gas flows downstream while repeatedly colliding with all the inclined heat transfer surfaces of the cooled heat transfer tube. However, at this time, the gas flow proceeds while gradually peeling the boundary layer simultaneously with the collision with the inclined heat transfer surface, so that the surface condition on the heat transfer surface is improved, and the gas flow The process proceeds downstream without increasing the thickness of the layer, and effective heat exchange proceeds on all the heat transfer surfaces to ensure excellent cooling efficiency. In addition, the gas flow traveling downstream on the outer peripheral surface of the heat transfer tube having a wedge-shaped cross section undergoes a sudden cross-sectional change on the rear side of the heat transfer tube to generate a so-called “Kalman vortex street”, increasing the flow velocity and transferring the gas flow. Effective heat exchange is promoted on all the heat transfer surfaces of the heat transfer tube including the heat transfer surface arranged on the back surface or downstream side of the heat tube, and excellent cooling performance can be exhibited. On the other hand, the cooling medium flowing through the wedge-shaped heat transfer tube has its flow path narrowed at the narrow end face of the heat transfer tube, and the cooling efficiency is increased by passing through the tube at an increased flow rate. On the downstream side where the width is expanded, a large amount of cooling water flows with a low flow resistance to control boiling, and effective heat exchange is achieved along with the expanded surface area. Contributes to improvement.

又、楔形形状の伝熱管同士もしくは該伝熱管とガス配管との間に、前記任意形状のプレートフィンを密着させて固定することにより、伝熱面積の増大により一層の熱交換効率の向上がはかられると共に、ガス配管内における強固な支持体となって作用して補強効果を発揮するため、過酷な運転条件の中で配設されるガス冷却装置としてそのまま用いることができ、装置の小型軽量化とコンパクト化が可能となり、限られたスペースに容易に設置することができる。   In addition, by fixing the plate fin of the arbitrary shape in close contact with each other between the wedge-shaped heat transfer tubes or between the heat transfer tube and the gas pipe, the heat transfer area can be further increased to further improve the heat exchange efficiency. In addition, it acts as a strong support in the gas piping and exerts a reinforcing effect, so it can be used as it is as a gas cooling device placed under severe operating conditions. And can be easily installed in a limited space.

第７発明に係るガス冷却装置は、当該装置内に複数配列される伝熱管列群のそれぞれの境界に、交互に堰を設け、該堰の位置を任意に変更することによって、該伝熱管列群を通流する冷却媒体の流路を意のままに制御できるため、その流れ方向流速や流量を任意にコントロールすることが可能となり、冷却媒体を所望の伝熱管列群、さらには該伝熱管列群単位の個々の伝熱管に集中して通流させることも可能となり、該冷却装置の冷却媒体流路内における淀みや流量のばらつき幅を減少させて、それに起因する冷却媒体の沸騰や該沸騰によって生じた気泡を速やかに伝熱面から剥離・移動させて冷却効率の低下を未然に抑制することができる。   In the gas cooling device according to the seventh aspect of the present invention, the heat transfer tube row is provided by alternately providing a weir at each boundary of a plurality of heat transfer tube row groups arranged in the device, and arbitrarily changing the position of the weir. Since the flow path of the cooling medium flowing through the group can be controlled as desired, the flow direction flow velocity and flow rate can be arbitrarily controlled, and the cooling medium can be controlled to a desired heat transfer tube array group, and further to the heat transfer tube. It is also possible to concentrate the flow through the individual heat transfer tubes of the row group unit, reduce the stagnation and flow rate variation in the cooling medium flow path of the cooling device, and cause the boiling of the cooling medium and the Bubbles generated by boiling can be promptly peeled and moved from the heat transfer surface to prevent a decrease in cooling efficiency.

又、組み込まれる伝熱管の形状は自由で、従来から多用されている各種円筒状チューブ管、長円形の偏平管、断面楔形形状に加工された金属管等の中から適宜に採用することが可能である。さらに、伝熱管同士もしくは該伝熱管とガス配管との間に、前記任意形状のプレートフィンを密着させて固定することにより、伝熱面積の増大をはかり、より一層の熱交換効率をはかると共に、ガス配管内における強固な支持体となって作用して補強効果を発揮するため、過酷な運転条件の中で配設される当該ガス冷却装置としてそのまま用いることができ、装置の小型軽量化とコンパクト化が可能となり、限られたスペースに容易に設置することができる。
さらに、本発明のガス冷却装置のガス配管（胴管を含む）や冷却配管あるいは伝熱管の壁面に必要に応じて凹凸を形成して乱流化や伝熱面積を増加させてもよい。 In addition, the shape of the heat transfer tube to be incorporated is free, and can be appropriately selected from various types of conventionally used cylindrical tube tubes, oblong flat tubes, metal tubes processed into wedge-shaped cross sections, etc. It is. Furthermore, between the heat transfer tubes or between the heat transfer tube and the gas pipe, by fixing the plate fin of the arbitrary shape in close contact, the heat transfer area is increased, and further heat exchange efficiency is achieved. Since it acts as a strong support in the gas pipe and exerts a reinforcing effect, it can be used as it is as the gas cooling device placed under severe operating conditions, making the device smaller and lighter and compact And can be easily installed in a limited space.
Furthermore, irregularities may be formed on the wall of the gas pipe (including the trunk pipe), the cooling pipe or the heat transfer pipe of the gas cooling apparatus of the present invention as necessary to increase the turbulent flow or heat transfer area.

なお、本発明によるガス冷却装置は、例えばエンジン冷却水を冷却媒体として用いることにより、偏平伝熱管の内表面の伝熱係数が、ＥＧＲガスに対してほぼ１０倍となるため、該外表面に接触したガスは確実に冷却され、優れた熱交換性能を得ることができる。   In the gas cooling device according to the present invention, for example, by using engine cooling water as a cooling medium, the heat transfer coefficient of the inner surface of the flat heat transfer tube is almost 10 times that of EGR gas. The gas in contact is reliably cooled, and excellent heat exchange performance can be obtained.

図１〜図１８は本発明の請求項１〜５に対応するガス冷却装置であって、図１は第１実施例装置を一部省略して示す縦断側面図、図２は図１のイーイ線上の横断平面図、図３は図１のローロ線上の縦断正面図、図４は第２実施例装置を一部省略して示す縦断側面図、図５は図４のハーハ線上の横断平面図、図６は第３実施例装置を一部省略して示す縦断側面図、図７は図６のニーニ線上の横断平面図、図８は図６、図７に示す第３実施例装置における冷却配管（伝熱管）とプレートフィンの接合構造の一例を示す断面図、図９は図６、図７に示す第３実施例装置におけるプレートフィンの各種構造例を示す断面図で、（ａ）は貫孔を設けたプレートフィン、（ｂ）（ｃ）はルーバーを設けたプレートフィン、（ｄ）はピンフィンを設けたプレートフィン、（ｅ）はプレス成形による凹凸を設けたプレートフィンをそれぞれ示す。図１０は第４実施例装置を一部省略して示す縦断側面図、図１１は図１０のホーホ線上の横断平面図、図１２は図１０のヘーヘ線上の縦断正面図、図１３は第５実施例装置を一部省略して示す縦断側面図、図１４は図１３のトート線上の縦断正面図、図１５（ａ）（ｂ）は第５実施例装置における波板部品を拡大して示す部分斜視図である。
図１６〜図２３は本発明の請求項６に対応するガス冷却装置であって、図１６は第６実施例装置を示す縦断側面図、図１７は同上装置におけるプレートフィンを示す斜視図、図１８は図１６のチ−チ線上の横断平面図、図１９は図１６のリ−リ線上の縦断正面図、図２０は第７実施例装置を示す縦断側面図、図２１は同上第７実施例装置におけるプレートフィンを示す斜視図、図２２は図２０のヌ−ヌ線上の横断平面図、図２３は図２０のル−ル線上の縦断正面図である。
図２４〜図３４は本発明の請求項７〜１１に対応するガス冷却装置であって、図２４は第８実施例装置を示す模式的な要部斜視図、図２５は同上実施例装置におけるフレキ成形部を示す要部斜視図、図２６は同上実施例装置におけるフレキ成形部の要部斜視図、図２７は第９実施例装置を示す縦断正面図、図２８は第１０実施例装置を示し、（ａ）は横断平面図、（ｂ）は縦断正面図、図２９は第１１実施例装置を示し、（ａ）は横断平面図、（ｂ）は縦断正面図、図３０は第１２実施例装置を示し、（ａ）は横断平面図、（ｂ）は縦断正面図、図３１は第１３実施例装置を示し、（ａ）は横断平面図、（ｂ）は縦断正面図、図３２は上記第８実施例装置〜第１３実施例装置に任意に用いられるうねりを有した波形フィンの一部を示す斜視図である。
図３３〜図４０は本発明の請求項１２〜１７に対応するガス冷却装置であって、図３３は第１４実施例装置を示す模式的正面図、図３４は同上実施例装置を部分的に示す一部拡大断面図、図３５は第１５実施例装置を示す模式的正面図、図３６は同上実施例装置を部分的に示す一部拡大断面図、図３７は同上実施例装置において用いられる一部切り起こし帯状フィン単体を示す斜視図、図３８は各実施例装置において任意に用いることが可能な各種フィンの単体を示す斜視図で、（ａ）は円形の孔を設けたもの、（ｂ）は断面半円形の凹凸を設けたもの、（ｃ）は断面凹凸状のヒダを全長にわたり設けたもの、（ｄ）はリップ状の折り曲げ部を形成したものをそれぞれ示し、図３９（ａ）（ｂ）（ｃ）は各種フィンのうち、ルーバーを設けたものを例示した斜視図、図４０はフィンの組み付け状態を部分的に示す平面図である。
図４１〜図４８は本発明の請求項１８〜２７に対応するガス冷却装置であって、図４１は第１６実施例装置を示す模式的正面図、図４２は同上実施例装置における伝熱管の他の実施例を部分的に示す一部拡大斜視図、図４３は同じく伝熱管の別の実施例を部分的に示す正面図、図４４は同じく伝熱管のさらに他の実施例を部分的に示す斜視図、図４５は同じく伝熱管のさらに別の実施例を部分的に示す平面図、図４６は第１７実施例装置を示す概略三面図で、（ａ）はその平面図、（ｂ）はその縦断側面図、（ｃ）は（ａ）のア−ア線上の横断平面図、図４７は上記各実施例装置において任意に用いることが可能な各種フィンを部分的に示し、（ａ）はＩ型形状フィン、（ｂ）はＳ字型形状フィン、（ｃ）はコの字型形状フィンを示す斜視図、図４８は同じくプレートフィンの構造を示す断面図で、（ａ）はプレートフィンに貫孔を設けたもの、（ｂ）および（ｃ）はルーバーを設けたもの、（ｄ）はピンフィンを設けたもの、（ｅ）は凹凸を設けたものをそれぞれ示す。
図４９〜図５６は本発明の請求項２８〜３１に対応するガス冷却装置であって、図４９は第１８実施例装置を示す縦断側面図、図５０は図４９のル−ル線上の横断平面図、図５１は図４９のオ−オ線上の縦断正面図、図５２は第１９実施例装置を示す縦断側面図、図５３は図５２のワ−ワ線上の横断平面図、図５４は図５２のカ−カ線上の縦断正面図、図５５は本発明に係る伝熱管単体の一例を示す斜視図、図５６は同じく伝熱管単体の他の例を示す斜視図である。
図５７〜図７４は本発明の請求項３２〜３６に対応するガス冷却装置であって、図５７は第１９実施例装置を一部省略して示す縦断側面図、図５８は図５７のヨ−ヨ線上の横断平面図、図５９は図５７のタ−タ線上の縦断正面図、図６０は第２０実施例装置を一部省略して示す縦断側面図、図６１は図６０のレ−レ線上の横断平面図、図６２は第２１実施例装置を一部省略して示す縦断側面図、図６３は図６２のソ−ソ線上の横断平面図、図６４は第２２実施例装置を一部省略して示す縦断側面図、図６５は図６４のツ−ツ線上の横断平面図、図６６は図６４のネ−ネ線上の縦断正面図、図６７は第２３実施例装置を一部省略して示す縦断側面図、図６８は図６７のナ−ナ線上の縦断正面図、図６９は第２４実施例装置を一部省略して示す縦断側面図、図７０は図６９のラ−ラ線上の横断平面図、図７１は図６９のム−ム線上の縦断正面図、図７２は第２５実施例装置を一部省略して示す縦断側面図、図７３は図７４のウーウ線上の横断平面図、図７４は図７２のノ−ノ線上の縦断正面図、図７５は本発明の各実施例装置のガス配管（胴管を含む）壁面の断面構造の一例を示す部分断面図、図７６は同じく本発明の各実施例装置の冷却配管あるいは伝熱管の壁面の断面構造の一例を示す部分断面図である。
なおここでは、ＥＧＲガスの冷却装置を例にとり説明する。 1 to 18 are gas cooling apparatuses corresponding to claims 1 to 5 of the present invention. FIG. 1 is a longitudinal side view showing a part of the apparatus of the first embodiment, and FIG. FIG. 3 is a longitudinal sectional front view on the roll line of FIG. 1, FIG. 4 is a longitudinal sectional side view showing a part of the apparatus of the second embodiment omitted, and FIG. 5 is a transverse planar view on the haha line of FIG. 6 is a longitudinal side view showing the third embodiment apparatus with a part omitted, FIG. 7 is a transverse plan view on the Nini line of FIG. 6, and FIG. 8 is a cooling in the third embodiment apparatus shown in FIGS. FIG. 9 is a sectional view showing an example of a joining structure of a pipe (heat transfer tube) and a plate fin, FIG. 9 is a sectional view showing various structural examples of the plate fin in the third embodiment apparatus shown in FIG. 6 and FIG. Plate fins with through-holes, (b) and (c) plate fins with louvers, (d) pre-pin fins Tofin, (e) denotes a plate fin having irregularities by press molding. FIG. 10 is a longitudinal side view showing the apparatus of the fourth embodiment with a part thereof omitted, FIG. 11 is a cross-sectional plan view on the hoho line in FIG. 10, FIG. 12 is a longitudinal front view on the hae line in FIG. FIG. 14 is a front view of the longitudinal section on the tote line in FIG. 13, and FIGS. 15A and 15B are enlarged views of corrugated plate parts in the fifth embodiment apparatus. It is a fragmentary perspective view.
FIGS. 16 to 23 show a gas cooling device corresponding to claim 6 of the present invention, in which FIG. 16 is a longitudinal side view showing the device of the sixth embodiment, FIG. 17 is a perspective view showing plate fins in the device, and FIG. 18 is a cross-sectional plan view on the teach line in FIG. 16, FIG. 19 is a longitudinal front view on the reel line in FIG. 16, FIG. 20 is a longitudinal side view showing the apparatus of the seventh embodiment, and FIG. The perspective view which shows the plate fin in an example apparatus, FIG. 22 is the cross-sectional top view on the Noon line of FIG. 20, FIG. 23 is the vertical front view on the Rule line of FIG.
FIGS. 24 to 34 are gas cooling apparatuses corresponding to the seventh to eleventh aspects of the present invention, FIG. 24 is a schematic perspective view of the main part showing the eighth embodiment apparatus, and FIG. 25 is the same as the embodiment apparatus. FIG. 26 is a perspective view of the principal part of the flexible molding part in the apparatus of the embodiment, FIG. 27 is a longitudinal front view of the ninth embodiment apparatus, and FIG. 28 is the tenth embodiment apparatus. FIG. 29A is a cross-sectional plan view, FIG. 29B is a vertical front view, FIG. 29 is an eleventh embodiment device, FIG. 29A is a cross-sectional plan view, FIG. FIG. 31 shows a cross-sectional plan view, FIG. 31 shows a thirteenth embodiment device, (a) a cross-sectional plan view, and (b) a vertical front view, FIG. 32 is a perspective view showing a part of a corrugated fin having undulations optionally used in the eighth embodiment apparatus to the thirteenth embodiment apparatus. A.
FIGS. 33 to 40 are gas cooling apparatuses corresponding to claims 12 to 17 of the present invention. FIG. 33 is a schematic front view showing a fourteenth embodiment apparatus, and FIG. FIG. 35 is a schematic front view showing the fifteenth embodiment apparatus, FIG. 36 is a partially enlarged sectional view partially showing the embodiment apparatus, and FIG. 37 is used in the embodiment apparatus. FIG. 38 is a perspective view showing a single piece of various fins that can be arbitrarily used in each example device, and FIG. 38A is a view provided with a circular hole. FIG. 39 (a) shows a case in which unevenness with a semicircular cross section is provided, FIG. 39 (c) shows a case in which folds with an uneven cross section are provided over the entire length, and FIG. ) (B) (c) provided louvers among various fins Illustrated perspective view from FIG. 40 is a plan view showing an assembled state of the fin partially.
FIGS. 41 to 48 are gas cooling apparatuses corresponding to claims 18 to 27 of the present invention. FIG. 41 is a schematic front view showing the apparatus of the sixteenth embodiment, and FIG. 42 is a view of the heat transfer tube in the apparatus of the same embodiment. FIG. 43 is a partially enlarged perspective view partially showing another embodiment, FIG. 43 is a front view partially showing another embodiment of the heat transfer tube, and FIG. 44 is a partial view of still another embodiment of the heat transfer tube. 45 is a plan view partially showing still another embodiment of the heat transfer tube, FIG. 46 is a schematic three-view diagram showing the seventeenth embodiment device, (a) is a plan view thereof, and (b) is a plan view thereof. Is a longitudinal side view thereof, (c) is a cross-sectional plan view on the line A of (a), FIG. 47 is a partial view of various fins that can be arbitrarily used in the devices of the above embodiments, (a) Is an I-shaped fin, (b) is an S-shaped fin, and (c) is a perspective view showing a U-shaped fin. FIG. 48 is a cross-sectional view showing the structure of the plate fin. (A) is a plate fin provided with a through hole, (b) and (c) are provided with a louver, and (d) is provided with a pin fin. And (e) show those provided with irregularities.
49 to 56 are gas cooling apparatuses corresponding to claims 28 to 31 of the present invention, wherein FIG. 49 is a longitudinal side view showing the apparatus of the eighteenth embodiment, and FIG. 50 is a cross-sectional view on the rule line of FIG. FIG. 51 is a longitudinal front view of FIG. 49 taken along the line of FIG. 49. FIG. 52 is a longitudinal side view of the nineteenth embodiment. FIG. FIG. 52 is a perspective view showing an example of a single heat transfer tube according to the present invention, and FIG. 56 is a perspective view showing another example of the single heat transfer tube.
57 to 74 are gas cooling devices corresponding to claims 32 to 36 of the present invention. FIG. 57 is a longitudinal side view showing a part of the nineteenth embodiment omitted, and FIG. 58 is a side view of FIG. 59 is a cross-sectional plan view on the line Y, FIG. 59 is a vertical front view on the line of FIG. 57, FIG. 60 is a vertical side view showing a part of the twentieth embodiment omitted, and FIG. 62 is a longitudinal sectional side view showing the apparatus of the 21st embodiment with a part thereof omitted, FIG. 63 is a transverse plane view on the source line of FIG. 62, and FIG. 64 is the apparatus of the 22nd embodiment. FIG. 65 is a cross-sectional plan view taken along the line of FIG. 64, FIG. 66 is a longitudinal front view of the line of FIG. 64, and FIG. 68 is a vertical side view of the vertical section on the null line of FIG. 67, and FIG. 69 is a vertical view of the apparatus shown in FIG. 70 is a cross-sectional plan view on the line of FIG. 69, FIG. 71 is a longitudinal front view on the line of FIG. 69, and FIG. 72 is a longitudinal side view partially omitting the 25th embodiment. 73, FIG. 73 is a transverse plan view on the Wu line in FIG. 74, FIG. 74 is a longitudinal front view on the Nono line in FIG. 72, and FIG. 75 is a wall surface of a gas pipe (including a trunk pipe) of each apparatus of the present invention. FIG. 76 is a partial cross-sectional view showing an example of the cross-sectional structure of the wall surface of the cooling pipe or the heat transfer tube of each embodiment of the present invention.
Here, an EGR gas cooling device will be described as an example.

まず、図１、図２、図３に示すＥＧＲガス冷却装置１は、断面矩形に拡径したＥＧＲガス配管２に、該配管内を流れるＥＧＲガスのガス流れ方向（矢印ｇ）に対して直角に交差する多数の冷却配管（伝熱管）３を、各配管の両管端が外部に開口するごとく当該ＥＧＲガス配管の外周壁を貫通して所定の間隔に固着配列する。そして、前記冷却配管の管軸方向両側のＥＧＲガス配管外面に冷却ジャケット４−１、４−２を固着する。この冷却ジャケット４−１、４−２には、それぞれ冷却媒体の流入口Ｐ１、流出口Ｐ２が設けられている。   First, the EGR gas cooling device 1 shown in FIG. 1, FIG. 2, and FIG. 3 is perpendicular to the gas flow direction (arrow g) of the EGR gas flowing in the EGR gas pipe 2 whose diameter is expanded to a rectangular cross section. A large number of cooling pipes (heat transfer pipes) 3 intersecting with each other are fixedly arranged at predetermined intervals through the outer peripheral wall of the EGR gas pipe as both pipe ends of the pipes open to the outside. Then, the cooling jackets 4-1 and 4-2 are fixed to the outer surfaces of the EGR gas pipes on both sides in the pipe axis direction of the cooling pipe. The cooling jackets 4-1 and 4-2 are respectively provided with an inlet P1 and an outlet P2 for the cooling medium.

上記構成のＥＧＲガス冷却装置１において、ＥＧＲガス配管２内を矢印ｇ方向に流れるＥＧＲガスは、一方の冷却ジャケット４−１より各冷却配管３内を矢印ｃ方向に流れる冷却媒体により冷却される。この時、ＥＧＲガス配管２を流れるＥＧＲガスは、当該ガス流れに対し交差するごとく配設した多数の冷却配管３によってガス流れが乱流化するため、多数の冷却配管３内をＥＧＲガス流れと直交する方向（矢印ｃ方向）に流れる冷却媒体との熱交換が速やかに行われる。   In the EGR gas cooling device 1 configured as described above, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 2 is cooled by the cooling medium flowing in the direction of the arrow c in each cooling pipe 3 from one cooling jacket 4-1. . At this time, since the EGR gas flowing through the EGR gas pipe 2 is turbulent by the multiple cooling pipes 3 arranged so as to intersect the gas flow, the EGR gas flow is circulated in the multiple cooling pipes 3. Heat exchange with the cooling medium flowing in the orthogonal direction (direction of arrow c) is promptly performed.

図４、図５に示すＥＧＲガス冷却装置１１は、冷却配管にフィン付きチューブ１３−１、１３−２を用いた以外は、図１、図２に示す冷却装置と同じ構成である。即ち、断面矩形に拡径したＥＧＲガス配管１２に、該配管内を流れるＥＧＲガスのガス流れ方向（矢印ｇ）に対して直角に交差する多数のフィン付きチューブ１３−１、１３−２を、各配管の両管端が外部に開口するごとく当該ＥＧＲガス配管の外周壁を貫通して所定の間隔に固着配列し、前記冷却配管の管軸方向両側のＥＧＲガス配管外面に冷却ジャケット１４−１、１４−２を固着したものである。ここで、前記フィン付きチューブ１３−１は、チューブ本体外周面にスパイラル状のフィン１３−１ａを、フィン付きチューブ１３−２は、チューブ本体外周面にディスク状のフィン１３−２ａを、それぞれ設けたものである。
なお、ここでは、スパイラル状フィン付きチューブ１３−１とディスク状フィン付きチューブ１３−２を組合わせた構成を示したが、スパイラル状のフィンやディスク状のフィンの外、波形フィン、ピン形フィン等を使用した各種フィン付きチューブを組合わせて構成してもよく、また、全体を１種類のチューブのみ、例えばスパイラル状フィン付きチューブ１３−１のみ、またはディスク状フィン付きチューブ１３−２のみ等で構成してもよいことはいうまでもない。 The EGR gas cooling device 11 shown in FIGS. 4 and 5 has the same configuration as the cooling device shown in FIGS. 1 and 2 except that finned tubes 13-1 and 13-2 are used for cooling piping. That is, a large number of finned tubes 13-1 and 13-2 that intersect the EGR gas pipe 12 expanded in a rectangular cross section at right angles to the gas flow direction (arrow g) of the EGR gas flowing in the pipe, As the both pipe ends of each pipe open to the outside, they pass through the outer peripheral wall of the EGR gas pipe and are fixedly arranged at a predetermined interval, and the cooling jacket 14-1 is attached to the outer surface of the EGR gas pipe on both sides in the pipe axis direction of the cooling pipe. 14-2 are fixed. Here, the finned tube 13-1 is provided with spiral fins 13-1a on the outer peripheral surface of the tube main body, and the tube 13-2 with fins is provided with disc-shaped fins 13-2a on the outer peripheral surface of the tube main body. It is a thing.
In addition, although the structure which combined the tube 13-1 with a spiral fin and the tube 13-2 with a disk-shaped fin was shown here, a corrugated fin and a pin-shaped fin outside a spiral fin and a disk-shaped fin were shown. Etc., and may be configured by combining various types of finned tubes using only one type of tube, for example, only a spiral finned tube 13-1 or a disk-shaped finned tube 13-2. Needless to say, it may be configured by.

上記図４、図５に示す構成のＥＧＲガス冷却装置１１の場合も、図１、図２に示す装置と同様、ＥＧＲガス配管１２内を矢印ｇ方向に流れるＥＧＲガスは、一方の冷却ジャケット１４−１より各フィン付きチューブ１３−１、１３−２内を矢印ｃ方向に流れる冷却媒体により冷却される。この時、ＥＧＲガス配管１２を流れるＥＧＲガスは、当該ガス流れに対し交差するごとく配設したフィン付きチューブ１３−１、１３−２によってガス流れが乱流化するのみならず、スパイラル状のフィン１３−１ａおよびディスク状のフィン１３−２ａの攪拌作用も加わって熱伝達がより速やかに行われるとともに、フィンの伝熱面積増大効果により高い熱交換性能が得られる。   In the case of the EGR gas cooling device 11 having the configuration shown in FIGS. 4 and 5, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 12 is supplied to one cooling jacket 14 as in the devices shown in FIGS. 1 and 2. -1 is cooled by the cooling medium flowing in the direction of the arrow c in the finned tubes 13-1 and 13-2. At this time, the EGR gas flowing through the EGR gas pipe 12 is not only turbulent in gas flow by the finned tubes 13-1 and 13-2 disposed so as to cross the gas flow, but also spiral fins. 13-1a and the stirring action of the disk-shaped fins 13-2a are added to perform heat transfer more quickly, and high heat exchange performance is obtained due to the effect of increasing the heat transfer area of the fins.

図６、図７に示すＥＧＲガス冷却装置２１は、冷却配管群の固着配列された熱交換領域のＥＧＲガス配管２２内に、当該ＥＧＲガス配管内のガス流に平行で前記冷却配管に直角なプレートフィン２５を設けた以外は、前記図１、図２に示すＥＧＲガス冷却装置１と同じ構成である。即ち、断面矩形に拡径したＥＧＲガス配管２２に、該配管内を流れるＥＧＲガスのガス流れ方向（矢印ｇ）に対して直角に交差する多数の冷却配管２３を、各配管の両管端が外部に開口するごとく当該ＥＧＲガス配管の外周壁を貫通して所定の間隔に固着配列し、この多数の冷却配管２３が配列されたＥＧＲガス配管２２内に、当該ガス配管内を流れるガス流（矢印ｇ）に平行で冷却配管２３に直角なプレートフィン２５を、ここでは５枚定間隔に配設し、前記冷却配管の管軸方向両側のＥＧＲガス配管外面に冷却ジャケット２４−１、２４−２を固着して構成したものである。   The EGR gas cooling device 21 shown in FIG. 6 and FIG. 7 is parallel to the gas flow in the EGR gas pipe and perpendicular to the cooling pipe in the EGR gas pipe 22 in the heat exchange region where the cooling pipe group is fixedly arranged. Except for the provision of the plate fins 25, the configuration is the same as that of the EGR gas cooling apparatus 1 shown in FIGS. That is, a large number of cooling pipes 23 intersecting at right angles to the gas flow direction (arrow g) of the EGR gas flowing in the EGR gas pipe 22 having an enlarged diameter in cross section are connected to both ends of each pipe. A gas flow (in the EGR gas pipe 22 in which a large number of cooling pipes 23 are arranged and fixed in a predetermined interval through the outer peripheral wall of the EGR gas pipe as it opens to the outside (flowing through the gas pipe ( Here, five plate fins 25 parallel to the arrow g) and perpendicular to the cooling pipe 23 are arranged at regular intervals, and cooling jackets 24-1 and 24- are provided on the outer surface of the EGR gas pipe on both sides in the pipe axis direction of the cooling pipe. 2 is fixed.

上記図６、図７に示す構成のＥＧＲガス冷却装置２１の場合も、図１、図２に示す装置と同様、ＥＧＲガス配管２２内を矢印ｇ方向に流れるＥＧＲガスは、一方の冷却ジャケット２４−１より各冷却配管３内を矢印ｃ方向に流れる冷却媒体により冷却されるが、この時、ＥＧＲガス配管２２を流れるＥＧＲガスは、当該ガス流れに対し交差するごとく配設した多数の冷却配管３によってガス流れが乱流化するのみならず、当該ガス配管内を流れるガス流（矢印ｇ）に平行で冷却配管２３に直角なプレートフィン２５により伝熱面積が増大することも加わるため、この場合も熱伝達がより速やかに行われ、より高い熱交換性能が得られる。   In the case of the EGR gas cooling device 21 having the configuration shown in FIGS. 6 and 7 as well, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 22 is supplied to one cooling jacket 24 as in the devices shown in FIGS. -1 is cooled by the cooling medium flowing in each cooling pipe 3 in the direction of the arrow c. At this time, the EGR gas flowing through the EGR gas pipe 22 is arranged so as to intersect with the gas flow. 3 not only makes the gas flow turbulent, but also increases the heat transfer area by the plate fin 25 parallel to the gas flow (arrow g) flowing through the gas pipe and perpendicular to the cooling pipe 23. Also in this case, heat transfer is performed more quickly, and higher heat exchange performance can be obtained.

また、上記図６、図７に示すプレートフィン２５内蔵のＥＧＲガス冷却装置２１における冷却配管２３とプレートフィン２５の接合構造としては、図８に示すように、プレートフィン２５の冷却配管２３が挿入される貫孔に、該プレートフィンと冷却配管との接触面積を増加させるためにバーリング壁２５−１を設けてもよい。   Moreover, as shown in FIG. 8, the cooling pipe 23 of the plate fin 25 is inserted as the joining structure of the cooling pipe 23 and the plate fin 25 in the EGR gas cooling device 21 with the plate fin 25 built-in shown in FIGS. In order to increase the contact area between the plate fin and the cooling pipe, a burring wall 25-1 may be provided in the through-hole.

さらに、ＥＧＲガス配管２２を流れるＥＧＲガスの乱流化や攪拌作用を増大させるために、例えば図９に示すように、プレートフィン２５に多数の貫孔２５−２（図ａ）、ルーバー２５−３（図ｂ）、２５−４（図ｃ）、ピンフィン２５−５（図ｄ）、プレス成形による凹凸２５−６（図ｅ）を設けてもよい。なお、図ｅに示す凹凸２５−６としては、円形または条のいずれでもよい。   Further, in order to increase the turbulent flow and the stirring action of the EGR gas flowing through the EGR gas pipe 22, for example, as shown in FIG. 9, a large number of through holes 25-2 (FIG. A) and louvers 25- 3 (FIG. B), 25-4 (FIG. C), pin fins 25-5 (FIG. D), and unevenness 25-6 (FIG. E) by press molding may be provided. Note that the unevenness 25-6 shown in FIG.

図１０、図１１および図１２に示すＥＧＲガス冷却装置３１は、断面矩形に拡径したＥＧＲガス配管３２に、該配管内を流れるＥＧＲガスのガス流れ方向（矢印ｇ）に対して直角に交差する多数の偏平チューブ３３を、前記のものと同様、各偏平チューブ３３の両管端が外部に開口するごとく当該ＥＧＲガス配管の外周壁を貫通して所定の間隔に固着配列し、そのＥＧＲガス配管３２の外側全周に、内部がセパレータ３４−１を介して上下２つに区分された冷却ジャケット３４を固着して構成した、いわゆる二重管タイプのものである。   The EGR gas cooling device 31 shown in FIG. 10, FIG. 11 and FIG. 12 intersects an EGR gas pipe 32 whose diameter is expanded to a rectangular cross section at right angles to the gas flow direction (arrow g) of the EGR gas flowing in the pipe. In the same manner as described above, a number of flat tubes 33 are fixedly arranged at predetermined intervals through the outer peripheral wall of the EGR gas pipe so that both ends of the flat tubes 33 open to the outside. This is a so-called double pipe type in which a cooling jacket 34 whose inside is divided into two upper and lower parts via a separator 34-1 is fixed to the entire outer periphery of the pipe 32.

上記図１０、図１１および図１２に示す構成の二重管タイプのＥＧＲガス冷却装置３１の場合は、ＥＧＲガス配管３２内を矢印ｇ方向に流れるＥＧＲガスは、このＥＧＲガス配管３２を囲むように設けた冷却ジャケット３４より各偏平チューブ３３内を矢印ｃ方向に流れる冷却媒体により冷却される。この二重管タイプのＥＧＲガス冷却装置３１の場合も、ＥＧＲガス配管３２内を流れるＥＧＲガスは、当該ガス流れに対し交差するごとく配設した偏平チューブ３３によってガス流れが乱流化するため、多数の偏平チューブ３３内をＥＧＲガス流れと直交する方向（矢印ｃ方向）に流れる冷却媒体との熱交換が速やかに行われる。
なお、本実施例装置では、ＥＧＲガス配管３２の入側と出側とで偏平チューブ３３の配置を変えているが、偏平チューブ３３の配置についてはこの配置に限定するものではなく、ＥＧＲガス配管３２の全体を入側または出側のそれぞれの偏平チューブ３３の配置で構成してもよいことはいうまでもない。 In the case of the EGR gas cooling device 31 of the double pipe type configured as shown in FIGS. 10, 11, and 12, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 32 surrounds the EGR gas pipe 32. It cools with the cooling medium which flows in the inside of each flat tube 33 from the cooling jacket 34 provided in the arrow c direction. Also in the case of this EGR gas cooling device 31 of the double pipe type, the EGR gas flowing in the EGR gas pipe 32 is turbulent in the gas flow by the flat tube 33 arranged so as to intersect the gas flow. Heat exchange with the cooling medium flowing in the direction (arrow c direction) orthogonal to the EGR gas flow in the many flat tubes 33 is performed quickly.
In this embodiment, the arrangement of the flat tubes 33 is changed between the entry side and the exit side of the EGR gas pipe 32. However, the arrangement of the flat tubes 33 is not limited to this arrangement, and the EGR gas pipe is arranged. Needless to say, the entire 32 may be configured by the arrangement of the flat tubes 33 on the entry side or the exit side.

図１３、図１４に示すＥＧＲガス冷却装置４１は、断面矩形に拡径したＥＧＲガス配管４２に、該配管内を流れるＥＧＲガスのガス流れ方向（矢印ｇ）に対して直角に交差する多数の偏平チューブ４３を、各偏平チューブ４３の両管端が外部に開口するごとく当該ＥＧＲガス配管の側壁を水平方向に貫通して相互に平行にかつ間隔をおいて多段となるよう並設し、さらに各偏平チューブ４３の間に図１５に拡大して示す２種類の波板４５ａ、４５ｂをそれぞれ数段ずつ分けてＥＧＲガス配管４２の長手方向に介在させて流路４６ａ、４６ｂを形成し、ＥＧＲガス配管４２の外側全周に、内部がセパレータ４４−１を介して左右２つに区分された冷却ジャケット４４を固着して構成したもので、型式的には前記と同様二重管タイプのものである。   The EGR gas cooling device 41 shown in FIG. 13 and FIG. 14 has a number of EGR gas pipes 42 whose diameters are expanded to a rectangular cross section, and intersect with the gas flow direction (arrow g) of EGR gas flowing through the pipes at right angles. The flat tubes 43 are juxtaposed in parallel so as to be multistage in parallel with each other through the side walls of the EGR gas pipe as the both ends of the flat tubes 43 open to the outside. Between the flat tubes 43, two types of corrugated plates 45a and 45b shown in an enlarged manner in FIG. 15 are divided into several stages, respectively, and interposed in the longitudinal direction of the EGR gas pipe 42 to form flow paths 46a and 46b. A gas jacket 42 is formed by fixing a cooling jacket 44, which is divided into two left and right sides through a separator 44-1, around the entire outer periphery of the gas pipe 42. Is

なお、前記２種類の波板４５ａ、４５ｂのうち、一方の波板４５ａは、図１５（ａ）に示すように頂部４５ａ−１が丸みを帯びている。他方の波板４５ｂは、図１５（ｂ）に示すように頂部４５ｂ−１が平坦となっており、該頂部間の平坦面を凹凸状の障壁４５ｂ−２とすることにより、ＥＧＲガス配管４２内を流動するガスの流れに乱流または渦流を生ぜしめ、ＥＧＲガスの熱交換効率をよりいっそう向上できるようにしたものである。又、この図１３、図１４に示すＥＧＲガス冷却装置４１の場合も、ここではＥＧＲガス配管４２の上部側に波板４５ａを、下部側に波板４５ｂを配置した例を示したが、これとは逆に上部側に波板４５ｂを、下部側に波板４５ａを配置してもよく、あるいはＥＧＲガス配管４２の全体をどちらか一方の波板で構成してもよいことはいうまでもない。   Of the two types of corrugated plates 45a and 45b, one corrugated plate 45a has a rounded top 45a-1 as shown in FIG. The other corrugated plate 45b has a flat top portion 45b-1 as shown in FIG. 15 (b), and the flat surface between the top portions is formed as an uneven barrier 45b-2. A turbulent flow or a vortex flow is generated in the flow of the gas flowing inside, so that the heat exchange efficiency of the EGR gas can be further improved. Also, in the case of the EGR gas cooling device 41 shown in FIGS. 13 and 14, here, an example is shown in which the corrugated plate 45a is disposed on the upper side of the EGR gas pipe 42 and the corrugated plate 45b is disposed on the lower side. On the contrary, the corrugated plate 45b may be disposed on the upper side and the corrugated plate 45a may be disposed on the lower side, or the entire EGR gas pipe 42 may be composed of either one of the corrugated plates. Absent.

上記図１３、図１４に示す構成の二重管タイプのＥＧＲガス冷却装置４１の場合は、ＥＧＲガス配管４２内を矢印ｇ方向に流れるＥＧＲガスは、このＥＧＲガス配管４２を囲むように設けた冷却ジャケット４４より各偏平チューブ４３内を矢印ｃ方向に流れる冷却媒体により冷却される。この二重管タイプのＥＧＲガス冷却装置４１の場合は、ＥＧＲガス配管４２内を流れるＥＧＲガスは、２種類の波板４５ａ、４５ｂにより形成された流路４６ａ、４６ｂを流れる間に当該ガスの流れに乱流又は渦流が生じるため、多数の偏平チューブ４３内をＥＧＲガス流れと直交する方向（矢印ｃ方向）に流れる冷却媒体との熱交換が速やかに行われ、より高い熱交換効率が得られる。   In the case of the EGR gas cooling device 41 of the double pipe type configured as shown in FIGS. 13 and 14, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 42 is provided so as to surround the EGR gas pipe 42. The cooling jacket 44 cools each flat tube 43 by a cooling medium flowing in the direction of arrow c. In the case of this double pipe type EGR gas cooling device 41, the EGR gas flowing in the EGR gas pipe 42 flows while flowing through the flow paths 46a and 46b formed by the two types of corrugated plates 45a and 45b. Since turbulent flow or vortex flow is generated in the flow, heat exchange with the cooling medium flowing in the direction (arrow c direction) orthogonal to the EGR gas flow in a number of flat tubes 43 is performed quickly, and higher heat exchange efficiency is obtained. It is done.

なお、上記したＥＧＲガス冷却装置における前記冷却配管３、２３、フィン付きチューブ１３−１、１３−２、偏平チューブ３３、４３の配列、本数、肉厚等は、特に限定するものではなく、ＥＧＲガス配管２、１２、２２、３２、４２の大きさ、冷却装置の規模等に応じて適宜決められる。又、冷却配管は、ここでは断面形状が真円の円形パイプや偏平パイプを示したが、これに限定するものではなく、楕円の円形パイプ、矩形や多角形断面のパイプ等も使用できることはいうまでもない。又、各部の密着、固定手段としては、溶接、ろう付け等を用いることができる。
The arrangement, number, thickness, etc. of the cooling pipes 3, 23, finned tubes 13-1, 13-2, and flat tubes 33, 43 in the EGR gas cooling device described above are not particularly limited. It is determined appropriately according to the size of the gas pipes 2, 12, 22, 32, 42, the scale of the cooling device, and the like. In addition, the cooling pipe is shown here as a circular pipe or a flat pipe with a perfect cross-sectional shape, but the invention is not limited to this, and an elliptical circular pipe, a pipe with a rectangular or polygonal cross section, etc. can also be used. Not too long. Moreover, welding, brazing, etc. can be used as the close contact and fixing means of each part.

次に、図１６〜図１９に示すＥＧＲガス冷却装置１０１は、断面矩形に拡径したＥＧＲガス配管１０２内に、該配管内を流れるＥＧＲガスのガス流れ方向（矢印ｇ）に対して直角に交差する多数のチューブ状冷却媒体流路１０３−２を有する複数のプレートフィン１０３−１で構成されたコア１０３を、各プレートフィン１０３−１がＥＧＲガス配管内のガス流に平行になるように収納設置し、前記チューブ状冷却媒体流路１０３−２の両端側のＥＧＲガス配管外面に、冷却媒体の流入口Ｐ１、流出口Ｐ２が設けられた冷却ジャケット１０４−１、１０４−２を固着して構成したものである。   Next, the EGR gas cooling apparatus 101 shown in FIGS. 16 to 19 is perpendicular to the gas flow direction (arrow g) of the EGR gas flowing in the EGR gas pipe 102 whose diameter is expanded to a rectangular cross section. The core 103 composed of a plurality of plate fins 103-1 having a large number of intersecting tubular coolant flow paths 103-2 is arranged so that each plate fin 103-1 is parallel to the gas flow in the EGR gas pipe. The cooling jackets 104-1 and 104-2 provided with the cooling medium inlet P1 and the outlet P2 are fixed to the outer surfaces of the EGR gas pipes at both ends of the tubular cooling medium flow path 103-2. It is configured.

このＥＧＲガス冷却装置１０１におけるコア１０３は、図１７に示すように１枚の板にバーリング加工を施して同一高さの断面真円形の突出筒体１０３−３を縦方向および横方向に所定の間隔を隔てて例えば１５個形成したプレートフィン１０３−１を複数枚（ここでは５枚）作製し、この５枚のプレートフィン１０３−１を各突出筒体１０３−３が合致するように相互に重ねて当該突出筒体部を他方のプレートフィン１０３−１に溶接またはろう付けにて接合して１５個のチューブ状冷却媒体流路１０３−２を形成したものである。
そして、このようにして組立てたコア１０３をＥＧＲガス配管２内に設置する場合は、該コア１０３をＥＧＲガス配管１０２の一方の外壁をあらかじめ切断除去して形成した矩形の窓孔より当該ＥＧＲガス配管１０２内に挿入し、該コアの各チューブ状冷却媒体流路１０３−２を構成する外側の突出筒体１０３−３部の開口端部を当該ＥＧＲガス配管２の外周壁にあらかじめ穿設した同一形状の円孔に嵌合させて当該部分を溶接またはろう付けにて固着し、その反対側の外側に位置するプレートフィン１０３−１の四辺を当該ＥＧＲガス配管１０２の外壁に溶接またはろう付けにて接合する。 As shown in FIG. 17, the core 103 in the EGR gas cooling device 101 is subjected to burring on a single plate to form a protruding circular body 103-3 having a perfectly circular cross section with a predetermined height and width in a predetermined direction. For example, a plurality of plate fins 103-1 (in this case, 5) formed, for example, with 15 intervals are produced, and the five plate fins 103-1 are mutually connected so that the projecting cylinders 103-3 are matched. The protruding cylindrical body portion is overlapped and joined to the other plate fin 103-1 by welding or brazing to form 15 tubular cooling medium flow paths 103-2.
When the core 103 assembled in this way is installed in the EGR gas pipe 2, the EGR gas is inserted into the EGR gas through a rectangular window hole formed by cutting and removing one outer wall of the EGR gas pipe 102 in advance. Inserted into the pipe 102, the opening end of the outer projecting cylinder 103-3 constituting each tubular cooling medium flow path 103-2 of the core was previously drilled in the outer peripheral wall of the EGR gas pipe 2 The part is fixed by welding or brazing by fitting it into a circular hole of the same shape, and the four sides of the plate fin 103-1 located outside the opposite side are welded or brazed to the outer wall of the EGR gas pipe 102 Join with.

上記図１６〜図１９に示すＥＧＲガス冷却装置において、ＥＧＲガス配管１０２内を矢印ｇ方向に流れるＥＧＲガスは、一方の冷却ジャケット１０４−１よりコア１０３の各チューブ状冷却媒体流路１０３−２内を矢印ｃ方向に流れる冷却媒体（例えば冷却水）により冷却される。この時、ＥＧＲガス配管１０２内を流れるＥＧＲガスは、当該ガス流れに対し交差するごとく配設したコア１０３の多数のチューブ状冷却媒体流路１０３−２によってガス流れが乱流化するのみならず、当該ガス配管内を流れるガス流（矢印ｇ）に平行でチューブ状冷却媒体流路１０３−２に直角なプレートフィン１０３−１により伝熱面積が増大することも加わって熱伝達がより速やかに行われ、より高い熱交換性能が得られる。   In the EGR gas cooling apparatus shown in FIGS. 16 to 19, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 102 flows from each cooling jacket 104-1 to each tubular cooling medium flow path 103-2 of the core 103. It is cooled by a cooling medium (for example, cooling water) flowing in the direction of arrow c. At this time, the EGR gas flowing in the EGR gas pipe 102 is not only turbulent but also turbulent by the numerous tubular cooling medium flow paths 103-2 of the core 103 disposed so as to intersect the gas flow. The heat transfer area is further increased by the plate fin 103-1 parallel to the gas flow (arrow g) flowing through the gas pipe and perpendicular to the tubular cooling medium flow path 103-2. And higher heat exchange performance is obtained.

図２０〜図２３に示すＥＧＲガス冷却装置１１１は、ＥＧＲガス配管１１２の外側全周に、内部がセパレータ１１４−１を介して上下２つに区分された冷却ジャケット１１４を固着して構成した、いわゆる二重管タイプのものであって、かつ偏平形のチューブ状冷却媒体流路１１３−２で構成したものである。
すなわち、このＥＧＲガス冷却装置１１１は、断面矩形に拡径したＥＧＲガス配管１１２内に、該配管内を流れるＥＧＲガスのガス流れ方向（矢印ｇ）に対して直角に交差する多数のチューブ状冷却媒体流路１１３−２を有する複数のプレートフィン１１３−１で構成されたコア１１３を、各プレートフィン１１３−１がＥＧＲガス配管内のガス流に平行になるように収納設置し、このＥＧＲガス配管１１２の外側全周に、内部がセパレータ１１４−１を介して上下２つに区分され、その一方に冷却媒体の流入口Ｐ１が、他方に流出口Ｐ２がそれぞれ設けられた冷却ジャケット１１４を固着して構成したものである。 The EGR gas cooling device 111 shown in FIG. 20 to FIG. 23 is configured by fixing a cooling jacket 114, which is divided into two upper and lower parts via a separator 114-1, around the entire outer periphery of the EGR gas pipe 112. It is what is called a double pipe type, and is comprised by the flat tubular cooling medium flow path 113-2.
In other words, this EGR gas cooling device 111 has a number of tube-shaped coolings intersecting at right angles to the gas flow direction (arrow g) of the EGR gas flowing in the EGR gas pipe 112 whose diameter is expanded to a rectangular cross section. A core 113 composed of a plurality of plate fins 113-1 having a medium flow path 113-2 is housed and installed so that each plate fin 113-1 is parallel to the gas flow in the EGR gas pipe, and this EGR gas A cooling jacket 114 is provided on the entire outer periphery of the pipe 112. The cooling jacket 114 is divided into an upper part and a lower part through a separator 114-1, and a cooling medium inlet P1 is provided on one side and an outlet P2 is provided on the other side. It is configured as follows.

このＥＧＲガス冷却装置１１１におけるコア１１３も、前記図１６〜図１９に示す冷却装置と同様、図２１に示すように１枚の板にバーリング加工を施して同一高さの断面偏平形の突出筒体１１３−３を縦方向および横方向に所定の間隔を隔てて例えば９個形成したプレートフィン１１３−１を５枚作製し、この５枚のプレートフィン１１３−１を各偏平形突出筒体１１３−３が合致するように相互に重ねて当該突出筒体部を他方のプレートフィン１１３−１に溶接またはろう付けにて接合して９個の偏平チューブ状冷却媒体流路１１３−２を形成したものである。
そして、このようにして組立てたコア１１３をＥＧＲガス配管１１２内に設置する場合も前記と同様、該コア１１３をＥＧＲガス配管１１２の一方の外壁にあらかじめ形成した矩形の窓孔より当該ＥＧＲガス配管１１２内に挿入し、該コアの各偏平チューブ状冷却媒体流路１１３−２を構成する外側の偏平形突出筒体１１３−３部の開口端部を当該ＥＧＲガス配管１１２の外周壁にあらかじめ穿設した同一形状の楕円孔に嵌合させて当該部分を溶接またはろう付けにて固着し、その反対側の外側に位置するプレートフィン１１３−１の四辺を当該ＥＧＲガス配管２の外壁に溶接またはろう付けにて接合する。 Similarly to the cooling device shown in FIGS. 16 to 19, the core 113 in the EGR gas cooling device 111 is also a protruding cylinder having a flat cross section having the same height as shown in FIG. For example, five plate fins 113-1 each having nine bodies 113-3 formed at predetermined intervals in the vertical direction and the horizontal direction are manufactured. The five plate fins 113-1 are each formed into a flat projecting cylindrical body 113. -3 are overlapped with each other so as to match, and the projecting cylindrical part is joined to the other plate fin 113-1 by welding or brazing to form nine flat tubular coolant flow paths 113-2. Is.
When the core 113 assembled in this manner is installed in the EGR gas pipe 112, the core 113 is inserted into the EGR gas pipe from a rectangular window hole formed in advance on one outer wall of the EGR gas pipe 112, as described above. 112 is inserted into the outer peripheral wall of the EGR gas pipe 112 in advance. This portion is fitted into an elliptical hole having the same shape and fixed by welding or brazing, and the four sides of the plate fin 113-1 positioned outside the opposite side are welded to the outer wall of the EGR gas pipe 2 or Join by brazing.

上記図２０〜図２３に示す構成の二重管タイプのＥＧＲガス冷却装置１１１の場合は、ＥＧＲガス配管１１２内を矢印ｇ方向に流れるＥＧＲガスは、このＥＧＲガス配管１１２を囲むように設けた冷却ジャケット１１４よりコア１１３の各偏平チューブ状冷却媒体流路１１３−２内を矢印ｃ方向に流れる冷却媒体（例えば冷却水）により冷却される。この二重管タイプのＥＧＲガス冷却装置の場合も前記と同様、ＥＧＲガス配管１１２内を流れるＥＧＲガスは、当該ガス流れに対し交差するごとく配設したコア１１３の偏平チューブ状冷却媒体流路１１３−２によってガス流れが乱流化するのみならず、当該ガス配管内を流れるガス流（矢印ｇ）に平行で偏平チューブ状冷却媒体流路１１３−２に直角なプレートフィン１１３−１により伝熱面積が増大することも加わって熱伝達がより速やかに行われ、より高い熱交換性能が得られる。   In the case of the double-tube type EGR gas cooling device 111 configured as shown in FIGS. 20 to 23, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 112 is provided so as to surround the EGR gas pipe 112. The cooling jacket 114 is cooled by a cooling medium (for example, cooling water) flowing in the direction of the arrow c in each flat tubular cooling medium flow path 113-2 of the core 113. Also in the case of this double pipe type EGR gas cooling device, the EGR gas flowing in the EGR gas pipe 112 is the flat tubular cooling medium flow path 113 of the core 113 disposed so as to intersect the gas flow, as described above. -2 not only makes the gas flow turbulent, but also transfers heat by plate fins 113-1 parallel to the gas flow (arrow g) flowing in the gas pipe and perpendicular to the flat tubular coolant flow path 113-2. In addition to the increase in area, heat transfer is performed more quickly, and higher heat exchange performance is obtained.

なお、上記した図１６〜図２３に示すＥＧＲガス冷却装置における前記冷却媒体流路を構成するプレートフィンの突出筒体１０３−３、１１３−３の個数、肉厚等は、特に限定するものではなく、ＥＧＲガス配管１０２、１１２の大きさ、冷却装置の規模等に応じて適宜決められる。また、プレートフィンには、ガスの乱流化、拡散、混合等による伝熱性能向上を目的として、前記図９に示す種々の加工（波付き加工、貫孔、ルーバー、凹凸等）を施してもよい。さらに、冷却媒体流路は、ここでは断面形状が真円や楕円形を示したが、これに限定するものではなく、矩形や多角形断面でも同様の作用効果が得られることはいうまでもない。さらにまた、本実施例装置はそれぞれ、ＥＧＲガス配管１０２、１１２の全体を同一の冷却媒体流路で構成しているが、ＥＧＲガス配管の全体を入側または出側とで断面形状や大きさの異なる冷却媒体流路で構成してもよいことはいうまでもない。   It should be noted that the number, thickness, etc. of the plate fin projecting cylinders 103-3, 113-3 constituting the cooling medium flow path in the EGR gas cooling apparatus shown in FIGS. 16 to 23 are not particularly limited. Rather, it is appropriately determined according to the size of the EGR gas pipes 102 and 112, the scale of the cooling device, and the like. In addition, the plate fins are subjected to various processes shown in FIG. 9 (corrugated processes, through holes, louvers, irregularities, etc.) for the purpose of improving heat transfer performance by gas turbulence, diffusion, mixing, etc. Also good. Further, the cooling medium flow path has a perfect circle or ellipse here, but the present invention is not limited to this, and it goes without saying that the same effect can be obtained even with a rectangular or polygonal cross section. . Furthermore, in the apparatus of this embodiment, the entire EGR gas pipes 102 and 112 are configured by the same cooling medium flow path, but the entire EGR gas pipe has a cross-sectional shape and size on the inlet side or the outlet side. Needless to say, the cooling medium flow paths may be different.

図２４に示すＥＧＲガス冷却装置２０１は、断面がほぼ矩形に形成された胴管２０６の両サイドに、主としてエンジン冷却水が用いられる冷却媒体ｃの流入口Ｐ１を備えた冷却ジャケット２０２−１と、流出口Ｐ２を備えた冷却ジャケット２０２−２を正対して配置し、該２つの冷却ジャケット２０２−１および２０２−２間にあって、前記胴管２０６を貫通して、ガスの流れ方向ｇに対して直角に交差する複数の断面が円形、長円形、楕円形、矩形等の伝熱管２０３が配設され、冷却水ｃの流路を形成している。さらに、本実施例によるガス冷却装置２０１は、該胴管６の前記２つの冷却ジャケット２０２−１および２０２−２によって、覆われている部分を除いた壁面に、ガスの流れる方向ｇに平行して、複数のフレキ成形を施すことによって図２５に示すような凹部を形成する。図２５中、２０５はフレキ成形部である。   The EGR gas cooling device 201 shown in FIG. 24 includes a cooling jacket 202-1 having an inlet P1 of a cooling medium c mainly using engine cooling water on both sides of a trunk pipe 206 having a substantially rectangular cross section. , A cooling jacket 202-2 having an outlet P2 is arranged in a face-to-face relationship, between the two cooling jackets 202-1 and 202-2, passing through the body tube 206, and with respect to the gas flow direction g. A plurality of cross-sections that intersect at right angles are circular, oval, elliptical, rectangular or the like, and heat transfer tubes 203 are disposed to form a flow path for cooling water c. Furthermore, the gas cooling apparatus 201 according to the present embodiment is parallel to the gas flow direction g on the wall surface except for the portion covered by the two cooling jackets 202-1 and 202-2 of the trunk pipe 6. Thus, a plurality of flexible moldings are performed to form a recess as shown in FIG. In FIG. 25, 205 is a flexible molding part.

前記フレキ成形によって形成された微妙な凹部によって該装置内を通過するガスは、当該壁面において乱流を生じると共に外表面積が増加して相当程度の放熱作用が認められるが、本実施例においては、さらに図２４に示すように前記２つの冷却ジャケット２０２−１および２０２−２によって覆われている部分を除く、外側の壁面にガスの流れ方向ｇに対して平行に、複数のプレートフィン２０４−１を接合すると共に、前記伝熱管２０３の外表面にも同様ガスの流れ方向ｇに対して平行に複数のプレートフィン２０４−２を接合する。加えて本実施例においては、図２４に示すように前記壁面側に配設した伝熱管２０３の外表面に接合したプレートフィン２０４−３の他端を、前記フレキ成形によって形成された凹部に挿入し、一体として挟持させることによって、その伝熱効果を増大させると共に、前記複数の伝熱管を介して２つの冷却ジャケット間を流れる冷却水の高い伝熱係数が相乗的に作用して、優れた冷却効率が得られることが可能となる。   The gas passing through the device by the delicate recess formed by the flexible molding causes turbulent flow on the wall surface and increases the outer surface area, and a considerable heat dissipation effect is recognized, but in this example, Further, as shown in FIG. 24, a plurality of plate fins 204-1 are arranged in parallel to the gas flow direction g on the outer wall surface except for the portions covered by the two cooling jackets 202-1 and 202-2. And a plurality of plate fins 204-2 are also joined to the outer surface of the heat transfer tube 203 in parallel to the gas flow direction g. In addition, in this embodiment, as shown in FIG. 24, the other end of the plate fin 204-3 joined to the outer surface of the heat transfer tube 203 disposed on the wall surface side is inserted into the recess formed by the flexible molding. And by sandwiching them as a unit, the heat transfer effect is increased, and the high heat transfer coefficient of the cooling water flowing between the two cooling jackets through the plurality of heat transfer tubes acts synergistically and is excellent. Cooling efficiency can be obtained.

図２６に示す大小２つのフレキ成形部は、本実施例の応用例であり深い凹部２０５−１と、浅い凹部２０５−２を交互に形成し、深い奥部凹部２０５−１に伝熱管３の外表面に接合したプレートフィン２０４−４の他端を挿入し、挟持させることによって一体としている。上記の構成によりフレキ成形部と、プレートフィンとによってもたらされる伝熱性能が更に向上する。   The two large and small flexible molded portions shown in FIG. 26 are an application example of the present embodiment, in which deep concave portions 205-1 and shallow concave portions 205-2 are alternately formed, and the heat transfer tube 3 is formed in the deep inner concave portion 205-1. The other end of the plate fin 204-4 joined to the outer surface is inserted and held together. With the above configuration, the heat transfer performance provided by the flexible molded part and the plate fins is further improved.

図２７に示すＥＧＲガス冷却装置２０１−１は、冷却媒体の流入口Ｐ１−１を備えた冷却ジャケット２０２−３と、流出口Ｐ２−２を備えた冷却ジャケット２０２−４が上下に正対して配置され、その中間を貫通してガスの流れ方向ｇに対して直角に交差する複数の伝熱管２０３−１が配設されている。このＥＧＲガス冷却装置２０１−１は、前記正対する２つの冷却ジャケット２０２−３および２０２−４に覆われている部分を除く側壁部に、ガスの流れ方向に対して平行に、複数のフレキ成形部２０５−１が形成され、伝熱管２０３−１の外表面にはガスの流れ方向ｇに対して平行に、プレートフィン２０４−６が接合され、前記フレキ成形部２０５−１に隣接した伝熱管２０３−１に接合されたプレートフィン２０４−６の他端２０４−５は、該フレキ成形部２０５−１の凹部に挿入して挟持されている。
このように構成されたＥＧＲガス冷却装置２０１−１は、壁面に形成されたフレキ成形部２０５−１による複数の凹部と、伝熱管２０３−１の外表面に接合された複数のプレートフィン２０４−６と、該プレートフィン２０４−６の他端２０４−５を前記フレキ成形部２０５−１の凹部に挿入して挟持させること等によって、該装置内に流入したガスの熱は効果的に熱交換され、優れた冷却効率が得られることが可能となる。 The EGR gas cooling device 201-1 shown in FIG. 27 has a cooling jacket 202-3 having a cooling medium inlet P1-1 and a cooling jacket 202-4 having an outlet P2-2 facing each other vertically. A plurality of heat transfer tubes 203-1 that are arranged and pass through the middle thereof and intersect at right angles to the gas flow direction g are arranged. This EGR gas cooling device 201-1 has a plurality of flexible moldings in parallel to the gas flow direction on the side wall portion excluding the portion covered with the two facing cooling jackets 202-3 and 202-4. Part 205-1 is formed, a plate fin 204-6 is joined to the outer surface of the heat transfer tube 203-1 in parallel to the gas flow direction g, and the heat transfer tube adjacent to the flexible molding part 205-1 The other end 204-5 of the plate fin 204-6 joined to the 203-1 is inserted and held in the concave portion of the flexible molding part 205-1.
The EGR gas cooling device 201-1 configured as described above includes a plurality of concave portions formed by the flexible molding portion 205-1 formed on the wall surface and a plurality of plate fins 204- joined to the outer surface of the heat transfer tube 203-1. 6 and the other end 204-5 of the plate fin 204-6 are inserted into the concave portion of the flexible molding portion 205-1 so that the heat of the gas flowing into the apparatus is effectively exchanged. Thus, excellent cooling efficiency can be obtained.

図２８、図２９に示すＥＧＲガス冷却装置は、冷却ジャケット２０２−５および２０２−６、２０２−７および２０２−８によって覆われていない壁面に、図２８の方はガスの流れ方向ｇに対して直角に交差する複数のフレキ成形部２０５−２を、図２９の方はガスの流れ方向ｇと平行する複数のフレキ成形部２０５−３をそれぞれ形成したものである。
上記ＥＧＲガス冷却装置２０１−２、２０１−３はシンプルな構造であるにもかかわらず、前記フレキ成形部２０５−２、２０５−３によって壁面を通過するガスに乱流を生ぜじめたり、フレキ成形による凹部によって外壁部との接触面積が広がって放熱作用を促進させ、それに起因して効果的な冷却効率を得られることが可能となる。 The EGR gas cooling apparatus shown in FIGS. 28 and 29 has a wall surface not covered by the cooling jackets 202-5 and 202-6, 202-7 and 202-8, and FIG. 28 shows the gas flow direction g. In FIG. 29, a plurality of flexible molding portions 205-2 that are parallel to the gas flow direction g are formed.
Although the EGR gas cooling devices 201-2 and 201-3 have a simple structure, the flexible molding portions 205-2 and 205-3 cause turbulent flow in the gas passing through the wall surface, The contact area with the outer wall portion is widened by the concave portion formed by molding, and the heat dissipation action is promoted, so that effective cooling efficiency can be obtained.

又、図３０に示すＥＧＲガス冷却装置は、相対する冷却ジャケットによって覆われていない壁面に、任意に放熱用プレートフィンを接合することによって、本発明の効果をさらに向上させたもので、相対する冷却ジャケット２０２−９、２０２−１０によって覆われていない壁面に、ガスの流れ方向ｇに対して直角に交差する放熱用プレートフィン２０４−７を複数接合したり、あるいは図３１に示すように、相対する冷却ジャケット２０２−１１、２０２−１２によって覆われていない壁面に、ガスの流れ方向ｇと平行する複数の放熱用プレートフィン２０４−８を複数接合する。
上記ＥＧＲガス冷却装置２０１−４、２０１−５は、前記放熱用プレートフィン２０４−７、２０４−８による放熱作用によって、冷却ジャケットに直接接することのない壁面付近を通過するガスの熱が、効率的に熱交換され、優れた冷却効率が得られることが可能となる。
なお、本発明においては、前記放熱用プレートフィン２０４−７、２０４−８の方向が交差された状態であることを妨げるものではない。又、前記放熱用プレートフィン２０４−７、２０４−８は、ガスの流れ方向ｇに対して傾斜して設けてもよい。 In addition, the EGR gas cooling device shown in FIG. 30 further improves the effect of the present invention by arbitrarily joining a heat radiating plate fin to a wall surface not covered by a facing cooling jacket. A plurality of heat radiating plate fins 204-7 intersecting at right angles to the gas flow direction g are joined to the wall surface not covered with the cooling jackets 202-9 and 202-10, or as shown in FIG. A plurality of heat dissipating plate fins 204-8 parallel to the gas flow direction g are joined to the wall surfaces not covered by the opposing cooling jackets 202-11 and 202-12.
The EGR gas cooling devices 201-4 and 201-5 are configured so that the heat of the gas passing through the vicinity of the wall surface that is not in direct contact with the cooling jacket is improved due to the heat dissipation action of the heat dissipation plate fins 204-7 and 204-8. Thus, it is possible to obtain an excellent cooling efficiency.
In the present invention, it does not prevent the direction of the heat dissipating plate fins 204-7 and 204-8 from intersecting. The heat dissipating plate fins 204-7 and 204-8 may be provided inclined with respect to the gas flow direction g.

又、上記ＥＧＲガス冷却装置に用いるフィンとしては、例えば図３２に示すうねりを有した矩形の波板２０４ａ等もある。さらに、上記ＥＧＲガス冷却装置においても、前記図９〜図１２に示す各種フィン、すなわち多数の貫孔が設けられたプレートフィン、ルーバーが設けられたプレートフィン、ピンフィンが設けられたプレートフィン、連続もしくは断続した凹凸が設けられたプレートフィンや前記図１５（ａ）（ｂ）に示す波形フィンを用いることができる。   Moreover, as a fin used for the EGR gas cooling device, there is, for example, a rectangular corrugated plate 204a having a swell as shown in FIG. Furthermore, also in the EGR gas cooling device, various fins shown in FIGS. 9 to 12, that is, plate fins provided with a large number of through holes, plate fins provided with louvers, plate fins provided with pin fins, continuous fins, Or the plate fin provided with the intermittent unevenness | corrugation and the corrugated fin shown to the said Fig.15 (a) (b) can be used.

上記図２４〜図３２に示すＥＧＲガス冷却装置は、相対する２つの冷却ジャケットの間にあって、ガスの流れ方向に直角に交差して貫く複数の伝熱管を配置せしめると共に、前記２つの冷却ジャケットによって覆われている部分を除く壁面に、ガスの流れ方向に対して平行に、もしくは交差して複数のフレキ成形部を施すか、或いは各種プレートフィンを選択的に接合することにより、フレキ成形や各種プレートフィンによってもたらされる伝熱面積の拡大と、形成された凹部（外表面は凸部）によってもたらされるガス流の乱流化に加え、エンジン冷却水によって冷やされる前記冷却ジャケットや伝熱管の外表面の伝熱係数が、ＥＧＲガスに対して約１０倍であること等が相乗的に作用して、その熱交換が速やかにかつほぼ完璧に実施され、優れた冷却効率を得られる。又、フレキ成形部には、熱応力緩和の作用効果もあり、ＥＧＲガス冷却装置の耐久性を向上させることもできる。
なお、上記ＥＧＲガス冷却装置２０１、２０１−１を説明するための図２４及び図２７に示すように、伝熱管の外表面に接合されたプレートフィン２０４−３、２０４−４、２０４−５は、その他端を、胴管２０６の前記平滑な壁面にフレキ成形によって形成された凹部に挿入させ、密着して挟持されると共に、各伝熱管２０３、２０３−１どうしも同様プレートフィン２０４−２、２０４−６によってそれぞれ接合された状態となるため、相互に支持された状態となり、結果として伝熱管２０３、２０３−１相互と胴管２０６とを補強する支持体を形成して、装置のコンパクト化にも寄与する。 The EGR gas cooling apparatus shown in FIGS. 24 to 32 is provided with a plurality of heat transfer tubes arranged between two opposing cooling jackets and penetrating at right angles to the gas flow direction, and by the two cooling jackets. By applying multiple flex molded parts to the wall surface excluding the covered part in parallel or intersecting with the gas flow direction, or by selectively joining various plate fins, In addition to the expansion of the heat transfer area provided by the plate fins and the turbulent flow of the gas flow provided by the formed recess (outer surface is a protrusion), the outer surface of the cooling jacket or heat transfer tube cooled by the engine cooling water The heat transfer coefficient is approximately 10 times that of EGR gas, and so on, synergistically acting so that the heat exchange is carried out quickly and almost perfectly. It obtained an excellent cooling efficiency. Further, the flexible molded part also has an effect of relaxing thermal stress, and the durability of the EGR gas cooling device can be improved.
In addition, as shown in FIG.24 and FIG.27 for demonstrating the said EGR gas cooling device 201,201-1, the plate fins 204-3,204-4,204-5 joined to the outer surface of a heat exchanger tube are as follows. The other end is inserted into a concave portion formed by flexible molding on the smooth wall surface of the trunk tube 206 and is tightly sandwiched, and the heat transfer tubes 203 and 203-1 are similarly plate fins 204-2, 204-6 is joined to each other, so that they are supported by each other. As a result, a support body that reinforces the heat transfer tubes 203 and 203-1 and the trunk tube 206 is formed, thereby reducing the size of the apparatus. Also contributes.

図３３に示すＥＧＲガス冷却装置３０１は、断面がほぼ矩形に拡管されたＥＧＲガス配管３０２の上下に、主としてエンジン冷却水が用いられる冷却媒体の流入口Ｐ１と、流出口Ｐ２とを備えた冷却ジャケット３０４−１、３０４−２を配置し、該冷却ジャケット３０４−１、３０４−２間にあって前記ＥＧＲガス配管３０２を貫通して、ガスの流れ方向に対して直角に交差する複数の偏平の伝熱管３０３が配設され、上記冷却水の流路を形成している。さらにこのＥＧＲガス冷却装置３０１は、前記偏平伝熱管３０３の偏平した外表面間およびに該偏平伝熱管３０３と前記ガス配管３０２との間に、全長にわたりもしくは長さ方向に小割した多数のチャンネル形状のフィン３０５を、ガスの流れ方向に対して略平行に固定することによって、該偏平伝熱管３同士もしくは偏平伝熱管３０３とガス配管３０２の間にあって、ガス流路を形成せしめることを基本的な構造としている。   The EGR gas cooling device 301 shown in FIG. 33 includes a cooling medium inlet P1 and an outlet P2 for cooling medium mainly using engine cooling water above and below an EGR gas pipe 302 having a substantially rectangular cross section. Jackets 304-1 and 304-2 are disposed, and a plurality of flat transmissions intersecting the EGR gas pipe 302 between the cooling jackets 304-1 and 304-2 and intersecting at right angles to the gas flow direction. A heat pipe 303 is provided to form a flow path for the cooling water. Further, the EGR gas cooling device 301 includes a large number of channels divided between the flat outer surface of the flat heat transfer tube 303 and between the flat heat transfer tube 303 and the gas pipe 302 over the entire length or in the length direction. Basically, by fixing the fin 305 having a shape substantially parallel to the gas flow direction, a gas flow path is formed between the flat heat transfer tubes 3 or between the flat heat transfer tubes 303 and the gas pipe 302. It has a simple structure.

上記チャンネル形状のフィン３０５は、断面略コの字形状でその長さが略全長にわたるものもしくは短く小割されていることが特徴的要件であり、それによって偏平伝熱管３０３同士、もしくは該偏平伝熱管３０３とガス配管３０２との間において、図３３および図３４に示すようにガスの流れ方向に対して平行して、任意の位置に、任意のピッチで多数配置され、その接合面を例えばろう付けによって固定される。前記チャンネル形状のフィン３０５は、図３４に示すようにチャンネル状に折り曲げられたフラットな両側面を、前記偏平伝熱管３０３の偏平した外周面に当接することにより、相互の平坦面同士で密着して固定されるため、広い伝熱面積を得て相互の熱伝達は理想的な状態で確保することができ、かかる構成のガス冷却装置内を通過するＥＧＲガスは速やかに熱交換され、優れた冷却効率が得られる。   The channel-shaped fins 305 are characterized by having a substantially U-shaped cross-section and having a length that extends over the entire length or is shortly divided, whereby the flat heat transfer tubes 303 or the flat heat transfer tubes are arranged. As shown in FIGS. 33 and 34, a large number of heat pipes 303 and gas pipes 302 are arranged at arbitrary positions and at arbitrary pitches in parallel with the gas flow direction. Fixed by attaching. As shown in FIG. 34, the channel-shaped fins 305 are brought into close contact with each other by bringing flat both side surfaces bent into a channel shape into contact with the flat outer peripheral surface of the flat heat transfer tube 303. Therefore, it is possible to obtain a wide heat transfer area and ensure mutual heat transfer in an ideal state, and the EGR gas passing through the gas cooling device having such a structure is quickly heat-exchanged and excellent Cooling efficiency is obtained.

又、上記チャンネル形状のフィン３０５は、ガス配管３０２と、該ガス配管３０２を貫いてガスの流れ方向に直角に交差して配設される複数の偏平伝熱管３０３との間において、ガスの流れ方向に略平行して配列・固定される範囲内で、その位置やピッチについては任意であるが、その形状についても自由に設計変更が可能である。   The channel-shaped fins 305 flow between the gas pipe 302 and a plurality of flat heat transfer pipes 303 that pass through the gas pipe 302 and intersect at right angles to the gas flow direction. The position and pitch are arbitrary as long as they are arranged and fixed substantially parallel to the direction, but the shape can be freely changed in design.

例えば図３５に示す実施例装置においては、帯状フィンの一部を偏平伝熱管３０３の幅に合わせて切り起こし、図３７に示すような一部切り起こし帯状フィン３０５−１を形成し、該帯状フィン３０５−１を偏平伝熱管３同士もしくは該偏平伝熱管３０３とガス配管３０２との間隙において、図３６に示すように相互に連携しあうように配列して固定することにより、その伝熱性能をより一層向上せしめることが確認された。   For example, in the embodiment apparatus shown in FIG. 35, a part of the belt-like fin is cut and raised in accordance with the width of the flat heat transfer tube 303 to form a partly raised belt-like fin 305-1 as shown in FIG. The fins 305-1 are arranged and fixed so as to cooperate with each other as shown in FIG. 36 in the gaps between the flat heat transfer tubes 3 or between the flat heat transfer tubes 303 and the gas pipe 302, and thereby the heat transfer performance. It has been confirmed that this can be further improved.

又、他の実施例においては所望によりチャンネル形状のフィンの一部に特殊な加工を施し、図３８（ａ）に示すように貫通孔を設けたチャンネル形状のフィン３０５−４、図３８（ｂ）に示すように断面半円状の凹凸を設けたチャンネル形状のフィン３０５−５、図３８（ｃ）に示すように断面凹凸状のヒダを全長にわたり設けたチャンネル形状のフィン３０５−６、図３８（ｄ）に示すようにリップ状の折り曲げ部を設けたチャンネル形状のフィン３０５−７を形成することも可能であり、図３９（ａ）〜（ｃ）に示すような各種のルーバーを設けたチャンネル形状のフィン３０５−８〜３０５−１０を形成し、本発明に係るＥＧＲガス冷却装置に組み込まれるチャンネル形状のフィンの一部もしくは全部として採用され、それぞれＥＧＲガスの攪拌作用により初期の成果を達成し得る。又、図３９（ａ）〜（ｃ）に示す異なる形態のルーバーは、それぞれ一例を示すものであって、その目的としてガス流路に乱流や渦流を生起せしめ、伝熱面積を拡大して効果的な熱交換を促進することによって、冷却効率の上昇を図れるものであれば自由に設計変更が可能である。なお、これらのフィンは単独で、若しくは上記各実施例で用いられた各種チャンネルフィンを含む他のフィンと、それぞれ併用して用いることが可能である。
なお、これらの各実施例において任意に採用される上記の各チャンネル形状のフィンは、前記偏平伝熱管３０３との接合部にのみフラットな折り曲げ部が残され、該フラットな折り曲げ部と偏平伝熱管３０３の平坦な面とを当接することによって、その接合を容易にすると同時に、相互の密着性が確保されてその優れた伝熱性能が維持される。 In another embodiment, a channel-shaped fin 305-4 having a through hole as shown in FIG. 38 (a) is formed on a part of the channel-shaped fin as desired, as shown in FIG. 38 (b). ), A channel-shaped fin 305-5 provided with semicircular irregularities in cross section, as shown in FIG. 38C, and a channel-shaped fin 305-6 provided with pleats in cross-sectional unevenness as shown in FIG. It is also possible to form channel-shaped fins 305-7 provided with lip-shaped bent portions as shown in FIG. 38 (d), and various louvers as shown in FIGS. 39 (a) to (c) are provided. The channel-shaped fins 305-8 to 305-10 are formed and employed as part or all of the channel-shaped fins incorporated in the EGR gas cooling device according to the present invention. It can be achieved initial results by the stirring action of the scan. In addition, the louvers of different forms shown in FIGS. 39A to 39C are examples, respectively. For that purpose, turbulence and vortex flow are generated in the gas flow path, and the heat transfer area is expanded. The design can be freely changed as long as the cooling efficiency can be increased by promoting effective heat exchange. These fins can be used alone or in combination with other fins including various channel fins used in the above embodiments.
The channel-shaped fins that are arbitrarily adopted in each of these embodiments have a flat bent portion only at the junction with the flat heat transfer tube 303, and the flat bent portion and the flat heat transfer tube. By abutting the flat surface of 303, the joining is facilitated, and at the same time, mutual adhesion is ensured and the excellent heat transfer performance is maintained.

さらに、上記各実施例において、チャンネル形状フィンの組付け手段については特に制限はなく任意であるが、その一例として平板状のフィン材料を図４０（ａ）に示すように一旦湾曲させるか、図４０（ｂ）および（ｄ）に示すように偏平伝熱管３０５同士の間隙に合わせた折り曲げ部を設け、その後該偏平伝熱管３０３同士の間隙に押し込むことによって、相互に平坦な面同士を以って強固に密着し、図４０（ｃ）および（ｅ）に示すように略コの字形状のチャンネルフィン３０５−２または３０５−３となって、それぞれの溶着部３０６を例えばろう付けによって固定される。   Further, in each of the above embodiments, the means for assembling the channel-shaped fins is not particularly limited and is arbitrary, but as an example, a flat fin material is temporarily bent as shown in FIG. As shown in 40 (b) and (d), a bent portion is provided in accordance with the gap between the flat heat transfer tubes 305, and then pushed into the gap between the flat heat transfer tubes 303, so that the flat surfaces of each other are provided. As shown in FIGS. 40 (c) and (e), channel fins 305-2 or 305-3 are formed as shown in FIGS. 40 (c) and 40 (e), and the respective welded portions 306 are fixed by brazing, for example. The

上記図３３〜図４０に示すＥＧＲガス冷却装置は、拡径されたガス配管３０２内を貫き、ガスの流れ方向と直角に交差して配設される偏平伝熱管３０３の偏平した外表面に加え、該偏平伝熱管３０３の平坦な外表面にガスの流れ方向に平行して、自らのフラットな折り曲げ部を密着させながら、ランダムに固定される好ましくは小割された多数のチャンネル形状フィン３０５が、伝熱面積をより拡大すると共に、エッヂ効果を得て偏平伝熱管３０３の外表面の形状と、ランダムに固定されたチャンネル形状フィン３０５によってもたらされるガス流の乱流化や、エンジン冷却水によって冷やされる該偏平伝熱管３の内表面の伝熱係数が、前記図２７〜図３７に示すＥＧＲガス冷却装置と同様、ＥＧＲガスに対して約１０倍であること等が相乗的に作用して、その熱交換が速やかにかつほぼ完璧に実施され、優れた冷却効率を得られる。
なお、図３３〜図４０に示すチャンネル形状フィンは、偏平伝熱管３０３同士もしくは該偏平伝熱管２０３とガス配管２０２の間において固定されてコアを形成するため、偏平伝熱管２０３相互とガス配管２０２とを補強する支持体となり、装置のコンパクト化にも寄与する。 The EGR gas cooling apparatus shown in FIGS. 33 to 40 is added to the flat outer surface of the flat heat transfer tube 303 that passes through the expanded gas pipe 302 and intersects the gas flow direction at a right angle. A plurality of preferably channel-shaped fins 305 that are fixed at random, with their flat bent portions closely contacting the flat outer surface of the flat heat transfer tube 303 in parallel with the gas flow direction. The heat transfer area is further expanded, the edge effect is obtained and the shape of the outer surface of the flat heat transfer tube 303, the turbulent flow of the gas flow caused by the channel shape fins 305 fixed at random, and the engine cooling water Synergistically, the heat transfer coefficient of the inner surface of the flat heat transfer tube 3 to be cooled is about 10 times that of the EGR gas as in the EGR gas cooling device shown in FIGS. Acts on, the heat exchange is rapidly and almost completely carried out, obtain a superior cooling efficiency.
33 to 40 are fixed between the flat heat transfer tubes 303 or between the flat heat transfer tubes 203 and the gas pipe 202 to form a core. Therefore, the flat heat transfer pipes 203 and the gas pipe 202 are connected to each other. This contributes to the downsizing of the device.

図４１に示すＥＧＲガス冷却装置４０１は、断面がほぼ矩形に形成されたＥＧＲガス配管４０３の両サイドに、主としてエンジン冷却水が用いられる冷却媒体の流入口（図示せず）と、流出口（図示せず）を備えた冷却ジャケット４０２を配置し、該冷却ジャケット４０２間にあって前記ＥＧＲガス配管４０３を貫通して、ガスの流れ方向に対して直角に交差する複数の偏平の伝熱管４０４が配設され、冷却水の流路（ｃ）を形成している。さらにこのＥＧＲガス冷却装置４０１は、前記偏平伝熱管の偏平した外表面にコルゲートフィン４０５を、ガスの流れ方向に平行して交互に介装させて固定することによって、該偏平伝熱管４０４どうしもしくは偏平伝熱管４とガス配管３の間にあってコアの１セグメントとなし、ガス流路（ｇ）を形成せしめることを基本的な構造としている。   An EGR gas cooling device 401 shown in FIG. 41 has an inlet (not shown) for a coolant mainly using engine cooling water and an outlet (not shown) on both sides of an EGR gas pipe 403 having a substantially rectangular cross section. A plurality of flat heat transfer tubes 404 that intersect between the cooling jackets 402 and pass through the EGR gas pipe 403 and intersect at right angles to the gas flow direction. The cooling water flow path (c) is formed. Further, the EGR gas cooling device 401 is configured such that the corrugated fins 405 are alternately interposed in parallel to the gas flow direction on the flat outer surface of the flat heat transfer tubes, thereby fixing the flat heat transfer tubes 404 or The basic structure is to form a gas flow path (g) between the flat heat transfer tube 4 and the gas pipe 3 as one segment of the core.

各セグメントよりなる上記コアは、偏平伝熱管４０４に対するＥＧＲガス流路（ｇ）の長さを規定して、冷却効率を極力高めるように設計されるが、そのアスペクト比が偏平伝熱管４０４の長さ／ＥＧＲガス流路（ｇ）の長さの比において、１：１．５〜１：７、好ましくは１：２．５から１：５の範囲が望ましく、そのアスペクト比が１：１．５以下の場合はガスの流路が短いため、ガスと伝熱面との接触時間が短すぎて、十分な伝熱性能が得られず、一方、１：５を超える場合は装置が巨大化して設置するスペースが限定されるため、図４１に示す本例において１：３に設計した。なお、ガス配管４０３内をガスの流れ方向に対して直角に貫いて、冷却ジャケット４０２に配設される偏平伝熱管４０４と、該偏平伝熱管４０４の外表面にガスの流れ方向に対して平行に介装・固定されるコルゲートフィン４０５は、本例によってはそれぞれろう付けによって固着したが、固定手段は伝熱性能を妨げない、例えば溶接等を選択することも可能である。   The core composed of each segment is designed so as to increase the cooling efficiency as much as possible by defining the length of the EGR gas flow path (g) with respect to the flat heat transfer tube 404, but the aspect ratio is the length of the flat heat transfer tube 404. In the ratio of length / length of EGR gas flow path (g), a range of 1: 1.5 to 1: 7, preferably 1: 2.5 to 1: 5 is desirable, and its aspect ratio is 1: 1. In the case of 5 or less, since the gas flow path is short, the contact time between the gas and the heat transfer surface is too short, and sufficient heat transfer performance cannot be obtained. In this example shown in FIG. 41, the space is set to 1: 3. Note that a flat heat transfer tube 404 disposed in the cooling jacket 402 passes through the gas pipe 403 at a right angle to the gas flow direction, and an outer surface of the flat heat transfer tube 404 is parallel to the gas flow direction. In this example, the corrugated fins 405 interposed and fixed to each other are fixed by brazing. However, the fixing means may not select the heat transfer performance, for example, welding or the like can be selected.

上記のごとく構成されたＥＧＲガス冷却装置４０１によれば、伝熱管４０４を偏平としたことによって冷却ジャケット４０２間を流れる冷却媒体、即ちエンジン冷却水の流路（ｃ）が狭められてその流速が早くなり、一方、ＥＧＲガスの流れは上記コルゲートフィン４０５によって形成された多数フィンにより、その流路（ｇ）が延長されて偏平伝熱管４０４およびフィン４０５との接触時間が長くなると共に、該偏平伝熱管４０４の偏平した外表面による伝熱面積の拡大と、その外表面の形状によってもたらされるガス流の乱流化や、エンジン冷却水によって冷やされる該偏平伝熱管４０４の内表面の伝熱係数が、ＥＧＲガスに対するフィン側（ガス側）の伝熱係数に対して約１０倍であること等が相乗的に作用して、その熱交換が速やかにかつほぼ完璧に実施され、優れた冷却効率を得られることが確認された。なお、図４１に示すように本例によるコルゲートフィン４０５は、偏平伝熱管４０４の間に交互に介装させて固定されてコアを形成するため、偏平伝熱管４０４相互とガス配管４０３とを補強する支持体となり、装置のコンパクト化にも寄与する。   According to the EGR gas cooling apparatus 401 configured as described above, the flow rate of the cooling medium flowing between the cooling jackets 402, that is, the flow path (c) of the engine cooling water is narrowed by flattening the heat transfer pipe 404. On the other hand, the flow of the EGR gas is extended by the multiple fins formed by the corrugated fins 405, and the flow path (g) is extended to increase the contact time between the flat heat transfer tubes 404 and the fins 405. Expansion of the heat transfer area due to the flat outer surface of the heat transfer tube 404, turbulence of the gas flow caused by the shape of the outer surface, and the heat transfer coefficient of the inner surface of the flat heat transfer tube 404 cooled by engine cooling water However, it is about 10 times the heat transfer coefficient on the fin side (gas side) with respect to EGR gas, and so on. And is almost perfectly implemented, it was confirmed that the resulting superior cooling efficiency. As shown in FIG. 41, the corrugated fins 405 according to this example are alternately interposed between the flat heat transfer tubes 404 and fixed to form a core, so that the flat heat transfer tubes 404 and the gas pipe 403 are reinforced. This contributes to the compactness of the device.

図４２は、偏平伝熱管４０４−１と、該伝熱管に固定されるコルゲートフィン４０５−１とを部分的に示す拡大斜視図であるが、本例による該偏平伝熱管４０４−１は、その内面の任意箇所に略Ｓ字型のリブ４０６が設けられ、偏平伝熱管４０４−１を補強すると共に冷却媒体の流れを整流するように機能する。   FIG. 42 is an enlarged perspective view partially showing the flat heat transfer tube 404-1 and the corrugated fin 405-1 fixed to the heat transfer tube. A substantially S-shaped rib 406 is provided at an arbitrary position on the inner surface, and functions to reinforce the flat heat transfer tube 404-1 and rectify the flow of the cooling medium.

又、偏平伝熱管４０４−２は、図４３に示すように水平方向に複数本並列して設置している。これにより個々の偏平伝熱管４０４−２の垂直方向に対する強度を増すと共に、偏平管４０４−２の偏平幅が小さいので製造が容易である。   Further, a plurality of flat heat transfer tubes 404-2 are installed in parallel in the horizontal direction as shown in FIG. As a result, the strength of the individual flat heat transfer tubes 404-2 in the vertical direction is increased, and the flat width of the flat tubes 404-2 is small, so that the manufacture is easy.

さらに、偏平伝熱管４０４−３は、図４４に示すように偏平伝熱管４０４−３そのものが波型に変形して形成され、それに固定されるコルゲートフィン４０５−２も同様波型に形成される。このような構造とすることにより、冷却媒体の流れも乱流化され、同時にガスの流れも一層複雑となり、該フィン４０５−２を介しての熱交換が促進され、優れた冷却効率が得られると共に熱変形が可能なため熱応力が緩和され、耐久性が優れることが確認された。なお、偏平伝熱管４０４−３の波形への変形は図４９に限定されるものではなく、冷却媒体の流方向に変形しても，組み合わせて変形させてもよい。   Furthermore, as shown in FIG. 44, the flat heat transfer tube 404-3 is formed by deforming the flat heat transfer tube 404-3 itself into a corrugated shape, and the corrugated fins 405-2 fixed thereto are also formed in a corrugated shape. . By adopting such a structure, the flow of the cooling medium is also turbulent, and at the same time, the gas flow is further complicated, heat exchange through the fins 405-2 is promoted, and excellent cooling efficiency is obtained. At the same time, since thermal deformation was possible, it was confirmed that the thermal stress was relaxed and the durability was excellent. In addition, the deformation | transformation to the waveform of the flat heat exchanger tube 404-3 is not limited to FIG. 49, You may deform | transform in the flow direction of a cooling medium, or may deform | transform in combination.

図４５は、偏平伝熱管４０４−４と、該偏平伝熱管４０４−４に固定されるコルゲートフィン４０５−３を部分的に示す平面図で、該コルゲートフィン４０５−３は、偏平伝熱管４０４−４の外表面に蛇行するように固定されている。かかる構造によりガスの流れに乱流若しくは渦流などへの変化をもたせると共に、ガスの流路がより一層延長されるため、該フィン４０５−３を介しての熱交換を助長して、冷却効率がさらに向上することが確認された。なお、上記図４２に示す偏平伝熱管４０４−１及びコルゲートフィン４０５−１は、図４１に示すガス冷却装置４０１に、適宜にかつ部分的に置き換えて用いることにより、その効果を一層高めることも可能である。   FIG. 45 is a plan view partially showing the flat heat transfer tube 404-4 and the corrugated fin 405-3 fixed to the flat heat transfer tube 404-4. The corrugated fin 405-3 includes the flat heat transfer tube 404-. The outer surface of 4 is fixed so as to meander. With this structure, the gas flow is changed to a turbulent flow or a vortex flow, and the gas flow path is further extended. Therefore, the heat exchange through the fins 405-3 is promoted, and the cooling efficiency is improved. Further improvement has been confirmed. The flat heat transfer tubes 404-1 and the corrugated fins 405-1 shown in FIG. 42 can be used to replace the gas cooling device 401 shown in FIG. Is possible.

図４６に示す実施例装置は、同図（ａ）、（ｂ）、（ｃ）の各図に示すようにガス配管４０３−１に配置する冷却ジャケット４０２−１の構造を、アウターシェルディフューザー形状とし、該冷却ジャケット４０２−１とガス流路との境界に、チューブシートからなる仕切り板４０７を設け、偏平伝熱管４０４−５どうしもしくは該偏平伝熱管４０４−５とアウターシェルとの間に介装・固定されるコルゲートフィン４０５−４を波型形状とした以外は、実質的に前記図４１に示す実施例装置と同様であるが、冷却効率等の性能は図４１に示す実施例装置とほぼ同様である。   The embodiment apparatus shown in FIG. 46 has an outer shell diffuser shape in the structure of the cooling jacket 402-1 disposed in the gas pipe 403-1 as shown in the respective drawings (a), (b), and (c). A partition plate 407 made of a tube sheet is provided at the boundary between the cooling jacket 402-1 and the gas flow path, and the flat heat transfer tubes 404-5 or between the flat heat transfer tubes 404-5 and the outer shell are provided. The corrugated fins 405-4 to be mounted and fixed are substantially the same as the embodiment apparatus shown in FIG. 41 except that the corrugated fins 405-4 have a corrugated shape, but the performance such as cooling efficiency is the same as that of the embodiment apparatus shown in FIG. It is almost the same.

又、図４１、図４６に示す各実施例装置においても、コルゲートフィンの代替品として前記図１５に示す波板形状フィンを用いることができるのみならず、図４７（ａ）〜（ｃ）に示すＩ型形状フィン４０５ａ−１（図ａ）、Ｓ字型形状フィン４０５ａ−２（図ｂ）、コの字型形状フィン４０５ａ−３７（図ｃ）や、前記図９に示す各種フィン同様の図４８（ａ）〜（ｅ）に示すフィン、すなわち多数の貫孔が設けられたプレートフィン４０５ｂ−２（図ａ）、ルーバーが設けられたプレートフィン４０５ｂ−３（図ｂ）、変形したルーバーが設けられたプレートフィン４０５ｂ−４（図ｃ）、ピンフィンが設けられたプレートフィン４０５ｂ−５（図ｄ）、凹凸が設けられたプレートフィン４０５ｂ−６（図ｅ）等を用いることができる。なお、これらのフィンは単独、もしくは上記各実施例で用いられた各種コルゲートフィンを含む他のフィンと、それぞれ併用して用いることが可能である。   Also, in each of the embodiments shown in FIGS. 41 and 46, the corrugated fins shown in FIG. 15 can be used as an alternative to the corrugated fins, as shown in FIGS. 47 (a) to 47 (c). I-shaped fins 405a-1 (FIG. A), S-shaped fins 405a-2 (FIG. B), U-shaped fins 405a-37 (FIG. C), and the various fins shown in FIG. 48 (a) to 48 (e), that is, plate fins 405b-2 (FIG. A) provided with a large number of through holes, plate fins 405b-3 (FIG. B) provided with louvers, and deformed louvers. Plate fins 405b-4 (FIG. C) provided with pin fins, plate fins 405b-5 (FIG. D) provided with pin fins, plate fins 405b-6 (FIG. E) provided with irregularities, and the like can be used. These fins can be used alone or in combination with other fins including various corrugated fins used in the above embodiments.

図４９に示すＥＧＲガス冷却装置５０１は、断面がほぼ矩形に拡管されたＥＧＲガス配管５０２の上下に、主としてエンジン冷却水が用いられる冷却媒体の流入口Ｐ１と、流出口Ｐ２とを備えた冷却ジャケット５０４−１、５０４−２を配置し、該冷却ジャケット５０４−１、５０４−２間にあって前記ＥＧＲガス配管（以下、単に「ガス配管」ということがある。）５０２を貫通して、ガスの流れ方向（矢印ｇ）に対して直角に交差する複数（本例においては１２本）の伝熱管５０３が配設され、上記冷却ジャケット５０４−１、５０４−２間における冷却水の流路を形成している。
ここで、上記伝熱管５０３は、ガスの流れ方向後方に向かってその断面形状が次第に拡張するように形成されていることが必須の要件となる。すなわち、本例における当該伝熱管５０３は、図５５に示すようにその断面形状が、先端部５０３−２から後端部５０３−３の方に行くに従い徐々に幅が拡大されたいわゆる楔形形状で、その傾斜面５０３−１を含む伝熱管３の外周面全体が広い伝熱面として形成され、該楔形形状の伝熱管５０３を図４９に示すようにガスの流れ方向に直角に交差して、間隔を保持しながら複数配置し、その管端はガス配管５０２内を貫いて冷却ジャケット５０４−１および５０４−２に、それぞれ開口部を設けた状態で固着された構造となっている。 An EGR gas cooling device 501 shown in FIG. 49 includes a cooling medium inlet P1 and an outlet P2 that are mainly used for engine cooling water above and below an EGR gas pipe 502 having a substantially rectangular cross section. Jackets 504-1 and 504-2 are arranged, and pass between the cooling jackets 504-1 and 504-2 through the EGR gas pipe (hereinafter, simply referred to as “gas pipe”) 502, and A plurality (12 in this example) of heat transfer tubes 503 intersecting at right angles to the flow direction (arrow g) are provided to form a cooling water flow path between the cooling jackets 504-1 and 504-2. doing.
Here, it is an essential requirement that the heat transfer tube 503 be formed so that its cross-sectional shape gradually expands toward the rear in the gas flow direction. That is, the heat transfer tube 503 in this example has a so-called wedge shape in which the cross-sectional shape gradually increases in width from the front end portion 503-2 toward the rear end portion 503-3 as shown in FIG. The entire outer peripheral surface of the heat transfer tube 3 including the inclined surface 503-1 is formed as a wide heat transfer surface, and the wedge-shaped heat transfer tube 503 intersects the gas flow direction at a right angle as shown in FIG. A plurality of pipe ends are arranged while maintaining an interval, and the pipe ends penetrate the inside of the gas pipe 502 and are fixed to the cooling jackets 504-1 and 504-2 with respective openings.

上記のように構成された本例によるＥＧＲガス冷却装置５０１において、冷却媒体となるエンジン冷却水Ｃは、下段の冷却ジャケット５０４−１に設けられた流入口Ｐ１より流入して該冷却ジャケット５０４−１を通過し、次いで前記楔形形状の伝熱管５０３内のそれぞれに通流して上段の冷却ジャケット５０４−２を通過した後、流出口Ｐ２を介して系外に流出する。一方、ガス配管５０２の上流側から当該冷却装置５０１内に流入したＥＧＲガスは、該配管内をガスの流れ方向（矢印ｇ）に直角に交差して複数配設された伝熱管５０３の外周面に、接触を繰り返しながら下流側へ流下して系外へ流出する。この際、該冷却装置１内に流入した、熱せられた状態のＥＧＲガスは、該伝熱管５０３の傾斜面５０３−１を中心とする伝熱面に衝突を繰り返しながら下流方向へ移動するが、該伝熱面、とりわけ傾斜面５０３−１との衝突の繰り返しによってガスの境界層がつぎつぎと剥離を繰り返し、効果的な熱交換が行なわれて、ＥＧＲガスは可及的速やかに冷却され、４列に配設された伝熱管５０３群に次々と接触を繰り返しながら系外に流出されたＥＧＲガスは、エンジンの吸気系に戻されての再循環に、全く支障のない温度域にまで冷却される。   In the EGR gas cooling apparatus 501 according to the present example configured as described above, the engine coolant C serving as a cooling medium flows in from the inlet P1 provided in the lower cooling jacket 504-1, and the cooling jacket 504- 1, then flows through each of the wedge-shaped heat transfer tubes 503, passes through the upper cooling jacket 504-2, and then flows out of the system through the outlet P2. On the other hand, the EGR gas that has flowed into the cooling device 501 from the upstream side of the gas pipe 502 has an outer peripheral surface of a heat transfer pipe 503 that is disposed in a plurality of positions in the pipe so as to intersect at right angles to the gas flow direction (arrow g). In addition, it flows down to the downstream side while repeating contact and flows out of the system. At this time, the heated EGR gas flowing into the cooling device 1 moves in the downstream direction while repeatedly colliding with the heat transfer surface centering on the inclined surface 503-1 of the heat transfer tube 503. Due to repeated collisions with the heat transfer surface, particularly the inclined surface 503-1, the gas boundary layer repeats peeling one after another, and effective heat exchange is performed, and the EGR gas is cooled as quickly as possible. The EGR gas that has flowed out of the system while repeatedly contacting the heat transfer tubes 503 arranged in a row is cooled to a temperature range that does not hinder the recirculation after returning to the intake system of the engine. The

また、図５２〜図５３に示す他のＥＧＲガス冷却装置は、前記楔型形状の伝熱管５０３を、図５６に示すような形状に変更し、該楔型形状の伝熱管５０３ａを図５３に示すようにガスの流れ方向に直角に交差して、間隔を保持しながら複数位置した構造としたものであり、該楔形形状の伝熱管の形状を一部変更した以外は実質的に実施例１と同一の多管式ガス熱交換装置５０１ａを構成した。このＥＧＲガス冷却装置５０１ａの場合も、前記図４９〜図５１に示すＥＧＲガス冷却装置とほぼ同等の冷却性能が得られる。   Further, in another EGR gas cooling device shown in FIGS. 52 to 53, the wedge-shaped heat transfer tube 503 is changed to the shape shown in FIG. 56, and the wedge-shaped heat transfer tube 503a is changed to FIG. As shown in the figure, the structure is a plurality of positions that intersect with the gas flow direction at right angles while maintaining the interval, and substantially the first embodiment except that the shape of the wedge-shaped heat transfer tube is partially changed. The same multi-tubular gas heat exchange device 501a as that of FIG. Also in the case of this EGR gas cooling device 501a, substantially the same cooling performance as that of the EGR gas cooling device shown in FIGS. 49 to 51 can be obtained.

さらに、前記図４９〜図５４に示すＥＧＲガス冷却装置においても、所望により楔型形状の伝熱管５０３または５０３ａ同士の間隙か、もしくは楔形形状の伝熱管５０３または５０３ａとガス配管５０２または５０２ａとの間隙に、ガスの流れ方向（矢印ｇ）と平行してプレートフィンを固着することも好ましい実施形態として採用することができる。プレートフィンの形状については、前記図９に示すプレートフィン、すなわちプレートフィンの一部に貫孔を設けたもの、ルーバーを設けたもの、ピンフィンを取り付けたもの、凹凸を設けたもの等から適宜選択して使用することができる。   Further, also in the EGR gas cooling device shown in FIGS. 49 to 54, the gap between the wedge-shaped heat transfer tubes 503 or 503a or the wedge-shaped heat transfer tubes 503 or 503a and the gas pipes 502 or 502a as required. It is also possible to adopt a preferred embodiment in which a plate fin is fixed to the gap in parallel with the gas flow direction (arrow g). The shape of the plate fin is appropriately selected from the plate fin shown in FIG. 9, that is, a plate fin provided with a through hole, a louver provided, a pin fin attached, and an uneven provided. Can be used.

図４９〜図５４に示すＥＧＲガス冷却装置において、楔形形状の伝熱管５０３、５０３ａに加え、任意で前記の各種プレートフィンを固着することにより、冷却装置内におけるガス流の攪拌効果がさらに促進されると共に、プレートフィンそのものによる伝熱面積の拡大が期待され、冷却効率の一層の向上を図ることができると共に、該伝熱管５０３または５０３ａ同士、もしくは伝熱管５０３または５０３ａとガス配管５０２または５０２ａとの間に強固な支持体が形成されて、優れた補強効果が得られるために、他の補強手段を要することが無く、装置のコンパクト化に寄与する。   In the EGR gas cooling apparatus shown in FIGS. 49 to 54, in addition to the wedge-shaped heat transfer tubes 503 and 503a, the above-described various plate fins are optionally fixed, thereby further promoting the gas flow stirring effect in the cooling apparatus. In addition, expansion of the heat transfer area by the plate fin itself is expected, and the cooling efficiency can be further improved, and the heat transfer tubes 503 or 503a, or between the heat transfer tubes 503 or 503a and the gas pipe 502 or 502a, Since a strong support is formed between them and an excellent reinforcing effect is obtained, other reinforcing means are not required, contributing to the compactness of the apparatus.

また、図４９〜図５４に示すＥＧＲガス冷却装置において、拡管されたガス配管内を貫き、ガスの流れ方向と直角に交差して複数配設される断面形状が楔形形状の伝熱管の形状については、伝熱管５０３、５０３ａの形状によって拘束されるものではなく、その先端部５０３−２、５０３ａ−２からガスの流れ方向後方に当たる後端部５０３−３、５０３ａ−３にかけてその幅が拡大し、ガスの流れ方向上流側から下流側に向かっての傾斜面５０３−１、５０３ａ−１を含んで広い伝熱面を有し、該伝熱管５０３、５０３ａの後流側における急激な断面変化によって「カルマンの渦列」が生ずることが期待される形状であれば、該傾斜面５０３−１、５０３ａ−１の傾斜角、伝熱管５０３、５０３ａ群の配設位置やピッチは伝熱管５０３、５０３ａ群の数を含め、特に制限するものではなくその効果と設置スペースとの兼ね合いにおいて自由に設計変更が可能である。   In addition, in the EGR gas cooling apparatus shown in FIGS. 49 to 54, the shape of the heat transfer tube having a wedge-shaped cross-section that extends through the expanded gas pipe and intersects at right angles to the gas flow direction. Is not constrained by the shape of the heat transfer tubes 503 and 503a, and the width increases from the front end portions 503-2 and 503a-2 to the rear end portions 503-3 and 503a-3 that hit the rear in the gas flow direction. And a wide heat transfer surface including inclined surfaces 503-1 and 503a-1 from the upstream side to the downstream side in the gas flow direction, and by a sudden cross-sectional change on the downstream side of the heat transfer tubes 503 and 503a If the shape is expected to generate a “Kalman vortex street”, the inclination angles of the inclined surfaces 503-1 and 503a-1, the arrangement positions and pitches of the heat transfer tubes 503 and 503a, and the heat transfer tubes 503 and 5 are determined. Including the number of 3a group, in particular it can be freely modified in design tradeoff restrict not its effect as installation space.

図５７に示すＥＧＲガス冷却装置６０１は、図５７〜図５９に示すように断面がほぼ矩形に拡管されたＥＧＲガス配管６０２の上下に、主としてエンジン冷却水が用いられる冷却媒体（以下単に「冷却水」ということがある。）Ｃの流入口Ｐ１と、流出口Ｐ２とを備えた冷却ジャケット６０４−１、６０４−２を配置し、該冷却ジャケット６０４−１、６０４−２間にあって前記ＥＧＲガス配管６０２を貫通して、ガスの流れ方向（矢印ｇ）に対して直角に交差する円筒状チューブからなる複数の伝熱管６０３が固着・配設されて、ガスの流れ方向上流から下流方向に複数列の伝熱管列群を形成すると共に、上記冷却ジャケット６０４−１、６０４−２間における冷却水の流路を形成している。
ここで、上記伝熱管列群の冷却水流路には、ガスの流れ方向上流側の第１列と第２列の間の冷却ジャケット６０４−１に堰を設け、次に第２列と第３列の間の冷却ジャケット６０４−２に堰６０６−１を設け、また第３列と第４列の間の冷却ジャケット６０４−１に、さらに第４列と第５列の間の冷却ジャケット６０４−２にそれぞれ堰６０６−Ｘを設けるという、いわゆる各伝熱管列群毎交互に上下の冷却ジャケット６０４−１および６０４−２内に堰６０６を形成して、流入口Ｐ１から流入した冷却水が流出口Ｐ２から系外に流れ去するまでの流路を、強制的に制御することが必須の要件となる。かなわち、本例における冷却水は、流入口Ｐ１から冷却ジャケット６０４−１内に流入すると堰６０６−１に遮られて、当該冷却ジャケット６０４−１をから第１列の伝熱管列群を形成する各々の伝熱管６０３を通流し、他方の冷却ジャケット６０４−２に流入するが、ここでも堰６０６−Ｘに遮られて冷却ジャケット６０４−２をから第２列の伝熱管列群を形成する各々の伝熱管６０３を通流して、冷却ジャケット６０４−１に流入するという経路を繰返し、最終的に冷却ジャケット６０４−２を経て流出口Ｐ２から系外に流れ去るように構成されている。 57. The EGR gas cooling device 601 shown in FIG. 57 has a cooling medium (hereinafter simply referred to as “cooling medium”) in which engine cooling water is mainly used above and below an EGR gas pipe 602 having a substantially rectangular cross section as shown in FIGS. The cooling jackets 604-1 and 604-2 each having a C inlet P1 and an outlet P2 are disposed between the cooling jackets 604-1 and 604-2, and the EGR gas. A plurality of heat transfer tubes 603 made of a cylindrical tube that penetrates the pipe 602 and intersects at right angles to the gas flow direction (arrow g) are fixed and arranged, and a plurality of heat transfer tubes from the upstream to the downstream in the gas flow direction. A heat transfer tube row group is formed, and a cooling water flow path is formed between the cooling jackets 604-1 and 604-2.
Here, in the cooling water flow path of the heat transfer tube row group, a weir is provided in the cooling jacket 604-1 between the first row and the second row on the upstream side in the gas flow direction, and then the second row and the third row. A weir 606-1 is provided in the cooling jacket 604-2 between the rows, the cooling jacket 604-1 between the third row and the fourth row, and a cooling jacket 604 between the fourth row and the fifth row. The weir 606 is formed in the upper and lower cooling jackets 604-1 and 604-2 alternately so-called each heat transfer tube row group in which the weir 606-X is provided in each of the two, so that the cooling water flowing in from the inlet P1 flows. It is an essential requirement to forcibly control the flow path from the outlet P2 until it flows out of the system. In other words, when the cooling water in this example flows into the cooling jacket 604-1 from the inflow port P1, it is blocked by the weir 606-1 to form the first row of heat transfer tube rows from the cooling jacket 604-1. Each heat transfer tube 603 flows and flows into the other cooling jacket 604-2, but here again is blocked by the weir 606-X to form the second heat transfer tube row group from the cooling jacket 604-2. A path of passing through each heat transfer tube 603 and flowing into the cooling jacket 604-1 is repeated, and finally, it flows out of the system from the outlet P2 via the cooling jacket 604-2.

上記のように構成されたＥＧＲ式ガス冷却装置６０１において、冷却媒体となるエンジン冷却水Ｃは、上段の冷却ジャケット６０４−１に設けられた流入口Ｐ１より流入すると同時に、第１列の伝熱管列群を経由して下段の冷却ジャケット６０４−２内に至り、さらに第２列の伝熱管列群を経て冷却ジャケット６０４−１に流入するという経路を繰返し、早い流速と多量の流量を維持しながら全ての伝熱管列群を経由して流出口Ｐ２から流去するが、この間にＥＧＲガス配管６０２のガスの流れ方向（矢印ｇ）上流側から当該ガス冷却装置６０１内に流入したＥＧＲガスの熱は、該伝熱管列群の各々の伝熱管６０３に順次接触を繰り返しながら効果的に熱交換が行われて、可及的速やかに冷却され、該ガス冷却装置６０１の下流側からＥＧＲガス配管内に戻る際には、エンジンの吸気系に戻されての再循環に、全く支障のない温度域にまで冷却される。   In the EGR type gas cooling apparatus 601 configured as described above, the engine coolant C serving as a cooling medium flows in from the inlet P1 provided in the upper cooling jacket 604-1, and at the same time, the first row of heat transfer tubes. It repeats the route of reaching the cooling jacket 604-2 in the lower stage through the row group, and flowing into the cooling jacket 604-1 through the second row of heat transfer tube rows to maintain a high flow rate and a large amount of flow rate. While flowing out from the outlet P2 through all the heat transfer tube rows, the EGR gas flowing into the gas cooling device 601 from the upstream side in the gas flow direction (arrow g) of the EGR gas pipe 602 during this period The heat is effectively exchanged while repeating contact with each of the heat transfer tubes 603 in the heat transfer tube row group in order to cool as quickly as possible, and from the downstream side of the gas cooling device 601, EGR When returning to the scan pipe, the recirculation of the returned to the intake system of the engine, is cooled at all to a temperature range not interfering.

なお、ＥＧＲガス冷却装置６０１は、図５８に示すように冷却ジャケット６０４−１、６０４−２間におけるＥＧＲガス配管６０２を貫いて、ガスに流れ（矢印ｇ）に対して直角に交差して固着・配列されて伝熱管列群を形成する伝熱管６０３を、ガス流路に対してその間隔を狭くするよう配列したことにより、堰によって増幅された冷却水の流速と水量とが相互に作用して、より効果的な熱交換が促進されて、沸騰による気泡の発生も無く、優れた冷却効率が得られる。   As shown in FIG. 58, the EGR gas cooling device 601 passes through the EGR gas pipe 602 between the cooling jackets 604-1 and 604-2, and adheres to the gas at a right angle with respect to the flow (arrow g). -By arranging the heat transfer tubes 603 that are arranged to form a heat transfer tube array so that the interval between the heat transfer tubes 603 is narrowed with respect to the gas flow path, the flow rate and the amount of cooling water amplified by the weir interact with each other. Thus, more effective heat exchange is promoted, no bubbles are generated due to boiling, and excellent cooling efficiency is obtained.

また、図６０〜図６１に示すＥＧＲガス冷却装置６１１は、伝熱管列群を形成する伝熱管６１３−１、６１３−２の本数が疎らであり、該伝熱管６１３−１および６１３−２に予めスパイラル状フィン６１３−１ａおよびディスク状フィン６１３−２ａが取り付けられていることを除いて、実質的に前記ＥＧＲガス冷却装置６０１と同様のガス冷却装置６１１を構成した。６１２はＥＧＲガス配管である。
このＥＧＲガス冷却装置６１１の場合も、堰６１６−１および６１６−Ｘによって流路を規制された冷却水は、速い流速と多量の水量を維持して伝熱管６１３−１、６１３−２内を通流し、加えてスパイラル状フィン６１３−１ａおよびディスク状フィンによるガス流の攪拌と、伝熱面積の拡大が相乗的に作用し、ＥＧＲガス冷却装置６１１とほぼ同等の冷却性能が得られる。 In addition, the EGR gas cooling device 611 shown in FIGS. 60 to 61 has sparse heat transfer tubes 613-1 and 613-2 that form a heat transfer tube array group, and the heat transfer tubes 613-1 and 613-2 A gas cooling device 611 substantially similar to the EGR gas cooling device 601 was configured except that the spiral fins 613-1a and the disk-shaped fins 613-2a were previously attached. Reference numeral 612 denotes an EGR gas pipe.
Also in the case of this EGR gas cooling device 611, the cooling water whose flow path is restricted by the weirs 616-1 and 616-X is maintained in the heat transfer tubes 613-1 and 613-2 while maintaining a high flow rate and a large amount of water. In addition, the stirring of the gas flow by the spiral fins 613-1a and the disk-shaped fins and the expansion of the heat transfer area act synergistically, and a cooling performance substantially equivalent to that of the EGR gas cooling device 611 is obtained.

さらに、図６２〜図６３に示すＥＧＲガス冷却装置６２１は、伝熱管列群を形成する伝熱管６２３の本数が若干疎らであり、該伝熱管６２３のそれぞれにガスの流れ方向に平行して複数のプレートフィン６２５が取り付けられていることを除いて、実質的に前記ＥＧＲガス冷却装置６０１と同様のガス冷却装置６２１を構成した。６２２はＥＧＲガス配管である。
このＥＧＲガス冷却装置６２１の場合も、堰６２６−１および６２６−Ｘによって流路を規制された冷却水は、速い流速と多量の水量を維持して伝熱管６２３内を通流し、加えてプレートフィン６２５によるガス流の乱流化と、伝熱面積の拡大が相乗的に作用し、実施例１とほぼ同等の冷却性能を得られることが確認された。 Further, in the EGR gas cooling device 621 shown in FIGS. 62 to 63, the number of the heat transfer tubes 623 forming the heat transfer tube array group is slightly sparse, and a plurality of heat transfer tubes 623 are arranged in parallel with the gas flow direction. The gas cooling device 621 was substantially the same as the EGR gas cooling device 601 except that the plate fins 625 were attached. Reference numeral 622 denotes an EGR gas pipe.
Also in the case of this EGR gas cooling device 621, the cooling water whose flow path is regulated by the weirs 626-1 and 626-X flows through the heat transfer pipe 623 while maintaining a high flow rate and a large amount of water, and in addition to the plate It was confirmed that the turbulent flow of the gas flow by the fins 625 and the expansion of the heat transfer area act synergistically to obtain a cooling performance substantially equivalent to that of Example 1.

また、図６４〜６６に示すＥＧＲガス冷却装置は、６３１は、伝熱管列群を形成する伝熱管６３３が偏平チューブからなり、冷却ジャケット６３４が拡管されたＥＧＲガス配管６３２外周の全周を覆ういわゆる２重管タイプであり、該２重管タイプの冷却ジャケット６３４がセパレータ６３４−１によって上下に区分された構造となっていることを除いて、実質的に前記ＥＧＲガス冷却装置６０１と同様のガス冷却装置６３１を構成した。
この冷却装置６３１の場合も、堰６３６−１および６３６−Ｘによって流路を規制された冷却水は、速い流速と多量の水量を維持して伝熱管６２３内を通流し、加えて偏平伝熱管６３３による流速の更なる加速と、伝熱面積の拡大が相乗的に作用し、前記ＥＧＲガス冷却装置６０１とほぼ同等の冷却性能が得られる。 Also, in the EGR gas cooling apparatus shown in FIGS. 64 to 66, 631 covers the entire circumference of the outer periphery of the EGR gas pipe 632 in which the heat transfer tube 633 forming the heat transfer tube row group is formed of a flat tube and the cooling jacket 634 is expanded. It is a so-called double pipe type, and is substantially the same as the EGR gas cooling device 601 except that the double pipe type cooling jacket 634 has a structure vertically divided by a separator 634-1. A gas cooling device 631 was configured.
Also in the case of this cooling device 631, the cooling water whose flow path is regulated by the weirs 636-1 and 636-X flows through the heat transfer pipe 623 while maintaining a high flow rate and a large amount of water, and in addition, the flat heat transfer pipe Further acceleration of the flow velocity by 633 and expansion of the heat transfer area act synergistically, and a cooling performance substantially equivalent to that of the EGR gas cooling device 601 is obtained.

図６７〜６８に示すＥＧＲガス冷却装置６４１は、伝熱管列群を形成する各々の偏平伝熱管６４３の間隙、若しくは該偏平伝熱管６４３とＥＧＲガス配管６４２の内壁との間隙に、前記図１５に示すようなコルゲートフィンをガスの流れ方向と平行に接合した以外は、実質的に前記ＥＧＲガス冷却装置６０１と同様のガス冷却装置６４１を構成した。
このＥＧＲガス冷却装置６４１の場合も、堰６４６−１および６４６−Ｘによって流路を規制された冷却水は、速い流速と多量の水量を維持して伝熱管６４３内を通流し、加えて偏平伝熱管６３３による流速の更なる加速と、接合されたコルゲートフィンによるガス流の乱流化や伝熱面積の拡大が相乗的に作用し、迅速な熱交換によって効率的な冷却性能が得られる。 67 to 68, the EGR gas cooling device 641 is arranged in the gap between the flat heat transfer tubes 643 forming the heat transfer tube row group or the gap between the flat heat transfer tubes 643 and the inner wall of the EGR gas pipe 642. A gas cooling device 641 that is substantially the same as the EGR gas cooling device 601 is configured except that corrugated fins as shown in FIG.
Also in the case of this EGR gas cooling device 641, the cooling water whose flow path is regulated by the weirs 646-1 and 646-X flows through the heat transfer pipe 643 while maintaining a high flow rate and a large amount of water, and in addition, is flat. Further acceleration of the flow velocity by the heat transfer tube 633 and turbulent gas flow and expansion of the heat transfer area by the joined corrugated fins act synergistically, and efficient cooling performance can be obtained by rapid heat exchange.

さらにまた、図６９〜７１に示すＥＧＲガス冷却装置６５１と、図７２〜７４に示すＥＧＲガス冷却装置６６１は、伝熱管列群を形成する各々の伝熱管６５３および６６３の形状が、ガスの流れ方向（矢印ｇ）上流側の先端部から下流側の後端部にかけて幅が拡張する、いわゆる楔形形状としたものであり、楔形形状の伝熱管６５３および６６３を用い、冷却ジャケットをそれぞれ上下に配置したいわゆるヘッダータイプとした以外は、実質的に前記ＥＧＲガス冷却装置６５１および６６１を構成した。
このＥＧＲガス冷却装置６５１、６６１においても、堰６５６−１、６５６−Ｘおよび６６６−１、６６６−Ｘによって流路を規制された冷却水は、速い流速と多量の水量を維持して楔型形状の伝熱管６５３、６６３内を通流し、加えてこの楔型形状の伝熱管６５３および６６３に形成された伝熱面に、ガス流が順次衝突を繰り返しながら剥離されることにより、薄い境界層が維持されて効果的に熱交換が促進され、極めて優れた冷却性能が得られる。 Furthermore, in the EGR gas cooling device 651 shown in FIGS. 69 to 71 and the EGR gas cooling device 661 shown in FIGS. 72 to 74, the shape of each of the heat transfer tubes 653 and 663 forming the heat transfer tube row group is the flow of gas. Direction (arrow g) is a so-called wedge shape that expands in width from the upstream tip to the downstream rear end, and uses the wedge-shaped heat transfer tubes 653 and 663 and arranges the cooling jacket vertically. Except for the so-called header type, the EGR gas cooling devices 651 and 661 were substantially configured.
Also in the EGR gas cooling devices 651 and 661, the cooling water whose flow path is restricted by the weirs 656-1, 656-X and 666-1, 666-X maintains a high flow rate and a large amount of water, and is wedge-shaped. The thin boundary layer is formed by flowing through the heat transfer tubes 653 and 663 having a shape and, in addition, the gas flow is separated from the heat transfer surfaces formed in the wedge-shaped heat transfer tubes 653 and 663 while sequentially colliding with each other. Is maintained and heat exchange is effectively promoted, and extremely excellent cooling performance is obtained.

なお、上記図５７〜図７４に示すＥＧＲガス冷却装置においても、任意で前記図９に例示するプレートフィンおよび前記図１５に例示する波板状のフィンなどを固着することにより、冷却装置内におけるガス流の攪拌効果がさらに促進されると共に、フィンそのものによる伝熱面積の拡大が期待され、冷却効率の一層の向上を図ることができると共に、該伝熱管同士、若しくは該伝熱管とガス配管との間に強固な支持体が形成されて、優れた補強効果が得られるために、他の補強手段を要することが無く、装置のコンパクト化に寄与する。   In the EGR gas cooling apparatus shown in FIGS. 57 to 74, the plate fins exemplified in FIG. 9 and the corrugated fins exemplified in FIG. The stirring effect of the gas flow is further promoted, and the expansion of the heat transfer area by the fin itself is expected, and the cooling efficiency can be further improved, and the heat transfer tubes, or between the heat transfer tubes and the gas piping, Since a strong support is formed between them and an excellent reinforcing effect is obtained, other reinforcing means are not required, contributing to the compactness of the apparatus.

また、上記図５７〜図７４に示す各ＥＧＲガス冷却装置における伝熱管は、その優れた伝熱性と加工の容易性および機械的強度等を加味して、金属性チューブが好ましく採用されるが、伝熱管列群における冷却水流路を規制する堰は、通流する冷却水の水圧に耐え、その流路を任意に規制しうるものであれば特に制限を加えるものではなく、冷却ジャケット内において任意に移動が可能な、可撤式構造であることがより好ましい。なお、上記各実施例における堰は、伝熱管列群毎の境界に交互に設けて冷却水流路を一本の流れに規制したが、本発明はこれによって拘束されるものではなく、第１列の流れから後流に行くに従いその流れを緩めたり、中流域の流れを意図的に速めたり、堰を設ける位置を移動することによって、任意にかつ所望の流れを操作することが可能である。かかる構成によって本発明のＥＧＲガス冷却装置は、該装置内における連続沸騰に起因する気泡によって、効果的熱交換が阻害される現象を未然に防止して、優れた冷却効率を得ることができる。   In addition, as the heat transfer tube in each EGR gas cooling device shown in FIGS. 57 to 74, a metal tube is preferably adopted in consideration of its excellent heat transfer property, ease of processing, mechanical strength, and the like. The weir that regulates the cooling water flow path in the heat transfer tube array group is not particularly limited as long as it can withstand the water pressure of the flowing cooling water and can arbitrarily regulate the flow path, and can be arbitrarily placed in the cooling jacket. It is more preferable that the structure is removable. In addition, although the weir in each said Example provided alternately in the boundary for every heat exchanger tube row group, and restricted the cooling water flow path to one flow, this invention is not restrained by this, The 1st row It is possible to manipulate the desired flow arbitrarily and arbitrarily by slowing the flow from the current flow to the rear flow, intentionally speeding the flow in the middle basin, or moving the position where the weir is provided. With this configuration, the EGR gas cooling device of the present invention can prevent the phenomenon in which effective heat exchange is hindered by bubbles caused by continuous boiling in the device, and can obtain excellent cooling efficiency.

さらに、本発明では上記した全てのＥＧＲガス冷却装置におけるＥＧＲガス配管や胴管、冷却配管あるいは伝熱管の壁面に必要に応じて凹凸を形成して乱流化や伝熱面積を増加させてもよい。図７５、図７６はその一例を示したもので、図１〜図３に示すＥＧＲガス冷却装置のＥＧＲガス配管２と冷却配管３の各壁面に凹凸を形成したものである。なお、この凹凸は必要に応じて設けることはいうまでもない。   Furthermore, in the present invention, even if the EGR gas pipe, the trunk pipe, the cooling pipe, or the heat transfer pipe wall surface is formed as necessary on all the EGR gas cooling apparatuses described above, the turbulence and the heat transfer area can be increased. Good. FIG. 75 and FIG. 76 show an example, in which unevenness is formed on each wall surface of the EGR gas pipe 2 and the cooling pipe 3 of the EGR gas cooling apparatus shown in FIGS. Needless to say, the unevenness is provided as necessary.

なお、本発明におけるこれら各部材の固着手段としては、前記したごとく溶接やろう付けによるいわゆる溶着手段が好ましく採用されるが、該溶着によって相互に優れた密着性が確保され、伝熱作用が阻害されないことと、激しい振動が繰り返されるなど、過酷な操作環境の中で信頼し得る接合が期待されるためである。   In addition, as described above, so-called welding means by welding or brazing is preferably used as the fixing means of these members in the present invention, but the adhesion ensures mutual excellent adhesion, and the heat transfer action is hindered. This is because reliable bonding is expected in a harsh operating environment, such as not being performed and repeated intense vibrations.

上記各実施例によって明らかなように、本発明に係るガス冷却装置は、その構造が簡略であるにも拘らず、優れた冷却効率を発揮する。従って、装置の軽量・小型化を可能とするため、自動車用のＥＧＲガス冷却装置として広範に用いられることは勿論、排気ガスからの熱回収装置や他のガス冷却装置としても転用し得るなど幅広い用途が期待される。   As is clear from the above embodiments, the gas cooling device according to the present invention exhibits excellent cooling efficiency despite its simple structure. Therefore, in order to make the device lighter and smaller, it can be widely used as an EGR gas cooling device for automobiles, as well as widely used as a heat recovery device from exhaust gas and other gas cooling devices. Applications are expected.

本発明の第１実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows the apparatus of 1st Example of this invention. 図１のイーイ線上の横断平面図である。FIG. 2 is a cross-sectional plan view on the easy line of FIG. 1. 図１のローロ線上の縦断正面図である。It is a vertical front view on the roll line of FIG. 本発明の第２実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows the apparatus of 2nd Example of this invention. 図４のハーハ線上の横断平面図である。It is a cross-sectional plan view on the ha ha line of FIG. 本発明の第３実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows the apparatus of 3rd Example of this invention. 図６のニーニ線上の横断平面図である。FIG. 7 is a cross-sectional plan view on the Nini line in FIG. 6. 図６、図７に示す第３実施例装置における冷却配管（伝熱管）とプレートフィンの接合構造の一例を示す断面図である。It is sectional drawing which shows an example of the joining structure of the cooling piping (heat-transfer tube) and plate fin in the 3rd Example apparatus shown in FIG. 6, FIG. 図６、図７に示す第３実施例装置におけるプレートフィンの各種構造例を示す断面図で、（ａ）は貫孔を設けたプレートフィン、（ｂ）（ｃ）はルーバーを設けたプレートフィン、（ｄ）はピンフィンを設けたプレートフィン、（ｅ）はプレス成形による凹凸を設けたプレートフィンをそれぞれ示す。6 and 7 are sectional views showing various structural examples of plate fins in the apparatus of the third embodiment, wherein (a) is a plate fin provided with a through hole, and (b) and (c) are plate fins provided with a louver. , (D) shows plate fins provided with pin fins, and (e) shows plate fins provided with unevenness by press molding. 本発明の第４実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows the apparatus of 4th Example of this invention. 図１０のホーホ線上の横断平面図である。It is a cross-sectional plan view on the Hoho line of FIG. 図１０のヘーヘ線上の縦断正面図である。It is a vertical front view on the hae line of FIG. 本発明の第５実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows the apparatus of 5th Example of this invention. 図１３のトート線上の縦断正面図である。It is a vertical front view on the tote line of FIG. 本発明装置における波板部品の一例を拡大して示す部分斜視図で、（ａ）は円弧状断面の波板部品、（ｂ）は台形状断面の波板部品をそれぞれ示す。It is the fragmentary perspective view which expands and shows an example of the corrugated sheet part in this invention apparatus, (a) shows the corrugated sheet part of an arc-shaped cross section, (b) shows the corrugated sheet part of a trapezoidal cross section, respectively. 本発明の第６実施例装置を示す縦断側面図である。It is a vertical side view which shows the 6th Example apparatus of this invention. 図１６に示す第６実施例装置におけるプレートフィンを示す斜視図である。It is a perspective view which shows the plate fin in the 6th Example apparatus shown in FIG. 図１６のチ−チ線上の横断平面図である。FIG. 17 is a transverse plan view on the teach line in FIG. 16. 図１６のリ−リ線上の縦断正面図である。FIG. 17 is a longitudinal front view on the reel line of FIG. 16. 本発明の第７実施例装置を示す縦断側面図である。It is a vertical side view which shows the 7th Example apparatus of this invention. 図２０に示す第７実施例装置におけるプレートフィンを示す斜視図である。It is a perspective view which shows the plate fin in the 7th Example apparatus shown in FIG. 図２０のヌ−ヌ線上の横断平面図である。FIG. 21 is a cross-sectional plan view on the Noon line of FIG. 20. 図２０のル−ル線上の縦断正面図である。It is a longitudinal front view on the rule line of FIG. 本発明の第８実施例装置を示す模式的な要部斜視図である。It is a typical principal part perspective view which shows the 8th Example apparatus of this invention. 図２４に示す第８実施例装置におけるフレキ成形部を示す要部斜視図である。It is a principal part perspective view which shows the flexible molding part in the 8th Example apparatus shown in FIG. 図２４に示す第８実施例装置における他のフレキ成形部を示す要部斜視図である。It is a principal part perspective view which shows the other flexible molding part in the 8th Example apparatus shown in FIG. 本発明の第９実施例装置を示す縦断正面図である。It is a vertical front view which shows the 9th Example apparatus of this invention. 本発明の第１０実施例装置を示し、（ａ）は横断平面図、（ｂ）は縦断正面図である。The apparatus of 10th Example of this invention is shown, (a) is a cross-sectional top view, (b) is a vertical front view. 本発明の第１１実施例装置を示し、（ａ）は横断平面図、（ｂ）は縦断正面図である。The 11th Example apparatus of this invention is shown, (a) is a cross-sectional top view, (b) is a vertical front view. 本発明の第１２実施例装置を示し、（ａ）は横断平面図、（ｂ）は縦断正面図である。The apparatus of 12th Example of this invention is shown, (a) is a cross-sectional top view, (b) is a vertical front view. 本発明の第１３実施例装置を示し、（ａ）は横断平面図、（ｂ）は縦断正面図である。The apparatus of 13th Example of this invention is shown, (a) is a cross-sectional top view, (b) is a vertical front view. 本発明装置におけるうねりを有した波形フィンを示す斜視図である。It is a perspective view which shows the waveform fin with the wave | undulation in this invention apparatus. 本発明の第１４実施例装置を示す縦断正面図である。It is a vertical front view which shows the 14th Example apparatus of this invention. 図３３に示す第１４実施例装置を部分的に示す一部拡大断面図である。FIG. 34 is a partially enlarged sectional view partially showing the fourteenth embodiment apparatus shown in FIG. 33; 本発明の第１５実施例装置を示す縦断正面図である。It is a vertical front view which shows the 15th Example apparatus of this invention. 図３５に示す第１５実施例装置を部分的に示す一部拡大断面図である。FIG. 36 is a partially enlarged sectional view partially showing the fifteenth embodiment apparatus shown in FIG. 35; 図３５に示す第１５実施例装置において用いられる一部切り起こし帯状フィン単体を示す斜視図である。FIG. 36 is a perspective view showing a single partially raised belt-like fin used in the fifteenth embodiment apparatus shown in FIG. 35. 同じく各実施例装置において任意に用いることが可能な各種フィンの単体を示す斜視図で、（ａ）は円形の孔を設けたもの、（ｂ）は断面半円形の凹凸を設けたもの、（ｃ）は断面凹凸状のヒダを全長にわたり設けたもの、（ｄ）はリップ上の折り曲げ部を形成したものをそれぞれ示す。Similarly, it is a perspective view showing a single unit of various fins that can be arbitrarily used in each example device, (a) is provided with a circular hole, (b) is provided with a semicircular cross section, ( c) shows a pleated portion having a concavo-convex cross section over the entire length, and (d) shows a fold formed on the lip. 同じく各実施例装置において任意に用いることが可能な形態の異なるルーバーを設けたチャンネルフィンを例示したもので、（ａ）は一端を屈曲させたルーバを有するチャンネルフィンを示す斜視図、（ｂ）は両端を屈曲させたルーバーを有するチャンネルフィンを示す斜視図、（ｃ）は湾曲形のルーバーを有するチャンネルフィンを示す斜視図である。Similarly, the channel fins provided with different louvers that can be arbitrarily used in each embodiment apparatus are illustrated, (a) is a perspective view showing a channel fin having a louver with one end bent, (b). FIG. 5 is a perspective view showing a channel fin having a louver with both ends bent, and FIG. 5C is a perspective view showing a channel fin having a curved louver. 同じく各実施例装置におけるフィンの組み付け状態を部分的に示す平面図である。It is a top view which shows partially the assembly | attachment state of the fin in each Example apparatus similarly. 本発明の第１６実施例装置を示す模式的正面図である。It is a typical front view which shows the 16th Example apparatus of this invention. 図４１に示す第１６実施例装置における伝熱管の他の実施例を部分的に示す一部拡大斜視図である。FIG. 42 is a partially enlarged perspective view partially showing another embodiment of the heat transfer tube in the apparatus of the sixteenth embodiment shown in FIG. 41. 同じく第１６実施例装置における伝熱管の別の実施例を部分的に示す正面図である。It is a front view which shows partially another Example of the heat exchanger tube in a 16th Example apparatus similarly. 同じく第１６実施例装置における伝熱管のさらに他の実施例を部分的に示す斜視図である。It is a perspective view which shows the other Example of the heat exchanger tube in a 16th Example apparatus partially partially similarly. 同じく第１６実施例装置における伝熱管のさらに別の実施例を部分的に示す平面図である。It is a top view which shows partially another Example of the heat exchanger tube in a 16th Example apparatus similarly. 本発明の第１７実施例装置を示す概略三面図で、（ａ）はその平面図、（ｂ）はその縦断側面図、（ｃ）は（ａ）のア−ア線上の横断平面図である。It is a schematic three-plane figure which shows the 17th Example apparatus of this invention, (a) is the top view, (b) is the vertical side view, (c) is a cross-sectional plan view on the AA line of (a). . 同じく第１６実施例装置および第１７実施例装置において任意に用いることが可能な各種フィンを部分的に示し、（ａ）はＩ型形状フィン、（ｂ）はＳ字型形状フィン、（ｃ）はコの字型形状フィンを示す斜視図である。Similarly, various fins that can be arbitrarily used in the sixteenth embodiment device and the seventeenth embodiment device are partially shown, (a) is an I-shaped fin, (b) is an S-shaped fin, (c) FIG. 3 is a perspective view showing a U-shaped fin. 同じくプレートフィンの構造を示す断面図で、（ａ）はプレートフィンに貫孔を設けたもの、（ｂ）および（ｃ）はルーバーを設けたもの、（ｄ）はピンフィンを設けたもの、（ｅ）は凹凸を設けたものをそれぞれ示す。Similarly, it is sectional drawing which shows the structure of a plate fin, (a) what provided the through-hole in the plate fin, (b) and (c) what provided the louver, (d) what provided the pin fin, e) shows the thing which provided the unevenness | corrugation, respectively. 本発明の第１８実施例装置を示す縦断側面図である。It is a vertical side view which shows the 18th Example apparatus of this invention. 図４９のル−ル線上の横断平面図である。FIG. 50 is a transverse plan view on the rule line of FIG. 49. 図４９のオ−オ線上の縦断正面図である。FIG. 50 is a longitudinal front view on the line of FIG. 49. 本発明の第１９実施例装置を示す縦断側面図である。It is a vertical side view which shows the 19th Example apparatus of this invention. 図５２のワ−ワ線上の横断平面図である。FIG. 53 is a cross-sectional plan view on the wire line of FIG. 52. 図５２のカ−カ線上の縦断正面図である。FIG. 53 is a longitudinal front view on the car line in FIG. 52. 同じく第１８実施例装置および第１９実施例装置における伝熱管単体の一例を示す斜視図である。It is a perspective view which similarly shows an example of the heat exchanger tube in 18th Example apparatus and 19th Example apparatus similarly. 同じく伝熱管単体の他の例を示す斜視図である。It is a perspective view which similarly shows the other example of a heat exchanger tube single-piece | unit. 本発明の第１９実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows a 19th Example apparatus of this invention. 図５７のヨ−ヨ線上の横断平面図である。It is a cross-sectional plan view on the yo-yo line of FIG. 図５７のタ−タ線上の縦断正面図である。FIG. 58 is a longitudinal front view on the tar line of FIG. 57. 本発明の第２０実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows a 20th Example apparatus of this invention. 図６０のレ−レ線上の横断平面図である。FIG. 61 is a transverse plan view on the rail line of FIG. 60. 本発明の第２１実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows a 21st Example apparatus of this invention. 図６２のソ−ソ線上の横断平面図である。FIG. 63 is a cross-sectional plan view on the source line of FIG. 62. 本発明の第２２実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows a 22nd Example apparatus of this invention. 図６４のツ−ツ線上の横断平面図である。FIG. 65 is a transverse plan view on the toe line of FIG. 64. 図６４のネ−ネ線上の縦断正面図である。FIG. 67 is a longitudinal front view on the lane line of FIG. 64. 本発明の第２３実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows the apparatus of 23rd Example of this invention. 図６７のナ−ナ線上の縦断正面図である。FIG. 68 is a longitudinal sectional front view on the null line of FIG. 67. 本発明の第２４実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows a part of apparatus of 24th Example of this invention. 図６９のラ−ラ線上の横断平面図である。FIG. 70 is a cross-sectional plan view on the roller line of FIG. 69. 図６９のム−ム線上の縦断正面図である。FIG. 70 is a longitudinal front view on the moo line of FIG. 69. 本発明の第２５実施例装置を一部省略して示す縦断側面図である。It is a vertical side view which abbreviate | omits and shows a part of apparatus of 25th Example of this invention. 図７２のウーウ線上の横断平面図である。FIG. 73 is a transverse plan view on the Wu line of FIG. 72. 図７２のノ−ノ線上の縦断正面図である。FIG. 73 is a longitudinal front view on the non-line of FIG. 72. 図１〜図３に示す実施例装置におけるＥＧＲガス配管の壁面の断面構造の一例を示す部分断面図である。It is a fragmentary sectional view which shows an example of the cross-section of the wall surface of EGR gas piping in the Example apparatus shown in FIGS. 同じく図１〜図３に示す実施例装置における冷却配管（伝熱管）の壁面の断面構造の一例を示す部分断面図である。It is a fragmentary sectional view which shows an example of the cross-section of the wall surface of the cooling pipe (heat exchanger tube) in the Example apparatus similarly shown in FIGS.

符号の説明Explanation of symbols

１、１１、２１、３１、４１、１０１、２０１、２０１−１、２０１−２、２０１−３、２０１−４、２０１−５、３０１、３０１−１、５０１、５０１ａ、６０１、６１１、６２１、６３１、６４１、６５１、６６１ ＥＧＲガス冷却装置２、１２、２２、３２、４２、１０２、１１２、２０３、２０３−１、３０２、４０３、４０３−１、５０２、５０２ａ、６０２、６１１、６２１、６３１、６４１、６５１、６６１ ＥＧＲガス配管
３、２３ 冷却配管
４−１、４−２、１４−１、１４−２、２４−１、２４−２、３４、４４、１０４−１、１０４−２、１１４、２０２−１、２０２−２、２０２−３、２０２−４、２０２−５、２０２−６、２０２−７、２０２−８、２０２−９、２０２−１０、２０２−１１、２０２−１２、３０４−１、３０４−２、４０２、４０２−１、５０４−１、５０４−２、５０４ａ−１、５０４ａ−２、６５４−１、６５４−２、６６４−１、６６４−２ 冷却ジャケット
１３−１、１３−２ フィン付きチューブ
２５、１０３−１、１１３−１、２０４−１、２０４−２、２０４−３、２０４−３、２０４−４、２０４−５、２０４−６、５０５、５０５−１、５０５−２、５０５−３、５０５−４、５０５−５、６２５ プレートフィン
２５−１ バーリング壁
２５−２、６２５−２、貫孔
２５−３、２５−４、６２５−３、６２５−４ ルーバー
２５−５ ピンフィン
２５−６ 凹凸
３３、４３、 偏平チューブ
４５ａ、４５ｂ、２０４ａ−１、２０４ａ−２、２０４ａ−３ 波板
１０３、１１３ コア
１０３−３、１１３−３ 突出筒体
２０５、２０５−１、２０５−２、２０５−３ フレキ成形部
２０６ 胴管
３０５−６、３０５−７、３０５−８、３０５−９、３０５−１０ チャンネルフィン
Ｐ１ 流入口
Ｐ２ 流出口
1, 11, 21, 31, 41, 101, 201, 201-1, 201-2, 201-3, 201-4, 201-5, 301, 301-1, 501, 501a, 601, 611, 621, 631, 641, 651, 661 EGR gas cooling device 2, 12, 22, 32, 42, 102, 112, 203, 203-1, 302, 403, 403-1, 502, 502a, 602, 611, 621, 631 641, 651, 661 EGR gas piping 3, 23 Cooling piping 4-1, 4-2, 14-1, 14-2, 24-1, 24-2, 34, 44, 104-1, 104-2, 114, 202-1, 202-2, 202-3, 202-4, 202-5, 202-6, 202-7, 202-8, 202-9, 202-10, 202-11, 202-12, 304 1, 304-2, 402, 402-1, 504-1, 504-2, 504a-1, 504a-2, 654-1, 654-2, 664-1, 664-2 Cooling jackets 13-1, 13 -2 finned tube 25, 103-1, 113-1, 204-1, 204-2, 204-3, 204-3, 204-4, 204-5, 204-6, 505, 505-1, 505 -2, 505-3, 505-4, 505-5, 625 Plate fin 25-1 Burring wall 25-2, 625-2, Through hole 25-3, 25-4, 625-3, 625-4 Louver 25 -5 Pin fin 25-6 Concavities and convexities 33, 43, flat tubes 45a, 45b, 204a-1, 204a-2, 204a-3 Corrugated plates 103, 113 Cores 103-3, 113-3 Projecting cylinders 205, 205 -1, 205-2, 205-3 Flexible forming portion 206 Trunk tube 305-6, 305-7, 305-8, 305-9, 305-10 Channel fin P1 Inlet P2 Outlet

Claims (37)

ガス配管に、該配管のガス流れ方向に対して直角に交差する多数の冷却配管が、該各配管の両管端が外部に開口するごとく当該ガス配管の外周壁を貫通して固着配列され、さらに前記冷却媒体配管群の管軸方向両側のガス配管外面またはガス配管外面全体に、冷却媒体の流入出口を有する冷却ジャケットが固着され、前記冷却配管内を通流する冷却媒体によって前記ガス配管内のガスが冷却される構成となしたことを特徴とするガス冷却装置。 A large number of cooling pipes that intersect the gas pipe at right angles to the gas flow direction of the pipes are fixedly arranged through the outer peripheral wall of the gas pipes so that both pipe ends open to the outside, Further, a cooling jacket having an inflow / outlet of the cooling medium is fixed to the outer surface of the gas pipe on both sides in the pipe axis direction of the cooling medium pipe group or the entire outer surface of the gas pipe. A gas cooling device characterized in that the gas is cooled. 前記冷却配管は、その外周にスパイラル状もしくはディスク状のフィンを有することを特徴とする請求項１に記載のガス冷却装置。 The gas cooling device according to claim 1, wherein the cooling pipe has spiral or disk-shaped fins on an outer periphery thereof. 前記冷却配管が固着配列された熱交換領域のガス配管内に、当該ガス配管内のガス流に平行で前記冷却配管に直角なプレートフィンを少なくとも１枚有することを特徴とする請求項１又は２に記載のガス冷却装置。 The gas pipe in the heat exchange region in which the cooling pipes are fixedly arranged has at least one plate fin parallel to the gas flow in the gas pipe and perpendicular to the cooling pipe. The gas cooling device described in 1. 前記プレートフィンの冷却配管が挿入される貫孔には、バーリング壁が設けられていることを特徴とする請求項３に記載のガス冷却装置。 The gas cooling device according to claim 3, wherein a burring wall is provided in a through hole into which the cooling pipe of the plate fin is inserted. 前記プレートフィンには、ルーバー、貫孔、ピンフィン、凹凸のうち、少なくとも一つが設けられていることを特徴とする請求項４に記載のガス冷却装置。 The gas cooling device according to claim 4, wherein the plate fin is provided with at least one of a louver, a through hole, a pin fin, and unevenness. ガス配管に、１枚の板にバーリング加工を施して多数の突出筒体を同一位相で形成したプレートフィンを複数枚重ねて前記各突出筒体部を溶接又はろう付けにて接合することにより多数のチューブ状冷却媒体流路が形成されたコアが、該コアのチューブ状冷却媒体流路が該配管のガス流れ方向に対して直角に交差し、かつ各チューブ状冷却媒体流路の端部が外部に開口するごとく当該ガス配管の外周壁を貫通して固着配列され、さらに前記チューブ状冷却媒体流路群の両開口端側のガス配管外面又はガス配管外面全体に、冷却媒体の流入出口を有する冷却ジャケットが固着され、前記チューブ状冷却媒体流路内を通流する冷却媒体によって前記ガス配管内のガスが冷却される構成となしたことを特徴とするガス冷却装置。 A gas pipe is subjected to burring on a single plate, and a plurality of plate fins in which a large number of protruding cylindrical bodies are formed in the same phase are overlapped, and the protruding cylindrical body portions are joined together by welding or brazing. The core in which the tubular cooling medium flow path is formed, the tubular cooling medium flow path of the core intersects at right angles to the gas flow direction of the pipe, and the end of each tubular cooling medium flow path is As it opens to the outside, it is fixedly arranged through the outer peripheral wall of the gas pipe. A gas cooling apparatus comprising: a cooling jacket having a fixed structure, wherein the gas in the gas pipe is cooled by a cooling medium flowing through the tubular cooling medium flow path. 冷却媒体の流入口もしくは流出口のいずれかを備え、相対する冷却ジャケットの間にあって、ガスの流れ方向に対して直角に交差する伝熱管を、間隔を保持して複数配置したガス冷却装置において、前記冷却ジャケットによって覆われている部分を除く隣接する壁面に、ガスの流れ方向に対して平行に、もしくは交差して複数のフレキ成形部及び／又は複数の放熱用フィンを有することを特徴とするガス冷却装置。 In a gas cooling apparatus having either a cooling medium inlet or an outlet and having a plurality of heat transfer tubes arranged at regular intervals between opposing cooling jackets and intersecting at right angles to the gas flow direction, An adjacent wall surface excluding a portion covered by the cooling jacket has a plurality of flexible molding portions and / or a plurality of heat radiation fins parallel to or intersecting with the gas flow direction. Gas cooling device. 前記間隔を保持して複数配置される伝熱管の外周面に、ガスの流れ方向に対して平行に、複数のプレートフィンを接合することを特徴とする請求項７に記載のガス冷却装置。 The gas cooling device according to claim 7, wherein a plurality of plate fins are joined in parallel to the gas flow direction on the outer peripheral surface of a plurality of the heat transfer tubes arranged while maintaining the interval. 前記伝熱管に接合されるプレートフィンの他端を、前記フレキ成形部に挿入し、挟持させることを特徴とする請求項７又は８に記載のガス冷却装置。 9. The gas cooling device according to claim 7, wherein the other end of the plate fin joined to the heat transfer tube is inserted into the flexible molding portion and clamped. 前記プレートフィンには、波形、うねりを有した矩形の波形、貫孔、凹凸、ルーバー等の加工が施されていることを特徴とする請求項７乃至９のいずれか１項に記載のガス冷却装置。 The gas cooling according to any one of claims 7 to 9, wherein the plate fin is processed into a corrugated shape, a corrugated rectangular corrugated shape, a through hole, an unevenness, a louver, and the like. apparatus. 前記ガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付けであることを特徴とする請求項７乃至１０のいずれか１項に記載のガス冷却装置。 The gas cooling device according to any one of claims 7 to 10, wherein the joining means of each part constituting the gas cooling device is welding and / or brazing. 冷却媒体の流入口若しくは流出口のいずれかを有し、相対する冷却ジャケットの間にあって、ガスの流れ方向に対して直角に交差する複数の偏平伝熱管を、間隔を保持して配置したガス冷却装置であって、前記偏平伝熱管の偏平した外表面に、ガスの流れ方向に対して平行に、多数のチャンネル形状のフィンを設けたことを特徴とするガス冷却装置。 Gas cooling in which a plurality of flat heat transfer tubes having either an inlet or an outlet for a cooling medium and disposed between opposing cooling jackets and perpendicular to the gas flow direction are arranged at intervals. An apparatus for cooling a gas, wherein a plurality of channel-shaped fins are provided on a flat outer surface of the flat heat transfer tube in parallel with a gas flow direction. 前記フィンが前記偏平伝熱管の全長にわたりもしくは長さ方向に小型分割形状であることを特徴とする請求項１２に記載のガス冷却装置。 The gas cooling device according to claim 12, wherein the fin has a small divided shape over the entire length of the flat heat transfer tube or in the length direction. 前記フィンが切り起こし付き帯状フィンであることを特徴とする請求項１２又は１３に記載のガス冷却装置。 The gas cooling device according to claim 12 or 13, wherein the fin is a band-shaped fin with a cut and raised portion. 前記フィンには、ルーバー、貫孔、凹凸、波形等が設けられることを特徴とする請求項１２乃至１４のいずれか１項に記載のガス冷却装置。 The gas cooling device according to any one of claims 12 to 14, wherein the fin is provided with a louver, a through hole, an unevenness, a corrugation, and the like. 前記フィンを偏平伝熱管同士若しくは偏平伝熱管と冷却装置外壁との間において圧接せしめたのち、接合することを特徴とする請求項１２乃至５のいずれか１項に記載のガス冷却装置。 6. The gas cooling device according to claim 12, wherein the fins are joined after being brought into pressure contact with each other between the flat heat transfer tubes or between the flat heat transfer tubes and the outer wall of the cooling device. 前記フィンを含むガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付であることを特徴とする請求項１２至１６のいずれか１項に記載のガス冷却装置。 The gas cooling device according to any one of claims 12 to 16, wherein a joining means of each part constituting the gas cooling device including the fin is welding and / or brazing. 冷却媒体の流入口若しくは流出口のいずれかを有し、相対する冷却ジャケットの間にあって、ガスの流れ方向に対して直角に交差する複数の偏平伝熱管を、間隔を保持して複数配置したガス冷却装置であって、前記間隔を保持して配置した偏平伝熱管の偏平した外表面に、略直角でかつガスの流れ方向に対して平行に多数のフィンを設け、これを交互に介装させて固定することによってコアを形成せしめたことを特徴とするガス冷却装置。 A gas having either a cooling medium inlet or an outlet and a plurality of flat heat transfer tubes arranged between the opposing cooling jackets and intersecting at right angles to the gas flow direction at intervals. A cooling device, wherein a plurality of fins are provided on a flat outer surface of the flat heat transfer tube arranged at a predetermined distance so as to be substantially perpendicular and parallel to the gas flow direction, and these fins are alternately interposed. A gas cooling device characterized in that a core is formed by fixing. 前記コアのアスペクト比が、偏平伝熱管長さ／ＥＧＲガス流路の長さ比において、１：１．５〜１：７であることを特徴とする請求項１８に記載のガス冷却装置。 19. The gas cooling device according to claim 18, wherein the aspect ratio of the core is 1: 1.5 to 1: 7 in a flat heat transfer tube length / EGR gas flow channel length ratio. 前記コアのアスペクト比が、偏平伝熱管長さ／ＥＧＲガス流路の長さ比において、１：２．５〜１：５であることを特徴とする請求項１８に記載のガス冷却装置。 The gas cooling device according to claim 18, wherein the aspect ratio of the core is 1: 2.5 to 1: 5 in the ratio of the flat heat transfer tube length / the length of the EGR gas flow path. 前記偏平伝熱管単体が、一体もの、若しくは複数の偏平管で構成されていることを特徴とする請求項１乃至２０のいずれか１項に記載のガス冷却装置。 The gas cooling device according to any one of claims 1 to 20, wherein the flat heat transfer tube alone is constituted by a single member or a plurality of flat tubes. 前記一体ものの偏平伝熱管単体は、内部に１〜複数個の補強用リブを有することを特徴とする請求項２１に記載のガス冷却装置。 The gas cooling device according to claim 21, wherein the single unitary flat heat transfer tube has one to a plurality of reinforcing ribs therein. 前記偏平伝熱管の偏平した外表面に固定されるフィンが、ガスの流れ方向に蛇行するように固定されていることを特徴とする請求項１８乃至２２のいずれか１項に記載のガス冷却装置。 The gas cooling device according to any one of claims 18 to 22, wherein the fin fixed to the flat outer surface of the flat heat transfer tube is fixed so as to meander in the gas flow direction. . 前記偏平伝熱管単体は、ガスの流れ方向に波型に変形して形成され、その外表面に固定されるフィンも同様に波型に形成されることを特徴とする請求項１８乃至２２のいずれか１項に記載のガス冷却装置。 The flat heat transfer tube itself is formed in a corrugated shape in the gas flow direction, and fins fixed to the outer surface thereof are also formed in a corrugated shape. The gas cooling device according to claim 1. 前記フィンが、コルゲートフィンであることを特徴とする請求項１８乃至２４のいずれか１項に記載のガス冷却装置。 The gas cooling device according to any one of claims 18 to 24, wherein the fin is a corrugated fin. 前記フィンには、ルーバー、貫孔、ピンフィン、凹凸等が設けられることを特徴とする請求項１８乃至２５のいずれか１項に記載のガス冷却装置。 The gas cooling device according to any one of claims 18 to 25, wherein the fin is provided with a louver, a through hole, a pin fin, an unevenness and the like. 前記ＥＧＲガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付であることを特徴とする請求項１８乃至２６のいずれか１項に記載のガス冷却装置。 27. The gas cooling apparatus according to any one of claims 18 to 26, wherein a joining means of each part constituting the EGR gas cooling apparatus is welding and / or brazing. 冷却媒体の流入口若しくは流出口のいずれかを有し、相対する冷却ジャケットの間にあって、ガスの流れ方向に対して直角に交差する伝熱管を、間隔を保持して複数配置したガス冷却装置において、該伝熱管の断面形状をガスの流れ方向後方に向かって、その幅を次第に拡張せしめた楔形形状とし、該楔形形状の伝熱管内を通流する冷却媒体によってガスを冷却することを特徴とするガス冷却装置。 In a gas cooling apparatus in which a plurality of heat transfer tubes that have either an inlet or an outlet for a cooling medium and that intersect between the opposing cooling jackets and intersect at right angles to the gas flow direction are arranged at intervals. The cross-sectional shape of the heat transfer tube is a wedge shape whose width is gradually expanded toward the rear in the gas flow direction, and the gas is cooled by a cooling medium flowing through the heat transfer tube having the wedge shape. Gas cooling device. 前記楔形形状の伝熱管同士、若しくは該伝熱管とガス配管との間隙に、ガスの流れ方向と平行してプレートフィンが固着されてなることを特徴とする請求項２８に記載のガス冷却装置。 29. The gas cooling apparatus according to claim 28, wherein plate fins are fixed to the wedge-shaped heat transfer tubes or in the gap between the heat transfer tube and the gas pipe in parallel with the gas flow direction. 前記プレートフィンには貫孔、ルーバー、ピンフィン、凹凸等が設けられることを特徴とする請求項２８又は２９に記載のガス冷却装置。 30. The gas cooling device according to claim 28 or 29, wherein the plate fin is provided with a through hole, a louver, a pin fin, an unevenness and the like. 前記プレートフィンを含む前記ガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付であることを特徴とする請求項２８乃至３０のいずれか１項に記載のガス冷却装置。 The gas cooling device according to any one of claims 28 to 30, wherein a joining means of each part constituting the gas cooling device including the plate fin is welding and / or brazing. ガス配管内を流れるガスの流れ方向に対して直角に交差する伝熱管が、間隔を保持して複数配置されたガス冷却装置において、該伝熱管はその両管端を開口した状態で前記ガス配管の外周壁を貫通して固着配列され、該固着配列された伝熱管列群の管軸方向両端におけるガス配管の上下若しくは両側面又は全周に渡るガス配管外周面に、冷却媒体の流入口若しくは流出口のいずれかを有する冷却ジャケットが固着され、該冷却ジャケットの流入口から流入した冷却媒体が、前記伝熱管列群を経由して他の冷却ジャケット流出口から系外に流去する冷却媒体流路にあって、隣接する前記伝熱管列群境界の冷却媒体の流れ方向交互に堰を設け、該伝熱管内を通流する冷却媒体の流路と流速とを任意に制御しながら、該伝熱管列群を通流する冷却媒体によってガスを冷却することを特徴とするガス冷却装置。 In the gas cooling apparatus in which a plurality of heat transfer tubes intersecting at right angles to the flow direction of the gas flowing in the gas piping are arranged at intervals, the heat transfer tubes are opened in the state where both tube ends are opened. Fixed to the outer peripheral wall of the heat transfer tube array, and the cooling medium inflow or Cooling medium to which a cooling jacket having one of the outlets is fixed, and the cooling medium flowing in from the inlet of the cooling jacket flows out from the other cooling jacket outlet through the heat transfer tube group. In the flow path, weirs are provided alternately in the flow direction of the cooling medium at the boundary between adjacent heat transfer tube row groups, and the flow path and flow rate of the cooling medium flowing through the heat transfer pipe are arbitrarily controlled, Coolant flowing through heat transfer tube group Gas cooling apparatus characterized by cooling the gas by. 前記伝熱管列群を形成する複数の伝熱管の形状が円筒状チューブ管、長円形の偏平管、断面楔形形状に加工された金属管等であることを特徴とする請求項３２に記載のガス冷却装置。 The gas according to claim 32, wherein the plurality of heat transfer tubes forming the heat transfer tube row group are a cylindrical tube tube, an oblong flat tube, a metal tube processed into a wedge-shaped cross section, and the like. Cooling system. 前記伝熱管列群を形成するそれぞれの伝熱管同士、若しくは該伝熱管とガス配管外壁の内周面との間隙に、ガスの流れ方向に平行して、プレートフィンを固着してなることを特徴とする請求項３２又は３３に記載のガス冷却装置。 A plate fin is fixed in parallel to the gas flow direction between the heat transfer tubes forming the heat transfer tube array group or between the heat transfer tubes and the inner peripheral surface of the gas pipe outer wall. The gas cooling device according to claim 32 or 33. 前記プレートフィンには貫孔、ルーバー、ピンフィン、凹凸等が設けられることを特徴とする請求項３２乃至３４のいずれか１項に記載のガス冷却装置。 The gas cooling device according to any one of claims 32 to 34, wherein the plate fin is provided with a through hole, a louver, a pin fin, unevenness and the like. 前記プレートフィンを含むガス冷却装置を構成する各部の接合手段が、溶接及び／又はろう付であることを特徴とする請求項３２乃至３５のいずれか１項に記載のガス冷却装置。 36. The gas cooling apparatus according to any one of claims 32 to 35, wherein a joining means of each part constituting the gas cooling apparatus including the plate fin is welding and / or brazing. 前記ガス配管または冷却配管あるいは伝熱管の壁面に凹および／または凸を形成したことを特徴とする請求項１、６、７、１２、１８、２８、３２のいずれか１項に記載のガス冷却装置。 The gas cooling according to any one of claims 1, 6, 7, 12, 18, 28, and 32, wherein a recess and / or a protrusion is formed on a wall surface of the gas pipe, the cooling pipe, or the heat transfer pipe. apparatus.
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