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JP2011190708A - Engine exhaust gas heat exchanger and energy supply device using the same - Google Patents

Engine exhaust gas heat exchanger and energy supply device using the same Download PDF

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Publication number
JP2011190708A
JP2011190708A JP2010055575A JP2010055575A JP2011190708A JP 2011190708 A JP2011190708 A JP 2011190708A JP 2010055575 A JP2010055575 A JP 2010055575A JP 2010055575 A JP2010055575 A JP 2010055575A JP 2011190708 A JP2011190708 A JP 2011190708A
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Prior art keywords
exhaust gas
heat exchanger
engine
passage
pipe
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Pending
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JP2010055575A
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Japanese (ja)
Inventor
Hiroshi Azuma
洋志 東
Kosuke Matsuura
航典 松浦
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Yanmar Co Ltd
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Yanmar Co Ltd
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Publication date
Application filed by Yanmar Co Ltd filed Critical Yanmar Co Ltd
Priority to JP2010055575A priority Critical patent/JP2011190708A/en
Priority to EP11753434.7A priority patent/EP2546491B1/en
Priority to US13/583,774 priority patent/US8904772B2/en
Priority to CA2792916A priority patent/CA2792916A1/en
Priority to ES11753434.7T priority patent/ES2575583T3/en
Priority to PCT/JP2011/055633 priority patent/WO2011111776A1/en
Publication of JP2011190708A publication Critical patent/JP2011190708A/en
Pending legal-status Critical Current

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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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/103—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 one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/24—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by constructional aspects of converting apparatus
    • F01N3/28—Construction of catalytic reactors
    • F01N3/2882—Catalytic reactors combined or associated with other devices, e.g. exhaust silencers or other exhaust purification devices
    • F01N3/2889—Catalytic reactors combined or associated with other devices, e.g. exhaust silencers or other exhaust purification devices with heat exchangers in a single housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • 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
    • F28D7/10—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 one within the other, e.g. concentrically
    • F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N2470/00—Structure or shape of exhaust gas passages, pipes or tubes
    • F01N2470/18—Structure or shape of exhaust gas passages, pipes or tubes the axis of inlet or outlet tubes being other than the longitudinal axis of apparatus
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Health & Medical Sciences (AREA)
  • Toxicology (AREA)
  • Exhaust Gas After Treatment (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide an engine exhaust gas heat exchanger having nozzle holes which improve the heat exchange efficiency in the engine exhaust gas heat exchanger which makes the exhaust gas collide with a coolant passage through the nozzle holes. <P>SOLUTION: An engine exhaust gas heat exchanger serves as a heat exchanger 2 between the exhaust gas and the coolant of the engine, and includes the nozzle holes 30 facing a coolant passage 20 in the circumferential direction of an exhaust gas passage and in the exhaust gas flowing direction so that the whole amount of the exhaust gas collide with the coolant passage 20. In the engine exhaust gas heat exchanger, each nozzle hole 30 is formed into a shape to be gradually reduced in an area, through which the exhaust gas passes, from an inlet to an outlet thereof. In this engine exhaust gas heat exchanger, the area, through which the exhaust gas flows, and an outlet area are formed equal to each other from a middle part of each nozzle hole 30. In this engine exhaust gas heat exchanger, a surface of the coolant passage 20, with which the exhaust gas collides, is formed with a groove by machining. The energy supply device uses the catalyst containing engine exhaust gas heat exchanger in an exhaust gas passage of the engine. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

本発明は、エンジン駆動式空気調和機やコージェネレーションシステムなどで使用される触媒内蔵型のエンジン排気ガス熱交換器に関するものである。   The present invention relates to an engine exhaust gas heat exchanger with a built-in catalyst used in an engine driven air conditioner, a cogeneration system, and the like.

従来より、エンジンの排気ガスと冷却水との間の熱交換器において、排気ガス通路の周方向および排気ガス流れ方向に冷却水通路と対向した噴孔を複数設けて排気ガス全量を冷却水通路に衝突させるようにした構成が公知である（特許文献１，２参照）。   Conventionally, in a heat exchanger between exhaust gas and cooling water of an engine, a plurality of nozzle holes facing the cooling water passage are provided in the circumferential direction of the exhaust gas passage and in the exhaust gas flow direction so that the entire amount of the exhaust gas is supplied to the cooling water passage. The structure which made it collide with is known (refer patent document 1, 2).

特許第４３２４２１６号公報Japanese Patent No. 4324216 特許第４３２４２１９号公報Japanese Patent No. 4324219

しかし、上記従来のエンジン排気ガス熱交換器の場合、噴孔は、単に円筒状に開口されているだけで、その具体的形状が開示されていない。   However, in the case of the conventional engine exhaust gas heat exchanger, the injection hole is merely opened in a cylindrical shape, and its specific shape is not disclosed.

本発明は、係る実情に鑑みてなされたものであって、排気ガスを噴孔から冷却水通路に衝突させるエンジン排気ガス熱交換器において、熱交換効率の向上を図ることができる噴孔を有するエンジン排気ガス熱交換器を提供することを目的としている。   The present invention has been made in view of such circumstances, and has an injection hole capable of improving heat exchange efficiency in an engine exhaust gas heat exchanger that causes exhaust gas to collide with a cooling water passage from the injection hole. The object is to provide an engine exhaust gas heat exchanger.

上記課題を解決するための本発明のエンジン排気ガス熱交換器は、エンジンの排気ガスと冷却水との間の熱交換器であって、排気ガス通路の周方向および排気ガス流れ方向に冷却水通路と対向した噴孔を設けて排気ガス全量を冷却水通路に衝突させるエンジン排気ガス熱交換器において、各噴孔を入口から出口にかけて排気ガスの通過面積が漸減する形状としたものである。また、上記エンジン排気ガス熱交換器において、各噴孔の途中部から排気ガスの通過面積を出口面積と等しくしたものである。さらに、上記エンジン排気ガス熱交換器において、冷却水通路の排気ガス衝突面に溝加工を行ったものである。   An engine exhaust gas heat exchanger according to the present invention for solving the above-mentioned problems is a heat exchanger between the exhaust gas and cooling water of an engine, and the cooling water is disposed in the circumferential direction of the exhaust gas passage and in the exhaust gas flow direction. In an engine exhaust gas heat exchanger in which an injection hole facing the passage is provided so that the entire exhaust gas collides with the cooling water passage, the passage area of the exhaust gas gradually decreases from the inlet to the outlet. In the engine exhaust gas heat exchanger, the exhaust gas passage area from the middle of each nozzle hole is made equal to the outlet area. Furthermore, in the engine exhaust gas heat exchanger, the exhaust gas collision surface of the cooling water passage is grooved.

また、上記課題を解決するための本発明のエネルギー供給装置は、エンジン駆動式ヒートポンプおよびコージェネレーションなどのエネルギー供給装置において、上記エンジン排気ガス熱交換器をエンジンの排気ガス経路に使用したものである。   In addition, an energy supply device of the present invention for solving the above-described problems is the use of the engine exhaust gas heat exchanger in an engine exhaust gas path in an energy supply device such as an engine-driven heat pump and cogeneration. .

以上述べたように、本発明によると、同一噴孔通過流速において、排気ガスの圧力損失を低減できるので、熱交換器の設計許容圧力損失値に対する噴孔通過流速をあげることができ、平均熱通過率を上昇し熱交換量を増加できる。   As described above, according to the present invention, the pressure loss of the exhaust gas can be reduced at the same injection hole passage flow velocity, so that the injection hole passage flow velocity with respect to the design allowable pressure loss value of the heat exchanger can be increased, and the average heat The passage rate can be increased and the amount of heat exchange can be increased.

（ａ）は本発明に係るエンジン排気ガス熱交換器の噴孔を示す拡大断面図、（ｂ）は噴孔の他の形状を示す拡大断面図である。(A) is an expanded sectional view which shows the nozzle hole of the engine exhaust gas heat exchanger which concerns on this invention, (b) is an expanded sectional view which shows the other shape of a nozzle hole. （ａ）は本発明に係る触媒内蔵型エンジン排気ガス熱交換器の断面図、（ｂ）は同図（ａ）のI-I 線断面図である。(A) is sectional drawing of the catalyst exhaust type engine exhaust gas heat exchanger which concerns on this invention, (b) is the II sectional view taken on the line of the same figure (a). 図２に示す触媒内蔵型エンジン排気ガス熱交換器を設けたエンジンの冷却水回路図である。FIG. 3 is a circuit diagram of a cooling water circuit of an engine provided with a catalyst built-in engine exhaust gas heat exchanger shown in FIG. 2.

本発明の実施の形態を図に基づいて説明する。   Embodiments of the present invention will be described with reference to the drawings.

図１は本発明に係るエンジン排気ガス熱交換器１の噴孔３０の構成を示し、図２は同噴孔３０を設けた本発明に係るエンジン排気ガス熱交換器１を示し、図３は同エンジン排気ガス熱交換器１を設けたガスエンジン１１の冷却水回路図の一例を示している。   FIG. 1 shows the configuration of the nozzle hole 30 of the engine exhaust gas heat exchanger 1 according to the present invention, FIG. 2 shows the engine exhaust gas heat exchanger 1 according to the present invention provided with the nozzle hole 30, and FIG. An example of a cooling water circuit diagram of a gas engine 11 provided with the engine exhaust gas heat exchanger 1 is shown.

すなわち、このエンジン排気ガス熱交換器１は、熱交換器２の冷却水通路２０と対向した噴孔３０を排気ガス噴出管３１に設けて、排気ガス全量を噴孔３０から冷却水通路２０に衝突させるように構成されており、噴孔３０を入口から出口にかけて排気ガスの通過面積が漸減する形状としている。   That is, the engine exhaust gas heat exchanger 1 is provided with an injection hole 30 facing the cooling water passage 20 of the heat exchanger 2 in the exhaust gas injection pipe 31, and the entire amount of exhaust gas is transferred from the injection hole 30 to the cooling water passage 20. It is comprised so that it may collide, and it is set as the shape where the passage area of exhaust gas reduces gradually from the inlet 30 to an exit.

噴孔３０の形状としては、図１（ａ）に示すように、排気ガス噴出管３１の厚み方向全体にわたって漸減する円錐台形状に穿孔されたものであってもよいし、図１（ｂ）に示すように、排気ガス噴出管３１の厚み方向の途中までは入口側から漸減する円錐台形状に穿孔され、この途中から出口側と同じ直径の円柱状に穿孔されものであってもよい。   As the shape of the nozzle hole 30, as shown in FIG. 1 (a), it may be perforated into a truncated cone shape that gradually decreases over the entire thickness direction of the exhaust gas ejection pipe 31, or FIG. 1 (b). As shown in FIG. 4, the exhaust gas ejection pipe 31 may be perforated into a truncated cone shape that gradually decreases from the inlet side until the middle in the thickness direction, and may be perforated into a cylindrical shape having the same diameter as the outlet side from this middle.

このように漸減する形状とした噴孔３０にしたエンジン排気ガス熱交換器１の場合、同一噴孔通過流速において、排気ガスの圧力損失を低減できるので、熱交換器２の設計許容圧力損失値に対する噴孔通過流速をあげることができ、平均熱通過率を上昇し熱交換量を増加できる。   In the case of the engine exhaust gas heat exchanger 1 having the nozzle hole 30 having a gradually decreasing shape as described above, the pressure loss of the exhaust gas can be reduced at the same nozzle hole passage flow velocity. Therefore, the design allowable pressure loss value of the heat exchanger 2 Can increase the flow rate through the nozzle hole, increase the average heat passage rate, and increase the amount of heat exchange.

次に、このような噴孔３０を有する排気ガス噴出管３１を設けたエンジン排気ガス熱交換器１について説明する。   Next, the engine exhaust gas heat exchanger 1 provided with the exhaust gas ejection pipe 31 having such a nozzle hole 30 will be described.

エンジン排気ガス熱交換器１は、図２および図３に示すように、エンジン１１からサイレンサ１２へと向かう排気が、エンジン排気ガス熱交換器１内で、前室５、排気ガス浄化触媒（以下、単に触媒という。）４および単位排気ガス通路３ａ，３ｂ，３ｃを通過するように設けられ、かつ、エンジン１１の冷却水が、エンジン排気ガス熱交換器１の熱交換器２を通過してからエンジン１１に導入するように設けられている。エンジン１１を通過した後の冷却水は、ポンプ１３によって循環するように構成されている。また、冷却水は、サーモスタット１４によって温度管理することができるようになされており、三方弁１５によって、ラジエータ１６または熱交換器１７へと流れを切り替えることができるようになされている。   As shown in FIGS. 2 and 3, the engine exhaust gas heat exchanger 1 is configured such that the exhaust from the engine 11 to the silencer 12 flows into the front chamber 5, the exhaust gas purification catalyst (hereinafter referred to as “exhaust gas purification catalyst”). 4) and the unit exhaust gas passages 3a, 3b, 3c, and the cooling water of the engine 11 passes through the heat exchanger 2 of the engine exhaust gas heat exchanger 1. To be introduced into the engine 11. The cooling water after passing through the engine 11 is configured to circulate by a pump 13. Further, the temperature of the cooling water can be controlled by the thermostat 14, and the flow can be switched to the radiator 16 or the heat exchanger 17 by the three-way valve 15.

熱交換器２は、内筒管２１と、外筒管２２と、その両端に設けられた内蓋２１ａ，２１ｂおよび外蓋２２ａ，２２ｂとからなり、その間隙は、冷却水が通過する冷却水通路２０となされている。   The heat exchanger 2 includes an inner tube 21, an outer tube 22, inner lids 21 a and 21 b and outer lids 22 a and 22 b provided at both ends of the heat exchanger 2. A passage 20 is provided.

この熱交換器２は、他端部の外蓋２２ｂには、冷却水通路２０と連通する冷却水流入管２３が設けられており、一端部の外筒管２２には、冷却水通路２０と連通する冷却水流出管２４が設けられている。これにより、冷却水は、冷却水流入管２３から冷却水通路２０内へと導入され、熱交換器２の他端部側から一端部側へと流れた後、冷却水流出管２４から排水されるようになされている。   In the heat exchanger 2, the outer lid 22 b at the other end is provided with a cooling water inflow pipe 23 that communicates with the cooling water passage 20, and the outer cylinder pipe 22 at one end communicates with the cooling water passage 20. A cooling water outflow pipe 24 is provided. Thereby, the cooling water is introduced into the cooling water passage 20 from the cooling water inflow pipe 23, flows from the other end side to the one end side of the heat exchanger 2, and then drained from the cooling water outflow pipe 24. It is made like that.

また、熱交換器２は、一端部の内筒管２１および外筒管２２を貫通して内筒管２１内に連通する排気ガス流入管２５が設けられており、他端部の内筒管２１および外筒管２２を貫通して内筒管２１内に連通する排気ガス流出管２６が設けられている。これにより、排気ガスは、排気ガス流入管２５から内筒管２１内へと導入され、この内筒管２１内に形成された前室５、触媒４および３段の単位排気ガス通路３ａ、３ｂ、３ｃを通過した後、排気ガス流出管２６から排気されるように構成されている。   In addition, the heat exchanger 2 is provided with an exhaust gas inflow pipe 25 that penetrates the inner cylindrical pipe 21 and the outer cylindrical pipe 22 at one end and communicates with the inner cylindrical pipe 21, and the inner cylindrical pipe at the other end. An exhaust gas outflow pipe 26 that passes through the inner cylinder pipe 21 through the outer cylinder pipe 21 and the outer cylinder pipe 22 is provided. As a result, the exhaust gas is introduced from the exhaust gas inflow pipe 25 into the inner cylinder pipe 21, and the front chamber 5, the catalyst 4 and the three-stage unit exhaust gas passages 3 a, 3 b formed in the inner cylinder pipe 21. After passing through 3c, the exhaust gas outflow pipe 26 is exhausted.

前室５は、内筒管２１内に、この内筒管２１よりも若干小径の筒状で一端が曲面を形成しながら漸次的に縮径するように形成された管材５１を、内筒管２１との間に空隙Ｓを形成するように設けて構成されている。管材５１の縮径された側の一端は、熱交換器２の一端に設けられた内蓋２１ａに固定される。排気ガス流入管２５は、この管材５１内に連通するようになされている。この管材５１の他端は、触媒４および排気ガス噴出管３１を受挿接続するための筒状の接続部材５２が設けられている。この接続部材５２は、内筒管２１の内周面に接する筒状の本体５２ａ部分からさらに二段階に縮径して排気ガス噴出管接続部５２ｂ、触媒接続部５２ｃを形成するようになされている。最大径の本体５２ａの部分は、内筒管２１と管材５１との間に介在して、これら内筒管２１と管材５１との間に空隙Ｓを維持するように固定される。排気ガス噴出管接続部５２ｂは、その外側に排気ガス噴出管３１を受挿接続して内筒管２１と排気ガス噴出管３１との間に間隔ｄを形成するようになされている。触媒接続部５２ｃは、その内側に触媒４を受挿接続するようになされている。   The front chamber 5 includes a pipe member 51 formed in the inner tube 21 so as to be gradually reduced in diameter while forming a curved surface with a slightly smaller diameter than the inner tube 21. 21 is formed so as to form a gap S between the two. One end of the pipe member 51 on the reduced diameter side is fixed to an inner lid 21 a provided at one end of the heat exchanger 2. The exhaust gas inflow pipe 25 communicates with the pipe material 51. The other end of the pipe member 51 is provided with a cylindrical connection member 52 for receiving and connecting the catalyst 4 and the exhaust gas ejection pipe 31. The connecting member 52 is further reduced in diameter from the cylindrical main body 52a portion in contact with the inner peripheral surface of the inner cylindrical tube 21 to form an exhaust gas ejection pipe connecting portion 52b and a catalyst connecting portion 52c. Yes. The portion of the main body 52a having the maximum diameter is interposed between the inner tube 21 and the tube material 51, and is fixed so as to maintain a gap S between the inner tube 21 and the tube material 51. The exhaust gas ejection pipe connecting portion 52b is configured to receive and connect the exhaust gas ejection pipe 31 to the outside thereof so as to form a gap d between the inner tube 21 and the exhaust gas ejection pipe 31. The catalyst connection portion 52c is configured to receive and connect the catalyst 4 inside thereof.

単位排気ガス通路３ａは、上記接続部材５２の排気ガス噴出管接続部５２ｂに接続される排気ガス噴出管３１と、この排気ガス噴出管３１の下流側に設けられる接続部材３２とによって構成されている。   The unit exhaust gas passage 3 a is configured by an exhaust gas ejection pipe 31 connected to the exhaust gas ejection pipe connection portion 52 b of the connection member 52 and a connection member 32 provided on the downstream side of the exhaust gas ejection pipe 31. Yes.

排気ガス噴出管３１は、内筒管２１との間に間隙ｄを形成することが可能で、かつ、触媒４を内装可能な直径および長さの円筒状に形成されている。この排気ガス噴出管３１の周壁には、長手方向および周方向に沿って等間隔で複数の噴孔３０が設けられている。この噴孔３０は、上記したように、周壁の内側から外側に向かって漸減する円錐台形状に形成されている、または、排気ガス噴出管３１の厚み方向の途中までは入口側から漸減する円錐台形状に形成され、この途中から出口側と同じ直径の円筒状に形成されている。
また、排気ガス噴出管３１は、下流側端部が蓋体３１ａによって閉塞されている。この排気ガス噴出管３１は、内筒管２１の内周面との間で噴孔３０を邪魔しない位置に適宜に設けたリブ片３１ｂによって、内筒管２１内に固定される。また、このリブ片３１ｂは、排気ガス噴出管３１の内周面にも設けられ、この排気ガス噴出管３１に内装される触媒４を保持することができるようになされている。この触媒４を保持した状態で、触媒４と蓋体３１ａとの間には、熱交換器２の外筒管２２および内筒管２１と、この排気ガス噴出管３１とを貫通して温度計６が設けられている。触媒４は、排気ガス温度により浄化作用が有効に機能しないことがあるため温度管理をすることが望ましいが、この触媒４を通過直後の位置で温度計６によって温度測定することで、触媒４の浄化状態をある程度把握できることとなる。 The exhaust gas ejection pipe 31 is formed in a cylindrical shape having a diameter and a length capable of forming the gap d between the exhaust pipe 31 and the inner cylinder pipe 21 and capable of incorporating the catalyst 4 therein. A plurality of nozzle holes 30 are provided in the circumferential wall of the exhaust gas ejection pipe 31 at equal intervals along the longitudinal direction and the circumferential direction. As described above, the nozzle hole 30 is formed in a truncated cone shape that gradually decreases from the inner side to the outer side of the peripheral wall, or a cone that gradually decreases from the inlet side until the middle of the exhaust gas injection pipe 31 in the thickness direction. It is formed in a trapezoidal shape, and is formed in a cylindrical shape having the same diameter as the outlet side from this middle.
Further, the exhaust gas ejection pipe 31 is closed at the downstream end by a lid body 31a. The exhaust gas ejection pipe 31 is fixed in the inner cylinder pipe 21 by a rib piece 31b appropriately provided at a position not interfering with the nozzle hole 30 with the inner peripheral surface of the inner cylinder pipe 21. The rib piece 31 b is also provided on the inner peripheral surface of the exhaust gas ejection pipe 31 so that the catalyst 4 built in the exhaust gas ejection pipe 31 can be held. In a state where the catalyst 4 is held, a thermometer is passed between the catalyst 4 and the lid 31a through the outer tube 22 and the inner tube 21 of the heat exchanger 2 and the exhaust gas jet tube 31. 6 is provided. The catalyst 4 is desirably temperature-controlled because the purification action may not function effectively depending on the exhaust gas temperature, but the temperature of the catalyst 4 is measured by the thermometer 6 at a position immediately after passing through the catalyst 4. The purification state can be grasped to some extent.

接続部材３２は、筒状の本体３２ａ部分からさらに縮径して排気ガス噴出管接続部３２ｂを形成するようになされている。最大径の本体３２ａの部分は、上記排気ガス噴出管３１に隣接する下流側で、内筒管２１の内周面に固定される。排気ガス噴出管接続部３２ｂは、その外側に、次段の単位排気ガス通路３ｂを構成する排気ガス噴出管３３を受挿接続して内筒管２１と排気ガス噴出管３３との間に間隔ｄを形成するようになされている。   The connecting member 32 is further reduced in diameter from the cylindrical main body 32a portion to form an exhaust gas ejection pipe connecting portion 32b. The portion of the main body 32 a having the maximum diameter is fixed to the inner peripheral surface of the inner tube 21 on the downstream side adjacent to the exhaust gas ejection pipe 31. The exhaust gas ejection pipe connecting portion 32b is connected to the exhaust gas ejection pipe 33 constituting the unit exhaust gas passage 3b of the next stage on the outside thereof, and is spaced between the inner tube 21 and the exhaust gas ejection pipe 33. d is formed.

これにより、単位排気ガス通路３ａは、触媒を通過した排気ガスが、蓋体３１ａによって行き止まり、噴孔３０から噴出するようになされた第一排気ガス通路Ａと、この噴孔３０から噴出後、排気ガス噴出管３１と内筒管２１との間隙ｄを通過し、接続部材３２の噴出管接続部３２ｂから次段の噴出管３３へと排気ガスを通過させる第二排気ガス通路Ｂとを形成することとなる。   As a result, the exhaust gas passage 3a passes through the first exhaust gas passage A in which the exhaust gas that has passed through the catalyst is stopped by the lid body 31a and is ejected from the nozzle hole 30, and after being ejected from the nozzle hole 30, A second exhaust gas passage B that passes through the gap d between the exhaust gas ejection pipe 31 and the inner cylinder pipe 21 and allows the exhaust gas to pass from the ejection pipe connection portion 32b of the connection member 32 to the ejection pipe 33 of the next stage is formed. Will be.

単位排気ガス通路３ｂは、上記接続部材３２の排気ガス噴出管接続部３２ｂに接続される排気ガス噴出管３３と、この排気ガス噴出管３３の下流側に設けられる接続部材３４とによって構成されている。   The unit exhaust gas passage 3b includes an exhaust gas ejection pipe 33 connected to the exhaust gas ejection pipe connection portion 32b of the connection member 32 and a connection member 34 provided on the downstream side of the exhaust gas ejection pipe 33. Yes.

排気ガス噴出管３３は、内筒管２１との間に間隙ｄを形成することが可能な円筒状に形成されている。この排気ガス噴出管３３の周壁には、長手方向および周方向に沿って等間隔で複数の噴孔３０が設けられている。この噴孔３０は、上記単位排気ガス通路３ａに設けられる排気ガス噴出管３１と同様に、周壁の内側から外側に向かって漸減する円錐台形状に形成されている、または、排気ガス噴出管３３の厚み方向の途中までは入口側から漸減する円錐台形状に形成され、この途中から出口側と同じ直径の円筒状に形成されている。また、排気ガス噴出管３３は、下流側端部が蓋体３３ａによって閉塞されている。この排気ガス噴出管３３は、内筒管２１の内周面との間で噴孔３０を邪魔しない位置に適宜に設けたリブ片３３ｂによって、内筒管２１内に固定される。   The exhaust gas ejection pipe 33 is formed in a cylindrical shape capable of forming a gap d with the inner cylinder pipe 21. A plurality of nozzle holes 30 are provided in the circumferential wall of the exhaust gas ejection pipe 33 at equal intervals along the longitudinal direction and the circumferential direction. The nozzle hole 30 is formed in a truncated cone shape that gradually decreases from the inner side to the outer side of the peripheral wall, or the exhaust gas jet pipe 33, similarly to the exhaust gas jet pipe 31 provided in the unit exhaust gas passage 3 a. It is formed in a truncated cone shape that gradually decreases from the inlet side until halfway in the thickness direction, and is formed in a cylindrical shape having the same diameter as the outlet side from this middle. Further, the exhaust gas ejection pipe 33 is closed at the downstream end by a lid 33a. The exhaust gas ejection pipe 33 is fixed in the inner cylinder pipe 21 by a rib piece 33b that is appropriately provided at a position that does not interfere with the nozzle hole 30 between the exhaust gas ejection pipe 33 and the inner peripheral surface of the inner cylinder pipe 21.

接続部材３４は、筒状の本体３４ａ部分からさらに縮径して排気ガス噴出管接続部３４ｂを形成するようになされている。最大径の本体３４ａの部分は、上記排気ガス噴出管３３に隣接する下流側で、内筒管２１の内周面に固定される。排気ガス噴出管接続部３４ｂは、その外側に、次段の単位排気ガス通路３ｃを構成する排気ガス噴出管３５を受挿接続して内筒管２１と排気ガス噴出管３５との間に間隔ｄを形成するようになされている。   The connecting member 34 is further reduced in diameter from the cylindrical main body 34a portion to form an exhaust gas ejection pipe connecting portion 34b. The portion of the main body 34 a having the maximum diameter is fixed to the inner peripheral surface of the inner tube 21 on the downstream side adjacent to the exhaust gas ejection pipe 33. The exhaust gas ejection pipe connecting portion 34b is connected to the outside thereof by receiving and connecting an exhaust gas ejection pipe 35 constituting the unit exhaust gas passage 3c of the next stage, and is spaced between the inner tube 21 and the exhaust gas ejection pipe 35. d is formed.

これにより、単位排気ガス通路３ｂは、接続部材３４の噴出管接続部３４ｂを通過した排気ガスが蓋体３３ａによって行き止まり、噴孔３０から噴出するようになされた第一排気ガス通路Ａと、この噴孔３０から噴出後、排気ガス噴出管３３と内筒管２１との間隙ｄを通過し、接続部材３４の噴出管接続部３４ｂから次段の噴出管３５へと排気ガスを通過させる第二排気ガス通路Ｂとを形成することとなる。   Thereby, the unit exhaust gas passage 3b includes the first exhaust gas passage A configured such that the exhaust gas that has passed through the ejection pipe connection portion 34b of the connection member 34 is stopped by the lid body 33a and is ejected from the injection hole 30. After ejecting from the nozzle hole 30, the second gas passes through the gap d between the exhaust gas ejection pipe 33 and the inner cylinder pipe 21, and passes the exhaust gas from the ejection pipe connection portion 34 b of the connection member 34 to the ejection pipe 35 of the next stage. The exhaust gas passage B is formed.

単位排気ガス通路３ｃは、上記接続部材３４の排気ガス噴出管接続部３４ｂに接続される排気ガス噴出管３５と、排気ガス流出管２６とによって構成されている。   The unit exhaust gas passage 3 c includes an exhaust gas ejection pipe 35 connected to the exhaust gas ejection pipe connection portion 34 b of the connection member 34 and an exhaust gas outflow pipe 26.

排気ガス噴出管３５は、内筒管２１との間に間隙ｄを形成することが可能な円筒状に形成されている。この排気ガス噴出管３５の周壁には、長手方向および周方向に沿って等間隔で複数の噴孔３０が設けられている。この噴孔３０は、上記単位排気ガス通路３ａに設けられる排気ガス噴出管３１と同様に、周壁の内側から外側に向かって漸減する円錐台形状に形成されている、または、排気ガス噴出管３３の厚み方向の途中までは入口側から漸減する円錐台形状に形成され、この途中から出口側と同じ直径の円筒状に形成されている。また、排気ガス噴出管３５は、下流側端部が熱交換器２の他端側の内蓋２１ｂによって閉塞されるように、その長さが調整されている。この排気ガス噴出管３５の下流側端部は、熱交換器２の他端側の内蓋２１ｂに固定される。   The exhaust gas ejection pipe 35 is formed in a cylindrical shape capable of forming a gap d with the inner cylinder pipe 21. A plurality of nozzle holes 30 are provided in the circumferential wall of the exhaust gas ejection pipe 35 at equal intervals along the longitudinal direction and the circumferential direction. The nozzle hole 30 is formed in a truncated cone shape that gradually decreases from the inner side to the outer side of the peripheral wall, or the exhaust gas jet pipe 33, similarly to the exhaust gas jet pipe 31 provided in the unit exhaust gas passage 3 a. It is formed in a truncated cone shape that gradually decreases from the inlet side until halfway in the thickness direction, and is formed in a cylindrical shape having the same diameter as the outlet side from this middle. Further, the length of the exhaust gas ejection pipe 35 is adjusted so that the downstream end is closed by the inner lid 21 b on the other end side of the heat exchanger 2. The downstream end of the exhaust gas ejection pipe 35 is fixed to the inner lid 21 b on the other end side of the heat exchanger 2.

これにより、単位排気ガス通路３ｃは、接続部材３４の噴出管接続部３４ｂを通過した排気ガスが内蓋２１ｂによって行き止まり、噴孔３０から噴出するようになされた第一排気ガス通路Ａと、この噴孔３０から噴出後、排気ガス噴出管３５と内筒管２１との間隙ｄを通過し、排気ガス流出管２６から排気される第二排気ガス通路Ｂとを形成することとなる。   As a result, the unit exhaust gas passage 3c includes the first exhaust gas passage A configured such that the exhaust gas that has passed through the ejection pipe connection portion 34b of the connection member 34 stops at the inner lid 21b and is ejected from the nozzle hole 30. After ejection from the nozzle hole 30, a second exhaust gas passage B that passes through the gap d between the exhaust gas ejection pipe 35 and the inner cylinder pipe 21 and is exhausted from the exhaust gas outflow pipe 26 is formed.

このように構成されたエンジン排気ガス熱交換器１によると、エンジンからの排気ガスは、排気ガス流入管２５から前室５、触媒４、単位排気ガス通路３ａ，３ｂ，３ｃを経て、排気ガス流出管２６から排気されることとなる。   According to the engine exhaust gas heat exchanger 1 configured as described above, the exhaust gas from the engine passes through the exhaust gas inflow pipe 25, the front chamber 5, the catalyst 4, and the unit exhaust gas passages 3a, 3b, 3c, and the exhaust gas. The air is exhausted from the outflow pipe 26.

この際、排気ガスは、全ての噴孔３０から一挙に噴出させるのではなく、単位排気ガス通路３ａの噴孔３０から噴出させた後、回収され、次段の単位排気ガス通路３ｂの噴孔３０から噴出させた後、再度回収され、次段の単位排気ガス通路３ｃの噴孔３０から噴出させるといった構成としているため、噴孔３０から熱交換器２の内筒管２１に向けて噴出される排気ガスの噴射速度は、各単位排気ガス通路３ａ，３ｂ，３ｃで低下させることなく一定に保つことができる。したがって、噴孔３０当たりの流速の低下を防止して所定の平均熱通過率（Ｋ値）を維持することが可能となる。   At this time, the exhaust gas is not ejected from all the nozzle holes 30 at once, but is ejected from the nozzle holes 30 of the unit exhaust gas passage 3a and then recovered, and the nozzle holes of the next unit exhaust gas passage 3b are collected. After being ejected from 30, it is recovered again and ejected from the nozzle hole 30 of the unit exhaust gas passage 3 c at the next stage, so that it is ejected from the nozzle hole 30 toward the inner tube 21 of the heat exchanger 2. The exhaust gas injection speed can be kept constant without being lowered in each unit exhaust gas passage 3a, 3b, 3c. Therefore, it is possible to prevent a decrease in flow rate per nozzle hole 30 and maintain a predetermined average heat passage rate (K value).

また、前室５は、管材５１と内筒管２１との間に空隙Ｓを形成しているので、排気ガス流入管２５から流入した排気ガスが、内筒管２１を介して冷却水によって冷却されるのを防止することができる。したがって、触媒４に流入される前の排気ガスの温度低下を防止して触媒４での反応を活性化することができる。   Further, since the front chamber 5 forms a gap S between the pipe material 51 and the inner tube 21, the exhaust gas flowing from the exhaust gas inflow tube 25 is cooled by the cooling water through the inner tube 21. Can be prevented. Therefore, it is possible to prevent the temperature of the exhaust gas before flowing into the catalyst 4 from decreasing and activate the reaction at the catalyst 4.

さらに、排気ガス噴出管３１，３３，３５に設けた各噴孔３０は、排気ガスの入口から出口にかけて通過面積が漸減する形状としているので、同一噴孔通過流速において、排気ガスの圧力損失を低減できる。したがって、熱交換器２の設計許容圧力損失値に対する噴孔通過流速をあげることができ、平均熱通過率を上昇し熱交換量を増加できる。特に、上記構成のエンジン排気ガス熱交換器１の場合、排気ガスの噴射速度は、各単位排気ガス通路３ａ，３ｂ，３ｃで低下させることなく一定に保つことができるので、このような噴孔３０の構成は有効に作用することとなる。   Furthermore, each nozzle hole 30 provided in the exhaust gas jet pipes 31, 33, 35 has a shape in which the passage area gradually decreases from the exhaust gas inlet to the outlet, so that the pressure loss of the exhaust gas is reduced at the same nozzle hole passage flow velocity. Can be reduced. Therefore, the nozzle hole passage flow velocity with respect to the design allowable pressure loss value of the heat exchanger 2 can be increased, and the average heat passage rate can be increased to increase the heat exchange amount. In particular, in the case of the engine exhaust gas heat exchanger 1 configured as described above, the injection speed of the exhaust gas can be kept constant without being lowered in each of the unit exhaust gas passages 3a, 3b, 3c. The configuration of 30 works effectively.

なお、本実施の形態では、噴孔３０の形状を周壁の内側から外側に向かって漸減する形状となされているが、この噴孔３０の構成と併せて、噴孔３０から噴出されたガスが当たる内筒管２１の内周面に、溝加工を施してもよい。この場合、内筒管２１の内周面で、この内周面に噴きつけられた排気ガスの乱れを誘起できるので、熱交換量を増加できることとなる。溝加工の形状としては、内筒管２１の長さ方向に沿って形成されたものであってもよいし、周方向に沿って形成されたものであってもよいし、排気ガスの流れ方向に沿って渦流となるように、周方向に対して斜めになった螺旋状に形成されたものであってもよい。また、この溝加工は内筒管２１の内周面側に凸、外周面側に凸のいずれでもよい。さらに、この溝加工と同様の効果を得る為に、噴孔３０から噴出されたガスが当たる内筒管２１の内周面にディンプル加工を施してもよい。ディンプルの形状としては、ゴルフボールに設けられているような円形状の凹部が挙げられる。このディンプル加工は内筒管２１の内周面側に凸、外周面側に凸のいずれでもよい。   In the present embodiment, the shape of the nozzle hole 30 is gradually reduced from the inner side to the outer side of the peripheral wall. In addition to the configuration of the nozzle hole 30, the gas ejected from the nozzle hole 30 is Groove processing may be performed on the inner peripheral surface of the inner tube 21 that hits. In this case, since the turbulence of the exhaust gas sprayed on the inner peripheral surface can be induced on the inner peripheral surface of the inner tube 21, the heat exchange amount can be increased. As the shape of the groove processing, it may be formed along the length direction of the inner tube 21, may be formed along the circumferential direction, or the flow direction of the exhaust gas It may be formed in a spiral shape that is slanted with respect to the circumferential direction so as to form a vortex. Further, this groove processing may be either convex on the inner peripheral surface side of the inner tube 21 or convex on the outer peripheral surface side. Furthermore, in order to obtain the same effect as the groove processing, dimple processing may be performed on the inner peripheral surface of the inner tube 21 to which the gas ejected from the nozzle hole 30 hits. Examples of the dimple shape include a circular concave portion as provided in a golf ball. This dimple processing may be either convex on the inner peripheral surface side of the inner tube 21 or convex on the outer peripheral surface side.

本発明は、空調装置やコージェネレーションシステムで使用される各種エンジンの排気ガス熱交換器として利用できる。   The present invention can be used as an exhaust gas heat exchanger for various engines used in air conditioners and cogeneration systems.

１ エンジン排気ガス熱交換器
１１ エンジン
２ 熱交換器
２０ 冷却水通路
２１ 内筒管（排気ガス衝突面）
３１ 排気ガス噴出管
３０ 噴孔 DESCRIPTION OF SYMBOLS 1 Engine exhaust gas heat exchanger 11 Engine 2 Heat exchanger 20 Coolant passage 21 Inner cylinder pipe (exhaust gas collision surface)
31 Exhaust gas ejection pipe 30 Injection hole

Claims (4)

エンジンの排気ガスと冷却水との間の熱交換器であって、排気ガス通路の周方向および排気ガス流れ方向に冷却水通路と対向した噴孔を設けて排気ガス全量を冷却水通路に衝突させるエンジン排気ガス熱交換器において、
各噴孔を入口から出口にかけて排気ガスの通過面積が漸減する形状としたことを特徴とするエンジン排気ガス熱交換器。 This is a heat exchanger between the exhaust gas and cooling water of the engine, and an exhaust hole facing the cooling water passage is provided in the circumferential direction of the exhaust gas passage and in the exhaust gas flow direction so that the entire exhaust gas collides with the cooling water passage. In the engine exhaust gas heat exchanger
An engine exhaust gas heat exchanger characterized in that each nozzle hole has a shape in which an exhaust gas passage area gradually decreases from an inlet to an outlet. 請求項１記載の触媒内蔵型エンジン排気ガス熱交換器において、各噴孔の途中部から排気ガスの通過面積を出口面積と等しくしたことを特徴とするエンジン排気ガス熱交換器。   The engine exhaust gas heat exchanger with built-in catalyst according to claim 1, wherein the passage area of the exhaust gas from the middle of each nozzle hole is made equal to the outlet area. 請求項１または２記載のエンジン排気ガス熱交換器において、冷却水通路の排気ガス衝突面に溝加工を行ったことを特徴とするエンジン排気ガス熱交換器。   The engine exhaust gas heat exchanger according to claim 1 or 2, wherein a groove is formed on an exhaust gas collision surface of the cooling water passage. エンジン駆動式ヒートポンプおよびコージェネレーションなどのエネルギー供給装置において、請求項１ないし３の何れか一記載の触媒内蔵型エンジン排気ガス熱交換器をエンジンの排気ガス経路に使用したことを特徴とするエネルギー供給装置。   An energy supply apparatus such as an engine-driven heat pump and a cogeneration system, wherein the catalyst exhaust type engine exhaust gas heat exchanger according to any one of claims 1 to 3 is used for an engine exhaust gas path. apparatus.
JP2010055575A 2010-03-12 2010-03-12 Engine exhaust gas heat exchanger and energy supply device using the same Pending JP2011190708A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2010055575A JP2011190708A (en) 2010-03-12 2010-03-12 Engine exhaust gas heat exchanger and energy supply device using the same
EP11753434.7A EP2546491B1 (en) 2010-03-12 2011-03-10 Engine exhaust gas heat exchanger and energy supply device using same
US13/583,774 US8904772B2 (en) 2010-03-12 2011-03-10 Engine exhaust gas heat exchanger and energy supplying device using the same
CA2792916A CA2792916A1 (en) 2010-03-12 2011-03-10 Engine exhaust gas heat exchanger and energy supplying device using the same
ES11753434.7T ES2575583T3 (en) 2010-03-12 2011-03-10 Exhaust gas heat exchanger of the engine and power supply device that uses it
PCT/JP2011/055633 WO2011111776A1 (en) 2010-03-12 2011-03-10 Engine exhaust gas heat exchanger and energy supply device using same

Applications Claiming Priority (1)

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JP2010055575A JP2011190708A (en) 2010-03-12 2010-03-12 Engine exhaust gas heat exchanger and energy supply device using the same

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JP2011190708A true JP2011190708A (en) 2011-09-29

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