JP2014034922A - Exhaust heat recovery device - Google Patents

Exhaust heat recovery device Download PDF

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Publication number
JP2014034922A
JP2014034922A JP2012176351A JP2012176351A JP2014034922A JP 2014034922 A JP2014034922 A JP 2014034922A JP 2012176351 A JP2012176351 A JP 2012176351A JP 2012176351 A JP2012176351 A JP 2012176351A JP 2014034922 A JP2014034922 A JP 2014034922A
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Prior art keywords
exhaust
heat recovery
cylinder portion
valve
flow path
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Japanese (ja)
Inventor
Ryutaro Shinohara
竜太郎 篠原
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Suzuki Motor Corp
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Suzuki Motor Corp
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Priority to JP2012176351A priority Critical patent/JP2014034922A/en
Priority to DE102013107868.0A priority patent/DE102013107868B4/en
Priority to CN201310332131.5A priority patent/CN103573355B/en
Publication of JP2014034922A publication Critical patent/JP2014034922A/en
Pending legal-status Critical Current

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    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • 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
    • F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
    • F01N2240/36—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being an exhaust flap
    • 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
    • F28F2250/06—Derivation channels, e.g. bypass
    • 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)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Exhaust Silencers (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

PROBLEM TO BE SOLVED: To prevent decrease of an amount of heat recovery due to influence by traveling wind, to reduce pressure loss of exhaust and a refrigerant exchanging heat with each other, and further to easily control the amount of heat recovery.SOLUTION: An exhaust heat recovery device includes: an inner cylindrical portion 11 in which cooling water 2 flows; an intermediate cylindrical portion 12 disposed outside of the inner cylindrical portion 11 at a prescribed interval, and forming a heat recovery flow channel 16 with the inner cylindrical portion 11 to allow the cooling water 2 in the inner cylindrical portion 11 to recover heat of introduced exhaust 1; an outer cylindrical portion 13 disposed outside of the intermediate cylindrical portion 12 at a prescribed interval, and forming a bypass flow channel 17 with the intermediate cylindrical portion 12 to allow the bypassed exhaust to flow therein; and an exhaust valve 14 disposed at an upstream end in a flowing direction of the exhaust 1 in the intermediate cylindrical portion 12, and allowing the exhaust 1 to selectively flow to the heat recovery flow channel 16 and the bypass flow channel 17.

Description

本発明は、エンジンの排気の熱を冷媒、例えばエンジンの冷却水に回収する排気熱回収装置に関する。   The present invention relates to an exhaust heat recovery device that recovers heat of engine exhaust into a refrigerant, for example, engine coolant.

従来より、自動車用内燃機関（自動車用エンジン；以下エンジンと称する）の排気の熱を回収する機器として、排気熱回収装置が知られている。このような排気熱回収装置は、エンジンの排気管の途中に設置され、排気管を通過するエンジンからの排気とエンジンの冷却水との間で熱交換を行う。エンジンの冷却水を介して回収された排気熱は、例えばエンジンの暖機運転を早期に完了させるために、エンジンの冷間時に冷却水温度を急激に上昇させることに利用され、あるいは車室内の暖房にも利用される。   2. Description of the Related Art Conventionally, an exhaust heat recovery device is known as a device that recovers the heat of exhaust gas from an automobile internal combustion engine (automobile engine; hereinafter referred to as an engine). Such an exhaust heat recovery device is installed in the middle of the exhaust pipe of the engine, and performs heat exchange between the exhaust from the engine passing through the exhaust pipe and the cooling water of the engine. The exhaust heat recovered via the engine coolant is used to rapidly increase the coolant temperature when the engine is cold, for example, in order to complete the warm-up operation of the engine at an early stage. It is also used for heating.

現在実用化されている排気熱回収装置は、特許文献１に開示された第１従来技術（図５）と、特許文献２に開示された第２従来技術（不図示）に大別されるが、コスト面などの理由から第１従来技術が主流である。   Exhaust heat recovery devices that are currently in practical use are broadly divided into a first prior art disclosed in Patent Document 1 (FIG. 5) and a second prior art disclosed in Patent Document 2 (not shown). The first prior art is mainstream for reasons such as cost.

第１従来技術の排気熱回収器１００は、排気を通過させるバイパス流路１０４を形成する内筒部１０１と、この内筒部１０１の下流側でバイパス流路１０４を開閉する排気バルブ１０２と、内筒部１０１の外周側に間隔をもって設けられた外筒部１０３と、内筒部１０１と外筒部１０３との間に設けられた熱交換部（排気熱回収流路１０５及び１０６並びに冷却水流路１０７及び１０８）とを備えている。   The exhaust heat recovery device 100 of the first prior art includes an inner cylinder portion 101 that forms a bypass passage 104 that allows exhaust to pass through, an exhaust valve 102 that opens and closes the bypass passage 104 on the downstream side of the inner cylinder portion 101, The outer cylinder part 103 provided at intervals on the outer peripheral side of the inner cylinder part 101, and the heat exchange part provided between the inner cylinder part 101 and the outer cylinder part 103 (exhaust heat recovery flow paths 105 and 106, and cooling water flow Roads 107 and 108).

排気熱回収を行う場合には排気バルブ１０２を閉動作させ、内筒部１０１内に導入された排気を、内筒部１０１の側部に設けられた多数の小孔１０９から、内筒部１０１の外周に設けられた第１排気熱回収流路１０５及び第２排気熱回収流路１０６へ順次流し、内側冷却水流路１０７及び外側冷却水流路１０８を流れる冷却水との間で熱交換を行わせる。   When exhaust heat recovery is performed, the exhaust valve 102 is closed, and the exhaust gas introduced into the inner cylinder portion 101 is discharged from a large number of small holes 109 provided on the side of the inner cylinder portion 101. Are sequentially passed through a first exhaust heat recovery flow path 105 and a second exhaust heat recovery flow path 106 provided on the outer periphery, and heat exchange is performed with cooling water flowing through the inner cooling water flow path 107 and the outer cooling water flow path 108. Make it.

この排気熱回収器１００は、前述のように、エンジン始動時の暖機や車室内の暖房を主目的とすることから、エンジンの始動から一定時間経過して暖機や暖房のニーズが低下したときには、排気熱の回収を行わず排気を排出（廃棄）している。この排気熱の廃棄時にはバルブ１０２を開動作して、内筒部１０１内に導入された排気を直接下流側へ排出し、排気を第１熱回収流路１０５及び第２熱回収流路１０６へ流動させないようにして、必要以上の冷却水の温度上昇を抑制すると共に、排気の圧力損失を抑制している。   As described above, the exhaust heat recovery device 100 is mainly used for warming up the engine and heating the vehicle interior, so that the needs for warming up and heating have decreased after a certain period of time since the engine started. Sometimes exhaust is exhausted (discarded) without exhaust heat recovery. When the exhaust heat is discarded, the valve 102 is opened to exhaust the exhaust gas introduced into the inner cylinder portion 101 directly to the downstream side, and the exhaust gas is discharged to the first heat recovery flow path 105 and the second heat recovery flow path 106. In order not to make it flow, while suppressing the temperature rise of the cooling water more than necessary, the pressure loss of the exhaust gas is suppressed.

一方、第２従来技術の排気熱回収装置（車両用蓄熱システム）は、エンジンの冷却水系統に排熱回収手段と蓄熱器を備え、排熱回収手段は、エンジンから排出された排気とエンジンの冷却水の間で熱交換可能に、二股に分岐された一方のエンジンの排気系統に沿って配置されたものである。   On the other hand, the exhaust gas heat recovery device (vehicle heat storage system) of the second prior art is provided with an exhaust heat recovery means and a heat storage device in the engine cooling water system, and the exhaust heat recovery means includes the exhaust discharged from the engine and the engine exhaust. It is arranged along the exhaust system of one of the engines that is bifurcated so that heat can be exchanged between the cooling water.

特開２０１０−３１６７１号公報JP 2010-31671 A 特開２００１−３０７４１号公報JP 2001-30741 A

ところが、排気熱回収装置には、エンジンの暖機や車室内の暖房の目的を達成した後、エンジンの定常運転時や高負荷運転時にも継続的に排気熱を回収できるようにして、燃費を向上させたいとする要請がある。例えば、ランキンサイクルシステムを搭載した車両において、排気の熱を冷却水に常時回収し、その回収熱をランキンサイクル加熱器の熱源とするような場合である。   However, the exhaust heat recovery device achieves the fuel efficiency by enabling the exhaust heat to be recovered continuously even during steady engine operation or high load operation after achieving the purpose of warming up the engine or heating the passenger compartment. There is a request to improve. For example, in a vehicle equipped with a Rankine cycle system, the exhaust heat is always recovered in cooling water, and the recovered heat is used as a heat source for the Rankine cycle heater.

しかしながら、第１及び第２従来技術では、エンジンの定常運転時に継続的に排気熱を回収しようとすると、次のような課題が生じる。   However, in the first and second conventional techniques, the following problems occur when exhaust heat is continuously collected during steady operation of the engine.

第１に、走行風により冷却水が冷却されて熱回収効率が低下してしまう。つまり、前部にエンジンが搭載されている車両では、排気管が車両前部からフロア下面を通って後方へ延びているため、排気熱回収器１００はフロア下面に設置されることになる。ところが、排気熱回収器１００では冷却水が外筒部１０３近傍を流れるため、エンジンの定常運転時や高速運転時のような流れの強い走行風によって、排気熱を回収した冷却水が冷却されやすく、熱損失が発生して排気熱の回収効率が低下してしまう。この点は、第２従来技術においても同様である。   First, the cooling water is cooled by the traveling wind, and the heat recovery efficiency is reduced. That is, in a vehicle in which an engine is mounted on the front, the exhaust pipe extends rearward from the front of the vehicle through the floor lower surface, so that the exhaust heat recovery device 100 is installed on the floor lower surface. However, in the exhaust heat recovery device 100, since the cooling water flows in the vicinity of the outer cylinder portion 103, the cooling water from which the exhaust heat has been recovered is easily cooled by the strong running wind during steady engine operation or high speed operation. As a result, heat loss occurs and exhaust heat recovery efficiency decreases. This also applies to the second prior art.

第２に、排気及び冷却水の圧力損失が大きい。つまり、排気側について、排気熱回収器１００は小孔１０９を通して排気を第１排気熱回収流路１０５に流出させ、その後更に上流側で排気の流れを折り返して第２排気熱回収流路１０６へ流すことから、排気の圧力損失が大きい。このため、特にエンジンの高負荷時の出力及び燃費の低下が課題となる。また、冷却水側においても、内側冷却水流路１０７及び外側冷却水流路１０８の流路断面が狭小なため、冷却水の圧力損失が大きく、ウォータポンプ負荷が高くなって燃費の低下が課題となる。第２従来技術は、この点においても同様である。   Second, the pressure loss of exhaust and cooling water is large. In other words, on the exhaust side, the exhaust heat recovery device 100 causes the exhaust to flow out to the first exhaust heat recovery flow path 105 through the small hole 109, and then the flow of the exhaust is turned further upstream to return to the second exhaust heat recovery flow path 106. Since it flows, the pressure loss of the exhaust is large. For this reason, the output at the time of high load of an engine and the fall of a fuel consumption become a subject. In addition, on the cooling water side, since the cross sections of the inner cooling water passage 107 and the outer cooling water passage 108 are narrow, the pressure loss of the cooling water is large, the water pump load becomes high, and the fuel consumption decreases. . The second prior art is the same in this respect.

尚、エンジンの定常運転時に継続的に排気熱を回収する排気熱回収装置であっても、ランキンサイクルシステムなどからの要請により、排気熱回収量を容易に制御できる必要がある。   Even in an exhaust heat recovery device that continuously recovers exhaust heat during steady operation of the engine, it is necessary to easily control the exhaust heat recovery amount in response to a request from a Rankine cycle system or the like.

本発明の目的は、上述の事情を考慮してなされたものであり、走行風の影響により回収熱量が低下せず、且つ熱交換を行う排気及び冷媒の圧力損失を低減でき、更に熱回収量を容易に制御できる排気熱回収装置を提供することにある。   The object of the present invention has been made in consideration of the above circumstances, and the amount of recovered heat does not decrease due to the influence of the traveling wind, and the pressure loss of the exhaust and refrigerant for heat exchange can be reduced. It is an object of the present invention to provide an exhaust heat recovery device that can easily control the above.

本発明に係る排気熱回収装置は、内部に冷媒が流動する内筒部と、この内筒部の外側に所定間隔をもって配置され、前記内筒部との間に、導入された排気の熱を前記内筒部内の冷媒に回収させる熱回収流路を形成する中間筒部と、この中間筒部の外側に所定間隔をもって配置され、前記中間筒部との間に、バイパスされた排気を流動させるバイパス流路を形成する外筒部と、前記中間筒部における排気の流れ方向上流端に設置され、排気を前記熱回収流路と前記バイパス流路に切り替えて流す排気バルブと、を有して構成されたことを特徴とするものである。   The exhaust heat recovery apparatus according to the present invention is arranged with a predetermined interval on the outer side of the inner cylinder part through which the refrigerant flows, and between the inner cylinder part. An intermediate cylinder part that forms a heat recovery flow path to be recovered by the refrigerant in the inner cylinder part and an outer side of the intermediate cylinder part are arranged at a predetermined interval, and the bypassed exhaust gas flows between the intermediate cylinder part. An outer cylinder part that forms a bypass flow path, and an exhaust valve that is installed at an upstream end in the flow direction of the exhaust gas in the intermediate cylinder part and flows the exhaust gas by switching to the heat recovery flow path and the bypass flow path. It is characterized by having been comprised.

本発明によれば、冷媒が流れる内筒部は、内筒部と中間筒部により形成される熱回収流路、中間筒部と外筒部により形成されるバイパス流路により順次覆われることになるので、冷媒に回収された回収熱量が走行風の影響により低下することを防止できる。また、熱回収流路が直線形状に形成されて、この熱回収流路内を流れる排気の流れがスムーズであり、また冷媒が流れる内筒部の流路断面積も確保されるので、排気及び冷媒の圧力損失を共に低減できる。更に、排気バルブの開度を調節して、熱回収流路内へ流れる排気の流量を調整することで、冷媒による熱回収量を容易に制御できる。   According to the present invention, the inner cylinder part through which the refrigerant flows is sequentially covered by the heat recovery channel formed by the inner cylinder part and the intermediate cylinder part and the bypass channel formed by the intermediate cylinder part and the outer cylinder part. Therefore, it is possible to prevent the recovered heat amount recovered by the refrigerant from being lowered due to the influence of the traveling wind. Further, since the heat recovery flow path is formed in a linear shape, the flow of the exhaust flowing through the heat recovery flow path is smooth, and the flow path cross-sectional area of the inner cylinder portion through which the refrigerant flows is ensured. Both the pressure loss of the refrigerant can be reduced. Furthermore, the amount of heat recovered by the refrigerant can be easily controlled by adjusting the opening of the exhaust valve and adjusting the flow rate of the exhaust flowing into the heat recovery flow path.

本発明に係る排気熱回収装置の第１実施形態における非熱回収状態を示し、（Ａ）は横断面図、（Ｂ）は図１（Ａ）のＩ−Ｉ線に沿う断面図。The non-heat recovery state in 1st Embodiment of the exhaust heat recovery apparatus which concerns on this invention is shown, (A) is a cross-sectional view, (B) is sectional drawing which follows the II line | wire of FIG. 1 (A). 図１の排気熱回収装置における熱回収状態を示し、（Ａ）は横断面図、（Ｂ）は図２（Ａ）のＩＩ−ＩＩ線に沿う断面図。The heat recovery state in the exhaust heat recovery apparatus of FIG. 1 is shown, (A) is a cross-sectional view, (B) is sectional drawing which follows the II-II line | wire of FIG. 2 (A). 本発明に係る排気熱回収装置の第２実施形態における非熱回収状態を示し、（Ａ）は横断面図、（Ｂ）は図３（Ａ）のＩＩＩ−ＩＩＩ線に沿う断面図。The non-heat recovery state in 2nd Embodiment of the exhaust heat recovery apparatus which concerns on this invention is shown, (A) is a cross-sectional view, (B) is sectional drawing which follows the III-III line | wire of FIG. 3 (A). 図３の排気熱回収装置における熱回収状態を示し、（Ａ）は横断面図、（Ｂ）は図４（Ａ）のＩＶ−ＩＶ線に沿う断面図。The heat recovery state in the exhaust heat recovery apparatus of FIG. 3 is shown, (A) is a cross-sectional view, (B) is sectional drawing which follows the IV-IV line | wire of FIG. 4 (A). 第１従来技術の排熱回収器を示す断面図。Sectional drawing which shows the waste heat recovery device of 1st prior art.

以下、本発明を実施するための実施形態を図面に基づき説明する。
［Ａ］第１実施形態（図１、図２）
図１は、本発明に係る排気熱回収装置の第１実施形態における非熱回収状態を示し、（Ａ）は横断面図、（Ｂ）は図１（Ａ）のＩ−Ｉ線に沿う断面図である。また、図２は、図１の排気熱回収装置における熱回収状態を示し、（Ａ）は横断面図、（Ｂ）は図２（Ａ）のＩＩ−ＩＩ線に沿う断面図である。 DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.
[A] First embodiment (FIGS. 1 and 2)
FIG. 1 shows a non-heat recovery state in the first embodiment of the exhaust heat recovery apparatus according to the present invention, where (A) is a cross-sectional view, and (B) is a cross section taken along the line I-I in FIG. FIG. 2 shows a heat recovery state in the exhaust heat recovery apparatus of FIG. 1, (A) is a cross-sectional view, and (B) is a cross-sectional view taken along line II-II in FIG. 2 (A).

図１及び図２に示す排気熱回収装置１０は、図示しないエンジンの始動時のほか、エンジンの定常運転時や高負荷運転時にも継続的に、エンジンからの排気１の熱を冷媒（本実施形態ではエンジンの冷却水２）に回収して、その回収熱をエンジンの暖機運転、車室内の暖房、ランキンサイクル加熱器の熱源に利用するものであり、内筒部１１、中間筒部１２、外筒部１３及び排気バルブ１４を有して構成される。   The exhaust heat recovery device 10 shown in FIG. 1 and FIG. 2 continuously cools the heat of the exhaust 1 from the engine (not shown) when the engine (not shown) is started, or during steady engine operation or high load operation. In the embodiment, it is recovered in the engine cooling water 2), and the recovered heat is used for warming up the engine, heating the passenger compartment, and the heat source of the Rankine cycle heater. The outer cylinder portion 13 and the exhaust valve 14 are configured.

内筒部１１は例えば円筒形状であって、内部に冷却水２が流動するものであり、スタティックミキサー１５が内蔵されている。このスタティックミキサー１５は、右方向に捩られた右捩り羽根１５Ａと、左方向に捩られた左捩り羽根１５Ｂとが、軸方向に交互に複数接合されて構成されたものである。隣接する右捩り羽根１５Ａと左捩り羽根１５Ｂとの交叉角度は例えば９０度である。従って、内筒部１１に内蔵されたスタティックミキサー１５によって、内筒部１１内を流れる冷却水２は撹拌される。   The inner cylinder portion 11 has, for example, a cylindrical shape, in which the cooling water 2 flows, and a static mixer 15 is incorporated. This static mixer 15 is configured by joining a plurality of right twist blades 15A twisted in the right direction and left twist blades 15B twisted in the left direction alternately in the axial direction. The crossing angle between the adjacent right twist blade 15A and left twist blade 15B is, for example, 90 degrees. Therefore, the cooling water 2 flowing in the inner cylinder portion 11 is agitated by the static mixer 15 incorporated in the inner cylinder portion 11.

中間筒部１２は例えば円筒形状であって、内筒部１１の外周側に所定間隔をもって配置される。この中間筒部１２と内筒部１１との間に熱回収流路１６が形成される。この熱回収流路１６は、導入される排気１の熱を、熱交換によって内筒部１１内の冷却水２に回収させるものである。   The intermediate cylinder part 12 has, for example, a cylindrical shape, and is arranged at a predetermined interval on the outer peripheral side of the inner cylinder part 11. A heat recovery channel 16 is formed between the intermediate cylinder portion 12 and the inner cylinder portion 11. The heat recovery flow path 16 is for recovering the heat of the introduced exhaust 1 to the cooling water 2 in the inner cylinder portion 11 by heat exchange.

外筒部１３は例えば円筒形状であって、中間筒部１２の外周側に所定間隔をもって配置される。この外筒部１３と中間筒部１２との間に、熱回収流路１６内に導入されずにバイパスされた排気１を流動させるバイパス流路１７が形成される。   The outer cylinder part 13 is, for example, a cylindrical shape, and is arranged at a predetermined interval on the outer peripheral side of the intermediate cylinder part 12. Between the outer cylinder part 13 and the intermediate cylinder part 12, a bypass channel 17 is formed for flowing the exhaust 1 bypassed without being introduced into the heat recovery channel 16.

排気バルブ１４は、例えば円板形状の弁体１８と、この弁体１８の略中央位置（例えば直径位置）に設けられた弁体棒１９と、を有して構成される。この排気バルブ１４は、中間筒部１２における排気１の流れ方向上流端に設置される。具体的には、排気バルブ１４の弁体棒１９は、中間筒部１２における排気１の流れ方向上流端であって、中間筒部１２の直径方向または幅方向（本実施形態では直径方向Ｄ）略中央位置に、回転可能に枢支される。   The exhaust valve 14 includes, for example, a disc-shaped valve body 18 and a valve body rod 19 provided at a substantially central position (for example, a diameter position) of the valve body 18. The exhaust valve 14 is installed at the upstream end of the intermediate cylinder portion 12 in the flow direction of the exhaust 1. Specifically, the valve body rod 19 of the exhaust valve 14 is the upstream end in the flow direction of the exhaust 1 in the intermediate cylinder part 12, and the diameter direction or the width direction of the intermediate cylinder part 12 (diameter direction D in this embodiment). It is pivotally supported at a substantially central position.

排気バルブ１４の弁体１８が中間筒部１２の軸心Ｏに対し直交して位置づけられることで、排気バルブ１４はその開度が全閉となる（図１）。このとき、外筒部１３内に導入された排気１は、排気バルブ１４の弁体１８に遮られて中間筒部１２内の熱回収流路１６には流入せず、図１の矢印Ａに示すように、略全量が外筒部１３内のバイパス流路１７を流動する。従って、排気１の熱は、内筒部１１内の冷却水にほとんど回収されない。   Since the valve body 18 of the exhaust valve 14 is positioned perpendicular to the axis O of the intermediate cylinder portion 12, the opening degree of the exhaust valve 14 is fully closed (FIG. 1). At this time, the exhaust gas 1 introduced into the outer cylinder portion 13 is blocked by the valve body 18 of the exhaust valve 14 and does not flow into the heat recovery flow path 16 in the intermediate cylinder portion 12, and the arrow 1 in FIG. As shown, substantially the entire amount flows through the bypass channel 17 in the outer cylinder part 13. Accordingly, the heat of the exhaust 1 is hardly recovered by the cooling water in the inner cylinder portion 11.

排気バルブ１４の弁体１８が中間筒部１２の軸心Ｏに対し平行に位置づけられると、排気バルブ１４はその開度が全開となる（図２）。このとき、外筒部１３内に導入された排気１は、図２の矢印Ｂ、Ｃにそれぞれ示すように、中間筒部１２内の熱回収流路１６と外筒部１３内のバイパス流路１７とを流れ、熱回収流路１６を流動する排気１の熱が、内筒部１１内を流動する冷却水２に回収される。   When the valve body 18 of the exhaust valve 14 is positioned parallel to the axis O of the intermediate cylinder portion 12, the exhaust valve 14 is fully opened (FIG. 2). At this time, the exhaust 1 introduced into the outer cylinder part 13 is converted into the heat recovery flow path 16 in the intermediate cylinder part 12 and the bypass flow path in the outer cylinder part 13 as shown by arrows B and C in FIG. 17 and the heat of the exhaust 1 flowing through the heat recovery passage 16 is recovered by the cooling water 2 flowing in the inner cylinder portion 11.

排気バルブ１４の弁体１８が中間筒部１２の軸心Ｏに対し直交状態から平行状態までの所定の位置に位置づけられる排気バルブ１４の開度で、外筒部１３内の排気１は、排気バルブ１４の開度に応じて中間筒部１２内の熱回収流路１６に流入し、この排気１の熱が、内筒部１１内を流動する冷却水２に回収される。   The exhaust 1 in the outer cylinder portion 13 is exhausted by the opening degree of the exhaust valve 14 where the valve body 18 of the exhaust valve 14 is positioned at a predetermined position from the orthogonal state to the parallel state with respect to the axis O of the intermediate cylinder portion 12. Depending on the opening degree of the valve 14, it flows into the heat recovery passage 16 in the intermediate cylinder portion 12, and the heat of the exhaust 1 is recovered in the cooling water 2 flowing in the inner cylinder portion 11.

以上のように構成されたことから、本実施形態によれば、次の効果（１）〜（５）を奏する。
（１）冷却水２が流れる内筒部１１が、この内筒部１１と中間筒部１２により形成される熱回収流路１６により覆われ、この更にこの熱回収流路１６が、中間筒部１２と外筒部１３により形成されるバイパス流路１７により覆われているので、冷却水２に回収された回収熱が、外筒部１３の外側を流れる走行風の影響により低下することを防止できる。この結果、排気熱の回収効率が向上する。 With the configuration as described above, according to the present embodiment, the following effects (1) to (5) are obtained.
(1) The inner cylinder part 11 through which the cooling water 2 flows is covered with a heat recovery flow path 16 formed by the inner cylinder part 11 and the intermediate cylinder part 12, and this heat recovery flow path 16 is further connected to the intermediate cylinder part. 12 is covered with a bypass passage 17 formed by the outer cylinder portion 13, so that the recovered heat recovered in the cooling water 2 is prevented from being lowered by the influence of traveling wind flowing outside the outer cylinder portion 13. it can. As a result, exhaust heat recovery efficiency is improved.

（２）内筒部１１と中間筒部１２とにより形成される熱回収流路１６が直線形状に形成されて、この熱回収流路１６内を流れる排気１の流れがスムーズあることと、冷却水２が流れる内筒部１１が、スタティックミキサー１５を内蔵するに十分な流路断面積に確保されていることとから、排気１及び冷却水２の圧力損失を共に低減できる。この結果、エンジンの定常運転時や高負荷運転時における出力及び燃費の低下を防止でき、エンジンの定常運転時や高負荷運転時に継続的に熱回収を行うに適した排気熱回収装置１０とすることができる。   (2) The heat recovery passage 16 formed by the inner cylinder portion 11 and the intermediate cylinder portion 12 is formed in a linear shape, and the flow of the exhaust gas 1 flowing through the heat recovery passage 16 is smooth, and cooling Since the inner cylinder portion 11 through which the water 2 flows is ensured to have a flow path cross-sectional area sufficient to incorporate the static mixer 15, both the pressure loss of the exhaust 1 and the cooling water 2 can be reduced. As a result, it is possible to prevent a decrease in output and fuel consumption during steady operation or high load operation of the engine, and to provide an exhaust heat recovery device 10 suitable for continuously recovering heat during steady operation or high load operation of the engine. be able to.

（３）排気バルブ１４の開度を調整して、熱回収流路１６内へ流れる排気１の流量を調整することで、内筒部１１内を流動する冷却水２による熱回収量を容易に制御できる。この結果、排気回収熱をランキンサイクル加熱器の熱源として利用する場合にも、そのランキンサイクルシステムの要請である熱量の制御に対応することができる。   (3) By adjusting the opening degree of the exhaust valve 14 and adjusting the flow rate of the exhaust 1 flowing into the heat recovery flow path 16, the amount of heat recovered by the cooling water 2 flowing in the inner cylinder portion 11 can be easily achieved. Can be controlled. As a result, even when the exhaust recovery heat is used as a heat source for the Rankine cycle heater, it is possible to cope with the control of the amount of heat, which is a requirement of the Rankine cycle system.

（４）内筒部１１には、冷却水２を撹拌して流動させるスタティックミキサー１５が内蔵されたので、内筒部１１の外側の熱回収流路１６を流れる排気１と、内筒部１１内の冷却水２との熱交換効率が向上して、冷却水２による排気１の回収熱量を増大させることができる。   (4) Since the static mixer 15 that stirs and flows the cooling water 2 is incorporated in the inner cylinder portion 11, the exhaust 1 flowing through the heat recovery flow path 16 outside the inner cylinder portion 11 and the inner cylinder portion 11. The heat exchange efficiency with the internal cooling water 2 is improved, and the amount of heat recovered from the exhaust 1 by the cooling water 2 can be increased.

（５）排気バルブ１４は、中間筒部１２における排気１の流れ方向上流端に設置されるが、このとき弁体１８の略中央位置に設けられた弁体棒１９が、中間筒部１２の直径方向Ｄの略中央位置に配置されている。このため、排気１は、中間筒部１２内の熱回収流路１６に流入する際に、弁体１８及び弁体棒１９により撹拌されて乱流状態になる。この結果、熱回収流路１６における乱流状態の排気１の熱を、内筒部１１内を流動する冷却水２に回収させる熱回収量を増大させることができる。   (5) The exhaust valve 14 is installed at the upstream end of the intermediate cylinder 12 in the flow direction of the exhaust 1. At this time, the valve body rod 19 provided at a substantially central position of the valve body 18 is connected to the intermediate cylinder 12. It is arranged at a substantially central position in the diameter direction D. For this reason, the exhaust gas 1 is agitated by the valve body 18 and the valve body rod 19 into a turbulent state when flowing into the heat recovery flow path 16 in the intermediate cylinder portion 12. As a result, it is possible to increase the amount of heat recovery for recovering the heat of the turbulent exhaust 1 in the heat recovery flow path 16 to the cooling water 2 flowing in the inner cylinder portion 11.

［Ｂ］第２実施形態（図３、図４）
図３は、本発明に係る排気熱回収装置の第２実施形態における非熱回収状態を示し、（Ａ）は横断面図、（Ｂ）は図３（Ａ）のＩＩＩ−ＩＩＩ線に沿う断面図である。また、図４は、図３の排気熱回収装置における熱回収状態を示し、（Ａ）は横断面図、（Ｂ）は図４（Ａ）のＩＶ−ＩＶ線に沿う断面図である。この第２実施形態において、前記第１実施形態と同様な部分については、同一の符号を付すことにより説明を簡略化し、または省略する。 [B] Second Embodiment (FIGS. 3 and 4)
FIG. 3 shows a non-heat recovery state in the second embodiment of the exhaust heat recovery apparatus according to the present invention, where (A) is a cross-sectional view, and (B) is a cross section taken along the line III-III in FIG. FIG. 4 shows a heat recovery state in the exhaust heat recovery apparatus of FIG. 3, wherein (A) is a cross-sectional view, and (B) is a cross-sectional view taken along line IV-IV in FIG. 4 (A). In the second embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description is simplified or omitted.

本第２実施形態の排気熱回収装置２０が前記第１実施形態と異なる点は、中間筒部２１及び外筒部２２が角筒形状に形成された点と、排気バルブ２３が複数のバルブアッセンブリ２４を備えて構成された点である。   The exhaust heat recovery apparatus 20 of the second embodiment is different from the first embodiment in that the intermediate cylinder portion 21 and the outer cylinder portion 22 are formed in a rectangular tube shape, and the exhaust valve 23 has a plurality of valve assemblies. 24 is configured.

各バルブアッセンブリ２４は、例えば四角板形状の弁体２５と、この弁体２５の端部に設けられた弁体棒２６とを有して構成される。このバルブアッセンブリ２４が観音開き構造に複数、例えば本実施形態では一対配置されて排気バルブ２３が構成される。このとき、各バルブアッセンブリ２４の弁体棒２６は、中間筒部２１における排気１の流れ方向上流端であって、中間筒部２１の幅方向または直径方向（本実施形態では幅方向Ｗ）の端部に配置される。   Each valve assembly 24 includes, for example, a square plate-shaped valve body 25 and a valve body rod 26 provided at an end of the valve body 25. A plurality of valve assemblies 24, for example, a pair in the present embodiment, are arranged in a double door structure to constitute the exhaust valve 23. At this time, the valve body rod 26 of each valve assembly 24 is the upstream end in the flow direction of the exhaust 1 in the intermediate cylinder portion 21, and is in the width direction or diameter direction (width direction W in the present embodiment) of the intermediate cylinder portion 21. Arranged at the end.

具体的には、一方のバルブアッセンブリ２４の弁体棒２６と他方のバルブアッセンブリ２４の弁体棒２６は、中間筒部２１の幅方向Ｗにおける対向する両端部にそれぞれ配置されて、両バルブアッセンブリ２４が観音開き構造に構成される。   Specifically, the valve body rod 26 of one valve assembly 24 and the valve body rod 26 of the other valve assembly 24 are respectively disposed at opposite ends of the intermediate cylinder portion 21 in the width direction W, and both valve assemblies are arranged. Reference numeral 24 is configured in a double door structure.

更に、排気バルブ２３を構成する全てのバルブアッセンブリ２４の弁体２５は、その面積及び形状が、中間筒部２１における排気１の流れ方向上流端の流路断面と同等以上に設定される。従って、排気バルブ２３の全閉時（図３）には、複数の全てのバルブアッセンブリ２４の弁体２５によって、中間筒部２１における排気１の流れ方向上流端の流路断面が閉塞される。このとき、外筒部２２内に導入された排気１は、図３の矢印Ｐに示すようにバイパス流路１７を流れ、熱回収流路１６には流れない。   Further, the valve bodies 25 of all the valve assemblies 24 constituting the exhaust valve 23 are set to have the same or larger area and shape as the flow path cross section at the upstream end of the intermediate cylinder portion 21 in the flow direction of the exhaust 1. Therefore, when the exhaust valve 23 is fully closed (FIG. 3), the flow path section at the upstream end in the flow direction of the exhaust 1 in the intermediate cylinder portion 21 is closed by the valve bodies 25 of all the plurality of valve assemblies 24. At this time, the exhaust 1 introduced into the outer cylindrical portion 22 flows through the bypass flow path 17 as shown by the arrow P in FIG. 3 and does not flow into the heat recovery flow path 16.

また、図４に示すように、排気バルブ２３を構成する全てのバルブアッセンブリ２４の弁体２５は、その先端部分２５Ａが、排気バルブ２３の全開時に外筒部２２に接近して、バイパス流路１７における排気１の流れ方向上流端が略閉塞されるよう構成される。このため、排気バルブ２３の全開時には、外筒部２２内の排気１はバイパス流路１７内へ流入せず、図４の矢印Ｑに示すように、バルブアッセンブリ２４の弁体２５に案内されて熱回収流路１６内へ略全量流れる。ここで、本実施形態においても、熱回収流路１６は内筒部１１と中間筒部２１との間に形成され、バイパス流路１７は中間筒部２１と外筒部２２との間に形成される。   Further, as shown in FIG. 4, the valve bodies 25 of all the valve assemblies 24 constituting the exhaust valve 23 have their tip portions 25A approaching the outer cylinder portion 22 when the exhaust valve 23 is fully opened, 17 is configured so that the upstream end in the flow direction of the exhaust 1 is substantially closed. For this reason, when the exhaust valve 23 is fully opened, the exhaust 1 in the outer cylinder portion 22 does not flow into the bypass flow path 17 but is guided to the valve body 25 of the valve assembly 24 as indicated by an arrow Q in FIG. Almost the entire amount flows into the heat recovery flow path 16. Here, also in this embodiment, the heat recovery flow path 16 is formed between the inner cylinder part 11 and the intermediate cylinder part 21, and the bypass flow path 17 is formed between the intermediate cylinder part 21 and the outer cylinder part 22. Is done.

以上のように構成されたことから、本第２実施形態においても、前記第１実施形態の効果（１）〜（４）と同様な効果を奏するほか、次の効果（６）を奏する。   Due to the above configuration, the second embodiment also provides the following effect (6) in addition to the same effects as the effects (1) to (4) of the first embodiment.

（６）排気バルブ２３の全開時に、全てのバルブアッセンブリ２４の弁体２５の先端部分２５Ａが外筒部２２に接近して、バイパス流路１７における排気１の流れ方向上流端が、全てのバルブアッセンブリ２４の弁体２５によって略閉塞される。このため、外筒部２２内からバイパス流路１７へ流れる排気１の流量を略ゼロとし、外筒部２２内の全ての排気１を熱回収流路１６へ導くことができる。この結果、内筒部１１内を流れる冷却水２による排気１の熱回収量を著しく増大させることができる。   (6) When the exhaust valve 23 is fully opened, the tip portions 25A of the valve bodies 25 of all the valve assemblies 24 approach the outer cylinder portion 22, and the upstream end in the flow direction of the exhaust 1 in the bypass flow path 17 is all the valves. The valve body 25 of the assembly 24 is substantially closed. For this reason, the flow rate of the exhaust gas 1 flowing from the outer cylinder part 22 to the bypass flow path 17 can be made substantially zero, and all the exhaust gas 1 in the outer cylinder part 22 can be guided to the heat recovery flow path 16. As a result, the heat recovery amount of the exhaust 1 by the cooling water 2 flowing in the inner cylinder portion 11 can be remarkably increased.

以上各実施形態について説明してきたが、本発明は、上述したような各実施形態の具体的構成に限定されるものではなく、本発明の主旨を逸脱しない範囲で種々変形することができる。例えば、第１及び第２実施形態において、内筒部１１の外表面にフィンなどの凹凸を設けて、排気１の熱回収量を更に増大させてもよい。また、内筒部１１、中間筒部１２、２１、外筒部１３、２２は、断面形状が円形状または多角形状の何れであってもよい。   Each embodiment has been described above, but the present invention is not limited to the specific configuration of each embodiment as described above, and can be variously modified without departing from the gist of the present invention. For example, in the first and second embodiments, the heat recovery amount of the exhaust 1 may be further increased by providing irregularities such as fins on the outer surface of the inner cylinder portion 11. Further, the inner cylindrical portion 11, the intermediate cylindrical portions 12, 21, and the outer cylindrical portions 13, 22 may have a circular or polygonal cross-sectional shape.

１ 排気
２ 冷却水（冷媒）
１０ 排気熱回収装置
１１ 内筒部
１２ 中間筒部
１３ 外筒部
１４ 排気バルブ
１５ スタティックミキサー
１６ 熱回収流路
１７ バイパス流路
１８ 弁体
１９ 弁体棒
２０ 排気熱回収装置
２１ 中間筒部
２２ 外筒部
２３ 排気バルブ
２４ バルブアッセンブリ
２５ 弁体
２５Ａ 先端部分
２６ 弁体棒 1 Exhaust 2 Cooling water (refrigerant)
DESCRIPTION OF SYMBOLS 10 Exhaust heat recovery apparatus 11 Inner cylinder part 12 Intermediate cylinder part 13 Outer cylinder part 14 Exhaust valve 15 Static mixer 16 Heat recovery flow path 17 Bypass flow path 18 Valve body 19 Valve body rod 20 Exhaust heat recovery apparatus 21 Intermediate cylinder part 22 Outside Tube portion 23 Exhaust valve 24 Valve assembly 25 Valve body 25A Tip portion 26 Valve body rod

Claims (4)

内部に冷媒が流動する内筒部と、
この内筒部の外側に所定間隔をもって配置され、前記内筒部との間に、導入された排気の熱を前記内筒部内の冷媒に回収させる熱回収流路を形成する中間筒部と、
この中間筒部の外側に所定間隔をもって配置され、前記中間筒部との間に、バイパスされた排気を流動させるバイパス流路を形成する外筒部と、
前記中間筒部における排気の流れ方向上流端に設置され、排気を前記熱回収流路と前記バイパス流路に切り替えて流す排気バルブと、を有して構成されたことを特徴とする排気熱回収装置。 An inner cylinder part in which refrigerant flows,
An intermediate cylinder portion that is disposed outside the inner cylinder portion at a predetermined interval, and forms a heat recovery flow path for recovering the heat of the introduced exhaust gas to the refrigerant in the inner cylinder portion between the inner cylinder portion,
An outer cylinder portion that is disposed outside the intermediate cylinder portion at a predetermined interval, and forms a bypass flow path for allowing the bypassed exhaust to flow between the intermediate cylinder portion,
An exhaust heat recovery system comprising an exhaust valve installed at an upstream end in the exhaust gas flow direction in the intermediate cylinder portion and configured to switch exhaust gas to the heat recovery flow path and the bypass flow path. apparatus. 前記内筒部には、冷媒を撹拌して流動させるスタティックミキサーが内蔵されたことを特徴とする請求項１に記載の排気熱回収装置。 The exhaust heat recovery apparatus according to claim 1, wherein a static mixer that stirs and flows the refrigerant is built in the inner cylinder portion. 前記排気バルブは、弁体と、この弁体の略中央位置に設けられた弁体棒とを有し、この弁体棒が、中間筒部の幅方向または直径方向の略中央位置に配置されたことを特徴とする請求項１または２に記載の排気熱回収装置。 The exhaust valve includes a valve body and a valve body rod provided at a substantially central position of the valve body, and the valve body rod is disposed at a substantially central position in the width direction or the diameter direction of the intermediate cylinder portion. The exhaust heat recovery apparatus according to claim 1 or 2, characterized in that. 前記排気バルブは、弁体と、この弁体の端部に設けられた弁体棒とを備えてなるバルブアッセンブリが観音開き構造に複数配設されて構成され、前記各バルブアッセンブリの前記弁体棒が、中間筒部における幅方向または直径方向の端部に配置され、
全閉時には、複数の前記バルブアッセンブリの前記弁体により前記中間筒部における排気の流れ方向上流端が閉塞され、全開時には、複数の前記バルブアッセンブリにおける前記弁体の先端部分が外筒部に接近して、バイパス流路における排気の流れ方向上流端が略閉塞されるよう構成されたことを特徴とする請求項１または２に記載の排気熱回収装置。 The exhaust valve is configured by a plurality of valve assemblies each including a valve body and a valve body rod provided at an end of the valve body in a double door structure, and the valve body rod of each valve assembly. Is disposed at the end of the intermediate tube portion in the width direction or the diametrical direction,
When fully closed, the upstream ends of the intermediate cylinder portions in the exhaust flow direction are closed by the valve bodies of the plurality of valve assemblies, and when fully opened, the tip portions of the valve bodies of the plurality of valve assemblies approach the outer cylinder portions. The exhaust heat recovery apparatus according to claim 1, wherein an upstream end in a flow direction of the exhaust gas in the bypass flow path is substantially closed.
JP2012176351A 2012-08-08 2012-08-08 Exhaust heat recovery device Pending JP2014034922A (en)

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