JP5993759B2 - Engine intake cooling system - Google Patents

Engine intake cooling system Download PDF

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JP5993759B2
JP5993759B2 JP2013036644A JP2013036644A JP5993759B2 JP 5993759 B2 JP5993759 B2 JP 5993759B2 JP 2013036644 A JP2013036644 A JP 2013036644A JP 2013036644 A JP2013036644 A JP 2013036644A JP 5993759 B2 JP5993759 B2 JP 5993759B2
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Prior art keywords
cooling water
engine
circuit
temperature
intake air
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JP2014163336A (en
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佳 酒川
佳 酒川
横山　裕一
裕一 横山
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Tokyo Radiator Manufacturing Co Ltd
Calsonic Kansei Corp
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Tokyo Radiator Manufacturing Co Ltd
Calsonic Kansei Corp
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Priority to JP2013036644A priority Critical patent/JP5993759B2/en
Priority to DE112014001021.9T priority patent/DE112014001021T8/en
Priority to PCT/JP2014/053230 priority patent/WO2014132798A1/en
Priority to CN201480010853.1A priority patent/CN105143633A/en
Priority to US14/770,719 priority patent/US20160003127A1/en
Publication of JP2014163336A publication Critical patent/JP2014163336A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0412—Multiple heat exchangers arranged in parallel or in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/12—Arrangements for cooling other engine or machine parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0437—Liquid cooled heat exchangers
    • F02B29/0443—Layout of the coolant or refrigerant circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/24—Layout, e.g. schematics with two or more coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/28—Layout, e.g. schematics with liquid-cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • F01P2003/182—Arrangements or mounting of liquid-to-air heat-exchangers with multiple heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/02—Intercooler
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2060/00—Cooling circuits using auxiliaries
    • F01P2060/16—Outlet manifold
    • 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)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Supercharger (AREA)

Description

この発明は、過給器付きエンジンに備えられる吸気冷却装置に関する。   The present invention relates to an intake air cooling device provided in an engine with a supercharger.

エンジンの排気によって吸気を過給する過給器付きエンジンが一般に用いられている。過給器により吸気が過給されると、吸気温度が高温となる。また、排気を吸気側に再循環させるＥＧＲシステムが備わっている場合は、さらに吸気温度が高温となる場合がある。吸気温度が高温となると燃費効率が低下する虞がある。   An engine with a supercharger that supercharges intake air by exhausting the engine is generally used. When the intake air is supercharged by the supercharger, the intake air temperature becomes high. In addition, when an EGR system that recirculates exhaust gas to the intake side is provided, the intake air temperature may further increase. If the intake air temperature becomes high, the fuel efficiency may decrease.

これを防ぐために、過給された吸気の温度を下げる冷却装置を備えることが行われている。冷却装置は、例えばエンジンの冷却水を吸気通路に流通させ、冷却水によって吸気温度を低下させている。   In order to prevent this, a cooling device that lowers the temperature of the supercharged intake air is provided. The cooling device circulates, for example, engine cooling water in the intake passage, and reduces the intake air temperature with the cooling water.

一方で、エンジンの冷却水は、エンジンの運転に最適な温度に制御されるため、吸気と冷却水との気水温度差が大きくとれず、吸気温度の低下に限度がある。   On the other hand, since the engine coolant is controlled to an optimum temperature for engine operation, the air-water temperature difference between the intake air and the coolant cannot be increased, and there is a limit to the decrease in the intake air temperature.

これに対して、エンジンの冷却水回路の一部を分岐した第２冷却水回路に、第２のラジエタを備え、このラジエタによって低温となった冷却水によって、エンジンに吸気される吸気温度を低下させる内燃機関の冷却装置が知られている（特許文献１参照）。   On the other hand, the second cooling water circuit that branches off a part of the cooling water circuit of the engine is provided with a second radiator, and the temperature of the intake air sucked into the engine is lowered by the cooling water that has become low temperature by this radiator. A cooling device for an internal combustion engine is known (see Patent Document 1).

米国特許出願公開第２００８／００６６６９７号明細書US Patent Application Publication No. 2008/0066697

吸気温度を下げるために冷却水温度を下げると、この低温の冷却水がエンジンに流入する。特にエンジンの暖機時に低温の冷却水温度が流入した場合は、エンジン内部で冷却水温度が低下して、エンジンの暖機が遅れてしまう。エンジンの暖機が遅れてしまうと、エンジンの燃費性能が低下するという問題がある。   When the cooling water temperature is lowered to lower the intake air temperature, this low-temperature cooling water flows into the engine. In particular, when a low-temperature coolant temperature flows in when the engine is warmed up, the coolant temperature falls inside the engine, and the engine warm-up is delayed. If the engine warm-up is delayed, there is a problem that the fuel efficiency of the engine decreases.

本発明は、このような問題点に鑑みてなされてものであり、エンジンの吸気を冷却する冷却装置を備えながら、エンジンの暖機の遅れを改善することができるエンジンの吸気冷却装置を提供することを目的とする。   The present invention has been made in view of such problems, and provides an intake air cooling device for an engine that can improve a delay in warming up the engine while including a cooling device that cools intake air of the engine. For the purpose.

本発明のある態様によると、エンジンの冷却水が流通する冷却水回路と、エンジンの吸気を過給する過給器と、を備えるエンジンにおいて、エンジンに備えられるエンジンの吸気冷却装置であって、冷却水回路は、第１冷却水回路と、第２冷却水回路とを含み、吸気を第１冷却水回路の冷却水により冷却する第１吸気冷却装置と、第１吸気冷却装置により冷却された吸気を第２冷却水回路の冷却水によりさらに冷却する第２吸気冷却装置と、が備えられ、第１冷却水回路は、エンジンから出た冷却水を、第１吸気冷却装置を流通させて再びエンジンに戻し、第２冷却水回路は、エンジンから出た冷却水を、第２吸気冷却装置を流通させて再びエンジンに戻し、エンジンから出て第１吸気冷却装置へと向かう冷却水と、第２吸気冷却装置から出てエンジンへと向かう冷却水と、の間で熱交換を行う熱交換器を備えたことを特徴とする。 According to an aspect of the present invention, in an engine comprising a cooling water circuit through which engine cooling water circulates and a supercharger that supercharges engine intake air, The cooling water circuit includes a first cooling water circuit and a second cooling water circuit, and is cooled by the first intake air cooling device that cools the intake air with the cooling water of the first cooling water circuit, and the first intake air cooling device . A second intake air cooling device that further cools the intake air with the cooling water of the second cooling water circuit, and the first cooling water circuit recirculates the cooling water from the engine through the first intake cooling device. The second cooling water circuit returns the cooling water from the engine to the engine through the second intake air cooling device, and returns to the first cooling air device from the engine to the first intake air cooling device. 2 Get out of the intake air cooling system Characterized by comprising a cooling water towards the engine, the heat exchanger for exchanging heat between the.

上記態様によれば、エンジンから出た第１冷却水回路の冷却水と、第２吸気冷却装置から出た第２冷却水回路の冷却水とが、熱交換器において熱交換を行うので、エンジンへと戻る第２冷却水回路の冷却水温度が上昇して、エンジンのコールドスタート時においても、エンジンの暖機の遅れ改善される。   According to the above aspect, the cooling water in the first cooling water circuit coming out of the engine and the cooling water in the second cooling water circuit coming out of the second intake air cooling device exchange heat in the heat exchanger. The cooling water temperature of the second cooling water circuit that goes back to rises, and the engine warm-up delay is improved even when the engine is cold started.

本発明の第１の実施形態のエンジンを中心とした冷却装置の説明図である。It is explanatory drawing of the cooling device centering on the engine of the 1st Embodiment of this invention. 本発明の第２の実施形態のエンジンを中心とした冷却装置の説明図である。It is explanatory drawing of the cooling device centering on the engine of the 2nd Embodiment of this invention. 本発明の第２の実施形態のコントローラが実行する処理のフローチャートである。It is a flowchart of the process which the controller of the 2nd Embodiment of this invention performs. 本発明の第３の実施形態のエンジンを中心とした冷却装置の説明図である。It is explanatory drawing of the cooling device centering on the engine of the 3rd Embodiment of this invention.

以下、本発明の実施形態を、図面を参照して説明する。   Embodiments of the present invention will be described below with reference to the drawings.

図１は、本発明の第１の実施形態のエンジン１０を中心とした冷却装置１の説明図である。   FIG. 1 is an explanatory diagram of a cooling device 1 centering on an engine 10 according to a first embodiment of the present invention.

第１の実施形態の冷却装置１は、例えば車両に搭載されて、車両の駆動源であるエンジン１０と、過給器（タービン）１８とを備え、過給された吸気の温度を、冷却水（クーラント）を用いて適切に冷却するものである。   The cooling device 1 according to the first embodiment is mounted on a vehicle, for example, and includes an engine 10 that is a drive source of the vehicle and a supercharger (turbine) 18, and the temperature of the supercharged intake air is reduced to cooling water. (Coolant) is used for proper cooling.

図１において、太矢印は高温側冷却水回路３１、細矢印は低温側冷却水回路３２、点線は排気管１６内の排気の流れ、一点鎖線は吸気管１４内の吸気の流れを示す。   In FIG. 1, the thick arrow indicates the high temperature side cooling water circuit 31, the thin arrow indicates the low temperature side cooling water circuit 32, the dotted line indicates the flow of exhaust gas in the exhaust pipe 16, and the alternate long and short dash line indicates the flow of intake air in the intake pipe 14.

冷却装置１は、エンジン１０と、エンジン１０の冷却水を流通させる冷却水回路３０とを備える。   The cooling device 1 includes an engine 10 and a cooling water circuit 30 that distributes the cooling water of the engine 10.

エンジン１０の内部には、冷却水が流通する冷却水流路１１が形成される。冷却水流路１１は冷却水回路３０に連通する。冷却水流路１１には、ウォーターポンプ（Ｗ／Ｐ）１２とサーモスタット（Ｔ／Ｓ）１３とが備えられている。   A cooling water flow path 11 through which cooling water flows is formed inside the engine 10. The cooling water channel 11 communicates with the cooling water circuit 30. The cooling water passage 11 is provided with a water pump (W / P) 12 and a thermostat (T / S) 13.

ウォーターポンプ１２は、冷却水を冷却水流路１１及び冷却水回路３０に循環させる。サーモスタット１３は、冷却水の温度が低い場合にはラジエタ４１をバイパスさせ、冷却水の温度が高い場合には、冷却水をラジエタ４１に経由させて冷却水温度を低下させる。   The water pump 12 circulates the cooling water through the cooling water passage 11 and the cooling water circuit 30. The thermostat 13 bypasses the radiator 41 when the temperature of the cooling water is low, and lowers the cooling water temperature through the radiator 41 when the temperature of the cooling water is high.

エンジン１０には、吸気管１４及び排気管１６が連通する。吸気管１４は、タービン１８により過給される。過給された吸気は、高温側インタクーラ（第１吸気冷却装置）７１及び低温側インタクーラ（第２吸気冷却装置）７２により温度が低下され、温度が低下された吸気がエンジン１０に送られる。排気管１６は、エンジン１０の排気をタービン１８を介して排出する。排気はタービン１８を回転させ、タービン１８の回転により吸気管１４の吸気が過給される。   An intake pipe 14 and an exhaust pipe 16 communicate with the engine 10. The intake pipe 14 is supercharged by the turbine 18. The temperature of the supercharged intake air is reduced by the high temperature side intercooler (first intake air cooling device) 71 and the low temperature side intercooler (second intake air cooling device) 72, and the intake air whose temperature has been reduced is sent to the engine 10. The exhaust pipe 16 discharges the exhaust of the engine 10 via the turbine 18. The exhaust gas rotates the turbine 18, and the intake air in the intake pipe 14 is supercharged by the rotation of the turbine 18.

エンジン１０には、ファン１９が備えられる。ファン１９によりラジエタ４１及びサブラジエタ４２に送風され、これらの冷却が促進される。   The engine 10 is provided with a fan 19. The fan 19 blows air to the radiator 41 and the sub-radiator 42, and cooling of these is promoted.

排気管１６からはＥＧＲ回路２０が分岐する。ＥＧＲ回路２０は、排気の一部を吸気に再循環させる排気再循環装置（ＥＧＲ）を構成する。ＥＧＲ回路２０には、高温側の第１のＥＧＲクーラ（第１排気冷却装置）２１と、その下流側に位置する同じく高温側の第２のＥＧＲクーラ（第２排気冷却装置）２２とが備えられ、ＥＧＲバルブ２３を介して吸気管１４に連通する。   An EGR circuit 20 branches from the exhaust pipe 16. The EGR circuit 20 constitutes an exhaust gas recirculation device (EGR) that recirculates a part of the exhaust gas to the intake air. The EGR circuit 20 includes a first EGR cooler (first exhaust cooling device) 21 on the high temperature side and a second EGR cooler (second exhaust cooling device) 22 located on the downstream side of the EGR circuit 20. And communicates with the intake pipe 14 via the EGR valve 23.

ＥＧＲ回路２０によって排気の一部を吸気に戻すことにより、エンジン１０の燃焼室における酸素濃度を低下させて燃焼温度を低下させることができ、ＮＯｘ等の酸化物の発生が抑制される。再循環される排気の温度は低いほど効率が高いため、排気温度を低下させるための高温側の第１のＥＧＲクーラ２１及びその下流側に位置する同じく高温側の第２のＥＧＲクーラ２２を設けている。   By returning a part of the exhaust gas to the intake air by the EGR circuit 20, the oxygen concentration in the combustion chamber of the engine 10 can be lowered to lower the combustion temperature, and the generation of oxides such as NOx is suppressed. The lower the temperature of the exhaust gas that is recirculated, the higher the efficiency. Therefore, the first EGR cooler 21 on the high temperature side for lowering the exhaust temperature and the second EGR cooler 22 on the downstream side are also provided. ing.

吸気管１４において、高温側インタクーラ７１と低温側インタクーラ７２とには、それぞれに冷却水が流通し、タービン１８により過給された吸気の温度を低下させる。吸気温度は場合により高温となり、冷却水との温度差が大きいため、高温側インタクーラ７１と低温側インタクーラ７２との二段階で吸気温度を低下させている。高温側インタクーラ７１によって温度が低下された吸気を、さらに低温側インタクーラ７２によって温度を低下させる。吸気管１４において、高温側インタクーラ７１及び低温側インタクーラ７２の下流側に、ＥＧＲバルブ２３が備えられる。ＥＧＲバルブ２３は、ＥＧＲ回路２０を経由して吸気管１４に再循環する排気の量を制御する。   In the intake pipe 14, cooling water flows through the high-temperature side intercooler 71 and the low-temperature side intercooler 72, respectively, and reduces the temperature of the intake air supercharged by the turbine 18. Since the intake air temperature becomes high in some cases and the temperature difference with the cooling water is large, the intake air temperature is lowered in two stages of the high temperature side intercooler 71 and the low temperature side intercooler 72. The intake air whose temperature has been lowered by the high temperature side intercooler 71 is further lowered by the low temperature side intercooler 72. In the intake pipe 14, an EGR valve 23 is provided downstream of the high temperature side intercooler 71 and the low temperature side intercooler 72. The EGR valve 23 controls the amount of exhaust gas recirculated to the intake pipe 14 via the EGR circuit 20.

冷却水回路３０は、高温側冷却水回路（第１冷却水回路）３１と低温側冷却水回路（第２冷却水回路）３２とを備える。   The cooling water circuit 30 includes a high temperature side cooling water circuit (first cooling water circuit) 31 and a low temperature side cooling water circuit (second cooling water circuit) 32.

高温側冷却水回路３１は、エンジン１０の冷却水流路１１のほか、ラジエタ（第１ラジエタ）４１、高温側の第１のＥＧＲクーラ２１及びその下流側に位置する同じく高温側の第２のＥＧＲクーラ２２を経由する冷却水回路により構成される。   The high temperature side cooling water circuit 31 includes a cooling water flow path 11 of the engine 10, a radiator (first radiator) 41, a high temperature side first EGR cooler 21, and a second high temperature side second EGR located downstream thereof. It is constituted by a cooling water circuit that passes through the cooler 22.

高温側冷却水回路３１においては、エンジン１０のウォーターポンプ１２から送出される冷却水は、エンジンの冷却水流路１１を循環すると共に、ラジエタ４１を経由して、再びエンジン１０の冷却水流路に戻る。また、ウォーターポンプ１２から送出される冷却水の一部は、エンジン１０を出て、高温側の第１のＥＧＲクーラ２１及びその下流側に位置する同じく高温側の第２のＥＧＲクーラ２２を経由して、再びエンジン１０の冷却水流路１１に戻る。また、ウォーターポンプ１２から送出される冷却水の一部は、エンジン１０を出て、熱交換器７６、及び高温側インタクーラ７１を経由して、再びエンジン１０の冷却水流路１１に戻る。   In the high temperature side cooling water circuit 31, the cooling water sent from the water pump 12 of the engine 10 circulates through the cooling water flow path 11 of the engine and returns to the cooling water flow path of the engine 10 again via the radiator 41. . A part of the cooling water sent out from the water pump 12 exits the engine 10 and passes through the first EGR cooler 21 on the high temperature side and the second EGR cooler 22 on the downstream side of the high temperature side. Then, it returns to the cooling water flow path 11 of the engine 10 again. A part of the cooling water sent from the water pump 12 exits the engine 10 and returns to the cooling water flow path 11 of the engine 10 again via the heat exchanger 76 and the high temperature side intercooler 71.

低温側冷却水回路３２は、サーモスタット４４、サブラジエタ（第２ラジエタ）４２、低温側インタクーラ７２及び熱交換器７６を経由する冷却水回路により構成される。   The low temperature side cooling water circuit 32 includes a thermostat 44, a sub-radiator (second radiator) 42, a low temperature side intercooler 72, and a cooling water circuit that passes through the heat exchanger 76.

エンジン１０のウォーターポンプから送出される冷却水は、エンジン１０を出てサーモスタット４４及びサブラジエタ４２を経由して低温側インタクーラ７２に送られる。低温側インタクーラ７２を出た冷却水は熱交換器７６を介して、再びエンジン１０の冷却水流路１１へと戻る。サーモスタット４４は、低温側冷却水回路３２の冷却水の温度が低い場合はサブラジエタ４２をバイパスさせて、冷却水温度がさらに低下することを防ぐ。   Cooling water delivered from the water pump of the engine 10 exits the engine 10 and is sent to the low temperature side intercooler 72 via the thermostat 44 and the sub-radiator 42. The cooling water exiting the low temperature side intercooler 72 returns to the cooling water flow path 11 of the engine 10 again through the heat exchanger 76. The thermostat 44 bypasses the sub radiator 42 when the temperature of the cooling water in the low temperature side cooling water circuit 32 is low, and prevents the cooling water temperature from further decreasing.

このように、低温側冷却水回路３２は、冷却水がサブラジエタ４２を通過することにより、高温側冷却水回路３１よりも低温の冷却水が流通するように構成されている。   As described above, the low temperature side cooling water circuit 32 is configured such that the cooling water passes through the sub radiator 42 so that the cooling water having a temperature lower than that of the high temperature side cooling water circuit 31 flows.

熱交換器７６は、高温側冷却水回路３１においてエンジン１０から出た冷却水と、低温側冷却水回路３２において低温側インタクーラ７２から出た冷却水と、で熱交換を行う。熱交換器７６は、例えば二重管構造を有し、高温側冷却水回路３１の冷却水と低温側冷却水回路３２の冷却水とが互いに対向流となるように構成することにより熱交換を行う。   The heat exchanger 76 performs heat exchange between the cooling water output from the engine 10 in the high temperature side cooling water circuit 31 and the cooling water output from the low temperature side intercooler 72 in the low temperature side cooling water circuit 32. The heat exchanger 76 has, for example, a double-pipe structure, and performs heat exchange by configuring the cooling water of the high temperature side cooling water circuit 31 and the cooling water of the low temperature side cooling water circuit 32 to face each other. Do.

このように構成された本発明の第１の実施形態の動作を説明する。   The operation of the thus configured first embodiment of the present invention will be described.

エンジン１０が停止してから長時間経過した場合など、エンジン１０及び冷却水の温度が低い状態からエンジン１０を始動（コールドスタート）するときは、エンジン１０の摺動抵抗が大きく、また、触媒の効率も低下しているので、エンジン１０の動作効率が低く燃費性能が悪化すると共に、排気中の規制物質も増加する。このため、エンジン１０のコールドスタート時にはエンジン１０の暖機をできるだけ速やかに行う必要がある。   When the engine 10 is started (cold start) from a state where the temperature of the engine 10 and the cooling water is low, such as when a long time has passed since the engine 10 was stopped, the sliding resistance of the engine 10 is large, and the catalyst Since the efficiency is also lowered, the operating efficiency of the engine 10 is low and the fuel efficiency is deteriorated, and the regulated substances in the exhaust also increase. For this reason, it is necessary to warm up the engine 10 as quickly as possible when the engine 10 is cold-started.

そこで、本発明の第１の実施形態の冷却装置１は、前述のような構成により、次のように動作する。   Therefore, the cooling device 1 according to the first embodiment of the present invention operates as follows with the above-described configuration.

エンジン１０において、ウォーターポンプ１２によって冷却水流路１１を冷却水が循環する。このとき、冷却水温度が低い場合は、サーモスタット１３が切り換えられ、ラジエタ４１をバイパスする。これにより、エンジン１０の運転により冷却水が加熱されて、冷却水温度が上昇する。   In the engine 10, the cooling water circulates through the cooling water passage 11 by the water pump 12. At this time, when the cooling water temperature is low, the thermostat 13 is switched to bypass the radiator 41. Thereby, the cooling water is heated by the operation of the engine 10, and the cooling water temperature rises.

冷却水流路１１の流通する冷却水の一部は、高温側冷却水回路３１に流れ、高温側の第１のＥＧＲクーラ２１及びその下流側に位置する同じく高温側の第２のＥＧＲクーラ２２を経由して冷却水流路１１に戻る。また、高温側冷却水回路３１の冷却水の一部は、高温側インタクーラ７１を経由して、冷却水流路１１に戻る。   A part of the cooling water flowing through the cooling water flow passage 11 flows into the high temperature side cooling water circuit 31 and passes through the first high temperature side EGR cooler 21 and the second high temperature side EGR cooler 22 located downstream thereof. It returns to the cooling water flow path 11 via. Further, part of the cooling water in the high temperature side cooling water circuit 31 returns to the cooling water flow path 11 via the high temperature side intercooler 71.

このように、高温側冷却水回路３１では、高温の排気と接触することで冷却水の温度が低下しないように構成されている。また、高温側インタクーラ７１において、過給された高温の吸気と接触することで冷却水の温度の低下が抑えられる。これにより、エンジン１０のコールドスタート時にも、比較的高温の冷却水が流通することで、エンジン１０の暖機の遅れが改善される。   As described above, the high temperature side cooling water circuit 31 is configured so that the temperature of the cooling water does not decrease by being in contact with the high temperature exhaust gas. Further, in the high temperature side intercooler 71, the temperature of the cooling water is prevented from lowering by contacting the supercharged high temperature intake air. Thereby, even when the engine 10 is cold-started, the relatively high-temperature cooling water flows, so that the delay in warming up the engine 10 is improved.

冷却水流路１１を流通する冷却水の一部は、低温側冷却水回路３２に流れ、サブラジエタ４２、低温側インタクーラ７２及び熱交換器７６を経由して冷却水流路１１に戻る。低温側冷却水回路３２の冷却水は、サブラジエタ４２で外気と熱交換を行うことで温度が低下する。温度が低下した冷却水は低温側インタクーラ７２において過給された吸気と熱交換を行うことにより、吸気温度を低下させると共に冷却水温度が上昇する。低温側インタクーラ７２を出た冷却水は、熱交換器７６で高温側冷却水回路３１の冷却水と熱交換を行うことでさらに温度が上昇する。温度が上昇した冷却水は、再びエンジン１０へと戻る。高温側冷却水回路３１の冷却水は、熱交換器７６で低温側冷却水回路３２の冷却水と熱交換を行うことで若干温度が低下するが、高温側インタクーラ７１において過給された高温の吸気と熱交換を行うことにより温度が上昇して再びエンジン１０へと戻る。   A part of the cooling water flowing through the cooling water channel 11 flows into the low temperature side cooling water circuit 32 and returns to the cooling water channel 11 via the sub radiator 42, the low temperature side intercooler 72 and the heat exchanger 76. The temperature of the cooling water in the low-temperature side cooling water circuit 32 is lowered by exchanging heat with the outside air by the sub radiator 42. The cooling water whose temperature has been lowered exchanges heat with the intake air supercharged in the low-temperature side intercooler 72, thereby lowering the intake air temperature and raising the cooling water temperature. The temperature of the cooling water exiting the low-temperature side intercooler 72 is further increased by exchanging heat with the cooling water in the high-temperature side cooling water circuit 31 by the heat exchanger 76. The cooling water whose temperature has risen returns to the engine 10 again. The temperature of the cooling water of the high temperature side cooling water circuit 31 is slightly lowered by exchanging heat with the cooling water of the low temperature side cooling water circuit 32 by the heat exchanger 76, but the high temperature supercooled by the high temperature side intercooler 71 is reduced. By performing heat exchange with intake air, the temperature rises and returns to the engine 10 again.

このように、低温側冷却水回路３２では、サブラジエタ４２において冷却水温度が低下した冷却水により、低温側インタクーラ７２で過給された吸気の温度を低下させる。   In this way, in the low temperature side cooling water circuit 32, the temperature of the intake air supercharged by the low temperature side intercooler 72 is lowered by the cooling water whose cooling water temperature has been lowered in the sub radiator 42.

温度が低下した冷却水は、低温側インタクーラ７２と熱交換器７６とを通過することにより温度が再び上昇させられて、この冷却水が再びエンジン１０に戻るように構成されている。この冷却水は、高温側冷却水回路３１と低温側冷却水回路３２とが合流してエンジン１０に戻る。このとき、高温側冷却水回路３１と低温側冷却水回路３２とが混じり合う。この構成により、低温側冷却水回路３２において、エンジン１０に戻る冷却水の温度が低下することがないので、エンジン１０の暖機の遅れが改善される。   The cooling water whose temperature has decreased is configured such that the temperature is raised again by passing through the low-temperature intercooler 72 and the heat exchanger 76, and this cooling water returns to the engine 10 again. The high-temperature side cooling water circuit 31 and the low-temperature side cooling water circuit 32 merge and return to the engine 10. At this time, the high temperature side cooling water circuit 31 and the low temperature side cooling water circuit 32 are mixed. With this configuration, in the low temperature side cooling water circuit 32, the temperature of the cooling water that returns to the engine 10 does not decrease, so that the delay in warming up the engine 10 is improved.

以上のように、本発明の第１の実施形態では、エンジン１０から出た高温側冷却水回路３１の冷却水と、低温側インタクーラ７２から出た低温側冷却水回路３２の冷却水とが、熱交換器７６において熱交換を行うように構成した。   As described above, in the first embodiment of the present invention, the cooling water of the high-temperature side cooling water circuit 31 exiting from the engine 10 and the cooling water of the low-temperature side cooling water circuit 32 exiting from the low-temperature side intercooler 72 are: The heat exchanger 76 is configured to perform heat exchange.

特に、低温側冷却水回路３２は、サブラジエタ４２によって冷却水の温度を低下させているので、過給された吸気の温度を低下させることができ、エンジンの動作効率を向上しつつ、ＮＯｘの発生を抑制できる。   In particular, since the low-temperature side cooling water circuit 32 reduces the temperature of the cooling water by the sub-radiator 42, the temperature of the supercharged intake air can be reduced, and the generation efficiency of the engine can be improved while generating NOx. Can be suppressed.

エンジン１０へと戻る低温側冷却水回路３２の冷却水は、熱交換器７６を通過することによって温度が上昇するので、エンジン１０の暖機の遅れが改善される。高温側インタクーラ７１に流れる高温側冷却水回路３１の冷却水は、熱交換器７６を通過することによって温度が低下するので、高温側インタクーラ７１において吸気温度を低下させることができる。高温側インタクーラ７１を出た冷却水は、エンジン１０の手前で低温側冷却水回路３２の冷却水と合流してエンジン１０に流れるので、エンジン１０に流れる冷却水の温度が上昇して、エンジン１０の暖機の遅れが改善される。   Since the temperature of the cooling water in the low temperature side cooling water circuit 32 returning to the engine 10 rises by passing through the heat exchanger 76, the warm-up delay of the engine 10 is improved. Since the temperature of the cooling water in the high temperature side cooling water circuit 31 flowing through the high temperature side intercooler 71 is lowered by passing through the heat exchanger 76, the intake air temperature can be lowered in the high temperature side intercooler 71. The cooling water exiting the high temperature side intercooler 71 merges with the cooling water in the low temperature side cooling water circuit 32 before the engine 10 and flows to the engine 10, so that the temperature of the cooling water flowing to the engine 10 rises and the engine 10 The warm-up delay is improved.

これにより、エンジン１０のコールドスタート時にも、エンジン１０の暖機の遅れが改善される。   Thereby, the warm-up delay of the engine 10 is improved even when the engine 10 is cold started.

次に、本発明の第２の実施形態について説明する。   Next, a second embodiment of the present invention will be described.

図３は、本発明の第２の実施形態のエンジン１０を中心とした冷却装置１の説明図である。なお、第１の実施形態と同一の構成には同一の符号を付し、その説明は省略する。   FIG. 3 is an explanatory diagram of the cooling device 1 centering on the engine 10 according to the second embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the structure same as 1st Embodiment, and the description is abbreviate | omitted.

第２の実施形態では、低温側冷却水回路３２おいて、熱交換器７６の入口側にバルブ８５を設け、熱交換器７６をバイパスするバイパス通路８６を設けた。このバルブ７５の開閉によって、熱交換器７６を流れる低温側冷却水回路３２の冷却水を制御する。   In the second embodiment, in the low temperature side cooling water circuit 32, the valve 85 is provided on the inlet side of the heat exchanger 76, and the bypass passage 86 that bypasses the heat exchanger 76 is provided. By opening and closing the valve 75, the cooling water of the low-temperature side cooling water circuit 32 flowing through the heat exchanger 76 is controlled.

また、第２の実施形態では、高温側冷却水回路３１から熱交換器７６へと流入する冷却水の水温を検出する第１水温計８１と低温側冷却水回路３２から熱交換器７６へと流入する冷却水の水温を検出する第２水温計８２と、を備えた。これら第１水温計８１が検出した高温側冷却水回路３１の水温ＴｗＨと、第２水温計８２が検出した低温側冷却水回路３２の水温ＴｗＬとに基づいて、バルブ８５の開閉を制御するコントローラ６０を備えた。   Moreover, in 2nd Embodiment, the 1st water temperature meter 81 which detects the water temperature of the cooling water which flows into the heat exchanger 76 from the high temperature side cooling water circuit 31, and the low temperature side cooling water circuit 32 to the heat exchanger 76. And a second water temperature gauge 82 for detecting the temperature of the cooling water flowing in. A controller that controls opening and closing of the valve 85 based on the water temperature TwH of the high-temperature side cooling water circuit 31 detected by the first water temperature gauge 81 and the water temperature TwL of the low-temperature side cooling water circuit 32 detected by the second water temperature gauge 82. 60.

次に、このように構成された第２の実施形態の冷却装置１の動作を説明する。   Next, operation | movement of the cooling device 1 of 2nd Embodiment comprised in this way is demonstrated.

図３は、本発明の第２の実施形態のコントローラ６０が実行する冷却水回路の制御のフローチャートである。   FIG. 3 is a flowchart of the control of the cooling water circuit executed by the controller 60 according to the second embodiment of the present invention.

図３のフローチャートは、エンジン１０が起動されたときにコントローラ６０により実行される。   The flowchart of FIG. 3 is executed by the controller 60 when the engine 10 is started.

まず、コントローラ６０は、低温側冷却水回路３２において、冷却水温度がサーモスタット４４の開弁温度に到達したか否かを確認する（ステップＳ１０）。冷却水温度がサーモスタット４４の開弁温度に到達していない場合は、冷却水温度が低い状態であると判定できるため、第１水温計８１及び第２水温計８２の誤動作を判定できる。なお、冷却水温度ではなく、サーモスタット４４が開弁したか否かを確認してもよい。   First, the controller 60 checks whether or not the coolant temperature has reached the valve opening temperature of the thermostat 44 in the low-temperature side coolant circuit 32 (step S10). When the cooling water temperature does not reach the valve opening temperature of the thermostat 44, it can be determined that the cooling water temperature is in a low state, and therefore malfunction of the first water temperature meter 81 and the second water temperature meter 82 can be determined. In addition, you may confirm not the cooling water temperature but whether the thermostat 44 opened.

次に、コントローラ６０は、第１水温計８１から、高温側冷却水回路３１の熱交換器７６の入口側の水温ＴｗＨを検出する。また、第２水温計８２から、低温側冷却水回路３２の熱交換器７６の出口側の水温ＴｗＬを検出する。そして、水温ＴｗＬが水温ＴｗＨよりも低いか否かを判定する（ステップＳ２０）。   Next, the controller 60 detects the water temperature TwH on the inlet side of the heat exchanger 76 of the high temperature side cooling water circuit 31 from the first water temperature gauge 81. Further, the water temperature TwL on the outlet side of the heat exchanger 76 of the low temperature side cooling water circuit 32 is detected from the second water temperature gauge 82. And it is determined whether water temperature TwL is lower than water temperature TwH (step S20).

水温ＴｗＬが水温ＴｗＨよりも低いと判定した場合は、ステップＳ３０に移行して、コントローラ６０は、バルブ８５を開くように制御する。これにより、低温側冷却水回路３２の冷却水が熱交換器７６を通過するようになり、熱交換器７６において、低温側冷却水回路３２の冷却水と高温側冷却水回路３１の冷却水とが熱交換を行う。その後、ステップＳ４０に移行する。   When it determines with water temperature TwL being lower than water temperature TwH, it transfers to step S30 and the controller 60 controls so that the valve | bulb 85 may be opened. Thereby, the cooling water of the low temperature side cooling water circuit 32 comes to pass through the heat exchanger 76, and in the heat exchanger 76, the cooling water of the low temperature side cooling water circuit 32 and the cooling water of the high temperature side cooling water circuit 31 Performs heat exchange. Thereafter, the process proceeds to step S40.

ステップＳ４０では、コントローラ６０は、水温ＴｗＬが水温ＴｗＨよりも高いか否かを判定する。水温ＴｗＬが水温ＴｗＨ未満である場合は、ステップＳ４０の処理を繰り返し、待機する。この場合は、バルブ８５は開いたままであり、熱交換器７６において、低温側冷却水回路３２の冷却水と高温側冷却水回路３１の冷却水とが熱交換を行う。   In step S40, the controller 60 determines whether or not the water temperature TwL is higher than the water temperature TwH. When the water temperature TwL is lower than the water temperature TwH, the process of step S40 is repeated and waits. In this case, the valve 85 remains open, and in the heat exchanger 76, the cooling water in the low temperature side cooling water circuit 32 and the cooling water in the high temperature side cooling water circuit 31 perform heat exchange.

水温ＴｗＬが水温ＴｗＨよりも高いと判定した場合は、ステップＳ５０に移行し、コントローラ６０は、バルブ８５を閉じるように制御する。これにより、低温側冷却水回路３２の冷却水は、熱交換器７６を通過せずバイパス通路８６を通過するようになり、熱交換器７６を流れる高温側冷却水回路３１の冷却水との間で熱交換は行われない。その後、ステップＳ６０に移行する。   When it is determined that the water temperature TwL is higher than the water temperature TwH, the process proceeds to step S50, and the controller 60 controls the valve 85 to be closed. Thereby, the cooling water of the low temperature side cooling water circuit 32 does not pass through the heat exchanger 76 but passes through the bypass passage 86, and between the cooling water of the high temperature side cooling water circuit 31 flowing through the heat exchanger 76. There is no heat exchange. Thereafter, the process proceeds to step S60.

ステップＳ２０において、水温ＴｗＬが水温ＴｗＨ以上であると判定した場合は、ステップＳ３０及びＳ４０の処理を行うことなく、すなわち、バルブ８５を開くことなくステップＳ５０に移行し、コントローラ６０は、バルブ８５を閉じるように制御する。   In Step S20, when it is determined that the water temperature TwL is equal to or higher than the water temperature TwH, the process proceeds to Step S50 without performing the processing of Steps S30 and S40, that is, without opening the valve 85, and the controller 60 Control to close.

ステップＳ６０では、コントローラ６０は、エンジン１０の運転が停止されたか否かを判定する。エンジン１０が運転中である場合は、ステップ２０に戻り、処理を繰り返す。エンジン１０の運転が停止された場合は、本フローチャートによる処理を終了する。   In step S60, the controller 60 determines whether or not the operation of the engine 10 has been stopped. If the engine 10 is in operation, the process returns to step 20 and the process is repeated. When the operation of the engine 10 is stopped, the process according to this flowchart is terminated.

このように第２の実施形態の冷却装置１では、コントローラ６０が、熱交換器７６において、低温側冷却水回路３２の水温ＴｗＬと、高温側冷却水回路３１の水温ＴｗＨとの温度に基づいて、バルブ８５を開閉して熱交換を行わせるか否かを決定する。   Thus, in the cooling device 1 of the second embodiment, the controller 60 uses the heat exchanger 76 based on the temperature of the water temperature TwL of the low temperature side cooling water circuit 32 and the water temperature TwH of the high temperature side cooling water circuit 31. Then, it is determined whether or not heat exchange is performed by opening and closing the valve 85.

すなわち、熱交換器７６に流入する低温側冷却水回路３２の冷却水の温度ＴｗＬが高温側冷却水回路３１の冷却水の温度ＴｗＨよりも低い場合は、熱交換器７６において熱交換を行う。これにより、低温側冷却水回路３２の冷却水温度を上昇させることができて、エンジン１０に流入する冷却水の温度が低下することなく、エンジンの暖機の遅れが改善される。また、熱交換器７６における熱交換により、高温側冷却水回路３１の冷却水温度を低下させることができて、高温側インタクーラ７１において過給された吸気の温度をより冷却することができる。   That is, when the temperature TwL of the cooling water in the low temperature side cooling water circuit 32 flowing into the heat exchanger 76 is lower than the temperature TwH of the cooling water in the high temperature side cooling water circuit 31, heat exchange is performed in the heat exchanger 76. Thereby, the cooling water temperature of the low temperature side cooling water circuit 32 can be raised, and the engine warm-up delay is improved without lowering the temperature of the cooling water flowing into the engine 10. Further, the heat exchange in the heat exchanger 76 can reduce the cooling water temperature of the high temperature side cooling water circuit 31, thereby further cooling the temperature of the intake air supercharged in the high temperature side intercooler 71.

一方で、熱交換器７６に流入する低温側冷却水回路３２の冷却水の温度ＴｗＬよりも高温側冷却水回路３１の冷却水の温度ＴｗＨが低い場合は、熱交換器７６での熱交換を行なわない。これにより、低温側冷却水回路３２の冷却水よりも低温の冷却水と熱交換を行わないことで、エンジン１０に流入する冷却水の温度が低下することなく、エンジンの暖機の遅れが改善される。また、高温側冷却水回路３１の冷却水温度がより高温の冷却水と熱交換を行わないことで、高温側インタクーラ７１において過給された吸気の温度をより冷却することができる。   On the other hand, when the temperature TwH of the cooling water in the high temperature side cooling water circuit 31 is lower than the temperature TwL of the cooling water in the low temperature side cooling water circuit 32 flowing into the heat exchanger 76, the heat exchange in the heat exchanger 76 is performed. Don't do it. Accordingly, heat exchange with the cooling water having a temperature lower than that of the cooling water in the low-temperature side cooling water circuit 32 is not performed, so that the temperature of the cooling water flowing into the engine 10 does not decrease and the delay in warming up the engine is improved. Is done. Moreover, the temperature of the high-temperature side cooling water circuit 31 does not exchange heat with the higher-temperature cooling water, so that the temperature of the intake air supercharged in the high-temperature side intercooler 71 can be further cooled.

次に、本発明の第３の実施形態について説明する。   Next, a third embodiment of the present invention will be described.

図４は、本発明の第３の実施形態のエンジン１０を中心とした冷却装置１の説明図である。なお、第１及び第２の実施形態と同一の構成には同一の符号を付し、その説明は省略する。   FIG. 4 is an explanatory diagram of the cooling device 1 centering on the engine 10 according to the third embodiment of the present invention. In addition, the same code | symbol is attached | subjected to the structure same as 1st and 2nd embodiment, and the description is abbreviate | omitted.

第３実施形態では、第１又は第２実施形態における高温側の第２のＥＧＲクーラ２２に代えて低温側の第３のＥＧＲクーラ２４を備え、これに低温側冷却水回路３２の冷却水が流入するように構成した。また、ＥＧＲ回路２０に備えられる高温側の第１のＥＧＲクーラ２１に流入する高温側冷却水回路３１の冷却水と、低温側の第３のＥＧＲクーラ２４から出た低温側冷却水回路３２の冷却水とで熱交換を行う第２熱交換器４６を備えた。前述のように、エンジン１０の吸気温度は低いほど効率がよいので、ＥＧＲにより再循環される排気温度を低下させるために、低温側の第３のＥＧＲクーラ２４にサブラジエタ４２から出た低温の冷却水が流れるように構成した。   In the third embodiment, a low temperature side third EGR cooler 24 is provided instead of the high temperature side second EGR cooler 22 in the first or second embodiment, and the cooling water of the low temperature side cooling water circuit 32 is provided to this. It was configured to flow in. In addition, the cooling water of the high temperature side cooling water circuit 31 flowing into the first EGR cooler 21 on the high temperature side provided in the EGR circuit 20 and the low temperature side cooling water circuit 32 exiting from the third EGR cooler 24 on the low temperature side. A second heat exchanger 46 that performs heat exchange with the cooling water is provided. As described above, the lower the intake air temperature of the engine 10, the higher the efficiency. Therefore, in order to reduce the exhaust gas temperature recirculated by EGR, the low temperature cooling from the sub-radiator 42 to the third EGR cooler 24 on the low temperature side. It was configured to allow water to flow.

高温側冷却水回路３１においては、エンジン１０のウォーターポンプ１２から送出される冷却水の一部は、エンジン１０を出て、第２熱交換器４６及び高温側の第１のＥＧＲクーラ２１を経由して、再びエンジン１０の冷却水流路１１に戻る。   In the high temperature side cooling water circuit 31, a part of the cooling water sent from the water pump 12 of the engine 10 exits the engine 10 and passes through the second heat exchanger 46 and the high temperature side first EGR cooler 21. Then, it returns to the cooling water flow path 11 of the engine 10 again.

低温側冷却水回路３２においては、サブラジエタ４２を出た冷却水の一部が、低温側の第３のＥＧＲクーラ２４に送られる。低温側の第３のＥＧＲクーラ２４を出た冷却水は第２熱交換器４６を介して、再びエンジン１０の冷却水流路１１へと戻る。   In the low temperature side cooling water circuit 32, a part of the cooling water that has exited the sub radiator 42 is sent to the third EGR cooler 24 on the low temperature side. The cooling water that has exited the third EGR cooler 24 on the low temperature side returns to the cooling water flow path 11 of the engine 10 again via the second heat exchanger 46.

第２熱交換器４６は、高温側冷却水回路３１においてエンジン１０から出た冷却水と、低温側冷却水回路３２において低温側の第３のＥＧＲクーラ２４から出た冷却水と、で熱交換を行う。第２熱交換器４６は、熱交換器７６と同様に、例えば二重管構造を有し、高温側冷却水回路３１の冷却水と低温側冷却水回路３２の冷却水とが互いに対向流となるように構成することにより熱交換を行う。   The second heat exchanger 46 exchanges heat between the cooling water exiting from the engine 10 in the high temperature side cooling water circuit 31 and the cooling water exiting from the third EGR cooler 24 on the low temperature side in the low temperature side cooling water circuit 32. I do. Similarly to the heat exchanger 76, the second heat exchanger 46 has, for example, a double pipe structure, and the cooling water of the high temperature side cooling water circuit 31 and the cooling water of the low temperature side cooling water circuit 32 are opposed to each other. The heat exchange is performed by configuring as described above.

このように、第３の実施形態では、ＥＧＲにより再循環される排気を冷却するために、高温側の第１のＥＧＲクーラ２１と低温側の第３のＥＧＲクーラ２４とを吸気管１４に設けたことは前述の第１及び第２実施例と共通であるが、低温側の第３のＥＧＲクーラ２４は、サブラジエタ４２において冷却水温度が低下した冷却水によって排気温度を低下させるように構成した。   Thus, in the third embodiment, the intake pipe 14 is provided with the first EGR cooler 21 on the high temperature side and the third EGR cooler 24 on the low temperature side in order to cool the exhaust gas recirculated by the EGR. This is the same as in the first and second embodiments described above, but the third EGR cooler 24 on the low temperature side is configured to lower the exhaust temperature by the cooling water whose cooling water temperature has decreased in the sub radiator 42. .

高温側冷却水回路３１では、高温の排気と接触することで冷却水の温度が低下しないように構成されているので、エンジン１０のコールドスタート時にも、比較的高温の冷却水が流通することで、エンジン１０の暖機の遅れが改善される。   The high temperature side cooling water circuit 31 is configured so that the temperature of the cooling water does not decrease by contacting with the high temperature exhaust gas. Therefore, even when the engine 10 is cold started, the relatively high temperature cooling water flows. The delay in warming up the engine 10 is improved.

また、低温側冷却水回路３２では、サブラジエタ４２によって温度が低下された冷却水が、低温側の第３のＥＧＲクーラ２４及び第２熱交換器４６を経由して冷却水流路１１に戻る。低温側冷却水回路３２の冷却水は、低温側の第３のＥＧＲクーラ２４において排気と熱交換を行うことにより、排気温度を低下させると共に冷却水温度は上昇する。低温側の第３のＥＧＲクーラ２４を出た冷却水は、第２熱交換器４６で高温側冷却水回路３１の冷却水と熱交換を行うことでさらに温度が上昇する。温度が上昇した冷却水は、再びエンジン１０へと戻る。   Further, in the low temperature side cooling water circuit 32, the cooling water whose temperature has been lowered by the sub radiator 42 returns to the cooling water flow path 11 via the low temperature side third EGR cooler 24 and the second heat exchanger 46. The cooling water in the low temperature side cooling water circuit 32 is subjected to heat exchange with the exhaust gas in the low temperature side third EGR cooler 24, thereby lowering the exhaust gas temperature and increasing the cooling water temperature. The temperature of the cooling water exiting the third EGR cooler 24 on the low temperature side is further increased by exchanging heat with the cooling water in the high temperature side cooling water circuit 31 in the second heat exchanger 46. The cooling water whose temperature has risen returns to the engine 10 again.

これら高温側冷却水回路３１の冷却水と低温側冷却水回路３２の冷却水とはエンジン１０の手前で合流して、エンジン１０に戻る。この構成により、低温側冷却水回路３２において、エンジン１０に戻る冷却水の温度が低下することがないので、エンジン１０の暖機の遅れが改善される。   The cooling water of the high temperature side cooling water circuit 31 and the cooling water of the low temperature side cooling water circuit 32 merge before the engine 10 and return to the engine 10. With this configuration, in the low temperature side cooling water circuit 32, the temperature of the cooling water that returns to the engine 10 does not decrease, so that the delay in warming up the engine 10 is improved.

なお、第３の実施形態においても、コントローラ６０が、低温側冷却水回路３２の水温と高温側冷却水回路３１の水温とに基づいて、第２熱交換器４６をバイパスさせるか否かを決定してもよい。   Also in the third embodiment, the controller 60 determines whether or not to bypass the second heat exchanger 46 based on the water temperature of the low temperature side cooling water circuit 32 and the water temperature of the high temperature side cooling water circuit 31. May be.

低温側冷却水回路３２おいて、第２熱交換器４６の入口側にバルブ６５を設け、第２熱交換器４６をバイパスするバイパス通路６６を設ける。このバルブ６５の開閉によって、第２熱交換器４６を流れる低温側冷却水回路３２の冷却水を制御する。   In the low temperature side cooling water circuit 32, a valve 65 is provided on the inlet side of the second heat exchanger 46, and a bypass passage 66 that bypasses the second heat exchanger 46 is provided. By opening and closing the valve 65, the cooling water of the low-temperature side cooling water circuit 32 flowing through the second heat exchanger 46 is controlled.

また、高温側冷却水回路３１から第２熱交換器４６へと流入する冷却水の水温を検出する第３水温計６１と低温側冷却水回路３２から第２熱交換器４６へと流入する冷却水の水温を検出する第４水温計６２と、を備えた。   Further, the third water thermometer 61 that detects the temperature of the cooling water flowing into the second heat exchanger 46 from the high temperature side cooling water circuit 31 and the cooling that flows into the second heat exchanger 46 from the low temperature side cooling water circuit 32. And a fourth water temperature meter 62 for detecting the water temperature.

コントローラ６０は、前述の第２実施形態と同様に、第３水温計６１が検出した高温側冷却水回路３１の水温ＴｗＨ３と第４水温計６２が検出した低温側冷却水回路３２の水温ＴｗＬ４とに基づいて、バルブ６５の開閉を制御する。   Similarly to the second embodiment described above, the controller 60 includes the water temperature TwH3 of the high temperature side cooling water circuit 31 detected by the third water temperature gauge 61 and the water temperature TwL4 of the low temperature side cooling water circuit 32 detected by the fourth water temperature gauge 62. Based on the above, the opening and closing of the valve 65 is controlled.

例えば、第２熱交換器４６に流入する低温側冷却水回路３２の水温ＴｗＬ４が高温側冷却水回路３１の水温ＴｗＨ３よりも低い場合は、第２熱交換器４６において熱交換を行うようにバルブ６５を切り換える。これにより、低温側冷却水回路３２の冷却水温度を上昇させることができて、エンジン１０に流入する冷却水の温度が低下することなく、エンジンの暖機の遅れが改善される。また、高温側冷却水回路３１の冷却水温度を低下させることができて、高温側の第１のＥＧＲクーラ２１において、排気温度をより冷却することができる。   For example, when the water temperature TwL4 of the low-temperature side cooling water circuit 32 flowing into the second heat exchanger 46 is lower than the water temperature TwH3 of the high-temperature side cooling water circuit 31, the valve is configured to perform heat exchange in the second heat exchanger 46. Switch 65. Thereby, the cooling water temperature of the low temperature side cooling water circuit 32 can be raised, and the engine warm-up delay is improved without lowering the temperature of the cooling water flowing into the engine 10. Moreover, the cooling water temperature of the high temperature side cooling water circuit 31 can be lowered, and the exhaust temperature can be further cooled in the first EGR cooler 21 on the high temperature side.

一方で、第２熱交換器４６に流入する低温側冷却水回路３２の水温ＴｗＬ４よりも高温側冷却水回路３１の水温ＴｗＨ３が低い場合は、第２熱交換器４６での熱交換を行なわないようにバルブ６５を切り換える。これにより、低温側冷却水回路３２の冷却水よりも低温の冷却水と熱交換を行わないことで、エンジン１０に流入する冷却水の温度が低下することなく、エンジンの暖機の遅れが改善される。また、高温側冷却水回路３１の冷却水温度がより高温の冷却水と熱交換を行わないことで、高温側の第１のＥＧＲクーラ２１での排気をより冷却することができる。   On the other hand, when the water temperature TwH3 of the high temperature side cooling water circuit 31 is lower than the water temperature TwL4 of the low temperature side cooling water circuit 32 flowing into the second heat exchanger 46, heat exchange in the second heat exchanger 46 is not performed. The valve 65 is switched as follows. Accordingly, heat exchange with the cooling water having a temperature lower than that of the cooling water in the low-temperature side cooling water circuit 32 is not performed, so that the temperature of the cooling water flowing into the engine 10 does not decrease and the delay in warming up the engine is improved. Is done. Moreover, the exhaust gas in the first EGR cooler 21 on the high temperature side can be further cooled by not performing heat exchange with the cooling water having a higher temperature in the high temperature side cooling water circuit 31.

このように、第３実施形態では、第１及び第２実施形態と同様に過給された吸気の温度を低下させるだけでなく、排気温度を高温側の第１のＥＧＲクーラ２１で低下させた後、低温側冷却水回路３２の冷却水によって低温側の第３のＥＧＲクーラ２４において排気温度を下げることができる。このように構成した場合にも、高温側冷却水回路３１及び低温側冷却水回路３２を循環してエンジン１０に戻る冷却水の温度を低下させることがないので、エンジン１０のコールドスタート時にも、エンジン１０の暖機の遅れを改善することができる。   As described above, in the third embodiment, not only the temperature of the supercharged intake air is lowered, but the exhaust temperature is lowered by the first EGR cooler 21 on the high temperature side, as in the first and second embodiments. Then, the exhaust temperature can be lowered in the third EGR cooler 24 on the low temperature side by the cooling water in the low temperature side cooling water circuit 32. Even in such a configuration, the temperature of the cooling water that circulates through the high temperature side cooling water circuit 31 and the low temperature side cooling water circuit 32 and returns to the engine 10 is not lowered. Delay in warming up the engine 10 can be improved.

以上、本発明の実施形態について説明したが、上記実施形態は本発明の適用例の一つを示したものに過ぎず、本発明の技術的範囲を上記実施形態の具体的構成に限定する趣旨ではない。   The embodiment of the present invention has been described above, but the above embodiment is merely one example of application of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. is not.

１ 冷却装置
１０ エンジン
１１ 冷却水流路
１２ ウォーターポンプ（Ｗ／Ｐ）
１３ サーモスタット（Ｔ／Ｓ）
１８ 過給器（タービン）
２０ ＥＧＲ回路
２１ 第１のＥＧＲクーラ（第１排気冷却装置）
高温側の第１のＥＧＲクーラ［第１実施形態、第２実施形態、第３実施形態］
２２ 第２のＥＧＲクーラ（第２排気冷却装置）
高温側の第２のＥＧＲクーラ［第１実施形態、第２実施形態］
２３ ＥＧＲバルブ
２４ 第３のＥＧＲクーラ（第３排気冷却装置）
低温側の第３のＥＧＲクーラ［第３実施形態］
３０ 冷却水回路
３１ 高温側冷却水回路（第１冷却水回路）
３２ 低温側冷却水回路（第２冷却水回路）
４１ ラジエタ（第１ラジエタ）
４２ サブラジエタ（第２ラジエタ）
６０ コントローラ
７１ 高温側インタクーラ（第１吸気冷却装置）
７２ 低温側インタクーラ（第２吸気冷却装置）
７６ 熱交換器
８１ 第１水温計
８２ 第２水温計
８５ バルブ
８６ バイパス通路 1 Cooling device 10 Engine 11 Cooling water flow path 12 Water pump (W / P)
13 Thermostat (T / S)
18 Supercharger (turbine)
20 EGR circuit 21 First EGR cooler (first exhaust cooling device)
High temperature side first EGR cooler [first embodiment, second embodiment, third embodiment]
22 2nd EGR cooler (2nd exhaust cooling device)
High temperature side second EGR cooler [first embodiment, second embodiment]
23 EGR valve 24 Third EGR cooler (third exhaust cooling device)
Low temperature side third EGR cooler [Third embodiment]
30 Cooling water circuit 31 High temperature side cooling water circuit (first cooling water circuit)
32 Low-temperature side cooling water circuit (second cooling water circuit)
41 Radiator (1st radiator)
42 Sub-radiator (second radiator)
60 controller 71 high temperature side intercooler (first intake air cooling system)
72 Low-temperature intercooler (second intake air cooling system)
76 Heat exchanger 81 First water temperature meter 82 Second water temperature meter 85 Valve 86 Bypass passage

Claims (4)

エンジンの冷却水が流通する冷却水回路と、前記エンジンの吸気を過給する過給器と、を備えるエンジンにおいて、前記エンジンに備えられるエンジンの吸気冷却装置であって、
前記冷却水回路は、第１冷却水回路と、第２冷却水回路とを含み、
吸気を前記第１冷却水回路の冷却水により冷却する第１吸気冷却装置と、前記第１吸気冷却装置により冷却された吸気を前記第２冷却水回路の冷却水によりさらに冷却する第２吸気冷却装置と、が備えられ、
前記第１冷却水回路は、前記エンジンから出た冷却水を、前記第１吸気冷却装置を流通させて再びエンジンに戻し、
前記第２冷却水回路は、前記エンジンから出た冷却水を、前記第２吸気冷却装置を流通させて再びエンジンに戻し、
前記エンジンから出て前記第１吸気冷却装置へと向かう冷却水と、前記第２吸気冷却装置から出て前記エンジンへと向かう冷却水と、の間で熱交換を行う熱交換器を備えたことを特徴とするエンジンの吸気冷却装置。 An engine comprising a cooling water circuit through which engine cooling water circulates and a supercharger that supercharges intake air of the engine, the engine intake air cooling device provided in the engine,
The cooling water circuit includes a first cooling water circuit and a second cooling water circuit,
A first intake air cooling device that cools the intake air with the cooling water of the first cooling water circuit, and a second intake air cooling that further cools the intake air cooled by the first intake water cooling device with the cooling water of the second cooling water circuit. An apparatus, and
The first cooling water circuit returns the cooling water from the engine to the engine again through the first intake air cooling device,
The second cooling water circuit returns the cooling water from the engine to the engine again through the second intake air cooling device,
A heat exchanger for exchanging heat between the cooling water exiting from the engine toward the first intake air cooling device and the cooling water exiting from the second intake air cooling device toward the engine; An intake air cooling system for engines. 前記第１冷却水回路は、冷却水を冷却する第１ラジエタを備えると共に、前記第２冷却水回路には、前記第２冷却水回路を流れる冷却水を冷却する第２ラジエタが備えられ、
前記エンジンから出て、前記第２ラジエタにより冷却された冷却水が、前記第２吸気冷却装置を流通することを特徴とする
請求項１に記載のエンジンの吸気冷却装置。 Wherein the first coolant circuit is provided with a first radiator for cooling the cooling water, the second cooling water circuit, a second radiator for cooling the coolant flowing through the second coolant circuit is provided,
2. The engine intake air cooling device according to claim 1, wherein cooling water that has exited from the engine and has been cooled by the second radiator flows through the second intake air cooling device. 3. 前記第１吸気冷却装置から出た前記第１冷却水回路の冷却水と、前記熱交換器を出た前記第２冷却水回路の冷却水と、を合流させて、前記エンジンへと戻すことを特徴とする請求項１又は２に記載のエンジンの吸気冷却装置。 And the coolant in the first coolant circuit exiting the first intake air cooling device, a cooling water in the second coolant circuit exiting the heat exchanger, and is combined with, to return to the engine The engine intake air cooling device according to claim 1, wherein the intake air cooling device is used. 前記熱交換器に入る前記第１冷却水回路の冷却水の水温を検出する第１水温検出部と、
前記熱交換器に入る前記第２冷却水回路の冷却水の水温を検出する第２水温検出部と、
前記第２冷却水回路の冷却水を、前記熱交換器を流通させずバイパスさせるバイパス流路と、
前記第２冷却水回路の冷却水を、前記バイパス流路に流すか否かを制御するバルブと、
前記バルブの動作を制御する制御装置と、
をさらに備え、
前記制御装置は、
前記第２冷却水回路の冷却水の水温が前記第１冷却水回路の冷却水の水温よりも低い場合は、前記第２冷却水回路の冷却水を前記熱交換器に流通させるように、前記バルブを制御し、
前記第１冷却水回路の冷却水の水温が前記第２冷却水回路の冷却水の水温よりも低い場合は、前記第２冷却水回路の冷却水を前記熱交換器に流通させずバイパスさせるように、前記バルブを制御する
ことを特徴とする請求項１から３のいずれか一つに記載のエンジンの吸気冷却装置。 A first water temperature detection unit for detecting the temperature of the cooling water in the first cooling water circuit entering the heat exchanger;
A second water temperature detection unit for detecting the temperature of the cooling water in the second cooling water circuit entering the heat exchanger;
A bypass flow path for bypassing the cooling water of the second cooling water circuit without circulating the heat exchanger;
A valve for controlling whether or not the cooling water of the second cooling water circuit flows to the bypass flow path;
A control device for controlling the operation of the valve;
Further comprising
The control device includes:
When the coolant temperature of the second coolant circuit is lower than the coolant temperature of the first coolant circuit, the coolant of the second coolant circuit is circulated through the heat exchanger. Control the valve,
When the coolant temperature of the first coolant circuit is lower than the coolant temperature of the second coolant circuit, the coolant of the second coolant circuit is bypassed without passing through the heat exchanger. The engine intake air cooling device according to any one of claims 1 to 3, wherein the valve is controlled.
JP2013036644A 2013-02-27 2013-02-27 Engine intake cooling system Expired - Fee Related JP5993759B2 (en)

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DE112014001021.9T DE112014001021T8 (en) 2013-02-27 2014-02-12 An intake air cooling device for an engine and method for cooling an engine
PCT/JP2014/053230 WO2014132798A1 (en) 2013-02-27 2014-02-12 Engine intake air cooling device and cooling method
CN201480010853.1A CN105143633A (en) 2013-02-27 2014-02-12 Engine intake air cooling device and cooling method
US14/770,719 US20160003127A1 (en) 2013-02-27 2014-02-12 Intake-air cooling device for engine and method for cooling engine

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