JP2013241858A - Exhaust heat recovery system - Google Patents

Exhaust heat recovery system Download PDF

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JP2013241858A
JP2013241858A JP2012114434A JP2012114434A JP2013241858A JP 2013241858 A JP2013241858 A JP 2013241858A JP 2012114434 A JP2012114434 A JP 2012114434A JP 2012114434 A JP2012114434 A JP 2012114434A JP 2013241858 A JP2013241858 A JP 2013241858A
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heat recovery
exhaust heat
cooling water
passage
closed circuit
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Katsufumi Inoue
勝文 井上
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Marelli Corp
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Calsonic Kansei Corp
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    • 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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Abstract

PROBLEM TO BE SOLVED: To restrain leading-up for warming performance from being delayed in a heater core when cold-started.SOLUTION: An exhaust heat recovery system 100 includes a cooling water passage 10 for an engine 11, a heater core 13 provided in the cooling water passage 10 and for transmitting heat of cooling water to blowing air toward an inside of a cabin, an exhaust heat recovery passage 30 provided in parallel to the cooling water passage 10, an exhaust heat recovery device 31 provided in the exhaust heat recovery passage 30, and for recovering heat of an exhaust gas from the engine 11, to be transmitted to cooling water, a passage 32 for a closed circuit for connecting an upper stream and a downstream of exhaust heat recovery device 31 in the exhaust heat recovery passage 30, and flow channel switching means 33, 34 for forming the closed circuit of circulating the cooling water between the passage 32 for the closed circuit and the exhaust heat recovery device 31, when a temperature of the cooling water is a temperature in a cold time of the engine 11.

Description

本発明は、排熱回収システムに関する。   The present invention relates to an exhaust heat recovery system.

エンジンの排気ガスから熱エネルギーを回収する排熱回収器が知られている。排熱回収器は、エンジンの排気通路及び冷却水通路の途中に設けられ、排気ガスとエンジンの冷却水との間で熱交換を行って排気ガスの熱を冷却水に伝達させる。   2. Description of the Related Art An exhaust heat recovery device that recovers thermal energy from engine exhaust gas is known. The exhaust heat recovery device is provided in the middle of the engine exhaust passage and the coolant passage, and exchanges heat between the exhaust gas and the engine coolant to transmit the heat of the exhaust gas to the coolant.

冷却水通路の途中に排熱回収器を設けると、排熱回収器及びこれを接続する配管の分だけ冷却水通路全体の冷却水量が増大するので、熱容量が増大する。これにより、冷却水の昇温速度が緩慢になるので、エンジンが冷間始動してから暖機が終了するまでに要する時間が長くなる。   If the exhaust heat recovery device is provided in the middle of the cooling water passage, the amount of cooling water in the entire cooling water passage increases by the amount of the exhaust heat recovery device and the piping connecting the exhaust heat recovery device, so that the heat capacity increases. As a result, the rate of temperature rise of the cooling water becomes slow, so that the time required from the start of the engine to the end of warm-up becomes longer.

特許文献１には、エンジンの冷却水通路にヒータコア、排熱回収器、及び冷却水の流路を切り換える三方弁を設けることが記載されている。特許文献１では、冷却水の加温中に三方弁を切り換え、エンジンに冷却水を流すことなくヒータコア及び排熱回収器間で冷却水を循環させている。   Patent Document 1 describes that a three-way valve for switching a heater core, an exhaust heat recovery device, and a cooling water flow path is provided in an engine cooling water passage. In Patent Document 1, the three-way valve is switched during heating of the cooling water, and the cooling water is circulated between the heater core and the exhaust heat recovery unit without flowing the cooling water to the engine.

特開２００８−２０８７１６号公報JP 2008-208716 A

上記従来の技術では、冷却水の加温中、冷却水は排熱回収器によって加熱されるが、冷却水が昇温するまでの間、ヒータコアに低温の冷却水が流れる。よって、ヒータコアにおける暖房性能の立ち上がりが遅くなる。   In the above conventional technique, while the cooling water is heated, the cooling water is heated by the exhaust heat recovery device, but the low-temperature cooling water flows through the heater core until the temperature of the cooling water rises. Therefore, the rise of the heating performance in the heater core is delayed.

本発明は、このような技術的課題に鑑みてなされたもので、冷間始動時にヒータコアにおける暖房性能の立ち上がりの遅れを抑制可能な排熱回収システムを提供することを目的とする。   The present invention has been made in view of such a technical problem, and an object of the present invention is to provide an exhaust heat recovery system capable of suppressing a delay in the rise of heating performance in a heater core during cold start.

本発明のある態様によれば、エンジンの冷却水通路と、冷却水通路に設けられ冷却水の熱を車室内への送風空気に伝達させるヒータコアと、冷却水通路と並列に設けられる排熱回収通路と、排熱回収通路に設けられエンジンの排気ガスの熱を回収して冷却水へ伝達する排熱回収器と、排熱回収通路における排熱回収器の上流側と下流側とを接続する閉回路用通路と、冷却水の温度がエンジンの冷間時の温度である場合、閉回路用通路と排熱回収器との間で冷却水を循環させる閉回路を形成する流路切換手段と、を備えることを特徴とする排熱回収システムが提供される。   According to an aspect of the present invention, an engine cooling water passage, a heater core provided in the cooling water passage for transmitting heat of the cooling water to the blown air into the vehicle interior, and exhaust heat recovery provided in parallel with the cooling water passage. A passage, a waste heat recovery unit that is provided in the exhaust heat recovery passage and collects heat of the engine exhaust gas and transmits it to the cooling water, and an upstream side and a downstream side of the exhaust heat recovery unit in the exhaust heat recovery passage are connected to each other A passage switching means for forming a closed circuit for circulating the cooling water between the closed circuit passage and the exhaust heat recovery device when the temperature of the cooling water is a cold engine temperature; A waste heat recovery system is provided.

上記態様によれば、冷却水の温度がエンジンの冷間時の温度である場合、閉回路内で冷却水を循環させるので、排熱回収器において十分に昇温されていない低温の冷却水が冷却水通路へと流れることを防止することができる。よって、冷間時におけるエンジンの暖機が促進され、ヒータコアにおける暖房性能の立ち上がりの遅れを抑制することができる。   According to the above aspect, when the temperature of the cooling water is the temperature when the engine is cold, the cooling water is circulated in the closed circuit, so that the low-temperature cooling water that has not been sufficiently heated in the exhaust heat recovery device It can prevent flowing into the cooling water passage. Therefore, warm-up of the engine during cold weather is promoted, and the delay in the rise of the heating performance in the heater core can be suppressed.

本発明の実施形態に係る排熱回収システムの全体構成を示している。1 shows an overall configuration of an exhaust heat recovery system according to an embodiment of the present invention. 排熱回収システムの処理内容を示すフローチャートである。It is a flowchart which shows the processing content of a waste heat recovery system.

以下、添付図面を参照しながら本発明の実施形態について説明する。   Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

図１は、本実施形態における排熱回収システム１００の全体構成を示している。   FIG. 1 shows an overall configuration of an exhaust heat recovery system 100 in the present embodiment.

排熱回収システム１００は、車両に搭載されたエンジン１１の冷却水通路１０と、冷却水通路１０と並列に設けられるラジエータ通路２０と、冷却水通路１０と並列に設けられる排熱回収通路３０と、コントローラ４０と、を備える。なお、すべての通路は、エンジン１１の冷却水、例えばＬＬＣで満たされている。   The exhaust heat recovery system 100 includes a cooling water passage 10 of an engine 11 mounted on a vehicle, a radiator passage 20 provided in parallel with the cooling water passage 10, and an exhaust heat recovery passage 30 provided in parallel with the cooling water passage 10. And a controller 40. All the passages are filled with cooling water of the engine 11, for example, LLC.

冷却水通路１０は、エンジン１１と、トランスミッションオイルウォーマ１２と、ヒータコア１３と、ウォータポンプ１４とを、この順に接続している。   The cooling water passage 10 connects an engine 11, a transmission oil warmer 12, a heater core 13, and a water pump 14 in this order.

ウォータポンプ１４は、エンジン１１の図示しないクランクシャフトプーリにベルトを介して連結されており、エンジン１１の駆動力によって回転駆動される。ウォータポンプ１４が回転すると、冷却水通路１０内の冷却水がエンジン１１へ供給される。   The water pump 14 is connected to a crankshaft pulley (not shown) of the engine 11 via a belt, and is rotated by the driving force of the engine 11. When the water pump 14 rotates, the cooling water in the cooling water passage 10 is supplied to the engine 11.

ヒータコア１３は、冷却水の熱を車室内への送風空気へ伝達する熱交換器であり、車両の空調ユニット内に設けられる。つまり、車両の暖房性能は、ヒータコア１３を通過する冷却水の温度が高いほど向上する。   The heater core 13 is a heat exchanger that transmits heat of the cooling water to the blown air into the vehicle interior, and is provided in the air conditioning unit of the vehicle. That is, the heating performance of the vehicle improves as the temperature of the cooling water passing through the heater core 13 increases.

トランスミッションオイルウォーマ１２は、冷却水と図示しない変速機のオイルとの間で熱交換を行う熱交換器である。トランスミッションオイルウォーマ１２は、エンジン１１の冷間時は、冷却水の熱を変速機のオイルへと伝達することで変速機のフリクションロスを迅速に低減させ、エンジン１１の暖機終了後は、変速機のオイルから冷却水へと熱を伝達させることでオイルを冷却するオイルクーラとして機能する。   The transmission oil warmer 12 is a heat exchanger that exchanges heat between cooling water and transmission oil (not shown). The transmission oil warmer 12 rapidly reduces the friction loss of the transmission by transmitting the heat of the cooling water to the transmission oil when the engine 11 is cold. It functions as an oil cooler that cools the oil by transferring heat from the machine oil to the cooling water.

ラジエータ通路２０は、エンジン１１と、ラジエータ２１と、サーモスタット２２と、ウォータポンプ１４とを、この順に接続している。   The radiator passage 20 connects the engine 11, the radiator 21, the thermostat 22, and the water pump 14 in this order.

サーモスタット２２は、冷却水の温度が予め設定された設定温度（例えば８０℃）に達するまではラジエータ通路２０を閉塞し、冷却水の温度が設定温度に達するとラジエータ通路２０を開放するように作動する開閉バルブである。したがって、サーモスタット２２が閉じている場合、ウォータポンプ１４から供給された冷却水はラジエータ通路２０には流れず、サーモスタット２２が開いた場合、冷却水がラジエータ通路２０に流れる。   The thermostat 22 closes the radiator passage 20 until the temperature of the cooling water reaches a preset temperature (for example, 80 ° C.), and operates to open the radiator passage 20 when the temperature of the cooling water reaches the preset temperature. This is an open / close valve. Therefore, when the thermostat 22 is closed, the cooling water supplied from the water pump 14 does not flow into the radiator passage 20, and when the thermostat 22 is opened, the cooling water flows into the radiator passage 20.

ラジエータ２１は、冷却水の熱を外気へ放熱する熱交換器である。ラジエータ２１は、車両の前方に設けられ、車両の走行風及びラジエータ２１の近傍に設けられた電動ファン２３によって生成された風、の少なくとも一方によって冷却される。   The radiator 21 is a heat exchanger that radiates heat of the cooling water to the outside air. The radiator 21 is provided in front of the vehicle and is cooled by at least one of traveling wind of the vehicle and wind generated by the electric fan 23 provided in the vicinity of the radiator 21.

排熱回収通路３０は、冷却水通路１０と並列に設けられ、エンジン１１と、排熱回収器３１とを、この順に接続している。排熱回収通路３０の下流端は、冷却水通路１０の途中であってエンジン１１とトランスミッションオイルウォーマ１２との間に合流している。   The exhaust heat recovery passage 30 is provided in parallel with the cooling water passage 10 and connects the engine 11 and the exhaust heat recovery device 31 in this order. The downstream end of the exhaust heat recovery passage 30 is in the middle of the cooling water passage 10 and joins between the engine 11 and the transmission oil warmer 12.

排熱回収器３１は、エンジン１１の排気管の近傍に設けられ、エンジン１１の排気ガスの熱を冷却水へ伝達する熱交換器である。エンジン１１の排気ガスは大気放出されるので、この排気ガスから熱エネルギーを回収してエンジン１１の暖機に利用することで、エンジン１１の熱効率を向上させることができる。   The exhaust heat recovery unit 31 is a heat exchanger that is provided in the vicinity of the exhaust pipe of the engine 11 and transmits heat of the exhaust gas of the engine 11 to the cooling water. Since the exhaust gas of the engine 11 is released to the atmosphere, the thermal efficiency of the engine 11 can be improved by recovering thermal energy from the exhaust gas and using it for warming up the engine 11.

排熱回収通路３０における排熱回収器３１の上流側と下流側とには、閉回路用通路３２が接続される。閉回路用通路３２は、排熱回収器３１の上流側に第１バルブ３３を介して接続され、排熱回収器３１の下流側に第２バルブ３４を介して接続される。排熱回収通路３０における排熱回収器３１と第１バルブ３３との間には、電動ウォータポンプ３５が設けられる。   A closed circuit passage 32 is connected to the exhaust heat recovery passage 30 upstream and downstream of the exhaust heat recovery device 31. The closed circuit passage 32 is connected to the upstream side of the exhaust heat recovery unit 31 via the first valve 33 and connected to the downstream side of the exhaust heat recovery unit 31 via the second valve 34. An electric water pump 35 is provided between the exhaust heat recovery device 31 and the first valve 33 in the exhaust heat recovery passage 30.

第１バルブ３３は、閉回路用通路３２を遮断して排熱回収通路３０を連通させる非閉回路状態と、排熱回収通路３０を遮断して閉回路用通路３２と第１バルブ３３より下流側の排熱回収通路３０とを連通させる閉回路状態と、を切り換え可能である。第２バルブ３４は、閉回路用通路３２を遮断して排熱回収通路３０を連通させる非閉回路状態と、排熱回収通路３０を遮断して閉回路用通路３２と第２バルブ３４より上流側の排熱回収通路３０とを連通させる閉回路状態と、を切り換え可能である。   The first valve 33 shuts off the closed circuit passage 32 and allows the exhaust heat recovery passage 30 to communicate, and shuts off the exhaust heat recovery passage 30 and is downstream of the closed circuit passage 32 and the first valve 33. It is possible to switch between a closed circuit state in which the exhaust heat recovery passage 30 on the side communicates. The second valve 34 shuts off the closed circuit passage 32 and allows the exhaust heat recovery passage 30 to communicate, and shuts off the exhaust heat recovery passage 30 and is upstream of the closed circuit passage 32 and the second valve 34. It is possible to switch between a closed circuit state in which the exhaust heat recovery passage 30 on the side communicates.

さらに、電動ウォータポンプ３５は、第１バルブ３３及び第２バルブ３４の状態によらずエンジン作動中は常に作動している。   Furthermore, the electric water pump 35 is always operating during engine operation regardless of the state of the first valve 33 and the second valve 34.

したがって、第１バルブ３３及び第２バルブ３４を切り換えることで、閉回路用通路３２と排熱回収通路３０との間に排熱回収器３１を循環する閉回路を形成することができ、電動ウォータポンプ３５によって閉回路内の冷却水が循環される。   Therefore, by switching the first valve 33 and the second valve 34, a closed circuit for circulating the exhaust heat recovery device 31 between the closed circuit passage 32 and the exhaust heat recovery passage 30 can be formed. Cooling water in the closed circuit is circulated by the pump 35.

コントローラ４０は、第１温度センサ３６、第２温度センサ３７、及び外気温度センサ３８から受信した信号に基づいて、第１バルブ３３及び第２バルブ３４を切り換え制御する。   The controller 40 switches and controls the first valve 33 and the second valve 34 based on signals received from the first temperature sensor 36, the second temperature sensor 37, and the outside air temperature sensor 38.

第１温度センサ３６は、排熱回収器３１と第１バルブ３３との間における冷却水の温度、すなわち排熱回収器３１に流入する冷却水の温度を検出する。第２温度センサ３７は、排熱回収器３１と第２バルブ３４との間における冷却水の温度、すなわち排熱回収器３１から流出する冷却水の温度を検出する。外気温度センサ３８は、外気温度を検出する。   The first temperature sensor 36 detects the temperature of the cooling water between the exhaust heat recovery device 31 and the first valve 33, that is, the temperature of the cooling water flowing into the exhaust heat recovery device 31. The second temperature sensor 37 detects the temperature of the cooling water between the exhaust heat recovery device 31 and the second valve 34, that is, the temperature of the cooling water flowing out from the exhaust heat recovery device 31. The outside air temperature sensor 38 detects the outside air temperature.

次に、コントローラ４０が行う制御について図２を参照しながら説明する。   Next, control performed by the controller 40 will be described with reference to FIG.

ステップＳ１においてコントローラ４０は、エンジン１１が冷間時であるか否かを判定する。エンジン１１が冷間時であると判定されると処理がステップＳ２へ進み、冷間時であると判定されない場合には処理が再度実行される。   In step S1, the controller 40 determines whether or not the engine 11 is cold. If it is determined that the engine 11 is cold, the process proceeds to step S2, and if it is not determined that the engine 11 is cold, the process is executed again.

エンジン１１が冷間時であることは、冷却水の温度が所定の温度より低いことに基づいて判定される。所定の温度は、冷却水がヒータコア１３に流れた場合に所望の暖房性能を発揮できる程度の温度であり、例えば、４０℃に設定される。   Whether the engine 11 is cold is determined based on the fact that the temperature of the cooling water is lower than a predetermined temperature. The predetermined temperature is a temperature at which a desired heating performance can be exhibited when the cooling water flows into the heater core 13, and is set to 40 ° C., for example.

ステップＳ２においてコントローラ４０は、第１バルブ３３及び第２バルブ３４を閉回路状態に切り換える。これにより、閉回路用通路３２と第１バルブ３３より下流側の排熱回収通路３０とが連通するとともに、閉回路用通路３２と第２バルブ３４より上流側の排熱回収通路３０とが連通するので、冷却水が電動ウォータポンプ３５及び排熱回収器３１を循環する閉回路が形成される。   In step S2, the controller 40 switches the first valve 33 and the second valve 34 to a closed circuit state. As a result, the closed circuit passage 32 and the exhaust heat recovery passage 30 downstream from the first valve 33 communicate with each other, and the closed circuit passage 32 and the exhaust heat recovery passage 30 upstream from the second valve 34 communicate with each other. Therefore, a closed circuit in which the cooling water circulates through the electric water pump 35 and the exhaust heat recovery device 31 is formed.

閉回路内の冷却水は、繰り返し排熱回収器３１に流れることで加熱されて昇温する。一方、冷却水通路１０には、排熱回収器３１及び排熱回収通路３０の低温の冷却水が流れ込まないので、冷却水通路１０内の冷却水の昇温速度の低下が抑制され、ヒータコア１３における暖房能力の発揮が促進される。   The cooling water in the closed circuit is heated and heated by repeatedly flowing to the exhaust heat recovery device 31. On the other hand, since the low-temperature cooling water of the exhaust heat recovery device 31 and the exhaust heat recovery passage 30 does not flow into the cooling water passage 10, a decrease in the temperature rise rate of the cooling water in the cooling water passage 10 is suppressed, and the heater core 13 The use of heating capacity is promoted.

なお、この場合、排熱回収通路３０の第１バルブ３３より上流側及び第２バルブ３４より下流側では、通路が閉回路によって閉塞されるので冷却水の流れが停止する。   In this case, on the upstream side of the first valve 33 and the downstream side of the second valve 34 in the exhaust heat recovery passage 30, the passage is closed by a closed circuit, so that the flow of cooling water stops.

ステップＳ３においてコントローラ４０は、所定の温度条件が成立したか否かを判定する。所定の温度条件が成立した場合には処理がステップＳ４へ進み、成立しない場合には処理が再度実行される。   In step S3, the controller 40 determines whether or not a predetermined temperature condition is satisfied. If the predetermined temperature condition is satisfied, the process proceeds to step S4. If not, the process is executed again.

所定の温度条件は、以下の３つの条件のうち、少なくとも一つを満たす場合に成立すると判定される。３つの条件は、第２温度センサ３７の検出値が第１温度センサ３６の検出値より高くなった場合、第２温度センサ３７の検出値がヒータコア１３において所望の暖房性能を発揮できる程度の暖房性能発揮温度（例えば４０℃）に達した場合、第２温度センサ３７の検出値と外気温度センサ３８の検出値との温度差がヒータコア１３において所望の暖房性能を発揮できる程度の暖房性能発揮温度差（例えば３０℃）に達した場合、である。   The predetermined temperature condition is determined to be satisfied when at least one of the following three conditions is satisfied. The three conditions are that the detection value of the second temperature sensor 37 is higher than the detection value of the first temperature sensor 36, and the heating value is such that the detection value of the second temperature sensor 37 can exhibit the desired heating performance in the heater core 13. When the performance exhibiting temperature (for example, 40 ° C.) is reached, the heating performance exhibiting temperature such that the temperature difference between the detected value of the second temperature sensor 37 and the detected value of the outside air temperature sensor 38 can exhibit the desired heating performance in the heater core 13. When the difference (for example, 30 ° C.) is reached.

なお、暖房性能発揮温度及び暖房性能発揮温度差は、車両の空調ユニットの設定温度に応じて変化させてもよい。   The heating performance display temperature and the heating performance display temperature difference may be changed according to the set temperature of the air conditioning unit of the vehicle.

ステップＳ４においてコントローラ４０は、第１バルブ３３及び第２バルブ３４を非閉回路状態に切り換える。これにより、閉回路用通路３２が遮断されて排熱回収通路３０が第１バルブ３３及び第２バルブ３４間で連通し、閉回路が開放される。したがって、閉回路内で循環中に昇温された冷却水が下流側へと流れて冷却水通路１０へ流入する。よって、冷却水通路１０に設けられるヒータコア１３を流れる冷却水温度の低下が抑制される。   In step S4, the controller 40 switches the first valve 33 and the second valve 34 to the non-closed circuit state. As a result, the closed circuit passage 32 is blocked, the exhaust heat recovery passage 30 communicates between the first valve 33 and the second valve 34, and the closed circuit is opened. Therefore, the cooling water whose temperature has been increased during circulation in the closed circuit flows downstream and flows into the cooling water passage 10. Therefore, a decrease in the temperature of the cooling water flowing through the heater core 13 provided in the cooling water passage 10 is suppressed.

以上の実施形態によれば、以下に示す効果を奏する。   According to the above embodiment, there exist the effects shown below.

エンジン１１の冷間時であると判定されると、排熱回収通路３０の冷却水が排熱回収器３１のみを循環する閉回路が形成されるので、排熱回収器３１内の昇温されていない低温の冷却水が冷却水通路１０へと流れ込むことによる冷却水温度の低下を抑制することができる。よって、エンジン１１の暖機が促進され、冷却水通路１０に設けられるヒータコア１３を流れる冷却水の温度上昇速度を増加させることができるので、冷間時の暖房性能の立ち上がりの遅れを抑制することができる。   If it is determined that the engine 11 is cold, a closed circuit is formed in which the cooling water in the exhaust heat recovery passage 30 circulates only through the exhaust heat recovery device 31, so that the temperature in the exhaust heat recovery device 31 is increased. It is possible to suppress a decrease in the cooling water temperature due to the low-temperature cooling water not flowing into the cooling water passage 10. Therefore, warming-up of the engine 11 is promoted, and the temperature rise rate of the cooling water flowing through the heater core 13 provided in the cooling water passage 10 can be increased. Can do.

さらに、コントローラ４０は第２温度センサ３７の検出値が第１温度センサ３６の検出値より高くなった場合に第１バルブ３３及び第２バルブ３４を非閉回路状態へと切り換えるので、排熱回収器３１が暖機され、通過する冷却水を昇温できる状態となってから閉回路が開放される。よって、低温の冷却水が冷却水通路１０へと流れることによる暖房性能の立ち上がりの遅れをより確実に抑制することができる。   Further, the controller 40 switches the first valve 33 and the second valve 34 to the non-closed circuit state when the detection value of the second temperature sensor 37 is higher than the detection value of the first temperature sensor 36, so that the exhaust heat recovery is performed. The closed circuit is opened after the vessel 31 is warmed up and the cooling water passing therethrough can be heated. Therefore, it is possible to more reliably suppress the delay in the rise of the heating performance due to the low-temperature cooling water flowing into the cooling water passage 10.

さらに、コントローラ４０は第２温度センサ３７の検出値がヒータコア１３において所望の暖房性能を発揮できる程度の暖房性能発揮温度に達した場合に第１バルブ３３及び第２バルブ３４を非閉回路状態へと切り換えるので、排熱回収器３１が暖機され、通過する冷却水を十分な温度まで昇温できる状態となってから閉回路が開放される。よって、低温の冷却水が冷却水通路１０へと流れることによる暖房性能の立ち上がりの遅れをより確実に抑制することができる。   Further, the controller 40 brings the first valve 33 and the second valve 34 into a non-closed circuit state when the detected value of the second temperature sensor 37 reaches a heating performance exhibiting temperature at which the heater core 13 can exhibit a desired heating performance. Therefore, after the exhaust heat recovery device 31 is warmed up and the temperature of the passing cooling water can be raised to a sufficient temperature, the closed circuit is opened. Therefore, it is possible to more reliably suppress the delay in the rise of the heating performance due to the low-temperature cooling water flowing into the cooling water passage 10.

さらに、コントローラ４０は第２温度センサ３７の検出値と外気温度センサ３８の検出値との温度差がヒータコア１３において所望の暖房性能を発揮できる程度の暖房性能発揮温度差に達した場合に第１バルブ３３及び第２バルブ３４を非閉回路状態へと切り換えるので、排熱回収器３１が暖機され、通過する冷却水を外気温度よりも十分に昇温できる状態となってから閉回路が開放される。よって、低温の冷却水が冷却水通路１０へと流れることによる暖房性能の立ち上がりの遅れをより確実に抑制することができる。   Furthermore, the controller 40 is configured to perform the first operation when the temperature difference between the detection value of the second temperature sensor 37 and the detection value of the outside air temperature sensor 38 reaches a heating performance exhibiting temperature difference that can exhibit a desired heating performance in the heater core 13. Since the valve 33 and the second valve 34 are switched to the non-closed circuit state, the exhaust heat recovery device 31 is warmed up and the closed circuit is opened after the passing cooling water can be sufficiently heated above the outside air temperature. Is done. Therefore, it is possible to more reliably suppress the delay in the rise of the heating performance due to the low-temperature cooling water flowing into the cooling water passage 10.

さらに、排熱回収通路３０における閉回路の形成及び開放を、第１バルブ３３及び第２バルブ３４の切り換えによって行うので、冷間時には閉回路を形成して排熱回収通路３０の冷却水が冷却水通路１０へ流れ込むことを防止することと、閉回路内の冷却水温度が上昇したら閉回路内の冷却水を冷却水通路１０へと流すこととを、より確実に切り換え制御することができる。特に、閉回路を形成して閉回路内の冷却水が所定の温度条件を満たすまでの間、低温の冷却水をより確実に閉回路内に留めることができる。   Furthermore, since the closed circuit is formed and opened in the exhaust heat recovery passage 30 by switching the first valve 33 and the second valve 34, the closed circuit is formed in the cold state to cool the cooling water in the exhaust heat recovery passage 30. It is possible to more reliably perform switching control between preventing the water from flowing into the water passage 10 and flowing the cooling water in the closed circuit into the cooling water passage 10 when the temperature of the cooling water in the closed circuit rises. In particular, the low-temperature cooling water can be more reliably retained in the closed circuit until the closed circuit is formed and the cooling water in the closed circuit satisfies a predetermined temperature condition.

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を示したものであり、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 shows an application example of the present invention, and is not intended to limit the technical scope of the present invention to the specific configuration of the above embodiment.

例えば、上記実施形態では、冷却水通路１０にエンジン駆動のウォータポンプ１４を設けているが、冷却水通路１０の水温を検出する水温センサの検出値を考慮して第１バルブ３３及び第２バルブ３４の切り換えを行うようにするのであれば、ウォータポンプ１４を省略して、電動ウォータポンプ３５だけですべての冷却水の循環を行ってもよい。   For example, in the above embodiment, the engine-driven water pump 14 is provided in the cooling water passage 10, but the first valve 33 and the second valve are considered in consideration of the detection value of the water temperature sensor that detects the water temperature of the cooling water passage 10. If the switching of 34 is performed, the water pump 14 may be omitted, and only the electric water pump 35 may circulate all the cooling water.

１０ 冷却水通路
１１ エンジン
１３ ヒータコア
３０ 排熱回収通路
３１ 排熱回収器
３２ 閉回路用通路
３３ 第１バルブ（流路切換手段）
３４ 第２バルブ（流路切換手段）
１００ 排熱回収システム DESCRIPTION OF SYMBOLS 10 Cooling water passage 11 Engine 13 Heater core 30 Waste heat recovery passage 31 Waste heat recovery device 32 Passage for closed circuit 33 First valve (flow path switching means)
34 Second valve (flow path switching means)
100 Waste heat recovery system

Claims (5)

エンジンの冷却水通路と、
前記冷却水通路に設けられ冷却水の熱を車室内への送風空気に伝達させるヒータコアと、
前記冷却水通路と並列に設けられる排熱回収通路と、
前記排熱回収通路に設けられ前記エンジンの排気ガスの熱を回収して冷却水へ伝達する排熱回収器と、
前記排熱回収通路における前記排熱回収器の上流側と下流側とを接続する閉回路用通路と、
冷却水の温度が前記エンジンの冷間時の温度である場合、前記閉回路用通路と前記排熱回収器との間で冷却水を循環させる閉回路を形成する流路切換手段と、
を備えることを特徴とする排熱回収システム。 An engine coolant passage,
A heater core that is provided in the cooling water passage and transmits heat of the cooling water to the air blown into the vehicle interior;
An exhaust heat recovery passage provided in parallel with the cooling water passage;
An exhaust heat recovery unit provided in the exhaust heat recovery passage for recovering heat of the exhaust gas of the engine and transmitting it to cooling water;
A closed circuit path connecting the upstream side and the downstream side of the exhaust heat recovery unit in the exhaust heat recovery path;
A flow path switching means for forming a closed circuit for circulating the cooling water between the closed circuit passage and the exhaust heat recovery device, when the temperature of the cooling water is a cold temperature of the engine;
An exhaust heat recovery system comprising: 請求項１に記載の排熱回収システムであって、
前記流路切換手段は、前記排熱回収器から流出する冷却水の温度が前記排熱回収器へ流入する冷却水の温度より高くなった場合、前記閉回路を開放する、
ことを特徴とする排熱回収システム。 The exhaust heat recovery system according to claim 1,
The flow path switching means opens the closed circuit when the temperature of the cooling water flowing out from the exhaust heat recovery device becomes higher than the temperature of the cooling water flowing into the exhaust heat recovery device.
An exhaust heat recovery system characterized by that. 請求項１又は請求項２に記載の排熱回収システムであって、
前記流路切換手段は、前記排熱回収器から流出する冷却水の温度が暖房性能発揮温度を超えた場合、前記閉回路を開放する、
ことを特徴とする排熱回収システム。 The exhaust heat recovery system according to claim 1 or 2,
The flow path switching means opens the closed circuit when the temperature of the cooling water flowing out of the exhaust heat recovery device exceeds the heating performance exhibiting temperature.
An exhaust heat recovery system characterized by that. 請求項１から請求項３までのいずれか一項に記載の排熱回収システムであって、
前記流路切換手段は、前記排熱回収器から流出する冷却水の温度と外気温度との差が暖房性能発揮温度差を超えた場合、前記閉回路を開放する、
ことを特徴とする排熱回収システム。 The exhaust heat recovery system according to any one of claims 1 to 3,
The flow path switching means opens the closed circuit when the difference between the temperature of the cooling water flowing out of the exhaust heat recovery device and the outside air temperature exceeds the heating performance exhibiting temperature difference,
An exhaust heat recovery system characterized by that. 請求項１から請求項４までのいずれか一項に記載の排熱回収システムであって、
前記排熱回収通路と前記閉回路用通路との接続部であって前記排熱回収器より上流側の前記接続部に設けられ、前記閉回路用通路と前記排熱回収器より上流側の前記排熱回収通路とを連通可能な第１バルブと、
前記排熱回収器より下流側の前記接続部に設けられ、前記閉回路用通路と前記排熱回収器より下流側の前記排熱回収通路とを連通可能な第２バルブと、
をさらに備え、
前記流路切換手段は、前記第１バルブ及び前記第２バルブを切り換えることで前記閉回路を形成する、
ことを特徴とする排熱回収システム。 The exhaust heat recovery system according to any one of claims 1 to 4,
It is a connecting portion between the exhaust heat recovery passage and the closed circuit passage, and is provided in the connection portion upstream from the exhaust heat recovery device, and the upstream side from the closed circuit passage and the exhaust heat recovery device. A first valve capable of communicating with the exhaust heat recovery passage;
A second valve provided in the connecting portion downstream of the exhaust heat recovery device and capable of communicating the closed circuit passage and the exhaust heat recovery passage downstream of the exhaust heat recovery device;
Further comprising
The flow path switching means forms the closed circuit by switching the first valve and the second valve;
An exhaust heat recovery system characterized by that.
JP2012114434A 2012-05-18 2012-05-18 Exhaust heat recovery system Pending JP2013241858A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019060239A (en) * 2017-09-25 2019-04-18 トヨタ自動車株式会社 Vehicular cooling system

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019060239A (en) * 2017-09-25 2019-04-18 トヨタ自動車株式会社 Vehicular cooling system
US10710470B2 (en) 2017-09-25 2020-07-14 Toyota Jidosha Kabushiki Kaisha Vehicular cooling system

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