JP2012251516A - Waste heat recovery apparatus - Google Patents

Waste heat recovery apparatus Download PDF

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Publication number
JP2012251516A
JP2012251516A JP2011126331A JP2011126331A JP2012251516A JP 2012251516 A JP2012251516 A JP 2012251516A JP 2011126331 A JP2011126331 A JP 2011126331A JP 2011126331 A JP2011126331 A JP 2011126331A JP 2012251516 A JP2012251516 A JP 2012251516A
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Prior art keywords
heat
flow path
refrigerant
expander
heat exchanger
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Hidefumi Mori
英文 森
Masao Iguchi
雅夫 井口
Fuminobu Enoshima
史修 榎島
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Toyota Industries Corp
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Toyota Industries Corp
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Priority to JP2011126331A priority Critical patent/JP2012251516A/en
Priority to PCT/JP2012/063469 priority patent/WO2012169376A1/en
Publication of JP2012251516A publication Critical patent/JP2012251516A/en
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    • 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
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
    • 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
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from combustion engines
    • 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)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

PROBLEM TO BE SOLVED: To avoid decrease in efficiency of waste heat recovery while reducing warm-up time of a heat engine.SOLUTION: A rankine cycle circuit 13 comprises an expander 31, a heat exchanger 47, a condenser 49, a pump 41, and a boiler 42. A high temperature and high pressure cooling medium heated by the boiler 42 is introduced into the expander 31 via a supply flow path 46. A heat exchanger 47 is provided downstream of the expander 31. The condenser 49 is provided downstream of the heat exchanger 47. The low-pressure cooling medium expanded by the expander 31 is sent to the condenser 49 via the heat exchanger 47. The heat exchanger 47 comprises a heat dissipation part 471 and a heat absorption part 472. A discharge flow path 48 and a connection flow path 50 are connected via the heat dissipation part 471. A heat absorption part 422 is provided at a branch flow path 521 of a cooling water circulation passage 52 connected to an engine 12.

Description

本発明は、熱機関の廃熱を回収する廃熱回収装置に関する。   The present invention relates to a waste heat recovery apparatus that recovers waste heat of a heat engine.

この種の廃熱回収装置が特許文献１に開示されている。特許文献１に開示の廃熱回収装置では、エンジンから排出された排気ガスの熱を作動流体に伝達する蒸気発生器と、作動流体の熱をエンジン冷却水に伝達する熱交換器とが備えられている。作動流体を膨張機へ送ると、発電機が発電し、発電された電気がバッテリに蓄えられる。   This type of waste heat recovery apparatus is disclosed in Patent Document 1. The waste heat recovery apparatus disclosed in Patent Document 1 includes a steam generator that transmits the heat of exhaust gas discharged from the engine to the working fluid, and a heat exchanger that transfers the heat of the working fluid to the engine coolant. ing. When the working fluid is sent to the expander, the generator generates electricity, and the generated electricity is stored in the battery.

このような構成によれば、排気ガスの熱を利用して発電することができ、しかも排気ガスの熱を冷却水に伝達してエンジンの暖機運転を短縮することができる、という効果の開示がなされている。   According to such a configuration, it is possible to generate power using the heat of the exhaust gas, and to disclose the effect that the heat of the exhaust gas can be transmitted to the cooling water to shorten the engine warm-up operation. Has been made.

特開２００５−４２６１８号公報JP 2005-42618 A

しかし、特許文献１の構成であると、エンジン冷却水の温度が上昇した場合には
熱交換器（凝縮器）の凝縮圧が高くなってしまう。そうすると、膨張機から流出した作動流体（気体）を熱交換器（凝縮器）において液化することが困難になり、廃熱回収の効率低下をもたらす。 However, with the configuration of Patent Document 1, when the temperature of the engine coolant increases, the condensation pressure of the heat exchanger (condenser) becomes high. If it does so, it will become difficult to liquefy the working fluid (gas) which flowed out from the expander in a heat exchanger (condenser), and will bring about a reduction in the efficiency of waste heat recovery.

本発明は、熱機関の暖機時間の短縮化を図りつつ廃熱回収の効率低下を回避することを目的とする。   An object of the present invention is to avoid a reduction in the efficiency of waste heat recovery while shortening the warm-up time of a heat engine.

本発明は、熱機関の廃熱を熱源とするボイラと、前記ボイラで熱を与えられた冷媒を導入して廃熱を回収するための膨張機と、前記膨張機から流出した冷媒を凝縮する凝縮器と、前記凝縮器から流出した冷媒を前記ボイラへ送るポンプと、前記ボイラ、前記膨張機、前記凝縮器及び前記ポンプを接続する冷媒流路とを備える廃熱回収装置を対象とし、請求項１の発明では、前記膨張機及び前記凝縮器間の前記冷媒流路と前記熱機関を冷却する冷却液が流れる冷却流路との間で熱交換を行なうための熱交換器が設けられている。   The present invention contemplates a boiler that uses waste heat of a heat engine as a heat source, an expander for recovering waste heat by introducing a refrigerant that is heated by the boiler, and a refrigerant that flows out of the expander Intended for a waste heat recovery apparatus comprising a condenser, a pump for sending refrigerant flowing out of the condenser to the boiler, and a refrigerant flow path connecting the boiler, the expander, the condenser and the pump, In the invention of Item 1, a heat exchanger is provided for heat exchange between the refrigerant flow path between the expander and the condenser and a cooling flow path through which a cooling liquid for cooling the heat engine flows. Yes.

熱交換器における冷却液の温度が膨張機から流出した冷媒の温度より低い場合には、膨張機から流出した冷媒の熱が熱交換器を介して冷却流路内の冷却液に伝達される。これは、熱機関の暖機時間の短縮化をもたらす。熱交換器における冷却液の温度が膨張機から流出した冷媒の温度より高い場合には、膨張機から流出した冷媒は、凝縮器にて放熱する。凝縮器での冷媒の放熱は、冷媒の液化をもたらし、凝縮圧が高くなり熱効率が悪化することはない。これは、廃熱回収の効率低下の回避をもたらす。   When the temperature of the coolant in the heat exchanger is lower than the temperature of the refrigerant that has flowed out of the expander, the heat of the refrigerant that has flowed out of the expander is transferred to the coolant in the cooling channel via the heat exchanger. This leads to a shortening of the warm-up time of the heat engine. When the temperature of the coolant in the heat exchanger is higher than the temperature of the refrigerant that has flowed out of the expander, the refrigerant that has flowed out of the expander radiates heat in the condenser. The heat radiation of the refrigerant in the condenser causes liquefaction of the refrigerant, so that the condensation pressure is increased and the thermal efficiency is not deteriorated. This results in avoiding a reduction in the efficiency of waste heat recovery.

好適な例では、前記熱交換器と並列なバイパス流路が前記膨張機と前記凝縮器との間で設けられており、前記膨張機から流出した冷媒を前記バイパス流路へ供給する割合を調整する調整手段と、前記冷却液の温度を検出する液温度検出手段とが設けられており、前記調整手段は、前記液温度検出手段によって検出された温度に基づいて、前記割合を調整する。   In a preferred example, a bypass flow path parallel to the heat exchanger is provided between the expander and the condenser, and the ratio of supplying the refrigerant flowing out of the expander to the bypass flow path is adjusted. Adjusting means for detecting the temperature of the cooling liquid, and adjusting means for adjusting the ratio based on the temperature detected by the liquid temperature detecting means.

冷却液の温度が低い場合には冷媒を熱交換器へ流し、冷却液の温度が高い場合には冷媒をバイパス流路へ流すことにより、熱機関の暖機時間の短縮化がもたらされると共に、廃熱回収の効率向上が得られる。   When the temperature of the cooling liquid is low, the refrigerant flows to the heat exchanger, and when the temperature of the cooling liquid is high, the refrigerant flows to the bypass flow path, thereby shortening the warm-up time of the heat engine, Increased efficiency of waste heat recovery.

好適な例では、前記ポンプより下流の前記冷媒流路と前記バイパス流路との間で熱交換を行なう内部熱交換器が設けられている。
冷却液の温度が低い場合には冷媒を熱交換器へ流すことにより、熱機関の暖機時間の短縮化が図られる。冷却液の温度が高い場合には冷媒をバイパス流路（つまり内部熱交換器）へ流すことにより、ポンプより下流の冷媒に熱エネルギーが付与され、熱効率が向上する。 In a preferred example, an internal heat exchanger that performs heat exchange between the refrigerant flow path and the bypass flow path downstream from the pump is provided.
When the temperature of the coolant is low, the warm-up time of the heat engine can be shortened by flowing the refrigerant to the heat exchanger. When the temperature of the coolant is high, by flowing the refrigerant to the bypass channel (that is, the internal heat exchanger), thermal energy is imparted to the refrigerant downstream from the pump, and the thermal efficiency is improved.

好適な例では、前記熱交換器と前記凝縮器との間の前記冷媒流路には内部熱交換器が設けられている。
冷却液の温度が低い場合には冷媒を熱交換器へ流すことにより、熱機関の暖機時間の短縮化が図られる。冷却液の温度が高い場合には冷媒をバイパス流路へ流す（つまり熱交換器を迂回させる）ことにより、膨張機から流出した冷媒の熱エネルギーの多くがポンプより下流の冷媒に付与され、熱効率が向上する。 In a preferred example, an internal heat exchanger is provided in the refrigerant flow path between the heat exchanger and the condenser.
When the temperature of the coolant is low, the warm-up time of the heat engine can be shortened by flowing the refrigerant to the heat exchanger. When the temperature of the coolant is high, the refrigerant flows into the bypass flow path (that is, bypasses the heat exchanger), so that most of the heat energy of the refrigerant flowing out of the expander is given to the refrigerant downstream from the pump, and the thermal efficiency Will improve.

本発明は、熱機関の暖機時間の短縮化を図りつつ廃熱回収の効率低下を回避することができるという優れた効果を奏する。   The present invention has an excellent effect of reducing the efficiency of waste heat recovery while shortening the warm-up time of the heat engine.

第１の実施形態の廃熱回収装置を示す模式図。The schematic diagram which shows the waste-heat recovery apparatus of 1st Embodiment. 第２の実施形態の廃熱回収装置を示す模式図。The schematic diagram which shows the waste-heat recovery apparatus of 2nd Embodiment. 第３の実施形態の廃熱回収装置を示す模式図。The schematic diagram which shows the waste heat recovery apparatus of 3rd Embodiment. 第４の実施形態の廃熱回収装置を示す模式図。The schematic diagram which shows the waste-heat recovery apparatus of 4th Embodiment.

以下、本発明を具体化した第１の実施形態を図１に基づいて説明する。
図１に示すように、廃熱回収装置１１は、廃熱源としてのエンジン１２（熱機関）と、ランキンサイクル回路１３とを備えている。 Hereinafter, a first embodiment of the present invention will be described with reference to FIG.
As shown in FIG. 1, the waste heat recovery apparatus 11 includes an engine 12 (heat engine) as a waste heat source and a Rankine cycle circuit 13.

ランキンサイクル回路１３では、エンジン１２からの廃熱によって加熱される冷媒が循環する。廃熱回収装置１１を構成する回転電機１４は、ランキンサイクル回路１３の一部を構成している。   In the Rankine cycle circuit 13, the refrigerant heated by the waste heat from the engine 12 circulates. The rotating electrical machine 14 constituting the waste heat recovery device 11 constitutes a part of the Rankine cycle circuit 13.

次に、廃熱回収装置１１におけるランキンサイクル回路１３について説明する。
図１に示すように、ランキンサイクル回路１３は、回転電機１４を構成する膨張機３１、熱交換器４７、凝縮器４９、回転電機１４を構成するポンプ４１、及びボイラ４２によって構成されている。 Next, the Rankine cycle circuit 13 in the waste heat recovery apparatus 11 will be described.
As shown in FIG. 1, the Rankine cycle circuit 13 includes an expander 31 that constitutes the rotating electrical machine 14, a heat exchanger 47, a condenser 49, a pump 41 that constitutes the rotating electrical machine 14, and a boiler 42.

ボイラ４２は、放熱部４２１と吸熱部４２２とを備える。ポンプ４１の吐出側にはボイラ４２の吸熱部４２２が第１流路４３を介して接続されている。
放熱部４２１は、エンジン１２に接続された排気通路４４上に設けられている。エンジン１２からの排気は、放熱部４２１で放熱した後、マフラ４５から排気される。ポンプ４１から吐出された冷媒は、ボイラ４２の吸熱部４２２と放熱部４２１との間での熱交換によりエンジン１２からの廃熱によって加熱される。 The boiler 42 includes a heat radiating part 421 and a heat absorbing part 422. A heat absorption part 422 of the boiler 42 is connected to the discharge side of the pump 41 via a first flow path 43.
The heat radiating portion 421 is provided on the exhaust passage 44 connected to the engine 12. The exhaust from the engine 12 is exhausted from the muffler 45 after radiating heat at the heat radiating portion 421. The refrigerant discharged from the pump 41 is heated by the waste heat from the engine 12 by heat exchange between the heat absorbing portion 422 and the heat radiating portion 421 of the boiler 42.

ボイラ４２の吸熱部４２２の吐出側には膨張機３１が供給流路４６を介して接続されている。ボイラ４２で加熱された高温高圧の冷媒は、供給流路４６を介して膨張機３１に導入されるようになっている。膨張機３１には熱交換器４７が排出流路４８を介して接続されている。熱交換器４７には凝縮器４９が接続流路５０を介して接続されている。膨張機３１で膨張した低圧の冷媒は、熱交換器４７を経由して凝縮器４９へ送られる。凝縮器４９の下流側にはポンプ４１が第２流路５１を介して接続されている。ポンプ４１の吸入側には第２流路５１が接続されており、ポンプ４１の吐出側には第１流路４３が接続されている。   The expander 31 is connected to the discharge side of the heat absorption part 422 of the boiler 42 via a supply flow path 46. The high-temperature and high-pressure refrigerant heated by the boiler 42 is introduced into the expander 31 via the supply channel 46. A heat exchanger 47 is connected to the expander 31 via a discharge channel 48. A condenser 49 is connected to the heat exchanger 47 via a connection channel 50. The low-pressure refrigerant expanded by the expander 31 is sent to the condenser 49 via the heat exchanger 47. A pump 41 is connected to the downstream side of the condenser 49 via the second flow path 51. A second flow path 51 is connected to the suction side of the pump 41, and a first flow path 43 is connected to the discharge side of the pump 41.

第２流路５１、第１流路４３、供給流路４６、排出流路４８及び接続流路５０は、ランキンサイクル回路の冷媒流路を構成する。
熱交換器４７は、放熱部４７１と吸熱部４７２とを備える。排出流路４８と接続流路５０とは、放熱部４７１を介して接続されている。吸熱部４７２は、エンジン１２に接続された冷却流路である冷却水循環経路５２の分岐流路５２１上に設けられている。冷却水循環経路５２の分岐流路５２２にはラジエータ５３が設けられている。車両のエンジン１２を冷却した冷却水は、温度切換弁５４の作用により、水温が高い場合には冷却水循環経路５２の分岐流路５２２を循環してラジエータ５３で放熱する。一方、水温が低い場合には冷却水循環経路５２の分岐流路５２１に冷却水が流される。 The second flow path 51, the first flow path 43, the supply flow path 46, the discharge flow path 48, and the connection flow path 50 constitute a refrigerant flow path of the Rankine cycle circuit.
The heat exchanger 47 includes a heat radiating part 471 and a heat absorbing part 472. The discharge flow path 48 and the connection flow path 50 are connected via a heat radiating portion 471. The heat absorption part 472 is provided on the branch flow path 521 of the cooling water circulation path 52 which is a cooling flow path connected to the engine 12. A radiator 53 is provided in the branch flow path 522 of the cooling water circulation path 52. The cooling water that has cooled the engine 12 of the vehicle circulates through the branch flow path 522 of the cooling water circulation path 52 and dissipates heat by the radiator 53 when the water temperature is high due to the action of the temperature switching valve 54. On the other hand, when the water temperature is low, the cooling water flows through the branch flow path 521 of the cooling water circulation path 52.

次に、第１の実施形態の作用を説明する。
ポンプ４１のポンプ作用により、第２流路５１内の冷媒は、第１流路４３、ボイラ４２の吸熱部４２２を通過して供給流路４６へ送られる。 Next, the operation of the first embodiment will be described.
Due to the pumping action of the pump 41, the refrigerant in the second flow path 51 passes through the first flow path 43 and the heat absorption part 422 of the boiler 42 and is sent to the supply flow path 46.

ボイラ４２で加熱された高圧の冷媒は、膨張機３１に導入されて膨張する。この冷媒の膨張により膨張機３１が機械的エネルギー（回転付与力）を出力する。つまり、膨張機３１は、冷媒を利用して膨張機３１の回転軸〔図示略〕及びオルタネータ２４の駆動軸〔図示略〕に回転力を付与する。膨張して圧力が低下した冷媒は、排出流路４８へ排出される。   The high-pressure refrigerant heated by the boiler 42 is introduced into the expander 31 and expands. The expander 31 outputs mechanical energy (rotation imparting force) by the expansion of the refrigerant. That is, the expander 31 applies a rotational force to the rotation shaft (not shown) of the expander 31 and the drive shaft (not shown) of the alternator 24 using the refrigerant. The refrigerant whose pressure has decreased due to expansion is discharged to the discharge channel 48.

冷却水循環経路５２内の水温が排出流路４８へ排出された冷媒の温度よりも低い場合、排出流路４８へ排出された冷媒の熱が熱交換器４７にて冷却水循環経路５２の分岐流路５２１内の冷却水に伝達される。この熱伝達により、冷却水循環経路５２内の水温が高められる。従って、エンジン１２始動直後の冷却水の温度が熱交換器４７における熱伝達によっても高められ、エンジン１２の暖機運転の時間が短縮される。   When the water temperature in the cooling water circulation path 52 is lower than the temperature of the refrigerant discharged to the discharge flow path 48, the heat of the refrigerant discharged to the discharge flow path 48 is branched by the heat exchanger 47 in the cooling water circulation path 52. It is transmitted to the cooling water in 521. By this heat transfer, the water temperature in the cooling water circulation path 52 is increased. Therefore, the temperature of the cooling water immediately after the engine 12 is started is also increased by heat transfer in the heat exchanger 47, and the warm-up operation time of the engine 12 is shortened.

熱交換器４７にて熱を奪われた冷媒は、凝縮器４９を通過してポンプ４１へ還流する。凝縮器４９を通過して第２流路５１を流れる冷媒は、冷却されて液化している。
熱交換器４７における冷却水の温度が膨張機３１から流出した冷媒の温度より高い場合にも、膨張機３１から流出した冷媒は、凝縮器４９にて冷却されて液化する。 The refrigerant deprived of heat in the heat exchanger 47 passes through the condenser 49 and returns to the pump 41. The refrigerant passing through the condenser 49 and flowing through the second flow path 51 is cooled and liquefied.
Even when the temperature of the cooling water in the heat exchanger 47 is higher than the temperature of the refrigerant flowing out from the expander 31, the refrigerant flowing out from the expander 31 is cooled by the condenser 49 and liquefied.

第１の実施形態では以下の効果が得られる。
（１）熱交換器４７における冷却水の温度（冷却水循環経路５２の分岐流路５２１内の水温）が膨張機３１から流出した冷媒の温度より低い場合には、膨張機３１から流出した冷媒の熱が熱交換器４７を介して冷却水循環経路５２に伝達される。これは、エンジン１２の暖機時間の短縮化をもたらす。 In the first embodiment, the following effects can be obtained.
(1) When the temperature of the cooling water in the heat exchanger 47 (water temperature in the branch flow path 521 of the cooling water circulation path 52) is lower than the temperature of the refrigerant flowing out from the expander 31, the refrigerant flowing out from the expander 31 Heat is transferred to the cooling water circulation path 52 through the heat exchanger 47. This shortens the warm-up time of the engine 12.

熱交換器４７における冷却水の温度が膨張機３１から流出した冷媒の温度より高い場合には、膨張機３１から流出した冷媒は、凝縮器４９にて放熱する。つまり、膨張機３１から流出した冷媒は、熱交換器４７における冷却水の温度の高低に関わりなく凝縮器４９にて液化される。従って、凝縮器４９での凝縮圧が高くなって熱効率が悪化することはなく、廃熱回収の効率低下が回避される。   When the temperature of the cooling water in the heat exchanger 47 is higher than the temperature of the refrigerant flowing out from the expander 31, the refrigerant flowing out from the expander 31 dissipates heat in the condenser 49. That is, the refrigerant flowing out of the expander 31 is liquefied in the condenser 49 regardless of the temperature of the cooling water in the heat exchanger 47. Therefore, the condensing pressure in the condenser 49 is not increased and the thermal efficiency is not deteriorated, and a reduction in the efficiency of waste heat recovery is avoided.

次に、図２の第２の実施形態を説明する。第１の実施形態と同じ構成部には同じ符合を用い、その詳細説明は省略する。
熱交換器４７と並列なバイパス流路５５が膨張機３１と凝縮器４９との間で設けられている。バイパス流路５５は、排出流路４８から分岐して接続流路５０に合流する。バイパス流路５５と排出流路４８との分岐部には電磁三方弁５６が設けられている。電磁三方弁５６は、制御部５７の励消磁制御を受ける。 Next, a second embodiment of FIG. 2 will be described. The same reference numerals are used for the same components as those in the first embodiment, and detailed description thereof is omitted.
A bypass passage 55 in parallel with the heat exchanger 47 is provided between the expander 31 and the condenser 49. The bypass channel 55 branches from the discharge channel 48 and joins the connection channel 50. An electromagnetic three-way valve 56 is provided at a branch portion between the bypass passage 55 and the discharge passage 48. The electromagnetic three-way valve 56 receives excitation / demagnetization control of the control unit 57.

制御部５７には水温検出器５８が信号接続されている。水温検出器５８は、温度切換弁５４より下流、且つ熱交換器４７の吸熱部４７２より上流の分岐流路５２１内の冷却水の温度を検出する。水温検出器５８によって得られた水温検出情報は、制御部５７へ送られる。制御部５７は、水温検出器５８から得られる水温検出情報に基づいて、電磁三方弁５６の励消磁を制御する。   A water temperature detector 58 is connected to the controller 57 as a signal. The water temperature detector 58 detects the temperature of the cooling water in the branch flow path 521 downstream from the temperature switching valve 54 and upstream from the heat absorption part 472 of the heat exchanger 47. The water temperature detection information obtained by the water temperature detector 58 is sent to the control unit 57. The controller 57 controls excitation and demagnetization of the electromagnetic three-way valve 56 based on the water temperature detection information obtained from the water temperature detector 58.

水温検出器５８によって検出された水温が予め設定された基準温度以上の場合、制御部５７は、電磁三方弁５６を励磁する。これにより、膨張機３１から流出した冷媒がバイパス流路５５へ送られる。水温検出器５８によって検出された水温が前記基準温度に満たない場合、制御部５７は、電磁三方弁５６を消磁する。これにより、膨張機３１から流出した冷媒が熱交換器４７へ送られ、排出流路４８を流れる冷媒の熱が熱交換器４７を介して冷却水循環経路５２内の冷却水へ伝達される。   When the water temperature detected by the water temperature detector 58 is equal to or higher than a preset reference temperature, the control unit 57 excites the electromagnetic three-way valve 56. Thereby, the refrigerant that has flowed out of the expander 31 is sent to the bypass channel 55. When the water temperature detected by the water temperature detector 58 is less than the reference temperature, the control unit 57 demagnetizes the electromagnetic three-way valve 56. As a result, the refrigerant that has flowed out of the expander 31 is sent to the heat exchanger 47, and the heat of the refrigerant flowing through the discharge passage 48 is transmitted to the cooling water in the cooling water circulation path 52 via the heat exchanger 47.

水温検出器５８は、冷却水の温度を検出する液温度検出手段である。電磁三方弁５６及び制御部５７は、液温度検出手段によって検出された温度に基づいて、膨張機３１から流出した冷媒をバイパス流路５５へ供給する割合を調整する調整手段を構成する。   The water temperature detector 58 is a liquid temperature detecting means for detecting the temperature of the cooling water. The electromagnetic three-way valve 56 and the control unit 57 constitute an adjusting unit that adjusts the ratio of supplying the refrigerant that has flowed out of the expander 31 to the bypass passage 55 based on the temperature detected by the liquid temperature detecting unit.

第２の実施形態では、水温が高い場合（冷媒の熱によって水温を上げる必要がない暖機完了の状態）には、冷媒がバイパス流路５５へ送られるため、エンジン１２の暖機が完了した後の熱効率が向上する。   In the second embodiment, when the water temperature is high (warm-up completion state in which it is not necessary to raise the water temperature due to the heat of the refrigerant), the refrigerant is sent to the bypass passage 55, so that the engine 12 has been warmed up. Later thermal efficiency is improved.

次に、図３の第３の実施形態を説明する。第２の実施形態と同じ構成部には同じ符合を用い、その詳細説明は省略する。
バイパス流路５５には内部熱交換器５９が設けられている。内部熱交換器５９は、放熱部５９１と吸熱部５９２とを備える。放熱部５９１は、バイパス流路５５上に設けられており、吸熱部５９２は、第１流路４３上に設けられている。 Next, a third embodiment of FIG. 3 will be described. The same reference numerals are used for the same components as those in the second embodiment, and detailed description thereof is omitted.
An internal heat exchanger 59 is provided in the bypass channel 55. The internal heat exchanger 59 includes a heat radiating part 591 and a heat absorbing part 592. The heat dissipating part 591 is provided on the bypass channel 55, and the heat absorbing part 592 is provided on the first channel 43.

水温検出器５８によって検出された水温が予め設定された基準温度以上の場合、制御部５７は、電磁三方弁５６を励磁する。これにより、膨張機３１から流出した冷媒は、バイパス流路５５へ送られ、バイパス流路５５を流れる冷媒の熱が内部熱交換器５９を介して第１流路４３内の冷媒へ伝達される。   When the water temperature detected by the water temperature detector 58 is equal to or higher than a preset reference temperature, the control unit 57 excites the electromagnetic three-way valve 56. As a result, the refrigerant that has flowed out of the expander 31 is sent to the bypass channel 55, and the heat of the refrigerant flowing through the bypass channel 55 is transmitted to the refrigerant in the first channel 43 via the internal heat exchanger 59. .

水温検出器５８によって検出された水温が前記基準温度に満たない場合、制御部５７は、電磁三方弁５６を消磁する。これにより、膨張機３１から流出した冷媒は、熱交換器４７へ送られ、排出流路４８を流れる冷媒の熱が熱交換器４７を介して冷却水循環経路５２内の冷却水へ伝達される。   When the water temperature detected by the water temperature detector 58 is less than the reference temperature, the control unit 57 demagnetizes the electromagnetic three-way valve 56. Thereby, the refrigerant that has flowed out of the expander 31 is sent to the heat exchanger 47, and the heat of the refrigerant flowing through the discharge flow path 48 is transmitted to the cooling water in the cooling water circulation path 52 via the heat exchanger 47.

第３の実施形態では、第１の実施形態と同様の効果が得られる。又、冷却水の水温が高い場合には冷媒を内部熱交換器５９へ流すことにより、ポンプ４１より下流の冷媒に熱エネルギーが付与され、熱効率が向上する。   In the third embodiment, the same effect as in the first embodiment can be obtained. In addition, when the coolant temperature is high, by flowing the refrigerant to the internal heat exchanger 59, thermal energy is given to the refrigerant downstream from the pump 41, and the thermal efficiency is improved.

次に、図４の第４の実施形態を説明する。第３の実施形態と同じ構成部には同じ符合を用い、その詳細説明は省略する。
第４の実施形態では、内部熱交換器５９の放熱部５９１が第２流路５１上に設けられており、内部熱交換器５９の吸熱部５９２が第１流路４３上に設けられている。 Next, a fourth embodiment of FIG. 4 will be described. The same components as those in the third embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.
In the fourth embodiment, the heat dissipation part 591 of the internal heat exchanger 59 is provided on the second flow path 51, and the heat absorption part 592 of the internal heat exchanger 59 is provided on the first flow path 43. .

水温検出器５８によって検出された水温が予め設定された基準温度以上の場合、制御部５７は、電磁三方弁５６を励磁する。これにより、膨張機３１から流出した冷媒は、バイパス流路５５を経由して内部熱交換器５９へ送られ、バイパス流路５５を流れてきた冷媒の熱が内部熱交換器５９を介して第１流路４３内の冷媒へ伝達される。   When the water temperature detected by the water temperature detector 58 is equal to or higher than a preset reference temperature, the control unit 57 excites the electromagnetic three-way valve 56. As a result, the refrigerant that has flowed out of the expander 31 is sent to the internal heat exchanger 59 via the bypass flow path 55, and the heat of the refrigerant that has flowed through the bypass flow path 55 passes through the internal heat exchanger 59. It is transmitted to the refrigerant in one flow path 43.

水温検出器５８によって検出された水温が前記基準温度に満たない場合、制御部５７は、電磁三方弁５６を消磁する。これにより、膨張機３１から流出した冷媒は、熱交換器４７へ送られ、排出流路４８を流れる冷媒の熱が熱交換器４７を介して冷却水循環経路５２内の冷却水へ伝達される。熱交換器４７を通過した冷媒は、内部熱交換器５９へ送られ、熱交換器４７を流れてきた冷媒の熱が内部熱交換器５９を介して第１流路４３内の冷媒へ伝達される。   When the water temperature detected by the water temperature detector 58 is less than the reference temperature, the control unit 57 demagnetizes the electromagnetic three-way valve 56. Thereby, the refrigerant that has flowed out of the expander 31 is sent to the heat exchanger 47, and the heat of the refrigerant flowing through the discharge flow path 48 is transmitted to the cooling water in the cooling water circulation path 52 via the heat exchanger 47. The refrigerant that has passed through the heat exchanger 47 is sent to the internal heat exchanger 59, and the heat of the refrigerant that has flowed through the heat exchanger 47 is transmitted to the refrigerant in the first flow path 43 via the internal heat exchanger 59. The

熱交換器４７を通ってきた冷媒の熱が内部熱交換器５９を介して第１流路４３内の冷媒へ伝達されるため、ポンプ４１より下流の冷媒に熱エネルギーが付与され、熱効率が向上する。   Since the heat of the refrigerant that has passed through the heat exchanger 47 is transmitted to the refrigerant in the first flow path 43 via the internal heat exchanger 59, thermal energy is given to the refrigerant downstream from the pump 41, and thermal efficiency is improved. To do.

本発明では以下のような実施形態も可能である。
○バイパス流路５５と排出流路４８との分岐部より下流の排出流路４８に開閉弁を、設けると共に、バイパス流路５５に別の開閉弁を設け、両開閉弁の開閉を制御して電磁三方弁５６と同じ役割を行なわせるようにしてもよい。 In the present invention, the following embodiments are also possible.
○ An opening / closing valve is provided in the discharge flow path 48 downstream from the branch portion between the bypass flow path 55 and the discharge flow path 48, and another open / close valve is provided in the bypass flow path 55 to control the opening / closing of both open / close valves. The same role as the electromagnetic three-way valve 56 may be performed.

○バイパス流路５５と熱交換器４７とへの冷媒配分流量を任意に調整できる流量分配器を用いてもよい。
○冷却液は、水以外の液体でもよい。 A flow distributor that can arbitrarily adjust the refrigerant distribution flow rate to the bypass channel 55 and the heat exchanger 47 may be used.
○ The coolant may be a liquid other than water.

１１…廃熱回収装置。１２…熱機関であるエンジン。３１…膨張機。４１…ポンプ。４２…ボイラ。４７…熱交換器。４８…冷媒流路を構成する排出流路。４９…凝縮器。５０…冷媒流路を構成する接続流路。５２…冷却流路である冷却水循環経路。５３…ラジエータ。５５…バイパス流路。５６…調整手段を構成する電磁三方弁。５７…調整手段を構成する制御部。５８…液温度検出手段としての水温検出器。５９…内部熱交換器。   11 ... Waste heat recovery device. 12 ... An engine that is a heat engine. 31 ... Expander. 41 ... Pump. 42 ... Boiler. 47 ... Heat exchanger. 48: Discharge flow path constituting the refrigerant flow path. 49 ... Condenser. 50: Connection flow path constituting the refrigerant flow path. 52: A cooling water circulation path which is a cooling flow path. 53 ... Radiator. 55: Bypass channel. 56: An electromagnetic three-way valve constituting adjusting means. 57... Control unit constituting adjustment means. 58: A water temperature detector as a liquid temperature detecting means. 59 ... Internal heat exchanger.

Claims (4)

熱機関の廃熱を熱源とするボイラと、前記ボイラで熱を与えられた冷媒を導入して廃熱を回収するための膨張機と、前記膨張機から流出した冷媒を凝縮する凝縮器と、前記凝縮器から流出した冷媒を前記ボイラへ送るポンプと、前記ボイラ、前記膨張機、前記凝縮器及び前記ポンプを接続する冷媒流路とを備える廃熱回収装置において、
前記膨張機及び前記凝縮器間の前記冷媒流路と前記熱機関を冷却する冷却液が流れる冷却流路との間で熱交換を行なうための熱交換器が設けられている廃熱回収装置。 A boiler that uses waste heat of a heat engine as a heat source, an expander for introducing a refrigerant that has been heated by the boiler to recover waste heat, a condenser that condenses the refrigerant that has flowed out of the expander, In a waste heat recovery apparatus comprising a pump that sends the refrigerant that has flowed out of the condenser to the boiler, and a refrigerant flow path that connects the boiler, the expander, the condenser, and the pump.
A waste heat recovery apparatus provided with a heat exchanger for exchanging heat between the refrigerant flow path between the expander and the condenser and a cooling flow path through which a cooling liquid for cooling the heat engine flows. 前記熱交換器と並列なバイパス流路が前記膨張機と前記凝縮器との間で設けられており、前記膨張機から流出した冷媒を前記バイパス流路へ供給する割合を調整する調整手段と、前記冷却液の温度を検出する液温度検出手段とが設けられており、前記調整手段は、前記液温度検出手段によって検出された温度に基づいて、前記割合を調整する請求項１に記載の廃熱回収装置。   A bypass passage in parallel with the heat exchanger is provided between the expander and the condenser, and adjusting means for adjusting a ratio of supplying the refrigerant flowing out of the expander to the bypass passage; 2. The waste according to claim 1, further comprising: a liquid temperature detecting unit configured to detect a temperature of the cooling liquid, wherein the adjusting unit adjusts the ratio based on a temperature detected by the liquid temperature detecting unit. Heat recovery device. 前記ポンプより下流の前記冷媒流路と前記バイパス流路との間で熱交換を行なう内部熱交換器が設けられている請求項２に記載の廃熱回収装置。   The waste heat recovery apparatus according to claim 2, wherein an internal heat exchanger that performs heat exchange between the refrigerant flow path and the bypass flow path downstream from the pump is provided. 前記ポンプより下流の前記冷媒流路と、前記熱交換器と前記凝縮器との間の前記冷媒流路との間で熱交換を行なう内部熱交換器が設けられている請求項１及び請求項２のいずれか１項に記載の廃熱回収装置。   The internal heat exchanger which performs heat exchange between the said refrigerant | coolant flow path downstream from the said pump, and the said refrigerant | coolant flow path between the said heat exchanger and the said condenser is provided. The waste heat recovery apparatus according to any one of 2.
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