JP5828219B2 - Cogeneration system, waste heat utilization apparatus, cogeneration system control method, and heat pump hot water supply apparatus - Google Patents

Cogeneration system, waste heat utilization apparatus, cogeneration system control method, and heat pump hot water supply apparatus Download PDF

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JP5828219B2
JP5828219B2 JP2011099731A JP2011099731A JP5828219B2 JP 5828219 B2 JP5828219 B2 JP 5828219B2 JP 2011099731 A JP2011099731 A JP 2011099731A JP 2011099731 A JP2011099731 A JP 2011099731A JP 5828219 B2 JP5828219 B2 JP 5828219B2
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heat exchanger
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JP2012229895A (en
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邦彦 中野
邦彦 中野
諒一 山崎
諒一 山崎
直人 岩澤
直人 岩澤
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Noritz 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]
    • 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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Description

本発明は、コージェネレーションシステムに関するものであり、特に家庭用のコージェネレーションシステムに好適なものである。
また本発明は、ヒートポンプ式給湯装置に関するものであり、特に家庭用のヒートポンプ式給湯装置に好適なものである。 The present invention relates to a cogeneration system, and is particularly suitable for a home cogeneration system.
The present invention also relates to a heat pump type hot water supply apparatus, and is particularly suitable for a household heat pump type hot water supply apparatus.

近年、一般家庭で使用する小型のコージェネレーションシステムが開発されている。このコージェネレーションシステムは、ガスエンジンを搭載した発電機や、燃料電池によって構成される発電部を備え、前記発電機や燃料電池によって電気エネルギーを発生させる。またこれらのガスエンジンや、燃料電池が発生する排熱を熱源として活用する。   In recent years, small cogeneration systems for use in ordinary households have been developed. This cogeneration system includes a generator equipped with a gas engine and a power generation unit constituted by a fuel cell, and generates electric energy by the generator and the fuel cell. The exhaust heat generated by these gas engines and fuel cells is used as a heat source.

ここで、一般家庭においては、電気を消費する時刻と、熱を消費する時刻は必ずしも一致しない。例えば夏期であれば電力需要が高いのは、クーラを使用する昼間であり、熱需要が高いのは風呂を使用する夕刻である。
そこで特許文献１に開示されたコージェネレーションシステムでは、貯留タンクを具備していて、当該貯留タンクに温水を溜めることによって熱エネルギーを貯留する構成を採用している。
即ち電力需要が高い時刻にガスエンジン等を駆動して発電を行う。そしてその際に発生する熱によって水を昇温し、この昇温した水（湯）を貯留タンクに溜置く。そして熱需要が高い時刻に、貯留タンクから湯をくみ出し、所望の用途に使用する。 Here, in a general household, the time when electricity is consumed and the time when heat is consumed are not necessarily the same. For example, in summer, the demand for power is high during the daytime when using a cooler, and the heat demand is high during the evening when using a bath.
Therefore, the cogeneration system disclosed in Patent Document 1 employs a configuration in which a storage tank is provided and thermal energy is stored by storing hot water in the storage tank.
That is, power generation is performed by driving a gas engine or the like at a time when power demand is high. And water is heated up with the heat | fever which generate | occur | produces in that case, and this heated water (hot water) is stored in a storage tank. And at the time when heat demand is high, hot water is drawn from the storage tank and used for a desired application.

特許文献１に開示されたコージェネレーションシステムでは、一次側が熱源たるガスエンジン側に接続された排熱・消費熱交換器を有している。そして当該排熱・消費熱交換器の二次側と貯留タンクを含む貯湯循環回路が形成されている。また貯留タンクを含む貯湯循環回路は、湯水で満たされている。
そして貯留タンクの底側から水を取り出して排熱・消費熱交換器の二次側に送水し、加熱後の湯水を貯留タンクの上部側から導入する。その結果、貯留タンク内の対流が少なくなり、貯留タンクの上部側に高温の湯が溜まり、貯留タンクの底側は低温の水が残る。即ち貯留タンクの内部に温度成層が形成されることとなる。 The cogeneration system disclosed in Patent Document 1 has an exhaust heat / consumed heat exchanger whose primary side is connected to the gas engine side as a heat source. A hot water circulation circuit including the secondary side of the exhaust heat / consumption heat exchanger and the storage tank is formed. The hot water circulation circuit including the storage tank is filled with hot water.
Then, water is taken out from the bottom side of the storage tank and is sent to the secondary side of the exhaust heat / consumption heat exchanger, and hot water after heating is introduced from the upper side of the storage tank. As a result, convection in the storage tank is reduced, hot water is accumulated on the upper side of the storage tank, and low temperature water remains on the bottom side of the storage tank. That is, temperature stratification is formed inside the storage tank.

湯を消費する場合には、貯留タンクの底側から冷水を注入し、貯留タンクの上部に溜まった高温の湯を押し出す。   When consuming hot water, cold water is injected from the bottom side of the storage tank, and the hot water accumulated at the top of the storage tank is pushed out.

また特許文献２には、熱源側（ガスエンジン側）を流れる冷却水の水温に応じて、排熱・消費熱交換器の二次側を流れる水量を増減する技術が開示されている。   Patent Document 2 discloses a technique for increasing or decreasing the amount of water flowing on the secondary side of the exhaust heat / consumed heat exchanger according to the temperature of the cooling water flowing on the heat source side (gas engine side).

特許文献３には、家庭用のヒートポンプ式給湯装置が開示されている。   Patent Literature 3 discloses a household heat pump hot water supply apparatus.

特開２００４−２６３９１５号公報JP 2004-263915 A 特開２００７−６４５１８号公報JP 2007-64518 A 特開２００８−１３４０４５号公報JP 2008-134045 A

ところで、貯留タンク内に温度成層を形成し、貯留タンクの上部に高温の湯を溜めるためには、貯留タンクに導入する湯水の温度が一定以上でなければならない。
そこで本発明者らは、図１に示す様な配管系統を持つコージェネレーションシステム２００を試作した。
試作したコージェネレーションシステム２００は、熱源ユニット１０１と貯湯ユニット１０２によって構成されている。
熱源ユニット１０１は、ガスエンジン１０５で駆動される発電機１０６を搭載している。また熱源ユニット１０１には、ガスエンジン１０５に冷却液を循環させて熱エネルギーを回収する排熱回収側循環回路１０７がある。 By the way, in order to form a temperature stratification in the storage tank and store hot water in the upper part of the storage tank, the temperature of the hot water introduced into the storage tank must be above a certain level.
Therefore, the inventors made a trial production of a cogeneration system 200 having a piping system as shown in FIG.
The prototype cogeneration system 200 includes a heat source unit 101 and a hot water storage unit 102.
The heat source unit 101 is equipped with a generator 106 driven by a gas engine 105. The heat source unit 101 includes an exhaust heat recovery side circulation circuit 107 that circulates a coolant through the gas engine 105 and recovers thermal energy.

排熱回収側循環回路１０７には、膨張タンク１１０と循環ポンプ１１１がある。そして排熱回収側循環回路１０７は、循環ポンプ１１１、ガスエンジン１０５、後記する排熱・消費熱交換器１１２の一次側流路及び膨張タンク１１０を環状に繋ぐものである。
排熱回収側循環回路１０７内には冷却液があり、当該冷却液は、循環ポンプ１１１で加圧されてガスエンジン１０５に入り、さらに排熱・消費熱交換器１１２の一次側流路を通過して膨張タンク１１０に入り、循環ポンプ１１１に戻る。
また排熱回収側循環回路１０７の排熱・消費熱交換器１１２の吐出側とガスエンジン１０５の吸い込み側との間には冷却液用温度センサー１０８が設けられ、ガスエンジン１０５に導入される冷却液の温度が監視されている。冷却液用温度センサー１０８のより具体的な位置は、膨張タンク１１０と循環ポンプ１１１の間である。 The exhaust heat recovery side circulation circuit 107 includes an expansion tank 110 and a circulation pump 111. The exhaust heat recovery side circulation circuit 107 connects the circulation pump 111, the gas engine 105, a primary side flow path of the exhaust heat / consumption heat exchanger 112, which will be described later, and the expansion tank 110 in an annular shape.
There is a coolant in the exhaust heat recovery side circulation circuit 107, and the coolant is pressurized by the circulation pump 111 and enters the gas engine 105, and further passes through the primary flow path of the exhaust heat / consumed heat exchanger 112. Then, it enters the expansion tank 110 and returns to the circulation pump 111.
Further, a coolant temperature sensor 108 is provided between the discharge side of the exhaust heat / consumption heat exchanger 112 of the exhaust heat recovery side circulation circuit 107 and the suction side of the gas engine 105, and cooling introduced into the gas engine 105. The liquid temperature is monitored. A more specific position of the coolant temperature sensor 108 is between the expansion tank 110 and the circulation pump 111.

一方、貯湯ユニット１０２には貯留タンク１２０と、循環ポンプ１２１と、排熱・消費熱交換器１１２が内蔵されている。そして貯留タンク１２０と、循環ポンプ１２１と、排熱・消費熱交換器１１２の二次側流路が環状に接続されて貯湯循環回路（熱消費側回路）１２２が形成されている。
貯留タンク１２０を含む貯湯循環回路１２２内には湯水が満たされている。そして循環ポンプ１２１が起動すると、貯留タンク１２０の底側から循環ポンプ１２１に冷水が導入され、排熱・消費熱交換器１１２の二次側流路を経由して加熱された湯水が貯留タンク１２０の上部から注入される。
さらに排熱・消費熱交換器１１２の二次側流路の吐出側と、貯留タンク１２０の上部との間には、加熱水用温度センサー１１３が設けられており、排熱・消費熱交換器１１２から吐出される湯水の温度を監視している。 On the other hand, the hot water storage unit 102 includes a storage tank 120, a circulation pump 121, and a waste heat / consumed heat exchanger 112. The storage tank 120, the circulation pump 121, and the secondary side flow path of the exhaust heat / consumption heat exchanger 112 are connected in a ring shape to form a hot water storage circulation circuit (heat consumption side circuit) 122.
The hot water circulation circuit 122 including the storage tank 120 is filled with hot water. When the circulation pump 121 is activated, cold water is introduced into the circulation pump 121 from the bottom side of the storage tank 120, and hot water heated through the secondary side flow path of the exhaust heat / consumption heat exchanger 112 is stored in the storage tank 120. It is injected from the top.
Further, a temperature sensor 113 for heating water is provided between the discharge side of the secondary side flow path of the exhaust heat / consumption heat exchanger 112 and the upper part of the storage tank 120, and the exhaust heat / consumption heat exchanger The temperature of hot water discharged from 112 is monitored.

また特に試作したコージェネレーションシステム２００では、貯留タンク１２０を迂回するバイパス流路１２５が形成されている。そしてバイパス流路１２５と循環ポンプ１２１の上流側との間には、混合弁１２６が介在されている。
即ち混合弁１２６は、３個のポートを持ち、その一つは貯留タンク１２０の底側に接続され、他の一つはバイパス流路１２５の末端に接続され、残る一つが循環ポンプ１２１の上流側（吸い込み側）に接続されている。 In particular, in the prototype cogeneration system 200, a bypass passage 125 that bypasses the storage tank 120 is formed. A mixing valve 126 is interposed between the bypass flow path 125 and the upstream side of the circulation pump 121.
That is, the mixing valve 126 has three ports, one of which is connected to the bottom side of the storage tank 120, the other one is connected to the end of the bypass passage 125, and the remaining one is upstream of the circulation pump 121. Connected to the side (suction side).

試作したコージェネレーションシステム２００では、熱源ユニット１０１のガスエンジン１０５を起動し、循環ポンプ１１１を運転させることによって排熱回収側循環回路１０７に冷却液が循環する。そしてガスエンジン１０５に導入された冷却液はガスエンジン１０５の排熱で昇温され、排熱・消費熱交換器１１２の一次側流路を流れる。   In the prototype cogeneration system 200, the gas engine 105 of the heat source unit 101 is started and the circulation pump 111 is operated, whereby the coolant circulates in the exhaust heat recovery side circulation circuit 107. The coolant introduced into the gas engine 105 is heated by the exhaust heat of the gas engine 105 and flows through the primary side flow path of the exhaust heat / consumed heat exchanger 112.

一方、貯湯ユニット１０２側では、循環ポンプ１２１が起動され、貯留タンク１２０の底側から循環ポンプ１２１に冷水が導入され、排熱・消費熱交換器１１２の二次側流路を流れる。ここで排熱・消費熱交換器１１２の一次側流路は、排熱回収側循環回路１０７の一部を構成しており、熱源ユニット１０１側から高温の冷却液が流れるから、排熱回収側循環回路１０７の熱エネルギーが貯湯ユニット１０２の貯湯循環回路１２２に移動する。
その結果、排熱・消費熱交換器１１２の二次側流路を流れる湯水が加熱昇温する。
そして昇温した湯水の一部が貯留タンク１２０の上部から注入される。また昇温した湯水の残部はバイパス流路１２５を流れて循環ポンプ１２１の吸い込み側に戻る。 On the other hand, on the hot water storage unit 102 side, the circulation pump 121 is activated, cold water is introduced into the circulation pump 121 from the bottom side of the storage tank 120, and flows through the secondary side flow path of the exhaust heat / consumed heat exchanger 112. Here, the primary side flow path of the exhaust heat / consumption heat exchanger 112 constitutes a part of the exhaust heat recovery side circulation circuit 107, and high temperature coolant flows from the heat source unit 101 side. The thermal energy of the circulation circuit 107 moves to the hot water storage circuit 122 of the hot water storage unit 102.
As a result, the hot water flowing through the secondary flow path of the exhaust heat / consumed heat exchanger 112 is heated and heated.
Then, a part of the heated hot water is injected from the upper part of the storage tank 120. Further, the remaining portion of the heated hot water flows through the bypass passage 125 and returns to the suction side of the circulation pump 121.

試作したコージェネレーションシステム２００では、前記した様に排熱・消費熱交換器１１２の二次側流路の吐出側と、貯留タンク１２０の上部との間に、加熱水用温度センサー１１３が設けられており、排熱・消費熱交換器１１２から吐出される湯水の温度を監視している。
そして試作したコージェネレーションシステム２００では、排熱・消費熱交換器１１２から吐出される湯水の温度を監視し、これが貯湯目標温度（使用用途目標温度）と一致する様に混合弁１２６の混合比率を調整する制御方式を採用した。ここで貯湯目標温度は、貯留タンク１２０に注入するのに適する温度であり、温度成層を構成することができる程度に高い温度である。例えば貯湯目標温度は摂氏８０度程度の温度である。
即ち試作したコージェネレーションシステム２００では、排熱・消費熱交換器１１２の二次側流路の吐出側と、貯留タンク１２０の上部との間に、加熱水用温度センサー１１３が設けられており、排熱・消費熱交換器１１２から吐出される湯水の温度を監視している。
そしてこの加熱水用温度センサー１１３の検知温度が例えば摂氏８０度といった所定の高温となる様に混合弁１２６の混合比率を調整する。より具体的には、加熱水用温度センサー１１３の検知温度が低い場合には、バイパス流路１２５から導入される湯水の量を増やし、貯留タンク１２０の下部から導入される湯水の量を減らす。そうすると循環ポンプ１２１に導入される湯水に高温の湯水が多く混じり、排熱・消費熱交換器１１２に導入される湯水の温度が上昇する。その結果、排熱・消費熱交換器１１２から吐出される湯水の温度が上昇し、排熱・消費熱交換器１１２から吐出される湯水の温度が貯湯目標温度（使用用途目標温度）に至る。 In the prototype cogeneration system 200, the heating water temperature sensor 113 is provided between the discharge side of the secondary side flow path of the exhaust heat / consumption heat exchanger 112 and the upper portion of the storage tank 120 as described above. The temperature of the hot water discharged from the exhaust heat / consumed heat exchanger 112 is monitored.
In the prototype cogeneration system 200, the temperature of the hot water discharged from the exhaust heat / consumed heat exchanger 112 is monitored, and the mixing ratio of the mixing valve 126 is adjusted so that the temperature matches the hot water storage target temperature (use target temperature). The control method to adjust is adopted. Here, the hot water storage target temperature is a temperature suitable for pouring into the storage tank 120, and is high enough to constitute a temperature stratification. For example, the hot water storage target temperature is about 80 degrees Celsius.
That is, in the prototype cogeneration system 200, a heating water temperature sensor 113 is provided between the discharge side of the secondary side flow path of the exhaust heat / consumption heat exchanger 112 and the upper portion of the storage tank 120. The temperature of the hot water discharged from the exhaust heat / consumed heat exchanger 112 is monitored.
Then, the mixing ratio of the mixing valve 126 is adjusted so that the temperature detected by the heating water temperature sensor 113 becomes a predetermined high temperature such as 80 degrees Celsius. More specifically, when the temperature detected by the heating water temperature sensor 113 is low, the amount of hot water introduced from the bypass passage 125 is increased, and the amount of hot water introduced from the lower portion of the storage tank 120 is reduced. Then, a lot of hot water is mixed with the hot water introduced into the circulation pump 121, and the temperature of the hot water introduced into the exhaust heat / consumed heat exchanger 112 rises. As a result, the temperature of the hot water discharged from the exhaust heat / consumed heat exchanger 112 rises, and the temperature of the hot water discharged from the exhaust heat / consumed heat exchanger 112 reaches the hot water storage target temperature (use target temperature).

逆に、加熱水用温度センサー１１３の検知温度が高い場合には、バイパス流路１２５から導入される湯水の量を減らし、貯留タンク１２０の下部から導入される湯水の量を増加させる。その結果、循環ポンプ１２１に導入される湯水の温度が低下し、排熱・消費熱交換器１１２に導入される湯水の温度が低下する。その結果、排熱・消費熱交換器１１２から吐出される湯水の温度が下がって、排熱・消費熱交換器１１２から吐出される湯水の温度が貯湯目標温度（使用用途目標温度）に降下する。   Conversely, when the temperature detected by the heating water temperature sensor 113 is high, the amount of hot water introduced from the bypass passage 125 is reduced and the amount of hot water introduced from the lower portion of the storage tank 120 is increased. As a result, the temperature of the hot water introduced into the circulation pump 121 is lowered, and the temperature of the hot water introduced into the exhaust heat / consumed heat exchanger 112 is lowered. As a result, the temperature of the hot water discharged from the exhaust heat / consumption heat exchanger 112 decreases, and the temperature of the hot water discharged from the exhaust heat / consumption heat exchanger 112 falls to the target hot water storage temperature (use target temperature). .

しかしながら、試作したコージェネレーションシステム２００は、排熱・消費熱交換器１１２から吐出される湯水の温度が安定せず、予定した温度制御が出来ないものであった。
即ち試作したコージェネレーションシステム２００では、消費電力を極力小さくするために、貯湯ユニット１０２側の循環ポンプ１２１に容量の小さいものを選定した。そのため貯湯循環回路１２２（バイパス流路１２５を含む）を流れる湯水の流量が少なく、加熱水用温度センサー１１３の検知速度に若干の遅れが生じた。
これに対して混合弁１２６の反応は鋭敏であった。そのため加熱水用温度センサー１１３の検知速度と混合弁１２６の反応速度がマッチングせず、動作が不安定となった。即ち加熱水用温度センサー１１３の検知速度に対して混合弁１２６の反応速度が早すぎ、混合弁１２６がハンチングを起こしてしまった。
そこで混合弁１２６の反応速度を故意に遅らせる処置を施したが、外乱に対して追従が困難となってしまった。
即ち加熱水用温度センサー１１３の検知速度と混合弁１２６の反応速度がマッチングする領域は狭く、両者をマッチングさせることは実際上困難であった。 However, the prototype cogeneration system 200 has a problem that the temperature of the hot water discharged from the exhaust heat / consumed heat exchanger 112 is not stable, and the planned temperature control cannot be performed.
That is, in the prototype cogeneration system 200, in order to reduce power consumption as much as possible, a circulating pump 121 on the hot water storage unit 102 side having a small capacity was selected. Therefore, the flow rate of hot water flowing through the hot water storage circuit 122 (including the bypass flow path 125) is small, and the detection speed of the heating water temperature sensor 113 is slightly delayed.
On the other hand, the reaction of the mixing valve 126 was sensitive. For this reason, the detection speed of the heating water temperature sensor 113 and the reaction speed of the mixing valve 126 do not match, and the operation becomes unstable. That is, the reaction speed of the mixing valve 126 is too fast for the detection speed of the temperature sensor 113 for heated water, and the mixing valve 126 has caused hunting.
Therefore, a measure was taken to intentionally delay the reaction speed of the mixing valve 126, but it was difficult to follow the disturbance.
That is, the region where the detection speed of the heating water temperature sensor 113 and the reaction speed of the mixing valve 126 match is narrow, and it is practically difficult to match the two.

そこで次の方策として、ガスエンジン１０５に導入される冷却液の温度が一定となる様に混合弁１２６の混合比率を調整することとした。
即ちガスエンジン１０５を冷却する冷却液は、循環量を絞ることによる弊害が大きいために、比較的大容量の循環量が確保されている。
そのため熱源ユニット１０１側の冷却液用温度センサー１０８の反応速度は早い。
また冷却液の温度と、貯湯ユニット１０２の貯湯循環回路１２２を流れる湯水の温度の間には相関がある。
例えば貯湯循環回路１２２における排熱・消費熱交換器１１２の吐出側の温度と、排熱回収側循環回路１０７における排熱・消費熱交換器１１２の吐出側の温度は、一つの熱交換器の一次側出口温度と二次側出口温度の関係にあるから、強い正の相関がある。即ち排熱回収側循環回路１０７における排熱・消費熱交換器１１２の吐出側の温度が高い場合には貯湯循環回路１２２における排熱・消費熱交換器１１２の吐出側の温度も高い。逆に排熱回収側循環回路１０７における排熱・消費熱交換器１１２の吐出側の温度が低い場合には貯湯循環回路１２２における排熱・消費熱交換器１１２の吐出側の温度も低い。 Therefore, as a next measure, the mixing ratio of the mixing valve 126 is adjusted so that the temperature of the coolant introduced into the gas engine 105 is constant.
That is, the coolant that cools the gas engine 105 has a large adverse effect due to the reduction of the circulation amount, and therefore a relatively large circulation amount is secured.
Therefore, the reaction rate of the coolant temperature sensor 108 on the heat source unit 101 side is fast.
Further, there is a correlation between the temperature of the coolant and the temperature of the hot water flowing through the hot water circulation circuit 122 of the hot water storage unit 102.
For example, the temperature on the discharge side of the exhaust heat / consumption heat exchanger 112 in the hot water storage circulation circuit 122 and the temperature on the discharge side of the exhaust heat / consumption heat exchanger 112 in the exhaust heat recovery side circulation circuit 107 are the same as those of one heat exchanger. Since there is a relationship between the primary side outlet temperature and the secondary side outlet temperature, there is a strong positive correlation. That is, when the temperature on the discharge side of the exhaust heat / consumption heat exchanger 112 in the exhaust heat recovery side circulation circuit 107 is high, the temperature on the discharge side of the exhaust heat / consumption heat exchanger 112 in the hot water storage circulation circuit 122 is also high. Conversely, when the temperature on the discharge side of the exhaust heat / consumption heat exchanger 112 in the exhaust heat recovery side circulation circuit 107 is low, the temperature on the discharge side of the exhaust heat / consumption heat exchanger 112 in the hot water storage circulation circuit 122 is also low.

上記した様に、ガスエンジン１０５に導入される冷却液の温度が一定となる様に混合弁１２６の混合比率を調整する制御を採用すると、冷却液用温度センサー１０８の検知速度と混合弁１２６の反応速度がマッチングし、貯湯循環回路１２２を流れる湯水の温度が安定した。   As described above, when the control of adjusting the mixing ratio of the mixing valve 126 so that the temperature of the coolant introduced into the gas engine 105 is constant, the detection speed of the coolant temperature sensor 108 and the mixing valve 126 are controlled. The reaction rates matched and the temperature of the hot water flowing through the hot water circulation circuit 122 was stabilized.

しかしながら、この方策によると、貯留タンク１２０に導入される湯の温度を正確に検知することができず、貯留タンク１２０に導入される湯の温度が貯湯目標温度（使用用途目標温度）から離れてしまう場合があった。
そこで本発明は上記した問題点に注目し、熱消費側回路の温度が安定し、且つ消費側の液体の温度を所定の使用用途目標温度に近づけることができるコージェネレーションシステム等を提供することを目的とする。
またヒートポンプ式給湯装置についても類似の問題がある。
そこで本発明は、冷媒液の温度が安定し、且つ消費側の液体の温度を所定の使用用途目標温度に近づけることができるヒートポンプ式給湯装置を提供することを目的とする。 However, according to this measure, the temperature of the hot water introduced into the storage tank 120 cannot be accurately detected, and the temperature of the hot water introduced into the storage tank 120 is away from the hot water storage target temperature (use target temperature). There was a case.
Therefore, the present invention pays attention to the above-described problems, and provides a cogeneration system and the like that can stabilize the temperature of the heat consumption side circuit and can bring the temperature of the liquid on the consumption side closer to a predetermined target temperature for use. Objective.
There are similar problems with heat pump hot water supply devices.
Therefore, an object of the present invention is to provide a heat pump type hot water supply apparatus in which the temperature of the refrigerant liquid is stable and the temperature of the liquid on the consumption side can be brought close to a predetermined use application target temperature.

上記した課題を解決するための請求項１に記載の発明は、電気エネルギーと熱エネルギーとを同時に発生させる発電部と、前記発電部に冷却液を循環させて発電部の熱エネルギーを回収する排熱回収側循環回路と、液体を循環及び／又は通過させて熱エネルギーを貯留及び／又は消費する熱消費側回路と、排熱回収側循環回路及び熱消費側回路の一部を構成し排熱回収側循環回路から熱消費側回路に熱エネルギーを移動させる排熱・消費熱交換器とを備えたコージェネレーションシステムにおいて、排熱回収側循環回路を流れる冷却液の温度を検知する冷却液温度検知手段と、排熱・消費熱交換器の下流側であって熱消費側回路を流れる液体の温度を検知する消費側温度検知手段と、排熱・消費熱交換器の熱消費側回路側に流入する液体の温度及び／又は流量を増減することができる消費側液制御手段とを備え、前記冷却液温度検知手段の検知温度と消費側温度検知手段の検知温度の双方に基づいて消費側液制御手段を制御し、排熱回収側循環回路を流れる冷却液の目標温度を冷却液目標温度とし、熱消費側回路は、湯水を貯留する貯留タンクを有していて熱エネルギーを貯留する機能を備え、排熱・消費熱交換器と貯留タンクの双方を含む貯湯循環回路があり、排熱・消費熱交換器には貯留タンクの下部側から湯水が供給され、排熱・消費熱交換器から吐出される湯水は貯留タンクの上部から注入され、貯留タンクをバイパスするバイパス流路を有し、前記消費側液制御手段は、排熱回収側循環回路を流れる冷却液の温度が冷却液目標温度よりも高い場合には、バイパス流路から排熱・消費熱交換器に導入される湯水の量を減らし、貯留タンクの下部から排熱・消費熱交換器に導入される湯水の量を増加させる様に動作することを特徴とするコージェネレーションシステムである。 The invention described in claim 1 for solving the above-described problem includes a power generation unit that simultaneously generates electrical energy and thermal energy, and an exhaust that recovers thermal energy of the power generation unit by circulating a coolant through the power generation unit. A heat recovery side circulation circuit, a heat consumption side circuit that circulates and / or passes liquid to store and / or consume thermal energy, and a part of the exhaust heat recovery side circulation circuit and the heat consumption side circuit constitutes exhaust heat. Coolant temperature detection for detecting the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit in a cogeneration system equipped with an exhaust heat / consumption heat exchanger that transfers heat energy from the recovery side circulation circuit to the heat consumption side circuit Means, a consumption side temperature detection means for detecting the temperature of the liquid flowing in the heat consumption side circuit downstream of the exhaust heat / consumption heat exchanger, and the heat consumption side circuit side of the exhaust heat / consumption heat exchanger Liquid temperature And / or a consumer fluid control means may increase or decrease the flow rate to control the consumer fluid control means based on both the detected temperature of the detected temperature and the consuming temperature detecting means of the coolant temperature detecting means The target temperature of the coolant flowing through the exhaust heat recovery side circulation circuit is the coolant target temperature, and the heat consumption side circuit has a storage tank for storing hot water and has a function of storing thermal energy, There is a hot water circulation circuit that includes both a heat exchanger and a storage tank. Hot water is supplied to the exhaust heat / consumption heat exchanger from the lower side of the storage tank, and the hot water discharged from the exhaust heat / consumption heat exchanger is Injected from the upper part of the storage tank, and has a bypass flow path that bypasses the storage tank, the consumption side liquid control means, when the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit is higher than the target coolant temperature From the bypass channel Cogeneration system characterized by reducing the hot water of the amount introduced into the heat-dissipation heat exchanger operated as to increase the hot water in the amount to be introduced into the exhaust heat-dissipation heat exchanger from the bottom of the storage tank It is.

本発明のコージェネレーションシステムでは、冷却液温度検知手段の検知温度と消費側温度検知手段の検知温度の双方に基づいて消費側液制御手段を制御する。
一例として、試作したコージェネレーションシステム２００に構成要素を当てはめると、本発明では、熱源ユニット（熱源部）１０１側の冷却液用温度センサー（冷却液温度検知手段）１０８の検知温度と貯湯ユニット（排熱利用装置）１０２側の加熱水用温度センサー（消費側温度検知手段）１１３の検知温度の双方に基づいて混合弁（消費側液制御手段）１２６を制御する。
本発明のコージェネレーションシステムでは、冷却液温度検知手段の検知温度を考慮して消費側液制御手段を制御するので、排熱回収側循環回路の排熱・消費熱交換器から吐出される液体の温度が安定する。
また本発明のコージェネレーションシステムでは、消費側温度検知手段の検知温度を考慮して消費側液制御手段を制御するので、熱消費側回路の排熱・消費熱交換器から吐出される液体の温度は所望の目標温度に近いものとなる。 In the cogeneration system of the present invention, the consumption side liquid control means is controlled based on both the detected temperature of the coolant temperature detection means and the detected temperature of the consumption side temperature detection means.
As an example, when components are applied to the prototype cogeneration system 200, in the present invention, the detected temperature of the coolant temperature sensor (coolant temperature detection means) 108 on the heat source unit (heat source section) 101 side and the hot water storage unit (exhaust temperature). The mixing valve (consumption side liquid control means) 126 is controlled based on both the detected temperatures of the heating water temperature sensor (consumption side temperature detection means) 113 on the heat utilization apparatus) 102 side.
In the cogeneration system of the present invention, the consumption side liquid control means is controlled in consideration of the temperature detected by the coolant temperature detection means, so the liquid discharged from the exhaust heat / consumption heat exchanger of the exhaust heat recovery side circulation circuit is controlled. The temperature stabilizes.
In the cogeneration system of the present invention, since the consumption side liquid control means is controlled in consideration of the temperature detected by the consumption side temperature detection means, the temperature of the liquid discharged from the exhaust heat / consumption heat exchanger of the heat consumption side circuit Is close to the desired target temperature.

冷却液温度検知手段の検知温度と消費側温度検知手段の検知温度のいずれを主とし、いずれを従とするかは任意であるが、冷却液温度検知手段の検知温度を主とし、消費側温度検知手段の検知温度を従とすることが推奨される。即ち冷却液温度検知手段の検知温度を制御対象として消費側液制御手段を動作させ、補助的に消費側温度検知手段の検知温度を利用することが推奨される。   The temperature detected by the coolant temperature detection means or the temperature detected by the consumption side temperature detection means is the main and the subordinate is arbitrary, but the detection temperature of the coolant temperature detection means is the main and the consumption side temperature. It is recommended that the detection temperature of the detection means be subordinate. That is, it is recommended that the consumption side liquid control means is operated with the detection temperature of the coolant temperature detection means as a control target and the detection temperature of the consumption side temperature detection means is used as an auxiliary.

この思想を反映させた請求項２に記載の発明は、熱消費側回路であって排熱・消費熱交換器の下流側を流れる液体の目標温度を使用用途目標温度とし、消費側液制御手段は冷却液温度検知手段の検知温度が冷却液目標温度に一致する様に制御され、且つ消費側温度検知手段の検知温度と使用用途目標温度との偏差に応じて前記冷却液目標温度が補正されることを特徴とする請求項１に記載のコージェネレーションシステムである。   The invention according to claim 2 reflecting this idea is a heat consumption side circuit, wherein the target temperature of the liquid flowing on the downstream side of the exhaust heat / consumption heat exchanger is used as the use target temperature, and the consumption side liquid control means Is controlled so that the detected temperature of the coolant temperature detecting means coincides with the target temperature of the coolant, and the coolant target temperature is corrected according to the deviation between the detected temperature of the consumption side temperature detecting means and the intended use target temperature. The cogeneration system according to claim 1.

本発明のコージェネレーションシステムでは、消費側液制御手段は冷却液温度検知手段の検知温度が冷却液目標温度に一致する様に制御されるから、排熱回収側循環回路の排熱・消費熱交換器から吐出される液体の温度が安定する。
また消費側温度検知手段の検知温度と使用用途目標温度との偏差に応じて前記冷却液目標温度が補正されるので、実際の消費側温度も消費側液制御手段の動きに反映される。そのため消費側温度が目標温度に近づく。 In the cogeneration system of the present invention, the consumption side liquid control means is controlled so that the detected temperature of the coolant temperature detection means matches the target temperature of the coolant, so that the exhaust heat / consumed heat exchange of the exhaust heat recovery side circulation circuit The temperature of the liquid discharged from the container is stabilized.
Further, since the coolant target temperature is corrected in accordance with the deviation between the detected temperature of the consumption side temperature detection means and the intended use target temperature, the actual consumption side temperature is also reflected in the movement of the consumption side liquid control means. Therefore, the consumption side temperature approaches the target temperature.

消費側液制御手段は混合弁であり、熱消費側回路は、湯水を貯留する貯留タンクを有していて熱エネルギーを貯留する機能を備え、排熱・消費熱交換器と貯留タンクの双方を含む貯湯循環回路があり、排熱・消費熱交換器には貯留タンクの下部側から湯水が供給され、排熱・消費熱交換器から吐出される湯水は貯留タンクの上部から注入され、貯留タンクをバイパスするバイパス流路を有し、前記混合弁はバイパス流路を流れる湯水と貯留タンクの下部から供給される湯水を混合することが可能な位置に設けられていることが望ましい。 The consumption side liquid control means is a mixing valve, and the heat consumption side circuit has a storage tank for storing hot water and has a function of storing thermal energy, and has both a waste heat / consumption heat exchanger and a storage tank. There is a hot water storage circuit that contains hot water from the lower side of the storage tank to the exhaust heat / consumption heat exchanger, and hot water discharged from the exhaust heat / consumption heat exchanger is injected from the upper part of the storage tank. It is desirable that the mixing valve is provided at a position where hot water flowing through the bypass flow channel and hot water supplied from a lower portion of the storage tank can be mixed .

上記した態様のコージェネレーションシステムでは、貯留タンクをバイパスするバイパス流路を有する。ここでバイパス流路には、排熱・消費熱交換器から吐出された湯水が流れるので、昇温された湯水が流れることとなる。
そして本発明では、バイパス流路を流れる昇温された湯水と、貯留タンクの下部から供給される低温の湯水が混合弁で混合されて適度の温度となる。そしてこの混合後の湯水が、排熱・消費熱交換器に導入されて再度加熱されるので、排熱・消費熱交換器から吐出される湯水が所望の温度に近いものとなる。即ち本発明は、排熱・消費熱交換器によって加熱される前の湯水の温度を、予め適温に調節するものであり、排熱・消費熱交換器から排出された湯水は所望の温度となっている。 The cogeneration system according to the aspect described above has a bypass flow path that bypasses the storage tank. Here, since the hot water discharged from the exhaust heat / consumed heat exchanger flows through the bypass flow path, the hot water heated up flows.
In the present invention, the heated hot water flowing through the bypass channel and the low-temperature hot water supplied from the lower part of the storage tank are mixed by the mixing valve to obtain an appropriate temperature. Then, the mixed hot water is introduced into the exhaust heat / consumption heat exchanger and heated again, so that the hot water discharged from the exhaust heat / consumption heat exchanger becomes close to a desired temperature. That is, according to the present invention, the temperature of the hot water before being heated by the exhaust heat / consumption heat exchanger is adjusted to an appropriate temperature in advance, and the hot water discharged from the exhaust heat / consumption heat exchanger becomes a desired temperature. ing.

また一つの態様として、電気エネルギーと熱エネルギーとを同時に発生させる発電部と、前記発電部に冷却液を循環させて発電部の熱エネルギーを回収する排熱回収側循環回路と、液体を循環及び／又は通過させて熱エネルギーを貯留及び／又は消費する熱消費側回路と、排熱回収側循環回路及び熱消費側回路の一部を構成し排熱回収側循環回路から熱消費側回路に熱エネルギーを移動させる排熱・消費熱交換器とを備えたコージェネレーションシステムにおいて、排熱回収側循環回路を流れる冷却液の温度を検知する冷却液温度検知手段と、排熱・消費熱交換器の下流側にあって熱消費側回路を流れる液体の温度を検知する消費側温度検知手段とを備え、排熱回収側循環回路を流れる冷却液の目標温度を冷却液目標温度とし、熱消費側回路であって排熱・消費熱交換器の下流側を流れる液体の目標温度を使用用途目標温度とし、冷却液温度検知手段の検知温度が冷却液目標温度に一致する様に熱消費側回路が制御され、且つ消費側温度検知手段の検知温度と使用用途目標温度との偏差に応じて前記冷却液目標温度が補正されることを特徴とするコージェネレーションシステムが考えられる。 Also, as one aspect, a power generation unit that simultaneously generates electrical energy and thermal energy, a waste heat recovery side circulation circuit that circulates a coolant through the power generation unit and recovers thermal energy of the power generation unit, and circulates liquid and A heat consumption side circuit that stores and / or consumes heat energy by passing through, and forms a part of the exhaust heat recovery side circulation circuit and the heat consumption side circuit, and heat from the exhaust heat recovery side circulation circuit to the heat consumption side circuit In a cogeneration system equipped with an exhaust heat / consumption heat exchanger that moves energy, a coolant temperature detection means that detects the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit, and an exhaust heat / consumption heat exchanger And a consumption side temperature detecting means for detecting the temperature of the liquid flowing in the downstream side and flowing through the heat consumption side circuit, the target temperature of the coolant flowing through the exhaust heat recovery side circulation circuit as the cooling liquid target temperature, and the heat consumption side circuit The target temperature of the liquid flowing downstream of the exhaust heat / consumption heat exchanger is used as the target temperature for use, and the heat consumption side circuit is controlled so that the detected temperature of the coolant temperature detection means matches the target coolant temperature. In addition, a cogeneration system is conceivable in which the coolant target temperature is corrected in accordance with the deviation between the detected temperature of the consumption side temperature detecting means and the intended use target temperature .

本態様のコージェネレーションシステムについても、冷却液温度検知手段の検知温度が冷却液目標温度に一致する様に制御されるから、排熱回収側循環回路の排熱・消費熱交換器から吐出される液体の温度が安定する。
また消費側温度検知手段の検知温度と使用用途目標温度との偏差に応じて前記冷却液目標温度が補正されるので、実際の消費側温度も消費側液制御手段の動きに反映される。そのため消費側温度が目標温度に近づく。 The cogeneration system of this aspect is also controlled so that the detected temperature of the coolant temperature detecting means matches the coolant target temperature, so that it is discharged from the exhaust heat / heat consumption heat exchanger of the exhaust heat recovery side circulation circuit. The liquid temperature stabilizes.
Further, since the coolant target temperature is corrected in accordance with the deviation between the detected temperature of the consumption side temperature detection means and the intended use target temperature, the actual consumption side temperature is also reflected in the movement of the consumption side liquid control means. Therefore, the consumption side temperature approaches the target temperature.

請求項３に記載の発明は、電気エネルギーと熱エネルギーとを同時に発生させる発電部と、前記発電部に冷却液を循環させて発電部の熱エネルギーを回収する排熱回収側循環回路と、排熱回収側循環回路を流れる冷却液の温度を検知する冷却液温度検知手段を備えた熱源部に接続され、発電部で発生した熱エネルギーを貯留及び／又は消費する排熱利用装置において、液体を循環及び／又は通過させて熱エネルギーを消費及び／又は貯留する熱消費側回路と、排熱回収側循環回路及び熱消費側回路の一部を構成し排熱回収側循環回路から熱消費側回路に熱エネルギーを移動させる排熱・消費熱交換器と、排熱・消費熱交換器の下流側にあって熱消費側回路を流れる液体の温度を検知する消費側温度検知手段と、排熱・消費熱交換器の熱消費側回路側に流入する液体の温度及び／又は流量を増減することができる消費側液制御手段とを備え、前記冷却液温度検知手段の検知温度と消費側温度検知手段の検知温度の双方に基づいて消費側液制御手段を制御し、排熱回収側循環回路を流れる冷却液の目標温度を冷却液目標温度とし、熱消費側回路は、湯水を貯留する貯留タンクを有していて熱エネルギーを貯留する機能を備え、排熱・消費熱交換器と貯留タンクの双方を含む貯湯循環回路があり、排熱・消費熱交換器には貯留タンクの下部側から湯水が供給され、排熱・消費熱交換器から吐出される湯水は貯留タンクの上部から注入され、貯留タンクをバイパスするバイパス流路を有し、前記消費側液制御手段は、排熱回収側循環回路を流れる冷却液の温度が冷却液目標温度よりも高い場合には、バイパス流路から排熱・消費熱交換器に導入される湯水の量を減らし、貯留タンクの下部から排熱・消費熱交換器に導入される湯水の量を増加させる様に動作することを特徴とする排熱利用装置である。 According to a third aspect of the present invention, there is provided a power generation unit that simultaneously generates electric energy and thermal energy, an exhaust heat recovery side circulation circuit that recovers thermal energy of the power generation unit by circulating a coolant through the power generation unit, In the exhaust heat utilization device that stores and / or consumes the thermal energy generated in the power generation unit, connected to a heat source unit that includes a coolant temperature detection means that detects the temperature of the coolant flowing through the heat recovery side circulation circuit. A heat consumption side circuit that consumes and / or stores heat energy by circulating and / or passing, and a part of the exhaust heat recovery side circulation circuit and the heat consumption side circuit, from the exhaust heat recovery side circulation circuit to the heat consumption side circuit A waste heat / consumption heat exchanger that transfers heat energy to the waste heat, a consumption side temperature detection means that detects the temperature of the liquid that is downstream of the waste heat / consumption heat exchanger and flows through the heat consumption side circuit, Heat consumption side of the heat exchanger Consumption-side liquid control means capable of increasing or decreasing the temperature and / or flow rate of the liquid flowing into the road side, and consumed based on both the detected temperature of the cooling liquid temperature detection means and the detected temperature of the consumption-side temperature detection means The side liquid control means is controlled to set the target temperature of the coolant flowing through the exhaust heat recovery side circulation circuit as the coolant target temperature, and the heat consumption side circuit has a storage tank for storing hot water and stores thermal energy. There is a hot water circulation circuit that has both functions and includes both a waste heat / consumption heat exchanger and a storage tank. Hot water is supplied to the waste heat / consumption heat exchanger from the lower side of the storage tank to exchange waste heat / consumption heat. Hot water discharged from the container is injected from the upper part of the storage tank, and has a bypass flow path that bypasses the storage tank. The consumption side liquid control means is configured such that the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit is When the temperature is higher than the target temperature To reduce the hot water amount introduced into the exhaust heat-dissipation heat exchanger from the bypass flow path operated as to increase the hot water in the amount to be introduced into the exhaust heat-dissipation heat exchanger from the bottom of the storage tank This is a waste heat utilization device.

本発明の排熱利用装置でも、冷却液温度検知手段の検知温度を考慮して消費側液制御手段を制御するので、排熱回収側循環回路の排熱・消費熱交換器から吐出される液体の温度が安定する。
また本発明の排熱利用装置でも、消費側温度検知手段の検知温度を考慮して消費側液制御手段を制御するので、熱消費側回路の排熱・消費熱交換器から吐出される液体の温度は所望の目標温度に近いものとなる。 Also in the exhaust heat utilization apparatus of the present invention, since the consumption side liquid control means is controlled in consideration of the temperature detected by the coolant temperature detection means, the liquid discharged from the exhaust heat / consumption heat exchanger of the exhaust heat recovery side circulation circuit The temperature is stabilized.
In the exhaust heat utilization apparatus of the present invention, the consumption side liquid control means is controlled in consideration of the temperature detected by the consumption side temperature detection means, so that the liquid discharged from the exhaust heat / consumption heat exchanger of the heat consumption side circuit is controlled. The temperature is close to the desired target temperature.

請求項４に記載の発明は、電気エネルギーと熱エネルギーとを同時に発生させる発電部と、前記発電部に冷却液を循環させて発電部の熱エネルギーを回収する排熱回収側循環回路と、液体を循環及び／又は通過させて熱エネルギーを貯留及び／又は消費する熱消費側回路と、排熱回収側循環回路及び熱消費側回路の一部を構成し排熱回収側循環回路から熱消費側回路に熱エネルギーを移動させる排熱・消費熱交換器とを備え、熱消費側回路は、湯水を貯留する貯留タンクを有していて熱エネルギーを貯留する機能を備え、排熱・消費熱交換器と貯留タンクの双方を含む貯湯循環回路があり、排熱・消費熱交換器には貯留タンクの下部側から湯水が供給され、排熱・消費熱交換器から吐出される湯水は貯留タンクの上部から注入され、貯留タンクをバイパスするバイパス流路を有したコージェネレーションシステムを制御するコージェネレーションシステムの制御方法において、排熱回収側循環回路を流れる冷却液の温度と、排熱・消費熱交換器の下流側にあって熱消費側回路を流れる液体の温度の双方に基づいて排熱・消費熱交換器の熱消費側回路側に流入する液体の温度及び／又は流量を増減し、排熱回収側循環回路を流れる冷却液の目標温度を冷却液目標温度とし、排熱回収側循環回路を流れる冷却液の温度が冷却液目標温度よりも高い場合には、バイパス流路から排熱・消費熱交換器に導入される湯水の量を減らし、貯留タンクの下部から排熱・消費熱交換器に導入される湯水の量を増加させる様に動作させることを特徴とするコージェネレーションシステムの制御方法である。 According to a fourth aspect of the present invention, there is provided a power generation unit that simultaneously generates electric energy and thermal energy, a waste heat recovery side circulation circuit that recovers thermal energy of the power generation unit by circulating a coolant through the power generation unit, and a liquid A heat consumption side circuit for storing and / or consuming heat energy by circulating and / or passing the heat, and a part of the exhaust heat recovery side circulation circuit and the heat consumption side circuit, from the exhaust heat recovery side circulation circuit to the heat consumption side It is equipped with a waste heat / consumption heat exchanger that moves thermal energy to the circuit, and the heat consumption side circuit has a storage tank that stores hot water and has a function of storing heat energy, and waste heat / consumption heat exchange There is a hot water circulation circuit that includes both a storage tank and a storage tank. Hot water is supplied to the exhaust heat / consumption heat exchanger from the lower side of the storage tank, and hot water discharged from the exhaust heat / consumption heat exchanger is stored in the storage tank. Infused from above, storage tank A method for controlling a cogeneration system for controlling a cogeneration system having a bypass passage which bypasses a a temperature of the cooling liquid flowing through the exhaust heat recovery side circulation circuit, on the downstream side of the exhaust heat-dissipation heat exchanger Based on both the temperature of the liquid flowing through the heat consumption side circuit, the temperature and / or flow rate of the liquid flowing into the heat consumption side circuit side of the exhaust heat / consumption heat exchanger is increased or decreased to flow through the exhaust heat recovery side circulation circuit. When the coolant target temperature is the coolant target temperature and the coolant temperature flowing through the exhaust heat recovery side circulation circuit is higher than the coolant target temperature, the coolant is introduced into the waste heat / heat consumption heat exchanger from the bypass channel. that reduces the hot water amount, the control method der cogeneration system characterized by operating so as to increase the hot water in the amount to be introduced into the exhaust heat-dissipation heat exchanger from the bottom of the storage tank .

本発明のコージェネレーションシステムの制御方法では、排熱回収側循環回路を流れる冷却液の温度と、排熱・消費熱交換器の下流側にあって熱消費側回路を流れる液体の温度の双方に基づいて排熱・消費熱交換器の熱消費側回路側に流入する液体の温度や流量を増減するので、排熱回収側循環回路及び熱消費側回路の双方における排熱・消費熱交換器から吐出される液体の温度が安定し、且つ所望の目標温度に近いものとなる。   In the control method of the cogeneration system of the present invention, both the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit and the temperature of the liquid flowing downstream of the exhaust heat / consumption heat exchanger and flowing through the heat consumption side circuit are used. Since the temperature and flow rate of the liquid flowing into the heat consumption side circuit side of the exhaust heat / consumption heat exchanger are increased or decreased based on the exhaust heat / consumption heat exchanger in both the exhaust heat recovery side circulation circuit and the heat consumption side circuit The temperature of the discharged liquid is stable and close to the desired target temperature.

また同様の発想に基づいて完成された請求項５に記載の発明は、圧縮手段、凝縮手段、膨張手段及び蒸発手段が環状に接続され相変化する冷媒液を循環させて熱エネルギーを発生させるヒートポンプ回路と、液体を循環及び／又は通過させて熱エネルギーを貯留及び／又は消費する熱消費側回路と、前記ヒートポンプ回路の凝縮手段及び熱消費側回路の一部を構成しヒートポンプ回路から熱消費側回路に熱エネルギーを移動させる凝縮・消費熱交換器とを備えたヒートポンプ式給湯装置において、ヒートポンプ回路の凝縮・消費熱交換器を流れる冷媒液の温度を検知する冷媒液温度検知手段と、凝縮・消費熱交換器の下流側であって熱消費側回路を流れる液体の温度を検知する消費側温度検知手段と、凝縮・消費熱交換器の熱消費側回路側に流入する液体の温度及び／又は流量を増減することができる消費側液制御手段とを備え、冷媒液の目標温度を冷媒液目標温度とし、熱消費側回路であって凝縮・消費熱交換器の下流側を流れる液体の目標温度を使用用途目標温度とし、消費側液制御手段は冷媒液温度検知手段の検知温度が冷媒液目標温度に一致する様に制御され、熱消費側回路は、湯水を貯留する貯留タンクを有していて熱エネルギーを貯留する機能を備え、排熱・消費熱交換器と貯留タンクの双方を含む貯湯循環回路があり、排熱・消費熱交換器には貯留タンクの下部側から湯水が供給され、排熱・消費熱交換器から吐出される湯水は貯留タンクの上部から注入され、貯留タンクをバイパスするバイパス流路を有し、前記消費側液制御手段は、排熱回収側循環回路を流れる冷媒液の温度が冷媒液目標温度よりも高い場合には、バイパス流路から排熱・消費熱交換器に導入される湯水の量を減らし、貯留タンクの下部から凝縮・消費熱交換器に導入される湯水の量を増加させる様に動作することを特徴とするヒートポンプ式給湯装置である。 Further, the invention according to claim 5 completed based on the same idea is a heat pump for generating heat energy by circulating a refrigerant liquid whose phase changes by connecting a compression means, a condensation means, an expansion means and an evaporation means in an annular shape. A circuit, a heat consuming side circuit for circulating and / or passing liquid to store and / or consume heat energy, and a part of the heat pump circuit condensing means and the heat consuming side circuit, from the heat pump circuit to the heat consuming side In a heat pump type hot water supply apparatus provided with a condensation / consumption heat exchanger for transferring thermal energy to the circuit, refrigerant liquid temperature detection means for detecting the temperature of the refrigerant liquid flowing through the condensation / consumption heat exchanger of the heat pump circuit, On the downstream side of the consumption heat exchanger, on the consumption side temperature detection means for detecting the temperature of the liquid flowing in the heat consumption side circuit, on the heat consumption side circuit side of the condensation / consumption heat exchanger Consumption side liquid control means capable of increasing or decreasing the temperature and / or flow rate of the liquid to be entered, and the target temperature of the refrigerant liquid is set as the refrigerant liquid target temperature. The target temperature of the liquid flowing downstream is used as the target temperature for use, the consumption side liquid control means is controlled so that the detection temperature of the refrigerant liquid temperature detection means matches the refrigerant liquid target temperature, and the heat consumption side circuit It has a storage tank that stores heat energy, and has a hot water circulation circuit that includes both a waste heat / consumption heat exchanger and a storage tank. The waste heat / consumption heat exchanger has a storage tank Hot water is supplied from the lower side, and hot water discharged from the exhaust heat / consumption heat exchanger is injected from the upper part of the storage tank, and has a bypass flow path that bypasses the storage tank. Flow through heat recovery side circulation circuit When the temperature of the liquid medium is higher than the target coolant temperature, the amount of hot water introduced into the exhaust heat / consumption heat exchanger from the bypass channel is reduced and introduced into the condensation / consumption heat exchanger from the bottom of the storage tank. It is a heat pump type hot water supply device that operates so as to increase the amount of hot water .

本発明のヒートポンプ式給湯装置では、消費側液制御手段は冷媒液温度検知手段の検知温度が冷媒液目標温度に一致する様に制御されるから、ヒートポンプ回路の凝縮・消費熱交換器から吐出される液体の温度が安定する。
また消費側温度検知手段の検知温度と使用用途目標温度との偏差に応じて前記冷媒液目標温度が補正されるので、実際の消費側温度も消費側液制御手段の動きに反映される。そのため消費側温度が目標温度に近づく。 In the heat pump type hot water supply apparatus of the present invention, the consumption side liquid control means is controlled so that the detected temperature of the refrigerant liquid temperature detecting means coincides with the refrigerant liquid target temperature, so that it is discharged from the condensation / consumption heat exchanger of the heat pump circuit. The liquid temperature is stable.
In addition, since the refrigerant liquid target temperature is corrected according to the deviation between the detected temperature of the consumption side temperature detection means and the intended use target temperature, the actual consumption side temperature is also reflected in the movement of the consumption side liquid control means. Therefore, the consumption side temperature approaches the target temperature.

本発明のコージェネレーションシステム、排熱利用装置及びコージェネレーションシステムの制御方法によると、熱消費側回路の液体の温度が安定し、且つ消費側の液体の温度が所定の使用用途目標温度に近いものとなる。
また本発明のヒートポンプ式給湯装置では、冷媒液の温度が安定し、且つ消費側の液体の温度も所定の使用用途目標温度に近いものとなる。 According to the cogeneration system, the exhaust heat utilization apparatus, and the cogeneration system control method of the present invention, the temperature of the liquid in the heat consumption side circuit is stable, and the temperature of the liquid on the consumption side is close to a predetermined target temperature for use. It becomes.
In the heat pump type hot water supply apparatus of the present invention, the temperature of the refrigerant liquid is stable, and the temperature of the liquid on the consumption side is close to a predetermined target temperature for use.

本発明の実施形態のコージェネレーションシステム及び試作したコージェネレーションシステムの作動原理図である。It is an operation | movement principle figure of the cogeneration system of embodiment of this invention, and the prototype cogeneration system. 本発明の他の実施形態のコージェネレーションシステムの作動原理図である。It is an operation | movement principle figure of the cogeneration system of other embodiment of this invention. 図２の実施形態の作動原理図であって、加熱循環回路を示す。FIG. 3 is an operation principle diagram of the embodiment of FIG. 2 and shows a heating circulation circuit. 図２の実施形態の作動原理図であって、貯湯循環回路を示す。FIG. 3 is an operation principle diagram of the embodiment of FIG. 2 and shows a hot water storage circulation circuit. 図２の実施形態の作動原理図であって、バイパス路を示す。It is an operation principle figure of embodiment of Drawing 2, and shows a bypass way. 図２の実施形態の作動原理図であって、給湯回路を示す。It is an operation principle figure of embodiment of Drawing 2, and shows a hot-water supply circuit. 図２の実施形態の作動原理図であって、貯湯運転時における湯水及び冷却液の流れを示す。It is an operation principle figure of the embodiment of Drawing 2, and shows the flow of hot water and a cooling fluid at the time of hot water storage operation. 図２の実施形態の作動原理図であって、給湯運転時における湯水及び冷却液の流れを示す。FIG. 3 is an operation principle diagram of the embodiment of FIG. 2 and shows the flow of hot water and coolant during a hot water supply operation. 図２の実施形態の作動原理図であって、熱源部の運転中に給湯運転が実行された場合の湯水及び冷却液の流れを示す。FIG. 3 is an operation principle diagram of the embodiment of FIG. 2 and shows the flow of hot water and coolant when a hot water supply operation is performed during operation of the heat source unit. 図２の実施形態の作動原理図であって、熱源部の運転中に暖房運転が実行された場合の湯水及び冷却液の流れを示す。FIG. 3 is an operation principle diagram of the embodiment of FIG. 2 and shows the flow of hot water and coolant when a heating operation is performed during operation of the heat source unit. 図２の実施形態の作動原理図であって、熱源部の運転中に追い焚き運転が実行された場合の湯水及び冷却液の流れを示す。FIG. 3 is an operation principle diagram of the embodiment of FIG. 2 and shows the flow of hot water and coolant when a reheating operation is performed during operation of the heat source unit. 本発明の実施形態のヒートポンプ式給湯装置の作動原理図である。It is an operation principle figure of the heat pump type hot-water supply apparatus of the embodiment of the present invention. 本発明の他の実施形態のヒートポンプ式給湯装置の作動原理図である。It is an operation | movement principle figure of the heat pump type hot-water supply apparatus of other embodiment of this invention.

以下さらに本発明の実施形態について説明する。
本実施形態のコージェネレーションシステム１００の機械的構成は、先に試作したコージェネレーションシステム２００と同一であり、作動原理図は共通である。
即ちコージェネレーションシステム１００は、熱源ユニット１０１と貯湯ユニット１０２によって構成されている。
熱源ユニット１０１は、ガスエンジン１０５で駆動される発電機１０６を搭載している。また熱源ユニット１０１には、ガスエンジン１０５に冷却液を循環させて熱エネルギーを回収する排熱回収側循環回路１０７がある。 Embodiments of the present invention will be further described below.
The mechanical configuration of the cogeneration system 100 of the present embodiment is the same as that of the cogeneration system 200 previously prototyped, and the operation principle diagram is common.
That is, the cogeneration system 100 includes a heat source unit 101 and a hot water storage unit 102.
The heat source unit 101 is equipped with a generator 106 driven by a gas engine 105. The heat source unit 101 includes an exhaust heat recovery side circulation circuit 107 that circulates a coolant through the gas engine 105 and recovers thermal energy.

排熱回収側循環回路１０７内には冷却液があり、当該冷却液は、循環ポンプ１１１からガスエンジン１０５に入り、さらに排熱・消費熱交換器１１２の一次側流路を通過して膨張タンク１１０に入り、循環ポンプ１１１に戻る。また排熱回収側循環回路１０７の排熱・消費熱交換器１１２の吐出側とガスエンジン１０５の導入側との間には冷却液用温度センサー１０８が設けられ、ガスエンジン１０５に導入される冷却液の温度が監視されている。同時に排熱・消費熱交換器１１２を通過して熱を奪われた後の冷却液の温度が監視されているとも言える。   There is a coolant in the exhaust heat recovery side circulation circuit 107, and the coolant enters the gas engine 105 from the circulation pump 111, and further passes through the primary side flow path of the exhaust heat / consumed heat exchanger 112 to expand the expansion tank. 110 enters and returns to the circulation pump 111. Further, a coolant temperature sensor 108 is provided between the discharge side of the exhaust heat / consumption heat exchanger 112 of the exhaust heat recovery side circulation circuit 107 and the introduction side of the gas engine 105, and the cooling introduced into the gas engine 105. The liquid temperature is monitored. At the same time, it can be said that the temperature of the coolant after being deprived of heat through the exhaust heat / consumed heat exchanger 112 is monitored.

一方、貯湯ユニット１０２には貯留タンク１２０と、循環ポンプ１２１と、排熱・消費熱交換器１１２が内蔵されている。貯留タンク１２０を含む貯湯循環回路１２２内には湯水が満たされている。そして循環ポンプ１２１が起動すると、貯留タンク１２０の底側から循環ポンプ１２１に冷水が導入され、排熱・消費熱交換器１１２の二次側流路を経由して加熱された湯水が貯留タンク１２０の上部から注入される。排熱・消費熱交換器１１２の二次側流路の吐出側と、貯留タンク１２０の上部との間には、加熱水用温度センサー１１３が設けられており、排熱・消費熱交換器１１２から吐出される湯水の温度を監視している。   On the other hand, the hot water storage unit 102 includes a storage tank 120, a circulation pump 121, and a waste heat / consumed heat exchanger 112. The hot water circulation circuit 122 including the storage tank 120 is filled with hot water. When the circulation pump 121 is activated, cold water is introduced into the circulation pump 121 from the bottom side of the storage tank 120, and hot water heated through the secondary side flow path of the exhaust heat / consumption heat exchanger 112 is stored in the storage tank 120. It is injected from the top. A heating water temperature sensor 113 is provided between the discharge side of the secondary side flow path of the exhaust heat / consumption heat exchanger 112 and the upper portion of the storage tank 120, and the exhaust heat / consumption heat exchanger 112. The temperature of hot water discharged from the water is monitored.

またコージェネレーションシステム１００では、貯留タンク１２０を迂回するバイパス流路１２５が形成されている。そしてバイパス流路１２５と循環ポンプ１２１の上流側との間には、混合弁（消費側液制御手段）１２６が介在されている。   In the cogeneration system 100, a bypass channel 125 that bypasses the storage tank 120 is formed. A mixing valve (consumption side liquid control means) 126 is interposed between the bypass flow path 125 and the upstream side of the circulation pump 121.

そして本実施形態のコージェネレーションシステム１００では、排熱・消費熱交換器１１２の一次側から吐出された冷却水の温度と、排熱・消費熱交換器１１２の二次側から吐出された湯水の温度の双方に基づいて混合弁１２６が制御される。
より具体的には、排熱・消費熱交換器１１２の一次側の下流側に設けられた冷却液用温度センサー（冷却液温度検知手段）１０８の検知温度と、排熱・消費熱交換器１１２の二次側の下流側に設けられた加熱水用温度センサー（消費側温度検知手段）１１３の検知温度に基づいて混合弁１２６が制御される。 In the cogeneration system 100 according to the present embodiment, the temperature of the cooling water discharged from the primary side of the exhaust heat / consumption heat exchanger 112 and the hot water discharged from the secondary side of the exhaust heat / consumption heat exchanger 112. The mixing valve 126 is controlled based on both the temperatures.
More specifically, the temperature detected by the coolant temperature sensor (coolant temperature detection means) 108 provided downstream of the primary side of the exhaust heat / consumption heat exchanger 112 and the exhaust heat / consumption heat exchanger 112. The mixing valve 126 is controlled based on the temperature detected by the heating water temperature sensor (consumption side temperature detecting means) 113 provided downstream of the secondary side.

ここで二つの温度センサー１０８，１１３の混合弁１２６の制御に対する寄与は、対等ではなく、冷却液の温度を検知する熱源ユニット１０１側の冷却液用温度センサー１０８が主体となって混合弁１２６が制御され、補助的に貯湯ユニット１０２側の加熱水用温度センサー（消費側温度検知手段）１１３の検知温度が使用される。   Here, the contribution of the two temperature sensors 108 and 113 to the control of the mixing valve 126 is not equal, but the cooling valve temperature sensor 108 on the heat source unit 101 side that detects the temperature of the cooling liquid is the main component of the mixing valve 126. The detected temperature of the heated water temperature sensor (consumption side temperature detecting means) 113 on the hot water storage unit 102 side is used in an auxiliary manner.

より具体的には、冷却液用温度センサー１０８の検知温度が所定の冷却液目標温度に一致する様に、混合弁１２６の開度がフィードバック制御される。
即ち冷却液用温度センサー１０８の検知温度が冷却液目標温度よりも高い場合には、混合弁１２６のバイパス流路１２５側の開度が閉鎖方向に動作し、貯留タンク１２０の底側と繋がる側の開度が開く方向に動作する。
その結果、排熱・消費熱交換器１１２の二次側に供給される湯水の温度が低下し、一次側を流れる冷却液との温度差が増大して一次側の冷却液から、より多くの熱を奪う。その結果一次側を流れる冷却液の温度が低下し、冷却液目標温度に近づく。 More specifically, the opening degree of the mixing valve 126 is feedback-controlled so that the temperature detected by the coolant temperature sensor 108 matches a predetermined coolant target temperature.
That is, when the detected temperature of the coolant temperature sensor 108 is higher than the coolant target temperature, the opening of the mixing valve 126 on the bypass flow path 125 side operates in the closing direction and is connected to the bottom side of the storage tank 120. It operates in the direction of opening of the opening.
As a result, the temperature of the hot water supplied to the secondary side of the exhaust heat / consumed heat exchanger 112 decreases, the temperature difference with the coolant flowing through the primary side increases, and more from the coolant on the primary side. Take away heat. As a result, the temperature of the coolant flowing on the primary side decreases and approaches the coolant target temperature.

逆に冷却液用温度センサー１０８の検知温度が冷却液目標温度よりも低い場合には、混合弁１２６のバイパス流路１２５側の開度が開く方向に動作し、貯留タンク１２０の底側と繋がる側の開度が閉鎖方向に動作する。
その結果、排熱・消費熱交換器１１２の二次側に供給される湯水の温度が上昇し、一次側を流れる冷却液との温度差が減少して一次側の冷却液から奪う熱量が減少する。その結果一次側を流れる冷却液の温度が上昇し、冷却液目標温度に近づく。 On the contrary, when the temperature detected by the coolant temperature sensor 108 is lower than the coolant target temperature, the opening of the mixing valve 126 on the bypass flow path 125 side is opened and connected to the bottom side of the storage tank 120. The opening on the side operates in the closing direction.
As a result, the temperature of hot water supplied to the secondary side of the exhaust heat / consumed heat exchanger 112 rises, the temperature difference with the coolant flowing through the primary side decreases, and the amount of heat taken from the primary side coolant decreases. To do. As a result, the temperature of the coolant flowing on the primary side rises and approaches the coolant target temperature.

また前記した様に本実施形態では、補助的に貯湯ユニット１０２側の加熱水用温度センサー（消費側温度検知手段）１１３の検知温度が参酌される。
即ち貯湯ユニット１０２側の加熱水用温度センサー（消費側温度検知手段）１１３の検知温度が貯湯目標温度（使用用途目標温度）から外れた場合には、冷却液目標温度を変更することとした。
具体的に説明すると、加熱水用温度センサー（消費側温度検知手段）１１３の検知温度が貯湯目標温度（使用用途目標温度）よりも高い場合には、冷却液目標温度を下げる。
その結果、冷却液用温度センサー１０８の現在の検知温度が補正後の冷却液目標温度よりも高い状態となり、混合弁１２６のバイパス流路１２５側の開度が閉鎖方向に動作し、貯留タンク１２０の底側と繋がる側の開度が開く方向に動作する。
その結果、排熱・消費熱交換器１１２の二次側に供給される湯水の温度が低下し、一次側を流れる冷却液との温度差が増大して一次側の冷却液からより多くの熱を奪う。その結果一次側を流れる冷却液の温度が低下し、冷却液目標温度に近づく。
また排熱・消費熱交換器１１２の二次側に供給される湯水の温度が低下するので、排熱・消費熱交換器１１２の二次側から吐出される湯水の温度も低下し、その後の排熱・消費熱交換器１１２の二次側から吐出される湯水の温度が貯湯目標温度に近づく。 In addition, as described above, in the present embodiment, the temperature detected by the heating water temperature sensor (consumption side temperature detecting means) 113 on the hot water storage unit 102 side is taken into consideration.
That is, when the temperature detected by the heating water temperature sensor (consumption side temperature detection means) 113 on the hot water storage unit 102 side deviates from the hot water storage target temperature (use target temperature), the coolant target temperature is changed.
More specifically, when the temperature detected by the heating water temperature sensor (consumption side temperature detection means) 113 is higher than the hot water storage target temperature (use target temperature), the coolant target temperature is lowered.
As a result, the current detected temperature of the coolant temperature sensor 108 is higher than the corrected coolant target temperature, the opening of the mixing valve 126 on the bypass flow path 125 side operates in the closing direction, and the storage tank 120 The opening on the side connected to the bottom side of the door moves in the direction of opening.
As a result, the temperature of the hot water supplied to the secondary side of the exhaust heat / consumed heat exchanger 112 decreases, the temperature difference with the coolant flowing through the primary side increases, and more heat is generated from the coolant on the primary side. Take away. As a result, the temperature of the coolant flowing on the primary side decreases and approaches the coolant target temperature.
Moreover, since the temperature of the hot water supplied to the secondary side of the exhaust heat / consumed heat exchanger 112 is lowered, the temperature of the hot water discharged from the secondary side of the exhaust heat / consumed heat exchanger 112 is also lowered. The temperature of the hot water discharged from the secondary side of the exhaust heat / consumed heat exchanger 112 approaches the hot water storage target temperature.

逆に加熱水用温度センサー１１３の検知温度が貯湯目標温度よりも低い場合には、冷却液目標温度を上げる。
その結果、冷却液用温度センサー１０８の現在の検知温度が補正後の冷却液目標温度よりも低い状態となり、混合弁１２６のバイパス流路１２５側の開度が開く方向に動作し、貯留タンク１２０の底側と繋がる側の開度が閉じる方向に動作する。
その結果、排熱・消費熱交換器１１２の二次側に供給される湯水の温度が上昇し、一次側を流れる冷却液との温度差が減少して一次側の冷却液から奪う熱量が減少する。その結果一次側を流れる冷却液の温度が上昇し、冷却液目標温度に近づく。
また排熱・消費熱交換器１１２の二次側に供給される湯水の温度が上昇するので、排熱・消費熱交換器１１２の二次側から吐出される湯水の温度も上昇し、その後の排熱・消費熱交換器１１２の二次側から吐出される湯水の温度が貯湯目標温度に近づく。 Conversely, when the temperature detected by the heating water temperature sensor 113 is lower than the hot water storage target temperature, the coolant target temperature is raised.
As a result, the current detected temperature of the coolant temperature sensor 108 is lower than the corrected coolant target temperature, the opening of the mixing valve 126 on the bypass flow path 125 side is opened, and the storage tank 120 is operated. The opening on the side connected to the bottom side of the lens moves in the closing direction.
As a result, the temperature of hot water supplied to the secondary side of the exhaust heat / consumed heat exchanger 112 rises, the temperature difference with the coolant flowing through the primary side decreases, and the amount of heat taken from the primary side coolant decreases. To do. As a result, the temperature of the coolant flowing on the primary side rises and approaches the coolant target temperature.
Moreover, since the temperature of the hot water supplied to the secondary side of the exhaust heat / consumption heat exchanger 112 increases, the temperature of the hot water discharged from the secondary side of the exhaust heat / consumption heat exchanger 112 also increases, The temperature of the hot water discharged from the secondary side of the exhaust heat / consumed heat exchanger 112 approaches the hot water storage target temperature.

ただし、ガスエンジン１０５に供給する冷却液の温度には許容範囲があり、加熱水用温度センサー１１３の検知温度が貯湯目標温度よりいくら離れていたとしても許容範囲を越えて冷却液目標温度を補正することは制限されている。
即ちガスエンジン１０５に供給する冷却液の温度が過度に高い場合にはガスエンジン１０５内で冷却液が沸騰する懸念がありガスエンジン１０５がオーバーヒートしてしまう。一方、ガスエンジン１０５に供給する冷却液の温度が低くても、致命的な問題は生じないが、過度に低いとガスエンジン１０５の回転が円滑性を欠き、燃焼効率が低下する。 However, the temperature of the coolant supplied to the gas engine 105 has an allowable range, and the coolant target temperature is corrected beyond the allowable range even if the detected temperature of the heating water temperature sensor 113 is far from the hot water storage target temperature. To be restricted.
That is, when the temperature of the coolant supplied to the gas engine 105 is excessively high, there is a concern that the coolant will boil in the gas engine 105 and the gas engine 105 will overheat. On the other hand, even if the temperature of the coolant supplied to the gas engine 105 is low, a fatal problem does not occur. However, if the temperature is too low, the rotation of the gas engine 105 lacks smoothness and combustion efficiency decreases.

一般的にガスエンジン１０５に供給する冷却液の温度の上限は摂氏８０度程度である。ガスエンジン１０５に供給する冷却液の温度の下限は、厳密なものではないが、摂氏５０度程度に設定することが推奨される。
即ち冷却液目標温度は次の式の範囲である。 Generally, the upper limit of the temperature of the coolant supplied to the gas engine 105 is about 80 degrees Celsius. The lower limit of the temperature of the coolant supplied to the gas engine 105 is not strict, but it is recommended to set it to about 50 degrees Celsius.
That is, the coolant target temperature is in the range of the following equation.

Figure 0005828219
Figure 0005828219

本実施形態では、予め冷却液目標温度の初期値が定められている。冷却液目標温度の初期値は、貯湯目標温度よりも低い温度である。
即ち排熱・消費熱交換器１１２の一次側には冷却液が流れ、二次側を流れる湯水と熱交換される。排熱・消費熱交換器１１２の一次側の入口では冷却液の温度が高く、出口側は低いものとなる。逆に排熱・消費熱交換器１１２の二次側の入口では湯水の温度が低く、湯水はしだいに昇温して吐出口では高いものとなる。
そのため排熱・消費熱交換器１１２の吐出側で比較すると、二次側の湯水の温度が一次側の冷却液の温度よりも高くなっている。
両者の差は、導入される湯水と冷却液との温度差、及び排熱・消費熱交換器１１２の変換効率に依存するが、概ね摂氏３度〜摂氏１２度程度である。
従って冷却液目標温度の初期値は、貯湯目標温度から摂氏３度〜摂氏１２度を引いた値であり、次式で表される。 In this embodiment, the initial value of the coolant target temperature is determined in advance. The initial value of the coolant target temperature is a temperature lower than the hot water storage target temperature.
That is, the coolant flows on the primary side of the exhaust heat / consumed heat exchanger 112 and exchanges heat with hot water flowing on the secondary side. The temperature of the coolant is high at the primary inlet of the exhaust heat / consumed heat exchanger 112, and the outlet is low. Conversely, the temperature of the hot water at the secondary inlet of the exhaust heat / consumed heat exchanger 112 is low, and the temperature of the hot water gradually increases and becomes high at the discharge port.
Therefore, when compared on the discharge side of the exhaust heat / consumed heat exchanger 112, the temperature of the hot water on the secondary side is higher than the temperature of the coolant on the primary side.
The difference between the two depends on the temperature difference between the hot water and the coolant to be introduced and the conversion efficiency of the exhaust heat / consumed heat exchanger 112, but is generally about 3 degrees Celsius to 12 degrees Celsius.
Therefore, the initial value of the coolant target temperature is a value obtained by subtracting 3 degrees Celsius to 12 degrees Celsius from the hot water storage target temperature, and is expressed by the following equation.

Figure 0005828219
Figure 0005828219

また冷却液目標温度の補正量は、加熱水用温度センサー１１３の検知温度と貯湯目標温度との偏差に応じて増減される。
ただし、動作を安定化させる目的から、両者の偏差が一定量以下である場合には、補正を行わない。例えば両者の偏差が摂氏１度以下である場合には、偏差を反映させない。より推奨される範囲は、両者の偏差が摂氏０．８度以下である場合には、偏差を反映させない。 The correction amount of the coolant target temperature is increased or decreased according to the deviation between the temperature detected by the heating water temperature sensor 113 and the target hot water storage temperature.
However, for the purpose of stabilizing the operation, no correction is performed when the deviation between the two is below a certain amount. For example, if the deviation between the two is 1 degree Celsius or less, the deviation is not reflected. The more recommended range does not reflect the deviation if the deviation between them is 0.8 degrees Celsius or less.

補正は、例えば一定時間内の偏差の積算に応じて決定する。例えば次式によって補正値を決める。   The correction is determined according to, for example, integration of deviations within a certain time. For example, the correction value is determined by the following equation.

Figure 0005828219
Figure 0005828219

上記の式に代わって次式を使用してもよい。   The following equation may be used instead of the above equation.

Figure 0005828219
Figure 0005828219

以上、本発明の基本的構成について説明したが、実際に本発明を実施する際には他の構成部材が付加される。以下、周辺機器を含めた本発明の実施形態を説明する。   Although the basic configuration of the present invention has been described above, other components are added when actually implementing the present invention. Hereinafter, embodiments of the present invention including peripheral devices will be described.

図２に示すコージェネレーションシステム１は、具体的には給湯・追い焚き・暖房装置であり、大別して熱源部２と排熱利用装置３とにより構成されるコージェネレーション系Ｓを形成している。熱源部２と排熱利用装置３はいずれもユニット化されている。
熱源部２は、ガスエンジン５を備えたものであり、コージェネレーション系Ｓの外にある電気機器等の外部負荷に電力を供給すると共に、発電に伴い発生した排熱により冷却液を加熱することができる。また、排熱利用装置３は、温水装置６（補助熱源）を備えたものであり、主として給湯栓７や床暖房やファンコンベクタ等の暖房装置８等に供給される湯水を加熱するものである。 The cogeneration system 1 shown in FIG. 2 is specifically a hot water supply / reheating / heating device, and roughly forms a cogeneration system S including a heat source unit 2 and an exhaust heat utilization device 3. The heat source unit 2 and the exhaust heat utilization device 3 are both unitized.
The heat source unit 2 includes a gas engine 5 and supplies power to an external load such as an electric device outside the cogeneration system S and heats the coolant by exhaust heat generated by power generation. Can do. The exhaust heat utilization device 3 is provided with a hot water device 6 (auxiliary heat source), and mainly heats hot water supplied to a hot water tap 7, a heating device 8 such as a floor heater or a fan convector, and the like. .

コージェネレーションシステム１は、熱源部２および排熱利用装置３の駆動を司る制御部を持つ駆動制御装置（いずれも図示せず）を具備している。制御部は、熱源部２および排熱利用装置３に設けられた各センサの検知信号に基づいて弁の開閉を行ったり、循環ポンプ１６，４７やガスエンジン５、温水装置６等の駆動を司るものである。   The cogeneration system 1 includes a drive control device (none of which is shown) having a control unit that controls driving of the heat source unit 2 and the exhaust heat utilization device 3. The control unit opens and closes valves based on detection signals from the sensors provided in the heat source unit 2 and the exhaust heat utilization device 3, and controls the circulation pumps 16, 47, the gas engine 5, the hot water device 6, and the like. Is.

熱源部２は、ガスエンジン５と、ガスエンジン５によって駆動する発電機１０を具備している。熱源部２において発生した電力は、コージェネレーション系Ｓの外部にある電気機器等の外部負荷に供給される。熱源部２は、ガスエンジン５を冷却するための排熱回収側循環回路１２を具備している。   The heat source unit 2 includes a gas engine 5 and a generator 10 driven by the gas engine 5. The electric power generated in the heat source unit 2 is supplied to an external load such as an electric device outside the cogeneration system S. The heat source unit 2 includes an exhaust heat recovery side circulation circuit 12 for cooling the gas engine 5.

排熱回収側循環回路１２は、排熱利用装置３側にある排熱・消費熱交換器３０を経由して湯水を循環させるものである。排熱回収側循環回路１２は、ガスエンジン５から排熱・消費熱交換器３０に向けて湯水を流す往き側冷却水路１３と、排熱・消費熱交換器３０からガスエンジン５側へと湯水を戻す戻り側冷却水路１５とから構成されている。排熱回収側循環回路１２内を流れる冷却液は、戻り側冷却水路１５の中途に設けられた循環ポンプ１６によって圧送される。そして戻り側冷却水路１５内を流れる湯水は、ガスエンジン５の駆動に伴い発生した排熱により加熱され往き側冷却水路１３へと流出する。   The exhaust heat recovery side circulation circuit 12 circulates hot water through the exhaust heat / consumption heat exchanger 30 on the exhaust heat utilization device 3 side. The exhaust heat recovery-side circulation circuit 12 includes a forward-side cooling water channel 13 through which hot water flows from the gas engine 5 toward the exhaust heat / consumption heat exchanger 30, and hot water from the exhaust heat / consumption heat exchanger 30 to the gas engine 5 side. And a return side cooling water channel 15 for returning the air. The coolant flowing in the exhaust heat recovery side circulation circuit 12 is pumped by a circulation pump 16 provided in the middle of the return side cooling water passage 15. Then, the hot water flowing through the return side cooling water passage 15 is heated by the exhaust heat generated when the gas engine 5 is driven, and flows out to the outgoing side cooling water passage 13.

ガスエンジン５の排熱により加熱され、往き側冷却水路１３内を流れる湯水は、排熱・消費熱交換器３０へと流入する。そして排熱・消費熱交換器３０において熱交換を行い低温となった湯水は、戻り側冷却水路１５を介してガスエンジン５へと戻る。   The hot water heated by the exhaust heat of the gas engine 5 and flowing in the outward cooling water channel 13 flows into the exhaust heat / consumed heat exchanger 30. Then, the hot and cold water that has undergone heat exchange in the exhaust heat / consumed heat exchanger 30 and has reached a low temperature returns to the gas engine 5 through the return side cooling water passage 15.

戻り側冷却水路１５の中途には、上記した循環ポンプ１６の他に冷却液タンク（膨張タンク）２２が設けられている。冷却液タンク２２には、外部から湯水を供給するための給水管２７が設けられており、その中途に設けられている補給水弁２８によって冷却水タンク２２への給水量が調整される。
また戻り側冷却水路１５の中途であって、冷却液タンク２２と循環ポンプ１６との間には、冷却液用温度センサー２５が設けられ、ガスエンジン５に導入される冷却液の温度が監視されている。冷却液用温度センサー２５は排熱・消費熱交換器３０で熱を奪われた冷却液の温度を計るものであるとも言える。 A coolant tank (expansion tank) 22 is provided in the middle of the return side cooling water channel 15 in addition to the circulation pump 16 described above. The cooling liquid tank 22 is provided with a water supply pipe 27 for supplying hot water from the outside, and the amount of water supplied to the cooling water tank 22 is adjusted by a replenishing water valve 28 provided in the middle thereof.
Further, a coolant temperature sensor 25 is provided in the middle of the return side cooling water passage 15 and between the coolant tank 22 and the circulation pump 16 to monitor the temperature of the coolant introduced into the gas engine 5. ing. It can be said that the coolant temperature sensor 25 measures the temperature of the coolant deprived of heat by the exhaust heat / consumed heat exchanger 30.

排熱利用装置３は、燃料ガスを燃焼し湯水を加熱する温水装置６と、排熱回収側循環回路１２内を流れるガスエンジン５の排熱により加熱された湯水と熱交換を行う排熱・消費熱交換器３０と、貯留タンク３１とを具備している。排熱利用装置３は、貯湯循環回路４１（図４）と、ガスエンジン５および温水装置６において発生した熱によって加熱された湯水を給湯栓７を介して外部に供給する給湯回路３３（図６）とを備え、これに加えて暖房装置８等の熱負荷に接続される負荷循環回路３５と、湯水を浴槽に供給して循環させる浴槽循環回路３６とを有する。またバイパス流路１１（図５）を備えている。
また、本実施形態のコージェネレーションシステム１は、図３に示される加熱循環回路３２が形成されている。 The exhaust heat utilization device 3 combusts heat with hot water device 6 that burns fuel gas and heats hot water, and hot water heated by the exhaust heat of the gas engine 5 that flows in the exhaust heat recovery side circulation circuit 12. A consumption heat exchanger 30 and a storage tank 31 are provided. The exhaust heat utilization device 3 includes a hot water storage circuit 41 (FIG. 4) and a hot water supply circuit 33 (FIG. 6) that supplies hot water heated by heat generated in the gas engine 5 and the hot water device 6 to the outside through the hot water tap 7. In addition to this, a load circulation circuit 35 connected to a thermal load such as the heating device 8 and a bathtub circulation circuit 36 for supplying hot water to the bathtub for circulation. Further, a bypass channel 11 (FIG. 5) is provided.
In the cogeneration system 1 of the present embodiment, a heating circulation circuit 32 shown in FIG. 3 is formed.

なお温水装置６は、内部に１系統の熱交換器６ａを備えたものであり、バーナ６ｂの熱を受けて内部を通過する湯水を加熱するものである。
本実施形態では、熱源たる温水装置６の熱交換器６ａと、排熱・消費熱交換器３０が直列に接続されている。ただし温水装置６をバイパスする温水装置バイパス路２３があり、三方弁５０によって温水装置６側と温水装置バイパス路２３側が切り換えられる。 The hot water device 6 includes a heat exchanger 6a of one system inside, and heats hot water passing through the inside by receiving heat from the burner 6b.
In this embodiment, the heat exchanger 6a of the hot water device 6 as a heat source and the exhaust heat / consumed heat exchanger 30 are connected in series. However, there is a hot water device bypass path 23 that bypasses the hot water device 6, and the three-way valve 50 switches between the hot water device 6 side and the hot water device bypass path 23 side.

加熱循環回路３２は、図３に示すように、排熱・消費熱交換器３０と熱交換部４５を含む循環回路である。
即ち加熱循環回路３２は、排熱・消費熱交換器３０の吐出側を起点とする高温湯往き側流路３８を有し、三方弁５０、温水装置バイパス路２３、熱交換部４５、混合弁（消費側液制御手段）４６、循環ポンプ４７を含んで排熱・消費熱交換器３０に戻る一連の循環回路である。また高温湯往き側流路３８の三方弁５０の手前の位置に加熱水用温度センサー２１が設けられている。
排熱・消費熱交換器３０と温水装置６（実際には三方弁５０）の間に設けられた加熱水用温度センサー２１は、排熱・消費熱交換器３０から吐出された直後の湯水の温度を測定するものである。 As shown in FIG. 3, the heating circulation circuit 32 is a circulation circuit including an exhaust heat / consumption heat exchanger 30 and a heat exchange unit 45.
That is, the heating circulation circuit 32 has a high temperature hot water supply side flow path 38 starting from the discharge side of the exhaust heat / consumption heat exchanger 30, and includes a three-way valve 50, a hot water device bypass path 23, a heat exchange unit 45, a mixing valve. (Consumption side liquid control means) 46 and a series of circulation circuits including a circulation pump 47 and returning to the exhaust heat / consumption heat exchanger 30. A heating water temperature sensor 21 is provided at a position in front of the three-way valve 50 in the high temperature hot water flow path 38.
A heating water temperature sensor 21 provided between the exhaust heat / consumption heat exchanger 30 and the hot water device 6 (actually the three-way valve 50) is a hot water just after being discharged from the exhaust heat / consumption heat exchanger 30. It measures temperature.

また高温湯往き側流路３８は、往き側分岐点６０で熱交換部４５側と給湯回路３３側に分岐され、図６に示す給湯回路３３側と接続されている。給湯往路８３は給湯混合弁８０に繋がる。
またさらに給湯往路８３からは、貯留タンク３１に至る貯留部給湯管８７が分岐されている。より具体的には、往き側分岐点６０から枝分けされた給湯往路８３は、分岐部Ｄ１において、給湯混合弁８０側と、貯留タンク３１に繋がる貯留部給湯管８７とに分岐されている。貯留部給湯管８７が分岐される分岐部Ｄ1 の上流側（温水装置６側）に、高温湯分配制御比例弁８４が設けられている。即ち高温湯分配制御比例弁８４は、給湯往路８３であって往き側分岐点６０と分岐部Ｄ1 の間に設けられている。 Further, the high temperature hot water supply side flow path 38 is branched to the heat exchange section 45 side and the hot water supply circuit 33 side at the forward side branch point 60, and is connected to the hot water supply circuit 33 side shown in FIG. The hot water supply forward path 83 is connected to the hot water supply mixing valve 80.
Further, a storage part hot water supply pipe 87 reaching the storage tank 31 is branched from the hot water supply outward path 83. More specifically, the hot water supply forward path 83 branched from the forward branch point 60 is branched at the branch part D1 into the hot water mixing valve 80 side and the storage part hot water supply pipe 87 connected to the storage tank 31. A high-temperature hot water distribution control proportional valve 84 is provided on the upstream side (hot water device 6 side) of the branch portion D1 where the storage portion hot water supply pipe 87 is branched. That is, the high temperature hot water distribution control proportional valve 84 is provided in the hot water supply forward path 83 between the forward branch point 60 and the branch part D1.

また貯留部給湯管８７はさらに分岐されて貯留タンク３１を迂回するバイパス流路１１が形成されている（図５）。そしてバイパス流路１１の末端は、混合弁４６の一つのポートに接続されている。
即ち混合弁４６は、３個のポートを持ち、その一つは熱交換部４５及び貯留タンク３１の底側に接続され、他の一つはバイパス流路１１の末端に接続され、残る一つが循環ポンプ４７の上流側に接続されている。 Further, the reservoir hot water supply pipe 87 is further branched to form a bypass passage 11 that bypasses the storage tank 31 (FIG. 5). The end of the bypass channel 11 is connected to one port of the mixing valve 46.
That is, the mixing valve 46 has three ports, one of which is connected to the bottom side of the heat exchange unit 45 and the storage tank 31, the other one is connected to the end of the bypass flow path 11, and the remaining one is It is connected to the upstream side of the circulation pump 47.

貯留タンク３１には、内部に貯留されている湯水の高さ方向の温度分布を検知するために、最上部温度センサ３４ａ、上部温度センサ３４ｂ、中部温度センサ３４ｃおよび下部温度センサ３４ｄが設けられている。   The storage tank 31 is provided with a top temperature sensor 34a, an upper temperature sensor 34b, a middle temperature sensor 34c, and a lower temperature sensor 34d in order to detect the temperature distribution in the height direction of hot water stored therein. Yes.

熱交換部４５は、加熱循環回路３２の一部を構成するものであり、熱交換分岐流路９４の先端に設けられており、負荷循環回路３５の中途に設けられた負荷熱交換器４２と、負荷熱交出口電磁弁５２とを有する流路４５ａと、浴槽循環回路３６の中途に設けられた追焚熱交換器４３と追焚熱交出口電磁弁５３とを有する流路４５ｂとが並列に配されたものである。そのため、負荷熱交換器４２および追焚熱交換器４３への湯水の流入は、負荷熱交出口電磁弁５２および追焚熱交出口電磁弁５３によって調整される。   The heat exchanging part 45 constitutes a part of the heating circulation circuit 32, is provided at the tip of the heat exchange branch flow path 94, and is connected to the load heat exchanger 42 provided in the middle of the load circulation circuit 35. The flow path 45 a having the load heat exchange outlet electromagnetic valve 52 and the flow path 45 b having the reheating heat exchanger 43 and the reheating heat exchange outlet electromagnetic valve 53 provided in the middle of the bathtub circulation circuit 36 are arranged in parallel. It has been arranged. Therefore, the inflow of hot water into the load heat exchanger 42 and the additional heat exchanger 43 is adjusted by the load heat exchange outlet electromagnetic valve 52 and the additional heat exchange electromagnetic valve 53.

負荷熱交換器４２に接続されている負荷循環回路３５は、暖房装置８に湯水を供給する回路である。   The load circulation circuit 35 connected to the load heat exchanger 42 is a circuit that supplies hot water to the heating device 8.

追焚熱交換器４３に接続されている浴槽循環回路３６は、浴槽側に繋がる回路である。   The bathtub circulation circuit 36 connected to the memory heat exchanger 43 is a circuit connected to the bathtub side.

給湯回路３３は、具体的には、給湯混合弁８０を介して高温湯往き側流路３８の中途で分岐された給湯往路８３と、外部から湯水を供給する給水管８５とが接続されたものである。給水管８５は、給湯混合弁８０に接続されている。   More specifically, the hot water supply circuit 33 is connected to a hot water supply path 83 branched in the middle of the high temperature hot water supply side flow path 38 via a hot water supply mixing valve 80 and a water supply pipe 85 for supplying hot water from the outside. It is. The water supply pipe 85 is connected to the hot water supply mixing valve 80.

給水管８５の中途には、外部から導入された湯水を貯留タンク３１側に向けて供給する貯留部給水管９１が接続されている。貯留部給水管９１は、貯留タンク３１の底部側に接続されている。
さらに、貯留タンク３１の上部には、給湯往路８３から分岐され、貯留タンク３１への湯水の流出入を行うための貯留部給湯管８７が接続されている。貯留タンク３１には、貯留部給湯管８７を通って貯留タンク３１の外部に流出する湯水と略同量の湯水が貯留部給水管９１を介して給水されるため、貯留タンク３１は常に満水状態に維持される。 A reservoir water supply pipe 91 that supplies hot water introduced from the outside toward the storage tank 31 is connected to the middle of the water supply pipe 85. The storage unit water supply pipe 91 is connected to the bottom side of the storage tank 31.
Furthermore, a reservoir hot water supply pipe 87 that branches from the hot water supply forward path 83 and flows into and out of the storage tank 31 is connected to the upper part of the storage tank 31. Since the storage tank 31 is supplied with approximately the same amount of hot water flowing out of the storage tank 31 through the storage section hot water supply pipe 87 via the storage section water supply pipe 91, the storage tank 31 is always full. Maintained.

続いて、本実施形態のコージェネレーションシステム１における湯水の流れについて説明する。
コージェネレーションシステム１は、多数の運転モードで駆動制御されるものであり、各モード毎に湯水の流れが異なる。
本明細書では、代表的なものに限って説明することとする。
運転モードには、貯留タンク３１に湯水を貯留する排熱貯留運転モードと、給湯栓７から湯水を排出する給湯運転モード、暖房モード及び追い焚きモードがある。 Then, the flow of the hot water in the cogeneration system 1 of this embodiment is demonstrated.
The cogeneration system 1 is driven and controlled in a number of operation modes, and the flow of hot water differs for each mode.
In this specification, only typical ones will be described.
The operation modes include an exhaust heat storage operation mode for storing hot water in the storage tank 31, a hot water supply operation mode for discharging hot water from the hot water tap 7, a heating mode, and a reheating mode.

先ず、排熱貯留運転モードにおける湯水の流れについて、図７を参照しながら説明する。排熱貯留運転モードである場合、熱源部２においてガスエンジン５が駆動を開始し、それに伴い循環ポンプ１６が作動して排熱回収側循環回路１２内を湯水が循環し始める。排熱回収側循環回路１２内を流れる湯水は、ガスエンジン５の駆動に伴い発生する排熱により加熱される。   First, the flow of hot water in the exhaust heat storage operation mode will be described with reference to FIG. In the exhaust heat storage operation mode, the gas engine 5 starts to be driven in the heat source unit 2, and the circulation pump 16 is activated accordingly, and hot water starts to circulate in the exhaust heat recovery side circulation circuit 12. The hot water flowing in the exhaust heat recovery side circulation circuit 12 is heated by the exhaust heat generated when the gas engine 5 is driven.

一方、排熱利用装置３では、循環ポンプ４７が駆動を開始し、貯留タンク３１の底部に設けられた貯留部排出管８９から貯留タンク３１内の湯水が循環ポンプ４７に流入する。そして循環ポンプ４７から吐出された湯水は、排熱・消費熱交換器３０においてガスエンジン５の排熱によって加熱された湯水と熱交換を行って加熱された後、高温湯往き側流路３８を流れ温水装置バイパス路２３を経由して流れ、貯留部給湯管８７に入る。
そして排熱・消費熱交換器３０から排出された湯水の一部が貯留タンク３１に入り、残部は、バイパス流路１１を経由して流れ、混合弁４６に入る。 On the other hand, in the exhaust heat utilization device 3, the circulation pump 47 starts to be driven, and hot water in the storage tank 31 flows into the circulation pump 47 from a storage portion discharge pipe 89 provided at the bottom of the storage tank 31. The hot water discharged from the circulation pump 47 is heated by exchanging heat with the hot water heated by the exhaust heat of the gas engine 5 in the exhaust heat / consumed heat exchanger 30, and then passed through the high-temperature hot water flow-through channel 38. It flows via the flowing hot water apparatus bypass 23 and enters the reservoir hot water supply pipe 87.
A part of the hot water discharged from the exhaust heat / consumption heat exchanger 30 enters the storage tank 31, and the remaining part flows via the bypass flow path 11 and enters the mixing valve 46.

ここで本実施形態では、先の実施形態と同様に、熱源部２側の冷却液用温度センサー２５の検知温度が所定の冷却液目標温度に一致する様に、混合弁４６の開度がフィードバック制御される。
そのため排熱・消費熱交換器３０に供給される湯水の温度が調整され、排熱・消費熱交換器３０の一次側を流れる冷却液が冷却液目標温度に一致する。 In this embodiment, as in the previous embodiment, the opening of the mixing valve 46 is fed back so that the temperature detected by the coolant temperature sensor 25 on the heat source unit 2 side matches the predetermined coolant target temperature. Be controlled.
Therefore, the temperature of the hot water supplied to the exhaust heat / consumption heat exchanger 30 is adjusted, and the coolant flowing on the primary side of the exhaust heat / consumption heat exchanger 30 matches the coolant target temperature.

また排熱利用装置３側の加熱水用温度センサー（消費側温度検知手段）２１の検知温度と貯湯目標温度（使用用途目標温度）との偏差に応じて冷却液目標温度が補正される。補正のための関数は、前記した実施形態と同一である。
その結果、排熱・消費熱交換器３０の二次側から吐出される湯水の温度が調整され、貯湯目標温度に近づく。
そして貯湯目標温度に近い温度の湯水が貯留タンク３１に供給され、貯留タンク３１内に温度成層を構成する。 Further, the coolant target temperature is corrected in accordance with the deviation between the detected temperature of the heating water temperature sensor (consumption side temperature detecting means) 21 on the exhaust heat utilization device 3 side and the hot water storage target temperature (use target temperature). The function for correction is the same as in the above-described embodiment.
As a result, the temperature of the hot water discharged from the secondary side of the exhaust heat / consumed heat exchanger 30 is adjusted and approaches the hot water storage target temperature.
Then, hot water having a temperature close to the hot water storage target temperature is supplied to the storage tank 31, and a temperature stratification is formed in the storage tank 31.

貯留タンク３１内に貯留されている湯水の略全体が所定温度以上となると、排熱貯湯モードによる湯水の貯留が完了する。   When substantially the entire hot water stored in the storage tank 31 reaches a predetermined temperature or higher, the hot water storage in the exhaust heat hot water storage mode is completed.

コージェネレーションシステム１を使用して給湯を行う場合の湯水の流れは、図８の通りである。即ちガスエンジン５が停止した状態の時に、給湯栓７が開栓されると、給水管８５を介して外部から供給される低温の水の一部は、給湯混合弁８０に向けて供給される。一方、外部から供給される低温の水の一部は、給水管８５から分岐された貯留部給水管９１を介して貯留タンク３１の底部に流入する。貯留タンク３１の底部から湯水が流入すると、この湯水によって貯留タンク３１内に貯留されている湯水が上方に押し上げられ、貯留タンク３１の上部側に貯留されている高温の湯水が貯留部給湯管８７から排出される。貯留部給湯管８７から排出された湯水は給湯往路８３内を流れ、給湯混合弁８０側へと流れ、給水管８５を介して供給された低温の水と混合されて適温となり、給湯回路３３を介して給湯栓７から排出される。   The flow of hot water when hot water is supplied using the cogeneration system 1 is as shown in FIG. That is, when the hot water tap 7 is opened while the gas engine 5 is stopped, a part of the low-temperature water supplied from the outside through the water supply pipe 85 is supplied toward the hot water supply mixing valve 80. . On the other hand, a part of the low-temperature water supplied from the outside flows into the bottom of the storage tank 31 through the storage unit water supply pipe 91 branched from the water supply pipe 85. When hot water flows from the bottom of the storage tank 31, the hot water stored in the storage tank 31 is pushed upward by this hot water, and the hot hot water stored on the upper side of the storage tank 31 becomes the storage section hot water supply pipe 87. Discharged from. Hot water discharged from the reservoir hot water supply pipe 87 flows in the hot water supply forward path 83, flows to the hot water supply mixing valve 80 side, is mixed with the low-temperature water supplied through the water supply pipe 85, and reaches an appropriate temperature. And discharged from the hot-water tap 7.

一方、ガスエンジン５が駆動している状態のときに給湯栓７が開栓された場合の湯水の流れは、図９の通りであり、給湯栓７が開栓されると、給水管８５を介して外部から供給される低温の水の一部が、直接排熱・消費熱交換器３０に導入されて昇温される。
この場合についても、排熱貯留運転モードと同様に、熱源部２側の冷却液用温度センサー２５の検知温度が所定の冷却液目標温度に一致する様に、混合弁４６の開度がフィードバック制御される。
そのため排熱・消費熱交換器３０に供給される湯水の温度が調整され、排熱・消費熱交換器３０の一次側を流れる冷却液が冷却液目標温度に一致する。 On the other hand, the flow of hot water when the hot-water tap 7 is opened while the gas engine 5 is in operation is as shown in FIG. 9, and when the hot-water tap 7 is opened, the water supply pipe 85 is opened. A part of the low-temperature water supplied from the outside is directly introduced into the exhaust heat / consumed heat exchanger 30 to be heated.
Also in this case, as in the exhaust heat storage operation mode, the opening degree of the mixing valve 46 is feedback controlled so that the temperature detected by the coolant temperature sensor 25 on the heat source unit 2 side matches the predetermined coolant target temperature. Is done.
Therefore, the temperature of the hot water supplied to the exhaust heat / consumption heat exchanger 30 is adjusted, and the coolant flowing on the primary side of the exhaust heat / consumption heat exchanger 30 matches the coolant target temperature.

またこの場合も、排熱利用装置３側の加熱水用温度センサー（消費側温度検知手段）２１の検知温度を参酌して冷却液目標温度が補正される。しかしながら、給湯が実行されている際の加熱水側の目標温度は、必ずしも貯湯目標温度とは一致しない。即ち給湯が実行されている際には、加熱水用温度センサー２１の検知温度と、給湯時目標温度との偏差に基づいて冷却液目標温度が補正される。   Also in this case, the coolant target temperature is corrected in consideration of the detected temperature of the heating water temperature sensor (consumption side temperature detecting means) 21 on the exhaust heat utilization device 3 side. However, the target temperature on the heated water side when hot water is being supplied does not necessarily match the target hot water storage temperature. That is, when hot water is being supplied, the coolant target temperature is corrected based on the deviation between the temperature detected by the heating water temperature sensor 21 and the hot water supply target temperature.

また本実施形態のコージェネレーションシステム１では、暖房運転や風呂追い焚き運転が可能である。
ガスエンジン５が駆動している状態のときに暖房運転が実行された場合の湯水の流れは、図１０の通りであり、風呂追い焚き運転が実行された場合の湯水の流れは、図１１の通りである。 Moreover, in the cogeneration system 1 of this embodiment, heating operation and bath reheating operation are possible.
The flow of hot water when the heating operation is executed while the gas engine 5 is driven is as shown in FIG. 10, and the flow of hot water when the bath reheating operation is executed is as shown in FIG. Street.

いずれの場合についても排熱利用装置３側の加熱水用温度センサー（消費側温度検知手段）２１の検知温度を参酌して冷却液目標温度が補正される。しかしながら、追い焚き運転や暖房運転が実行されている際の加熱水側の目標温度は、必ずしも貯湯目標温度とは一致しない。即ち風呂追い焚き運転が実行されている際には、加熱水用温度センサー２１の検知温度と、風呂追い焚き目標温度との偏差に基づいて冷却液目標温度が補正される。
また暖房運転が実行されている際の加熱水側の目標温度は、加熱水用温度センサー２１の検知温度と、暖房運転目標温度との偏差に基づいて冷却液目標温度が補正される。 In any case, the coolant target temperature is corrected in consideration of the temperature detected by the heating water temperature sensor (consumption side temperature detection means) 21 on the exhaust heat utilization device 3 side. However, the target temperature on the heated water side when the reheating operation or the heating operation is being executed does not necessarily coincide with the hot water storage target temperature. That is, when the bath reheating operation is performed, the coolant target temperature is corrected based on the deviation between the temperature detected by the heating water temperature sensor 21 and the bath reheating target temperature.
The target temperature on the heating water side when the heating operation is being executed is corrected to the target coolant temperature based on the deviation between the temperature detected by the heating water temperature sensor 21 and the heating operation target temperature.

以上説明した実施形態では、消費側液制御手段として混合弁を採用したが、本発明はこれに限定されるものではなく、２ポートの流量制御弁や流量可変型のポンプを採用することも可能である。   In the embodiment described above, the mixing valve is used as the consumption side liquid control means. However, the present invention is not limited to this, and a two-port flow control valve or a variable flow rate pump can also be used. It is.

また上記した実施形態では、冷却液温度検知手段として冷却液用温度センサー１０８，２５を使用し、これらのセンサーは、いずれも膨張タンク１１０，２２と循環ポンプ１１１，１６の間に設けた。即ち上記した実施形態では、排熱回収側循環回路１０７，１２によって熱を奪われた後、加熱も冷却もされない状態の冷却液の温度を検知する構成を採用した。
しかし冷却液温度検知手段の取付け位置は、この位置に限定されるものではなく、排熱回収側循環回路１０７，１２のいずれかに設けられておればよい。例えばガスエンジン１０５，５の吐出側から排熱・消費熱交換器１１２，３０に至る間に冷却液温度検知手段を設けてもよい。この場合、冷却液目標温度の初期値は、貯湯目標温度よりも高い温度となる。 In the above-described embodiment, the coolant temperature sensors 108 and 25 are used as the coolant temperature detecting means, and these sensors are provided between the expansion tanks 110 and 22 and the circulation pumps 111 and 16, respectively. That is, in the above-described embodiment, a configuration is adopted in which the temperature of the coolant that is not heated or cooled after the heat is removed by the exhaust heat recovery side circulation circuits 107 and 12 is detected.
However, the mounting position of the coolant temperature detecting means is not limited to this position, and it may be provided in any one of the exhaust heat recovery side circulation circuits 107 and 12. For example, a coolant temperature detecting means may be provided between the discharge side of the gas engines 105 and 5 and the exhaust heat / consumed heat exchangers 112 and 30. In this case, the initial value of the coolant target temperature is higher than the hot water storage target temperature.

ただし排熱・消費熱交換器１１２，３０の上流側の温度は、熱消費側回路の排熱・消費熱交換器１１２，３０の吐出側温度の温度変化に対して反応が鈍いので、排熱回収側循環回路１０７，１２によって熱を奪われた後の冷却液の温度を検知する構成を採用することが望ましい。
そのため冷却液用温度センサー１０８，２５の取付け位置は、排熱回収側循環回路の排熱・消費熱交換器１１２，３０の吐出側の直後、膨張タンク１１０，２２の前後、循環ポンプ１１１，１６の前後及びガスエンジン１０５，５の直前のいずれかであることが望ましい。 However, since the temperature on the upstream side of the exhaust heat / consumed heat exchangers 112, 30 is slow to react to the temperature change of the discharge side temperature of the exhaust heat / consumed heat exchangers 112, 30 of the heat consumption side circuit, It is desirable to employ a configuration that detects the temperature of the coolant after heat has been removed by the recovery-side circulation circuits 107 and 12.
For this reason, the mounting positions of the coolant temperature sensors 108 and 25 are immediately after the discharge side of the exhaust heat / consumption heat exchangers 112 and 30 of the exhaust heat recovery side circulation circuit, before and after the expansion tanks 110 and 22, and the circulation pumps 111 and 16. It is desirable that either before or after the gas engine 105 or 5.

本発明は、コージェネレーションシステムの改良を端緒として完成されたものであるが、本発明の技術思想は、ヒートポンプ式給湯装置１５０，１７０にも応用することができる。
即ちヒートポンプ式給湯装置１５０，１７０は、コージェネレーションシステム１，１００と共通点が多く、技術的問題点も共通してる場合が多い。
具体的には、コージェネレーションシステム１，１００の排熱回収側循環回路１０７，１２と同様の機能を発揮するものとして、ヒートポンプ式給湯装置１５０，１７０では、ヒートポンプ回路１６０がある。またヒートポンプ式給湯装置１５０，１７０についても、貯湯循環回路（熱消費側回路）１２２，４１を持つものが多い。さらにコージェネレーションシステム１，１００の排熱・消費熱交換器１１２，３０と同様の機能を発揮するものとして、ヒートポンプ式給湯装置では、凝縮・消費熱交換器１５７，１７１がある。 Although the present invention has been completed with the improvement of the cogeneration system, the technical idea of the present invention can also be applied to the heat pump hot water supply apparatuses 150 and 170.
That is, the heat pump type hot water supply apparatuses 150 and 170 have many common points with the cogeneration systems 1 and 100, and often have common technical problems.
Specifically, in the heat pump hot water supply apparatuses 150 and 170, there is a heat pump circuit 160 that exhibits the same function as the exhaust heat recovery side circulation circuits 107 and 12 of the cogeneration systems 1 and 100. Also, the heat pump hot water supply apparatuses 150 and 170 often have hot water storage circulation circuits (heat consumption side circuits) 122 and 41. Furthermore, as a heat pump type hot water supply apparatus, there are condensation / consumption heat exchangers 157 and 171 that perform the same functions as the exhaust heat / consumption heat exchangers 112 and 30 of the cogeneration systems 1 and 100.

以下、図１２を参照しつつ、本発明の技術思想を応用したヒートポンプ式給湯装置１５０を説明する。
本実施形態のヒートポンプ式給湯装置１５０の機械的構成は、先に試作したコージェネレーションシステム１００と共通するものが多い。
即ちヒートポンプ式給湯装置１５０は、前記したコージェネレーションシステム１００の熱源ユニット１０１に代わってヒートポンプユニット１５１を有している。またヒートポンプ式給湯装置１５０は、前記したコージェネレーションシステム１００と同様に貯湯ユニット１５２を備えている。
ヒートポンプユニット１５１は、圧縮機１５３と、膨張弁１５５と、蒸発器１５６を備えている。そして、圧縮機１５３と、貯湯ユニット１５２側の凝縮・消費熱交換器１５７と膨張弁１５５及び蒸発器１５６が環状に繋がれ、相変化する冷媒液を循環させて熱エネルギーを発生させる。 Hereinafter, a heat pump type hot water supply apparatus 150 to which the technical idea of the present invention is applied will be described with reference to FIG.
The mechanical configuration of the heat pump hot water supply apparatus 150 of this embodiment is often the same as that of the cogeneration system 100 that was previously prototyped.
That is, the heat pump hot water supply apparatus 150 includes a heat pump unit 151 in place of the heat source unit 101 of the cogeneration system 100 described above. The heat pump hot water supply apparatus 150 includes a hot water storage unit 152 as in the cogeneration system 100 described above.
The heat pump unit 151 includes a compressor 153, an expansion valve 155, and an evaporator 156. The compressor 153, the condensing / consuming heat exchanger 157 on the hot water storage unit 152 side, the expansion valve 155, and the evaporator 156 are connected in an annular shape, and circulate the phase-change refrigerant liquid to generate thermal energy.

即ち圧縮機１５３と、貯湯ユニット１５２側の凝縮・消費熱交換器１５７と膨張弁１５５及び蒸発器１５６が環状に繋がれてヒートポンプ回路１６０が構成され、当該ヒートポンプ回路１６０内には相変化する冷媒があり、当該冷媒は、圧縮機１５３から凝縮・消費熱交換器１５７に入り、凝縮・消費熱交換器１５７の一次側流路を通過して膨張弁１５５に入り、蒸発器１５６を経て圧縮機１５３に戻る。また内部の冷媒は、圧縮機１５３で圧縮される前の段階では気体であり、圧縮機１５３で断熱圧縮されて昇温する。そして凝縮・消費熱交換器１５７で熱を奪われて液化し、膨張弁１５５を経て蒸発器１５６に入り、再度気化して圧縮機１５３に戻る。   That is, the compressor 153, the condenser / consumer heat exchanger 157 on the hot water storage unit 152 side, the expansion valve 155, and the evaporator 156 are connected in an annular shape to form a heat pump circuit 160, and the heat pump circuit 160 has a phase-change refrigerant. The refrigerant enters the condensation / consumption heat exchanger 157 from the compressor 153, passes through the primary flow path of the condensation / consumption heat exchanger 157, enters the expansion valve 155, passes through the evaporator 156, and then enters the compressor. Return to 153. In addition, the internal refrigerant is a gas before being compressed by the compressor 153 and is adiabatically compressed by the compressor 153 to increase the temperature. Then, heat is removed from the condenser / consumption heat exchanger 157 to be liquefied, enters the evaporator 156 through the expansion valve 155, vaporizes again, and returns to the compressor 153.

本実施形態では、凝縮・消費熱交換器１５７の一次側に第１冷媒液用温度センサー１６１が設けられており、凝縮・消費熱交換器１５７の一次側を流れる冷媒液の温度を監視している。またヒートポンプ回路１６０の凝縮・消費熱交換器１５７の吐出側と膨張弁１５５の導入側との間には第２冷媒液用温度センサー１６２が設けられ、凝縮・消費熱交換器１５７の一次側から吐出される冷媒液の温度が監視されている。即ち凝縮・消費熱交換器１５７を通過して熱を奪われた後の冷媒液の温度が監視されている。   In the present embodiment, the first refrigerant liquid temperature sensor 161 is provided on the primary side of the condensation / consumption heat exchanger 157, and the temperature of the refrigerant liquid flowing on the primary side of the condensation / consumption heat exchanger 157 is monitored. Yes. Further, a second refrigerant liquid temperature sensor 162 is provided between the discharge side of the condensation / consumption heat exchanger 157 of the heat pump circuit 160 and the introduction side of the expansion valve 155, and from the primary side of the condensation / consumption heat exchanger 157. The temperature of the discharged refrigerant liquid is monitored. That is, the temperature of the refrigerant liquid after being deprived of heat through the condenser / consumption heat exchanger 157 is monitored.

貯湯ユニット１５２の構成は、図１の実施形態と大差なく、貯留タンク１２０と、循環ポンプ１２１と、凝縮・消費熱交換器１５７が内蔵されている。貯湯ユニット１５２の構成は、図１の実施形態と大差無いので、詳細な説明を省略する。   The configuration of the hot water storage unit 152 is not much different from the embodiment of FIG. 1, and the storage tank 120, the circulation pump 121, and the condensation / consumption heat exchanger 157 are built in. The configuration of the hot water storage unit 152 is not much different from that of the embodiment of FIG.

そして本実施形態のヒートポンプ式給湯装置１５０では、凝縮・消費熱交換器１５７の一次側から吐出された冷媒液の温度と、凝縮・消費熱交換器１５７の二次側から吐出された湯水の温度の双方に基づいて混合弁１２６が制御される。
より具体的には、凝縮・消費熱交換器１５７の一次側の下流側に設けられた第２冷媒液用温度センサー（冷媒液温度検知手段）１６２の検知温度と、凝縮・消費熱交換器１５７の二次側の下流側に設けられた加熱水用温度センサー（消費側温度検知手段）１１３の検知温度に基づいて混合弁１２６が制御される。 And in the heat pump type hot water supply apparatus 150 of this embodiment, the temperature of the refrigerant liquid discharged from the primary side of the condensation / consumption heat exchanger 157 and the temperature of the hot water discharged from the secondary side of the condensation / consumption heat exchanger 157 Based on both of these, the mixing valve 126 is controlled.
More specifically, the detection temperature of the second refrigerant liquid temperature sensor (refrigerant liquid temperature detection means) 162 provided downstream of the primary side of the condensation / consumption heat exchanger 157 and the condensation / consumption heat exchanger 157 The mixing valve 126 is controlled based on the temperature detected by the heating water temperature sensor (consumption side temperature detecting means) 113 provided downstream of the secondary side.

ここで二つの温度センサー１６２，１１３の混合弁１２６の制御に対する寄与は、対等ではなく、冷媒液の温度を検知するヒートポンプユニット１５１側の第２冷媒液用温度センサー１６２が主体となって混合弁１２６が制御され、補助的に貯湯ユニット１５２側の加熱水用温度センサー１１３の検知温度が使用される。   Here, the contribution of the two temperature sensors 162 and 113 to the control of the mixing valve 126 is not equal, but the mixing valve is mainly composed of the second refrigerant liquid temperature sensor 162 on the heat pump unit 151 side that detects the temperature of the refrigerant liquid. 126 is controlled, and the temperature detected by the temperature sensor 113 for the heated water on the hot water storage unit 152 side is used as an auxiliary.

より具体的には、第２冷媒液用温度センサー１６２の検知温度が所定の冷媒液目標温度に一致する様に、混合弁１２６の開度がフィードバック制御される。
即ち第２冷媒液用温度センサー１６２の検知温度が冷媒液目標温度よりも高い場合には、混合弁１２６のバイパス流路１２５側の開度が閉鎖方向に動作し、貯留タンク１２０の底側と繋がる側の開度が開く方向に動作する。
その結果、凝縮・消費熱交換器１５７の二次側に供給される湯水の温度が低下し、一次側を流れる冷媒液（この段階では気体）との温度差が増大して一次側の冷媒液から、より多くの熱を奪う。その結果一次側を流れる冷媒液の温度が低下し、冷媒液目標温度に近づく。 More specifically, the opening degree of the mixing valve 126 is feedback-controlled so that the temperature detected by the second refrigerant liquid temperature sensor 162 matches a predetermined refrigerant liquid target temperature.
That is, when the temperature detected by the second refrigerant liquid temperature sensor 162 is higher than the refrigerant liquid target temperature, the opening degree of the mixing valve 126 on the bypass flow path 125 side operates in the closing direction, and the bottom side of the storage tank 120 It operates in the direction that the opening on the connected side opens.
As a result, the temperature of the hot water supplied to the secondary side of the condensing / consuming heat exchanger 157 decreases, and the temperature difference from the refrigerant liquid flowing at the primary side (gas at this stage) increases, leading to the refrigerant liquid on the primary side. Take away more heat from. As a result, the temperature of the refrigerant liquid flowing on the primary side decreases and approaches the refrigerant liquid target temperature.

逆に第２冷媒液用温度センサー１６２の検知温度が冷媒液目標温度よりも低い場合には、混合弁１２６のバイパス流路１２５側の開度が開く方向に動作し、貯留タンク１２０の底側と繋がる側の開度が閉鎖方向に動作する。
その結果、凝縮・消費熱交換器１５７の二次側に供給される湯水の温度が上昇し、一次側を流れる冷媒液（この段階では気体）との温度差が減少して一次側の冷媒液から奪う熱量が減少する。その結果一次側を流れる冷媒液の温度が上昇し、冷媒液目標温度に近づく。 On the other hand, when the temperature detected by the second refrigerant liquid temperature sensor 162 is lower than the refrigerant liquid target temperature, the opening of the mixing valve 126 on the bypass flow path 125 side operates in the direction of opening, and the bottom side of the storage tank 120 The opening on the side connected to the valve operates in the closing direction.
As a result, the temperature of the hot water supplied to the secondary side of the condensing / consuming heat exchanger 157 rises, and the temperature difference from the refrigerant liquid (gas at this stage) flowing on the primary side decreases, and the primary side refrigerant liquid Reduces the amount of heat it takes. As a result, the temperature of the refrigerant liquid flowing on the primary side rises and approaches the refrigerant liquid target temperature.

また前記した様に本実施形態では、補助的に貯湯ユニット１５２側の加熱水用温度センサー（消費側温度検知手段）１１３の検知温度が参酌される。
即ち貯湯ユニット１５２側の加熱水用温度センサー（消費側温度検知手段）１１３の検知温度が貯湯目標温度（使用用途目標温度）から外れた場合には、冷媒液目標温度を変更する。
具体的に説明すると、加熱水用温度センサー１１３の検知温度が貯湯目標温度（使用用途目標温度）よりも高い場合には、冷媒液目標温度を下げる。
その結果、第２冷媒液用温度センサー１６２の現在の検知温度が補正後の冷媒液目標温度よりも高い状態となり、混合弁１２６のバイパス流路１２５側の開度が閉鎖方向に動作し、貯留タンク１２０の底側と繋がる側の開度が開く方向に動作する。
その結果、凝縮・消費熱交換器１５７の二次側に供給される湯水の温度が低下し、一次側を流れる冷媒液との温度差が増大して一次側の冷媒液からより多くの熱を奪う。その結果一次側を流れる冷媒液の温度が低下し、冷媒液目標温度に近づく。
また凝縮・消費熱交換器１５７の二次側に供給される湯水の温度が低下するので、凝縮・消費熱交換器１５７の二次側から吐出される湯水の温度も低下し、その後の凝縮・消費熱交換器１５７の二次側から吐出される湯水の温度が貯湯目標温度に近づく。 Further, as described above, in the present embodiment, the detected temperature of the heating water temperature sensor (consumption side temperature detecting means) 113 on the hot water storage unit 152 side is supplementarily taken into consideration.
That is, when the temperature detected by the hot water temperature sensor (consumption side temperature detecting means) 113 on the hot water storage unit 152 side deviates from the hot water storage target temperature (use target temperature), the refrigerant liquid target temperature is changed.
More specifically, when the detected temperature of the heating water temperature sensor 113 is higher than the hot water storage target temperature (use target temperature), the refrigerant liquid target temperature is lowered.
As a result, the current detected temperature of the second refrigerant liquid temperature sensor 162 is higher than the corrected refrigerant liquid target temperature, the opening degree of the mixing valve 126 on the bypass flow path 125 side operates in the closing direction, and storage is performed. The opening of the side connected with the bottom side of the tank 120 operates in the direction of opening.
As a result, the temperature of the hot water supplied to the secondary side of the condensation / consumption heat exchanger 157 decreases, the temperature difference with the refrigerant liquid flowing on the primary side increases, and more heat is generated from the refrigerant liquid on the primary side. Take away. As a result, the temperature of the refrigerant liquid flowing on the primary side decreases and approaches the refrigerant liquid target temperature.
Moreover, since the temperature of the hot water supplied to the secondary side of the condensation / consumption heat exchanger 157 decreases, the temperature of the hot water discharged from the secondary side of the condensation / consumption heat exchanger 157 also decreases, The temperature of the hot water discharged from the secondary side of the heat exchanger 157 approaches the hot water storage target temperature.

逆に加熱水用温度センサー１１３の検知温度が貯湯目標温度よりも低い場合には、冷媒液目標温度を上げる。
その結果、第２冷媒液用温度センサー１６２の現在の検知温度が補正後の冷媒液目標温度よりも低い状態となり、混合弁１２６のバイパス流路１２５側の開度が開く方向に動作し、貯留タンク１２０の底側と繋がる側の開度が閉じる方向に動作する。
その結果、凝縮・消費熱交換器１５７の二次側に供給される湯水の温度が上昇し、一次側を流れる冷媒液との温度差が減少して一次側の冷媒液から奪う熱量が減少する。その結果一次側を流れる冷媒液の温度が上昇し、冷媒液目標温度に近づく。
また凝縮・消費熱交換器１５７の二次側に供給される湯水の温度が上昇するので、凝縮・消費熱交換器１５７の二次側から吐出される湯水の温度も上昇し、その後の凝縮・消費熱交換器１５７の二次側から吐出される湯水の温度が貯湯目標温度に近づく。 Conversely, when the temperature detected by the heated water temperature sensor 113 is lower than the hot water storage target temperature, the refrigerant liquid target temperature is raised.
As a result, the current detected temperature of the second refrigerant liquid temperature sensor 162 is lower than the corrected refrigerant liquid target temperature, and the opening of the mixing valve 126 on the bypass flow path 125 side is opened and operated. The opening on the side connected to the bottom side of the tank 120 operates in the closing direction.
As a result, the temperature of the hot water supplied to the secondary side of the condensation / consumption heat exchanger 157 rises, the temperature difference with the refrigerant liquid flowing through the primary side decreases, and the amount of heat taken from the refrigerant liquid on the primary side decreases. . As a result, the temperature of the refrigerant liquid flowing on the primary side rises and approaches the refrigerant liquid target temperature.
Moreover, since the temperature of the hot water supplied to the secondary side of the condensation / consumption heat exchanger 157 increases, the temperature of the hot water discharged from the secondary side of the condensation / consumption heat exchanger 157 also increases, and the subsequent condensation / The temperature of the hot water discharged from the secondary side of the heat exchanger 157 approaches the hot water storage target temperature.

以上説明した実施形態では、第２冷媒液用温度センサー１６２の検知温度が所定の冷媒液目標温度に一致する様に、混合弁１２６の開度をフィードバック制御したが、第１冷媒液用温度センサー１６１の検知温度が所定の冷媒液目標温度に一致する様に、混合弁１２６の開度をフィードバック制御してもよい。   In the embodiment described above, the opening degree of the mixing valve 126 is feedback-controlled so that the detected temperature of the second refrigerant liquid temperature sensor 162 matches the predetermined refrigerant liquid target temperature, but the first refrigerant liquid temperature sensor The opening degree of the mixing valve 126 may be feedback-controlled so that the detected temperature 161 matches the predetermined refrigerant liquid target temperature.

また前記した図２の様な周辺機器を有する構成としてもよい。
図１３に示すヒートポンプ式給湯装置１７０の各構成は、前記した図２と同一であるから、同一の部材に同一の番号を付して重複した説明を省略する。図１３に示すヒートポンプ式給湯装置１７０では、符番１７１が付された部材が、凝縮・消費熱交換器である。 Moreover, it is good also as a structure which has a peripheral device like above-mentioned FIG.
Since each structure of the heat pump type hot water supply apparatus 170 shown in FIG. 13 is the same as that of FIG. 2 described above, the same reference numerals are assigned to the same members, and duplicate descriptions are omitted. In the heat pump type hot water supply apparatus 170 shown in FIG. 13, the member denoted by reference numeral 171 is a condensation / consumption heat exchanger.

１ コージェネレーションシステム
２ 熱源部
３ 排熱利用装置
５ ガスエンジン
６ 温水装置
８ 暖房装置
１０ 発電機
１１ バイパス流路
１２ 排熱回収側循環回路
１６ 循環ポンプ
２１ 加熱水用温度センサー
２５ 冷却液用温度センサー
３０ 排熱・消費熱交換器
３１ 貯留タンク
３３ 給湯回路
３６ 浴槽循環回路
４１ 貯湯循環回路（熱消費側回路）
４５ 熱交換部
４６ 混合弁（消費側液制御手段）
４７ 循環ポンプ
１００ コージェネレーションシステム
１０１ 熱源ユニット（熱源部）
１０２ 貯湯ユニット（排熱利用装置）
１０５ ガスエンジン
１０７ 排熱回収側循環回路
１０８ 冷却液用温度センサー
１１１ 循環ポンプ
１１２ 排熱・消費熱交換器
１１３ 加熱水用温度センサー
１２０ 貯留タンク
１２２ 貯湯循環回路（熱消費側回路）
１２５ バイパス流路
１２６ 混合弁（消費側液制御手段）
１５０ ヒートポンプ式給湯装置
１５１ ヒートポンプユニット
１５２ 貯湯ユニット
１５３ 圧縮機
１５５ 膨張弁
１５６ 蒸発器
１５７ 凝縮・消費熱交換器
１６０ ヒートポンプ回路
１６１ 第１冷媒液用温度センサー
１６２ 第２冷媒液用温度センサー
１７０ ヒートポンプ式給湯装置
１７１ 凝縮・消費熱交換器 DESCRIPTION OF SYMBOLS 1 Cogeneration system 2 Heat source part 3 Waste heat utilization apparatus 5 Gas engine 6 Hot water apparatus 8 Heating apparatus 10 Generator 11 Bypass flow path 12 Waste heat recovery side circulation circuit 16 Circulation pump 21 Temperature sensor 25 for heating water Cooling temperature sensor 30 Waste Heat / Consumption Heat Exchanger 31 Storage Tank 33 Hot Water Supply Circuit 36 Bathtub Circulation Circuit 41 Hot Water Storage Circulation Circuit (Heat Consumption Side Circuit)
45 Heat exchange section 46 Mixing valve (consumption liquid control means)
47 Circulation pump 100 Cogeneration system 101 Heat source unit (heat source part)
102 Hot water storage unit (exhaust heat utilization device)
105 Gas Engine 107 Waste Heat Recovery Side Circulation Circuit 108 Coolant Temperature Sensor 111 Circulation Pump 112 Waste Heat / Consumption Heat Exchanger 113 Heating Water Temperature Sensor 120 Storage Tank 122 Hot Water Storage Circulation Circuit (Heat Consumption Side Circuit)
125 Bypass passage 126 Mixing valve (consumption liquid control means)
150 Heat pump type hot water supply device 151 Heat pump unit 152 Hot water storage unit 153 Compressor 155 Expansion valve 156 Evaporator 157 Condensation / consumption heat exchanger 160 Heat pump circuit 161 First refrigerant liquid temperature sensor 162 Second refrigerant liquid temperature sensor 170 Heat pump hot water supply Equipment 171 Condensation / consumption heat exchanger

Claims (5)

電気エネルギーと熱エネルギーとを同時に発生させる発電部と、前記発電部に冷却液を循環させて発電部の熱エネルギーを回収する排熱回収側循環回路と、液体を循環及び／又は通過させて熱エネルギーを貯留及び／又は消費する熱消費側回路と、排熱回収側循環回路及び熱消費側回路の一部を構成し排熱回収側循環回路から熱消費側回路に熱エネルギーを移動させる排熱・消費熱交換器とを備えたコージェネレーションシステムにおいて、排熱回収側循環回路を流れる冷却液の温度を検知する冷却液温度検知手段と、排熱・消費熱交換器の下流側であって熱消費側回路を流れる液体の温度を検知する消費側温度検知手段と、排熱・消費熱交換器の熱消費側回路側に流入する液体の温度及び／又は流量を増減することができる消費側液制御手段とを備え、前記冷却液温度検知手段の検知温度と消費側温度検知手段の検知温度の双方に基づいて消費側液制御手段を制御し、
排熱回収側循環回路を流れる冷却液の目標温度を冷却液目標温度とし、
熱消費側回路は、湯水を貯留する貯留タンクを有していて熱エネルギーを貯留する機能を備え、排熱・消費熱交換器と貯留タンクの双方を含む貯湯循環回路があり、排熱・消費熱交換器には貯留タンクの下部側から湯水が供給され、排熱・消費熱交換器から吐出される湯水は貯留タンクの上部から注入され、貯留タンクをバイパスするバイパス流路を有し、
前記消費側液制御手段は、排熱回収側循環回路を流れる冷却液の温度が冷却液目標温度よりも高い場合には、バイパス流路から排熱・消費熱交換器に導入される湯水の量を減らし、貯留タンクの下部から排熱・消費熱交換器に導入される湯水の量を増加させる様に動作することを特徴とするコージェネレーションシステム。 A power generation unit that simultaneously generates electrical energy and thermal energy, a heat recovery side circulation circuit that circulates a coolant through the power generation unit to recover the heat energy of the power generation unit, and heats by circulating and / or passing the liquid Heat consumption side circuit that stores and / or consumes energy, waste heat recovery side circulation circuit, and heat consumption side circuit that constitute part of the heat consumption side circuit and exhaust heat that moves heat energy from the waste heat recovery side circulation circuit to the heat consumption side circuit -In a cogeneration system equipped with a heat exchanger, a coolant temperature detecting means for detecting the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit and a heat source downstream of the exhaust heat / heat exchanger Consumption side temperature detecting means for detecting the temperature of the liquid flowing through the consumption side circuit, and consumption side liquid capable of increasing / decreasing the temperature and / or flow rate of the liquid flowing into the heat consumption side circuit side of the exhaust heat / consumption heat exchanger Control hand With the door, it controls the consumer fluid control means based on both the detected temperature of the detected temperature and the consuming temperature detecting means of the coolant temperature detecting means,
The target temperature of the coolant flowing through the exhaust heat recovery side circulation circuit is the coolant target temperature,
The heat consumption side circuit has a storage tank that stores hot water and has a function of storing thermal energy, and has a hot water storage circuit that includes both a waste heat / consumption heat exchanger and a storage tank. Hot water is supplied to the heat exchanger from the lower side of the storage tank, and hot water discharged from the exhaust heat / consumed heat exchanger is injected from the upper part of the storage tank, and has a bypass channel that bypasses the storage tank,
When the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit is higher than the coolant target temperature, the consumption side liquid control means is the amount of hot water introduced into the exhaust heat / consumption heat exchanger from the bypass flow path. Cogeneration system that operates to increase the amount of hot water introduced into the exhaust heat / consumption heat exchanger from the bottom of the storage tank . 熱消費側回路であって排熱・消費熱交換器の下流側を流れる液体の目標温度を使用用途目標温度とし、消費側液制御手段は冷却液温度検知手段の検知温度が冷却液目標温度に一致する様に制御され、且つ消費側温度検知手段の検知温度と使用用途目標温度との偏差に応じて前記冷却液目標温度が補正されることを特徴とする請求項１に記載のコージェネレーションシステム。   The target temperature of the liquid that flows on the downstream side of the exhaust heat / consumption heat exchanger in the heat consumption side circuit is used as the target temperature for use, and the consumption liquid control means detects the temperature of the coolant temperature detection means at the coolant target temperature. 2. The cogeneration system according to claim 1, wherein the cogeneration system is controlled so as to match, and the coolant target temperature is corrected in accordance with a deviation between the detected temperature of the consumption side temperature detecting means and the intended use target temperature. . 電気エネルギーと熱エネルギーとを同時に発生させる発電部と、前記発電部に冷却液を循環させて発電部の熱エネルギーを回収する排熱回収側循環回路と、排熱回収側循環回路を流れる冷却液の温度を検知する冷却液温度検知手段を備えた熱源部に接続され、発電部で発生した熱エネルギーを貯留及び／又は消費する排熱利用装置において、液体を循環及び／又は通過させて熱エネルギーを消費及び／又は貯留する熱消費側回路と、排熱回収側循環回路及び熱消費側回路の一部を構成し排熱回収側循環回路から熱消費側回路に熱エネルギーを移動させる排熱・消費熱交換器と、排熱・消費熱交換器の下流側にあって熱消費側回路を流れる液体の温度を検知する消費側温度検知手段と、排熱・消費熱交換器の熱消費側回路側に流入する液体の温度及び／又は流量を増減することができる消費側液制御手段とを備え、前記冷却液温度検知手段の検知温度と消費側温度検知手段の検知温度の双方に基づいて消費側液制御手段を制御し、
排熱回収側循環回路を流れる冷却液の目標温度を冷却液目標温度とし、
熱消費側回路は、湯水を貯留する貯留タンクを有していて熱エネルギーを貯留する機能を備え、排熱・消費熱交換器と貯留タンクの双方を含む貯湯循環回路があり、排熱・消費熱交換器には貯留タンクの下部側から湯水が供給され、排熱・消費熱交換器から吐出される湯水は貯留タンクの上部から注入され、貯留タンクをバイパスするバイパス流路を有し、
前記消費側液制御手段は、排熱回収側循環回路を流れる冷却液の温度が冷却液目標温度よりも高い場合には、バイパス流路から排熱・消費熱交換器に導入される湯水の量を減らし、貯留タンクの下部から排熱・消費熱交換器に導入される湯水の量を増加させる様に動作することを特徴とする排熱利用装置。 A power generation unit that generates electrical energy and thermal energy simultaneously, a waste heat recovery side circulation circuit that circulates a coolant through the power generation unit and recovers thermal energy of the power generation unit, and a coolant that flows through the exhaust heat recovery side circulation circuit In a waste heat utilization device that is connected to a heat source unit equipped with a coolant temperature detection means for detecting the temperature of the liquid and stores and / or consumes the heat energy generated in the power generation unit, the liquid is circulated and / or passed to cause heat energy. A heat consumption side circuit that consumes and / or stores heat, a waste heat recovery side circulation circuit, and a part of the heat consumption side circuit to transfer heat energy from the waste heat recovery side circulation circuit to the heat consumption side circuit Consumption heat exchanger, consumption side temperature detection means for detecting the temperature of the liquid flowing in the heat consumption side circuit downstream of the exhaust heat / consumption heat exchanger, and the heat consumption side circuit of the exhaust heat / consumption heat exchanger Temperature of the liquid flowing into the side And / or a consumer fluid control means may increase or decrease the flow rate to control the consumer fluid control means based on both the detected temperature of the detected temperature and the consuming temperature detecting means of the coolant temperature detecting means ,
The target temperature of the coolant flowing through the exhaust heat recovery side circulation circuit is the coolant target temperature,
The heat consumption side circuit has a storage tank that stores hot water and has a function of storing thermal energy, and has a hot water storage circuit that includes both a waste heat / consumption heat exchanger and a storage tank. Hot water is supplied to the heat exchanger from the lower side of the storage tank, and hot water discharged from the exhaust heat / consumed heat exchanger is injected from the upper part of the storage tank, and has a bypass channel that bypasses the storage tank,
When the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit is higher than the coolant target temperature, the consumption side liquid control means is the amount of hot water introduced into the exhaust heat / consumption heat exchanger from the bypass flow path. The waste heat utilization device is characterized in that it operates to increase the amount of hot water introduced into the waste heat / consumption heat exchanger from the lower part of the storage tank . 電気エネルギーと熱エネルギーとを同時に発生させる発電部と、前記発電部に冷却液を循環させて発電部の熱エネルギーを回収する排熱回収側循環回路と、液体を循環及び／又は通過させて熱エネルギーを貯留及び／又は消費する熱消費側回路と、排熱回収側循環回路及び熱消費側回路の一部を構成し排熱回収側循環回路から熱消費側回路に熱エネルギーを移動させる排熱・消費熱交換器とを備え、
熱消費側回路は、湯水を貯留する貯留タンクを有していて熱エネルギーを貯留する機能を備え、排熱・消費熱交換器と貯留タンクの双方を含む貯湯循環回路があり、排熱・消費熱交換器には貯留タンクの下部側から湯水が供給され、排熱・消費熱交換器から吐出される湯水は貯留タンクの上部から注入され、貯留タンクをバイパスするバイパス流路を有したコージェネレーションシステムを制御するコージェネレーションシステムの制御方法において、
排熱回収側循環回路を流れる冷却液の温度と、排熱・消費熱交換器の下流側にあって熱消費側回路を流れる液体の温度の双方に基づいて排熱・消費熱交換器の熱消費側回路側に流入する液体の温度及び／又は流量を増減し、
排熱回収側循環回路を流れる冷却液の目標温度を冷却液目標温度とし、
排熱回収側循環回路を流れる冷却液の温度が冷却液目標温度よりも高い場合には、バイパス流路から排熱・消費熱交換器に導入される湯水の量を減らし、貯留タンクの下部から排熱・消費熱交換器に導入される湯水の量を増加させる様に動作させることを特徴とするコージェネレーションシステムの制御方法。 A power generation unit that simultaneously generates electrical energy and thermal energy, a heat recovery side circulation circuit that circulates a coolant through the power generation unit to recover the heat energy of the power generation unit, and heats by circulating and / or passing the liquid Heat consumption side circuit that stores and / or consumes energy, waste heat recovery side circulation circuit, and heat consumption side circuit that constitute part of the heat consumption side circuit and exhaust heat that moves heat energy from the waste heat recovery side circulation circuit to the heat consumption side circuit・ Equipped with a heat exchanger
The heat consumption side circuit has a storage tank that stores hot water and has a function of storing thermal energy, and has a hot water storage circuit that includes both a waste heat / consumption heat exchanger and a storage tank. Hot water is supplied to the heat exchanger from the lower side of the storage tank, and hot water discharged from the exhaust heat / consumed heat exchanger is injected from the upper part of the storage tank and has a bypass passage that bypasses the storage tank. In the control method of the cogeneration system that controls the generation system,
The heat of the exhaust heat / consumption heat exchanger based on both the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit and the temperature of the liquid downstream of the exhaust heat / consumption heat exchanger and flowing through the heat consumption side circuit Increase or decrease the temperature and / or flow rate of the liquid flowing into the consumption circuit side ,
The target temperature of the coolant flowing through the exhaust heat recovery side circulation circuit is the coolant target temperature,
When the temperature of the coolant flowing through the exhaust heat recovery side circulation circuit is higher than the coolant target temperature, the amount of hot water introduced into the exhaust heat / consumed heat exchanger from the bypass flow path is reduced and A control method for a cogeneration system, characterized in that it operates so as to increase the amount of hot water introduced into an exhaust heat / consumed heat exchanger . 圧縮手段、凝縮手段、膨張手段及び蒸発手段が環状に接続され相変化する冷媒液を循環させて熱エネルギーを発生させるヒートポンプ回路と、液体を循環及び／又は通過させて熱エネルギーを貯留及び／又は消費する熱消費側回路と、前記ヒートポンプ回路の凝縮手段及び熱消費側回路の一部を構成しヒートポンプ回路から熱消費側回路に熱エネルギーを移動させる凝縮・消費熱交換器とを備えたヒートポンプ式給湯装置において、ヒートポンプ回路の凝縮・消費熱交換器を流れる冷媒液の温度を検知する冷媒液温度検知手段と、凝縮・消費熱交換器の下流側であって熱消費側回路を流れる液体の温度を検知する消費側温度検知手段と、凝縮・消費熱交換器の熱消費側回路側に流入する液体の温度及び／又は流量を増減することができる消費側液制御手段とを備え、冷媒液の目標温度を冷媒液目標温度とし、熱消費側回路であって凝縮・消費熱交換器の下流側を流れる液体の目標温度を使用用途目標温度とし、消費側液制御手段は冷媒液温度検知手段の検知温度が冷媒液目標温度に一致する様に制御され、
熱消費側回路は、湯水を貯留する貯留タンクを有していて熱エネルギーを貯留する機能を備え、排熱・消費熱交換器と貯留タンクの双方を含む貯湯循環回路があり、排熱・消費熱交換器には貯留タンクの下部側から湯水が供給され、排熱・消費熱交換器から吐出される湯水は貯留タンクの上部から注入され、貯留タンクをバイパスするバイパス流路を有し、
前記消費側液制御手段は、排熱回収側循環回路を流れる冷媒液の温度が冷媒液目標温度よりも高い場合には、バイパス流路から排熱・消費熱交換器に導入される湯水の量を減らし、貯留タンクの下部から凝縮・消費熱交換器に導入される湯水の量を増加させる様に動作することを特徴とするヒートポンプ式給湯装置。 A compression means, a condensation means, an expansion means, and an evaporation means connected in an annular shape to circulate a phase change refrigerant liquid and generate heat energy; and to circulate and / or pass the liquid to store and / or store the heat energy A heat pump type comprising a heat consumption side circuit to be consumed, and a condenser / consumption heat exchanger that constitutes a part of the heat pump circuit condensing means and the heat consumption side circuit and transfers heat energy from the heat pump circuit to the heat consumption side circuit. In the water heater, a refrigerant liquid temperature detecting means for detecting the temperature of the refrigerant liquid flowing through the heat exchanger circuit condensation / consumption heat exchanger, and the temperature of the liquid flowing through the heat consumption side circuit downstream of the condensation / consumption heat exchanger Consumption that can increase or decrease the temperature and / or flow rate of the liquid flowing into the heat consumption side circuit side of the condenser / consumption heat exchanger Liquid control means, the refrigerant liquid target temperature is the refrigerant liquid target temperature, the heat consumption side circuit is the target temperature of the liquid flowing downstream of the condensation / consumption heat exchanger is the intended use target temperature, the consumption side The liquid control means is controlled so that the detection temperature of the refrigerant liquid temperature detection means matches the refrigerant liquid target temperature,
The heat consumption side circuit has a storage tank that stores hot water and has a function of storing thermal energy, and has a hot water storage circuit that includes both a waste heat / consumption heat exchanger and a storage tank. Hot water is supplied to the heat exchanger from the lower side of the storage tank, and hot water discharged from the exhaust heat / consumed heat exchanger is injected from the upper part of the storage tank, and has a bypass channel that bypasses the storage tank,
When the temperature of the refrigerant liquid flowing through the exhaust heat recovery side circulation circuit is higher than the target refrigerant liquid temperature, the consumption-side liquid control means is the amount of hot water introduced into the exhaust heat / consumed heat exchanger from the bypass flow path. The heat pump type hot water supply device that operates to increase the amount of hot water introduced into the condensation / consumption heat exchanger from the lower part of the storage tank .
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