JP5745912B2 - Heat supply system - Google Patents

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JP5745912B2
JP5745912B2 JP2011079823A JP2011079823A JP5745912B2 JP 5745912 B2 JP5745912 B2 JP 5745912B2 JP 2011079823 A JP2011079823 A JP 2011079823A JP 2011079823 A JP2011079823 A JP 2011079823A JP 5745912 B2 JP5745912 B2 JP 5745912B2
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storage device
heat medium
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heat storage
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JP2012215329A (en
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牛尾　雅之
雅之 牛尾
建 小野
建 小野
山口　秀樹
秀樹 山口
一久 井川
一久 井川
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Osaka Gas Co Ltd
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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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/20—Solar thermal
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/70—Hybrid systems, e.g. uninterruptible or back-up power supplies integrating renewable energies

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Description

本発明は、複数の消費者に対して熱を供給する熱供給システムに関する。   The present invention relates to a heat supply system that supplies heat to a plurality of consumers.

集合住宅などに居住する複数の消費者に対して、共通の蓄熱装置に蓄えられた熱を一括して供給する熱供給システムが提案されている。特に、集合住宅に共用の太陽熱集熱器を設け、その太陽熱集熱器で集められた熱を複数の消費者設備に供給可能に構成した熱供給システムが提案されている。例えば、特許文献１に記載の熱供給システムは、太陽熱を集める太陽熱集熱器（２）と、その太陽熱集熱器（２）が集めた熱を、貯えている熱媒を用いて蓄える蓄熱装置（１）と、その蓄熱装置（１）が蓄えている熱媒を複数の消費者設備に向けて循環させる熱媒循環路（１０）とを備える。尚、特許文献１では、熱媒循環路を循環する熱媒は、各消費者設備に設けられる集中型熱供給装置（４）に供給され、その集中型熱供給装置（４）で更に昇温された後で使用に供されるというシステム構成となっている。
尚、上述のような集中型熱供給装置（４）ではなく、各消費者設備に熱交換器を設けておき、各消費者設備では、熱媒循環路を循環する熱媒が有する熱を単にその熱交換器で受け取るような熱供給システムもある。例えば、特許文献２には、消費者設備の夫々に設けられ、熱媒循環路を循環する熱媒と、その消費者設備において加熱対象とする流体との間の熱交換を行う熱交換器を備えるような熱供給システムが記載されている。 There has been proposed a heat supply system that collectively supplies heat stored in a common heat storage device to a plurality of consumers living in an apartment house. In particular, a heat supply system has been proposed in which a shared solar heat collector is provided in an apartment house, and heat collected by the solar heat collector can be supplied to a plurality of consumer facilities. For example, a heat supply system described in Patent Document 1 includes a solar heat collector (2) that collects solar heat, and a heat storage device that stores heat collected by the solar heat collector (2) using a stored heat medium. (1) and a heat medium circulation path (10) for circulating the heat medium stored in the heat storage device (1) toward a plurality of consumer facilities. In Patent Document 1, the heat medium circulating in the heat medium circulation path is supplied to a centralized heat supply device (4) provided in each consumer facility, and the temperature is further increased by the centralized heat supply device (4). The system is configured to be used after being used.
In addition, instead of the centralized heat supply device (4) as described above, a heat exchanger is provided in each consumer facility, and in each consumer facility, the heat of the heat medium circulating in the heat medium circulation path is simply There is also a heat supply system that is received by the heat exchanger. For example, Patent Document 2 includes a heat exchanger that is provided in each consumer facility and performs heat exchange between the heat medium circulating in the heat medium circulation path and the fluid to be heated in the consumer facility. Such a heat supply system is described.

特開昭６３−２３８３４２号公報JP-A-63-238342 特開２００７−１９２４５１号公報JP 2007-192451 A

特許文献１及び特許文献２に記載の熱供給システムでは、蓄熱装置での蓄熱量に応じて各消費者設備への熱媒の供給状態を調節することは行われていない。例えば、蓄熱装置での蓄熱量が多ければ各消費者が使用できる熱量も多くなるが、蓄熱装置での蓄熱量が少なければ各消費者が使用できる熱量も少なくなる。特に、熱供給システムが備える蓄熱装置が、集合住宅などに居住する複数の消費者に対して熱を一括して供給する役割を担う場合、熱を各消費者に対して公平に分配する必要があるため、蓄熱装置での蓄熱量が如何ほどかを考慮せずに各消費者設備への熱媒の供給を行うことは問題となる可能性がある。例えば、大量の熱を消費する時間帯（例えば、入浴時間帯）などは各消費者によって様々であるため、早い時間帯に熱を消費する予定の消費者は、蓄熱装置での元々の蓄熱量の多少に関わらず熱を使用できるが、遅い時間帯に熱を消費する予定の消費者が実際に熱を消費しようとしたとき、蓄熱装置での元々の蓄熱量が少なかった場合には既に蓄熱装置には熱がほとんど残っていないという不公平な事態が発生し得る。また、蓄熱装置での元々の蓄熱量が多かった場合には、蓄熱装置での蓄熱量に応じて各消費者設備への熱媒の供給状態を調節しなければ、全ての消費者が熱消費を行った後でも蓄熱装置に多量の熱が余ってしまい、太陽熱集熱器で集めた熱が無駄になる可能性もある。   In the heat supply systems described in Patent Document 1 and Patent Document 2, the supply state of the heat medium to each consumer facility is not adjusted according to the amount of heat stored in the heat storage device. For example, the amount of heat that can be used by each consumer increases if the amount of heat stored in the heat storage device is large, but the amount of heat that can be used by each consumer decreases if the amount of heat stored in the heat storage device is small. In particular, when the heat storage device provided in the heat supply system plays a role of supplying heat to a plurality of consumers living in an apartment house, etc., it is necessary to distribute the heat fairly to each consumer. Therefore, it may be a problem to supply the heat medium to each consumer facility without considering how much heat is stored in the heat storage device. For example, since the time period (for example, bathing time period) in which a large amount of heat is consumed varies depending on each consumer, the consumer who intends to consume heat in the early time period is the original amount of heat stored in the heat storage device. Heat can be used regardless of the amount of heat, but when a consumer who intends to consume heat in a later time is actually trying to consume heat, if the original amount of heat stored in the heat storage device is small, heat is already stored. An unfair situation can occur where there is little heat left in the device. Also, if the original amount of heat stored in the heat storage device was large, all consumers would consume heat unless the heat medium supply state to each consumer facility was adjusted according to the amount of heat stored in the heat storage device. There is a possibility that a large amount of heat will remain in the heat storage device even after the heat treatment, and the heat collected by the solar heat collector will be wasted.

本発明は、上記の課題に鑑みてなされたものであり、その目的は、各消費者に対して、蓄熱装置での蓄熱量に見合った熱供給を行うことができる熱供給システムを提供する点にある。   This invention is made | formed in view of said subject, The objective is providing the heat supply system which can perform the heat supply corresponding to the amount of heat storage in a heat storage apparatus with respect to each consumer. It is in.

上記目的を達成するための本発明に係る熱供給システムの特徴構成は、複数の消費者に熱を供給する熱供給システムであって、
太陽熱を集める太陽熱集熱器と、
熱媒を貯え、前記太陽熱集熱器が集めた熱を前記熱媒を用いて蓄える蓄熱装置と、
前記蓄熱装置が貯えている前記熱媒を、それぞれが熱消費装置を有する複数の消費者の消費者設備に循環可能にさせる熱媒循環路と、
前記消費者設備の夫々に設けられ、前記熱媒循環路を循環する前記熱媒と、当該消費者設備において加熱対象とする流体との間の熱交換を行う熱交換器と、
前記熱媒循環路における前記熱媒の循環状態を調節する循環状態調節装置と、
前記循環状態調節装置の動作を制御して、１日の中の特定の時間帯にのみ前記熱媒循環路に前記熱媒を循環させる運転制御装置とを備え、
前記運転制御装置は、前記熱媒循環路に前記熱媒を循環させる間の前記循環状態調節装置の動作を前記蓄熱装置での蓄熱量に応じて制御するものであって、
前記運転制御装置は、前記特定の時間帯の開始前における前記蓄熱装置での蓄熱量が多いほど、前記熱交換器に流入する前記熱媒の温度が高くなるように前記循環状態調節装置の動作を制御する点にある。 The characteristic configuration of the heat supply system according to the present invention for achieving the above object is a heat supply system for supplying heat to a plurality of consumers,
A solar collector that collects solar heat,
A heat storage device for storing a heat medium and storing the heat collected by the solar heat collector using the heat medium;
A heat medium circulation path that allows the heat medium stored in the heat storage device to be circulated to consumer equipment of a plurality of consumers each having a heat consumption device;
A heat exchanger that is provided in each of the consumer facilities and performs heat exchange between the heat medium that circulates in the heat medium circulation path and a fluid that is to be heated in the consumer facilities;
A circulation state adjusting device for adjusting a circulation state of the heat medium in the heat medium circulation path;
An operation control device that controls the operation of the circulation state adjusting device and circulates the heat medium in the heat medium circulation path only during a specific time period in one day,
The operation control device controls the operation of the circulation state adjusting device according to the amount of heat stored in the heat storage device while circulating the heat medium in the heat medium circulation path ,
The operation control device operates the circulating state adjusting device so that the temperature of the heat medium flowing into the heat exchanger increases as the amount of heat stored in the heat storage device before the start of the specific time period increases. The point is to control .

上記特徴構成によれば、運転制御装置は、蓄熱装置での蓄熱量に応じて適切な量の熱を各消費者に供給するように循環状態調節装置の動作を制御できる。例えば、蓄熱装置での蓄熱量が多いときは各消費者へ分配される熱量を相対的に多くして、蓄熱装置での蓄熱量が少ないときは各消費者へ分配される熱量を相対的に少なくするように熱媒の循環状態を調節できる。その結果、太陽熱集熱器が集めた熱が天候に応じて日々変化したとしても、その蓄熱量に応じた熱供給を行える。そして、蓄熱装置での元々の蓄熱量の多少に応じて、上記特定の時間帯において各消費者へ供給される熱量が調節されるので、上記特定の時間帯の終了時点において蓄熱装置に残存している熱が多過ぎることも無く且つ少な過ぎることもない状態が得られる。つまり、太陽熱集熱器で集めた熱が各消費者に活用されずに無駄になることもなく且つ熱が各消費者に対して不公平に配分されることもなくなる。
従って、各消費者に対して、蓄熱装置での蓄熱量に見合った熱供給を行うことができる熱供給システムを提供できる。
さらに、運転制御装置は、蓄熱装置での蓄熱量が多いほど、各消費者の熱交換器に流入する熱媒の温度を高くして、単位時間当たりに各消費者に分配される熱量を多くできる。このように、蓄熱装置での蓄熱量が多いほど各消費者に分配される熱量を多くすることで、熱媒循環路を介して各消費者への熱供給が行われる特定の時間帯の終了時点において、蓄熱装置に多量の熱が残存するような事態を避けることができる。
逆の観点から説明すると、運転制御装置は、蓄熱装置での蓄熱量が少ないほど、各消費者の熱交換器に流入する熱媒の温度を低くして、単位時間当たりに各消費者に分配される熱量を相対的に少なくする。その結果、単位時間当たりに各消費者が消費できる熱量が有効に制限されるので、単位時間当たりの蓄熱装置での蓄熱量の減少度合いが緩やかになる。つまり、特定の時間帯の何れのタイミングで消費者が熱消費を行おうとしても、特に特定の時間帯の終期であっても、蓄熱装置には消費者が使用できる熱が残存している状態を確保できる。
従って、太陽熱集熱器で集めた熱を各消費者によって有効に且つ公平に活用できる。 According to the above characteristic configuration, the operation control device can control the operation of the circulation state adjusting device so as to supply an appropriate amount of heat to each consumer according to the amount of heat stored in the heat storage device. For example, when the amount of heat stored in the heat storage device is large, the amount of heat distributed to each consumer is relatively increased, and when the amount of heat stored in the heat storage device is small, the amount of heat distributed to each consumer is relatively The circulation state of the heat medium can be adjusted so as to reduce it. As a result, even if the heat collected by the solar heat collector changes daily according to the weather, heat can be supplied according to the amount of heat stored. And since the amount of heat supplied to each consumer in the specific time zone is adjusted according to the amount of the original heat storage amount in the heat storage device, it remains in the heat storage device at the end of the specific time zone. A state is obtained in which there is neither too much heat nor too little heat. That is, the heat collected by the solar heat collector is not utilized by each consumer and is not wasted, and the heat is not unfairly distributed to each consumer.
Therefore, it is possible to provide a heat supply system that can supply heat to each consumer according to the amount of heat stored in the heat storage device.
Furthermore, the operation control device increases the amount of heat distributed to each consumer per unit time by increasing the temperature of the heat medium flowing into each consumer's heat exchanger as the amount of heat stored in the heat storage device increases. it can. In this way, the greater the amount of heat stored in the heat storage device, the greater the amount of heat distributed to each consumer, thereby ending a specific time period during which heat is supplied to each consumer via the heat medium circuit It is possible to avoid a situation in which a large amount of heat remains in the heat storage device at the time.
To explain in reverse, the operation control device distributes to each consumer per unit time by lowering the temperature of the heat medium flowing into each consumer's heat exchanger as the amount of heat stored in the heat storage device is smaller. Relatively less heat is generated. As a result, since the amount of heat that can be consumed by each consumer per unit time is effectively limited, the degree of decrease in the amount of heat stored in the heat storage device per unit time becomes moderate. In other words, regardless of the timing of a specific time zone, when the consumer tries to consume heat, the heat storage device still has heat that can be used by the consumer, especially at the end of the specific time zone. Can be secured.
Therefore, the heat collected by the solar heat collector can be effectively and fairly utilized by each consumer.

本発明に係る熱供給システムの別の特徴構成は、前記運転制御装置は、前記特定の時間帯の開始前における前記蓄熱装置での蓄熱量が多いほど、単位時間当たりに前記熱交換器に流入する前記熱媒の流量が多くなるように前記循環状態調節装置の動作を制御する点にある。   Another characteristic configuration of the heat supply system according to the present invention is that the operation control device flows into the heat exchanger per unit time as the amount of heat stored in the heat storage device before the start of the specific time period increases. The operation of the circulating state adjusting device is controlled so that the flow rate of the heat medium to be increased.

上記特徴構成によれば、運転制御装置は、蓄熱装置での蓄熱量が多いほど、単位時間当たりに熱交換器に流入する熱媒の流量を多くして、各消費者に分配される熱量を多くできる。このように、蓄熱装置での蓄熱量が多いほど各消費者に分配される熱量を多くすることで、熱媒循環路を介して各消費者への熱供給が行われる特定の時間帯の終了時点において、蓄熱装置に多量の熱が残存するような事態を避けることができる。
逆の観点から説明すると、運転制御装置は、蓄熱装置での蓄熱量が少ないほど、単位時間当たりに熱交換器に流入する熱媒の流量を少なくして、各消費者に分配される熱量を相対的に少なくする。その結果、単位時間当たりに各消費者が消費できる熱量が有効に制限されるので、単位時間当たりの蓄熱装置での蓄熱量の減少度合いが緩やかになる。つまり、特定の時間帯の何れのタイミングで消費者が熱消費を行おうとしても、特に特定の時間帯の終期であっても、蓄熱装置には消費者が使用できる熱が残存している状態を確保できる。
従って、太陽熱集熱器で集めた熱を各消費者によって有効に且つ公平に活用できる。 According to the above characteristic configuration, the operation control device increases the flow rate of the heat medium flowing into the heat exchanger per unit time as the amount of heat stored in the heat storage device increases, thereby reducing the amount of heat distributed to each consumer. You can do more. In this way, the greater the amount of heat stored in the heat storage device, the greater the amount of heat distributed to each consumer, thereby ending a specific time period during which heat is supplied to each consumer via the heat medium circuit It is possible to avoid a situation in which a large amount of heat remains in the heat storage device at the time.
In other words, the operation control device reduces the amount of heat distributed to each consumer by reducing the flow rate of the heat medium flowing into the heat exchanger per unit time as the amount of heat stored in the heat storage device is smaller. Relatively less. As a result, since the amount of heat that can be consumed by each consumer per unit time is effectively limited, the degree of decrease in the amount of heat stored in the heat storage device per unit time becomes moderate. In other words, regardless of the timing of a specific time zone, when the consumer tries to consume heat, the heat storage device still has heat that can be used by the consumer, especially at the end of the specific time zone. Can be secured.
Therefore, the heat collected by the solar heat collector can be effectively and fairly utilized by each consumer.

本発明に係る熱供給システムの更に別の特徴構成は、前記運転制御装置は、前記循環状態調節装置の動作を制御して、前記蓄熱装置から前記熱媒循環路へ流出した後であり且つ前記消費者設備に設けられる前記熱交換器に流入する前の熱媒に対して、当該熱媒よりも温度の低い熱媒を加える点にある。   Still another characteristic configuration of the heat supply system according to the present invention is that the operation control device controls the operation of the circulation state adjustment device, and flows out from the heat storage device to the heat medium circulation path. A heat medium having a temperature lower than that of the heat medium is added to the heat medium before flowing into the heat exchanger provided in the consumer facility.

上記特徴構成によれば、蓄熱装置から熱媒循環路へ流出した後の高温の熱媒と、低温の熱媒とを混合することで、各消費者へ供給するための適当な温度の熱媒が得られる。つまり、高温の熱媒が有する熱と低温の熱媒が有する熱とを共に無駄にすることなく、各消費者へ供給できる。   According to the above characteristic configuration, a high-temperature heat medium after flowing out from the heat storage device to the heat medium circuit and a low-temperature heat medium are mixed, so that the heat medium having an appropriate temperature to be supplied to each consumer. Is obtained. That is, it is possible to supply to each consumer without wasting both the heat of the high-temperature heat medium and the heat of the low-temperature heat medium.

本発明に係る熱供給システムの更に別の特徴構成は、前記運転制御装置は、前記循環状態調節装置の動作を制御して、前記蓄熱装置から前記熱媒循環路へ流出した後であり且つ前記消費者設備に設けられる前記熱交換器に流入する前の熱媒に対して、前記消費者設備に設けられる前記熱交換器から流出した後であり且つ前記蓄熱装置に流入する前の熱媒を加える点にある。   Still another characteristic configuration of the heat supply system according to the present invention is that the operation control device controls the operation of the circulation state adjustment device, and flows out from the heat storage device to the heat medium circulation path. With respect to the heat medium before flowing into the heat exchanger provided in consumer equipment, the heat medium after flowing out from the heat exchanger provided in the consumer equipment and before flowing into the heat storage device There is a point to add.

上記特徴構成によれば、蓄熱装置から熱媒循環路へ流出した後であり且つ消費者設備に設けられる熱交換器に流入する前の高温の熱媒と、消費者設備に設けられる熱交換器から流出した後であり且つ蓄熱装置に流入する前の低温の熱媒とを混合することで、各消費者へ供給するための適当な温度の熱媒が得られる。この高温の熱媒が有する熱と低温の熱媒が有する熱とは、何れも蓄熱装置で蓄えていた熱を起源とする。その結果、蓄熱装置で蓄えていた熱を無駄にすることなく、各消費者へ供給できる。   According to the above characteristic configuration, the high-temperature heat medium after flowing out from the heat storage device to the heat medium circuit and before flowing into the heat exchanger provided in the consumer equipment, and the heat exchanger provided in the consumer equipment By mixing with a low-temperature heat medium after flowing out from the heat source and before flowing into the heat storage device, a heat medium having an appropriate temperature to be supplied to each consumer can be obtained. Both the heat of the high temperature heat medium and the heat of the low temperature heat medium originate from the heat stored in the heat storage device. As a result, the heat stored in the heat storage device can be supplied to each consumer without wasting it.

熱供給システムの構成を説明する図である。It is a figure explaining the structure of a heat supply system. 熱需要と蓄熱量と熱媒の温度との時間的な変化のシミュレーション結果を示すグラフである。It is a graph which shows the simulation result of the temporal change with the heat demand, the heat storage amount, and the temperature of the heat medium. 比較例として熱需要と蓄熱量と熱媒の温度との時間的な変化のシミュレーション結果を示すグラフである。It is a graph which shows the simulation result of the temporal change with the heat demand, the amount of heat storage, and the temperature of a heat medium as a comparative example. 比較例として熱需要と蓄熱量と熱媒の温度との時間的な変化のシミュレーション結果を示すグラフである。It is a graph which shows the simulation result of the temporal change with the heat demand, the amount of heat storage, and the temperature of a heat medium as a comparative example. 熱交換器に流入する湯水（熱媒）の流量を変化させたときの、蓄熱装置での蓄熱量の低下度合いのシミュレーション結果のグラフである。It is a graph of the simulation result of the fall degree of the thermal storage amount in a thermal storage apparatus when changing the flow volume of the hot water (heat medium) which flows into a heat exchanger. 配管送り温度を７５℃とした場合の、熱需要と蓄熱量と熱媒の温度との時間的な変化のシミュレーション結果を示すグラフである。It is a graph which shows the simulation result of the temporal change with the heat demand, the amount of heat storage, and the temperature of a heat medium when piping feed temperature is 75 degreeC. 配管送り温度を４５℃とした場合の、熱需要と蓄熱量と熱媒の温度との時間的な変化のシミュレーション結果を示すグラフである。It is a graph which shows the simulation result of the temporal change with the heat demand, the amount of heat storage, and the temperature of a heat medium when piping feed temperature is 45 degreeC. 熱交換器に流入する湯水（熱媒）の温度を変化させたときの、蓄熱装置での蓄熱量の低下度合いのシミュレーション結果のグラフである。It is a graph of the simulation result of the fall degree of the thermal storage amount in a thermal storage apparatus when changing the temperature of the hot water (heat medium) which flows into a heat exchanger. 別の熱供給システムの構成を説明する図である。It is a figure explaining the structure of another heat supply system.

＜第１実施形態＞
図１は、第１実施形態の熱供給システムＳ１（Ｓ）の構成を説明する図である。
図１に示す熱供給システムＳ１は、太陽熱集熱器１と蓄熱装置２と熱媒循環路３と循環状態調節装置Ｃとそれら各装置の動作を制御する運転制御装置４とを備え、集合住宅などに居住する複数の消費者に対して熱を供給するシステムである。特に、本実施形態の熱供給システムＳ１は、太陽熱集熱器１で集められた熱を、複数の消費者によって有効且つ公平に活用させるために、後述する蓄熱装置２から熱交換器１３を介して各消費者に供給される熱を、その蓄熱装置２での蓄熱量に応じて調節する。
以下の説明では、先ず、熱供給システムＳ１の構成及び熱交換器１３の熱交換能力について記載し、その後、各消費者に対して供給される熱量を調節する手法について記載する。 <First Embodiment>
Drawing 1 is a figure explaining the composition of heat supply system S1 (S) of a 1st embodiment.
A heat supply system S1 shown in FIG. 1 includes a solar heat collector 1, a heat storage device 2, a heat medium circulation path 3, a circulation state adjustment device C, and an operation control device 4 that controls the operation of each of these devices. It is a system that supplies heat to a plurality of consumers living in the city. In particular, the heat supply system S1 of the present embodiment uses the heat collected by the solar heat collector 1 through a heat exchanger 13 from the heat storage device 2 described later in order to effectively and fairly utilize the heat collected by a plurality of consumers. The heat supplied to each consumer is adjusted according to the amount of heat stored in the heat storage device 2.
In the following description, first, the configuration of the heat supply system S1 and the heat exchange capability of the heat exchanger 13 will be described, and then a method for adjusting the amount of heat supplied to each consumer will be described.

太陽熱集熱器１は、太陽熱（太陽からの熱エネルギー）を集める装置である。太陽熱集熱器１が集めた熱は蓄熱装置２に蓄えられる。太陽熱集熱器１と蓄熱装置２との間には熱媒としての水又は不凍液などが循環する集熱用熱媒循環路７が設けられる。集熱用熱媒循環路７の途中に設けたポンプＰ２を動作させることで集熱用熱媒循環路７の内部の熱媒の循環が行われる。熱媒は、太陽熱集熱器１へと流入し、そして太陽熱集熱器１で加熱された後、太陽熱集熱器１から流出して蓄熱装置２へ至る。加えて、蓄熱装置２の内部の熱交換部２ａでは、集熱用熱媒循環路７を通流する熱媒と蓄熱装置２に蓄えられている熱媒とが熱交換可能に構成されている。その結果、太陽熱集熱器１で集められた熱は蓄熱装置２に蓄えられる。通常、日の出時刻付近から日没時刻付近までの間、太陽熱集熱器１は太陽熱を集めて蓄熱装置２へ熱を供給できる。   The solar heat collector 1 is a device that collects solar heat (heat energy from the sun). The heat collected by the solar heat collector 1 is stored in the heat storage device 2. Between the solar heat collector 1 and the heat storage device 2, a heat collecting heat medium circulation path 7 in which water or antifreeze as a heat medium circulates is provided. The pump P2 provided in the middle of the heat collecting heat medium circulation path 7 is operated to circulate the heat medium inside the heat collecting heat medium circulation path 7. The heat medium flows into the solar heat collector 1 and is heated by the solar heat collector 1, and then flows out of the solar heat collector 1 and reaches the heat storage device 2. In addition, in the heat exchange part 2a inside the heat storage device 2, the heat medium flowing through the heat collecting heat medium circulation path 7 and the heat medium stored in the heat storage device 2 are configured to be able to exchange heat. . As a result, the heat collected by the solar heat collector 1 is stored in the heat storage device 2. Usually, the solar heat collector 1 can collect solar heat and supply heat to the heat storage device 2 from around the sunrise time to around the sunset time.

蓄熱装置２は、水などの熱媒を用いて熱を蓄える。蓄熱装置２には、図１に示すように、貯えられている水（湯水）を蓄熱装置２の外部に通流させる熱媒循環路３が接続されている。以下の説明では、蓄熱装置２に貯えられ、蓄熱装置２から熱媒循環路３へ供給されて循環される熱媒のことを「湯水」と記載する。熱媒循環路３の途中には複数の消費者の消費者設備１０が順に接続されているので、蓄熱装置２が貯えている湯水は熱媒循環路３によって複数の消費者設備１０に循環供給されることになる。各消費者設備１０は、例えば、集合住宅の各戸に設けられる設備に対応する。つまり、熱媒循環路３は、蓄熱装置２が貯えている湯水を、それぞれが集合住宅の各戸に設けられている複数の消費者設備１０に循環させるものである。具体的には、熱媒循環路３は、蓄熱装置２から出た湯水が各消費者設備１０へ流入するまでの間に流れる往路３ａと、各消費者設備１０から出た湯水が蓄熱装置２へ戻るまでの間に流れる復路３ｂとに分かれる。熱媒循環路３の往路３ａには、湯水の流量を設定値に調節する定流量弁Ｖ１が設けられている。各消費者設備１０は定流量弁Ｖ１より下流側の熱媒循環路３に接続されているので、各消費者設備１０へ流れ込む湯水の流量は定流量弁Ｖ１によって調節される。以上のように、ポンプＰ１と定流量弁Ｖ１とは、熱媒循環路３における湯水の循環状態を調節する循環状態調節装置Ｃとして機能し、運転制御装置４の動作制御を受ける。   The heat storage device 2 stores heat using a heat medium such as water. As shown in FIG. 1, the heat storage device 2 is connected to a heat medium circulation path 3 that allows stored water (hot water) to flow outside the heat storage device 2. In the following description, the heat medium stored in the heat storage device 2 and supplied to the heat medium circulation path 3 from the heat storage device 2 and circulated is referred to as “hot water”. Since a plurality of consumer equipments 10 are sequentially connected in the middle of the heat medium circulation path 3, hot water stored in the heat storage device 2 is circulated and supplied to the plurality of consumer equipments 10 through the heat medium circulation path 3. Will be. Each consumer equipment 10 corresponds to, for example, equipment provided in each house of the apartment house. That is, the heat-medium circulation path 3 circulates the hot water stored in the heat storage device 2 to a plurality of consumer equipments 10 each provided in each door of the apartment house. Specifically, the heat medium circulation path 3 includes a forward path 3a that flows until the hot water discharged from the heat storage device 2 flows into each consumer facility 10, and the hot water discharged from each consumer facility 10 is stored in the heat storage device 2. It is divided into a return path 3b that flows until it returns. A constant flow valve V1 that adjusts the flow rate of hot water to a set value is provided in the forward path 3a of the heat medium circulation path 3. Since each consumer equipment 10 is connected to the heat medium circulation path 3 on the downstream side of the constant flow valve V1, the flow rate of hot water flowing into each consumer equipment 10 is adjusted by the constant flow valve V1. As described above, the pump P <b> 1 and the constant flow valve V <b> 1 function as the circulation state adjustment device C that adjusts the circulation state of the hot water and the water in the heat medium circulation path 3, and receive operation control of the operation control device 4.

蓄熱装置２に貯えられている湯水の温度は温度センサＴ１で測定される。温度センサＴ１の測定結果は、収集手段５を用いて収集し、運転制御装置４が読み出し可能に記憶手段６に記憶しておくこともできる。本実施形態では、蓄熱装置２の内部で湯水は温度成層を形成しておらず、ほぼ均一になっているものとする。従って、温度センサＴ１で測定される温度が、蓄熱装置２から熱媒循環路３へ供給されて循環される湯水の温度となる。   The temperature of the hot water stored in the heat storage device 2 is measured by the temperature sensor T1. The measurement result of the temperature sensor T1 can be collected using the collecting means 5 and stored in the storage means 6 so that the operation control device 4 can read it. In the present embodiment, it is assumed that the hot water does not form a temperature stratification inside the heat storage device 2 and is substantially uniform. Therefore, the temperature measured by the temperature sensor T1 is the temperature of hot water supplied from the heat storage device 2 to the heat medium circulation path 3 and circulated.

更に、熱媒循環路３には、複数の消費者設備１０に向けて分岐する複数の往路３ａよりも上流側（即ち、分岐前の熱媒循環路３）と、複数の消費者設備１０から帰還した複数の復路３ｂの合流箇所よりも下流側（即ち、合流後の熱媒循環路３）とを接続する接続路３ｃとが設けられている。接続路３ｃには、流量調節弁Ｖ２が設けられている。そして、運転制御装置４は、流量調節弁Ｖ２の動作を制御して、蓄熱装置２から熱媒循環路３へ流出した後であり且つ消費者設備１０に設けられる熱交換器１３に流入する前の湯水に対して、その湯水よりも温度の低い水を加える。特に本実施形態では、運転制御装置４は、流量調節弁Ｖ２の動作を制御して、蓄熱装置２から熱媒循環路３へ流出した後であり且つ消費者設備１０に設けられる熱交換器１３に流入する前の湯水に対して、消費者設備１０に設けられる熱交換器１３から流出した後であり且つ蓄熱装置２に流入する前の湯水を加える。   Further, the heating medium circulation path 3 includes an upstream side (that is, the heating medium circulation path 3 before branching) branching toward the plurality of consumer equipments 10 and a plurality of consumer equipments 10. A connection path 3c is provided to connect the downstream side (that is, the heat medium circulation path 3 after merging) from the merging point of the plurality of returned paths 3b that have returned. A flow rate adjusting valve V2 is provided in the connection path 3c. Then, the operation control device 4 controls the operation of the flow rate control valve V2 and flows out from the heat storage device 2 to the heat medium circulation path 3 and before flowing into the heat exchanger 13 provided in the consumer equipment 10. To the hot water, add water having a temperature lower than that of the hot water. In particular, in the present embodiment, the operation control device 4 controls the operation of the flow rate control valve V <b> 2 and flows out from the heat storage device 2 to the heat medium circulation path 3 and is provided in the consumer facility 10. The hot water before flowing into the heat storage device 2 after being flowed out from the heat exchanger 13 provided in the consumer equipment 10 is added to the hot water before flowing into the heat storage device 10.

具体的には、運転制御装置４が流量調節弁Ｖ２の開度を調節することで、複数の消費者設備１０から合流した後の比較的低温の湯水が流れる復路３ｂから、蓄熱装置２に貯えられている比較的高温の湯水が流れる往路３ａに接続路３ｃを介して流入する湯水の量が調節される。つまり、運転制御装置４が流量調節弁Ｖ２の開度を調節することで、熱媒循環路３を介して各消費者設備１０の熱交換器１３に供給される湯水の温度が調節される。この温度調節後の湯水の温度は温度センサＴ２で計測可能であり、その計測結果は運転制御装置４に伝達される。従って、運転制御装置４は、温度センサＴ２で計測される湯水の温度が所望の温度となるように、流量調節弁Ｖ２の開度を調節できる。このように、流量調節弁Ｖ２は、熱媒循環路３における湯水の循環状態を調節する循環状態調節装置Ｃとして機能している。   Specifically, the operation control device 4 adjusts the opening degree of the flow rate control valve V <b> 2 to store in the heat storage device 2 from the return path 3 b through which a relatively low temperature hot water after joining from the plurality of consumer equipments 10 flows. The amount of hot water flowing into the forward path 3a through which the relatively hot hot water flows through the connection path 3c is adjusted. That is, the temperature of hot water supplied to the heat exchanger 13 of each consumer equipment 10 via the heat medium circulation path 3 is adjusted by the operation control device 4 adjusting the opening degree of the flow rate control valve V2. The temperature of the hot water after the temperature adjustment can be measured by the temperature sensor T2, and the measurement result is transmitted to the operation control device 4. Therefore, the operation control apparatus 4 can adjust the opening degree of the flow rate control valve V2 so that the temperature of the hot water measured by the temperature sensor T2 becomes a desired temperature. Thus, the flow rate adjustment valve V2 functions as a circulation state adjustment device C that adjusts the circulation state of the hot and cold water in the heat medium circulation path 3.

次に、消費者設備１０の構成について説明する。
消費者設備１０は、熱媒循環路３を通流する湯水と消費者設備１０の内部で供給される低温の給水とが熱交換可能な熱交換器１３を有している。具体的には、熱交換器１３には熱媒循環路３の往路３ａが引き込まれ、熱交換器１３から出た部分が熱媒循環路３の復路３ｂとなる。消費者設備１０が有する熱消費装置１１には、給水が熱交換器１３で加熱された後に得られる湯水が供給される。その際、必要に応じて、熱交換器１３で加熱された後に得られる湯水に対してミキシングユニット１４で給水が加えられた上で、或いは、熱交換器１３で加熱された後の湯水に対して熱源機１２で更に加熱された上で熱消費装置１１に供給される。熱源機１２としては、例えばガスなどの燃料を燃焼した際の燃焼熱を利用する湯沸器などを利用できる。 Next, the configuration of the consumer equipment 10 will be described.
The consumer equipment 10 has a heat exchanger 13 that can exchange heat between hot water flowing through the heat medium circulation path 3 and low-temperature water supplied inside the consumer equipment 10. Specifically, the forward path 3 a of the heat medium circulation path 3 is drawn into the heat exchanger 13, and the part exiting from the heat exchanger 13 becomes the return path 3 b of the heat medium circulation path 3. Hot water obtained after the feed water is heated by the heat exchanger 13 is supplied to the heat consuming device 11 of the consumer facility 10. At that time, if necessary, the hot water obtained after being heated by the heat exchanger 13 is added to the hot water by the mixing unit 14 or the hot water after being heated by the heat exchanger 13. After being further heated by the heat source unit 12, it is supplied to the heat consuming device 11. As the heat source unit 12, for example, a water heater that uses combustion heat when a fuel such as gas is burned can be used.

消費者設備１０において、熱交換器１３に引き込まれる熱媒循環路３の往路３ａの部分に湯水の流入温度を測定する流入温度センサＴｉｎと湯水の流量を測定する流量計Ｍとが設けられ、熱交換器１３から引き出された熱媒循環路３の復路３ｂの部分に湯水の流出温度を測定する流出温度センサＴｏｕｔが設けられている。流入温度センサＴｉｎ、流量計Ｍ及び流出温度センサＴｏｕｔの測定結果は、設定タイミング毎に収集手段５によって収集される。ここで、熱交換器１３への湯水の流入温度及び流出温度の間の温度差と流量との積を導出すると、熱媒循環路３を通流する湯水が消費者設備１０の熱交換器１３で失った熱量、即ち、消費者の熱需要となる。つまり、収集手段５が設定タイミング毎に収集する流入温度センサＴｉｎ、流量計Ｍ及び流出温度センサＴｏｕｔの測定結果は、熱需要に関する情報と言える。更に、運転制御装置４は、収集手段５が設定タイミング毎に収集した上記熱需要に関する情報を記憶手段６に記憶させることができる。操作部１５は、熱消費装置１１の予約運転に関する設定情報（例えば、風呂湯張り時刻、湯温、湯量など）を操作入力するためのものである。   In the consumer facility 10, an inflow temperature sensor Tin that measures the inflow temperature of hot water and a flow meter M that measures the flow rate of hot water are provided in the forward path 3 a portion of the heat medium circulation path 3 drawn into the heat exchanger 13. An outflow temperature sensor Tout for measuring the outflow temperature of the hot water is provided in a portion of the return path 3b of the heat medium circulation path 3 drawn out from the heat exchanger 13. The measurement results of the inflow temperature sensor Tin, the flow meter M, and the outflow temperature sensor Tout are collected by the collection unit 5 at each set timing. Here, when the product of the temperature difference between the inflow temperature and the outflow temperature of hot water to the heat exchanger 13 and the flow rate is derived, the hot water flowing through the heat medium circulation path 3 is converted into the heat exchanger 13 of the consumer equipment 10. This is the amount of heat lost by the consumer, that is, the heat demand of the consumer. That is, it can be said that the measurement results of the inflow temperature sensor Tin, the flow meter M, and the outflow temperature sensor Tout collected by the collection unit 5 at each set timing are information on heat demand. Furthermore, the operation control apparatus 4 can store in the storage unit 6 information regarding the heat demand collected by the collection unit 5 at each set timing. The operation unit 15 is for operating and inputting setting information related to the reserved operation of the heat consuming apparatus 11 (for example, bathing time, hot water temperature, hot water amount, etc.).

運転制御装置４は、収集手段５が設定タイミング毎に収集した上記熱需要に関する情報を記憶手段６にそのまま（即ち、流入温度センサＴｉｎ、流量計Ｍ及び流出温度センサＴｏｕｔの測定結果のまま）記憶させておくか、或いは、上述したように消費者の熱需要を逐次導出して、その結果を記憶手段６に記憶させておくことができる。運転制御装置４、収集手段５及び記憶手段６は、コンピュータなどの情報処理装置を用いて実現できる。   The operation control device 4 stores the information on the heat demand collected by the collecting unit 5 at each set timing in the storage unit 6 as it is (that is, as measured by the inflow temperature sensor Tin, the flow meter M, and the outflow temperature sensor Tout). Alternatively, the consumer's heat demand can be derived sequentially as described above, and the result can be stored in the storage means 6. The operation control device 4, the collection unit 5, and the storage unit 6 can be realized using an information processing device such as a computer.

図２〜図４は、消費者設備１０における熱交換器１３の熱交換能力を変化させた場合の、時刻１８時から時刻２４時の間における熱需要と蓄熱量と湯水の温度との時間的な変化のシミュレーション結果を示すグラフである。尚、図３及び図４は、図２の比較例として示す。図２〜図４において、複数の消費者による合計の予測熱需要を「黒三角印」で示し、温度センサＴ２で測定される湯水の温度（即ち、配管送り温度）のシミュレーション結果を「白四角印」で示し、蓄熱装置２での蓄熱量のシミュレーション結果を「黒丸印」で示す。   2 to 4 show temporal changes in heat demand, heat storage amount, and hot water temperature from 18:00 to 24:00 when the heat exchange capacity of the heat exchanger 13 in the consumer facility 10 is changed. It is a graph which shows the simulation result. 3 and 4 are shown as a comparative example of FIG. 2 to 4, the total predicted heat demand by a plurality of consumers is indicated by “black triangles”, and the simulation result of the temperature of the hot water (that is, the pipe feed temperature) measured by the temperature sensor T <b> 2 is represented by “white squares”. "," And the simulation results of the heat storage amount in the heat storage device 2 are indicated by "black circles".

図２〜図４に示すシミュレーション結果は、具体的には、１日の中の特定の循環時間帯の間、基準蓄熱量を蓄えている蓄熱装置２から湯水を基準流量で熱媒循環路３に継続的に供給して循環させ、それにより熱交換器１３での熱交換に伴う湯水の温度低下が消費者による予測熱需要に対応して発生すると想定した場合の、蓄熱量と湯水の温度との時間的な変化のシミュレーション結果のグラフである。本実施形態において、上記循環時間帯は、後述するように時刻１８時から時刻２３時２０分の間である。また、上記基準蓄熱量は、１日に太陽熱集熱器１から蓄熱装置２に蓄熱されると予測される蓄熱量のことであり、本実施形態では３００ｋＷｈである。更に、上記基準流量は、熱媒循環路３から各熱交換器１３に流入する湯水の流量であり、本実施形態では３リットル／分としている。尚、各熱交換器１３は、熱媒循環路３に設けられる定流量弁Ｖ１から見て並列に接続されているため、熱交換器１３が例えばＸ台接続されているならば、定流量弁Ｖ１では３×Ｘ（リットル／分）の湯水を通流させればよい。
以下に、熱需要（予測熱需要）、湯水の温度（即ち、配管送り温度）のシミュレーション結果、蓄熱装置２での蓄熱量のシミュレーション結果について具体的に説明する。 The simulation results shown in FIG. 2 to FIG. 4 show that the heat medium circulation path 3 at a reference flow rate of hot water from the heat storage device 2 storing the reference heat storage amount during a specific circulation time zone in one day. The amount of stored heat and the temperature of hot water when it is assumed that a decrease in the temperature of hot water accompanying heat exchange in the heat exchanger 13 occurs in response to the predicted heat demand by the consumer. It is a graph of the simulation result of a time change. In the present embodiment, the circulation time zone is between time 18:00 and time 23:20, as will be described later. The reference heat storage amount is a heat storage amount that is predicted to be stored in the heat storage device 2 from the solar heat collector 1 in one day, and is 300 kWh in this embodiment. Further, the reference flow rate is a flow rate of hot water flowing into the heat exchangers 13 from the heat medium circulation path 3, and is 3 liters / minute in this embodiment. Since each heat exchanger 13 is connected in parallel as viewed from the constant flow valve V1 provided in the heat medium circulation path 3, if the heat exchanger 13 is connected in X units, for example, a constant flow valve In V1, 3 × X (liter / minute) hot water may be passed.
Below, the simulation result of the heat demand (predicted heat demand), the temperature of hot water (that is, the pipe feed temperature) and the simulation result of the heat storage amount in the heat storage device 2 will be specifically described.

図２〜図４において黒三角印で示す熱需要は、複数の消費者による合計の予測熱需要である。上述のように、運転制御装置４は、各消費者設備１０の熱交換器１３への湯水の流入温度及び流出温度の間の温度差と流量との積を導出することで、各消費者の過去の熱需要を知ることができる。従って、運転制御装置４は、設定タイミング毎に収集された過去の熱需要に関する情報を参照して、各消費者の将来の予測熱需要を導出でき、更に、複数の消費者による合計の予測熱需要を導出できる。   The heat demand indicated by black triangles in FIGS. 2 to 4 is the total predicted heat demand by a plurality of consumers. As described above, the operation control device 4 derives the product of the temperature difference between the inflow temperature and the outflow temperature of the hot water to the heat exchanger 13 of each consumer facility 10 and the flow rate, and thereby the flow rate of each consumer. You can know the past heat demand. Accordingly, the operation control device 4 can derive the predicted heat demand of each consumer by referring to the information on the past heat demand collected at each set timing, and further can calculate the total predicted heat by a plurality of consumers. Demand can be derived.

図２〜図４において黒丸印で示す蓄熱量は、蓄熱装置２に蓄えられている熱量のシミュレーション結果である。図示するように、循環時間帯が開始されて各消費者での熱消費が開始されるにつれて、蓄熱装置２での蓄熱量は減少する。尚、運転制御装置４は、実際の蓄熱装置２での蓄熱量を、温度センサＴ１で測定される温度と、蓄熱装置２に貯えられている既知の湯水の量との積から導出することもできる。   The heat storage amount indicated by black circles in FIGS. 2 to 4 is a simulation result of the heat amount stored in the heat storage device 2. As shown in the drawing, the heat storage amount in the heat storage device 2 decreases as the circulation time period starts and heat consumption by each consumer starts. The operation control device 4 may derive the actual heat storage amount in the heat storage device 2 from the product of the temperature measured by the temperature sensor T1 and the amount of known hot water stored in the heat storage device 2. it can.

図２〜図４において白四角印で示す配管送り温度は、温度センサＴ２で測定される部位での湯水の温度のシミュレーション結果である。本実施形態では、循環時間帯の開始前において蓄熱装置２に７５℃の湯水が貯えられている状態を想定している。そして、運転制御装置４が流量調節弁Ｖ２の開度を制御することで、温度センサＴ２で測定される部位での湯水の温度を５０℃に調節し、その５０℃の湯水を消費者設備１０の熱交換器１３へ流入させる状態を想定している。例えば、図２に示す例では、時刻１８時から時刻２０時頃までは、運転制御装置４によって、蓄熱装置２に貯えられている７５℃の湯水が、５０℃の湯水へと温度低下された後で各消費者設備１０へと供給される。   The pipe feed temperature indicated by white squares in FIGS. 2 to 4 is a simulation result of the temperature of hot water at the site measured by the temperature sensor T2. In the present embodiment, it is assumed that 75 ° C. hot water is stored in the heat storage device 2 before the start of the circulation time period. Then, the operation control device 4 controls the opening degree of the flow control valve V2, thereby adjusting the temperature of the hot water at the site measured by the temperature sensor T2 to 50 ° C., and the 50 ° C. hot water is supplied to the consumer equipment 10. The state which is made to flow in into the heat exchanger 13 is assumed. For example, in the example shown in FIG. 2, from the time 18:00 to the time around 20:00, the temperature of the 75 ° C. hot water stored in the heat storage device 2 is lowered to 50 ° C. hot water by the operation control device 4. It is supplied to each consumer equipment 10 later.

その後、熱媒循環路３において湯水の循環を開始すると、蓄熱装置２には熱媒循環路３の復路３ｂを介して低温の湯水が帰還するため、蓄熱装置２に貯えられている湯水の温度は徐々に低下する。但し、この時刻１８時から時刻２０時頃までは、蓄熱装置２に貯えられている湯水の温度は未だ５０℃未満にまでは低下していないため、流量調節弁Ｖ２を用いた温度調節後の湯水の温度（即ち、図２に示す配管送り温度）は５０℃に調節できる。ところが、時刻２０時を越えると、蓄熱装置２に貯えられている湯水の温度が５０℃未満に低下するため、運転制御装置４は、最終的に流量調節弁Ｖ２を閉止しても、温度センサＴ２で測定される部位での湯水の温度を５０℃に調節できなくなる。そのため、運転制御装置４は、時刻２０時を越えると、流量調節弁Ｖ２を用いた温度調節を行わず、蓄熱装置２に貯えられている湯水をそのままの温度で各消費者設備１０の熱交換器１３に流入させるようにする。つまり、時刻２０時を越えると、蓄熱装置２に貯えられている湯水の温度が図２に示す配管送り温度となり、その温度は徐々に低下する。   Thereafter, when hot water circulation starts in the heat medium circulation path 3, the low temperature hot water returns to the heat storage device 2 via the return path 3 b of the heat medium circulation path 3, so the temperature of the hot water stored in the heat storage device 2 Gradually decreases. However, from this time 18:00 to around 20:00, the temperature of the hot water stored in the heat storage device 2 has not yet decreased to less than 50 ° C. Therefore, after the temperature adjustment using the flow rate control valve V2 The temperature of hot water (that is, the pipe feed temperature shown in FIG. 2) can be adjusted to 50 ° C. However, since the temperature of the hot water stored in the heat storage device 2 falls below 50 ° C. after the time 20:00, the operation control device 4 does not stop the flow rate control valve V2, but the temperature sensor The temperature of hot water at the site measured at T2 cannot be adjusted to 50 ° C. Therefore, when the operation control device 4 exceeds 20:00, the temperature control using the flow rate control valve V2 is not performed, and the hot water stored in the heat storage device 2 is exchanged for heat at each consumer equipment 10 at the same temperature. To flow into the vessel 13. That is, when the time exceeds 20:00, the temperature of the hot water stored in the heat storage device 2 becomes the pipe feed temperature shown in FIG. 2, and the temperature gradually decreases.

〔循環時間帯〕
次に、熱媒循環路３に湯水を循環させる循環時間帯をどのように決定するのかについて説明する。
上述のように、通常、太陽熱集熱器１は日の出時刻付近から日没時刻付近までの間に太陽熱を集め、その熱が蓄熱装置２へ供給されて蓄熱される。これに対して、図２〜図４の熱需要のグラフ（黒三角印）で示したように、通常、消費者が熱を大量に消費するのは夕方から夜の時間帯である。従って、昼間の時間帯に太陽熱集熱器１で集められた熱を蓄熱装置２に蓄熱し、それと同時に蓄熱装置２から熱媒循環路３へと湯水の循環を常時行わせていると、多くの消費者が夜の時間帯に熱消費を行うまでの間、熱媒循環路３を循環通流する湯水はほとんど消費されることなく単に放熱されるだけとなる。そこで、本実施形態では、各消費者が１日の中で熱を大量に消費しようとする特定の時間帯のみ湯水を循環させることで、余分な放熱ロスの発生を回避することを想定している。 [Circulation time zone]
Next, how to determine the circulation time zone for circulating hot water in the heat medium circulation path 3 will be described.
As described above, usually, the solar heat collector 1 collects solar heat between the sunrise time and the sunset time, and the heat is supplied to the heat storage device 2 to be stored. On the other hand, as shown in the graphs of heat demand in FIGS. 2 to 4 (black triangle marks), it is usually during the evening to night time that consumers consume a large amount of heat. Therefore, when the heat collected by the solar heat collector 1 during the daytime is stored in the heat storage device 2 and at the same time, the hot water is constantly circulated from the heat storage device 2 to the heat medium circulation path 3. Until the consumer consumes heat during the night time, the hot water circulating through the heat medium circulation path 3 is merely dissipated without being consumed. Therefore, in this embodiment, it is assumed that each consumer avoids the occurrence of extra heat loss by circulating hot water only during a specific time period when a large amount of heat is to be consumed during the day. Yes.

本実施形態において、熱媒循環路３に湯水を循環させる循環時間帯の開始タイミング、即ち、循環開始タイミングは、複数の消費者による合計の熱需要が設定量以上に増加するタイミングに対応する。つまり、熱媒循環路３での湯水循環を開始させる循環開始タイミングは、複数の消費者における過去の熱需要に関する情報を参照して導出される、複数の消費者による合計の予測熱需要が設定量以上に増加するタイミングに決定される。このように、複数の消費者における過去の熱需要に関する情報を参照することで、実際に複数の消費者の熱需要が大きくなるタイミングを正確に把握できる。また、熱媒循環路３に湯水を循環させる循環時間帯の終了タイミング、即ち、循環停止タイミングは、複数の消費者による合計の熱需要が設定量未満に低下するタイミングに対応する。つまり、熱媒循環路３での湯水循環を開始させる循環停止タイミングは、複数の消費者における過去の熱需要に関する情報を参照して導出される、複数の消費者による合計の予測熱需要が設定量未満に低下するタイミングに決定される。   In the present embodiment, the start timing of the circulation time zone in which hot water is circulated in the heat medium circulation path 3, that is, the circulation start timing, corresponds to the timing at which the total heat demand by a plurality of consumers increases beyond a set amount. In other words, the circulation start timing for starting the hot water circulation in the heat medium circulation path 3 is derived by referring to the information on the past heat demand of the plurality of consumers, and the total predicted heat demand by the plurality of consumers is set. The timing is determined to increase beyond the amount. In this way, by referring to information related to past heat demands of a plurality of consumers, it is possible to accurately grasp the timing at which the heat demands of the plurality of consumers actually increase. In addition, the end timing of the circulation time zone in which hot water is circulated in the heat medium circulation path 3, that is, the circulation stop timing, corresponds to the timing at which the total heat demand by a plurality of consumers decreases below a set amount. That is, the circulation stop timing for starting the hot water circulation in the heat medium circulation path 3 is derived by referring to the information on the past heat demand of the plurality of consumers, and the total predicted heat demand by the plurality of consumers is set. It is determined at the timing when it falls below the amount.

図２〜図４に示す例では、複数の消費者による合計の予測熱需要が設定量（図中において一点鎖線で示す）以上に増加するのは、時刻１８時になるタイミングである。従って、循環時間帯の開始タイミングは時刻１８時に決定される。また、複数の消費者による合計の予測熱需要が設定量未満に低下するのは、時刻２３時２０分になるタイミングである。従って、循環時間帯の終了タイミングは時刻２３時２０分に決定される。つまり、１８時から２３時２０分の時間帯を、蓄熱装置２から熱媒循環路３へ湯水を供給して循環させる上記特定の時間帯とする。この設定量のレベルは、運転制御装置４が適宜設定可能である。例えば、この設定量は、複数の消費者による１日の合計の予測熱需要量に対して設定割合となるレベルに設定できる。このように設定すると、各消費者が１日の中で熱を大量に消費しようとしたタイミングに合わせて蓄熱装置２から熱媒循環路３へ湯水を供給して循環させることができ、その結果、太陽熱集熱器１で集めた熱を、余分な放熱ロスの発生を回避しながら蓄熱装置２から各消費者へ有効に供給できる。   In the example shown in FIGS. 2 to 4, the total predicted heat demand by a plurality of consumers increases more than a set amount (indicated by a one-dot chain line in the figure) at the timing of 18:00. Therefore, the start timing of the circulation time zone is determined at 18:00. In addition, the total predicted heat demand by a plurality of consumers falls below the set amount at the timing of time 23:20. Therefore, the end timing of the circulation time zone is determined at time 23:20. That is, the time zone from 18 o'clock to 23:20 is set as the specific time zone in which hot water is supplied from the heat storage device 2 to the heat medium circulation path 3 for circulation. The operation control device 4 can appropriately set the level of the set amount. For example, this set amount can be set to a level that is a set ratio with respect to the predicted daily heat demand of a plurality of consumers. If it sets in this way, each consumer can supply hot water to the heat-medium circulation path 3 from the heat storage apparatus 2 according to the timing which consumes a lot of heat in one day, and can circulate it, As a result The heat collected by the solar heat collector 1 can be effectively supplied from the heat storage device 2 to each consumer while avoiding the occurrence of extra heat dissipation loss.

〔熱交換器の熱交換能力〕
以下に、図２〜図４に示すシミュレーション結果を参照して、熱交換器１３の熱交換能力をどのように設定すれば良いのかについて説明する。
本実施形態において、熱交換器１３は、熱媒循環路３を循環する湯水から消費者設備１０において加熱対象とする流体が受領することができる熱量の最大を制限する受領熱量制限手段として構成されている。具体的には、熱交換器１３の熱交換能力は、特定の循環時間帯の間、基準蓄熱量を蓄えている蓄熱装置２から湯水を基準流量で熱媒循環路３に継続的に供給して循環させ、それにより熱交換器１３での熱交換に伴う湯水の温度低下が消費者による予測熱需要に対応して発生すると想定した場合に、特定の循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度が基準温度範囲内となるように設定されることが好ましい。 [Heat exchange capacity of heat exchanger]
Hereinafter, how to set the heat exchange capacity of the heat exchanger 13 will be described with reference to the simulation results shown in FIGS.
In the present embodiment, the heat exchanger 13 is configured as received heat amount limiting means for limiting the maximum amount of heat that can be received by the fluid to be heated in the consumer facility 10 from the hot water circulating in the heat medium circulation path 3. ing. Specifically, the heat exchange capacity of the heat exchanger 13 is such that hot water is continuously supplied to the heat medium circulation path 3 at a reference flow rate from the heat storage device 2 storing the reference heat storage amount during a specific circulation time period. The heat storage device 2 at the end of a specific circulation time period when it is assumed that the temperature drop of the hot water accompanying the heat exchange in the heat exchanger 13 occurs in response to the predicted heat demand by the consumer. It is preferable that the temperature of hot and cold water that can be supplied and circulated to the heat medium circulation path 3 is set within the reference temperature range.

そこで、本実施形態では、上述したように、循環時間帯を時刻１８時から２３時２０分とし、基準蓄熱量を３００ｋＷｈとし、基準流量を３リットル／分とし、本例では基準温度範囲を２２℃〜２５℃とした場合において、図中に黒三角印で示す消費者による予測熱需要に対応して熱交換器１３での熱交換に伴う湯水の温度低下が発生すると想定した場合に、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度がどのような値になるのかを示すシミュレーション結果を得た。そして、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度（シミュレーション結果）が、上記基準温度範囲内にあるか否かを判定して、熱交換器１３の熱交換能力がどの程度であれば良いのかを判定した。   Therefore, in the present embodiment, as described above, the circulation time zone is from 18:00 to 23:20, the reference heat storage amount is 300 kWh, the reference flow rate is 3 liters / minute, and in this example, the reference temperature range is 22 In the case where the temperature is set to 25 ° C. to 25 ° C., when it is assumed that the temperature drop of the hot water accompanying the heat exchange in the heat exchanger 13 occurs in response to the predicted heat demand by the consumer indicated by black triangles in the figure, the circulation The simulation result which shows what kind of value the temperature of the hot water which can be supplied and circulated from the heat storage apparatus 2 to the heat-medium circulation path 3 at the time of the end of a time slot | zone was obtained. Then, it is determined whether or not the temperature (simulation result) of hot water that can be supplied and circulated from the heat storage device 2 to the heat medium circulation path 3 at the end of the circulation time zone is within the reference temperature range. The degree of heat exchange capability of the heat exchanger 13 was determined.

例えば、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる熱媒の温度が高過ぎる状態は、循環時間帯の終了時点において蓄熱装置２に残存している熱が多過ぎる状態であることを意味する。つまり、太陽熱集熱器１で集め、蓄熱装置２で蓄えた熱が消費者に充分に活用されなかった（即ち、蓄えた熱が無駄になった）ことを意味する。これに対して、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる熱媒の温度が低過ぎる状態は、循環時間帯の終了時点において蓄熱装置２に残存している熱が少な過ぎる状態であることを意味する。つまり、循環時間帯の終期には、各消費者に十分な熱量を供給できなかった（即ち、熱の公平な分配が行われなかった）ことを意味する。   For example, a state in which the temperature of the heat medium that can be supplied and circulated from the heat storage device 2 to the heat medium circulation path 3 at the end of the circulation time zone is too high remains in the heat storage device 2 at the end of the circulation time zone. It means that there is too much heat. That is, it means that the heat collected by the solar heat collector 1 and stored by the heat storage device 2 has not been fully utilized by the consumer (that is, the stored heat has been wasted). On the other hand, when the temperature of the heat medium that can be circulated by being supplied from the heat storage device 2 to the heat medium circulation path 3 at the end of the circulation time zone is too low, the heat storage device 2 at the end of the circulation time zone. This means that there is too little heat remaining in the. In other words, it means that a sufficient amount of heat could not be supplied to each consumer at the end of the circulation time period (that is, the heat was not distributed fairly).

図２は熱交換器１３の熱交換能力が０．７ｋＷ／Ｋに設定されている場合、図３は熱交換器１３の熱交換能力が１．５ｋＷ／Ｋに設定されている場合、図４は熱交換器１３の熱交換能力が０．３ｋＷ／Ｋに設定されている場合のシミュレーション結果を示す。本実施形態で用いている熱交換能力の単位は〔ｋＷ／Ｋ〕であり、単位温度差当たりの移動熱量を表している。従って、図２〜図４に示した例で最も熱交換能力が高いのは、図３の１．５ｋＷ／Ｋの場合であり、最も熱交換能力が低いのは、図４の０．３ｋＷ／Ｋの場合である。   2 shows a case where the heat exchange capacity of the heat exchanger 13 is set to 0.7 kW / K, and FIG. 3 shows a case where the heat exchange capacity of the heat exchanger 13 is set to 1.5 kW / K. These show the simulation results when the heat exchange capacity of the heat exchanger 13 is set to 0.3 kW / K. The unit of heat exchange capacity used in the present embodiment is [kW / K], and represents the amount of heat transferred per unit temperature difference. Therefore, in the example shown in FIGS. 2 to 4, the heat exchange capacity is highest in the case of 1.5 kW / K in FIG. 3, and the heat exchange capacity is lowest in the case of 0.3 kW / K in FIG. This is the case for K.

熱交換器１３の熱交換能力が高いほど、消費者は熱交換器１３において大きな熱量を受領できるようになる。つまり、熱交換器１３の熱交換能力が高いほど、蓄熱装置２での蓄熱量の減少速度は相対的に速くなる。これに対して、熱交換器１３の熱交換能力が低いほど、消費者は熱交換器１３において小さな熱量しか受領できなくなる。つまり、熱交換器１３の熱交換能力が低いほど、蓄熱装置２での蓄熱量の減少速度は相対的に遅くなる。   The higher the heat exchange capacity of the heat exchanger 13, the more the consumer can receive a larger amount of heat in the heat exchanger 13. That is, the higher the heat exchanging capacity of the heat exchanger 13 is, the faster the rate of decrease of the heat storage amount in the heat storage device 2 is. On the other hand, the lower the heat exchange capability of the heat exchanger 13, the smaller the amount of heat that can be received by the consumer in the heat exchanger 13. That is, the lower the heat exchange capacity of the heat exchanger 13, the slower the rate of decrease of the heat storage amount in the heat storage device 2.

図２に示すシミュレーション結果のグラフは、熱交換器１３の熱交換能力が０．７ｋＷ／Ｋに設定されている場合の結果である。図２に示す例では、循環時間帯の終了時点（２３時２０分）：ＴEにおいて蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度が、上限温度（２５℃）と下限温度（２２℃）とで規定される基準温度範囲内となる。従って、０．７ｋＷ／Ｋという値は、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度が基準温度範囲の下限温度以上且つ上限温度以下となるような熱交換器１３の熱交換能力であると言える。この基準温度範囲の上限温度及び下限温度は適宜設定可能である。但し、基準温度範囲の上限温度及び下限温度は、少なくとも各消費者設備１０において加熱対象とする流体（給水）の温度よりも高い温度でなければならない。例えば、その給水温度よりも１３℃だけ高い温度を上記上限温度と設定し、及び、その給水温度よりも１０℃だけ高い温度を上記下限温度に設定することもできる。 The graph of the simulation result shown in FIG. 2 is a result when the heat exchange capacity of the heat exchanger 13 is set to 0.7 kW / K. In the example shown in FIG. 2, the end of the circulation time zone (20 pm 23): T hot water temperature can be circulated by supplying from the heat storage unit 2 to the heat medium circulation passage 3 in E is, the upper limit temperature (25 ° C) and the reference temperature range defined by the lower limit temperature (22 ° C). Therefore, the value of 0.7 kW / K is equal to or higher than the lower limit temperature of the reference temperature range and the upper limit temperature at which hot water that can be supplied and circulated from the heat storage device 2 to the heat medium circulation path 3 at the end of the circulation time zone. It can be said that the heat exchange capacity of the heat exchanger 13 is as follows. The upper limit temperature and the lower limit temperature of this reference temperature range can be set as appropriate. However, the upper limit temperature and the lower limit temperature of the reference temperature range must be higher than at least the temperature of the fluid (water supply) to be heated in each consumer facility 10. For example, a temperature higher by 13 ° C. than the feed water temperature can be set as the upper limit temperature, and a temperature higher by 10 ° C. than the feed water temperature can be set as the lower limit temperature.

熱交換器１３の熱交換能力を高くして各消費者が相対的に大きな熱量を受領できるようにすることで、蓄熱装置２での蓄熱量の減少速度が相対的に速くなったとしても、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度は基準温度範囲の下限温度以上であることが確保される。従って、循環時間帯の終了時点において蓄熱装置２に残存している熱が少な過ぎる状態になることが回避されるので、循環時間帯の終期であっても各消費者に十分な熱量を供給できるようになる。このように、熱交換器１３の熱交換能力の上限は、循環時間帯の間、上記基準蓄熱量を蓄えている蓄熱装置２から湯水を上記基準流量で熱媒循環路３に継続的に供給して循環させ、それにより熱交換器１３での熱交換に伴う湯水の温度低下が消費者による予測熱需要に対応して発生すると想定した場合に、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度が基準温度範囲の下限温度以上となるような能力であることが好ましい。   Even if the reduction rate of the heat storage amount in the heat storage device 2 becomes relatively fast by increasing the heat exchange capability of the heat exchanger 13 so that each consumer can receive a relatively large amount of heat, It is ensured that the temperature of hot water that can be supplied and circulated from the heat storage device 2 to the heat medium circulation path 3 at the end of the circulation time zone is equal to or higher than the lower limit temperature of the reference temperature range. Therefore, since it is avoided that the heat remaining in the heat storage device 2 becomes too little at the end of the circulation time zone, a sufficient amount of heat can be supplied to each consumer even at the end of the circulation time zone. It becomes like this. Thus, the upper limit of the heat exchange capacity of the heat exchanger 13 is to continuously supply hot water from the heat storage device 2 storing the reference heat storage amount to the heat medium circulation path 3 at the reference flow rate during the circulation time period. When it is assumed that a decrease in the temperature of hot water accompanying heat exchange in the heat exchanger 13 occurs in response to the predicted heat demand by the consumer, the heat storage device 2 starts at the end of the circulation time period. It is preferable that the temperature of the hot water that can be supplied and circulated to the heat medium circulation path 3 be equal to or higher than the lower limit temperature of the reference temperature range.

また、熱交換器１３の熱交換能力を低くして各消費者が相対的に小さな熱量しか受領できないようにすることで、蓄熱装置２での蓄熱量の減少速度が相対的に遅くなったとしても、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度は基準温度範囲の上限温度以下であることが確保される。従って、循環時間帯の終了時点において蓄熱装置２に残存している熱が多過ぎる状態になることが回避されるので、蓄えた熱が消費者に活用されずに無駄になるような状態を無くすことができる。このように、熱交換器１３の熱交換能力の下限は、循環時間帯の間、上記基準蓄熱量を蓄えている蓄熱装置２から湯水を上記基準流量で熱媒循環路３に継続的に供給して循環させ、それにより熱交換器１３での熱交換に伴う湯水の温度低下が消費者による予測熱需要に対応して発生すると想定した場合に、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度が基準温度範囲の上限温度以下となるような能力であることが好ましい。   In addition, by reducing the heat exchange capacity of the heat exchanger 13 so that each consumer can receive only a relatively small amount of heat, the rate of decrease in the amount of heat stored in the heat storage device 2 is relatively slow. However, it is ensured that the temperature of hot water that can be supplied and circulated from the heat storage device 2 to the heat medium circulation path 3 at the end of the circulation time zone is equal to or lower than the upper limit temperature of the reference temperature range. Accordingly, since it is avoided that the heat remaining in the heat storage device 2 becomes too much at the end of the circulation time zone, a state where the stored heat is wasted without being utilized by the consumer is eliminated. be able to. Thus, the lower limit of the heat exchange capacity of the heat exchanger 13 is to continuously supply hot water from the heat storage device 2 storing the reference heat storage amount to the heat medium circulation path 3 at the reference flow rate during the circulation time period. When it is assumed that a decrease in the temperature of hot water accompanying heat exchange in the heat exchanger 13 occurs in response to the predicted heat demand by the consumer, the heat storage device 2 starts at the end of the circulation time period. It is preferable that the temperature of hot water that can be supplied and circulated to the heat medium circulation path 3 be equal to or lower than the upper limit temperature of the reference temperature range.

以上のように、本実施形態の場合、図２に例示した０．７ｋＷ／Ｋという熱交換能力を有する熱交換器１３を採用すると、循環時間帯の終了時点において蓄熱装置２に残存している熱が多過ぎることも無く且つ少な過ぎることもない状態が得られる。その結果、蓄熱装置２に蓄えた熱が各消費者に活用されずに無駄になることもなく且つ熱が各消費者に対して不公平に配分されることもなくなる。   As described above, in the case of the present embodiment, when the heat exchanger 13 having the heat exchange capability of 0.7 kW / K illustrated in FIG. 2 is employed, it remains in the heat storage device 2 at the end of the circulation time zone. A state is obtained in which there is neither too much heat nor too little heat. As a result, the heat stored in the heat storage device 2 is not utilized by each consumer and is not wasted, and the heat is not unfairly distributed to each consumer.

図３に比較例として示すシミュレーション結果は、熱交換器１３の熱交換能力が１．５ｋＷ／Ｋに設定されている場合の結果である。図３に示す例では、蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度が基準温度範囲の上限値以下にまで低下する時刻：ＴUは、約２１時１０分となる。加えて、蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度が基準温度範囲の下限値未満にまで低下となる時刻：ＴLは、約２１時５０分となる。つまり、約２１時５０分以前は、各消費者に対して基準温度範囲の下限値以上の温度の湯水を供給できるが、約２１時５０分より後は、各消費者に対して基準温度範囲の下限値未満の温度の湯水しか供給できない。従って、１８時から２３時２０分までの循環時間帯の中で、約２１時５０分以前に熱を消費した消費者と、約２１時５０分より後に熱を消費しようとした消費者との間で、熱の分配に不公平が生じてしまう。 The simulation result shown as a comparative example in FIG. 3 is a result when the heat exchange capacity of the heat exchanger 13 is set to 1.5 kW / K. In the example shown in FIG. 3, the time the temperature of hot water can be circulated by supplying from the heat storage unit 2 to the heat medium circulation passage 3 is reduced to below the upper limit of the reference temperature range: T U is from about 21:00 10 Minutes. In addition, the time when the temperature of the hot water that can be supplied and circulated from the heat storage device 2 to the heat medium circulation path 3 falls below the lower limit value of the reference temperature range: TL is about 21:50. . That is, before about 21:50, hot water at a temperature equal to or higher than the lower limit of the reference temperature range can be supplied to each consumer, but after about 21:50, each consumer is supplied with a reference temperature range. Only hot water with a temperature lower than the lower limit value can be supplied. Therefore, in the circulation time zone from 18:00 to 23:20, between consumers who consumed heat before about 21:50 and consumers who tried to consume heat after about 21:50 Inadequate heat distribution occurs.

図４に比較例として示すシミュレーション結果は、熱交換器１３の熱交換能力が０．３ｋＷ／Ｋに設定されている場合の結果である。図４に示す例では、蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度が基準温度範囲の上限値以下にまで低下する時刻：ＴUは、循環時間帯の終了時点：ＴEになってもまだ訪れていない。つまり、循環時間帯の終了時点において蓄熱装置２に残存している熱が多過ぎる状態となっている。 The simulation result shown as a comparative example in FIG. 4 is a result when the heat exchange capacity of the heat exchanger 13 is set to 0.3 kW / K. In the example shown in FIG. 4, the time at which the temperature of hot water that can be supplied and circulated from the heat storage device 2 to the heat medium circulation path 3 falls below the upper limit value of the reference temperature range: T U is the circulation time zone. Exit point: not visited yet even at T E. That is, there is too much heat remaining in the heat storage device 2 at the end of the circulation time zone.

以上のように、熱交換器１３での各消費者の受領熱量の制限によって、蓄熱装置２に蓄えられている蓄熱量の単位時間当たりの減少度合いを適切なものとして、特定の時間帯の初期及び終期に関わらず蓄熱装置には蓄熱量が残存している状態（即ち、各消費者に熱を充分に供給可能な状態）を確保できる。特に、熱交換器１３の熱交換能力が、循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度が基準温度範囲内となるように設定されているので、循環時間帯の終了時点において蓄熱装置２に残存している熱が多過ぎることも無く且つ少な過ぎることもない状態が得られる。その結果、蓄熱装置２に蓄えた熱が各消費者に活用されずに無駄になることもなく且つ熱が各消費者に対して不公平に配分されることもなくなる。   As described above, the degree of reduction per unit time of the heat storage amount stored in the heat storage device 2 is appropriately determined by limiting the amount of heat received by each consumer in the heat exchanger 13, and the initial value in a specific time zone. And the state (namely, the state which can fully supply heat to each consumer) can be ensured in the heat storage device irrespective of the end. In particular, the heat exchange capacity of the heat exchanger 13 is set so that the temperature of hot water that can be supplied and circulated from the heat storage device 2 to the heat medium circulation path 3 is within the reference temperature range at the end of the circulation time period. Therefore, a state is obtained in which the heat remaining in the heat storage device 2 is neither too much nor too little at the end of the circulation time zone. As a result, the heat stored in the heat storage device 2 is not utilized by each consumer and is not wasted, and the heat is not unfairly distributed to each consumer.

〔熱交換器への湯水流量〕
本実施形態の熱供給システムＳ１において、各消費者に対して実際に熱を供給する段階で、運転制御装置４は、熱媒循環路３に湯水を循環させる間の循環状態調節装置Ｃの動作を蓄熱装置２での蓄熱量に応じて制御する。具体的には、運転制御装置４は、特定の循環時間帯の開始前における蓄熱装置２での蓄熱量が多いほど、単位時間当たりに熱交換器１３に流入する湯水の流量が多くなるように循環状態調節装置Ｃの動作を制御する。 [Flow rate of hot water to heat exchanger]
In the heat supply system S1 of the present embodiment, the operation control device 4 operates the circulation state adjusting device C while circulating hot water in the heat medium circulation path 3 at the stage of actually supplying heat to each consumer. Is controlled according to the amount of heat stored in the heat storage device 2. Specifically, the operation control device 4 increases the flow rate of hot water flowing into the heat exchanger 13 per unit time as the amount of heat stored in the heat storage device 2 before the start of a specific circulation time period increases. The operation of the circulation state adjusting device C is controlled.

図５は、熱交換器１３に流入する湯水（熱媒）の流量を変化させると、蓄熱装置２での蓄熱量の低下度合いが変わることを説明するシミュレーション結果のグラフである。具体的には、図５は、同じ予測熱需要に対して熱を供給するに当たり、熱交換器１３に流入する湯水（熱媒）の流量を調節して変化させたときの蓄熱装置２での蓄熱量の推移がどのように異なるかを示すシミュレーション結果である。図５では、熱媒循環路３から各熱交換器１３に流入する湯水の流量を、循環時間帯の開始前における蓄熱装置２での蓄熱量が３００ｋＷｈのときには３リットル／分とし、循環時間帯の開始前における蓄熱装置２での蓄熱量が２００ｋＷｈのときには２リットル／分とした場合の２通りのシミュレーション結果を示す。   FIG. 5 is a graph of a simulation result for explaining that the degree of decrease in the amount of stored heat in the heat storage device 2 changes when the flow rate of hot water (heat medium) flowing into the heat exchanger 13 is changed. Specifically, FIG. 5 shows the heat storage device 2 when the flow rate of hot water (heat medium) flowing into the heat exchanger 13 is adjusted and changed in supplying heat to the same predicted heat demand. It is a simulation result which shows how transition of heat storage amount differs. In FIG. 5, the flow rate of hot water flowing into each heat exchanger 13 from the heat medium circulation path 3 is 3 liters / minute when the heat storage amount in the heat storage device 2 before the start of the circulation time zone is 300 kWh, and the circulation time zone When the amount of heat stored in the heat storage device 2 before the start of 200 kWh is 2 kW / min, two simulation results are shown.

図５から明らかなように、熱交換器１３に流入する湯水の流量が多い３リットル／分の方が蓄熱装置２での蓄熱量の単位時間当たりの減少度合いが急になり、熱媒循環路３から各熱交換器１３に流入する湯水の流量を２リットル／分と相対的に少なくした場合には蓄熱装置２での蓄熱量の単位時間当たりの減少度合いが相対的に緩やかになる。そして、熱媒循環路３から各熱交換器１３に流入する湯水の流量を３リットル／分とした場合及び２リットル／分とした場合の何れの場合でも、循環時間帯の終了時点：ＴEで残存している蓄熱量は同程度となる。つまり、循環時間帯の開始前における蓄熱装置２での蓄熱量が１００ｋＷｈ異なっていても、循環時間帯において熱媒循環路３から各熱交換器１３に流入する湯水の流量を調節することで、循環時間帯の終了時点で残存している蓄熱量を同程度にできる。 As is clear from FIG. 5, when the flow rate of hot water flowing into the heat exchanger 13 is 3 liters / minute, the degree of decrease in the amount of heat stored in the heat storage device 2 per unit time becomes steeper, and the heat medium circulation path 3, when the flow rate of hot water flowing into each heat exchanger 13 is relatively reduced to 2 liters / minute, the degree of reduction per unit time of the heat storage amount in the heat storage device 2 becomes relatively moderate. Then, in either case where the flow rate of hot water flowing into the heat exchangers 13 from the heat medium circulation path 3 is 3 liters / minute and 2 liters / minute, the end point of the circulation time zone: T E The amount of heat storage remaining in is about the same. That is, even if the heat storage amount in the heat storage device 2 before the start of the circulation time zone is different by 100 kWh, by adjusting the flow rate of hot water flowing into the heat exchangers 13 from the heat medium circulation path 3 in the circulation time zone, The amount of heat storage remaining at the end of the circulation time zone can be made comparable.

以上のように、運転制御装置４は、循環時間帯の開始前における蓄熱装置２での蓄熱量が多いほど、循環状態調節装置Ｃとしての定流量弁Ｖ１の開度を調節して、単位時間当たりに熱交換器１３に流入する湯水の流量が多くすることで、各消費者に分配される熱量を多く（即ち、蓄熱装置２での蓄熱量の単位時間当たりの減少度合いを急に）できる。言い換えると、運転制御装置４は、循環時間帯の開始前における蓄熱装置２での蓄熱量が多いほど各消費者に分配される熱量を多くすることで、熱媒循環路３を介して各消費者への熱供給が行われる特定の循環時間帯の終了時点において、蓄熱装置２に多量の熱が残存するような事態を避けることができる。
逆の観点から説明すると、運転制御装置４は、蓄熱装置２での蓄熱量が少ないほど、単位時間当たりに熱交換器１３に流入する湯水の流量を少なくして、各消費者に分配される熱量を相対的に少なく（即ち、蓄熱装置２での蓄熱量の単位時間当たりの減少度合いを緩やかに）すればよい。その結果、特定の循環時間帯の何れのタイミングで消費者が熱消費を行おうとしても、特に循環時間帯の終期であっても、蓄熱装置２には消費者が使用できる熱が残存している状態を確保できる。 As described above, the operation control device 4 adjusts the opening degree of the constant flow valve V1 as the circulation state adjusting device C as the amount of heat stored in the heat storage device 2 before the start of the circulation time zone increases, and unit time When the flow rate of hot water flowing into the heat exchanger 13 is increased, the amount of heat distributed to each consumer can be increased (that is, the degree of decrease per unit time of the heat storage amount in the heat storage device 2 can be suddenly increased). . In other words, the operation control device 4 increases the amount of heat distributed to each consumer as the amount of heat stored in the heat storage device 2 before the start of the circulation time period increases, thereby allowing each consumption through the heat medium circulation path 3. It is possible to avoid a situation in which a large amount of heat remains in the heat storage device 2 at the end of a specific circulation time period in which heat is supplied to the person.
If it demonstrates from a reverse viewpoint, the operation control apparatus 4 will reduce the flow volume of the hot water which flows into the heat exchanger 13 per unit time, and is distributed to each consumer, so that the heat storage amount in the heat storage apparatus 2 is small. The amount of heat may be relatively small (that is, the degree of decrease per unit time of the amount of heat stored in the heat storage device 2 may be moderated). As a result, regardless of the timing of the specific circulation time zone, the consumer may consume heat, and particularly at the end of the circulation time zone, heat that can be used by the consumer remains in the heat storage device 2. Can be ensured.

尚、熱供給システムＳを実際に運用する段階では、蓄熱装置２での蓄熱量と、単位時間当たりに熱交換器１３に流入させるべき湯水の流量との関係を予めメモリ（図示せず）に記憶しておけばよい。そして、運転制御装置４が、循環時間帯の開始前に蓄熱装置２での蓄熱量を計測し、更に、計測した蓄熱量の値とメモリに記憶されている上記関係とを参照して、循環状態調節装置Ｃとしての定流量弁Ｖ１の開度（即ち、単位時間当たりに熱交換器１３に流入する湯水の流量）を決定すればよい。   In the stage of actually operating the heat supply system S, the relationship between the amount of heat stored in the heat storage device 2 and the flow rate of hot water to flow into the heat exchanger 13 per unit time is stored in a memory (not shown) in advance. Just remember. Then, the operation control device 4 measures the amount of heat stored in the heat storage device 2 before the start of the circulation time zone, and further refers to the value of the measured heat storage amount and the relationship stored in the memory to circulate. What is necessary is just to determine the opening degree (namely, flow volume of the hot water which flows into the heat exchanger 13 per unit time) of the constant flow valve V1 as the state adjustment apparatus C.

＜第２実施形態＞
第２実施形態の熱供給システムは、運転制御装置による循環状態調節装置の動作制御の手法が上記第１実施形態と異なっており、熱供給システムの構成などは上記第１実施形態と同様である。以下に第２実施形態の熱供給システムについて説明するが、第１実施形態と同様の構成については説明を省略する。 Second Embodiment
The heat supply system of the second embodiment is different from the first embodiment in the method of operation control of the circulation state adjusting device by the operation control device, and the configuration of the heat supply system is the same as that of the first embodiment. . Although the heat supply system of 2nd Embodiment is demonstrated below, description is abbreviate | omitted about the structure similar to 1st Embodiment.

上記第１実施形態で説明したように、熱交換器１３の熱交換能力は単位温度差当たりの移動熱量で表すことができる。従って、同じ熱交換能力を有する熱交換器１３を用いたとしても、熱交換器１３に流入して熱交換する２つの流体の温度、即ち、熱媒循環路３の往路３ａを通流する湯水の温度と、消費者設備１０において加熱対象とする流体（給水）の温度との温度差が大きいほど、熱媒循環路３の往路３ａを通流する湯水から消費者設備１０において加熱対象とする流体（給水）への単位時間当たりの移動熱量が大きくなる。そして、熱媒循環路３の往路３ａを通流する湯水から消費者設備１０において加熱対象とする流体（給水）への単位時間当たりの移動熱量が大きくなれば、蓄熱装置２での蓄熱量の減少度合いも急になる。   As described in the first embodiment, the heat exchange capability of the heat exchanger 13 can be expressed by the amount of heat transferred per unit temperature difference. Therefore, even if the heat exchanger 13 having the same heat exchange capability is used, the temperatures of the two fluids that flow into the heat exchanger 13 and exchange heat, that is, hot water flowing through the forward path 3a of the heat medium circulation path 3 And the temperature of the fluid (water supply) to be heated in the consumer equipment 10 is larger, the hot water flowing through the forward path 3a of the heat medium circulation path 3 is the target of heating in the consumer equipment 10 The amount of heat transferred to the fluid (water supply) per unit time increases. If the amount of heat transferred per unit time from the hot water flowing through the forward path 3a of the heat medium circulation path 3 to the fluid (water supply) to be heated in the consumer facility 10 increases, the amount of heat stored in the heat storage device 2 is increased. The degree of decrease also becomes steep.

第２実施形態の熱供給システムにおいて、運転制御装置４は、特定の循環時間帯の開始前における蓄熱装置２での蓄熱量が多いほど、熱交換器１３に流入する湯水の温度が高くなるように循環状態調節装置Ｃの動作を制御する。   In the heat supply system of the second embodiment, the operation control device 4 is configured such that the temperature of the hot water flowing into the heat exchanger 13 increases as the amount of heat stored in the heat storage device 2 before the start of the specific circulation time zone increases. The operation of the circulation state adjusting device C is controlled.

図６は、配管送り温度（即ち、熱交換器１３に流入する湯水の温度）を７５℃と設定した場合の、熱需要と蓄熱量と熱媒の温度との時間的な変化のシミュレーション結果を示すグラフである。図６に示す例では、循環時間帯の開始前において蓄熱装置２に７５℃の湯水で３００ｋＷｈの熱量が蓄えられているものとする。
図７は、配管送り温度を４５℃と設定した場合の、熱需要と蓄熱量と熱媒の温度との時間的な変化のシミュレーション結果を示すグラフである。図７に示す例では、循環時間帯の開始前において蓄熱装置２に７５℃の湯水で２５０ｋＷｈの熱量が蓄えられているものとする。 FIG. 6 shows simulation results of temporal changes in the heat demand, the amount of heat storage, and the temperature of the heat medium when the pipe feed temperature (that is, the temperature of hot water flowing into the heat exchanger 13) is set to 75 ° C. It is a graph to show. In the example shown in FIG. 6, it is assumed that a heat amount of 300 kWh is stored in hot water at 75 ° C. in the heat storage device 2 before the start of the circulation time period.
FIG. 7 is a graph showing simulation results of temporal changes in the heat demand, the amount of heat storage, and the temperature of the heat medium when the pipe feed temperature is set to 45 ° C. In the example shown in FIG. 7, it is assumed that a heat amount of 250 kWh is stored in the heat storage device 2 with hot water of 75 ° C. before the start of the circulation time period.

図６に示す例（蓄熱量が３００ｋＷｈの例）では、蓄熱装置２に７５℃の湯水が貯えられており且つ配管送り温度を７５℃と設定しているため、白四角印で示すように、循環時間帯の開始時点では７５℃の湯水を熱交換器１３へと供給できるが、その後、蓄熱装置２に貯えられている湯水の温度が低下して７５℃未満となる。そのため、蓄熱装置２に貯えられている最高温度の湯水（７５℃未満の湯水）の温度が図６に示す配管送り温度となり、その温度は徐々に低下する。但し、蓄熱装置２から熱交換器１３へは、蓄熱装置２に貯えられている最高温度の湯水を供給しているため、各熱交換器１３において単位時間当たりに各消費者に分配される熱量は最大になっている。   In the example shown in FIG. 6 (an example in which the heat storage amount is 300 kWh), since the hot water of 75 ° C. is stored in the heat storage device 2 and the pipe feed temperature is set to 75 ° C., as shown by white square marks, At the start of the circulation time zone, 75 ° C. hot water can be supplied to the heat exchanger 13, but then the temperature of the hot water stored in the heat storage device 2 decreases to below 75 ° C. Therefore, the temperature of the hottest hot water (less than 75 ° C.) stored in the heat storage device 2 becomes the pipe feed temperature shown in FIG. 6, and the temperature gradually decreases. However, since the hot water stored in the heat storage device 2 is supplied from the heat storage device 2 to the heat exchanger 13, the amount of heat distributed to each consumer per unit time in each heat exchanger 13 Has become the maximum.

このように、図６に示す例では、配管送り温度を７５℃という高温に設定することで、蓄熱装置２から熱交換器１３へは、蓄熱装置２に貯えられている最高温度の湯水を供給して、各熱交換器１３において単位時間当たりに各消費者に分配される熱量を最大としているため、黒丸印で示すように、蓄熱装置２での蓄熱量の単位時間当たりの減少度合いが急になる。   Thus, in the example shown in FIG. 6, the hot water stored in the heat storage device 2 is supplied from the heat storage device 2 to the heat exchanger 13 by setting the pipe feed temperature to a high temperature of 75 ° C. Since each heat exchanger 13 maximizes the amount of heat distributed to each consumer per unit time, as shown by the black circles, the degree of decrease in the amount of heat stored in the heat storage device 2 per unit time is abrupt. become.

図７に示す例（蓄熱量が２５０ｋＷｈの例）では、蓄熱装置２に７５℃の湯水が貯えられており且つ配管送り温度を４５℃と設定しているため、白四角印で示すように、循環時間帯の開始時点からしばらくの間では４５℃の湯水を熱交換器１３へと供給し続けることができる。具体的には、蓄熱装置２に貯えられている湯水の温度が４５℃より高ければ、上述したのと同様の流量調節弁Ｖ２を用いた温度調節を行うことで、その温度調節後の湯水の温度（即ち、図７に示す配管送り温度）を４５℃に調節できる。但し、蓄熱装置２に貯えられている湯水の温度が４５℃未満に低下した後は、蓄熱装置２に貯えられている４５℃未満の湯水の温度が図７に示す配管送り温度となり、その温度は徐々に低下する。   In the example shown in FIG. 7 (an example in which the heat storage amount is 250 kWh), since 75 ° C. hot water is stored in the heat storage device 2 and the pipe feed temperature is set to 45 ° C., as shown by white square marks, For a while from the start of the circulation time zone, hot water of 45 ° C. can be continuously supplied to the heat exchanger 13. Specifically, if the temperature of the hot water stored in the heat storage device 2 is higher than 45 ° C, the temperature adjustment using the flow rate control valve V2 similar to that described above is performed, so that the hot water after the temperature adjustment is performed. The temperature (that is, the pipe feed temperature shown in FIG. 7) can be adjusted to 45 ° C. However, after the temperature of the hot water stored in the heat storage device 2 drops below 45 ° C., the temperature of the hot water stored in the heat storage device 2 below 45 ° C. becomes the pipe feed temperature shown in FIG. Gradually decreases.

このように、図７に示す例では、蓄熱装置２において循環時間帯の開始時点では７５℃の湯水を貯えながらも、配管送り温度をそれよりも低い４５℃と設定することで、各熱交換器１３において単位時間当たりに各消費者に分配される熱量が相対的に低く制限される。その結果、図７において黒丸印で示すように、蓄熱装置２での蓄熱量の単位時間当たりの減少度合いが相対的に緩やかになる。   As described above, in the example shown in FIG. 7, each heat exchange is performed by setting the pipe feed temperature to 45 ° C. lower than that while storing 75 ° C. hot water at the start of the circulation time zone in the heat storage device 2. The amount of heat distributed to each consumer per unit time in the unit 13 is limited to be relatively low. As a result, as indicated by black circles in FIG. 7, the degree of reduction per unit time of the heat storage amount in the heat storage device 2 becomes relatively moderate.

図８は、熱交換器に流入する湯水（熱媒）の温度を変化させたときの、蓄熱装置での蓄熱量の低下度合いのシミュレーション結果のグラフである。具体的には、図８には、図６に示した配管送り温度が７５℃の場合の蓄熱量の時間的変化の曲線（黒丸印）と、図７に示した配管送り温度が４５℃の場合の蓄熱量の時間的変化の曲線（白丸印）とを対比して示す。
図８から明らかなように、熱交換器１３に流入する湯水の温度が高い７５℃の方が蓄熱装置２での蓄熱量の単位時間当たりの減少度合いが急になり、熱媒循環路３から各熱交換器１３に流入する湯水の温度を４５℃と相対的に低くした場合には蓄熱装置２での蓄熱量の単位時間当たりの減少度合いが相対的に緩やかになる。そして、熱媒循環路３から各熱交換器１３に流入する湯水の温度を７５℃とした場合及び４５℃とした場合の何れの場合でも、循環時間帯の終了時点：ＴEで残存している蓄熱量は同程度となる。つまり、循環時間帯の開始前における蓄熱装置２での蓄熱量が５０ｋＷｈ異なっていても、循環時間帯において熱媒循環路３から各熱交換器１３に流入する湯水の温度を調節することで、循環時間帯の終了時点で残存している蓄熱量を同程度にできる。 FIG. 8 is a graph of a simulation result of the degree of decrease in the amount of heat stored in the heat storage device when the temperature of hot water (heat medium) flowing into the heat exchanger is changed. Specifically, FIG. 8 shows a curve (black circle) of the temporal change in the heat storage amount when the pipe feed temperature shown in FIG. 6 is 75 ° C., and the pipe feed temperature shown in FIG. It shows in contrast with the curve (white circle mark) of the temporal change of the heat storage amount in the case.
As is clear from FIG. 8, when the temperature of the hot water flowing into the heat exchanger 13 is 75 ° C., the degree of decrease in the amount of heat stored in the heat storage device 2 per unit time becomes steeper. When the temperature of the hot water flowing into each heat exchanger 13 is relatively lowered to 45 ° C., the degree of decrease in the amount of heat stored in the heat storage device 2 per unit time becomes relatively moderate. And in any case where the temperature of the hot water flowing into each heat exchanger 13 from the heat medium circulation path 3 is 75 ° C. and 45 ° C., it remains at the end point of the circulation time zone: T E. The amount of heat stored is about the same. That is, even if the heat storage amount in the heat storage device 2 before the start of the circulation time zone is different by 50 kWh, by adjusting the temperature of the hot water flowing into the heat exchangers 13 from the heat medium circulation path 3 in the circulation time zone, The amount of heat storage remaining at the end of the circulation time zone can be made comparable.

以上のように、運転制御装置４は、循環時間帯の開始前における蓄熱装置２での蓄熱量が多いほど、循環状態調節装置Ｃとしての流量調節弁Ｖ２の開度を調節して、温度センサＴ２で測定される熱交換器１３に流入する湯水の温度を高くすることで、各消費者に分配される熱量を多く（即ち、蓄熱装置２での蓄熱量の減少度合いを急に）できる。言い換えると、運転制御装置４は、循環時間帯の開始前における蓄熱装置２での蓄熱量が多いほど各消費者に分配される熱量を多くすることで、熱媒循環路３を介して各消費者への熱供給が行われる特定の循環時間帯の終了時点において、蓄熱装置２に多量の熱が残存するような事態を避けることができる。
逆の観点から説明すると、運転制御装置４は、蓄熱装置２での蓄熱量が少ないほど、熱交換器１３に流入する湯水の温度を低くして、単位時間当たりに各消費者に分配される熱量を相対的に少なく（即ち、蓄熱装置２での蓄熱量の減少度合いを緩やかに）すればよい。その結果、特定の循環時間帯の何れのタイミングで消費者が熱消費を行おうとしても、特に循環時間帯の終期であっても、蓄熱装置２には消費者が使用できる熱が残存している状態を確保できる。 As described above, the operation control device 4 adjusts the opening degree of the flow rate control valve V2 as the circulation state adjusting device C as the amount of heat stored in the heat storage device 2 before the start of the circulation time period increases, so that the temperature sensor By increasing the temperature of the hot water flowing into the heat exchanger 13 measured at T2, the amount of heat distributed to each consumer can be increased (that is, the degree of decrease in the amount of stored heat in the heat storage device 2 is abrupt). In other words, the operation control device 4 increases the amount of heat distributed to each consumer as the amount of heat stored in the heat storage device 2 before the start of the circulation time period increases, thereby allowing each consumption through the heat medium circulation path 3. It is possible to avoid a situation in which a large amount of heat remains in the heat storage device 2 at the end of a specific circulation time period in which heat is supplied to the person.
If it demonstrates from a reverse viewpoint, the operation control apparatus 4 makes the temperature of the hot water which flows into the heat exchanger 13 low, and is distributed to each consumer per unit time, so that the heat storage amount in the heat storage apparatus 2 is small. The amount of heat may be relatively small (that is, the degree of decrease in the amount of heat stored in the heat storage device 2 may be moderated). As a result, regardless of the timing of the specific circulation time zone, the consumer may consume heat, and particularly at the end of the circulation time zone, heat that can be used by the consumer remains in the heat storage device 2. Can be ensured.

尚、熱供給システムＳを実際に運用する段階では、蓄熱装置２での蓄熱量と、熱交換器１３に流入させるべき湯水の温度との関係を予めメモリ（図示せず）に記憶しておけばよい。そして、運転制御装置４が、循環時間帯の開始前に蓄熱装置２での蓄熱量を計測し、更に、計測した蓄熱量の値とメモリに記憶されている上記関係とを参照して、循環状態調節装置Ｃとしての流量調節弁Ｖ２の開度（即ち、熱交換器１３に流入する湯水の温度）を決定すればよい。   In the stage of actually operating the heat supply system S, the relationship between the amount of heat stored in the heat storage device 2 and the temperature of hot water to be introduced into the heat exchanger 13 can be stored in advance in a memory (not shown). That's fine. Then, the operation control device 4 measures the amount of heat stored in the heat storage device 2 before the start of the circulation time zone, and further refers to the value of the measured heat storage amount and the relationship stored in the memory to circulate. What is necessary is just to determine the opening degree (namely, the temperature of the hot water which flows into the heat exchanger 13) of the flow control valve V2 as the state control apparatus C. FIG.

＜１＞
上記実施形態において、太陽熱集熱器１が集めた熱以外の熱を蓄熱装置２で蓄えるように改変してもよい。例えば、図９は、別の熱供給システムＳ２（Ｓ）の構成を説明する図である。図９に示す熱供給システムＳ２は、熱源装置として、熱と電気とを併せて発生する熱電併給装置２０を備え、その熱電併給装置２０が発生した熱が蓄熱装置２に蓄えられるように構成されている。具体的には、図９に記載の熱供給システムＳ２では、熱媒循環路３の途中に三方弁８を設けることで、熱媒循環路３から熱媒路２１を分岐させている。熱媒路２１には熱電併給装置２０が接続されることで、蓄熱装置２から熱電併給装置２０へ湯水が供給可能となっている。また、それとは別に熱電併給装置２０と蓄熱装置２とを接続する熱媒路２２を設けることで、熱電併給装置２０で加熱された湯水が蓄熱装置２へと帰還するようになっている。蓄熱装置２に貯留されている湯水が熱電併給装置２０へと流入し、その後、蓄熱装置２へと帰還する際の湯水の流れは、熱媒路２２に設けられているポンプＰ３によって形成される。熱電併給装置２０としては、燃料電池や、原動機と発電機とを組み合わせた装置などを採用できる。また、熱源装置として、熱電併給装置２０ではなく例えばヒートポンプ装置やガスボイラーなどの他の装置を設けてもよい。或いは、１台の熱源装置ではなく、複数の熱源装置（熱電併給装置２０、ヒートポンプ装置、ガスボイラーなどの組み合わせ）を併設してもよい。
以上のように、熱供給システムＳ２が、太陽熱集熱器１が集めた熱以外の熱を蓄熱装置２で蓄えることで、上記循環時間帯の開始前における蓄熱装置２での蓄熱量を大きく確保できる。その結果、より規模の大きい集合住宅にも対応可能な熱供給システムとなる。 <1>
In the said embodiment, you may modify | change so that heat other than the heat which the solar heat collector 1 collected may be stored in the thermal storage apparatus 2. FIG. For example, FIG. 9 is a diagram illustrating the configuration of another heat supply system S2 (S). The heat supply system S2 shown in FIG. 9 includes a heat / electricity cogeneration device 20 that generates both heat and electricity as a heat source device, and the heat generated by the heat / electricity supply device 20 is stored in the heat storage device 2. ing. Specifically, in the heat supply system S2 illustrated in FIG. 9, the heat medium path 21 is branched from the heat medium circuit 3 by providing the three-way valve 8 in the middle of the heat medium circuit 3. Hot water can be supplied from the heat storage device 2 to the combined heat and power supply device 20 by connecting the combined heat and power supply device 20 to the heat medium passage 21. In addition, by providing a heat medium path 22 that connects the combined heat and power supply device 20 and the heat storage device 2, hot water heated by the combined heat and power supply device 20 returns to the heat storage device 2. The hot water stored in the heat storage device 2 flows into the combined heat and power supply device 20 and then flows back to the heat storage device 2, and the flow of hot water is formed by the pump P3 provided in the heat medium passage 22. . As the combined heat and power unit 20, a fuel cell, a device combining a prime mover and a generator, or the like can be employed. Moreover, you may provide other apparatuses, such as a heat pump apparatus and a gas boiler, for example instead of the cogeneration apparatus 20 as a heat source apparatus. Alternatively, instead of a single heat source device, a plurality of heat source devices (combination of a combined heat and power supply device 20, a heat pump device, a gas boiler, etc.) may be provided.
As described above, the heat supply system S2 stores heat other than the heat collected by the solar heat collector 1 in the heat storage device 2, thereby ensuring a large amount of heat storage in the heat storage device 2 before the start of the circulation time period. it can. As a result, it becomes a heat supply system that can also accommodate larger-scale apartment houses.

尚、図９に示した例において、熱電併給装置２０に流入する湯水を、熱媒循環路３の途中の三方弁８から分岐させる構成ではなく、熱媒循環路３とは別に、蓄熱装置２と熱電併給装置２０との間で湯水を循環させる循環路を独立して設ける構成に改変してもよい。また、蓄熱装置２の内部に追加の熱交換器を設け、且つ、熱電併給装置２０と蓄熱装置２の内部の上記追加の熱交換器との間で熱媒を循環させることで、その熱媒と蓄熱装置２に貯えられている湯水との熱交換（即ち、蓄熱装置２に貯えられている湯水の加熱）を行わせるような改変も可能である。   In the example shown in FIG. 9, the hot water flowing into the combined heat and power supply device 20 is not configured to branch from the three-way valve 8 in the middle of the heat medium circulation path 3, but separately from the heat medium circulation path 3. You may modify | change to the structure which provides independently the circulation path through which hot water is circulated between the heat and electric power supply apparatus 20. Further, an additional heat exchanger is provided inside the heat storage device 2, and the heat medium is circulated between the combined heat and power supply device 20 and the additional heat exchanger inside the heat storage device 2. It is also possible to make a modification that causes heat exchange between the hot water stored in the heat storage device 2 (that is, heating of the hot water stored in the heat storage device 2).

＜２＞
上記実施形態において、様々な種類の太陽熱集熱器１や蓄熱装置２を用いることができる。例えば、図１では、太陽熱集熱器１として強制循環型の平板型集熱器を想定した図を描いているが、現在用いられている様々な種類の太陽熱集熱器１を本発明の熱供給システムＳで利用できる。また、図１では、蓄熱装置２として開放式の貯水タンクを想定した図を描いているが、密閉式の貯水タンクを用いてもよい。そして、蓄熱装置２の内部で温度成層が形成されるように湯水を貯めてもよい。その場合、蓄熱装置２に貯えられている高温部分の湯水が熱媒循環路３へ供給され、且つ、温度センサＴ１は、その蓄熱装置２から熱媒循環路３に供給される湯水の温度を測定できる位置に設けておくことが好ましい。 <2>
In the said embodiment, various kinds of solar-heat collector 1 and the thermal storage apparatus 2 can be used. For example, in FIG. 1, a diagram assuming a forced circulation type flat plate collector as the solar collector 1 is drawn. However, various types of solar collectors 1 currently used are used in the heat of the present invention. Available in the supply system S. Moreover, although the figure which assumed the open type water storage tank as the heat storage apparatus 2 is drawn in FIG. 1, you may use a sealed type water storage tank. And hot water may be stored so that temperature stratification may be formed inside the heat storage device 2. In that case, the hot water stored in the heat storage device 2 is supplied to the heat medium circuit 3, and the temperature sensor T <b> 1 determines the temperature of the hot water supplied from the heat storage device 2 to the heat medium circuit 3. It is preferable to provide at a position where measurement is possible.

＜３＞
上記実施形態において、特定の循環時間帯の終了時点において蓄熱装置２から熱媒循環路３へ供給して循環させることができる湯水の温度のシミュレーション結果を得るために、幾つかの基準となる数値を例示したが、それらの数値は適宜変更可能である。例えば、上記実施形態では、基準蓄熱量を３００ｋＷｈとし、基準流量を３リットル／分とし、基準温度範囲を２２℃〜２５℃とした場合でのシミュレーション結果を示したが、この熱供給システムＳが設けられる集合住宅の規模や季節や各消費者の予測熱需要などの様々な要因に基づいて各数値は適宜変更してもよい。 <3>
In the above embodiment, in order to obtain a simulation result of the temperature of hot water that can be supplied and circulated from the heat storage device 2 to the heat medium circulation path 3 at the end point of the specific circulation time period, several reference numerical values are obtained. However, these numerical values can be changed as appropriate. For example, in the said embodiment, although the simulation result in case the reference | standard heat storage amount was 300 kWh, the reference | standard flow volume was 3 liter / min, and the reference | standard temperature range was 22 to 25 degreeC was shown, this heat supply system S is shown. Each numerical value may be changed as appropriate based on various factors such as the scale and season of the apartment house provided and the predicted heat demand of each consumer.

＜４＞
上記実施形態において、各消費者設備１０の熱交換器１３に供給される湯水の温度を調節するために、蓄熱装置２に貯えられている比較的高温の湯水が流れる往路３ａに接続路３ｃを介して低温の熱媒を流入させる例を説明したが、図示した接続路３ｃ以外の部位からその低温の熱媒を得てもよい。また、別途、上水（即ち、低温の熱媒）を導入する配管を熱媒循環路３の往路３ａに接続することで、各消費者設備１０の熱交換器１３に供給される湯水の温度を調節してもよい。 <4>
In the said embodiment, in order to adjust the temperature of the hot water supplied to the heat exchanger 13 of each consumer equipment 10, the connection path 3c is connected to the outward path 3a through which the relatively hot water stored in the heat storage device 2 flows. However, the low-temperature heat medium may be obtained from a portion other than the connection path 3c shown in the figure. Moreover, the temperature of the hot water supplied to the heat exchanger 13 of each consumer equipment 10 is separately connected by connecting a pipe for introducing clean water (that is, a low-temperature heat medium) to the forward path 3 a of the heat medium circulation path 3. May be adjusted.

本発明は、複数の消費者に対して熱を供給する熱供給システムに利用できる。   The present invention is applicable to a heat supply system that supplies heat to a plurality of consumers.

１ 太陽熱集熱器
２ 蓄熱装置
３ 熱媒循環路
４ 運転制御装置
１０ 消費者設備
１１ 熱消費装置
１３ 熱交換器
Ｐ１ ポンプ（循環状態調節装置 Ｃ）
Ｓ 熱供給システム
Ｖ１ 定流量弁（循環状態調節装置 Ｃ）
Ｖ２ 流量調節弁（循環状態調節装置 Ｃ） DESCRIPTION OF SYMBOLS 1 Solar thermal collector 2 Thermal storage apparatus 3 Heat-medium circulation path 4 Operation control apparatus 10 Consumer equipment 11 Heat consumption apparatus 13 Heat exchanger P1 Pump (circulation state adjustment apparatus C)
S Heat supply system V1 Constant flow valve (Circulating condition controller C)
V2 Flow control valve (Circulating state control device C)

Claims (4)

複数の消費者に熱を供給する熱供給システムであって、
太陽熱を集める太陽熱集熱器と、
熱媒を貯え、前記太陽熱集熱器が集めた熱を前記熱媒を用いて蓄える蓄熱装置と、
前記蓄熱装置が貯えている前記熱媒を、それぞれが熱消費装置を有する複数の消費者の消費者設備に循環可能にさせる熱媒循環路と、
前記消費者設備の夫々に設けられ、前記熱媒循環路を循環する前記熱媒と、当該消費者設備において加熱対象とする流体との間の熱交換を行う熱交換器と、
前記熱媒循環路における前記熱媒の循環状態を調節する循環状態調節装置と、
前記循環状態調節装置の動作を制御して、１日の中の特定の時間帯にのみ前記熱媒循環路に前記熱媒を循環させる運転制御装置とを備え、
前記運転制御装置は、前記熱媒循環路に前記熱媒を循環させる間の前記循環状態調節装置の動作を前記蓄熱装置での蓄熱量に応じて制御するものであって、
前記運転制御装置は、前記特定の時間帯の開始前における前記蓄熱装置での蓄熱量が多いほど、前記熱交換器に流入する前記熱媒の温度が高くなるように前記循環状態調節装置の動作を制御する熱供給システム。 A heat supply system for supplying heat to a plurality of consumers,
A solar collector that collects solar heat,
A heat storage device for storing a heat medium and storing the heat collected by the solar heat collector using the heat medium;
A heat medium circulation path that allows the heat medium stored in the heat storage device to be circulated to consumer equipment of a plurality of consumers each having a heat consumption device;
A heat exchanger that is provided in each of the consumer facilities and performs heat exchange between the heat medium that circulates in the heat medium circulation path and a fluid that is to be heated in the consumer facilities;
A circulation state adjusting device for adjusting a circulation state of the heat medium in the heat medium circulation path;
An operation control device that controls the operation of the circulation state adjusting device and circulates the heat medium in the heat medium circulation path only during a specific time period in one day,
The operation control device controls the operation of the circulation state adjusting device according to the amount of heat stored in the heat storage device while circulating the heat medium in the heat medium circulation path ,
The operation control device operates the circulating state adjusting device so that the temperature of the heat medium flowing into the heat exchanger increases as the amount of heat stored in the heat storage device before the start of the specific time period increases. To control the heat supply system. 前記運転制御装置は、前記特定の時間帯の開始前における前記蓄熱装置での蓄熱量が多いほど、単位時間当たりに前記熱交換器に流入する前記熱媒の流量が多くなるように前記循環状態調節装置の動作を制御する請求項１に記載の熱供給システム。   The operation control device is configured so that the greater the amount of heat stored in the heat storage device before the start of the specific time period, the greater the flow rate of the heat medium flowing into the heat exchanger per unit time. The heat supply system of Claim 1 which controls operation | movement of a regulator. 前記運転制御装置は、前記循環状態調節装置の動作を制御して、前記蓄熱装置から前記熱媒循環路へ流出した後であり且つ前記消費者設備に設けられる前記熱交換器に流入する前の熱媒に対して、当該熱媒よりも温度の低い熱媒を加える請求項１又は２に記載の熱供給システム。The operation control device controls the operation of the circulation state adjusting device to flow out from the heat storage device to the heat medium circulation path and before flowing into the heat exchanger provided in the consumer facility. The heat supply system according to claim 1 or 2, wherein a heat medium having a temperature lower than that of the heat medium is added to the heat medium. 前記運転制御装置は、前記循環状態調節装置の動作を制御して、前記蓄熱装置から前記熱媒循環路へ流出した後であり且つ前記消費者設備に設けられる前記熱交換器に流入する前の熱媒に対して、前記消費者設備に設けられる前記熱交換器から流出した後であり且つ前記蓄熱装置に流入する前の熱媒を加える請求項３に記載の熱供給システム。The operation control device controls the operation of the circulation state adjusting device to flow out from the heat storage device to the heat medium circulation path and before flowing into the heat exchanger provided in the consumer facility. The heat supply system according to claim 3, wherein a heat medium after flowing out from the heat exchanger provided in the consumer equipment and before flowing into the heat storage device is added to the heat medium.
JP2011079823A 2011-03-31 2011-03-31 Heat supply system Expired - Fee Related JP5745912B2 (en)

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