JP3689283B2

JP3689283B2 - Heat storage device

Info

Publication number: JP3689283B2
Application number: JP28229799A
Authority: JP
Inventors: 貞生西村
Original assignee: Yamato Co Ltd
Current assignee: Yamato Co Ltd
Priority date: 1999-10-04
Filing date: 1999-10-04
Publication date: 2005-08-31
Anticipated expiration: 2019-10-04
Also published as: JP2001108385A

Description

【０００１】
【発明の属する技術分野】
本発明は、余剰の電力を熱に代えて蓄熱しておき、日中使用電力が大きくなった時に蓄熱しておいた熱を取り出して利用し、全体として電気エネルギーの消費量をできるだけ少なくすることができる蓄熱装置に関するものである。
【０００２】
【従来の技術】
従来から、余剰電力を熱に代えて蓄熱しておくことにより、電力エネルギーを有効活用するシステムは実公平３−３０７４４号公報等に有るように公知であり、またこれとは別に図１１、図１２に示すようなシステムも公知である。
ここで、図１１に示すシステム構成を説明すると、
図１１において、Ｒは冷熱温熱兼用冷凍機、Ｐ１は第１ポンプ、１０１は第１切替え弁、１０２は第２切替え弁であり、これらは蓄熱槽１０３と接続されている第１流体管路１００内に直列に配置されている。また、この第１流体管路１００とは別に蓄熱槽１０３と接続されている第２管路管路１１０が第１流体管路に対して並列に配置され、第２流体管路１１０内に蓄熱槽１０３に対して並列に複数の放熱器１１１と、放熱器１１１に対して直列に第２ポンプＰ２、第３切替え弁１１３、第４切替え弁１１４が接続されており、さらに各放熱器１１１毎に制御弁１１２が配置されている。
蓄熱槽１０３は冷却または加熱される流体が満たされており、各流体管路に配置された各切替え弁１０１、１０２、１１３、１１４は図示のように蓄熱槽に接続されている。
このシステムでは、例えば電力に余剰が生じる時間帯（夜間等の電力料金の安価な時間帯）を利用して第１ポンプＰ１および冷熱温熱兼用冷凍機Ｒを運転し、蓄熱槽１０３内の流体を冷却あるいは加熱して蓄熱槽１０３内に蓄熱をしておく。そして冷房あるいは暖房等の負荷が最大になる昼間等の時間帯に、蓄熱槽１０３内の流体を第２ポンプＰ２によって汲み上げ放熱器１１１に流して、冷房あるいは暖房を行うことができるようになっている。
しかしながら、このシステムでは、第１、第２ポンプおよび流体管路は、複数有る放熱器の最大負荷運転状態に対応して設備しておく必要があり、大型のポンプおよび断面積の大きな４本の流体管（主管）を使用する必要があり、設備費が高価になるなどの問題がある。
【０００３】
また図１２に示すシステムは、放熱器２０１および冷熱温熱兼用冷凍機Ｒを有する回路を密閉型流体回路とし、この密閉型流体回路内に熱交換器２０３を配置し、さらに此の密閉型流体回路とは別に前記熱交換器２０３と接続する大気開放型流体回路２０５を設け、熱交換器２０３を介して蓄熱槽２０４内に蓄熱したり、蓄熱槽２０４内の熱を熱交換器２０１に流したりすることができる構成を採用している。このシステムでは冷熱温熱兼用冷凍機から複数の放熱器に流体を供給する管を共通にするとともに第１ポンプＰ１への流入管路と放熱器２０１からの吐出管路とを別々の管で構成し、これによってコストの低減を図ろうとしたものである。しかしながら、このシステムにおいても、冷熱温熱兼用冷凍機から複数の放熱器に流体を供給する管路は最大負荷に併せた大きな断面積のものを使用する必要があり、システムのコスト低減には十分寄与していない。
【０００４】
そこで、本発明は、蓄熱時と放熱時いずれの状態においても２本の管路で対応できるようにするとともに、その管路の太さを従来のそれと比較して細くできる蓄熱装置を提供し、上記問題を解決するとともに、ポンプが消費する搬送動力の低減を図ることを目的とする。
本発明は、密閉型流体回路と大気開放型流体回路とを熱交換器で接続し、この熱交換器を介して、夜間等の余剰の電力を熱に代えて蓄熱槽内に蓄熱しておき、日中使用電力が大きくなった時に蓄熱槽内に蓄熱しておいた熱を熱交換器を介して取り出して利用し、日中の消費電力を夜間にシフトするとともに流体搬送用電気エネルギーの消費量をできるだけ少なくすることができる蓄熱装置として構成されており、蓄熱槽内に蓄熱する蓄熱量は日中の最大負荷の全量でない蓄熱量（多くの計画は、５０％近くの蓄熱量）とし、放熱時には各放熱器に供給する熱は蓄熱槽と熱源機とが分担するように構成されている。このため、日中の負荷量が蓄熱量より大きい日の運転状況では、蓄熱時と放熱時に共用される配管内において両端より互いに冷（温）水を対向流として流し、それぞれに近い（流れの上流の）位置の各放熱器に対し必要とされる量が各分岐管を通じ供給されて行き、最後の放熱器には両者がそれぞれ受け持つ量が双方向より供給されることになる。そして各放熱器において必要とされた冷（温）水は、各放熱器において熱交換された後、蓄熱時と放熱時に共用される配管において相反する方向流を形成し、冷凍機、熱交換器に戻り循環を繰り返す。
また、日中の負荷量が蓄熱量以下の日の運転状況ではすべての負荷量を蓄熱槽に貯えた熱をもって対応することになる。この時の循環冷（温）水の全量は熱交換器を介し、蓄熱槽から熱を受けることになる。
【０００５】
【課題を解決するための手段】
このため、本発明が採用した技術解決手段は、
流体を循環させることができる密閉型流体回路内に、熱源機とこの熱源機に流体を供給する第１ポンプと熱交換器とをこの順で直列に配置し、さらに前記熱源機と第１ポンプおよび熱交換器に対して並列に複数の管路を設け、これら夫々の管路に放熱器を配置し、さらに前記熱交換器に対して前記とは別の並列管路を設けこの管路内に第２ポンプを配置し、また前記熱交換器には密閉型流体回路とは別に蓄熱槽からの流体を循環させることができる蓄熱流体回路を接続してなり、前記密閉型流体回路内の熱源機と第一ポンプとを運転して前記熱源機により密閉型流体回路内の流体を冷却または加熱し、この冷却または加熱した流体を前記熱交換器に流して前記蓄熱流体回路内の流体を冷熱または加熱して蓄熱槽内に蓄熱する第一過程と、前記密閉型流体回路内の熱源機と第一ポンプとを必要に応じて運転して前記熱源機によって密閉型流体回路内の流体を冷却または加熱し、冷却または加熱された流体を前記放熱器の一部に循環させるとともに、前記第二ポンプを運転して前記密閉型流体回路内の流体を前記熱交換器に供給して前記蓄熱流体回路の流体によって冷却または加熱し、この流体を前記残りの放熱器に前記第１ポンプからの流れと対向する方向に流して冷房または暖房する第二過程とを選択できるようにしたことを特徴とする蓄熱装置であり、
複数階からなるビルの上階に熱源機とこの熱源機に直列に接続され前記熱源機に流体を供給する第１ポンプとを配置し、地上側の階に熱交換器を配置し、これらを密閉型流体回路で直列に接続し、さらに、この密閉型流体回路内の前記熱源機、第１ポンプと熱交換器の間の各階毎に前記熱源機と第１ポンプに対して並列の管路を形成して各管路内に放熱器を配置し、また、前記熱交換器に対して地上側に並列に管路を形成し、該管路内に第２ポンプを配置し、また前記熱交換器には密閉型流体回路とは別に蓄熱槽からの流体を循環させることができる大気開放型の蓄熱流体回路を接続して流体回路を構成し、前記密閉型流体回路内の熱源機と第一ポンプとを運転して前記熱源機により密閉型流体回路内の流体を冷却または加熱し、この冷却または加熱した流体を前記熱交換器に流して前記蓄熱回路内の流体を冷熱または加熱して蓄熱槽内に蓄熱する第一過程と、前記密閉型流体回路内の熱源機と第一ポンプとを必要に応じて運転して前記熱源機によって密閉型流体回路内の流体を冷却または加熱し、冷却または加熱された流体を前記上階から下階の放熱器に向けて循環させるとともに、前記第二ポンプを運転して前記密閉型流体回路内の流体を前記熱交換器に供給して前記蓄熱流体回路の流体によって冷却または加熱し、この流体を下階から上階の放熱器に向けて前記第１ポンプからの流れに対向する方向に流して冷房または暖房する第二過程とを選択できるようにしたことを特徴とする蓄熱装置である。
【０００６】
【実施の形態】
以下、図面に基づいて本発明の実施の形態を説明すると、図１は建築物内（たとえば高層ビル等）に本蓄熱装置を装備した第１実施形態に関わる蓄熱装置の構成図である。
【０００７】
図において、１は夜間の蓄熱と日中の不足熱量を補うための熱源機としての冷熱温熱兼用冷凍機であり、切り替えによって冷熱と温熱とを供給出来る機能を有している。２は前記冷熱温熱兼用冷凍機１に流体を供給する第１ポンプであり、これら冷熱温熱兼用冷凍機１と第１ポンプ２とは流体回路内の最上部（例えばビルの最上階）に配置されている。３は建物内の各階を冷房又は暖房するための放熱器３であり、この放熱器３は各階毎に配置されている。４は流体回路内の最下部（例えばビルの地下等）に配置され安価な電力を熱に代え蓄熱槽（後述する）１１内に蓄熱するための熱交換器、５は前記熱交換器の近くに配置され前記放熱器３に流体を流すための第２ポンプ、６は冷熱温熱兼用冷凍機１の吐出側に接続された一方向流れを形成する逆止弁、７は放熱器３の流入側管路に接続された制御弁、８は管路を切り替える第１切替え弁、９は管路を切り替える第２切替え弁、１０は制御装置である。
【０００８】
前記冷熱温熱兼用冷凍機１、第１ポンプ２、熱交換器４は図中の符号（カ）、（キ）で示す管路で直列に接続されており、また前記放熱器３は、冷熱温熱兼用冷凍機１、第１ポンプ２と前記熱交換器４との間で、冷熱温熱兼用冷凍機１と第１ポンプ２および熱交換器４のそれぞれに対して並列に複数配置された管路（ク）内に設けられており、また前記第２ポンプ５も前記熱交換器４に対して並列の管路（コ）内に配置されている。さらに第１切替え弁８は管路（カ）内に、また、第２切替え弁９は管路（キ）内に配置され、さらに第１切替え弁８は、第１ポンプ２と第２切替え弁９との間の管路（キ）に管路（ケ）により接続されている。そして、前記冷熱温熱兼用冷凍機１、第１ポンプ２、熱交換器４、放熱器３等が接続される管路は全体として図のように密閉型流体回路を構成している。
また、第１ポンプ２および第２ポンプ５は運転状態によって吐出流量を変えることができる機能を有しており、さらに前記第１、第２切替え弁８、９、制御弁７も共に、制御装置１０からの指令によって管路の切替えや流量が制御される構成となっている。
【０００９】
前記熱交換器４には大気開放型流体回路（ア）が接続され、この流体回路は蓄熱槽１１に接続され、大気開放型流体回路は循環ポンプ１２と二つの分岐切替え弁１３、１４を備えている。
蓄熱槽１１は複数の隔壁１５によって区画された槽を有し、各槽は連通管１６で連通され、さらにそのうち図中左側の槽１７は低温側として右側の槽１８は高温側として機能を果たし、各槽は水等の流体によって満たされている。そして、蓄熱槽１１の低温側の槽１７および高温側の槽１８には前記二つの分岐切替え弁１３、１４に接続する管路（ウ）、（オ）、（イ）、（エ）が図のように配置されており、この大気開放型流体回路と蓄熱槽１１とによって、余剰電力を熱に代えて蓄熱する蓄熱手段を構成している。なおこの蓄熱手段は従来から公知のものであり、また種々の蓄熱手段を使用することができ、本発明の特徴部ではないので詳細な説明は省略する。
【００１０】
つづいて、上記蓄熱装置の運転状態を説明する。
冷房蓄熱時（図２）
図２は安価な電力を使用して蓄熱槽１１内に冷熱蓄熱する状態のシステム図であり、図中太線が運転されている状態の管路である。
基本動作
密閉型流体回路は、熱源である冷熱温熱兼用冷凍機１、第１ポンプ２は運転状態にあり、第１切替え弁８、第２切替え弁９は、密閉型流体回路（カ）、（キ）を連通するように切替えられ、さらに各放熱器３用の制御弁７は強制的に遮断され、第２ポンプ５は停止状態とする。また、大気開放型回路（ア）側は、循環ポンプ１２は運転され、分岐切替え弁１３、１４は図のように直流を形成するように切換られる。
この状態において、大気開放型回路側では、蓄熱槽１１の高温槽１８側の上部より、配管（ウ）を介し循環ポンプ１２により汲み上げられた高冷水（前夜に利用され温度が上昇した蓄熱槽水）は熱交換器４によって冷熱温熱兼用冷凍機１によって冷却された冷水によって冷却される。この冷却された蓄熱槽水は、蓄熱槽１１の低温槽１７側に配管（ア）、（イ）を介し移送され、蓄熱される。この状況が継続すると蓄熱槽１１内の低温槽１７は冷却された冷水で満たされ更に継続すると連通管１６で連結された隣の槽に移送され、順次冷却処理された冷水により蓄熱槽１１内は蓄熱されていく。
一方、密閉型流体回路では、冷熱温熱兼用冷凍機１によって冷却された冷水により熱交換器４によって大気開放型回路内の蓄熱槽水を冷却し、温度上昇した密閉型流体回路内の高冷水は第１ポンプ２により冷熱温熱兼用冷凍機１に供給して冷却され再度熱交換器４に供給され、上記事項を繰り返す。
【００１１】
冷房放熱時（図３）
図３は蓄熱槽１１内に蓄熱された冷熱を利用するとともに、冷熱温熱兼用冷凍機１を利用してして冷房を行う状態の図であり、図中太線が運転されている状態の管路であり、各放熱器３に対する流体の流れは太点線で示されている。
基本動作
密閉型流体回路は、熱源である冷熱温熱兼用冷凍機１、第１ポンプ２は運転状態にあり、第２切替え弁９は熱交換器４と第２ポンプ５の吸入口を接続するように、また第１切替え弁８は熱交換器４と第１ポンプ２の吸入口を接続するように切替えられる。さらに、各放熱器３用の制御弁７は各放熱器３が必要とする流量に応じた開閉状況となるように制御装置１０からの指令により作動され、第２ポンプ５は運転状態にする。
一方、開放回路側は、循環ポンプ１２は運転、分岐切替え弁１３、１４は図のように直流を形成するように切替えられる。
基本運転状況
大気開放型回路では、蓄熱槽１１の低温槽１７側の下部より、配管（オ）を介し循環ポンプ１２により汲み上げられた低冷水（前夜に冷却された蓄熱槽水）は熱交換器４を介し、密閉型流体回路内の放熱器３によって温度上昇された高冷水を冷却する。この温度上昇された蓄熱槽水は、蓄熱槽１１の高温槽１８側に配管（エ）を介し移送される。この状況が継続すると蓄熱槽１１内の高温槽１８は温度上昇された高冷水で満たされ更に継続すると連通管で連結された隣の槽に移送され、順次温度上昇された高冷水により蓄熱槽１１内は満たされていく。
一方、密閉型流体回路では、熱交換器４を介し蓄熱槽１１の冷水により冷却された冷水は第２切替え弁９、配管（コ）を介して第２ポンプ５により汲み上げられ共用配管（カ）内を蓄熱時とは逆方向に流れ、近傍の放熱器３にそれぞれが必要とする冷水量をその制御弁７の開度に応じて供給し熱交換する。ここで温度上昇した高冷水は再度第２ポンプ５によって共用配管（キ）を蓄熱時と反対方向に流れ、さらに第１切替え弁８を介して熱交換器４に供給される。
また、第１ポンプ２の運転により冷熱温熱兼用冷凍機１に供給され冷却された冷水は逆止弁６、共用配管（カ）を介し、蓄熱時と同方向の流れをし、近傍の放熱器３にそれぞれが必要とする冷水量をその制御弁７の開度に応じて供給し、熱交換する。ここで温度上昇した高冷水は共用配管（キ）を蓄熱時と同方向流れをして再度第１ポンプ２によって冷熱温熱兼用冷凍機１に供給され冷却されて、上記事項を繰り返す。
【００１２】
日中負荷が最大負荷量より減少し、且つ蓄熱槽内の蓄熱量以上の場合の運転状況
密閉型流体回路の運転は、各放熱器３の負荷の状況により第１ポンプ２の循環量を制御する。
全体負荷は冷熱温熱兼用冷凍機１と蓄熱槽１１からの蓄熱とがそれぞれ受け持ち、第２ポンプ５により供給される冷水量を優先的に各放熱器３に流し、温度上昇した水は熱交換器４で各放熱器３に供給すべき温度にまで冷却する。
全体の最大負荷量より負荷量が減少し、且つ蓄熱槽１１が保有する蓄熱量以上の場合、第２ポンプ５は初期の状況（最大負荷時の分担量）で運転する。この時第１ポンプ２は全体負荷量が減少した事による全体必要循環量の減少分を初期の状況（最大負荷時の分担量）から減少するよう制御装置１０が第１ポンプ２を制御し運転する。この結果、冷熱温熱兼用冷凍機１の運転負荷は第１ポンプ２からの供給冷水の供給量と、温度によるから、その供給負荷量によって冷凍機能力が制御される。
一方、大気開放型回路では、蓄熱槽１１と熱交換器４の関係は図３の基本運転状況と同様の作動を行う。即ち、熱交換器４によって対応出来る範囲の密閉回路の負荷を処理すべく、循環ポンプ１２は蓄熱槽１１から冷水を汲み上げ熱交換器４に供給する。例えば、１０階建ての建物において、最大負荷時に、冷熱温熱兼用冷凍機１と、蓄熱槽１１用の熱交換器４とがそれぞれ半分熱処理を受け持つ様に計画された施設において
全体の負荷量が、８０％に減少した時、冷熱温熱兼用冷凍機１と第１ポンプ２は上側の約４階分の負荷（放熱器３）に対応し、蓄熱槽１１と第２ポンプ５からの蓄熱は下側約６階分の負荷（放熱器３）に対応する。第１ポンプ２、第２ポンプ５からの放熱器３への冷水の供給は各ポンプ直近の放熱器３から順次その先へと共用配管（カ）を通じ行われ、最後の放熱器３には両方のポンプより合わせてその必要とする量が供給される。
【００１３】
日中負荷が最大負荷量より減少し蓄熱槽内の蓄熱量以下の場合の運転状況
密閉型流体回路では、各放熱器３の負荷の状況により第１ポンプ２の循環量を制御し、その結果として冷熱温熱兼用冷凍機１を２次的に制御する。
全体の最大負荷量より負荷量が減少し蓄熱槽１１からの蓄熱による熱交換が熱交換器４の能力以下となった場合（即ち、蓄熱槽１１からの熱で十分に負荷が賄える状態となった場合）、この時制御装置１０により冷熱温熱兼用冷凍機１は全体負荷量が減少した事により停止すると伴に第１ポンプ２も同時に停止させる。全体必要循環量を受け持つのは第２ポンプ５であり、蓄熱槽１１内の熱を熱交換器４を介して各放熱器３負荷に供給する。第２ポンプ５も受け持つ全体負荷量に対応する為、負荷量の減少分を初期の状況（最大負荷時の分担量）から減少させて運転する。
この時の冷水の流れは、共用配管（カ）では蓄熱時とは反対の流れ方向で循環するとともに、逆止弁６により冷熱蓄熱兼用冷凍機１および第１ポンプへの流れは止められる。
大気開放型回路である蓄熱槽１１と熱交換器４の関係は図３に基本運転状況と同じ作動を行う。
即ち、熱交換器４によって対応出来る範囲の密閉型流体回路の負荷を処理すべく、循環ポンプ１２は蓄熱槽１１から冷水を汲み上げ熱交換器４に供給する。
密閉型流体回路の負荷が熱交換器４の最大処理能力以下に減少した時、循環ポンプ１２はその負荷量に対応する循環量に変化する。
【００１４】
例えば、１０階建ての建物において、最大負荷時に、冷熱温熱兼用冷凍機１と、蓄熱槽１１からの蓄熱がそれぞれ半分熱処理を受け持つ様に計画された施設において
全体の負荷量が、４０％に減少した時、制御装置１０により冷熱温熱兼用冷凍機１と第１ポンプ２は停止し、蓄熱槽１１からの蓄熱により熱交換器４とその循環ポンプ１２が作動して全ての負荷（放熱器３）に対応する。第２ポンプ５の循環量は負荷量に応じて制御される。第２ポンプ５から全ての放熱器３への冷水の供給はポンプ直近の放熱器３から順次その先へと共用配管（カ）を通じ行われる。
この時、開放回路側の循環ポンプ１２の循環量は第２ポンプ５の循環量と同様に負荷量に応じて制御される。
【００１５】
暖房蓄熱時（図４）
基本動作
密閉型流体回路では、熱源である冷熱温熱兼用冷凍機１、第１ポンプ２は運転し、第１切替え弁８、第２切替え弁９は図のように直流を形成するように作動、各放熱器３用の制御弁７は強制的に閉塞、第２ポンプ５は停止とする。
大気開放型回路は、循環ポンプ１２は運転、分岐切替え弁１３、１４は図のように直角流を形成するように作動する。
基本運転状況
大気開放型回路では、蓄熱槽１１の低温槽１７側の下部より、配管（オ）を介し循環ポンプ１２により汲み上げられた低温水（前夜に利用され温度が下降した蓄熱槽水）は熱交換器４を介し、冷熱温熱兼用冷凍機１によって加温された温水によって加温される。この加温された蓄熱槽水は、蓄熱槽１１の高温槽１８側に配管（エ）を介し移送され、蓄熱される。この状況が継続すると蓄熱槽１１内の高温槽１８は加温された温水で満たされ更に継続すると連通管で連結された隣の槽に移送され、順次加温処理された温水により蓄熱槽１１内は蓄熱されていく。
一方、密閉型流体回路においては、熱交換器４によって蓄熱槽水を加温し、温度下降した低温水は第１ポンプ２により冷熱温熱兼用冷凍機１に供給加温され再度熱交換器４に供給され、上記事項を繰り返す。
【００１６】
暖房放熱時（図５）
基本動作
密閉型流体回路は、熱源である冷熱温熱兼用冷凍機１、第１ポンプ２は運転、第１切替え弁８、第２切替え弁９は図のように直角流を形成するように作動し、各放熱器３用の制御弁７は各放熱器３が必要とする流量に応じた開閉状況となるように制御され、また第２ポンプ５は運転状態とする。
大気開放型回路側は、循環ポンプ１２は運転、分岐切替え弁１３、１４は図のように直流を形成するように作動する。
基本運転状況
大気開放型回路側では、蓄熱槽１１の高温槽１８側の上部より、配管（ウ）を介し循環ポンプ１２により汲み上げられた高温水（前夜に加温された蓄熱槽水）は熱交換器４を介し、密閉型流体回路側の放熱器３によって温度下降された低温水を加熱する。この温度下降された蓄熱槽水は、蓄熱槽１１の低温槽１７側に配管（イ）を介し移送される。この状況が継続すると蓄熱槽１１内の低温槽１７は温度下降された低温水で満たされ更に継続すると連通管１６で連結された隣の槽に移送され、順次温度下降された低温水により蓄熱槽１１内は満たされていく。
一方、密閉回路側においては、第２ポンプ５により熱交換器４を介し蓄熱槽１１の温水により加温された温水は第２切替え弁９、配管（コ）を介し共用配管（カ）内を蓄熱時とは逆方向の流れをし、近傍の放熱器３にそれぞれが必要とする温水量をその制御弁７の開度に応じて放熱器３に供給して熱交換し温度下降した低温水は共用配管（キ）を蓄熱時と反対方向流れをして再度第２ポンプ５の作用によって熱交換器４に供給される。また、もう１台の第１ポンプ２の運転により冷熱温熱兼用冷凍機１に供給され加温された温水は逆止弁６、共用配管（カ）を介し、蓄熱時と同方向の流れをし、近傍の放熱器３にそれぞれが必要とする温水量をその制御弁７の開度に応じて放熱器３に供給され熱交換し温度下降した低温水は共用配管（キ）を蓄熱時と同方向流れをして再度第１ポンプ２によって冷熱温熱兼用冷凍機１に供給され加熱され、上記事項を繰り返す。
【００１７】
日中負荷が最大負荷量より減少し、且つ蓄熱槽内の蓄熱量以上の場合の運転状況
密閉型流体回路の運転は、各放熱器３の負荷の状況により第１ポンプ２の循環量を制御する。
全体負荷を冷熱温熱兼用冷凍機１と蓄熱槽１１からの蓄熱とがそれぞれ受け持ち第２ポンプ５により供給される温水量を優先的に各放熱器３に与え、放熱器３で降下した水を熱交換器４で再び熱処理する。
全体の最大負荷量より負荷量が減少し、且つ負荷が蓄熱槽１１での蓄熱能力以上の場合、第２ポンプ５は初期の状況（最大負荷時の分担量）で運転する。この時第１ポンプ２は全体負荷量が減少した事による全体必要循環量の減少分を初期の状況（最大負荷時の分担量）から減少させて運転する。この結果、冷熱温熱兼用冷凍機１の運転負荷は第１ポンプ２からの供給温水の供給量と、温度によるから、その供給負荷量によって冷熱温熱兼用冷凍機１が制御される。大気開放型回路である蓄熱槽１１と熱交換器４の関係は図５の基本作動と同様の作動を行う。
熱交換器４によって対応出来る範囲の密閉型流体回路の負荷を処理すべく、循環ポンプ１２は蓄熱槽１１から温水を汲み上げ熱交換器４に供給する。
【００１８】
例えば、１０階建ての建物において、最大負荷時に、冷熱温熱兼用冷凍機１と、蓄熱槽１１の蓄熱がそれぞれ半分熱処理を受け持つ様に計画された施設において
全体の負荷量が、８０％に減少した時、冷熱温熱兼用冷凍機１とその第１ポンプ２は上から約４階分の負荷（放熱器３）に対応し、蓄熱槽１１からの蓄熱が下から約６階分の負荷（放熱器３）に対応する。第１ポンプ２、第２ポンプ５からの放熱器３への温水の供給はポンプ直近の放熱器３から順次その先へと共用配管（カ）を通じ行われ、最後の放熱器３には両方のポンプより合わせてその必要とする量が供給される。
【００１９】
日中負荷が最大負荷量より減少し蓄熱槽内の蓄熱量以下の場合の運転状況
密閉型流体回路の運転は、各放熱器３の負荷の状況により第１ポンプ２の循環量を制御し、その結果として冷熱温熱兼用冷凍機１を２次的に制御する。
全体の最大負荷量より負荷量が減少し蓄熱槽１１での蓄熱量以下となった場合（即ち、蓄熱槽１１の蓄熱量で全ての負荷が賄える場合）、この時第１ポンプ２は全体負荷量が減少した事により停止すると伴に冷熱温熱兼用冷凍機１も同時に停止する。全体必要循環量を受け持つのは第２ポンプ５であり、蓄熱槽１１内の熱を熱交換器４を介して各放熱器３負荷に供給する。第２ポンプ５も受け持つ全体負荷量に対応する為、負荷量の減少分を初期の状況（最大負荷時の分担量）から減少させて運転する。
この時の温水の流れは、共用配管（カ）を蓄熱時とは反対の流れ方向で循環するとともに、逆止弁６により冷熱蓄熱兼用冷凍機１および第１ポンプへの流れは止められる。
大気開放型回路である蓄熱槽１１と熱交換器４の関係は図５の基本運転状況と同様の作動を行う。
熱交換器４によって対応出来る範囲の密閉型流体回路の負荷を処理すべく、循環ポンプ１２は蓄熱槽１１から温水を汲み上げ熱交換器４に供給する。
密閉型流体回路の負荷が熱交換器４の最大処理能力以下に減少した時、第２ポンプ５はその負荷量に対応する循環量に変化する。
【００２０】
例えば、１０階建ての建物において、最大負荷時に、冷熱温熱兼用冷凍機１と、蓄熱槽１１の蓄熱とがそれぞれ半分熱処理を受け持つ様に計画された施設において
全体の負荷量が、４０％に減少した時、冷熱温熱兼用冷凍機１とその第１ポンプ２は停止し、蓄熱槽１１の蓄熱が全ての負荷（放熱器３）に対応する。第２ポンプ５の循環量は負荷量に応じて制御される。第２ポンプ５から全ての放熱器３への温水の供給はポンプ直近の放熱器３から順次その先へと共用配管（カ）を通じ行われる。
この時、大気開放型回路側の循環ポンプ１２の循環量は第１ポンプ２の循環量と同様に負荷量に応じて制御される。
【００２１】
つづいて第２実施形態に関わる蓄熱装置について図面を参照して説明すると、図６は高層ビル内に第２実施形態に係る蓄熱装置を装備した構成図である。
図６に示すように第２実施形態は、第１実施形態のおける放熱器（負荷）３の上流側に配置されている制御弁７を放熱器３の下流側に配置し、制御弁７Ａを３方弁とするとともに、制御弁７Ａと放熱器３の上流側とを接続した点で、第１実施形態と異なる。その他の構成は第１実施形態と同様であるので説明は省略する。
この第２実施形態の運転状態は基本的には第１実施形態と同様であるが、以下各運転状態を簡単に説明する。
冷房蓄熱時（図７）
図７は安価な電力を使用して蓄熱槽１１内に冷熱蓄熱する状態のシステム図であり、図中太線が運転されている状態の管路である。この状態は第１実施形態と同様であり、大気開放型回路側では、蓄熱槽１１の高温槽１８側の上部より、配管（ウ）を介し循環ポンプ１２により汲み上げられた高冷水（前夜に利用され温度が上昇した蓄熱槽水）は熱交換器４によって冷熱温熱兼用冷凍機１によって冷却された冷水によって冷却され、蓄熱槽１１内に蓄熱が行われる。この状態は第１実施形態と同様である。
【００２２】
冷房放熱時（図８）
図８は蓄熱槽１１内に蓄熱された冷熱を利用するとともに、冷熱温熱兼用冷凍機１を利用してして冷房を行う状態の図であり、図中太線が運転されている状態の管路であり、各放熱器３に対する流体の流れは太点線で示されている。この状態の時には密閉型流体回路での運転状況が第１実施形態と異なっている。
即ち、大気開放型回路では、蓄熱槽１１の低温槽１７側の下部より、配管（オ）を介し循環ポンプ１２により汲み上げられた低冷水（前夜に冷却された蓄熱槽水）は熱交換器４を介し、密閉型流体回路内の放熱器３によって温度上昇された高冷水を冷却する。
一方、密閉型流体回路では、熱交換器４を介し蓄熱槽１１の冷水により冷却された冷水は第２切替え弁９、配管（コ）を介して第２ポンプ５により汲み上げられ共用配管（カ）内を蓄熱時とは逆方向に流れ、近傍の放熱器３にそれぞれが必要とする冷水量をその制御弁７Ａの開度に応じて供給し熱交換する。また放熱器３において余分となる冷水は制御弁７Ａを介して、放熱器３において熱交換し温度上昇した高冷水と混合し、再度第２ポンプ５によって共用配管（キ）を蓄熱時と反対方向に流れ、さらに第１切替え弁８を介して熱交換器４に供給される。
また、第１ポンプ２の運転により冷熱温熱兼用冷凍機１に供給され冷却された冷水は逆止弁６、共用配管（カ）を介し、蓄熱時と同方向の流れをし、近傍の放熱器３にそれぞれが必要とする冷水量をその制御弁７Ａの開度に応じて供給し、熱交換する。また放熱器３において余分となる冷水は制御弁７Ａを介して、放熱器３において熱交換し温度上昇した高冷水と混合し、再度第１ポンプ２によって冷熱温熱兼用冷凍機１に供給され冷却されて、上記事項を繰り返す。こうして放熱器３を通って熱交換される冷水の量は放熱器が必要とする量に制御することができ、これによって熱交換の効率を一層向上することができる。
【００２３】
暖房蓄熱時（図９）
大気開放型回路では、蓄熱槽１１の低温槽１７側の下部より、配管（オ）を介し循環ポンプ１２により汲み上げられた低温水（前夜に利用され温度が下降した蓄熱槽水）は熱交換器４を介し、冷熱温熱兼用冷凍機１によって加温された温水によって加温される。
一方、密閉型流体回路においては、熱交換器４によって蓄熱槽水を加温し、温度下降した低温水は第１ポンプ２により冷熱温熱兼用冷凍機１に供給加温され再度熱交換器４に供給され、上記事項を繰り返す。この状態は第１実施形態と同様である。
【００２４】
暖房放熱時（図１０）
基本動作
図１０は蓄熱槽１１内に蓄熱された温熱を利用するとともに、冷熱温熱兼用冷凍機１を利用してして暖房を行う状態の図であり、図中太線が運転されている状態の管路であり、各放熱器３に対する流体の流れは太点線で示されている。この状態の時には密閉型流体回路での運転状況が第１実施形態と異なっている。
即ち、大気開放型回路側では、蓄熱槽１１の高温槽１８側の上部より、配管（ウ）を介し循環ポンプ１２により汲み上げられた高温水（前夜に加温された蓄熱槽水）は熱交換器４を介し、密閉型流体回路側の放熱器３によって温度下降された低温水を加熱する。
一方、密閉回路側においては、第２ポンプ５により熱交換器４を介し蓄熱槽１１の温水により加温された温水は第２切替え弁９、配管（コ）を介し共用配管（カ）内を蓄熱時とは逆方向の流れをし、近傍の放熱器３にそれぞれが必要とする温水量をその制御弁７Ａの開度に応じて放熱器３に供給して熱交換する。また放熱器３において余分となる温水は制御弁７Ａを介して、放熱器３において熱交換し温度下降した低温水と混合し、再度第２ポンプ５によって共用配管（キ）を蓄熱時と反対方向に流れ、さらに第１切替え弁８を介して熱交換器４に供給される。
また、もう１台の第１ポンプ２の運転により冷熱温熱兼用冷凍機１に供給され加温された温水は逆止弁６、共用配管（カ）を介し、蓄熱時と同方向の流れをし、近傍の放熱器３にそれぞれが必要とする温水量をその制御弁７Ａの開度に応じて供給し、熱交換する。また放熱器３において余分となる温水は制御弁７Ａを介して、放熱器３において熱交換し温度下降した低温水と混合し、再度第１ポンプ２によって冷熱温熱兼用冷凍機１に供給され冷却されて、上記事項を繰り返す。こうして放熱器３を通って熱交換される温水の量は放熱器が必要とする量に制御することができ、これによって熱交換効率を一層向上することができる。
【００２５】
以上本発明に係る実施形態について説明したが、これらの実施形態が従来の蓄熱装置に比較して有利な点について説明する。
〔本発明と、従来装置との配管設備、冷温水循環量及びその搬送動力の差異〕
各装置は最大負荷時に対応出来る様決定される。
最大負荷時において
・一般的には、全負荷を蓄熱槽の蓄熱でまかなわず、５０％を蓄熱量で対応し、残りの５０％を冷凍機の追い掛け運転により処置するよう装置全体の設計を行うケースが経済性の面で多い。このケースを一般方式とここでは仮称する。
この一般方式において、
・放熱器全負荷＝ｑＬ
・冷凍機能力＝ｑＲ
・蓄熱槽用熱交換器能力＝ｑＨＥＸ（ｑＲ）
・放熱器出入口温度差をΔＴ
とすると
ｑＬ＝ｑＲ＋ｑＨＥＸ
＝２×ｑＲとなる。
【００２６】
一般方式の一方式である図−１１のシステム（従来システム）の場合では、
放熱時の最大負荷時の放熱運転は、各放熱器１１１の合計負荷に対応するため、循環ポンプＰ２により蓄熱槽から必要循環量ＱＬを放熱器系に供給すると、蓄熱槽内の利用温度差もΔＴとすることが出来、
ｑＬ＝ＱＬ・ΔＴであるから
ＱＬ＝ｑＬ／ΔＴとなる。
又、蓄熱時における、冷凍機と蓄熱槽間の循環量Ｑ_STは循環ポンプＰ１により蓄熱槽から冷凍機１に供給され
ｑＲ＝Ｑ_ST・ΔＴであるから
Ｑ_ST＝ｑＲ／ΔＴ＝１／２×ｑＬ／ΔＴとなる。
【００２７】
即ち、図１１の従来システムでは、蓄熱時の冷凍機と蓄熱槽間の主管における循環量はＱ_ST＝１／２×ｑＬ／ΔＴが必要であり、放熱時の蓄熱槽と各放熱器との間の主幹部における循環量はＱＬ＝ｑＬ／ΔＴを必要とする。
次に、一般方式の一方式である図１２のシステム（従来システム）の場合では、放熱時の最大負荷時の運転は、各放熱器負荷２０１の全負荷に対応するため、放熱器による全負荷を熱源装置である蓄熱槽用熱交換器２０３と冷凍機Ｒ１との両者が合せて対応する。
即ち、全放熱器負荷による温度上昇分ΔＴをそれぞれの熱源装置が各々１／２×ΔＴづつ直列に対応する。
このときの装置全体必要循環量Ｑ_LO、放熱器出入口温度差をΔＴとすると、
ｑＬ＝Ｑ_LO×ΔＴ＝２×ｑＲ＝２・ｑＨＥＸであるから
Ｑ_LO＝（２×ｑＲ）／ΔＴ＝（２×ｑＨＥＸ）／ΔＴ＝ｑＬ／ΔＴとなる。
即ち、冷凍機、蓄熱槽用熱交換器共に循環量はＱ_LO＝ｑＬ／ΔＴが必要となる。この時、前述した如く蓄熱槽用熱交換器を介し負荷の熱処理を行った結果の温度差は１／２×ΔＴとなり、蓄熱槽内の利用温度差は蓄熱槽用熱交換器２０３を介し決定されるため、その利用温度差も１／２×ΔＴとなる。
又、蓄熱時における、冷凍機と蓄熱槽用熱交換器との間の循環水量Ｑ_STOは
ｑＲ＝Ｑ_STO×（１／２）×ΔＴであるから
Ｑ_STO＝（２×ｑＲ）／ΔＴ＝ｑＬ／ΔＴとなる。
即ち、図１２の従来システムにおいては、蓄熱時における冷凍機と蓄熱槽用熱交換器とを直接結ぶ主管と、放熱時における冷凍機、蓄熱槽用熱交換器及び放熱器とを結ぶ主管とに流れる流量は共に、
Ｑ_LO＝Ｑ_STO＝ｑＬ／ΔＴが必要となる。
【００２８】
本発明によると
全負荷を蓄熱槽が５０％対応するという一般方式のもとでは
ｑＬ＝ｑＲ＋ｑＨＥＸ
ｑＲ＝ｑＬ／２であるから
ｑＨＥＸ＝ｑＬ×１／２
・放熱器出入口の温度差をΔＴ
という前述の従来方式と同一条件下において
放熱時では、図３（冷房時の放熱時フロー図）に示した如く、全放熱器負荷を２分割しながら冷凍機と蓄熱槽用熱交換器がそれぞれ分担し合う。負荷を２分割し合って対応する時、冷凍機とこれが対応する放熱器との間の循環量、蓄熱槽用熱交換器とこれが対応する放熱器との間の循環水量は同量であり、この循環量Ｑ_LNは
ｑＲ＝ｑＨＥＸ＝Ｑ_LN×ΔＴ＝ｑＬ／２であるから
Ｑ_LN＝１／２×ｑＬ／ΔＴとなる。
故に、本発明における放熱時の放熱器と冷凍機、蓄熱槽用熱交換器との間の必要循環量は図−１１のシステムにおける必要循環量Ｑ_L＝ｑＬ／ΔＴの１／２
同様に図−１２のシステムにおける循環量Ｑ_LO＝ｑＬ／ΔＴの１／２となる。
また、蓄熱時では、冷凍機と蓄熱槽用熱交換器との間の循環水量Ｑ_STNは
ｑＲ＝ΔＴ×Ｑ_STN＝ｑＨＥＸ＝１／２ｑＬであるから
Ｑ_STN＝Ｑ_LN＝１／２×ｑＬ／ΔＴとなり、
本発明における冷凍機と蓄熱槽用熱交換器との間の必要循環量は、図−１１のシステムにおける必要循環量
Ｑ_ST ＝１／２×ｑＬ／ΔＴと同量、
図−１２のシステムにおける必要循環量Ｑ_STO＝ｑＬ／ΔＴの１／２となる。
【００２９】
以上のことにより、本発明による冷凍機と蓄熱槽用熱交換器とを直接結ぶ主管及び放熱器への供給主管は、従来システムと比較し、その循環量を前述した如く減することが出来、その結果配管径を細くすることが出来る。
又、循環量が１／２ですむことにより、搬送動力も減少させることが出来る。
さらに蓄熱槽内の熱利用温度差に関しても、図−７のシステムに比べ、蓄熱槽用熱交換器における利用温度差はΔＴ／２からΔＴへと２倍に拡大する事が出来るため、同一熱量を蓄熱するとき蓄熱槽容積を１／２に減少する事ができる。
これらのことにより、本発明は経済性において、従来システムと比較すると配管口径を細くする事が出来ると共に、蓄熱水槽容積をも１／２にすることにが出来、装置のイニシャルコストの低減が計れる。
又、省エネルギー性に関しては、循環量を１／２にすることにより搬送動力を大幅に削減する事が出来、省エネルギー性も発揮する。
以上のように本発明によれば、蓄熱時と放熱時に共に２本の主管で対応でき、さらにその管の太さを従来のそれと比較し細くする事ができ、また、最大負荷時の放熱対応において、従来のシステムと比較すると各ポンプが受け持つ循環量と放熱器３の受け持ち分担域を約二分の一に減少させる事が出来き、各ポンプの消費動力のみならず、それらの合計消費量を低減できる。さらに循環量が従来方式と比較し半減する事になり配管の太さを細くする事が出来工事費も低減できる。
なお、上記実施形態においては熱源機として冷熱温熱兼用冷凍機を使用した例について説明したが、熱源機として、単独の暖房機あるいは冷凍機を使用したり、併用することもできる。また、本システムに使用する熱媒体としては水、ブライン等、本システムの機能を達成できる種々の熱媒体を使用することができる。さらに、上記実施形態ではビルのような上下に配管した具体例について説明したが、流体を循環させることができる密閉型流体回路と、蓄熱槽からの流体を循環させることができる蓄熱流体回路とを同一平面上に配置しても同様な効果を達成できることは当然である。また、本発明はその精神又は主要な特徴から逸脱することなく他の色々な形で実施することができ、また、前述の実施例はあらゆる点で単なる例示に過ぎず、限定的に解釈してはならない。
【００３０】
【発明の効果】
以上詳細に述べた如く本発明によれば、
本蓄熱装置では、蓄熱時と放熱時に共に２本の主管で対応でき、さらにその管の太さを従来のそれと比較し細くする事ができる。
最大負荷時の放熱対応において、従来のシステムと比較すると各ポンプが受け持つ循環量と放熱器３の受け持ち分担域を約二分の一に減少させる事が出来き、各ポンプの消費動力のみならず、それらの合計消費量を低減できる。又、循環量が従来方式と比較し半減する事になり配管の太さを細くする事が出来工事費も低減できる。
本装置の日中放熱時において、日中の負荷が蓄熱量以上の場合、即ち熱交換器を介し蓄熱槽の熱と熱源機の熱を同時に利用する場合、各放熱器の利用温度差に等しい温度差をもって各熱源は対応できる。一方、従来の冷凍機と熱交換器とが密閉配管で直列配列型のシステムにおいては、各放熱器の利用温度差を冷凍機と、蓄熱槽用の熱交換器とが合わせて受け持つ事となり各熱源の処理する温度差は小さい。このように本方式は従来方式と比較し各熱源の温度処理範囲を高くすることができる。
日中、最大負荷量に対し５０％蓄熱の場合には熱交換器（蓄熱槽）からの取り出した熱量を搬送するポンプと、不足分への対応をするポンプを、主管の相対する位置に設置しそれぞれのポンプの吐出流が主管内部を対向して流れるようにする。両端に設置した２台のポンプより供給された冷温水は、両端より主管からの分岐管を介し各放熱器に分割供給され、最終的には主管の半ばで最後の放熱器に両方のポンプより供給された冷温水がその必要量として分岐管を介し供給される。２台のポンプは、各放熱器が必要とするその量と場所とを受け持ち分担する。最大負荷時においては、両者が２等分して分担し合うが、その他の場合には、蓄熱槽の熱の利用が過半数を占めるように制御をする。最大負荷時には、搬送動力は激減し、省エネ、と電力費の削減ができる。
等々の優れた効果を奏することができる。
【図面の簡単な説明】
【図１】本発明の実施形態に係わる蓄熱装置の全体構成図である。
【図２】同装置の冷房蓄熱時の運転状況説明図である。
【図３】同装置の冷房放熱時の運転状況説明図である。
【図４】同装置の暖房蓄熱時の運転状況説明図である。
【図５】同装置の暖房放熱時の運転状況説明図である。
【図６】本発明の第２実施形態に係わる蓄熱装置の全体構成図である。
【図７】同装置の冷房蓄熱時の運転状況説明図である。
【図８】同装置の冷房放熱時の運転状況説明図である。
【図９】同装置の暖房蓄熱時の運転状況説明図である。
【図１０】同装置の暖房放熱時の運転状況説明図である。
【図１１】従来の蓄熱装置の全体構成図である。
【図１２】他の形態の従来の蓄熱装置の全体構成図である。
【符号の説明】
１冷熱温熱兼用冷凍機
２第１ポンプ
３放熱器
４熱交換器
５第２ポンプ
６逆止弁
７、７Ａ制御弁
８第１切替え弁
９第２切替え弁
１０制御装置
１１蓄熱槽
１２循環ポンプ
１３、１４分岐切替え弁
１５隔壁
１６連通管
１７低温槽
１８高温槽[0001]
BACKGROUND OF THE INVENTION
In the present invention, surplus power is stored in place of heat, and the stored heat is taken out and used when the power used during the day becomes large, and the overall consumption of electric energy is reduced as much as possible. It is related with the heat storage apparatus which can do.
[0002]
[Prior art]
Conventionally, a system that effectively uses power energy by storing surplus power in place of heat has been known as disclosed in Japanese Utility Model Publication No. 3-30744, and FIG. 11 and FIG. A system as shown in FIG. 12 is also known.
Here, the system configuration shown in FIG. 11 will be described.
In FIG. 11, R is a cold / hot refrigerator, P 1 is a first pump, 101 is a first switching valve, 102 is a second switching valve, and these are the first fluid conduit 100 connected to the heat storage tank 103. Are arranged in series. In addition to the first fluid conduit 100, a second conduit 110 connected to the heat storage tank 103 is disposed in parallel to the first fluid conduit, and heat is stored in the second fluid conduit 110. A plurality of radiators 111 are connected in parallel to the tank 103, and a second pump P2, a third switching valve 113, and a fourth switching valve 114 are connected in series to the radiator 111, and each radiator 111 is further connected. The control valve 112 is arranged in the front.
The heat storage tank 103 is filled with a fluid to be cooled or heated, and each switching valve 101, 102, 113, 114 disposed in each fluid pipe is connected to the heat storage tank as shown.
In this system, for example, the first pump P1 and the cooling / heating refrigerator R are operated using a time zone in which surplus electricity is generated (a time zone in which the power rate is low such as nighttime), and the fluid in the heat storage tank 103 is discharged. Heat is stored in the heat storage tank 103 by cooling or heating. Then, in the daytime or the like when the load such as cooling or heating becomes maximum, the fluid in the heat storage tank 103 is pumped up by the second pump P2 and flows to the radiator 111 so that cooling or heating can be performed. Yes.
However, in this system, the first and second pumps and the fluid lines need to be installed corresponding to the maximum load operation state of a plurality of radiators, and a large pump and four large cross-sectional areas are required. There is a problem that a fluid pipe (main pipe) needs to be used and the equipment cost is high.
[0003]
Further, in the system shown in FIG. 12, the circuit having the radiator 201 and the refrigerator R for cooling / heating temperature is used as a sealed fluid circuit, the heat exchanger 203 is disposed in the sealed fluid circuit, and the sealed fluid circuit is further provided. Separately, an open air fluid circuit 205 connected to the heat exchanger 203 is provided, and heat is stored in the heat storage tank 204 via the heat exchanger 203, or heat in the heat storage tank 204 is passed to the heat exchanger 201. A configuration that can be used is adopted. In this system, the pipe for supplying fluid from the refrigerator for cooling / heating and heating to a plurality of radiators is made common, and the inlet pipe to the first pump P1 and the outlet pipe from the radiator 201 are configured as separate pipes. This is intended to reduce costs. However, even in this system, it is necessary to use a pipe with a large cross-sectional area that matches the maximum load for supplying fluid from the cold / hot refrigerator to multiple radiators. Not done.
[0004]
Therefore, the present invention provides a heat storage device that can be handled by two pipe lines in both the state of heat storage and the time of heat dissipation, and that the thickness of the pipe line can be made thinner than that of the conventional one, It aims at solving the said problem and aiming at reduction of the conveyance power which a pump consumes.
In the present invention, a closed fluid circuit and an open air fluid circuit are connected by a heat exchanger, and surplus power at night or the like is stored in a heat storage tank in place of heat through the heat exchanger. The heat stored in the heat storage tank when the power used during the day increases is taken out through the heat exchanger and used to shift the power consumption during the day to night and consume the electric energy for fluid transportation. It is configured as a heat storage device that can reduce the amount as much as possible, and the amount of heat stored in the heat storage tank is not the total amount of the maximum load during the day (many plans are about 50% heat storage) The heat supplied to each radiator at the time of heat dissipation is configured so that the heat storage tank and the heat source unit share the heat. For this reason, in an operating situation on a day when the amount of load during the day is larger than the amount of stored heat, cold (warm) water is made to flow as opposed flows from both ends in the pipe shared during heat storage and heat dissipation, The amount required for each radiator at the upstream position is supplied through each branch pipe, and the amount each of the two is supplied to the last radiator is bidirectionally supplied. And the cold (hot) water required in each radiator forms a directional flow in the pipes shared during heat storage and heat dissipation after heat exchange in each radiator, and the refrigerator, heat exchanger Return to and repeat the cycle.
Moreover, in the operation state on the day when the amount of load during the day is equal to or less than the amount of stored heat, all loads are handled with the heat stored in the heat storage tank. At this time, the entire amount of the circulating cold (warm) water receives heat from the heat storage tank via the heat exchanger.
[0005]
[Means for Solving the Problems]
Therefore, the technical solution adopted by the present invention is:
A heat source unit, a first pump for supplying fluid to the heat source unit, and a heat exchanger are arranged in this order in a sealed fluid circuit capable of circulating the fluid, and further, the heat source unit and the first pump. In addition, a plurality of pipelines are provided in parallel to the heat exchanger, a radiator is disposed in each of these pipelines, and another parallel pipeline different from the above is provided for the heat exchanger. And a heat storage fluid circuit capable of circulating a fluid from the heat storage tank separately from the sealed fluid circuit, and a heat source in the sealed fluid circuit. And the first pump is operated to cool or heat the fluid in the closed fluid circuit with the heat source device, and the cooled or heated fluid is passed through the heat exchanger to cool the fluid in the heat storage fluid circuit. Or the first process of heating and storing heat in the heat storage tank, The heat source unit in the closed fluid circuit and the first pump are operated as necessary to cool or heat the fluid in the sealed fluid circuit by the heat source unit, and the cooled or heated fluid is supplied to one of the radiators. And the second pump is operated to supply the fluid in the sealed fluid circuit to the heat exchanger to be cooled or heated by the fluid in the heat storage fluid circuit, and this fluid is discharged to the remaining heat radiation. A heat storage device characterized in that a second process of cooling or heating by flowing in a direction opposite to the flow from the first pump can be selected.
A heat source machine and a first pump connected in series to the heat source machine and supplying fluid to the heat source machine are arranged on the upper floor of a building composed of a plurality of floors, and a heat exchanger is arranged on the ground floor. A series fluid pipe is connected in series with a closed fluid circuit, and a pipe line in parallel with the heat source machine and the first pump is provided for each floor between the heat source machine and the first pump and the heat exchanger in the sealed fluid circuit. And a radiator is arranged in each pipeline, a pipeline is formed in parallel to the ground side with respect to the heat exchanger, a second pump is arranged in the pipeline, and the heat In addition to the sealed fluid circuit, the exchanger is connected to an open air heat storage fluid circuit that can circulate fluid from the heat storage tank to form a fluid circuit. One pump is operated to cool or heat the fluid in the closed fluid circuit by the heat source device. Includes a first process of flowing a heated fluid through the heat exchanger to cool or heat a fluid in the heat storage circuit to store heat in the heat storage tank, and a heat source device and a first pump in the sealed fluid circuit. The heat source device is operated as necessary to cool or heat the fluid in the closed fluid circuit, and the cooled or heated fluid is circulated from the upper floor toward the lower floor radiator, and the second The pump is operated to supply the fluid in the sealed fluid circuit to the heat exchanger, and is cooled or heated by the fluid in the heat storage fluid circuit, and this fluid is directed from the lower floor toward the radiator on the upper floor. A heat storage device characterized in that a second process of cooling or heating by flowing in a direction opposite to the flow from one pump can be selected.
[0006]
Embodiment
Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a configuration diagram of a heat storage device according to the first embodiment in which the present heat storage device is installed in a building (for example, a high-rise building).
[0007]
In the figure, reference numeral 1 denotes a refrigerator for combined use of cold heat and heat as a heat source device for supplementing nighttime heat storage and daytime insufficient heat quantity, and has a function of supplying cold heat and heat by switching. Reference numeral 2 denotes a first pump for supplying a fluid to the refrigerator / heater combined with refrigerator 1, and the refrigerator / heater combined with refrigerator 1 and the first pump 2 are arranged at the top of the fluid circuit (for example, the top floor of the building). ing. Reference numeral 3 denotes a radiator 3 for cooling or heating each floor in the building, and the radiator 3 is arranged for each floor. 4 is a heat exchanger arranged in the lowermost part of the fluid circuit (for example, the basement of a building) and stores heat in a heat storage tank (described later) 11 instead of cheap electric power, and 5 is near the heat exchanger. 2 is a second pump for flowing fluid to the radiator 3, 6 is a check valve that forms a one-way flow connected to the discharge side of the refrigerator 1 for cooling and heating / cooling, and 7 is an inflow side of the radiator 3. A control valve connected to the pipeline, 8 is a first switching valve for switching the pipeline, 9 is a second switching valve for switching the pipeline, and 10 is a control device.
[0008]
The refrigerator / heater combined with refrigerator 1, the first pump 2, and the heat exchanger 4 are connected in series with pipes indicated by symbols (F) and (K) in the figure, and the radiator 3 is connected to the refrigerator / heater. Between the combined refrigerator 1, the first pump 2 and the heat exchanger 4, a plurality of pipe lines arranged in parallel with respect to each of the cold / hot combined refrigerator 1, the first pump 2 and the heat exchanger 4 ( The second pump 5 is also arranged in a pipe (co) parallel to the heat exchanger 4. Further, the first switching valve 8 is disposed in the pipe (f), the second switching valve 9 is disposed in the pipe (g), and the first switching valve 8 includes the first pump 2 and the second switching valve. 9 is connected to a pipe line (9) between the pipes 9 and 9 by a pipe line (ke). The pipe line to which the refrigerator 1 for cooling / heating temperature, the first pump 2, the heat exchanger 4, the radiator 3 and the like are connected constitutes a closed fluid circuit as a whole.
Further, the first pump 2 and the second pump 5 have a function of changing the discharge flow rate according to the operating state, and the first and second switching valves 8 and 9 and the control valve 7 are both control devices. 10 is configured to control the switching of the pipeline and the flow rate.
[0009]
The heat exchanger 4 is connected to an open air fluid circuit (A), which is connected to a heat storage tank 11, and the open air fluid circuit includes a circulation pump 12 and two branch switching valves 13 and 14. ing.
The heat storage tank 11 has a tank partitioned by a plurality of partition walls 15, and each tank communicates with a communication pipe 16, and among them, the left tank 17 functions as a low temperature side and the right tank 18 functions as a high temperature side. Each tank is filled with a fluid such as water. The low-temperature side tank 17 and the high-temperature side tank 18 of the heat storage tank 11 have pipes (c), (e), (a), and (e) connected to the two branch switching valves 13 and 14, respectively. The atmosphere open type fluid circuit and the heat storage tank 11 constitute a heat storage means for storing surplus power instead of heat. This heat storage means is conventionally known, and various heat storage means can be used, and since it is not a feature of the present invention, detailed description thereof is omitted.
[0010]
Next, the operating state of the heat storage device will be described.
Cooling heat storage (Figure 2)
FIG. 2 is a system diagram showing a state in which cold electricity is stored in the heat storage tank 11 using inexpensive electric power, and is a pipe line in a state where a thick line is operated.
basic action
In the closed fluid circuit, the cooling / heating refrigerator 1 and the first pump 2 which are heat sources are in an operating state, and the first switching valve 8 and the second switching valve 9 are sealed fluid circuits (f), (g). Are switched to communicate with each other, the control valve 7 for each radiator 3 is forcibly shut off, and the second pump 5 is stopped. On the atmosphere open circuit (A) side, the circulation pump 12 is operated, and the branch switching valves 13 and 14 are switched so as to form a direct current as shown in the figure.
In this state, on the open air circuit side, from the upper part of the heat storage tank 11 on the high temperature tank 18 side, the high cold water pumped up by the circulation pump 12 through the pipe (c) (heat storage tank water whose temperature has been increased on the previous night). ) Is cooled by the cold water cooled by the cold / hot refrigeration refrigerator 1 by the heat exchanger 4. This cooled heat storage tank water is transferred to the low temperature tank 17 side of the heat storage tank 11 through the pipes (a) and (b) and stored. If this situation continues, the low-temperature tank 17 in the heat storage tank 11 is filled with cooled cold water, and if further continued, it is transferred to the next tank connected by the communication pipe 16, and the inside of the heat storage tank 11 is sequentially cooled by cold water. The heat is stored.
On the other hand, in the closed fluid circuit, the heat storage tank water in the open-air circuit is cooled by the heat exchanger 4 with the cold water cooled by the refrigerator 1 for cooling and heating / cooling. The first pump 2 supplies the cooling / heating / heating refrigerator 1 with cooling, and then supplies it to the heat exchanger 4 again.
[0011]
During cooling and heat dissipation (Figure 3)
FIG. 3 is a diagram of a state in which the cold energy stored in the heat storage tank 11 is used and cooling is performed by using the refrigerator 1 that is combined with the cold / hot temperature, and a pipe line in a state where a thick line is operated in the drawing The fluid flow for each radiator 3 is indicated by a thick dotted line.
basic action
In the closed fluid circuit, the cold / hot refrigerator 1 and the first pump 2 which are heat sources are in an operating state, and the second switching valve 9 connects the heat exchanger 4 and the suction port of the second pump 5, The first switching valve 8 is switched to connect the heat exchanger 4 and the suction port of the first pump 2. Furthermore, the control valve 7 for each radiator 3 is actuated by a command from the control device 10 so as to be in an open / closed state according to the flow rate required by each radiator 3, and the second pump 5 is put into an operating state.
On the other hand, on the open circuit side, the circulation pump 12 is operated, and the branch switching valves 13 and 14 are switched so as to form a direct current as shown in the figure.
Basic operation status
In the open air circuit, low-temperature cold water (heat storage tank water cooled on the previous night) pumped by the circulation pump 12 from the lower part of the heat storage tank 11 on the low temperature tank 17 side via the pipe (e) passes through the heat exchanger 4. Then, the chilled water whose temperature has been raised by the radiator 3 in the sealed fluid circuit is cooled. The heat storage tank water whose temperature has been increased is transferred to the high temperature tank 18 side of the heat storage tank 11 through a pipe (d). If this situation continues, the high-temperature tank 18 in the heat storage tank 11 is filled with high-temperature cold water that has been raised in temperature. The inside will be filled.
On the other hand, in the closed fluid circuit, the cold water cooled by the cold water in the heat storage tank 11 through the heat exchanger 4 is pumped up by the second pump 5 through the second switching valve 9 and the pipe (co), and the common pipe (f) The inside flows in the opposite direction to the heat storage, and the amount of cold water required for each radiator 3 is supplied according to the opening of the control valve 7 to exchange heat. Here, the chilled water whose temperature has increased again flows through the common pipe (ki) in the opposite direction to that during heat storage by the second pump 5 and is supplied to the heat exchanger 4 via the first switching valve 8.
In addition, the chilled water supplied and cooled to the refrigerator / heater combined with chiller 1 by the operation of the first pump 2 flows in the same direction as the heat storage through the check valve 6 and the common pipe (f), and a nearby radiator 3 is supplied with the amount of cold water required by each according to the degree of opening of the control valve 7 to exchange heat. The chilled water whose temperature has risen flows in the same direction as in the heat storage through the common pipe (ki), and is again supplied to the chiller / heater combined refrigerator 1 by the first pump 2 to be cooled, and the above items are repeated.
[0012]
Operating conditions when the daytime load is less than the maximum load and is greater than or equal to the amount of heat stored in the heat storage tank
The operation of the closed fluid circuit controls the circulation amount of the first pump 2 according to the load state of each radiator 3.
The entire load is handled by the cold / hot refrigerator 1 and the heat storage from the heat storage tank 11 respectively, and the amount of cold water supplied by the second pump 5 is preferentially passed to each radiator 3, and the water whose temperature has increased is a heat exchanger. 4 to cool to the temperature to be supplied to each radiator 3.
When the load amount decreases from the overall maximum load amount and is equal to or greater than the heat storage amount possessed by the heat storage tank 11, the second pump 5 operates in the initial state (the amount of load at the maximum load). At this time, the control device 10 controls the first pump 2 to operate the first pump 2 so that the decrease in the total necessary circulation amount due to the decrease in the total load amount is reduced from the initial state (the amount of sharing at the maximum load). To do. As a result, the operating load of the refrigerator 1 for cooling and heating / heating depends on the supply amount and temperature of the supplied cold water from the first pump 2, and the refrigeration function is controlled by the supply load amount.
On the other hand, in the open air circuit, the relationship between the heat storage tank 11 and the heat exchanger 4 performs the same operation as in the basic operation state of FIG. That is, the circulation pump 12 draws cold water from the heat storage tank 11 and supplies it to the heat exchanger 4 in order to handle the load of the sealed circuit in a range that can be handled by the heat exchanger 4. For example, in a 10-story building, at the maximum load, in a facility that is designed so that the cold / hot refrigerator / freezer 1 and the heat exchanger 4 for the heat storage tank 11 each take half heat treatment.
When the total load is reduced to 80%, the refrigerator / heater 1 and the first pump 2 correspond to the upper load (heat radiator 3) of the fourth floor, and the heat storage tank 11 and the second pump 5 The heat storage from the top corresponds to the load (heatsink 3) for the lower six floors. The supply of cold water from the first pump 2 and the second pump 5 to the radiator 3 is performed sequentially from the radiator 3 immediately adjacent to each pump through the common pipe (f), and the last radiator 3 has both The required amount is supplied from the pump.
[0013]
Operating conditions when the daytime load is less than the maximum load and is less than or equal to the amount of heat stored in the heat storage tank
In the closed fluid circuit, the circulation amount of the first pump 2 is controlled according to the load condition of each radiator 3, and as a result, the cold / hot refrigerator 1 is secondarily controlled.
When the load amount is reduced from the overall maximum load amount and the heat exchange by the heat storage from the heat storage tank 11 becomes less than the capacity of the heat exchanger 4 (that is, the heat from the heat storage tank 11 can sufficiently cover the load). In this case, at this time, the control device 10 causes the cooling / heating refrigerator 1 to stop due to a decrease in the total load, and simultaneously stops the first pump 2. The second pump 5 is responsible for the total necessary circulation amount and supplies the heat in the heat storage tank 11 to each radiator 3 load via the heat exchanger 4. In order to correspond to the total load amount that the second pump 5 also takes charge, the operation is performed by reducing the decrease amount of the load amount from the initial state (the amount of sharing at the maximum load).
The flow of cold water at this time circulates in the flow direction opposite to that at the time of heat storage in the common pipe (f), and the check valve 6 stops the flow to the cold heat storage combined refrigerator 1 and the first pump.
The relationship between the heat storage tank 11 and the heat exchanger 4, which is an open-air circuit, performs the same operation as in the basic operation state in FIG.
That is, the circulation pump 12 draws cold water from the heat storage tank 11 and supplies it to the heat exchanger 4 in order to handle the load of the sealed fluid circuit in a range that can be handled by the heat exchanger 4.
When the load of the closed fluid circuit decreases below the maximum processing capacity of the heat exchanger 4, the circulation pump 12 changes to a circulation amount corresponding to the load amount.
[0014]
For example, in a 10-storey building, at the maximum load, in a facility that is designed so that the heat storage from the cold / hot refrigerator 1 and the heat storage tank 11 each take half heat treatment.
When the total load amount is reduced to 40%, the control device 10 stops the refrigerator / heater 1 and the first pump 2, and the heat exchanger 4 and its circulation pump 12 are activated by the heat storage from the heat storage tank 11. It corresponds to all loads (heat radiator 3). The circulation amount of the second pump 5 is controlled according to the load amount. The cold water is supplied from the second pump 5 to all the radiators 3 through the common pipe (female) from the radiator 3 immediately adjacent to the pump to the tip.
At this time, the circulation amount of the circulation pump 12 on the open circuit side is controlled in accordance with the load amount similarly to the circulation amount of the second pump 5.
[0015]
During heat storage (Figure 4)
basic action
In the closed fluid circuit, the cooling / heating refrigerator 1 and the first pump 2 which are heat sources are operated, and the first switching valve 8 and the second switching valve 9 operate so as to form a direct current as shown in the figure, and each heat release. The control valve 7 for the vessel 3 is forcibly closed and the second pump 5 is stopped.
In the open air circuit, the circulation pump 12 is operated, and the branch switching valves 13 and 14 are operated so as to form a right-angle flow as shown in the figure.
Basic operation status
In the open air circuit, the low-temperature water (heat storage tank water whose temperature has been lowered on the previous night) pumped by the circulation pump 12 from the lower part of the heat storage tank 11 on the low-temperature tank 17 side through the pipe (v) is a heat exchanger. 4 is heated by hot water heated by the cold / hot refrigerator 1. The heated heat storage tank water is transferred to the high temperature tank 18 side of the heat storage tank 11 via a pipe (d) and stored. If this situation continues, the high-temperature tank 18 in the heat storage tank 11 is filled with warmed hot water, and if further continued, it is transferred to the adjacent tank connected by a communication pipe, and is sequentially heated in the heat storage tank 11 by the heated water. The heat is stored.
On the other hand, in the closed fluid circuit, the heat storage tank water is heated by the heat exchanger 4, and the low-temperature water whose temperature has been lowered is supplied to the cold / hot refrigerator 1 by the first pump 2 and is again supplied to the heat exchanger 4. Supplied and repeat above.
[0016]
During heat dissipation (Figure 5)
basic action
The hermetic fluid circuit includes a cooling / heating refrigerator / heater 1 that is a heat source, the first pump 2 is operated, and the first switching valve 8 and the second switching valve 9 operate so as to form a right-angle flow as shown in FIG. The control valve 7 for the radiator 3 is controlled so as to be in an open / closed state according to the flow rate required for each radiator 3, and the second pump 5 is in an operating state.
On the open air circuit side, the circulation pump 12 is operated, and the branch switching valves 13 and 14 are operated so as to form a direct current as shown in the figure.
Basic operation status
On the open air circuit side, the high-temperature water (heat storage tank water heated on the previous night) pumped up by the circulation pump 12 from the upper part of the heat storage tank 11 on the high temperature tank 18 side through the pipe (c) is the heat exchanger 4. Then, the low-temperature water whose temperature has been lowered by the radiator 3 on the sealed fluid circuit side is heated. The temperature-reduced heat storage tank water is transferred to the low-temperature tank 17 side of the heat storage tank 11 via a pipe (A). If this state continues, the low temperature tank 17 in the heat storage tank 11 is filled with low temperature water whose temperature has been lowered, and if further continued, it is transferred to the adjacent tank connected by the communication pipe 16 and is sequentially stored by the low temperature water whose temperature has been lowered. 11 will be filled.
On the other hand, on the closed circuit side, the warm water heated by the warm water in the heat storage tank 11 via the heat exchanger 4 by the second pump 5 passes through the second switching valve 9 and the common pipe (ka) via the pipe (co). Low temperature water that flows in the opposite direction to the time of heat storage, and supplies the required amount of hot water to the nearby radiator 3 according to the opening degree of the control valve 7 to the radiator 3 to exchange heat and lower the temperature. Flows through the common pipe (ki) in the opposite direction to that during heat storage and is supplied to the heat exchanger 4 again by the action of the second pump 5. The warm water supplied to the cold / hot refrigerator 1 through the operation of the other first pump 2 flows through the check valve 6 and the common pipe (f) in the same direction as when storing heat. The amount of hot water required for each adjacent radiator 3 is supplied to the radiator 3 according to the opening degree of the control valve 7 to exchange heat, and the low-temperature water whose temperature has dropped is the same as when storing heat in the common pipe (ki). After flowing in the direction, the first pump 2 supplies the heat to the cold / hot refrigerator 1 again and is heated, and the above-described matters are repeated.
[0017]
Operating conditions when the daytime load is less than the maximum load and is greater than or equal to the amount of heat stored in the heat storage tank
The operation of the closed fluid circuit controls the circulation amount of the first pump 2 according to the load state of each radiator 3.
The entire load is handled by the refrigerator 1 for both heat and cold and the heat storage from the heat storage tank 11, and the amount of hot water supplied by the second pump 5 is given to each radiator 3 preferentially, and the water dropped by the radiator 3 is heated. It heat-processes again with the exchanger 4. FIG.
When the load amount is reduced from the overall maximum load amount and the load is equal to or greater than the heat storage capacity in the heat storage tank 11, the second pump 5 is operated in an initial state (a share amount at the maximum load). At this time, the first pump 2 operates by reducing the decrease in the total necessary circulation amount due to the decrease in the total load amount from the initial state (the amount of sharing at the maximum load). As a result, since the operating load of the refrigerator / heater combined with refrigerator 1 depends on the supply amount and temperature of the supply hot water from the first pump 2, the refrigerator / heater combined refrigerator 1 is controlled by the supply load. The relationship between the heat storage tank 11 and the heat exchanger 4 which is an open circuit is the same as the basic operation of FIG.
The circulation pump 12 draws hot water from the heat storage tank 11 and supplies it to the heat exchanger 4 in order to handle the load of the sealed fluid circuit in a range that can be handled by the heat exchanger 4.
[0018]
For example, in a 10-story building, at the maximum load, in a facility that is designed so that the heat storage in the refrigerator / heater combined with refrigerator 1 and the heat storage tank 11 are each subjected to half heat treatment.
When the total load is reduced to 80%, the refrigerator / heater 1 and its first pump 2 correspond to a load (heat radiator 3) of about four floors from the top, and the heat storage from the heat storage tank 11 is reduced. Corresponds to the load (heatsink 3) for about 6 floors from the bottom. The supply of hot water from the first pump 2 and the second pump 5 to the radiator 3 is carried out sequentially from the radiator 3 immediately adjacent to the pump to the tip through the common pipe (f), and the last radiator 3 has both The required amount is supplied from the pump.
[0019]
Operating conditions when the daytime load is less than the maximum load and is less than or equal to the amount of heat stored in the heat storage tank
In the operation of the closed fluid circuit, the circulation amount of the first pump 2 is controlled according to the load state of each radiator 3, and as a result, the refrigerator 1 for cooling and heating / heating is controlled secondarily.
When the load amount decreases from the overall maximum load amount and becomes less than the heat storage amount in the heat storage tank 11 (that is, when all the loads can be covered by the heat storage amount of the heat storage tank 11), the first pump 2 at this time When it stops due to a decrease in the amount, the cold / hot refrigerator 1 also stops simultaneously. The second pump 5 is responsible for the total necessary circulation amount and supplies the heat in the heat storage tank 11 to each radiator 3 load via the heat exchanger 4. In order to correspond to the total load amount that the second pump 5 also takes charge, the operation is performed by reducing the decrease amount of the load amount from the initial state (the amount of sharing at the maximum load).
The flow of hot water at this time circulates in the common pipe (f) in the direction of flow opposite to that during heat storage, and the check valve 6 stops the flow to the cold heat storage combined refrigerator 1 and the first pump.
The relationship between the heat storage tank 11 and the heat exchanger 4, which is an open-air circuit, performs the same operation as in the basic operation state of FIG.
The circulation pump 12 draws hot water from the heat storage tank 11 and supplies it to the heat exchanger 4 in order to handle the load of the sealed fluid circuit in a range that can be handled by the heat exchanger 4.
When the load of the closed fluid circuit is reduced below the maximum processing capacity of the heat exchanger 4, the second pump 5 changes to a circulation amount corresponding to the load amount.
[0020]
For example, in a 10-storey building, at the maximum load, in a facility that is planned so that each of the cold / hot refrigerator 1 and the heat storage in the heat storage tank 11 is half-heat treated.
When the entire load amount is reduced to 40%, the refrigerator / heater 1 and its first pump 2 are stopped, and the heat storage in the heat storage tank 11 corresponds to all loads (heat radiator 3). The circulation amount of the second pump 5 is controlled according to the load amount. The supply of warm water from the second pump 5 to all the radiators 3 is performed through the common pipe (female) from the radiator 3 immediately adjacent to the pump to the tip.
At this time, the circulation amount of the circulation pump 12 on the atmosphere open circuit side is controlled according to the load amount in the same manner as the circulation amount of the first pump 2.
[0021]
Next, the heat storage device according to the second embodiment will be described with reference to the drawings. FIG. 6 is a configuration diagram in which the heat storage device according to the second embodiment is installed in a high-rise building.
As shown in FIG. 6, in the second embodiment, the control valve 7 arranged on the upstream side of the radiator (load) 3 in the first embodiment is arranged on the downstream side of the radiator 3, and the control valve 7A is arranged. While differing from the first embodiment in that it is a three-way valve and the control valve 7A and the upstream side of the radiator 3 are connected. Since other configurations are the same as those of the first embodiment, description thereof will be omitted.
Although the operation state of the second embodiment is basically the same as that of the first embodiment, each operation state will be briefly described below.
Cooling heat storage (Figure 7)
FIG. 7 is a system diagram showing a state in which cold heat is stored in the heat storage tank 11 using inexpensive electric power, and a pipe line in a state where a thick line is operated. This state is the same as in the first embodiment, and on the open air circuit side, high-temperature cold water (used on the previous night) pumped up by the circulation pump 12 from the upper part of the heat storage tank 11 on the high-temperature tank 18 side via the pipe (c). The heat storage tank water whose temperature has risen) is cooled by the cold water cooled by the cold / hot heat combined use refrigerator 1 by the heat exchanger 4, and heat is stored in the heat storage tank 11. This state is the same as in the first embodiment.
[0022]
During cooling heat dissipation (Fig. 8)
FIG. 8 is a diagram showing a state in which the cold energy stored in the heat storage tank 11 is used and cooling is performed by using the refrigerator 1 that is also used for cooling and heating, and the thick line in the drawing is in operation. The fluid flow for each radiator 3 is indicated by a thick dotted line. In this state, the operation status in the closed fluid circuit is different from that in the first embodiment.
That is, in the open air circuit, the low cold water (heat storage tank water cooled on the previous night) pumped by the circulation pump 12 from the lower part of the heat storage tank 11 on the low temperature tank 17 side through the pipe (v) is the heat exchanger 4. Then, the chilled water whose temperature has been raised by the radiator 3 in the sealed fluid circuit is cooled.
On the other hand, in the closed fluid circuit, the cold water cooled by the cold water in the heat storage tank 11 through the heat exchanger 4 is pumped up by the second pump 5 through the second switching valve 9 and the pipe (co), and the common pipe (f) It flows in the direction opposite to that during heat storage, and the amount of cold water required by each radiator 3 is supplied according to the opening of the control valve 7A to exchange heat. Further, the extra cold water in the radiator 3 is mixed with the high cold water whose temperature has been increased by heat exchange in the radiator 3 via the control valve 7A, and the common pipe (ki) is again recharged by the second pump 5 in the direction opposite to that during heat storage. And then supplied to the heat exchanger 4 via the first switching valve 8.
In addition, the chilled water supplied and cooled to the refrigerator / heater combined with chiller 1 by the operation of the first pump 2 flows in the same direction as the heat storage through the check valve 6 and the common pipe (f), and a nearby radiator 3 is supplied with the amount of cold water required by each according to the opening degree of the control valve 7A to exchange heat. The extra cold water in the radiator 3 is mixed with high cold water whose temperature has been increased by heat exchange in the radiator 3 via the control valve 7A, and is again supplied to the cold / hot refrigerator 1 by the first pump 2 and cooled. Repeat the above. In this way, the amount of cold water that is heat-exchanged through the radiator 3 can be controlled to an amount required by the radiator, thereby further improving the efficiency of heat exchange.
[0023]
During heating and heat storage (Figure 9)
In the open air circuit, the low-temperature water (heat storage tank water whose temperature has been lowered on the previous night) pumped by the circulation pump 12 from the lower part of the heat storage tank 11 on the low-temperature tank 17 side through the pipe (v) is a heat exchanger. 4 is heated by hot water heated by the cold / hot refrigerator 1.
On the other hand, in the closed fluid circuit, the heat storage tank water is heated by the heat exchanger 4, and the low-temperature water whose temperature has been lowered is supplied to the cold / hot refrigerator 1 by the first pump 2 and is again supplied to the heat exchanger 4. Supplied and repeat above. This state is the same as in the first embodiment.
[0024]
During heat dissipation (Fig. 10)
basic action
FIG. 10 is a diagram of a state in which heating is performed using the cold / hot refrigerator combined use 1 while using the heat stored in the heat storage tank 11, and a pipe line in a state where a thick line is operated The fluid flow for each radiator 3 is indicated by a thick dotted line. In this state, the operation status in the closed fluid circuit is different from that in the first embodiment.
That is, on the open air circuit side, the high-temperature water (heat storage tank water heated on the previous night) pumped up by the circulation pump 12 through the pipe (c) from the upper part of the heat storage tank 11 on the high temperature tank 18 side is heat exchanged. The low temperature water whose temperature has been lowered by the radiator 3 on the sealed fluid circuit side is heated via the vessel 4.
On the other hand, on the closed circuit side, the warm water heated by the warm water in the heat storage tank 11 via the heat exchanger 4 by the second pump 5 passes through the second switching valve 9 and the common pipe (ka) via the pipe (co). The heat flows in the opposite direction to that during heat storage, and the amount of hot water required for each nearby radiator 3 is supplied to the radiator 3 according to the opening of the control valve 7A to exchange heat. Further, the extra warm water in the radiator 3 is mixed with the low-temperature water whose temperature has been lowered by heat exchange in the radiator 3 through the control valve 7A, and the second pump 5 again uses the common pipe (ki) in the direction opposite to that during heat storage. And then supplied to the heat exchanger 4 via the first switching valve 8.
The warm water supplied to the cold / hot refrigerator 1 through the operation of the other first pump 2 flows through the check valve 6 and the common pipe (f) in the same direction as when storing heat. The amount of hot water required by each of the nearby radiators 3 is supplied according to the opening degree of the control valve 7A to exchange heat. Further, the extra hot water in the radiator 3 is mixed with the low-temperature water whose temperature has been reduced by heat exchange in the radiator 3 through the control valve 7A, and is supplied again to the cold / hot refrigerator 1 by the first pump 2 and cooled. Repeat the above. Thus, the amount of hot water exchanged through the radiator 3 can be controlled to an amount required by the radiator, thereby further improving the heat exchange efficiency.
[0025]
As mentioned above, although embodiment which concerns on this invention was described, these embodiments demonstrate an advantage compared with the conventional heat storage apparatus.
[Differences in piping equipment between the present invention and the conventional apparatus, the amount of cold and hot water circulation, and the conveyance power thereof]
Each device is determined so that it can cope with the maximum load.
At maximum load
・ In general, it is economical to design the entire system so that the entire load is not covered by the heat storage in the heat storage tank, 50% is handled by the heat storage amount, and the remaining 50% is handled by the chasing operation of the refrigerator. Many in terms of This case is tentatively referred to herein as a general method.
In this general method,
・ Radiator full load = qL
・ Freezing function = qR
-Heat exchanger capacity for heat storage tank = qHEX (qR)
・ The temperature difference between the radiator inlet and outlet is ΔT
If
qL = qR + qHEX
= 2 × qR.
[0026]
In the case of the system shown in FIG. 11 (conventional system), which is a general method,
Since the heat radiation operation at the maximum load during heat radiation corresponds to the total load of each radiator 111, if the necessary circulation amount QL is supplied from the heat storage tank to the radiator system by the circulation pump P2, the use temperature difference in the heat storage tank is also increased. ΔT can be set,
Because qL = QL · ΔT
QL = qL / ΔT
Also, the amount of circulation Q between the refrigerator and the heat storage tank during heat storage _ST Is supplied from the heat storage tank to the refrigerator 1 by the circulation pump P1.
qR = Q _ST ・ Because it is ΔT
Q _ST = QR / ΔT = 1/2 × qL / ΔT
[0027]
That is, in the conventional system of FIG. 11, the circulation amount in the main pipe between the refrigerator and the heat storage tank during heat storage is Q _ST = 1/2 × qL / ΔT is necessary, and the circulation amount in the main part between the heat storage tank and each radiator during heat radiation requires QL = qL / ΔT.
Next, in the case of the system shown in FIG. 12 (conventional system), which is one of the general methods, the operation at the maximum load during heat radiation corresponds to the full load of each radiator load 201. Both the heat storage tank heat exchanger 203 and the refrigerator R1 as heat source devices correspond to each other.
That is, each heat source device corresponds to the temperature increase ΔT due to the total radiator load in series by 1/2 × ΔT.
The total required circulation volume Q at this time _LO If the temperature difference between the radiator inlet and outlet is ΔT,
qL = Q _LO × ΔT = 2 × qR = 2 · qHEX
Q _LO = (2 × qR) / ΔT = (2 × qHEX) / ΔT = qL / ΔT.
That is, the circulation rate is Q for both the refrigerator and heat storage tank heat exchanger. _LO = QL / ΔT is required. At this time, as described above, the temperature difference resulting from the heat treatment of the load via the heat storage tank heat exchanger is 1/2 × ΔT, and the use temperature difference in the heat storage tank is determined via the heat storage tank heat exchanger 203. Therefore, the use temperature difference is also ½ × ΔT.
In addition, the amount of circulating water Q between the refrigerator and the heat storage tank heat exchanger during heat storage _STO Is
qR = Q _STO Because x (1/2) × ΔT
Q _STO = (2 × qR) / ΔT = qL / ΔT.
That is, in the conventional system of FIG. 12, the main pipe directly connecting the refrigerator and the heat storage tank heat exchanger during heat storage, and the main pipe connecting the refrigerator, the heat storage tank heat exchanger and the radiator during heat dissipation. Both flowing flow
Q _LO = Q _STO = QL / ΔT is required.
[0028]
According to the present invention
Under the general method that the heat storage tank handles 50% of the full load
qL = qR + qHEX
Because qR = qL / 2
qHEX = qL × 1/2
・ The temperature difference between the radiator inlet and outlet is ΔT
Under the same conditions as the previous method
At the time of heat radiation, as shown in FIG. 3 (flow diagram at the time of heat radiation at the time of cooling), the refrigerator and the heat storage tank heat exchanger share each other while dividing the entire radiator load into two parts. When the load is divided into two, the amount of circulation between the refrigerator and the radiator to which it corresponds, the amount of circulating water between the heat storage tank heat exchanger and the radiator to which it corresponds is the same, This circulation amount Q _LN Is
qR = qHEX = Q _LN × ΔT = qL / 2
Q _LN = 1/2 × qL / ΔT
Therefore, the necessary amount of circulation between the heat radiator, the refrigerator, and the heat exchanger for the heat storage tank at the time of heat radiation in the present invention is the necessary amount of circulation Q in the system of FIG. _L = 1/2 of qL / ΔT
Similarly, the circulation amount Q in the system of FIG. _LO = 1/2 of qL / ΔT.
In addition, during heat storage, the amount of circulating water Q between the refrigerator and the heat storage tank heat exchanger _STN Is
qR = ΔT × Q _STN = QHEX = 1/2 qL
Q _STN = Q _LN = 1/2 × qL / ΔT
The necessary amount of circulation between the refrigerator and the heat exchanger for the heat storage tank in the present invention is the necessary amount of circulation in the system of FIG.
Q _ST = Same amount as 1/2 × qL / ΔT,
Required circulation volume Q in the system of Fig.-12 _STO = 1/2 of qL / ΔT.
[0029]
As described above, the main pipe directly connecting the refrigerator and the heat storage tank heat exchanger according to the present invention and the supply main pipe to the radiator can reduce the circulation amount as described above, As a result, the pipe diameter can be reduced.
Further, since the circulation amount is halved, the conveyance power can be reduced.
Furthermore, regarding the heat utilization temperature difference in the heat storage tank, compared to the system in Fig. 7, the temperature difference in the heat exchanger for heat storage tank can be doubled from ΔT / 2 to ΔT, so the same amount of heat. When storing heat, the heat storage tank volume can be reduced to 1/2.
As a result, the present invention can reduce the pipe diameter as compared with the conventional system and can also reduce the volume of the heat storage tank to ½, thereby reducing the initial cost of the apparatus. .
As for energy saving, the conveyance power can be greatly reduced by reducing the circulation amount to ½, and energy saving is also exhibited.
As described above, according to the present invention, two main pipes can be used for both heat storage and heat dissipation, and the thickness of the pipe can be made thinner than that of the conventional one, and heat radiation can be handled at the maximum load. In comparison with the conventional system, the circulation amount of each pump and the shared area of the radiator 3 can be reduced to about one-half, and not only the power consumption of each pump but also the total consumption of them. Can be reduced. Furthermore, the circulation amount is halved compared with the conventional method, and the thickness of the piping can be reduced, and the construction cost can be reduced.
In addition, although the example using the cold / hot temperature combined use refrigerator as a heat source machine was demonstrated in the said embodiment, a single heating machine or a refrigerator can also be used as a heat source machine, or it can also use together. Moreover, as a heat medium used for this system, various heat media which can achieve the function of this system, such as water and a brine, can be used. Furthermore, in the above-described embodiment, a specific example of plumbing up and down like a building has been described. However, a sealed fluid circuit capable of circulating fluid and a heat storage fluid circuit capable of circulating fluid from a heat storage tank Of course, similar effects can be achieved even if they are arranged on the same plane. The present invention can be carried out in various other forms without departing from the spirit or main features thereof, and the above-described embodiments are merely examples in all respects, and are interpreted in a limited manner. Must not.
[0030]
【The invention's effect】
As described in detail above, according to the present invention,
In this heat storage device, both main heat storage and heat dissipation can be handled by two main pipes, and the thickness of the pipe can be made thinner than that of the conventional one.
In response to heat dissipation at the maximum load, compared to the conventional system, the circulation amount that each pump is responsible for and the shared area of the radiator 3 can be reduced to about one-half, not only the power consumption of each pump, Their total consumption can be reduced. In addition, the circulation amount is halved compared with the conventional method, so that the thickness of the pipe can be reduced and the construction cost can be reduced.
During daytime heat dissipation of this device, if the daytime load is greater than the amount of heat storage, that is, if the heat of the heat storage tank and the heat of the heat source device are used simultaneously via a heat exchanger, it is equal to the use temperature difference of each radiator Each heat source can cope with the temperature difference. On the other hand, in a system in which a conventional refrigerator and a heat exchanger are in a series arrangement with a sealed pipe, the use temperature difference of each radiator is handled by the refrigerator and the heat exchanger for the heat storage tank. The temperature difference processed by the heat source is small. As described above, this method can increase the temperature processing range of each heat source as compared with the conventional method.
In the case of 50% heat storage with respect to the maximum load during the day, a pump that conveys the amount of heat extracted from the heat exchanger (heat storage tank) and a pump that responds to the shortage are installed at opposite positions on the main pipe. The discharge flow of each pump flows in the main pipe so as to face each other. Cold and hot water supplied from two pumps installed at both ends is divided and supplied from each end to each radiator via a branch pipe from the main pipe, and finally from both pumps to the last radiator in the middle of the main pipe The supplied cold / hot water is supplied as a necessary amount through the branch pipe. The two pumps share and share the amount and location required by each radiator. At the maximum load, the two are equally divided and shared, but in other cases, control is performed so that the majority of the heat storage tank uses heat. At maximum load, the conveyance power is drastically reduced, saving energy and reducing power costs.
And so on.
[Brief description of the drawings]
FIG. 1 is an overall configuration diagram of a heat storage device according to an embodiment of the present invention.
FIG. 2 is an explanatory diagram of an operation state during cooling heat storage of the apparatus.
FIG. 3 is an explanatory diagram of an operation state during cooling and heat dissipation of the apparatus.
FIG. 4 is an explanatory diagram of an operation state of the apparatus during heating and heat storage.
FIG. 5 is an explanatory diagram of an operation state during heating and heat dissipation of the apparatus.
FIG. 6 is an overall configuration diagram of a heat storage device according to a second embodiment of the present invention.
FIG. 7 is an explanatory diagram of an operation state during cooling heat storage of the apparatus.
FIG. 8 is an explanatory diagram of an operation state during cooling and heat dissipation of the apparatus.
FIG. 9 is an explanatory diagram of an operation state of the device during heating and heat storage.
FIG. 10 is an explanatory diagram of an operation state at the time of heat radiation of the apparatus.
FIG. 11 is an overall configuration diagram of a conventional heat storage device.
FIG. 12 is an overall configuration diagram of another conventional heat storage device.
[Explanation of symbols]
1 Refrigerator combined with heat and heat
2 First pump
3 radiators
4 Heat exchanger
5 Second pump
6 Check valve
7, 7A Control valve
8 First switching valve
9 Second switching valve
10 Control device
11 Thermal storage tank
12 Circulation pump
13, 14 Branch switching valve
15 Bulkhead
16 communication pipe
17 Low temperature tank
18 High temperature bath

Claims

A heat source unit, a first pump for supplying fluid to the heat source unit, and a heat exchanger are arranged in this order in a sealed fluid circuit capable of circulating the fluid, and further, the heat source unit and the first pump. In addition, a plurality of pipelines are provided in parallel to the heat exchanger, a radiator is disposed in each of these pipelines, and another parallel pipeline different from the above is provided for the heat exchanger. And a heat storage fluid circuit capable of circulating the fluid from the heat storage tank separately from the sealed fluid circuit, to the heat exchanger,
The heat source device and the first pump in the sealed fluid circuit are operated to cool or heat the fluid in the sealed fluid circuit by the heat source device, and the cooled or heated fluid is passed through the heat exchanger to A first process of cooling or heating the fluid in the heat storage fluid circuit to store heat in the heat storage tank, and the heat source device and the first pump in the sealed fluid circuit are operated as necessary and sealed by the heat source device. Cools or heats the fluid in the mold fluid circuit, circulates the cooled or heated fluid to the radiator, and operates the second pump to supply the fluid in the sealed fluid circuit to the heat exchanger And cooling or heating with the fluid of the heat storage fluid circuit, and allowing the fluid to flow in a direction opposite to the flow from the first pump to the radiator to select the second process of cooling or heating. With features That heat storage device.

A heat source machine and a first pump connected in series to the heat source machine and supplying fluid to the heat source machine are arranged on the upper floor of a building composed of a plurality of floors, and a heat exchanger is arranged on the ground floor. A series fluid pipe is connected in series with a closed fluid circuit, and a pipe line in parallel with the heat source machine and the first pump is provided for each floor between the heat source machine and the first pump and the heat exchanger in the sealed fluid circuit. And a radiator is arranged in each pipeline, a pipeline is formed in parallel to the ground side with respect to the heat exchanger, a second pump is arranged in the pipeline, and the heat In addition to the sealed fluid circuit, the exchanger is connected to an open air heat storage fluid circuit that can circulate the fluid from the heat storage tank to form a fluid circuit,
The first pump in the sealed fluid circuit is operated to cool or heat the fluid in the sealed fluid circuit by the heat source unit, and the cooled or heated fluid is passed through the heat exchanger to flow in the heat storage circuit. A first process for storing heat in the heat storage tank by cooling or heating the fluid, and a heat source device and a first pump in the sealed fluid circuit are operated as necessary, and the heat source device operates in the sealed fluid circuit. The fluid is cooled or heated, and the cooled or heated fluid is circulated from the upper floor to the lower floor radiator, and the second pump is operated to exchange the heat in the sealed fluid circuit. And is cooled or heated by the fluid in the heat storage fluid circuit, and the fluid is cooled or heated by flowing from the lower floor toward the radiator on the upper floor in a direction opposite to the flow from the first pump. You can choose between two processes Heat storage device, characterized in that had Unishi.

The heat storage device according to claim 1 or 2, wherein the heat source device is a refrigerator for both cold and hot temperature.

The heat storage device according to any one of claims 1 to 3, wherein a control valve is provided upstream of each radiator.

The heat storage fluid circuit connected to the heat exchanger is open to the atmosphere, and the circuit is provided with a heat storage tank, a circulation pump, and a switching valve. The heat storage device described in 1.

The heat storage device according to any one of claims 1 to 5, wherein the pipes constituting the sealed fluid circuit have substantially the same cross-sectional area.

A second switching valve is provided at a junction of the first pump suction side, the second pump suction side, and the pipe line connected to the heat exchanger, and in the pipe line connecting the discharge side of the second pump and the heat exchanger. A first switching valve is provided in the first switching valve, and the first switching valve is connected to a pipe line connecting the second switching valve and the first pump suction side. Crab heat storage device.

The heat storage device according to any one of claims 1 to 7, wherein the first pump and the second pump have substantially the same capacity.

The heat storage device according to any one of claims 1 to 8, wherein the heat source device and the heat exchanger are arranged at substantially symmetrical positions in a closed fluid circuit.

The heat storage device according to any one of claims 1 to 9, wherein a check valve is disposed on a discharge side of the heat source device.

The heat storage device according to any one of claims 1 to 10, wherein the fluid is water.

The heat storage device according to any one of claims 1 to 11, wherein in the second step, the discharge flow rates of the first pump and the second pump can be changed according to the heat radiation amount. .