JP4682493B2

JP4682493B2 - Absorption refrigeration system

Info

Publication number: JP4682493B2
Application number: JP2001293553A
Authority: JP
Inventors: 元八橋; 史朗薬師寺; 達己高瀬; 賢二安田
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2001-09-26
Filing date: 2001-09-26
Publication date: 2011-05-11
Anticipated expiration: 2021-09-26
Also published as: JP2003097861A

Description

【０００１】
【発明の属する技術分野】
【０００２】
本願発明は、吸収式冷凍装置、特に作動温度の異なる複数の再生器を備えてなる吸収式冷凍装置に関するものである。
【従来の技術】
【０００３】
一般に、吸収式冷凍装置は、凝縮器と蒸発器と吸収器及び再生器を基本構成要素とし、且つこれら各構成要素を溶液配管系と冷媒配管系とにより順次作動的に接続して構成される。
【０００４】
かかる吸収式冷凍装置においては、上記吸収器において生成された希溶液を上記再生器で加熱濃縮して濃溶液とし、さらにこれを上記吸収器に還流させる一方、上記再生器での希溶液の加熱濃縮によって生成された冷媒蒸気を上記凝縮器で凝縮させて液冷媒とするとともに、この液冷媒を上記蒸発器において蒸発させ、ここで発生した冷媒蒸気を上記吸収器で濃溶液に吸収させて希溶液を生成することで、吸収溶液と冷媒の循環サイクルが実現される。そして、通常、上記蒸発器における冷媒の蒸発熱を冷凍装置の冷熱源として利用されるものである。
【０００５】
ところで、吸収式冷凍装置では、その性能向上を図るには、溶液・冷媒循環系の熱効率を高めることが最も有効であることが知られており、これを具現化する手法として、再生器を複数設けて一つの外部熱源の熱を繰り返し再利用することが提案されている。即ち、再生器として、作動温度の異なるものを複数備え、高温で作動する高温側再生器の加熱によって生成される冷媒蒸気を、低温で作動する低温側再生器に導入し、これを該低温側再生器の加熱熱源として利用するものである。
【発明が解決しようとする課題】
【０００６】
ところが、従来の吸収式冷凍装置においては、再生器を複数化することによって所期の熱効率の向上効果は得られるものの、システム全体としての熱効率という点からすれば、未だ十分とは言えないものであった。
【０００７】
即ち、高温側の再生器で生成された冷媒蒸気で低温側の再生器を加熱する場合、この冷媒蒸気による再生器の加熱作用は、主として冷媒蒸気の潜熱変化によって行われ、従って冷媒蒸気は相変化してガス冷媒から液冷媒に変化するものの、依然として高い温度（顕熱）を保持している。しかるに、従来の吸収式冷凍装置においては、低温側の再生器の加熱作用を終えて凝縮した液冷媒は、これをそのまま冷媒ドレンとして凝縮器側へ還流させるのが通例であった。このため、上記冷媒ドレンが保有する顕熱を有効に利用できず、従って、本来ならば得られるであろう熱効率を、得ることができず、延いては吸収式冷凍装置の性能向上を図る上において障害となるものであった。
【０００８】
そこで本願発明は、吸収式冷凍装置における熱効率を改善することで、より一層の性能向上を図ることを目的としてなされたものである。
【課題を解決するための手段】
【０００９】
本願発明ではかかる課題を解決するための具体的手段として次のような構成を採用している。
【００１０】
本願の第１の発明では、少なくとも１個以上の凝縮器Ｃ、蒸発器Ｅ、吸収器Ａと、冷媒を含む吸収溶液が供給される作動温度の異なるｎ個（ｎ≧３）の再生器Ｇｎ〜Ｇ１を溶液配管系と冷媒配管系とで作動的に接続して循環サイクルを構成し、最も高温側の再生器Ｇｎの吸収溶液を外部熱源Ｊで加熱沸騰させて冷媒蒸気を発生させる一方、高温側の再生器Ｇｎで発生した冷媒蒸気を低温側の再生器Ｇｎ−１に導入しこれを該低温側の再生器Ｇｎ−１の加熱源として利用して該低温側の再生器Ｇｎ−１の溶液を加熱濃縮することを最も低温側の再生器Ｇ１まで繰り返すようにした吸収式冷凍装置において、最も高温側の再生器Ｇｎを除く他の再生器Ｇｎ−１〜Ｇ１における高温側の再生器Ｇｎ−１で発生した冷媒蒸気を低温側の再生器Ｇｎ−２へ供給する配管経路にフラッシュ室１を設け、該フラッシュ室１に上記高温側の再生器Ｇｎ−１を加熱した後の冷媒ドレンを導入しこれを再気化させるとともに、再気化した冷媒蒸気を上記高温側の再生器Ｇｎ−１で発生した冷媒蒸気と共に上記低温側の再生器Ｇｎ−２へ導入して該低温側の再生器Ｇｎ−２の加熱を行わせるように構成し、上記フラッシュ室１で再気化されずに残った残余ドレンが、上記低温側の再生器Ｇｎ−２を加熱した後の冷媒ドレンの配管系に、又は上記凝縮器Ｃにおける冷媒ドレン入口部に、又は該凝縮器Ｃへ直接に、戻されるようにしたことを特徴としている。
【００１１】
本願の第２の発明では、少なくとも１個以上の凝縮器Ｃ、蒸発器Ｅ、吸収器Ａと、冷媒を含む吸収溶液が供給される作動温度の異なるｎ個（ｎ≧３）の再生器Ｇｎ〜Ｇ１を溶液配管系と冷媒配管系とで作動的に接続して循環サイクルを構成し、最も高温側の再生器Ｇｎの吸収溶液を外部熱源Ｊで加熱沸騰させて冷媒蒸気を発生させる一方、高温側の再生器Ｇｎで発生した冷媒蒸気を低温側の再生器Ｇｎ−１に導入しこれを該低温側の再生器Ｇｎ−１の加熱源として利用して該低温側の再生器Ｇｎ−１の溶液を加熱濃縮することを最も低温側の再生器Ｇ１まで繰り返すようにした吸収式冷凍装置において、最も高温側の再生器Ｇｎを除く他の再生器Ｇｎ−１〜Ｇ１における高温側の再生器Ｇｎ−１で発生した冷媒蒸気を低温側の再生器Ｇｎ−２へ供給する配管経路にフラッシュ室１を設け、該フラッシュ室１に上記高温側の再生器Ｇｎ−１を加熱した後の冷媒ドレンを導入しこれを再気化させるとともに、再気化した冷媒蒸気を上記高温側の再生器Ｇｎ−１で発生した冷媒蒸気と共に上記低温側の再生器Ｇｎ−２へ導入して該低温側の再生器Ｇｎ−２の加熱を行わせるように構成し、上記フラッシュ室１から、上記フラッシュ室１で再気化されずに残った残余ドレンを排出する残余ドレン排出系に、冷媒蒸気の流通を阻止する流入阻止手段２，３を設けたことを特徴としている。
【００１２】
本願の第３の発明では、少なくとも１個以上の凝縮器Ｃ、蒸発器Ｅ、吸収器Ａと、冷媒を含む吸収溶液が供給される作動温度の異なるｎ個（ｎ≧３）の再生器Ｇｎ〜Ｇ１を溶液配管系と冷媒配管系とで作動的に接続して循環サイクルを構成し、最も高温側の再生器Ｇｎの吸収溶液を外部熱源Ｊで加熱沸騰させて冷媒蒸気を発生させる一方、高温側の再生器Ｇｎで発生した冷媒蒸気を低温側の再生器Ｇｎ−１に導入しこれを該低温側の再生器Ｇｎ−１の加熱源として利用して該低温側の再生器Ｇｎ−１の溶液を加熱濃縮することを最も低温側の再生器Ｇ１まで繰り返すようにした吸収式冷凍装置において、最も高温側の再生器Ｇｎを除く他の再生器Ｇｎ−１〜Ｇ１における高温側の再生器Ｇｎ−１で発生した冷媒蒸気を低温側の再生器Ｇｎ−２へ供給する配管経路にフラッシュ室１を設け、該フラッシュ室１に上記高温側の再生器Ｇｎ−１を加熱した後の冷媒ドレンを導入しこれを再気化させるとともに、再気化した冷媒蒸気を上記高温側の再生器Ｇｎ−１で発生した冷媒蒸気と共に上記低温側の再生器Ｇｎ−２へ導入して該低温側の再生器Ｇｎ−２の加熱を行わせるように構成し、吸収溶液の配管系に、上記フラッシュ室１における残余ドレンを用いて、又は該残余ドレンと上記低温側の再生器Ｇｎ−２を加熱後の冷媒ドレンの双方を用いて上記吸収溶液を加熱するドレン熱交換器Ｈｄを備えたことを特徴としている。
【発明の効果】
【００１３】
本願発明ではかかる構成とすることにより次のような効果が得られる。
【００１４】
（ａ）本願の第１の発明にかかる吸収式冷凍装置によれば、最も高温側の再生器Ｇｎを除く他の再生器Ｇｎ−１〜Ｇ１における高温側の再生器Ｇｎ−１で発生した冷媒蒸気を低温側の再生器Ｇｎ−２へ供給する配管経路にフラッシュ室１を設け、該フラッシュ室１に上記高温側の再生器Ｇｎ−１を加熱した後の冷媒ドレンを導入しこれを再気化させるとともに、再気化した冷媒蒸気を上記高温側の再生器Ｇｎ−１で発生した冷媒蒸気と共に上記低温側の再生器Ｇｎ−２へ導入して該低温側の再生器Ｇｎ−２の加熱を行わせるように構成しているので、上記冷媒ドレンが保有していた熱を上記低温側の再生器Ｇｎ−２の加熱熱源として有効に利用することができ、例えば従来のように上記高温側の再生器Ｇｎ−１で生成された冷媒蒸気のもつ熱のみによって上記低温側の再生器Ｇｎ−２を加熱する構成の場合に比して、上記冷媒ドレンからの熱回収分だけシステム全体としての熱効率が向上し、延いては吸収式冷凍装置の更なる性能向上が図れるものである。
【００１５】
また、上記フラッシュ室１で再気化されずに残った残余ドレンを、上記低温側の再生器Ｇｎ−２を加熱した後の冷媒ドレンの配管系に、又は上記凝縮器Ｃにおける冷媒ドレン入口部に、又は該凝縮器Ｃへ直接に、戻すようにしているので、残余ドレンの処理が確実となり、例えば残余ドレンが冷媒蒸気とともに低温側の再生器Ｇｎ−２側に進入するのが確実に防止され、それだけ上記冷媒蒸気による上記低温側の再生器Ｇｎ−２の加熱作用が高い信頼性と安定性とをもって行われ、延いては吸収式冷凍装置の作動上の信頼性と性能の安定性とが促進されることになる。
【００１６】
（ｂ）本願の第２の発明にかかる吸収式冷凍装置によれば、最も高温側の再生器Ｇｎを除く他の再生器Ｇｎ−１〜Ｇ１における高温側の再生器Ｇｎ−１で発生した冷媒蒸気を低温側の再生器Ｇｎ−２へ供給する配管経路にフラッシュ室１を設け、該フラッシュ室１に上記高温側の再生器Ｇｎ−１を加熱した後の冷媒ドレンを導入しこれを再気化させるとともに、再気化した冷媒蒸気を上記高温側の再生器Ｇｎ−１で発生した冷媒蒸気と共に上記低温側の再生器Ｇｎ−２へ導入して該低温側の再生器Ｇｎ−２の加熱を行わせるように構成しているので、上記冷媒ドレンが保有していた熱を上記低温側の再生器Ｇｎ−２の加熱熱源として有効に利用することができ、例えば従来のように上記高温側の再生器Ｇｎ−１で生成された冷媒蒸気のもつ熱のみによって上記低温側の再生器Ｇｎ−２を加熱する構成の場合に比して、上記冷媒ドレンからの熱回収分だけシステム全体としての熱効率が向上し、延いては吸収式冷凍装置の更なる性能向上が図れるものである。
【００１７】
また、この発明では、上記フラッシュ室１から、上記フラッシュ室１で再気化されずに残った残余ドレンを排出する残余ドレン排出系に冷媒蒸気の流通を阻止する流入阻止手段２，３を設けているので、上記フラッシュ室１内の冷媒蒸気はその全量が上記低温側の再生器Ｇｎ−２の加熱源として該再生器Ｇｎ−２側に導入され、例えば上記冷媒蒸気の一部が上記残余ドレン排出系へ漏出する場合に比して、上記冷媒蒸気による上記低温側の再生器Ｇｎ−２の加熱効率が向上し、延いては吸収式冷凍装置の更なる性能向上に寄与することになる。
【００１８】
（ｃ）本願の第３の発明にかかる吸収式冷凍装置によれば、最も高温側の再生器Ｇｎを除く他の再生器Ｇｎ−１〜Ｇ１における高温側の再生器Ｇｎ−１で発生した冷媒蒸気を低温側の再生器Ｇｎ−２へ供給する配管経路にフラッシュ室１を設け、該フラッシュ室１に上記高温側の再生器Ｇｎ−１を加熱した後の冷媒ドレンを導入しこれを再気化させるとともに、再気化した冷媒蒸気を上記高温側の再生器Ｇｎ−１で発生した冷媒蒸気と共に上記低温側の再生器Ｇｎ−２へ導入して該低温側の再生器Ｇｎ−２の加熱を行わせるように構成しているので、上記冷媒ドレンが保有していた熱を上記低温側の再生器Ｇｎ−２の加熱熱源として有効に利用することができ、例えば従来のように上記高温側の再生器Ｇｎ−１で生成された冷媒蒸気のもつ熱のみによって上記低温側の再生器Ｇｎ−２を加熱する構成の場合に比して、上記冷媒ドレンからの熱回収分だけシステム全体としての熱効率が向上し、延いては吸収式冷凍装置の更なる性能向上が図れるものである。
【００１９】
また、この発明では、吸収溶液の配管系に、上記フラッシュ室１における残余ドレンを用いて、又は該残余ドレンと上記低温側の再生器Ｇｎ−２を加熱後の冷媒ドレンの双方を用いて、上記吸収溶液を加熱するドレン熱交換器Ｈｄを備えているので、該ドレン熱交換器Ｈｄにおいて上記残余ドレンから、又は残余ドレンと冷媒ドレンの双方から吸収溶液側に熱回収がされる分だけ、システム全体としての熱効率がさらに向上し、この結果、吸収式冷凍装置の更なる性能向上が期待できることになる。
【発明の実施の形態】
【００２０】
以下、本願発明を好適な実施形態に基づいて具体的に説明する。
【００２１】
Ｉ：第１の実施形態
図１には、本願発明の第１の実施形態にかかる吸収式冷凍装置Ｚ１のシステム構成を示している。この吸収式冷凍装置Ｚ１は、水を冷媒とし、臭化リチウムを吸収溶液とする吸収式冷凍装置であって、各１個の凝縮器Ｃと吸収器Ａと蒸発器Ｅと３個の再生器Ｇ３，Ｇ２，Ｇ１を溶液配管系と冷媒配管系で作動的に接続して、冷媒Ｒと吸収溶液Ｌの循環サイクルを構成している。
【００２２】
尚、この実施形態で示すサイクルは所謂「シリースフロー」と呼ばれるサイクルであるが、本願発明はかかるサイクルに限定されるものではなく、例えば「パラレルフロー」とか「リバースフロー」、あるいはこれらを組み合わせたサイクル等、如何なるサイクルにも適用できることは勿論である。
【００２３】
先ず、上記吸収式冷凍装置Ｚ１を構成する上記各機器の基本的な機能を説明する。
【００２４】
蒸発器Ｅ
上記蒸発器Ｅは、容器Ｅｔの中に、被冷却液（水）Ｗｅを通す熱交換部Ｅｃと該熱交換部Ｅｃ上に冷媒（水）Ｒｅを散布する冷媒散布器Ｅｓとを有し、配管Ｕｅから流入して該蒸発器Ｅ内の上記熱交換部Ｅｃを流れる被冷却液（水）Ｗｅを冷却する。尚、上記蒸発器Ｅ内の冷媒Ｒｅは、冷媒ポンプＲＰにより、冷媒散布器Ｅｓ側に汲み上げられる。
【００２５】
吸収器Ａ
上記吸収器Ａは、上記蒸発器Ｅと連通して該蒸発器Ｅから流入する低温の気化冷媒（水蒸気）Ｒａを吸収溶液中に吸収させる作用を行うものであって、容器Ａｔ内に、溶液（濃溶液）Ｌｇを散布する溶液散布器Ａｓと、該吸収器Ａ内で発生する吸収熱を除去するための熱交換部（冷却部）Ａｃとを備えている。そして、上記熱交換部Ａｃは、配管Ｕａから冷却水Ｗａが供給されることで、上記吸収器Ａ内で発生する吸収熱を除去する。尚、この冷却水Ｗａは、さらに後述する凝縮器Ｃに送給されて凝縮器用冷却水としても利用される。
【００２６】
再生器Ｇ３，Ｇ２，Ｇ１
上記各再生器Ｇ３，Ｇ２，Ｇ１は、共に、冷媒を含む吸収溶液を加熱濃縮して順次高濃度の濃溶液とするためのものであって、これら相互間においてその作動温度が異なっており、最も高温で作動する高温再生器Ｇ３と、中温で作動する中温再生器Ｇ２と、最も低温で作動する低温再生器Ｇ１とされている。尚、上記吸収器Ａからの吸収溶液は、溶液ポンプＬＰにより、希溶液配管１１を通って、先ず上記高温再生器Ｇ３側に導入されるようになっている。
【００２７】
高温再生器Ｇ３
上記高温再生器Ｇ３は、容器Ｇ３ｔ内に外部熱源Ｊ（例えば、ガス燃焼器）を備え、上記吸収器Ａで生成される希溶液Ｌａを上記容器Ｇ３ｔ内に導入し、且つこれを加熱濃縮して、高温の濃溶液（高温溶液Ｌ３）を生成するとともに、冷媒蒸気Ｒ３を生成する。そして、上記高温再生器Ｇ３で生成される高温溶液Ｌ３と冷媒蒸気Ｒ３のうち、高温溶液Ｌ３は高温溶液配管２３を通って次段の上記中温再生器Ｇ２内に導入され、また冷媒蒸気Ｒ３は高温蒸気配管３３を通って上記中温再生器Ｇ２内の溶液加熱器Ｋ２（次述する）に導入される。
【００２８】
中温再生器Ｇ２
上記中温再生器Ｇ２は、容器Ｇ２ｔ内に溶液加熱器Ｋ２を備えるとともに、該容器Ｇ２ｔ内には上記高温溶液配管２３を介して上記高温再生器Ｇ３側から高温の濃溶液Ｌ３が導入される。また、上記溶液加熱器Ｋ２は、上記高温再生器Ｇ３で生成された冷媒蒸気Ｒ３が高温蒸気配管３３を介して導入され、上記濃溶液Ｌ３の加熱源として機能する。
【００２９】
上記中温再生器Ｇ２においては、上記溶液加熱器Ｋ２によって、高温再生器Ｇ３から導入される高温溶液Ｌ３が加熱濃縮されて、さらに高濃度で且つ中温の中温溶液Ｌ２が生成されるとともに、冷媒蒸気Ｒ２が生成される。そして、上記中温再生器Ｇ２で生成された中温溶液Ｌ２と冷媒蒸気Ｒ２のうち、中温溶液Ｌ２は中温溶液配管２２を通ってさらに次段の低温再生器Ｇ１に導入される一方、冷媒蒸気Ｒ２は中温蒸気配管３２を通って上記低温再生器Ｇ１に導入される。さらに、上記高温再生器Ｇ３から上記中温再生器Ｇ２の上記溶液加熱器Ｋ２に導入された冷媒蒸気Ｒ３は、該溶液加熱器Ｋ２での潜熱変化による加熱作用で相変化し、冷媒ドレンＲｄ２となり、冷媒ドレン配管４１を通して上記低温再生器Ｇ１側に設けられたフラッシュ室１に導入される。
【００３０】
低温再生器Ｇ１
上記低温再生器Ｇ１は、容器Ｇ１ｔ内に溶液加熱器Ｋ１を備えるとともに、上記溶液加熱器Ｋ１の入口ヘッダーと隣設して（図１）、又は冷媒ドレンの混合を防ぐ板４３を介して入口ヘッダーと兼用するようにして（図２）、設けられたフラッシュ室１を備えている。このフラッシュ室１は、上記中温再生器Ｇ２側の溶液加熱器Ｋ２から上記冷媒ドレン配管４１を通って導入される冷媒ドレンＲｄ２をフラッシュさせてこれを再気化させるものであって、該フラッシュ室１から再気化した冷媒蒸気Ｒ０と、上記中温再生器Ｇ２側から導入される冷媒蒸気Ｒ２とは、混合して上記溶液加熱器Ｋ１に導入され、上記中温溶液配管２２を通って上記低温再生器Ｇ１内に導入される中温溶液Ｌ２の加熱熱源となり、該中温溶液Ｌ２から低温溶液Ｌ１を生成せしめる。
【００３１】
さらに、上記フラッシュ室１には、ここに導入された冷媒ドレンＲｄ２のうち、フラッシュにより再気化されずに液相のまま残った残余ドレンＲｄ０は、該フラッシュ室１の底部に接続された冷媒ドレン配管４２を通って、上記溶液加熱器Ｋ１と上記凝縮器Ｃとを接続するドレン配管４０の途中に戻される。また、上記冷媒ドレン配管４２には、適度の絞りをもつオリフィス２が設けられており、該オリフィス２によって該冷媒ドレン配管４２に適度の通路抵抗が付与されることで、上記フラッシュ室１内の冷媒蒸気が上記ドレン配管４０側へ流入するのが阻止されるようになっている。即ち、この実施形態においては、上記オリフィス２が特許請求の範囲中の「流入阻止手段」に該当するものである。
【００３２】
また、上記低温再生器Ｇ１においては、上述のように、上記中温再生器Ｇ２から導入される中温溶液Ｌ２を加熱濃縮してさらに高濃度の低温溶液Ｌ１が生成されるとともに、冷媒蒸気Ｒ１が生成される。
【００３３】
そして、この低温溶液Ｌ１は、低温溶液配管２１を通って上記吸収器Ａへ導入され、上記溶液散布器Ａｓから濃溶液Ｌｇとして散布される。上記吸収器Ａ内では、上記溶液散布器Ａｓから散布される濃溶液Ｌｇ中に、上記蒸発器Ｅから導入される低温の冷媒蒸気Ｒａが吸収され、吸収溶液は希溶液Ｌａとなって上記容器Ａｔの底部に貯留される。また、上記吸収器Ａ内においては濃溶液Ｌｇが冷媒蒸気Ｒａを吸収する際に吸収熱が発生するが、この吸収熱は、上記熱交換部Ａｃに供給される冷却水Ｗａとの熱交換によって除去される。尚、この冷却水Ｗａは、上記吸収器Ａ通過後、さらに次述の凝縮器Ｃに送給される。
【００３４】
凝縮器Ｃ
上記凝縮器Ｃは、容器Ｃｔ内に、冷媒配管３１を介して上記低温再生器Ｇ１から導入される冷媒蒸気Ｒ１を冷却凝縮させて液冷媒Ｒｃを生成させるためのもので、その容器Ｃｔ内には冷媒蒸気Ｒ１を冷却して凝縮させるための熱交換部Ｃｃが設けられている。この熱交換部Ｃｃには、冷却水配管Ｕｃを通して吸収器Ａ通過後の冷却水が供給される。
【００３５】
尚、上記フラッシュ室１で生じた残余ドレンＲｄ０と上記低温再生器Ｇ１の溶液加熱器Ｋ１を通過して生成された冷媒ドレンＲｄとは、上記ドレン配管４０で合流し、上記凝縮器Ｃへ送られて液冷媒Ｒｃとされるとともに、この液冷媒Ｒｃは液冷媒配管４１を経て上記蒸発器Ｅに供給される。
【００３６】
熱交換器Ｈ１，Ｈ２，Ｈ３
一方、上記吸収器Ａから上記高温再生器Ｇ３に至る希溶液配管１１の途中には、３個の熱交換器Ｈ１，Ｈ２，Ｈ３が設けられている。これら各熱交換器Ｈ１，Ｈ２，Ｈ３は、上記各再生器Ｇ１，Ｇ２，Ｇ３で生成される低温溶液Ｌ１、中温溶液Ｌ２、及び高温溶液Ｌ３のそれぞれがもつ熱を吸収溶液Ｌａ側へ熱回収するためのものであって、最も低温側の低温溶液熱交換器Ｈ１には低温溶液配管２１を介して上記低温再生器Ｇ１から低温溶液Ｌ１が導入され、中温の中温溶液熱交換器Ｈ２には中温溶液配管２２を介して上記中温再生器Ｇ２からの中温溶液Ｌ２が導入され、最も高温の高温溶液熱交換器Ｈ３には上記高温溶液配管２３を介して高温溶液Ｌ３が導入され、これによって希溶液Ｌａは上記吸収器Ａ内での温度から昇温され、上記低温再生器Ｇ１側での加熱濃縮作用が促進される。
【００３７】
吸収式冷凍装置Ｚ１の作動説明
以上のように構成された吸収式冷凍装置Ｚ１においては、上述のように作動温度の異なる三つの再生器Ｇ３，Ｇ２，Ｇ１を備え、これら各再生器Ｇ３，Ｇ２，Ｇ１において吸収溶液を多段階に濃縮させるとともに、上記中温再生器Ｇ２と低温再生器Ｇ１においてはそれぞれその上段に位置する再生器、即ち、上記中温再生器Ｇ２にあっては上記高温再生器Ｇ３、上記低温再生器Ｇ１にあっては上記中温再生器Ｇ２で、それぞれ生成される冷媒蒸気Ｒ３、Ｒ２を、希溶液Ｌａを濃縮するための加熱源として利用することで、システム全体として高い熱効率が確保され、より高い性能が得られるものである。
【００３８】
しかし、この実施形態の吸収式冷凍装置Ｚ１においては、上記説明の性能向上効果に止まらず、さらに高い性能が確保されるものである。
【００３９】
即ち、この実施形態の吸収式冷凍装置Ｚ１においては、上述のように、上記低温再生器Ｇ１における上記溶液加熱器Ｋ１の入口ヘッダー側に上記フラッシュ室１を設け、該フラッシュ室１に上記中温再生器Ｇ２の溶液加熱器Ｋ２で加熱作用を行った後の冷媒ドレンＲｄ２を導入し、これをフラッシュにより再気化させ、この再気化冷媒蒸気Ｒ０を、上記中温再生器Ｇ２で生成された冷媒蒸気Ｒ１と共に上記溶液加熱器Ｋ１に導入し、これらの保有する熱を上記低温再生器Ｇ１内の吸収溶液の加熱源として利用するようにしているので、例えば従来のように上記中温再生器Ｇ２において吸収溶液の加熱に利用された後の冷媒ドレンＲｄ２をそのまま上記凝縮器Ｃ側に還流させる構成の場合に比して、該冷媒ドレンＲｄ２を再気化させてその再気化冷媒蒸気Ｒ０を吸収溶液の加熱源として利用した分だけ、システム全体としての熱効率が向上し、それだけ上記吸収式冷凍装置Ｚ１の更なる性能向上が期待できるものである。
【００４０】
尚、ここで、上記中温再生器Ｇ２において加熱源として利用された後の冷媒ドレンＲｄ２を上記フラッシュ室１において再気化させて再気化冷媒蒸気Ｒ０を生成させ、該再気化冷媒蒸気Ｒ０と上記中温再生器Ｇ２からの冷媒蒸気Ｒ２とによって上記低温再生器Ｇ１の吸収溶液を加熱凝縮して低温溶液Ｌ１を生成させる作動工程における熱的な相互関係を簡単に説明しておく。一般に、上記高温再生器Ｇ３を外部熱源Ｊによって加熱し高温溶液Ｌ３を凝縮させると、該高温再生器Ｇ３内には約１７０℃の冷媒蒸気Ｒ３が生成される。この冷媒蒸気Ｒ３が上記高温蒸気配管３３を通って上記中温再生器Ｇ２の溶液加熱器Ｋ２に導入され、該中温再生器Ｇ２内の吸収溶液を加熱凝縮させて中温溶液Ｌ２を生成する。
【００４１】
この場合、上記冷媒蒸気Ｒ３は潜熱変化によって加熱作用を行うことで凝縮し冷媒ドレンＲｄ２となるため、この冷媒ドレンＲｄ２は上記冷媒蒸気Ｒ３が保有していた顕熱をそのまま保有しており、その温度は約１７０℃に維持されることになる。一方、上記中温再生器Ｇ２は、約１７０℃の冷媒蒸気Ｒ３によって加熱されることで約９５℃の冷媒蒸気Ｒ２を生成する。また、約１７０℃の冷媒ドレンＲｄ２は、上記フラッシュ室１にてフラッシュして約９５℃の再気化冷媒蒸気Ｒ０になる。さらに、上記フラッシュ室１から上記冷媒ドレン配管４２を介して流出される残余ドレンＲｄ０も、約９５℃の温度をもっている。
【００４２】
従って、例えば、上記再気化冷媒蒸気Ｒ０を加熱源として利用せず、約９５℃の上記冷媒蒸気Ｒ２のみを上記溶液加熱器Ｋ１に導入する場合（従来構造）と、この実施形態のように、上記冷媒蒸気Ｒ２に加えて、約９５℃の再気化冷媒蒸気Ｒ０を上記溶液加熱器Ｋ１に導入する場合とを比較すると、この実施形態の場合の方が従来構造の場合よりも、上記再気化冷媒蒸気Ｒ０を利用する分だけ、上記溶液加熱器Ｋ１に供給される熱量を増大させることができ、これによってシステム全体としての熱効率が向上することになるものである。
【００４３】
ＩＩ：第２の実施形態
図３には、本願発明の第２の実施形態にかかる吸収式冷凍装置Ｚ２のシステム構成を示している。この実施形態の吸収式冷凍装置Ｚ２は、上記第１の実施形態にかかる吸収式冷凍装置Ｚ１の変形例として位置付けられるものであって、該第１の実施形態の吸収式冷凍装置Ｚ１と同様の基本構成をもち、これと異なる点はシステム循環系上における上記フラッシュ室１の設置位置である。
【００４４】
即ち、上記第１の循環系の吸収式冷凍装置Ｚ１においては上記フラッシュ室１を上記低温再生器Ｇ１における上記溶液加熱器Ｋ１の入口ヘッダー部分に配置していたのに対して、この実施形態の吸収式冷凍装置Ｚ２においては上記フラッシュ室１を上記中温再生器Ｇ２からの冷媒蒸気Ｒ２を上記低温再生器Ｇ１の上記溶液加熱器Ｋ１側へ導入する中温蒸気配管３２の中間位置に配置したものである。
【００４５】
このように、上記フラッシュ室１を上記高温蒸気配管３３の中間位置に設置する構成とした場合には、吸収式冷凍装置Ｚ２の製作時において上記フラッシュ室１を組付る場合、該フラッシュ室１を上記低温再生器Ｇ１及び中温再生器Ｇ２と切り離してこれらとは別個独立に組付ることができることから、例えば上記第１の実施形態の吸収式冷凍装置Ｚ１のように上記フラッシュ室１を上記低温再生器Ｇ１側に一体的に設置する場合に比して、該フラッシュ室１の組付作業が容易となり、その作業性が向上する分だれ吸収式冷凍装置Ｚ２の低コスト化が期待できるという利点がある。
【００４６】
尚、上記以外の構成及び作用効果については上記第１の実施形態の場合と同様であるので、図３の各構成要素に、図１の各構成要素に対応させてこれと同一の符号を付すとともに、第１の実施形態の該当説明を援用することで、ここでの説明を省略する。
【００４７】
ＩＩＩ：第３の実施形態
図４には、本願発明の第３の実施形態にかかる吸収式冷凍装置Ｚ３のシステム構成を示している。この実施形態の吸収式冷凍装置Ｚ３は、上記第１の実施形態にかかる吸収式冷凍装置Ｚ１の変形例として位置付けられるものであって、該第１の実施形態の吸収式冷凍装置Ｚ１と同様の基本構成をもち、これと異なる点はシステム循環系上における上記フラッシュ室１の設置位置と、該フラッシュ室１に接続された冷媒ドレン配管４２における冷媒蒸気の流入阻止構造にある。
【００４８】
即ち、先ず第１に、上記第１の循環系の吸収式冷凍装置Ｚ１においては上記フラッシュ室１を上記低温再生器Ｇ１における上記溶液加熱器Ｋ１の入口ヘッダー部分に配置していたのに対して、この実施形態の吸収式冷凍装置Ｚ３においては上記フラッシュ室１を上記中温再生器Ｇ２における冷媒蒸気Ｒ２の出口部分に配置している。従って、この構成によれば、上記中温再生器Ｇ２の溶液加熱器Ｋ２を出た直後の冷媒ドレンＲｄ２が上記フラッシュ室１に導入され、ここでフラッシュして再気化され、再気化冷媒蒸気Ｒ０とされる。そして、この再気化冷媒蒸気Ｒ０が、上記中温再生器Ｇ２から出た直後の冷媒蒸気Ｒ２と合流し、中温蒸気配管３２を通って上記低温再生器Ｇ１の溶液加熱器Ｋ１側に導入されることになる。
【００４９】
このように、上記フラッシュ室１を上記中温再生器Ｇ２側にこれと一体的に設けた場合、これら両者が共に圧力構造を必要とするものであることから、例えば上記中温再生器Ｇ２とフラッシュ室１とを別体に製作し且つこれらを共に圧力構造とする場合に比して、その製作が容易となり、それだけ低コスト化が促進されることになる。
【００５０】
第２に、上記第１の実施形態の吸収式冷凍装置Ｚ１においては、上記フラッシュ室１において発生する残余ドレンＲｄ０を上記凝縮器Ｃ側に還流させる冷媒ドレン配管４２に、冷媒蒸気の流入阻止手段としてオリフィス２を設け、該オリフィス２によって該冷媒ドレン配管４２に所要の通路抵抗を付与するようにしていたのに対して、この実施形態の吸収式冷凍装置Ｚ３においては上記冷媒ドレン配管４２に、冷媒蒸気の流入阻止手段としてフロート弁３を設けたものである。また、この実施形態においては、このフロート弁３が備えられた上記冷媒ドレン配管４２の下流端を、上記ドレン配管４０に接続するのではなく、上記凝縮器Ｃの容器Ｇ１ｔに設けたヘッダー４に接続し、冷媒ドレンＲｄを該凝縮器Ｃに直接還流させるようにしている。これらの構成によっても、上記第１の実施形態の吸収式冷凍装置Ｚ１において上記オリフィス２を備えたと同様の作用効果が得られるものである。
【００５１】
尚、上記以外の構成及び作用効果については上記第１の実施形態の場合と同様であるので、図４の各構成要素に、図１の各構成要素に対応させてこれと同一の符号を付すとともに、第１の実施形態の該当説明を援用することで、ここでの説明を省略する。
【００５２】
ＩＶ：第４の実施形態
図５には、本願発明の第４の実施形態にかかる吸収式冷凍装置Ｚ４のシステム構成を示している。この実施形態の吸収式冷凍装置Ｚ４は、上記第１の実施形態にかかる吸収式冷凍装置Ｚ１の発展例として位置付けられるものであって、該第１の実施形態の吸収式冷凍装置Ｚ１と同様の基本構成を備えたものを前提とし、これに更なる熱回収手段を付設し、もって第１の実施形態の吸収式冷凍装置Ｚ１よりもさらに高い熱効率を達成し、吸収式冷凍装置Ｚ４の性能をより一層高めるようにしたものである。
【００５３】
即ち、上記第１の実施形態の吸収式冷凍装置Ｚ１においては上記フラッシュ室１から上記冷媒ドレン配管４２を介して導出される残余ドレンＲｄ０をそのまま上記ドレン配管４０を介して上記凝縮器Ｃ側に還流させていたのに対して、この実施形態の吸収式冷凍装置Ｚ４においては、上記第１の実施形態において説明したように、上記フラッシュ室１から導出される残余ドレンＲｄ０は約９５℃という依然として高い温度をもつことに着目し、この残余ドレンＲｄ０が保有する熱を上記吸収器Ａから流出する希溶液Ｌａ側へ回収するようにしたものである。
【００５４】
この実施形態の吸収式冷凍装置Ｚ４においては、上記フラッシュ室１と上記ドレン配管４０とを接続する冷媒ドレン配管４２と、上記吸収器Ａと上記高温再生器Ｇ３とを接続する上記希溶液配管１１との間にドレン熱交換器Ｈｄを配置し、該ドレン熱交換器Ｈｄでの熱交換によって上記残余ドレンＲｄ０が保有する熱を上記希溶液Ｌａ側へ回収し、上記各溶液熱交換器Ｈ１，Ｈ２，Ｈ３と共働して、上記希溶液Ｌａをより一層昇温させ、これを上記高温再生器Ｇ３側へ導入させることでシステム全体としての熱効率をより一層高めるものである。
【００５５】
尚、上記以外の構成及び作用効果については上記第１の実施形態の場合と同様であるので、図５の各構成要素に、図１の各構成要素に対応させてこれと同一の符号を付すとともに、第１の実施形態の該当説明を援用することで、ここでの説明を省略する。
【００５６】
Ｖ：第５の実施形態
図６には、本願発明の第５の実施形態にかかる吸収式冷凍装置Ｚ５のシステム構成を示している。この実施形態の吸収式冷凍装置Ｚ５は、上記第１の実施形態の吸収式冷凍装置Ｚ１のシステム構成を大きく変更することなく、しかも上記第４の実施形態の吸収式冷凍装置Ｚ４よりもさらに高い熱効率を実現してより高い性能を確保できるようにしたものである。
【００５７】
即ち、この実現の吸収式冷凍装置Ｚ５においては、第１に、上記第４の実施形態の吸収式冷凍装置Ｚ４においては、上記ドレン熱交換器Ｈｄを上記吸収器Ａと上記高温再生器Ｇ３とを接続する上記希溶液配管１１と、上記フラッシュ室１と上記ドレン配管４０とを接続する上記冷媒ドレン配管４２との間に配置していたのに対して、この実施形態の吸収式冷凍装置Ｚ５では上記希溶液配管１１に上記低温溶液熱交換器Ｈ１を迂回するように分岐するバイパス配管１２を設け、該バイパス配管１２と上記冷媒ドレン配管４２との間に上記ドレン熱交換器Ｈｄを配置している。
【００５８】
かかる構成とすることで、上記各溶液熱交換器Ｈ１，Ｈ２，Ｈ２を備えた上記希溶液配管１１側の構成を大きく変えることなく上記ドレン熱交換器Ｈｄの設置が可能である。従って、上記第１の実施形態の吸収式冷凍装置Ｚ１の如き構成をもつものに、上記ドレン熱交換器Ｈｄを事後的に追加付設して性能向上を図ることが容易となる。
【００５９】
また、この実施形態においては、上記バイパス配管１２の下流側における上記希溶液配管１１との合流位置を、上記低温溶液熱交換器Ｈ１と中温溶液熱交換器Ｈ２との中間位置に設定しているが、かかる設定とした場合、上記冷媒ドレン配管４２を流れる残余ドレンＲｄ０の温度は上記低温溶液熱交換器Ｈ１に供給される上記低温再生器Ｇ１側の低温溶液Ｌ１の温度と上記中温溶液熱交換器Ｈ２に供給される上記中温再生器Ｇ２側の中温溶液Ｌ２との中間温度であることからして、上記希溶液配管１１を上記吸収器Ａ側から上記高温再生器Ｇ３側に流れる上記希溶液Ｌａに対する加熱作用が低温側から高温側に順次連続的に行われ、その流れ途中での熱損失がなく、それだけシステム全体としての熱効率が向上することにもなる。
【００６０】
第２に、上記第４の実施形態の吸収式冷凍装置Ｚ４においては、上記ドレン熱交換器Ｈｄに上記フラッシュ室１で発生した残余ドレンＲｄ０のみを供給するようにしていたのに対して、この実施形態の吸収式冷凍装置Ｚ５においては、上記ドレン熱交換器Ｈｄに、上記フラッシュ室１からの残余ドレンＲｄ０に加えて、上記低温再生器Ｇ１の溶液加熱器Ｋ１を通過後の冷媒ドレンＲｄも同時に供給するようにしている。かかる構成とすることで、上記ドレン熱交換器Ｈｄへの供給ドレン量そのものが増加するとともに、上記溶液加熱器Ｋ１を通過後の冷媒ドレンＲｄの熱も希溶液Ｌａ側に回収されることとなり、これらの相乗効果として、より高い熱効率が達成されるものである。
【００６１】
尚、上記以外の構成及び作用効果については上記第１又は第４の実施形態の場合と同様であるので、図６の各構成要素に、図１、図５の各構成要素に対応させてこれと同一の符号を付すとともに、第１又は第４の実施形態の該当説明を援用することで、ここでの説明を省略する。
【図面の簡単な説明】
【図１】本願発明の第１の実施形態にかかる吸収式冷凍装置におけるシステム構成及び作動サイクルの説明図である。
【図２】図１に示したフラッシュ室部分の構造を示す拡大断面図である。
【図３】本願発明の第２の実施形態にかかる吸収式冷凍装置におけるシステム構成及び作動サイクルの説明図である。
【図４】本願発明の第３の実施形態にかかる吸収式冷凍装置におけるシステム構成及び作動サイクルの説明図である。
【図５】本願発明の第４の実施形態にかかる吸収式冷凍装置におけるシステム構成及び作動サイクルの説明図である。
【図６】本願発明の第５の実施形態にかかる吸収式冷凍装置におけるシステム構成及び作動サイクルの説明図である。
【符号の説明】
１はフラッシュ室、２はオリフィス、３はフロート弁、４はヘッダー、１１は希溶液配管、１２はバイパス配管、２１は低温溶液配管、２２は中温溶液配管、２３は高温溶液配管、３１は冷媒配管、３２は中温蒸気配管、３３は高温蒸気配管、４０〜４２は冷媒ドレン配管、Ａは吸収器、Ｃは凝縮器、Ｅは蒸発器、Ｇ１〜Ｇ３は再生器、Ｈ１〜Ｈ３は溶液熱交換器、Ｈｄはドレン熱交換器、Ｊは加熱器、Ｋ１〜Ｋ３は溶液加熱器、Ｌａは希溶液、Ｌｇは濃溶液、ＬＰは溶液ポンプ、Ｌ１は低温溶液、Ｌ２は中温溶液、Ｌ３は高温溶液、Ｒａは気化冷媒、Ｒｃは液冷媒、Ｒｅは冷媒、Ｒｄは冷媒ドレン、ＲＰは冷媒ポンプ、Ｒ１〜Ｒ３は冷媒蒸気、Ｚ１〜Ｚ５は吸収式冷凍装置である。[0001]
BACKGROUND OF THE INVENTION
[0002]
The present invention relates to an absorption refrigeration apparatus, and more particularly to an absorption refrigeration apparatus including a plurality of regenerators having different operating temperatures.
[Prior art]
[0003]
In general, an absorption refrigeration apparatus includes a condenser, an evaporator, an absorber, and a regenerator as basic components, and these components are sequentially operatively connected by a solution piping system and a refrigerant piping system. .
[0004]
In such an absorption refrigeration apparatus, the dilute solution generated in the absorber is heated and concentrated in the regenerator to form a concentrated solution, which is then refluxed to the absorber, while the dilute solution is heated in the regenerator. The refrigerant vapor generated by the concentration is condensed in the condenser to form a liquid refrigerant, the liquid refrigerant is evaporated in the evaporator, and the refrigerant vapor generated here is absorbed in the concentrated solution by the absorber. By generating the solution, a circulation cycle of the absorbing solution and the refrigerant is realized. In general, the heat of evaporation of the refrigerant in the evaporator is used as a cold heat source of the refrigeration apparatus.
[0005]
By the way, in the absorption refrigeration apparatus, it is known that it is most effective to improve the thermal efficiency of the solution / refrigerant circulation system in order to improve the performance. As a method for realizing this, a plurality of regenerators are used. It has been proposed to recycle and reuse the heat of one external heat source. That is, a plurality of regenerators having different operating temperatures are provided, and refrigerant vapor generated by heating a high temperature side regenerator that operates at a high temperature is introduced into a low temperature side regenerator that operates at a low temperature. It is used as a heating heat source for the regenerator.
[Problems to be solved by the invention]
[0006]
However, in the conventional absorption refrigeration system, although the expected improvement in thermal efficiency can be obtained by using multiple regenerators, it is still not sufficient in terms of the thermal efficiency of the entire system. there were.
[0007]
That is, when the low temperature side regenerator is heated by the refrigerant vapor generated by the high temperature side regenerator, the heating action of the regenerator by this refrigerant vapor is mainly performed by the latent heat change of the refrigerant vapor. Although it changes and changes from a gas refrigerant to a liquid refrigerant, it still maintains a high temperature (sensible heat). However, in the conventional absorption refrigeration apparatus, the liquid refrigerant condensed after the heating action of the regenerator on the low temperature side is usually recirculated as a refrigerant drain to the condenser side. For this reason, the sensible heat possessed by the refrigerant drain cannot be effectively used. Therefore, the heat efficiency that would otherwise be obtained cannot be obtained, and as a result, the performance of the absorption refrigeration apparatus can be improved. It was an obstacle.
[0008]
Therefore, the present invention has been made for the purpose of further improving the performance by improving the thermal efficiency of the absorption refrigeration apparatus.
[Means for Solving the Problems]
[0009]
In the present invention, the following configuration is adopted as a specific means for solving such a problem.
[0010]
In the first invention of the present application, at least one condenser C, evaporator E, absorber A, and n (n ≧ 3) regenerators Gn having different operating temperatures to which an absorbing solution containing a refrigerant is supplied. ~ G1 is operatively connected between the solution piping system and the refrigerant piping system to constitute a circulation cycle, and the absorption solution of the regenerator Gn on the highest temperature side is heated and boiled by the external heat source J to generate refrigerant vapor, Refrigerant vapor generated in the high temperature side regenerator Gn is introduced into the low temperature side regenerator Gn-1, and this is used as a heating source for the low temperature side regenerator Gn-1. In the absorption refrigeration apparatus in which the heating and concentration of the solution is repeated up to the regenerator G1 on the lowest temperature side, the regenerator on the high temperature side in the other regenerators Gn-1 to G1 excluding the regenerator Gn on the highest temperature side Refrigerant vapor generated in Gn-1 is used as a low-temperature regenerator Gn-2 A flash chamber 1 is provided in the supply piping path, and the refrigerant drain after heating the regenerator Gn-1 on the high temperature side is introduced into the flash chamber 1 to re-vaporize it, and the re-vaporized refrigerant vapor is converted to the high temperature The refrigerant vapor generated in the regenerator Gn-1 on the side is introduced to the regenerator Gn-2 on the low temperature side to heat the regenerator Gn-2 on the low temperature side. Residual drain remaining without being revaporized is supplied to the refrigerant drain piping system after heating the low-temperature regenerator Gn-2, to the refrigerant drain inlet of the condenser C, or to the condenser C. It is characterized by being returned directly.
[0011]
In the second invention of the present application, at least one condenser C, evaporator E, absorber A, and n (n ≧ 3) regenerators Gn having different operating temperatures to which an absorbing solution containing a refrigerant is supplied. ~ G1 is operatively connected between the solution piping system and the refrigerant piping system to constitute a circulation cycle, and the absorption solution of the regenerator Gn on the highest temperature side is heated and boiled by the external heat source J to generate refrigerant vapor, Refrigerant vapor generated in the high temperature side regenerator Gn is introduced into the low temperature side regenerator Gn-1, and this is used as a heating source for the low temperature side regenerator Gn-1. In the absorption refrigeration apparatus in which the heating and concentration of the solution is repeated up to the regenerator G1 on the lowest temperature side, the regenerator on the high temperature side in the other regenerators Gn-1 to G1 excluding the regenerator Gn on the highest temperature side Refrigerant vapor generated in Gn-1 is used as a low-temperature regenerator Gn-2 A flash chamber 1 is provided in the supply piping path, and the refrigerant drain after heating the regenerator Gn-1 on the high temperature side is introduced into the flash chamber 1 to re-vaporize it, and the re-vaporized refrigerant vapor is converted to the high temperature The refrigerant vapor generated in the regenerator Gn-1 on the side is introduced into the regenerator Gn-2 on the low temperature side to heat the regenerator Gn-2 on the low temperature side. , the above Remains without being re-vaporized in flash chamber 1 For residual drain discharge system that discharges residual drain , Inflow blocking means 2 and 3 for blocking the circulation of the refrigerant vapor are provided.
[0012]
In the third invention of the present application, at least one condenser C, evaporator E, absorber A, and n (n ≧ 3) regenerators Gn having different operating temperatures to which the absorbing solution containing the refrigerant is supplied. ~ G1 is operatively connected between the solution piping system and the refrigerant piping system to constitute a circulation cycle, and the absorption solution of the regenerator Gn on the highest temperature side is heated and boiled by the external heat source J to generate refrigerant vapor, Refrigerant vapor generated in the high temperature side regenerator Gn is introduced into the low temperature side regenerator Gn-1, and this is used as a heating source for the low temperature side regenerator Gn-1. In the absorption refrigeration apparatus in which the heating and concentration of the solution is repeated up to the regenerator G1 on the lowest temperature side, the regenerator on the high temperature side in the other regenerators Gn-1 to G1 excluding the regenerator Gn on the highest temperature side Refrigerant vapor generated in Gn-1 is used as a low-temperature regenerator Gn-2 A flash chamber 1 is provided in the supply piping path, and the refrigerant drain after heating the regenerator Gn-1 on the high temperature side is introduced into the flash chamber 1 to re-vaporize it, and the re-vaporized refrigerant vapor is converted to the high temperature The refrigerant vapor generated in the side regenerator Gn-1 is introduced into the low temperature side regenerator Gn-2 to heat the low temperature side regenerator Gn-2, and the absorption solution piping system In addition, a drain heat exchanger Hd that heats the absorbing solution using the residual drain in the flash chamber 1 or both the residual drain and the refrigerant drain after heating the regenerator Gn-2 on the low temperature side is provided. It is characterized by having prepared.
【The invention's effect】
[0013]
In the present invention, the following effects can be obtained by adopting such a configuration.
[0014]
(A) According to the absorption refrigeration apparatus according to the first invention of the present application, the refrigerant generated in the regenerator Gn-1 on the high temperature side in the other regenerators Gn-1 to G1 excluding the regenerator Gn on the highest temperature side. A flash chamber 1 is provided in a piping path for supplying steam to the low temperature side regenerator Gn-2, and the refrigerant drain after heating the high temperature side regenerator Gn-1 is introduced into the flash chamber 1 to revaporize it. In addition, the revaporized refrigerant vapor is introduced into the low temperature side regenerator Gn-2 together with the refrigerant vapor generated in the high temperature side regenerator Gn-1 to heat the low temperature side regenerator Gn-2. Therefore, the heat held by the refrigerant drain can be effectively used as a heating heat source for the low temperature side regenerator Gn-2. For example, the high temperature side regeneration can be performed as in the prior art. Of the refrigerant vapor generated in the reactor Gn-1 Compared to the case where the regenerator Gn-2 on the low temperature side is heated only by this, the thermal efficiency of the entire system is improved by the amount of heat recovered from the refrigerant drain, and further the absorption refrigeration apparatus is further improved. The performance can be improved.
[0015]
Further, the residual drain remaining in the flash chamber 1 without being re-vaporized is supplied to the refrigerant drain piping system after the low-temperature regenerator Gn-2 is heated, or to the refrigerant drain inlet of the condenser C. Alternatively, since the residual drain is reliably treated, for example, the residual drain is reliably prevented from entering the regenerator Gn-2 on the low temperature side together with the refrigerant vapor. Therefore, the heating action of the regenerator Gn-2 on the low temperature side by the refrigerant vapor is performed with high reliability and stability, and thus the operational reliability and performance stability of the absorption refrigeration apparatus are increased. Will be promoted.
[0016]
(B) According to the absorption refrigeration apparatus according to the second invention of the present application, refrigerant generated in the regenerator Gn-1 on the high temperature side in the other regenerators Gn-1 to G1 excluding the regenerator Gn on the highest temperature side. A flash chamber 1 is provided in a piping path for supplying steam to the low temperature side regenerator Gn-2, and the refrigerant drain after heating the high temperature side regenerator Gn-1 is introduced into the flash chamber 1 to revaporize it. In addition, the revaporized refrigerant vapor is introduced into the low temperature side regenerator Gn-2 together with the refrigerant vapor generated in the high temperature side regenerator Gn-1 to heat the low temperature side regenerator Gn-2. Therefore, the heat held by the refrigerant drain can be effectively used as a heating heat source for the low temperature side regenerator Gn-2. For example, the high temperature side regeneration can be performed as in the prior art. Of the refrigerant vapor generated in the reactor Gn-1 Compared to the case where the regenerator Gn-2 on the low temperature side is heated only by this, the thermal efficiency of the entire system is improved by the amount of heat recovered from the refrigerant drain, and further the absorption refrigeration apparatus is further improved. The performance can be improved.
[0017]
In the present invention, the flash chamber 1 , the above Remains without being re-vaporized in flash chamber 1 Since the inflow blocking means 2 and 3 for blocking the circulation of the refrigerant vapor are provided in the residual drain discharge system for discharging the residual drain, all the refrigerant vapor in the flash chamber 1 is the regenerator Gn-2 on the low temperature side. The regenerator Gn-2 is introduced to the regenerator Gn-2 side as a heating source of the low temperature side by the refrigerant vapor as compared with, for example, a case where a part of the refrigerant vapor leaks to the residual drain discharge system. As a result, the heating efficiency is improved, which contributes to further improvement in performance of the absorption refrigeration apparatus.
[0018]
(C) According to the absorption refrigeration apparatus according to the third invention of the present application, the refrigerant generated in the regenerator Gn-1 on the high temperature side in the other regenerators Gn-1 to G1 excluding the regenerator Gn on the highest temperature side. A flash chamber 1 is provided in a piping path for supplying steam to the low temperature side regenerator Gn-2, and the refrigerant drain after heating the high temperature side regenerator Gn-1 is introduced into the flash chamber 1 to revaporize it. In addition, the revaporized refrigerant vapor is introduced into the low temperature side regenerator Gn-2 together with the refrigerant vapor generated in the high temperature side regenerator Gn-1 to heat the low temperature side regenerator Gn-2. Therefore, the heat held by the refrigerant drain can be effectively used as a heating heat source for the low temperature side regenerator Gn-2. For example, the high temperature side regeneration can be performed as in the prior art. Of the refrigerant vapor generated in the reactor Gn-1 Compared to the case where the regenerator Gn-2 on the low temperature side is heated only by this, the thermal efficiency of the entire system is improved by the amount of heat recovered from the refrigerant drain, and further the absorption refrigeration apparatus is further improved. The performance can be improved.
[0019]
In the present invention, the residual drain in the flash chamber 1 is used for the piping system of the absorbing solution, or both the residual drain and the refrigerant drain after heating the regenerator Gn-2 on the low temperature side are used. Since the drain heat exchanger Hd for heating the absorbing solution is provided, the amount of heat recovered from the residual drain or both the residual drain and the refrigerant drain to the absorbing solution side in the drain heat exchanger Hd. The thermal efficiency of the entire system is further improved, and as a result, further improvement in performance of the absorption refrigeration apparatus can be expected.
DETAILED DESCRIPTION OF THE INVENTION
[0020]
Hereinafter, the present invention will be specifically described based on preferred embodiments.
[0021]
I: First embodiment
FIG. 1 shows a system configuration of an absorption refrigeration apparatus Z1 according to the first embodiment of the present invention. The absorption refrigeration apparatus Z1 is an absorption refrigeration apparatus that uses water as a refrigerant and lithium bromide as an absorption solution, and includes one condenser C, one absorber A, one evaporator E, and three regenerators. G3, G2, and G1 are operatively connected by a solution piping system and a refrigerant piping system to constitute a circulation cycle of the refrigerant R and the absorbing solution L.
[0022]
The cycle shown in this embodiment is a so-called “series flow”, but the present invention is not limited to such a cycle. For example, “parallel flow”, “reverse flow”, or a combination thereof is used. Of course, it can be applied to any cycle such as a cycle.
[0023]
First, the basic functions of each of the above devices constituting the absorption refrigeration apparatus Z1 will be described.
[0024]
Evaporator E
The evaporator E includes, in the container Et, a heat exchange part Ec that passes the liquid (water) We to be cooled and a refrigerant spreader Es that spreads the refrigerant (water) Re on the heat exchange part Ec. The liquid to be cooled (water) We flowing from the pipe Ue and flowing through the heat exchanging portion Ec in the evaporator E is cooled. The refrigerant Re in the evaporator E is pumped up to the refrigerant spreader Es side by the refrigerant pump RP.
[0025]
Absorber A
The absorber A communicates with the evaporator E and absorbs the low-temperature vaporized refrigerant (water vapor) Ra flowing from the evaporator E into the absorbing solution. (Concentrated solution) A solution spreader As that spreads Lg and a heat exchanging portion (cooling portion) Ac for removing absorbed heat generated in the absorber A are provided. And the said heat exchange part Ac removes the absorbed heat which generate | occur | produces in the said absorber A by the cooling water Wa being supplied from the piping Ua. The cooling water Wa is further supplied to a condenser C, which will be described later, and is also used as condenser cooling water.
[0026]
Regenerator G3, G2, G1
Each of the regenerators G3, G2, and G1 is for heating and concentrating the absorbing solution containing the refrigerant to sequentially obtain a concentrated solution having a high concentration, and the operating temperatures thereof are different from each other. A high temperature regenerator G3 that operates at the highest temperature, a medium temperature regenerator G2 that operates at a medium temperature, and a low temperature regenerator G1 that operates at the lowest temperature. The absorbing solution from the absorber A is first introduced to the high temperature regenerator G3 side through the dilute solution pipe 11 by the solution pump LP.
[0027]
High temperature regenerator G3
The high-temperature regenerator G3 includes an external heat source J (for example, a gas combustor) in a container G3t, introduces the dilute solution La generated in the absorber A into the container G3t, and heats and concentrates it. Thus, a high-temperature concentrated solution (high-temperature solution L3) is generated and a refrigerant vapor R3 is generated. Of the high temperature solution L3 and the refrigerant vapor R3 generated in the high temperature regenerator G3, the high temperature solution L3 is introduced into the intermediate temperature regenerator G2 in the next stage through the high temperature solution pipe 23, and the refrigerant vapor R3 is The solution is introduced into the solution heater K2 (described later) in the intermediate temperature regenerator G2 through the high temperature steam pipe 33.
[0028]
Medium temperature regenerator G2
The intermediate temperature regenerator G2 includes a solution heater K2 in a container G2t, and a high temperature concentrated solution L3 is introduced into the container G2t from the high temperature regenerator G3 side through the high temperature solution pipe 23. The solution heater K2 functions as a heating source for the concentrated solution L3 by introducing the refrigerant vapor R3 generated by the high temperature regenerator G3 through the high temperature vapor pipe 33.
[0029]
In the intermediate temperature regenerator G2, the solution heater K2 heats and concentrates the high temperature solution L3 introduced from the high temperature regenerator G3 to generate a medium temperature intermediate solution L2 having a higher concentration and a medium temperature. R2 is generated. Of the intermediate temperature solution L2 and the refrigerant vapor R2 generated in the intermediate temperature regenerator G2, the intermediate temperature solution L2 is further introduced into the subsequent low temperature regenerator G1 through the intermediate temperature solution pipe 22, while the refrigerant vapor R2 is It is introduced into the low temperature regenerator G1 through the intermediate temperature steam pipe 32. Further, the refrigerant vapor R3 introduced from the high-temperature regenerator G3 into the solution heater K2 of the intermediate-temperature regenerator G2 undergoes a phase change due to a heating action due to a latent heat change in the solution heater K2, and becomes a refrigerant drain Rd2. The refrigerant is introduced into the flash chamber 1 provided on the low temperature regenerator G1 side through the refrigerant drain pipe 41.
[0030]
Low temperature regenerator G1
The low-temperature regenerator G1 includes a solution heater K1 in the container G1t and is provided adjacent to the inlet header of the solution heater K1 (FIG. 1) or through a plate 43 that prevents mixing of the refrigerant drain. The flash chamber 1 is provided so as to be used also as a header (FIG. 2). The flash chamber 1 is configured to flush the refrigerant drain Rd2 introduced from the solution heater K2 on the intermediate temperature regenerator G2 side through the refrigerant drain pipe 41 and re-evaporate the refrigerant drain Rd2. The refrigerant vapor R0 re-vaporized from the refrigerant vapor R2 introduced from the intermediate temperature regenerator G2 side is mixed and introduced into the solution heater K1, passes through the intermediate temperature solution pipe 22, and the low temperature regenerator G1. It becomes a heating heat source for the intermediate temperature solution L2 introduced into the inside, and generates the low temperature solution L1 from the intermediate temperature solution L2.
[0031]
Furthermore, in the flash chamber 1, the residual drain Rd 0 remaining in the liquid phase without being re-vaporized by the flash among the refrigerant drain Rd 2 introduced here is the refrigerant drain connected to the bottom of the flash chamber 1. The pipe 42 is returned to the middle of the drain pipe 40 connecting the solution heater K1 and the condenser C. In addition, the refrigerant drain pipe 42 is provided with an orifice 2 having an appropriate restriction, and the orifice 2 provides an appropriate passage resistance to the refrigerant drain pipe 42 so that the inside of the flash chamber 1 The refrigerant vapor is prevented from flowing into the drain pipe 40 side. That is, in this embodiment, the orifice 2 corresponds to the “inflow prevention means” in the claims.
[0032]
Further, in the low temperature regenerator G1, as described above, the intermediate temperature solution L2 introduced from the intermediate temperature regenerator G2 is heated and concentrated to generate a higher concentration low temperature solution L1 and a refrigerant vapor R1 is generated. Is done.
[0033]
And this low temperature solution L1 is introduce | transduced into the said absorber A through the low temperature solution piping 21, and is spread | dispersed as the concentrated solution Lg from the said solution spreader As. In the absorber A, the low-temperature refrigerant vapor Ra introduced from the evaporator E is absorbed into the concentrated solution Lg sprayed from the solution sprayer As, and the absorbing solution becomes the dilute solution La and the container. It is stored at the bottom of At. In the absorber A, absorption heat is generated when the concentrated solution Lg absorbs the refrigerant vapor Ra. This absorption heat is exchanged with the cooling water Wa supplied to the heat exchange part Ac. Removed. The cooling water Wa is supplied to the condenser C described below after passing through the absorber A.
[0034]
Condenser C
The condenser C is for cooling and condensing the refrigerant vapor R1 introduced from the low temperature regenerator G1 through the refrigerant pipe 31 in the container Ct to generate the liquid refrigerant Rc, and in the container Ct. Is provided with a heat exchanging section Cc for cooling and condensing the refrigerant vapor R1. The cooling water after passing through the absorber A is supplied to the heat exchanging portion Cc through the cooling water pipe Uc.
[0035]
The residual drain Rd0 generated in the flash chamber 1 and the refrigerant drain Rd generated through the solution heater K1 of the low-temperature regenerator G1 are merged in the drain pipe 40 and sent to the condenser C. The liquid refrigerant Rc is supplied to the evaporator E through the liquid refrigerant pipe 41.
[0036]
Heat exchanger H1, H2, H3
On the other hand, three heat exchangers H1, H2, and H3 are provided in the middle of the dilute solution pipe 11 from the absorber A to the high temperature regenerator G3. Each of these heat exchangers H1, H2, and H3 recovers the heat of each of the low temperature solution L1, the intermediate temperature solution L2, and the high temperature solution L3 generated in each of the regenerators G1, G2, and G3 to the absorption solution La side. The low temperature solution L1 is introduced from the low temperature regenerator G1 through the low temperature solution pipe 21 to the lowest temperature low temperature solution heat exchanger H1, and the intermediate temperature medium temperature solution heat exchanger H2 is supplied to the medium temperature medium temperature heat exchanger H2. The intermediate temperature solution L2 from the intermediate temperature regenerator G2 is introduced through the intermediate temperature solution pipe 22, and the high temperature solution L3 is introduced into the hottest high temperature solution heat exchanger H3 through the high temperature solution pipe 23. The temperature of the solution La is raised from the temperature in the absorber A, and the heating and concentration action on the low temperature regenerator G1 side is promoted.
[0037]
Operation explanation of absorption refrigeration system Z1
The absorption refrigeration apparatus Z1 configured as described above includes the three regenerators G3, G2, and G1 having different operating temperatures as described above, and in each of these regenerators G3, G2, and G1, the absorption solution is multistage. In the medium temperature regenerator G2 and the low temperature regenerator G1, the regenerators located in the upper stages thereof, that is, the medium temperature regenerator G2, the high temperature regenerator G3 and the low temperature regenerator G1, respectively. In the intermediate temperature regenerator G2, the refrigerant vapors R3 and R2 respectively generated are used as heating sources for concentrating the dilute solution La, so that high thermal efficiency is ensured as a whole system and higher performance is obtained. It is what
[0038]
However, in the absorption refrigeration apparatus Z1 of this embodiment, not only the performance improvement effect described above but also higher performance is ensured.
[0039]
That is, in the absorption refrigeration apparatus Z1 of this embodiment, as described above, the flash chamber 1 is provided on the inlet header side of the solution heater K1 in the low temperature regenerator G1, and the intermediate temperature regeneration is performed in the flash chamber 1. The refrigerant drain Rd2 after having been heated by the solution heater K2 of the vessel G2 is introduced and re-vaporized by flashing, and the re-vaporized refrigerant vapor R0 is converted into the refrigerant vapor R1 generated by the intermediate temperature regenerator G2. In addition, since the heat stored in the solution heater K1 is used as a heating source for the absorbing solution in the low-temperature regenerator G1, the absorbing solution is used in the intermediate-temperature regenerator G2 as in the prior art. Compared to the configuration in which the refrigerant drain Rd2 used for heating the refrigerant is recirculated to the condenser C side as it is, the refrigerant drain Rd2 is re-vaporized and re-aired. Amount corresponding to the use of the refrigerant vapor R0 as a heat source of the absorption solution, improves the thermal efficiency of the whole system, in which much further improvement in performance of the absorption refrigerating apparatus Z1 can be expected.
[0040]
Here, the refrigerant drain Rd2 used as a heating source in the intermediate temperature regenerator G2 is revaporized in the flash chamber 1 to generate revaporized refrigerant vapor R0, and the revaporized refrigerant vapor R0 and the intermediate temperature The thermal interrelation in the operation process in which the absorption solution of the low temperature regenerator G1 is heated and condensed by the refrigerant vapor R2 from the regenerator G2 to generate the low temperature solution L1 will be briefly described. Generally, when the high temperature regenerator G3 is heated by the external heat source J to condense the high temperature solution L3, a refrigerant vapor R3 of about 170 ° C. is generated in the high temperature regenerator G3. The refrigerant vapor R3 is introduced into the solution heater K2 of the intermediate temperature regenerator G2 through the high temperature vapor pipe 33, and the absorbing solution in the intermediate temperature regenerator G2 is heated and condensed to generate the intermediate temperature solution L2.
[0041]
In this case, the refrigerant vapor R3 condenses by performing a heating action due to a change in latent heat and becomes a refrigerant drain Rd2, so that the refrigerant drain Rd2 retains the sensible heat that the refrigerant vapor R3 has, The temperature will be maintained at about 170 ° C. On the other hand, the intermediate temperature regenerator G2 is heated by the refrigerant vapor R3 at about 170 ° C. to generate the refrigerant vapor R2 at about 95 ° C. Further, the refrigerant drain Rd2 at about 170 ° C. is flushed in the flash chamber 1 to become a re-vaporized refrigerant vapor R0 at about 95 ° C. Further, the residual drain Rd0 flowing out from the flash chamber 1 through the refrigerant drain pipe 42 also has a temperature of about 95 ° C.
[0042]
Therefore, for example, when the revaporized refrigerant vapor R0 is not used as a heating source and only the refrigerant vapor R2 at about 95 ° C. is introduced into the solution heater K1 (conventional structure), as in this embodiment, In comparison with the case where the revaporized refrigerant vapor R0 of about 95 ° C. is introduced into the solution heater K1 in addition to the refrigerant vapor R2, the revaporization is more effective in the case of this embodiment than in the case of the conventional structure. The amount of heat supplied to the solution heater K1 can be increased by the amount of use of the refrigerant vapor R0, thereby improving the thermal efficiency of the entire system.
[0043]
II: Second embodiment
FIG. 3 shows a system configuration of an absorption refrigeration apparatus Z2 according to the second embodiment of the present invention. The absorption refrigeration apparatus Z2 of this embodiment is positioned as a modification of the absorption refrigeration apparatus Z1 according to the first embodiment, and is similar to the absorption refrigeration apparatus Z1 of the first embodiment. It has a basic configuration and is different from this in the installation position of the flash chamber 1 on the system circulation system.
[0044]
That is, in the absorption refrigeration apparatus Z1 of the first circulation system, the flash chamber 1 is arranged at the inlet header portion of the solution heater K1 in the low temperature regenerator G1, whereas in this embodiment, In the absorption refrigeration apparatus Z2, the flash chamber 1 is disposed at an intermediate position of the intermediate temperature steam pipe 32 for introducing the refrigerant vapor R2 from the intermediate temperature regenerator G2 to the solution heater K1 side of the low temperature regenerator G1. is there.
[0045]
As described above, when the flash chamber 1 is installed at an intermediate position of the high-temperature steam pipe 33, when the flash chamber 1 is assembled when the absorption refrigeration apparatus Z2 is manufactured, the flash chamber 1 is used. Can be separated from the low-temperature regenerator G1 and the medium-temperature regenerator G2 and can be assembled separately and independently from the low-temperature regenerator G1 and the intermediate-temperature regenerator G2. Compared with the case where it is integrally installed on the low-temperature regenerator G1 side, the assembly work of the flash chamber 1 becomes easy, and the cost reduction of the drench absorption refrigeration apparatus Z2 can be expected to improve its workability. There are advantages.
[0046]
Since the configuration and the effect other than the above are the same as in the case of the first embodiment, the same reference numerals are assigned to the respective components in FIG. 3 corresponding to the respective components in FIG. Together with the corresponding description of the first embodiment, the description here is omitted.
[0047]
III: Third embodiment
FIG. 4 shows a system configuration of an absorption refrigeration apparatus Z3 according to the third embodiment of the present invention. The absorption refrigeration apparatus Z3 of this embodiment is positioned as a modification of the absorption refrigeration apparatus Z1 according to the first embodiment, and is the same as the absorption refrigeration apparatus Z1 of the first embodiment. It has a basic configuration and is different from this in the installation position of the flash chamber 1 on the system circulation system and the refrigerant vapor inflow prevention structure in the refrigerant drain pipe 42 connected to the flash chamber 1.
[0048]
That is, first of all, in the absorption refrigeration apparatus Z1 of the first circulation system, the flash chamber 1 is disposed at the inlet header portion of the solution heater K1 in the low temperature regenerator G1. In the absorption refrigeration apparatus Z3 of this embodiment, the flash chamber 1 is arranged at the outlet of the refrigerant vapor R2 in the intermediate temperature regenerator G2. Therefore, according to this configuration, the refrigerant drain Rd2 immediately after exiting the solution heater K2 of the intermediate temperature regenerator G2 is introduced into the flash chamber 1, where it is flashed and revaporized, and the revaporized refrigerant vapor R0 and Is done. Then, the revaporized refrigerant vapor R0 merges with the refrigerant vapor R2 immediately after exiting the intermediate temperature regenerator G2, and is introduced to the solution heater K1 side of the low temperature regenerator G1 through the intermediate temperature vapor pipe 32. become.
[0049]
Thus, when the flash chamber 1 is integrally provided on the intermediate temperature regenerator G2 side, both of them require a pressure structure. For example, the intermediate temperature regenerator G2 and the flash chamber are thus provided. As compared with the case where 1 and 2 are manufactured separately and both are made into a pressure structure, the manufacturing becomes easier and the cost reduction is promoted accordingly.
[0050]
Secondly, in the absorption refrigeration apparatus Z1 of the first embodiment, the refrigerant vapor inflow prevention means is connected to the refrigerant drain pipe 42 that recirculates the residual drain Rd0 generated in the flash chamber 1 to the condenser C side. In the absorption refrigeration apparatus Z3 of this embodiment, the orifice 2 is provided to provide the required passage resistance to the refrigerant drain pipe 42. The float valve 3 is provided as a refrigerant vapor inflow prevention means. Further, in this embodiment, the downstream end of the refrigerant drain pipe 42 provided with the float valve 3 is not connected to the drain pipe 40 but is connected to the header 4 provided in the container G1t of the condenser C. The refrigerant drain Rd is directly refluxed to the condenser C. Also with these configurations, the same operational effects as those provided with the orifice 2 in the absorption refrigeration apparatus Z1 of the first embodiment can be obtained.
[0051]
Since the other configurations and operational effects are the same as those in the first embodiment, the same reference numerals are assigned to the components in FIG. 4 corresponding to the components in FIG. Together with the corresponding description of the first embodiment, the description here is omitted.
[0052]
IV: Fourth embodiment
FIG. 5 shows a system configuration of an absorption refrigeration apparatus Z4 according to the fourth embodiment of the present invention. The absorption refrigeration apparatus Z4 of this embodiment is positioned as a development example of the absorption refrigeration apparatus Z1 according to the first embodiment, and is the same as the absorption refrigeration apparatus Z1 of the first embodiment. Assuming that it has a basic structure, additional heat recovery means is attached to it, thereby achieving higher thermal efficiency than the absorption refrigeration apparatus Z1 of the first embodiment, and the performance of the absorption refrigeration apparatus Z4. It is intended to be even higher.
[0053]
That is, in the absorption refrigeration apparatus Z1 of the first embodiment, the residual drain Rd0 led out from the flash chamber 1 through the refrigerant drain pipe 42 is directly passed to the condenser C side through the drain pipe 40. In contrast, in the absorption refrigeration apparatus Z4 of this embodiment, the residual drain Rd0 derived from the flash chamber 1 is still about 95 ° C. as described in the first embodiment. Focusing on the fact that it has a high temperature, the heat held by this residual drain Rd0 is recovered to the dilute solution La side that flows out of the absorber A.
[0054]
In the absorption refrigeration apparatus Z4 of this embodiment, the refrigerant drain pipe 42 that connects the flash chamber 1 and the drain pipe 40, and the dilute solution pipe 11 that connects the absorber A and the high temperature regenerator G3. And a drain heat exchanger Hd between the two and the heat of the remaining drain Rd0 is recovered to the dilute solution La side by heat exchange in the drain heat exchanger Hd, and each of the solution heat exchangers H1, By cooperating with H2 and H3, the temperature of the dilute solution La is further increased, and this is introduced into the high temperature regenerator G3 side, thereby further improving the thermal efficiency of the entire system.
[0055]
Since the configuration and operation other than those described above are the same as those in the first embodiment, the same reference numerals are assigned to the components in FIG. 5 corresponding to the components in FIG. Together with the corresponding description of the first embodiment, the description here is omitted.
[0056]
V: Fifth embodiment
FIG. 6 shows a system configuration of an absorption refrigeration apparatus Z5 according to the fifth embodiment of the present invention. The absorption refrigeration apparatus Z5 of this embodiment does not significantly change the system configuration of the absorption refrigeration apparatus Z1 of the first embodiment, and is higher than the absorption refrigeration apparatus Z4 of the fourth embodiment. It achieves higher efficiency by realizing thermal efficiency.
[0057]
That is, in the absorption refrigeration apparatus Z5 of this realization, first, in the absorption refrigeration apparatus Z4 of the fourth embodiment, the drain heat exchanger Hd is connected to the absorber A and the high temperature regenerator G3. Is disposed between the dilute solution pipe 11 for connecting the refrigerant and the refrigerant drain pipe 42 for connecting the flush chamber 1 and the drain pipe 40, whereas the absorption refrigeration apparatus Z5 of this embodiment is arranged. Then, the dilute solution pipe 11 is provided with a bypass pipe 12 that branches to bypass the low-temperature solution heat exchanger H1, and the drain heat exchanger Hd is disposed between the bypass pipe 12 and the refrigerant drain pipe 42. ing.
[0058]
By adopting such a configuration, the drain heat exchanger Hd can be installed without greatly changing the configuration on the side of the dilute solution pipe 11 including the solution heat exchangers H1, H2, and H2. Therefore, it becomes easy to improve the performance by adding the drain heat exchanger Hd afterwards to the one having the configuration of the absorption refrigeration apparatus Z1 of the first embodiment.
[0059]
In this embodiment, the junction position with the dilute solution pipe 11 on the downstream side of the bypass pipe 12 is set at an intermediate position between the low temperature solution heat exchanger H1 and the intermediate temperature solution heat exchanger H2. However, in such a setting, the temperature of the residual drain Rd0 flowing through the refrigerant drain pipe 42 is the medium temperature solution heat exchange with the temperature of the low temperature solution L1 on the low temperature regenerator G1 side supplied to the low temperature solution heat exchanger H1. The dilute solution flowing from the absorber A side to the high temperature regenerator G3 through the dilute solution pipe 11 because of the intermediate temperature with the medium temperature solution L2 on the medium temperature regenerator G2 side supplied to the regenerator H2. The heating action for La is performed sequentially from the low temperature side to the high temperature side, there is no heat loss during the flow, and the thermal efficiency of the entire system is improved accordingly.
[0060]
Second, in the absorption refrigeration apparatus Z4 of the fourth embodiment, only the residual drain Rd0 generated in the flash chamber 1 is supplied to the drain heat exchanger Hd. In the absorption refrigeration apparatus Z5 of the embodiment, in addition to the residual drain Rd0 from the flash chamber 1, the refrigerant drain Rd after passing through the solution heater K1 of the low-temperature regenerator G1 is also added to the drain heat exchanger Hd. I am trying to supply at the same time. By adopting such a configuration, the amount of drain supplied to the drain heat exchanger Hd itself increases, and the heat of the refrigerant drain Rd after passing through the solution heater K1 is also recovered to the dilute solution La side. As a synergistic effect, higher thermal efficiency is achieved.
[0061]
Since the configuration and operational effects other than those described above are the same as those in the first or fourth embodiment, each component shown in FIG. 6 corresponds to each component shown in FIGS. The description is omitted here by using the same reference numerals as those in the first or fourth embodiment.
[Brief description of the drawings]
FIG. 1 is an explanatory diagram of a system configuration and an operation cycle in an absorption refrigeration apparatus according to a first embodiment of the present invention.
2 is an enlarged cross-sectional view showing a structure of a flash chamber portion shown in FIG. 1. FIG.
FIG. 3 is an explanatory diagram of a system configuration and an operation cycle in an absorption refrigeration apparatus according to a second embodiment of the present invention.
FIG. 4 is an explanatory diagram of a system configuration and an operation cycle in an absorption refrigeration apparatus according to a third embodiment of the present invention.
FIG. 5 is an explanatory diagram of a system configuration and an operation cycle in an absorption refrigeration apparatus according to a fourth embodiment of the present invention.
FIG. 6 is an explanatory diagram of a system configuration and an operation cycle in an absorption refrigeration apparatus according to a fifth embodiment of the present invention.
[Explanation of symbols]
1 is a flush chamber, 2 is an orifice, 3 is a float valve, 4 is a header, 11 is a dilute solution pipe, 12 is a bypass pipe, 21 is a low temperature solution pipe, 22 is a medium temperature solution pipe, 23 is a high temperature solution pipe, and 31 is a refrigerant Piping, 32 is medium temperature steam piping, 33 is high temperature steam piping, 40 to 42 are refrigerant drain piping, A is an absorber, C is a condenser, E is an evaporator, G1 to G3 are regenerators, and H1 to H3 are solution heat. Exchanger, Hd is a drain heat exchanger, J is a heater, K1 to K3 are solution heaters, La is a dilute solution, Lg is a concentrated solution, LP is a solution pump, L1 is a low temperature solution, L2 is a medium temperature solution, and L3 is A high-temperature solution, Ra is a vaporized refrigerant, Rc is a liquid refrigerant, Re is a refrigerant, Rd is a refrigerant drain, RP is a refrigerant pump, R1 to R3 are refrigerant vapors, and Z1 to Z5 are absorption refrigeration apparatuses.

Claims

At least one condenser (C), evaporator (E), absorber (A), and n (n ≧ 3) regenerators (Gn˜) having different operating temperatures to which an absorbing solution containing a refrigerant is supplied. G1) is operatively connected between the solution piping system and the refrigerant piping system to form a circulation cycle. The absorption solution of the regenerator (Gn) on the highest temperature side is heated and boiled with an external heat source (J) to generate refrigerant vapor. On the other hand, the refrigerant vapor generated in the high temperature side regenerator (Gn) is introduced into the low temperature side regenerator (Gn-1) and used as a heating source for the low temperature side regenerator (Gn-1). An absorption refrigeration apparatus that repeats heating and concentrating the solution in the regenerator (Gn-1) on the low temperature side to the regenerator (G1) on the low temperature side,
Refrigerant vapor generated in the high temperature side regenerator (Gn-1) in the other regenerators (Gn-1 to G1) excluding the highest temperature side regenerator (Gn) is transferred to the low temperature side regenerator (Gn-2). A flush chamber (1) is provided in the supply piping path, and the refrigerant drain after heating the regenerator (Gn-1) on the high temperature side is introduced into the flash chamber (1) to re-vaporize and re-vaporize. The refrigerant vapor thus generated is introduced into the low temperature side regenerator (Gn-2) together with the refrigerant vapor generated in the high temperature side regenerator (Gn-1) to heat the low temperature side regenerator (Gn-2). Configured to do,
The residual drain remaining in the flash chamber (1) without being revaporized is supplied to the refrigerant drain piping system after heating the low-temperature regenerator (Gn-2) or to the refrigerant in the condenser (C). An absorption refrigeration apparatus characterized in that it is returned to the drain inlet or directly to the condenser (C).

At least one condenser (C), evaporator (E), absorber (A), and n (n ≧ 3) regenerators (Gn˜) having different operating temperatures to which an absorbing solution containing a refrigerant is supplied. G1) is operatively connected between the solution piping system and the refrigerant piping system to form a circulation cycle. The absorption solution of the regenerator (Gn) on the highest temperature side is heated and boiled with an external heat source (J) to generate refrigerant vapor. On the other hand, the refrigerant vapor generated in the high temperature side regenerator (Gn) is introduced into the low temperature side regenerator (Gn-1) and used as a heating source for the low temperature side regenerator (Gn-1). An absorption refrigeration apparatus that repeats heating and concentrating the solution in the regenerator (Gn-1) on the low temperature side to the regenerator (G1) on the low temperature side,
Refrigerant vapor generated in the high temperature side regenerator (Gn-1) in the other regenerators (Gn-1 to G1) excluding the highest temperature side regenerator (Gn) is transferred to the low temperature side regenerator (Gn-2). A flush chamber (1) is provided in the supply piping path, and the refrigerant drain after heating the regenerator (Gn-1) on the high temperature side is introduced into the flash chamber (1) to re-vaporize and re-vaporize. The refrigerant vapor thus generated is introduced into the low temperature side regenerator (Gn-2) together with the refrigerant vapor generated in the high temperature side regenerator (Gn-1) to heat the low temperature side regenerator (Gn-2). Configured to do,
An inflow blocking means (2, 3) for blocking the circulation of the refrigerant vapor is provided in the residual drain discharge system for discharging the residual drain remaining without being re-vaporized in the flash chamber (1) from the flash chamber (1). An absorption refrigeration apparatus characterized by that.

At least one condenser (C), evaporator (E), absorber (A), and n (n ≧ 3) regenerators (Gn˜) having different operating temperatures to which an absorbing solution containing a refrigerant is supplied. G1) is operatively connected between the solution piping system and the refrigerant piping system to form a circulation cycle. The absorption solution of the regenerator (Gn) on the highest temperature side is heated and boiled with an external heat source (J) to generate refrigerant vapor. On the other hand, the refrigerant vapor generated in the high temperature side regenerator (Gn) is introduced into the low temperature side regenerator (Gn-1) and used as a heating source for the low temperature side regenerator (Gn-1). An absorption refrigeration apparatus that repeats heating and concentrating the solution in the regenerator (Gn-1) on the low temperature side to the regenerator (G1) on the low temperature side,
Refrigerant vapor generated in the high temperature side regenerator (Gn-1) in the other regenerators (Gn-1 to G1) excluding the highest temperature side regenerator (Gn) is transferred to the low temperature side regenerator (Gn-2). A flush chamber (1) is provided in the supply piping path, and the refrigerant drain after heating the regenerator (Gn-1) on the high temperature side is introduced into the flash chamber (1) to re-vaporize and re-vaporize. The refrigerant vapor thus generated is introduced into the low temperature side regenerator (Gn-2) together with the refrigerant vapor generated in the high temperature side regenerator (Gn-1) to heat the low temperature side regenerator (Gn-2). Configured to do,
Using the residual drain in the flash chamber (1) or the refrigerant drain after heating the residual drain and the low-temperature regenerator (Gn-2) in the piping system of the absorbing solution, the absorbing solution An absorption refrigeration system comprising a drain heat exchanger (Hd) for heating