【０００１】
【発明の属する技術分野】
本発明は蒸発器、吸収器、再生器及び凝縮器を備えた吸収式ヒートポンプに関し、詳しくは、蒸発器及び吸収器の構造に関する。
【０００２】
【従来の技術】
従来の吸収式ヒートポンプにおいては、例えば図６に示すように、冷媒蒸気が通過可能な仕切り部２３を間にして蒸発器と吸収器が隣接配置され、蒸発器では凝縮器で凝縮された冷媒Ｒを、吸収器では再生器で濃縮再生された吸収液Ｌｃ（例えば、ＬｉＢｒ水溶液）を上方からスプレー噴射方式などにより夫々の伝熱管群１４ａ，１５ａへ滴下している。そして、蒸発器では冷媒Ｒの蒸発熱により伝熱管１４ａ内を流れる熱媒を冷却し、吸収器では蒸発器で蒸発した冷媒蒸気を吸収液に吸収させ、冷媒蒸気を吸収して濃度が低くなった吸収液Ｌａを再生器に送出している（これを第１の従来技術とする）。 また、別の吸収式ヒートポンプの技術として、蒸発器及び吸収器内を上下２段に分割して、上段部の伝熱管群を流れてきた冷媒等を上下の境界箇所に設けた受け皿にいったん収容した後、その受け皿の底部に開けた滴下孔から下段部の伝熱管群に滴下させるようにした構造が開示されている（これを第２の従来技術とする）（例えば、特許文献１参照）。
【０００３】
【特許文献１】
特開２０００−１７９９７５号公報（第２−８頁、図１〜図７）
【０００４】
【発明が解決しようとする課題】
しかし、上記第１の従来技術では、冷媒や吸収液が伝熱管群に滴下する際、伝熱管群と周囲の壁との間には少なからずデッドスペースが存在するため、滴下状況によってはそのデッドスペースへ冷媒等が流れ込み、伝熱管に当ることなく下部の液溜りまで落下して、伝熱に寄与しない場合があった。さらに、冷媒等が伝熱管をつたって流れていても、伝熱管の端部等においては濡れていない部分があり、濡れ方が不均一な場合もあった。その結果、蒸発器での蒸発効率及び吸収器での吸収効率が低下して、吸収式ヒートポンプの性能の低下を招くおそれがあった。
また、上記第２の従来技術では、上段部の伝熱管群と周囲の壁との間のデッドスペースに流れ込んだ冷媒等を受け皿に集めて、下段部の伝熱管群に滴下させているので、冷媒等が伝熱管に全く当らずに落下するということはないが、伝熱管に対する冷媒等の濡れ方で不均一が発生するおそれはあった。
【０００５】
本発明は、上記実情に鑑みてなされたものであり、その目的は、蒸発器や吸収器の伝熱管群に対して上部から滴下された冷媒等を有効に伝熱に寄与させて、蒸発器での蒸発効率及び吸収器での吸収効率を向上させるために、冷媒等が伝熱管群の各管に対して均一に濡れる状態にすることにある。
さらには、伝熱管群と周囲の壁との間のデッドスペースに流れ込んだ冷媒等を伝熱管群の方に戻して、蒸発器での蒸発効率及び吸収器での吸収効率の一層の向上を実現させることにある。
【０００６】
【課題を解決するための手段】
上記目的を実現するための吸収式ヒートポンプの請求項１に係る発明の特徴は、前記蒸発器と前記吸収器の少なくとも一方において、内部に設置された伝熱管群のうち上側に位置する上部管群と下側に位置する下部管群の間に、メッシュが形成された整流板をその整流板の下面が前記下部管群の伝熱管の上面と接触もしくは微小間隙を開ける状態で配置した点にある。
【０００７】
すなわち、この構成によれば、蒸発器と吸収器の少なくとも一方の内部に設置された伝熱管群の上部管群を伝って落下してきた冷媒や吸収液が、上部管群と下部管群の間に配置した整流板に達すると、整流板に形成されたメッシュに触れた冷媒等がメッシュの隙間に浸透して、伝熱管群の端部等の流れの悪い箇所にも流れて広がるため、滴下範囲を横方向に均一に広げることができる。さらに、メッシュで広げられ保持された冷媒等が、整流板の下面に接触もしくは微小間隙を開ける状態で配置された下部管群の伝熱管の上面に伝って落下するため、孔等による場合の点による滴下から線あるいは面による滴下が可能となる。
【０００８】
従って、例えば前記第２の従来技術のように滴下孔付きの板状の受け皿で冷媒等を受けるものでは、液量や板の傾斜等によって液が偏った状態で滴下されるおそれがあるのに対して、本発明のメッシュを備えた整流板では浸透作用によって液が迅速かつ均一に広がり、冷媒等が伝熱管群の各管に対して均一に濡れる状態で滴下することができる。これにより、蒸発器や吸収器の伝熱管群に対して上部から滴下された冷媒等を有効に伝熱に寄与させて、蒸発器での蒸発効率及び吸収器での吸収効率を向上させることが可能となる。
【０００９】
請求項２に係る発明の特徴は、請求項１に係る発明に加えて、前記伝熱管群と周囲の壁との間に、壁側から内側に向かって高さが低くなり且つ内側端部が前記伝熱管群の端に位置する斜板を配置した点にある。
【００１０】
すなわち、この構成によれば、上方から滴下された冷媒液等が伝熱管群と周囲の壁との間のデッドスペースに流れ込んだ場合に、そのデッドスペースに配置した斜板によって受止められるとともに、壁側から内側に向かって高さが低くなった斜板によって、壁側から内側端部の伝熱管群の端の位置まで戻される。これにより、デッドスペースに流れ込んだ冷媒等を内側に戻して伝熱管群に当てて伝熱に有効に寄与させ、蒸発器での蒸発効率及び吸収器での吸収効率の一層の向上を実現することができる。
【００１１】
請求項３に係る発明の特徴は、請求項１又は２に係る発明に加えて、前記伝熱管群の上方から冷媒液又は溶液を落下供給する液供給部と周囲の壁との間に、壁側から内側に向かって高さが低くなり且つ内側端部が前記伝熱管群の端に位置する斜板を配置した点にある。
【００１２】
すなわち、この構成によれば、伝熱管群の上方から冷媒液又は溶液を落下供給する液供給部の横側方に飛散した冷媒液等が液供給部と周囲の壁との間のデッドスペースに流れ込んだ場合に、そのデッドスペースに配置した斜板によって受止められるとともに、壁側から内側に向かって高さが低くなった斜板によって、壁側から内側端部の伝熱管群の端の位置まで戻される。これにより、上記液供給部から横側方に飛散した冷媒液等を伝熱管群に当てて伝熱に有効に寄与させ、蒸発器での蒸発効率及び吸収器での吸収効率の一層の向上を実現することができる。
【００１３】
請求項４に係る発明は、請求項２又は３に係る発明の実施に好適な実施形態を特定するものであり、その特徴は、前記斜板の内側端部を前記整流板の周縁部に連なるように接続した点にある。
【００１４】
すなわち、この構成によれば、斜板によって受止められ斜板の内側端部に戻された冷媒液等が、斜板の内側端部に連なるように接続された整流板の周縁部にスムーズに移行して、整流板の全体に広がるので、上記斜板で戻された冷媒液等を伝熱管群の端部の伝熱管のみでなく、全体の管群に触れる状態にして、蒸発器での蒸発効率及び吸収器での吸収効率を一層向上させることができる。
【００１５】
【発明の実施の形態】
図１は本発明を適用した吸収式冷温水機（吸収式ヒートポンプの一例）を備えたガスタービン・コージェネレーションシステムを示し、１はガスタービン、２はガスタービン１の出力軸１ａに連結した圧縮機であり、この圧縮機２により吸気路３から燃焼用空気Ａを吸入して、その吸入した燃焼用空気Ａを送気路４を通じガスタービン１の燃焼器５に加圧供給し、この燃焼器５で燃料路６からの供給燃料Ｆを燃焼させることによりガスタービン１の運転を継続する。
【００１６】
７は排ガス路８へ送出されたガスタービン１の排ガスＥと送気路４の燃焼用空気Ａとを熱交換させて燃焼用空気Ａを予熱する再生熱交換器であり、この再生熱交換器７による空気予熱により、所要のタービン作動温度を得るのに要する燃料量を低減してガスタービン１の燃料消費量を節減する。
９は圧縮機２とともにガスタービン１の出力軸１ａに連結した発電機であり、ガスタービン１の発生動力により発電機９を駆動することでコージェネレーションシステムとしての電力出力（タービン出力Ｇ）を得る。
【００１７】
一方、１０は二重効用型の吸収式冷温水機であり、この吸収式冷温水機１０の高温再生器１１において吸収液Ｌａを加熱する加熱管１１ａを再生熱交換器７よりも下流側で排ガス路８に介装して、この加熱管１１ａに対し再生熱交換器７を通過した後のタービン排ガスＥを熱源熱媒として供給する構成にし、これにより、再生熱交換器７を通過した後のタービン排ガスＥの保有熱を駆動熱源として吸収式冷温水機１０を運転することで、コージェネレーションシステムとしての熱出力を得る。
【００１８】
１２は高温再生器１１において加熱管１１ａによる加熱で冷媒Ｒを蒸発分離させた後の中濃度吸収液Ｌｂを導入する低温再生器、１２ａは高温再生器１１で発生した冷媒蒸気Ｒを熱源熱媒とする低温再生器用の加熱管であり、この加熱管１２ａによる低温再生器１２での吸収液加熱により低温再生器１２において中濃度吸収液Ｌｂから更に冷媒蒸気Ｒを発生させる。
【００１９】
１３は低温再生器１２で発生した冷媒蒸気Ｒ及び低温再生器１２の加熱管１２ａを通過した冷媒Ｒを冷却器１３ａの通過冷却水Ｃにより冷却して凝縮させる凝縮器であり、１４は凝縮器１３から送られる液冷媒Ｒを低圧雰囲気下で蒸発させて、出力熱交換器を構成する伝熱管１４ａにおける通過水Ｗをそれからの気化熱奪取により冷却する蒸発器であり、１５は冷却用の伝熱管１５ａの通過冷却水Ｃによる冷却下において低温再生器１２から送られる濃吸収液Ｌｃに蒸発器１４での蒸発冷媒Ｒを吸収させる吸収器である。そして、上記蒸発器１４により通過水Ｗを冷却して冷熱出力Ｑを得る。
【００２０】
また、１６ａは吸収器１５から高温再生器１１に戻す希吸収液Ｌａを低温再生器１２から吸収器１５に送る濃吸収液Ｌｃと熱交換させて予熱する低温熱交換器であり、１６ｂは低温熱交換器１６ａで予熱した希吸収液Ｌａを高温再生器１１から低温再生器１２に送る中濃度吸収液Ｌｂによりさらに予熱する高温熱交換器であり、ｐ１は冷媒循環ポンプ、ｐ２は吸収液循環ポンプである。
【００２１】
そして、この吸収式冷温水機１０では、高温熱交換器１６ｂで予熱した希吸収液Ｌａを高温再生器１１に戻す前段で、その希吸収液Ｌａを加熱管１１ａから送出されるタービン排ガスＥと熱交換させてさらに高温に予熱する最終予熱用の予熱熱交換器１６ｃを設けてあり、これにより、加熱管１１ａの出口におけるタービン排ガスＥの温度を高く設定して高温再生器１１における冷媒Ｒの蒸発温度（蒸発圧力）を高く確保しながらも、予熱熱交換器１６ｃでの希吸収液Ｌａの予熱により冷凍機全体としてのタービン排ガスＥからの取り入れ熱量を大きく確保して、未利用のままで機外へ排出するタービン排ガスＥの残存熱量を効果的に低減するようにしている。
なお、吸収式冷温水機１０の温水発生運転では、高温再生器１１において加熱管１１ａにより加熱した冷媒Ｒを短絡的に蒸発器１４に導いて、その加熱冷媒Ｒにより伝熱管１４ａにおける通過水Ｗを加熱する。これにより、蒸発器１４により通過水Ｗを加熱する温熱出力Ｑが得られる。
【００２２】
次に、前記蒸発器１４と前記吸収器１５の構造について説明すると、図２に示すように、蒸発器１４と吸収器１５において、内部に設置された伝熱管群１４ａ，１５ａのうち上側に位置する上部管群と下側に位置する下部管群の間に、メッシュが形成された整流板１６，１７をその整流板１６，１７の下面が前記下部管群の伝熱管の上面と接触もしくは微少間隙を開ける状態で配置している。
具体的には、伝熱管群１４ａ，１５ａを上下３群に分けて、一番上の管群１４ａ１，１５ａ１が上から２番目の管群１４ａ２，１５ａ２との関係では上部管群になるとともに、上から２番目の管群１４ａ２，１５ａ２が下部管群になり、また、上から２番目の管群１４ａ２，１５ａ２が上から３番目の管群１４ａ３，１５ａ３との関係では上部管群になるとともに、上から３番目の管群１４ａ３，１５ａ３が下部管群になる。ただし、伝熱管群１４ａ，１５ａの上部管群及び下部管群への群分けは適宜変更することができ、例えば、上記３群の各群内で上下方向に並ぶ各管の間に、さらに整流板１６，１７を配置する構成も可能である。
【００２３】
なお、上記蒸発器１４と吸収器１５は、蒸発器１４で蒸発した冷媒蒸気を吸収器１５に通過させる通過開口を備えた仕切り部２３で仕切られている。また、図では、伝熱管群１４ａ，１５ａを構成する各伝熱管が格子状に配列されたものを示すが、上下左右で隣接する各伝熱管同士の位置を半ピッチずらせた千鳥状に配列してもよい。
【００２４】
また、前記伝熱管群１４ａ，１５ａと周囲の壁２２との間に、壁側から内側に向かって高さが低くなり且つ内側端部が前記伝熱管群１４ａ，１５ａの端に位置する斜板１８，１９を配置している。そして、上記斜板１８，１９の内側端部を前記整流板１６，１７の周縁部に連なるように接続している。尚、図２には、斜板１８，１９の内側端部が上から２番目の管群１４ａ２，１５ａ２と上から３番目の管群１４ａ３，１５ａ３との間の整流板１６，１７に連なるものを示す。
さらに、蒸発器１４において前記伝熱管群１４ａの上方から冷媒液を落下供給する液供給部としての冷媒スプレー噴射装置２０及び吸収器１５において前記伝熱管群１５ａの上方からＬｉＢｒ溶液（吸収液）を落下供給する液供給部としてのＬｉＢｒ溶液スプレー噴射装置２１の夫々と周囲の壁２２との間にも、壁側から内側に向かって高さが低くなり且つ内側端部が前記伝熱管群１４ａ，１５ａの端に位置する斜板１８，１９を配置している。なお、上記液供給部は、スプレー噴射式の他に、底に滴下孔を開けたトレー（受け皿）式のものでもよい。
【００２５】
本実施形態では、蒸発器１４と吸収器１５を１つの壁体内に仕切り部２３で仕切って隣接設置しているため、斜板１８，１９のうち、仕切り部２３側の斜板１８，１９は、仕切り部２３との間のデッドスペースに流れ込んだ冷媒液等を伝熱管１４ａ，１５ａの方に戻す。この結果、斜板１８，１９は、蒸発器１４と吸収器１５との間での液の混入（吸収器１５の溶液が蒸発器１４に混入する、あるいは、蒸発器１４の冷媒が吸収器１５に混入すること）を防止する働きもする。
【００２６】
前記整流板１６，１７は、図３に示すように、中央のメッシュ部分１６ｂ，１７ｂと、これを保持する周囲の枠部分１６ａ，１７ａで構成される。なお、図３では、前記斜板１８，１９の内側端部が上記枠部分１６ａ，１７ａの縁部に接続されたものを示している。
【００２７】
図４に、上記整流板１６，１７と斜板１８，１９が一体に接続されたものを、上下３群の伝熱管群１４ａ，１５ａの間に配置した例を示す。なお、上記整流板１６，１７と斜板１８，１９を接続せず、分離状態で端部同士を近接配置するようにしてもよい。また、図５には、上記整流板１６，１７単体を、上下３群の伝熱管群１４ａ，１５ａの間に配置した例を示す。
【００２８】
上記整流板１６，１７と斜板１８，１９の材質としては、鋼材が使用される。ただし、強度及び腐食に問題が無ければ、樹脂材等で構成してもよい。また、整流板１６，１７のメッシュサイズは、冷媒や吸収液が通過できる範囲で種々のサイズを選択することができる。
【００２９】
〔別実施形態〕
次に別実施形態を列記する。
上記実施形態では、蒸発器１４と吸収器１５の両方において、メッシュが形成された整流板１６，１７、及び、斜板１８，１９を配置したが、蒸発器１４と吸収器１５の少なくとも一方において、整流板１６，１７、及び、斜板１８，１９を配置するようにしてもよい。
【００３０】
上記実施形態では、蒸発器１４と吸収器１５を１つの壁体内に仕切り部２３で仕切って隣接設置したが、蒸発器１４と吸収器１５を別々の壁体内に配置して、蒸発器１４と吸収器１５を配管で接続するようにしてもよい。
【図面の簡単な説明】
【図１】本発明を適用した吸収式冷温水機を備えたガスタービン・コージェネレーションシステムの全体構成図
【図２】本発明に係る蒸発器と吸収器の構造を示す側面図
【図３】本発明に係る整流板及び斜板の構造を示す斜視図
【図４】本発明に係る蒸発器と吸収器の構造の変形例を示す側面図
【図５】本発明に係る蒸発器と吸収器の構造の変形例を示す側面図
【図６】従来例の蒸発器と吸収器の構造を示す側面図
【符号の説明】
１１，１２ 再生器
１４ 蒸発器
１４ａ 伝熱管群
１５ 吸収器
１５ａ 伝熱管群
１６ 整流板
１７ 整流板
１８ 斜板
１９ 斜板
２０ 液供給部
２１ 液供給部[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to an absorption heat pump having an evaporator, an absorber, a regenerator, and a condenser, and more particularly, to a structure of an evaporator and an absorber.
[0002]
[Prior art]
In a conventional absorption heat pump, for example, as shown in FIG. 6, an evaporator and an absorber are arranged adjacent to each other with a partition 23 through which refrigerant vapor can pass, and the refrigerant R condensed in a condenser in the evaporator. In the absorber, the absorption liquid Lc (for example, LiBr aqueous solution) concentrated and regenerated by the regenerator is dropped from above onto the respective heat transfer tube groups 14a and 15a by a spray injection method or the like. In the evaporator, the heat medium flowing in the heat transfer tube 14a is cooled by the heat of evaporation of the refrigerant R, and in the absorber, the refrigerant vapor evaporated by the evaporator is absorbed by the absorbing liquid, and the refrigerant vapor is absorbed to reduce the concentration. The absorbed liquid La is sent to a regenerator (this is referred to as a first conventional technique). Also, as another absorption heat pump technology, the inside of the evaporator and the absorber is divided into upper and lower stages, and the refrigerant and the like flowing through the heat transfer tube group in the upper stage are temporarily stored in a tray provided at the upper and lower boundary points. After that, there is disclosed a structure in which a drop hole formed in the bottom of the tray is dropped into a heat transfer tube group in a lower portion (this is referred to as a second related art) (for example, see Patent Document 1). .
[0003]
[Patent Document 1]
JP-A-2000-179975 (pages 2 to 8, FIGS. 1 to 7)
[0004]
[Problems to be solved by the invention]
However, in the first prior art, when the refrigerant or the absorbing liquid is dropped onto the heat transfer tube group, there is not a small dead space between the heat transfer tube group and the surrounding wall, so that depending on the dripping situation, the dead space may be reduced. In some cases, the refrigerant or the like flows into the space and falls into the lower liquid pool without hitting the heat transfer tube, and does not contribute to heat transfer. Further, even when the refrigerant or the like flows through the heat transfer tubes, there are portions that are not wet at the ends and the like of the heat transfer tubes, and the wet manner is sometimes uneven. As a result, the evaporation efficiency in the evaporator and the absorption efficiency in the absorber are reduced, and there is a possibility that the performance of the absorption heat pump is reduced.
Further, in the second prior art, the refrigerant and the like flowing into the dead space between the upper part of the heat transfer tube group and the surrounding wall are collected in a tray and dropped on the lower part of the heat transfer tube group. Although the refrigerant or the like does not fall without hitting the heat transfer tube at all, there is a possibility that unevenness may occur due to the way the refrigerant or the like wets the heat transfer tube.
[0005]
The present invention has been made in view of the above-described circumstances, and an object of the present invention is to make a refrigerant or the like dropped from the upper part of a heat transfer tube group of an evaporator or an absorber effectively contribute to heat transfer, thereby evaporating the evaporator. In order to improve the evaporation efficiency of the heat transfer tube and the absorption efficiency of the absorber, it is necessary to make the refrigerant or the like uniformly wet each tube of the heat transfer tube group.
In addition, the refrigerant, etc., flowing into the dead space between the heat transfer tube group and the surrounding wall is returned to the heat transfer tube group, further improving the evaporation efficiency in the evaporator and the absorption efficiency in the absorber. To make it happen.
[0006]
[Means for Solving the Problems]
The feature of the invention according to claim 1 of the absorption heat pump for achieving the above object is that at least one of the evaporator and the absorber has an upper tube group located above a heat transfer tube group installed therein. And the lower tube group located on the lower side, the point where the mesh-formed flow straightening plate is arranged such that the lower surface of the flow straightening plate is in contact with the upper surface of the heat transfer tube of the lower tube group or a small gap is opened. .
[0007]
In other words, according to this configuration, the refrigerant or the absorbing liquid that has fallen along the upper tube group of the heat transfer tube group installed inside at least one of the evaporator and the absorber is moved between the upper tube group and the lower tube group. When the flow reaches the flow straightening plate, the refrigerant, etc., that has touched the mesh formed on the current straightening plate penetrates into the gaps between the meshes and flows to the poorly flowing places such as the ends of the heat transfer tube group to spread. The range can be extended uniformly in the lateral direction. Furthermore, since the refrigerant or the like spread and held by the mesh falls down on the upper surface of the heat transfer tubes of the lower tube group arranged in a state of contacting or forming a small gap with the lower surface of the flow straightening plate, a point due to holes or the like is generated. Can be dropped by a line or a surface.
[0008]
Therefore, for example, in the case of receiving a refrigerant or the like in a plate-shaped receiving tray with a drip hole as in the second related art, there is a possibility that the liquid may be dripped in an uneven state due to the liquid amount or the inclination of the plate. On the other hand, in the current plate provided with the mesh of the present invention, the liquid spreads quickly and uniformly due to the permeation action, and the refrigerant and the like can be dripped in a state of being uniformly wetted on each tube of the heat transfer tube group. As a result, the refrigerant and the like dropped from the upper portion to the heat transfer tube group of the evaporator and the absorber can effectively contribute to the heat transfer, thereby improving the evaporation efficiency in the evaporator and the absorption efficiency in the absorber. It becomes possible.
[0009]
A feature of the invention according to claim 2 is that, in addition to the invention according to claim 1, between the heat transfer tube group and the surrounding wall, the height decreases inward from the wall side and the inner end is The swash plate located at the end of the heat transfer tube group is arranged.
[0010]
That is, according to this configuration, when the refrigerant liquid or the like dropped from above flows into the dead space between the heat transfer tube group and the surrounding wall, it is received by the swash plate arranged in the dead space, The swash plate whose height is reduced from the wall side toward the inner side returns the swash plate from the wall side to the position of the end of the heat transfer tube group at the inner end. As a result, the refrigerant and the like flowing into the dead space are returned to the inside and applied to the heat transfer tube group to effectively contribute to heat transfer, thereby further improving the evaporation efficiency in the evaporator and the absorption efficiency in the absorber. Can be.
[0011]
A feature of the invention according to claim 3 is that, in addition to the invention according to claim 1 or 2, a wall is provided between a liquid supply unit that supplies a coolant liquid or a solution from above the heat transfer tube group and a surrounding wall. The point is that the swash plate located at the end of the heat transfer tube group is disposed such that the height decreases from the side toward the inside and the inside end is located at the end of the heat transfer tube group.
[0012]
That is, according to this configuration, the refrigerant liquid or the like scattered to the side of the liquid supply unit that supplies and supplies the refrigerant liquid or the solution from above the heat transfer tube group falls into the dead space between the liquid supply unit and the surrounding wall. When the swash plate flows in, it is received by the swash plate arranged in the dead space, and the position of the end of the heat transfer tube group from the wall side to the inner end portion is reduced by the swash plate whose height decreases inward from the wall side. Returned to Thereby, the refrigerant liquid or the like scattered laterally from the liquid supply unit is applied to the heat transfer tube group to effectively contribute to the heat transfer, thereby further improving the evaporation efficiency in the evaporator and the absorption efficiency in the absorber. Can be realized.
[0013]
The invention according to claim 4 specifies an embodiment suitable for carrying out the invention according to claim 2 or 3, characterized in that the inner end of the swash plate is connected to the peripheral edge of the rectifying plate. At the point where they are connected.
[0014]
That is, according to this configuration, the refrigerant liquid or the like received by the swash plate and returned to the inner end of the swash plate smoothly flows to the peripheral edge of the rectifying plate connected to the inner end of the swash plate. Since it shifts and spreads over the entire current plate, the refrigerant liquid and the like returned by the swash plate are brought into contact not only with the heat transfer tubes at the end of the heat transfer tube group but also with the entire tube group, and the evaporator is used. Evaporation efficiency and absorption efficiency in the absorber can be further improved.
[0015]
BEST MODE FOR CARRYING OUT THE INVENTION
FIG. 1 shows a gas turbine cogeneration system provided with an absorption chiller / heater (an example of an absorption heat pump) to which the present invention is applied, 1 is a gas turbine, and 2 is a compressor connected to an output shaft 1 a of a gas turbine 1. The compressor 2 sucks combustion air A from an intake passage 3 by the compressor 2 and pressurizes and supplies the sucked combustion air A to a combustor 5 of the gas turbine 1 through an air passage 4. The operation of the gas turbine 1 is continued by burning the supply fuel F from the fuel passage 6 in the heater 5.
[0016]
Reference numeral 7 denotes a regenerative heat exchanger for preheating the combustion air A by exchanging heat between the exhaust gas E of the gas turbine 1 sent to the exhaust gas passage 8 and the combustion air A in the air supply passage 4. The air preheating by 7 reduces the amount of fuel required to obtain the required turbine operating temperature, thereby saving fuel consumption of the gas turbine 1.
Reference numeral 9 denotes a generator connected to the output shaft 1a of the gas turbine 1 together with the compressor 2, and the generator 9 is driven by the generated power of the gas turbine 1 to obtain an electric power output (turbine output G) as a cogeneration system. .
[0017]
On the other hand, reference numeral 10 denotes a double-effect absorption chiller / heater, and a heating pipe 11a for heating the absorbent La in the high-temperature regenerator 11 of the absorption chiller / heater 10 is located downstream of the regenerative heat exchanger 7. The turbine exhaust gas E after passing through the regenerative heat exchanger 7 is supplied to the heating pipe 11 a as a heat source heat medium by being interposed in the exhaust gas path 8. By operating the absorption chiller / heater 10 using the retained heat of the turbine exhaust gas E as a driving heat source, a heat output as a cogeneration system is obtained.
[0018]
Reference numeral 12 denotes a low-temperature regenerator that introduces the medium-concentration absorption liquid Lb after the refrigerant R is evaporated and separated by heating by the heating pipe 11a in the high-temperature regenerator 11, and 12a transmits the refrigerant vapor R generated in the high-temperature regenerator 11 to a heat source heat medium. The low-temperature regenerator 12 further generates refrigerant vapor R from the medium-concentration absorbent Lb by heating the absorbent in the low-temperature regenerator 12 by the heating tube 12a.
[0019]
Reference numeral 13 denotes a condenser that cools and condenses the refrigerant vapor R generated in the low-temperature regenerator 12 and the refrigerant R that has passed through the heating pipe 12a of the low-temperature regenerator 12 with the cooling water C passing through the cooler 13a. 13 is an evaporator for evaporating the liquid refrigerant R sent from 13 under a low-pressure atmosphere and cooling the passing water W in the heat transfer tube 14a constituting the output heat exchanger by removing vaporized heat therefrom. This is an absorber for absorbing the evaporated refrigerant R in the evaporator 14 to the concentrated absorption liquid Lc sent from the low temperature regenerator 12 under cooling by the cooling water C passing through the heat pipe 15a. Then, the passing water W is cooled by the evaporator 14 to obtain the cooling power Q.
[0020]
Reference numeral 16a denotes a low-temperature heat exchanger that pre-heats the diluted absorbent La returned from the absorber 15 to the high-temperature regenerator 11 by exchanging heat with the concentrated absorbent Lc sent from the low-temperature regenerator 12 to the absorber 15, and 16b denotes a low-temperature heat exchanger. A high-temperature heat exchanger for preheating the diluted absorbent La preheated by the heat exchanger 16a with the medium-concentration absorbent Lb sent from the high-temperature regenerator 11 to the low-temperature regenerator 12, p1 is a refrigerant circulation pump, and p2 is an absorbent circulation. It is a pump.
[0021]
In the absorption chiller / heater 10, before the dilute absorbent La preheated by the high-temperature heat exchanger 16b is returned to the high-temperature regenerator 11, the dilute absorbent La and the turbine exhaust gas E sent out from the heating pipe 11a are combined. A preheating heat exchanger 16c for final preheating for preheating to a higher temperature by heat exchange is provided, whereby the temperature of the turbine exhaust gas E at the outlet of the heating pipe 11a is set to be high, and the temperature of the refrigerant R in the high temperature regenerator 11 is increased. While the evaporation temperature (evaporation pressure) is kept high, the amount of heat taken in from the exhaust gas E of the turbine as the entire refrigerator is largely secured by preheating the diluted absorption liquid La in the preheating heat exchanger 16c. The amount of residual heat of the turbine exhaust gas E discharged outside the machine is effectively reduced.
In the hot water generation operation of the absorption chiller / heater 10, the refrigerant R heated by the heating pipe 11a in the high-temperature regenerator 11 is short-circuited to the evaporator 14, and the passing water W in the heat transfer pipe 14a is heated by the heated refrigerant R. Heat. Thereby, a thermal output Q for heating the passing water W by the evaporator 14 is obtained.
[0022]
Next, the structure of the evaporator 14 and the absorber 15 will be described. As shown in FIG. 2, the evaporator 14 and the absorber 15 are located on the upper side of the heat transfer tube groups 14a and 15a installed inside. Between the upper tube group to be formed and the lower tube group located on the lower side, mesh-formed rectifying plates 16 and 17 are arranged such that the lower surfaces of the rectifying plates 16 and 17 are in contact with the upper surfaces of the heat transfer tubes of the lower tube group or are slightly smaller. They are arranged with a gap.
Specifically, the heat transfer tube groups 14a, 15a are divided into three groups, upper and lower, and the top tube group 14a1, 15a1 becomes the upper tube group in relation to the second top tube group 14a2, 15a2, The second tube group 14a2, 15a2 from the top becomes the lower tube group, and the second tube group 14a2, 15a2 from the top becomes the upper tube group in relation to the third tube group 14a3, 15a3 from the top. The third tube group 14a3, 15a3 from the top becomes the lower tube group. However, the grouping of the heat transfer tube groups 14a and 15a into the upper tube group and the lower tube group can be changed as appropriate. For example, rectification is further performed between the tubes vertically arranged in each of the three groups. A configuration in which the plates 16 and 17 are arranged is also possible.
[0023]
The evaporator 14 and the absorber 15 are partitioned by a partition 23 having a passage opening through which the refrigerant vapor evaporated by the evaporator 14 passes through the absorber 15. Also, in the figure, the heat transfer tubes constituting the heat transfer tube groups 14a and 15a are shown arranged in a lattice shape. However, the positions of the adjacent heat transfer tubes at the top, bottom, left, and right are arranged in a zigzag pattern shifted by half a pitch. You may.
[0024]
A swash plate between the heat transfer tube groups 14a, 15a and the surrounding wall 22 has a height decreasing from the wall side toward the inside and an inner end located at an end of the heat transfer tube groups 14a, 15a. 18 and 19 are arranged. The inner ends of the swash plates 18 and 19 are connected so as to be continuous with the peripheral edges of the rectifying plates 16 and 17. In FIG. 2, the inner ends of the swash plates 18 and 19 are connected to straightening plates 16 and 17 between the second tube group 14a2 and 15a2 from the top and the third tube group 14a3 and 15a3 from the top. Is shown.
Further, the LiBr solution (absorbing liquid) is supplied from above the heat transfer tube group 15a in the absorber 15 and the refrigerant spray injection device 20 as a liquid supply unit that supplies the coolant liquid from above the heat transfer tube group 14a in the evaporator 14. Also between each of the LiBr solution spray injection devices 21 as the liquid supply units to be dropped and the surrounding wall 22, the height decreases inward from the wall side and the inner ends are the heat transfer tube groups 14 a, Swash plates 18, 19 located at the end of 15a are arranged. The liquid supply unit may be a tray (dish) having a drip hole at the bottom, instead of the spray injection type.
[0025]
In the present embodiment, since the evaporator 14 and the absorber 15 are installed adjacent to each other by partitioning the partition wall 23 in the single wall, the swash plates 18 and 19 on the partition 23 side of the swash plates 18 and 19 are arranged. The refrigerant liquid and the like that have flowed into the dead space between the partition 23 are returned to the heat transfer tubes 14a and 15a. As a result, the swash plates 18 and 19 cause the mixture of the liquid between the evaporator 14 and the absorber 15 (the solution of the absorber 15 is mixed with the evaporator 14 or the refrigerant of the evaporator 14 is mixed with the absorber 15). Also mixes).
[0026]
As shown in FIG. 3, the rectifying plates 16 and 17 are composed of central mesh portions 16b and 17b and surrounding frame portions 16a and 17a that hold the mesh portions. In FIG. 3, the inner ends of the swash plates 18, 19 are connected to the edges of the frame portions 16a, 17a.
[0027]
FIG. 4 shows an example in which the rectifying plates 16, 17 and the swash plates 18, 19 are integrally connected and arranged between three upper and lower heat transfer tube groups 14a, 15a. The end portions may be arranged close to each other in a separated state without connecting the rectifying plates 16 and 17 and the swash plates 18 and 19. FIG. 5 shows an example in which the straightening plates 16 and 17 alone are arranged between three upper and lower heat transfer tube groups 14a and 15a.
[0028]
A steel material is used as a material for the rectifying plates 16 and 17 and the swash plates 18 and 19. However, if there is no problem in strength and corrosion, it may be made of a resin material or the like. Further, the mesh size of the flow regulating plates 16 and 17 can be selected from various sizes as long as the refrigerant and the absorbing liquid can pass through.
[0029]
[Another embodiment]
Next, another embodiment will be described.
In the above embodiment, the rectifying plates 16 and 17 and the swash plates 18 and 19 on which meshes are formed are arranged in both the evaporator 14 and the absorber 15, but in at least one of the evaporator 14 and the absorber 15. , The rectifying plates 16 and 17 and the swash plates 18 and 19 may be arranged.
[0030]
In the above-described embodiment, the evaporator 14 and the absorber 15 are separated from each other by the partitioning part 23 in one wall, and are installed adjacent to each other. However, the evaporator 14 and the absorber 15 are arranged in separate walls, and the evaporator 14 and the absorber 15 are separated. The absorber 15 may be connected by piping.
[Brief description of the drawings]
FIG. 1 is an overall configuration diagram of a gas turbine cogeneration system provided with an absorption type water heater / heater to which the present invention is applied. FIG. 2 is a side view showing a structure of an evaporator and an absorber according to the present invention. FIG. 4 is a perspective view showing a structure of a current plate and a swash plate according to the present invention. FIG. 4 is a side view showing a modification of a structure of an evaporator and an absorber according to the present invention. FIG. 5 is an evaporator and an absorber according to the present invention. FIG. 6 is a side view showing a modification of the structure of FIG. 6. FIG. 6 is a side view showing the structure of a conventional evaporator and absorber.
11, 12 Regenerator 14 Evaporator 14a Heat transfer tube group 15 Absorber 15a Heat transfer tube group 16 Rectifying plate 17 Rectifying plate 18 Swash plate 19 Swash plate 20 Liquid supply unit 21 Liquid supply unit
