JP2951649B2 - Absorption air conditioner - Google Patents
Absorption air conditionerInfo
- Publication number
- JP2951649B2 JP2951649B2 JP10187380A JP18738098A JP2951649B2 JP 2951649 B2 JP2951649 B2 JP 2951649B2 JP 10187380 A JP10187380 A JP 10187380A JP 18738098 A JP18738098 A JP 18738098A JP 2951649 B2 JP2951649 B2 JP 2951649B2
- Authority
- JP
- Japan
- Prior art keywords
- flow path
- hot water
- flows
- heat exchange
- fluid
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/62—Absorption based systems
Landscapes
- Sorption Type Refrigeration Machines (AREA)
- Central Heating Systems (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、吸収式冷暖房装置
（システム）に関し、特に、吸収式冷暖房装置に給湯機
能を付加して、給湯用ボイラーを別途設置しなくても1
台の冷暖房器で給湯機能を奏するようにした給湯機能を
付加した吸収式冷暖房装置（システム）に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an absorption type air conditioner (system), and more particularly, to an absorption type air conditioner having a hot water supply function added thereto without installing a separate hot water supply boiler.
The present invention relates to an absorption-type cooling and heating apparatus (system) having a hot-water supply function in which a cooling and heating unit has a hot-water supply function.
【０００２】[0002]
【従来の技術と発明が解決しようとする課題】一般的な
吸収式冷暖房システムは、アンモニア吸収式の場合とし
iBr 吸収式の場合とに分けられるが、差異点はアンモニ
ア吸収式の場合には作動流体がアンモニア水溶液で、Li
Br吸収式の場合には作動流体がLiBr水溶液で、冷媒とし
てはアンモニア吸収式の場合アンモニアが使用されて、
LiBr吸収式の場合には水が使用される。2. Description of the Related Art A general absorption type air conditioning system is based on the case of an ammonia absorption type.
The difference between the iBr absorption type and the iBr absorption type is that in the case of the ammonia absorption type, the working fluid is an aqueous ammonia solution and Li
In the case of Br absorption type, the working fluid is LiBr aqueous solution, and as the refrigerant, ammonia is used in the case of ammonia absorption type,
In the case of the LiBr absorption type, water is used.
【０００３】すなわち、再生器でアンモニア吸収式の場
合は冷媒としてのアンモニアと吸収媒体としての濃度が
低い低濃度溶液（弱溶液）が作られて、LiBr吸収式の場
合は冷媒としての水と吸収媒体としての濃度が高い高濃
度溶液（強溶液）が分離される。また、作動圧力範囲
は、アンモニア吸収式の場合、高圧で形成されるが、Li
Br吸収式の場合は低圧で形成されることが異なる。[0003] That is, in the case of an ammonia absorption type regenerator, ammonia as a refrigerant and a low concentration solution (weak solution) having a low concentration as an absorption medium are produced, and in the case of a LiBr absorption type, water and absorption as a refrigerant are produced. A highly concentrated solution (strong solution) having a high concentration as a medium is separated. In the case of the ammonia absorption type, the operating pressure range is formed at a high pressure.
It is different in the case of the Br absorption type that it is formed at low pressure.
【０００４】以下ではアンモニア吸収式を基準に説明
し、LiBr吸収式の場合は各々の流体をアンモニア吸収式
の場合とマッチングして考えるとされる。従来の吸収式
冷暖房システムは、図1 に示すように、熱を発生させる
バーナ(1) と、バーナ(1) から発生される熱を加えるこ
とによって高濃度溶液から冷媒蒸気と低濃度溶液を生成
する再生器(2) と、再生器(2) で生成された冷媒蒸気と
ともに蒸発される水を凝縮させて高濃度の冷媒蒸気に精
留する精留器(3) と、精留器(3) から供給された高濃度
の冷媒蒸気を冷却させて液体状態の冷媒に凝縮させる凝
縮器(4) と、凝縮器(4) から凝縮された液冷媒をもっと
過冷させる冷媒熱交換器(5) と、冷媒熱交換器(5) を通
過しながらもっと過冷された液冷媒を２相状態( 液相＋
気相) の冷媒に沸騰させる蒸発器(6) と、蒸発器(6) で
蒸発された２相状熊の冷媒がさらに冷媒熱交換器(5) を
通過しながら凝縮器(4) から蒸発器(6) に流れる相対的
に高温の液冷媒と熱交換を実施して沸騰された冷媒蒸気
及び再生器(2) から生成された低濃度溶液が流入されて
上記冷媒蒸気と低濃度溶液の間の接触で吸収現象が起き
て再生器(2) 初期濃度の高濃度溶液が生成される吸収器
(7) と、吸収器(7) から生成された高濃度溶液を精留器
(3) にポンピングする溶液ポンブ(8) と、再生器(2) で
生成された高濃度溶液と吸収器(7) で生成された高濃度
溶液を熱交換する溶液熱交換器(9) とで構成される。The following description is based on the ammonia absorption type. In the case of the LiBr absorption type, each fluid is considered to be matched with the case of the ammonia absorption type. As shown in Fig. 1, a conventional absorption air-conditioning system generates a burner (1) that generates heat and a refrigerant vapor and a low-concentration solution from a high-concentration solution by adding the heat generated by the burner (1). Regenerator (2), a rectifier (3) that condenses water that evaporates together with the refrigerant vapor generated by the regenerator (2), and rectifies it into high-concentration refrigerant vapor, and a rectifier (3) A condenser (4) that cools the high-concentration refrigerant vapor supplied from the condenser to condense it into a liquid refrigerant, and a refrigerant heat exchanger (5) that further cools the liquid refrigerant condensed from the condenser (4). ) And the supercooled liquid refrigerant passing through the refrigerant heat exchanger (5) to a two-phase state (liquid phase +
An evaporator (6) that boils into a (vapor phase) refrigerant, and a two-phase bear refrigerant evaporated in the evaporator (6) further evaporates from the condenser (4) while passing through the refrigerant heat exchanger (5). The refrigerant vapor boiled by performing heat exchange with the relatively high-temperature liquid refrigerant flowing into the regenerator (6) and the low-concentration solution generated from the regenerator (2) are flowed into the refrigerant vapor and the low-concentration solution. (2) Absorber in which high concentration solution with initial concentration is generated
(7) and the concentrated solution produced from the absorber (7)
A solution pump (8) to be pumped to (3) and a solution heat exchanger (9) to exchange heat between the highly concentrated solution generated by the regenerator (2) and the highly concentrated solution generated by the absorber (7). It consists of.
【０００５】そして、液冷媒流路上の冷媒熱交換器(5)
と蒸発器(6) の間及び低濃度溶液流路上の吸収器(7) と
溶液熱交換器(9) の間には、高圧部と低圧部の圧力差を
補償する膨脹弁(Restrictor)(10)が配置され、凝縮器
(4) 、蒸発器(6) 、吸収器(7)から冷媒と熱文換して温
度が低く若しくは高くなった冷房水又は暖房水が冷房又
は暖房のために移動する室内器(11)及び室外器( 図示せ
ず) が設けられる。The refrigerant heat exchanger (5) on the liquid refrigerant flow path
The expansion valve (Restrictor) (compensating for the pressure difference between the high-pressure section and the low-pressure section) is located between the pressure evaporator (6) and the absorber (7) and the solution heat exchanger (9) on the low concentration solution flow path. 10) is placed the condenser
(4) an indoor unit (11) in which cooling water or heating water whose temperature has been lowered or raised by cooling from the evaporator (6) or the absorber (7) with refrigerant is moved for cooling or heating, and An outdoor unit (not shown) is provided.
【０００６】このように構成された従来の吸収式冷暖房
システムの動作を説明する。再生器(2) 内にある高濃度
溶液が燃焼部であるバーナ(1) によって加熱されて冷媒
蒸気と低濃度溶液が生成されて、上記冷媒蒸気は上昇し
ながら精留器(3) に流入される。上記精留器(3) 内に流
入された冷媒蒸気は吸収器(7) から溶液ポンプ(8) のポ
ンピングにより精留器(3) の内部コイルに流入される高
濃度溶液と熱交換をした後、蒸発された水を凝縮させて
高濃度の冷媒蒸気に精留される。[0006] The operation of the conventional absorption air-conditioning system configured as described above will be described. The high-concentration solution in the regenerator (2) is heated by the burner (1), which is the combustion section, to produce refrigerant vapor and a low-concentration solution, and the refrigerant vapor rises and flows into the rectifier (3) Is done. The refrigerant vapor flowing into the rectifier (3) exchanged heat with the high-concentration solution flowing into the internal coil of the rectifier (3) from the absorber (7) by pumping the solution pump (8). Thereafter, the evaporated water is condensed and rectified into a high-concentration refrigerant vapor.
【０００７】そして、再生器(2) で生成された低濃度溶
液は高圧部である再生器(2) と低圧部である吸収器(7)
の間の圧力差によって吸収器(7) に流入される。上記精
留器(3) で精留された高濃度の冷媒蒸気は、凝縮器(4)
に流入されて凝縮器(4) の周囲に流れる低温の冷却水と
熱交換して液冷媒状態に凝縮されて、この液冷媒は冷媒
熱交換器(5) を通過しながら蒸発器(6) で生成された相
対的に温度が低い冷媒蒸気と熱交換するようになる。[0007] The low-concentration solution generated in the regenerator (2) has a regenerator (2) as a high-pressure part and an absorber (7) as a low-pressure part.
Flows into the absorber (7) due to the pressure difference between. The high-concentration refrigerant vapor rectified by the rectifier (3) is supplied to the condenser (4)
Heat exchanges with the low-temperature cooling water flowing around the condenser (4) and is condensed into a liquid refrigerant state.This liquid refrigerant passes through the refrigerant heat exchanger (5) and evaporates (6). The heat exchange occurs with the relatively low-temperature refrigerant vapor generated in step (1).
【０００８】このような熱交換作用によって、液冷媒の
温度は蒸発器(6) 内の蒸発温度程度まで下がって、冷媒
蒸気は吸収器(7) の飽和温度程度まで上がって吸収現象
が加速されて、冷媒蒸気に包含されている微少量の液冷
媒も蒸発される。以後、蒸発器(6) 内に流入された液冷
媒は蒸発器(6) の周囲に流れる相対的に高温の冷水と熱
交換して２相状態( 液相+ 気相) の冷媒に沸騰し、この
２相状態の冷媒はさらに冷媒熱交換器(5) を通過しなが
ら相対的に高温である液冷媒と熱交換をしてもっと沸騰
して冷媒蒸気になって吸収器(7) に流入される。[0008] By such a heat exchange action, the temperature of the liquid refrigerant drops to about the evaporation temperature in the evaporator (6), and the refrigerant vapor rises to about the saturation temperature of the absorber (7) to accelerate the absorption phenomenon. Thus, a very small amount of liquid refrigerant contained in the refrigerant vapor is also evaporated. Thereafter, the liquid refrigerant flowing into the evaporator (6) exchanges heat with relatively high-temperature cold water flowing around the evaporator (6) and boils into a refrigerant in a two-phase state (liquid phase + gas phase). Then, the refrigerant in the two-phase state further passes through the refrigerant heat exchanger (5) and exchanges heat with the relatively high-temperature liquid refrigerant to be further boiled to form refrigerant vapor and flow into the absorber (7). Is done.
【０００９】吸収器(7) へ流入された冷媒蒸気は再生器
(2) から流入された低濃度溶液とまぜられて吸収器(7)
の内部に流れながら低濃度溶液に吸収されて高濃度溶液
が生成されて、この時発生される吸収熱は吸収器(7) の
周囲に流れる低温の冷却水によって相殺される。一方、
再生器(2) で生成された低濃度溶液は溶液熱交換器(9)
に流入されて吸収器(7) で生成されて精留器(3) を経て
流入された低温の高濃度溶液と熱交換をした後さらに吸
収器(7) に流入される。The refrigerant vapor flowing into the absorber (7) is regenerated
Absorber (7) mixed with low-concentration solution from (2)
The high-concentration solution is generated by being absorbed by the low-concentration solution while flowing into the inside of the device, and the heat of absorption generated at this time is offset by the low-temperature cooling water flowing around the absorber (7). on the other hand,
The low-concentration solution generated in the regenerator (2) is converted to a solution heat exchanger (9).
The heat is exchanged with the low-concentration high-concentration solution generated by the absorber (7) and passed through the rectifier (3), and then further flows into the absorber (7).
【００１０】この時、吸収器(7) で生成された高濃度溶
液は溶液ポンブ(8) のポンビングによつて精留器(3) に
流入された後溶液熱交換器(9) に流入されて、この高濃
度溶液は再生器(2) から生成されて流入される高温の低
濃度溶液と熱交換をして温度が上昇された後さらに再生
器(2) に流入されて上記のような作動を順次繰り返すに
なる。At this time, the high-concentration solution generated in the absorber (7) flows into the rectifier (3) by the pumping of the solution pump (8), and then flows into the solution heat exchanger (9). The high-concentration solution exchanges heat with the high-temperature low-concentration solution generated from the regenerator (2) and flows thereinto. The operation is sequentially repeated.
【００１１】ここで、システムの特性上再生器(2) と凝
縮器(4) は高圧部を形成し、蒸発器(6) と吸収器(7) は
低圧部を形成することになるが、このような圧力の差は
多数の膨脹弁(10)の利用により解決できる。このような
吸収式冷暖房サイクルは冷房及び暖房機能のヒートポン
プとして、冷房の場合には、蒸発器(6) で冷媒の蒸発潜
熱から冷房水を得ることができ、暖房の場合には、凝縮
器(4) の凝縮潜熱及び吸収器(7) の吸収熱から暖房水を
得ることができる。Here, due to the characteristics of the system, the regenerator (2) and the condenser (4) form a high pressure part, and the evaporator (6) and the absorber (7) form a low pressure part. Such pressure differences can be overcome by using multiple expansion valves (10). Such an absorption type cooling / heating cycle serves as a heat pump for cooling and heating functions.In the case of cooling, cooling water can be obtained from the latent heat of evaporation of the refrigerant in the evaporator (6), and in the case of heating, the condenser ( Heating water can be obtained from the condensation heat of 4) and the heat of absorption of the absorber (7).
【００１２】このような動作はシステムが作動する間平
衡状態で連続循環的に進行する。一方、このような吸収
式冷暖房システムに給湯用熱交換器(12)と、給湯用熱交
換器(12)を加熱するための給湯用パーナ(13)を設けて、
湯が必要な場合に、給湯用熱交換器(12)に水を供給して
給湯用パーナ(13)を作動させて給湯し、そうでない場合
には作動させない形式が一般的である。このような形式
とは異なる別の技術形式のものは、現在のところ知られ
ていない。[0012] Such operation proceeds continuously and cyclically at equilibrium during operation of the system. On the other hand, such an absorption type cooling and heating system is provided with a hot water supply heat exchanger (12) and a hot water supply parner (13) for heating the hot water supply heat exchanger (12).
In general, when hot water is required, water is supplied to the hot water supply heat exchanger (12) by operating the hot water supply parner (13), and otherwise not operated. No other technical type is known at this time.
【００１３】以下、上記システムの各構成部( 凝縮器
(4) 、蒸発器(6) 、吸収器(7) 、溶液熱交換器(9))を基
本的に構成するプレート熱交換器について説明する。先
ず、その構造は、図２に示すように、多数枚が積層され
た熱交換プレート(14)に４つの流出入口が形成される
が、高温部流体か流出/ 流入することができる高温部流
体流入口(15)及び高温部流体流出口(16)が上下に形成さ
れており、その側面に低温部流体が流出/ 流入すること
ができる低温部流体流出口(17)及び低温部流体流入口(1
8)が上下に形成されている。Hereinafter, each component of the system (condenser)
(4) The plate heat exchanger basically comprising the evaporator (6), the absorber (7), and the solution heat exchanger (9) will be described. First, as shown in FIG. 2, four outflow ports are formed in a multi-layered heat exchange plate (14) as shown in FIG. An inflow port (15) and a high-temperature section fluid outlet (16) are formed at the top and bottom, and a low-temperature section fluid outlet (17) and a low-temperature section fluid inlet through which low-temperature section fluid can flow out / into the side surface. (1
8) is formed above and below.
【００１４】また、熱交換プレート(14)の表面は櫛歯模
様の皺が寄っているが、その側断面は山と谷が交互に形
成された波形状を呈する。そして、最初の板（プレー
ト）が櫛歯模様のＶ（ないし谷）部分が上方向を向くよ
うに配置され、次の板（プレート）がその対応するＶ部
分が下方向を向くように配置される、というような繰り
返し形式で多数枚の板（プレート）が前後に重ねられて
結合される。The surface of the heat exchange plate (14) is wrinkled in a comb-like pattern, but its side section has a wave shape in which peaks and valleys are alternately formed. Then, the first plate (plate) is arranged such that the V (or valley) portion of the comb pattern faces upward, and the next plate (plate) is arranged such that the corresponding V portion faces downward. A large number of plates (plates) are stacked one on top of the other in a repetitive manner.
【００１５】このように前後に隣接（結合）したプレー
ト(14)の山形の部分同士が密着することによって、断面
が網状を呈するような部分が形成される。図面上の矢印
→は、高温部流体の流れを示し、矢印⇒は、低温部流体
の流れを示す。このような構成において、高温部流体流
入口(15)と、低温部流体流入口(18)を通して高温の流体
と低温の流体が流入されると熱交換器内で高温部流体と
低温部流体は熱交換プレート(14)の間を流れ、熱交換が
起きる。この場合、熱交換プレート(14)が多数枚積み重
ねられているので、流体は各々のプレート(14)の間に形
成されている流路中の該当する流路を流れる。As described above, the chevron-shaped portions of the plate (14) which are adjacent (joined) in front and rear are in close contact with each other, so that a portion having a net-like cross section is formed. The arrow → in the drawing indicates the flow of the high temperature part fluid, and the arrow ⇒ indicates the flow of the low temperature part fluid. In such a configuration, when a high-temperature fluid and a low-temperature fluid are introduced through the high-temperature fluid inlet (15) and the low-temperature fluid inlet (18), the high-temperature fluid and the low-temperature fluid flow in the heat exchanger. It flows between the heat exchange plates (14) and heat exchange occurs. In this case, since a large number of heat exchange plates (14) are stacked, the fluid flows through a corresponding one of the channels formed between the plates (14).
【００１６】すなわち、最初（１番目）のプレートと２
番目のプレートの間には、低温部流体が流れ、２番目の
プレートと３番目のプレートの間には、高温部流体が流
れ、３番目のプレートと４番目のプレートの間には、低
温部流体が流れる、というような規則性をもって、他の
プレート間においても該当する流体が流れる。例えば、
低温部流体流入口／流出口(18/17) は、１番目のプレー
トと２番目のプレートとの間に形成された流路と、３番
目のプレートと４番目のプレートとの間に形成された流
路と連通される。同じように、高温部流体流入口／流出
口(15/16) は、２番目のプレートと３番目のプレートと
の間に形成された流路と、４番目のプレートと５番目の
プレートとの間に形成された流路と連通される。That is, the first (first) plate and 2
The cold fluid flows between the third plates, the hot fluid flows between the second and third plates, and the cold fluid flows between the third and fourth plates. With the regularity that the fluid flows, the corresponding fluid flows between other plates. For example,
The cold section fluid inlet / outlet (18/17) is formed between the first plate and the second plate, the flow path formed between the third plate and the fourth plate. Communication with the flow path. Similarly, the hot section fluid inlet / outlet (15/16) connects the flow path formed between the second and third plates with the fourth and fifth plates. It is communicated with the flow path formed between them.
【００１７】このようにして高温部流体と低温部流体
は、熱交換プレート(14)を間に挟んで離隔された状態で
熱交換が行われることになる。このとき、熱交換プレー
ト(14)の表面に形成された櫛歯模様に関して、１つのプ
レート(14)とこれに隣接した他のプレート(14)の間にお
いて逆向きになるので、各流路における流体の流動形態
が乱流形態になり伝熱性能が向上し得る。In this manner, heat exchange is performed between the high-temperature part fluid and the low-temperature part fluid while being separated from each other with the heat exchange plate (14) interposed therebetween. At this time, the comb pattern formed on the surface of the heat exchange plate (14) is reversed between one plate (14) and another plate (14) adjacent thereto, so The flow form of the fluid becomes turbulent, and the heat transfer performance can be improved.
【００１８】また、各プレート(14)は多数枚が密着され
た状態でろう付け技術を利用して結合され、各流体流路
の離隔が可能である。しかしながら、従来の吸収式冷暖
房システムは給湯機能を具えていなかった。例えば、給
湯機能を付加したい場合、バーナーと給湯用熱交換器と
を別途設けることが必要になり、構造が複雜になると共
に、部品要素の追加、バーナー使用による燃料費、維持
及び補修費によって生産原価が増大され、また、製品が
大型化する等の問題があった。Further, the plates 14 are connected to each other by using a brazing technique in a state in which a large number of the plates 14 are in close contact with each other, so that each fluid flow path can be separated. However, the conventional absorption cooling and heating system does not have a hot water supply function. For example, if it is desired to add a hot water supply function, it is necessary to separately provide a burner and a heat exchanger for hot water supply, which complicates the structure and adds parts and components, fuel costs by using the burner, and maintenance and repair costs. There have been problems such as an increase in cost and an increase in the size of the product.
【００１９】そこで、本発明の主たる目的は、給湯用ボ
イラーを別途設置する必要のない、すなわち、給湯機能
を元々具えた吸収式冷暖房システムを提供することにあ
る。Accordingly, a main object of the present invention is to provide an absorption type air conditioning system which does not require a separate hot water supply boiler, that is, has an original hot water supply function.
【００２０】[0020]
【課題を解決するための手段】上記課題を解決するため
に本発明は、再生器から発生されて流出される高温の低
濃度溶液と吸収器で生成されて再生器に流入される低温
の高濃度溶液間の熱交換過程で必要熱量を得ることがで
きるように再生器と吸収器の間に設置された第１熱交換
手段と、この再生器から発生された高温の低濃度溶液及
び再生器の外部発散熱を通して必要熱量を得ることがで
きるように再生器の周囲に設置された第２熱交換手段を
備えることを構成上の特徴とする。SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a high-temperature low-concentration solution generated and discharged from a regenerator and a low-temperature high-concentration solution generated in an absorber and flowing into a regenerator. First heat exchange means provided between the regenerator and the absorber so as to obtain a required amount of heat in a heat exchange process between the concentration solutions, a high-temperature low-concentration solution generated from the regenerator and a regenerator It is characterized in that it comprises a second heat exchange means installed around the regenerator so that the required amount of heat can be obtained through the external radiated heat.
【００２１】[0021]
【発明の実施の形態】以下に、本発明の実施の形態を図
面を参照して詳説する。 ［第１実施態様］図３は、本発明の第１実施態様に適用
される給湯用三重熱交換器として、従来構造の溶液熱交
換器を代替して使用される。Embodiments of the present invention will be described below in detail with reference to the drawings. [First Embodiment] FIG. 3 shows a triple heat exchanger for hot water supply applied to a first embodiment of the present invention, which is used instead of a solution heat exchanger having a conventional structure.
【００２２】その形状は概ね六面体の外観を有し、その
上下面には高温部流体流入口(102)及び高温部流体流出
口(103) が形成されて、その前後面には給湯水( 又は暖
房水) 流入口(104) 及び給湯水( 又は暖房水) 流出口(1
05) が形成されて、両側面には低温部流体流入口(106)
及び低温部流体流出口(107) が形成される。また、上記
給湯用三重熱交換器(101) の内部には、低温部流体分岐
管(108) と給湯水( 又は暖房水) 分岐管(109) が形成さ
れて、給湯用三重熱交換器(101) に流入される流体を上
記低温部流体分岐管(108) 又は給湯水( 又は暖房水) 分
岐管(109) に分岐するための分配板(110) が給湯用三重
熱交換器(101) の前面、後面、及び両側面に形成され
る。The shape has a substantially hexahedral appearance, and a high temperature part fluid inlet (102) and a high temperature part fluid outlet (103) are formed on the upper and lower surfaces thereof, and hot water (or hot water) is provided on the front and rear surfaces thereof. Heating water) Inlet (104) and hot water (or heating water) Outlet (1
05) is formed, and the low-temperature fluid inlet (106) is formed on both sides.
And a cold part fluid outlet (107) is formed. Further, a low temperature part fluid branch pipe (108) and hot water (or heating water) branch pipe (109) are formed inside the hot water supply triple heat exchanger (101), and the hot water triple heat exchanger (101) is formed. A distribution plate (110) for branching the fluid flowing into the low temperature section fluid branch pipe (108) or the hot water (or heating water) branch pipe (109) is provided by a triple heat exchanger (101) for hot water supply. Are formed on the front, rear, and both sides.
【００２３】また、上記低温部流体分岐管(108) と給湯
水( 又は暖房水) 分岐管(109) の中の１つは、相互間の
熱交換面積を確保するために湾曲状に形成され、他の１
つは最大限の空間活用のために湾曲状に形成された分岐
管の湾曲部に位置するように配置される。図３では、低
温部流体分岐管(108) が湾曲された形態で、給湯水分岐
管(109)が真直な形態であるように例示的に図示されて
いる。One of the low temperature part fluid branch pipe (108) and the hot water (or heating water) branch pipe (109) is formed in a curved shape to secure a heat exchange area between them. The other one
One is arranged so as to be located at a curved portion of a branch pipe formed in a curved shape for maximum space utilization. FIG. 3 exemplarily shows that the cold part fluid branch pipe (108) is curved and the hot water branch pipe (109) is straight.
【００２４】そして、上部に流入される高温部流体の流
路を形成しながら流体の熱交換器内における滞留時間を
長くするためのバフル板(111) が給湯用三重熱交換器(1
01)の上部から下部までジグザグ形状で形成される。実
質的にシステム内での高温部流体は再生器(2) から発生
された高温の低濃度溶液を、給湯水は給湯に必要な水
を、低温部流体は吸収器(7) から生成された相対的に低
温の高濃度溶液を意味する。A baffle plate (111) for increasing the residence time of the fluid in the heat exchanger while forming a flow path for the high temperature fluid flowing into the upper portion is provided by a triple heat exchanger (1) for hot water supply.
01) is formed in a zigzag shape from the upper part to the lower part. The high-temperature part fluid in the system was substantially the hot low-concentration solution generated from the regenerator (2), the hot water was the water necessary for hot water supply, and the low-temperature part fluid was generated from the absorber (7). Means a relatively cold, highly concentrated solution.
【００２５】図４は、本発明による再生器側給湯用熱交
換器として、再生器(2) で形成された高温の冷媒蒸気が
流動する外部流路(113) と、給湯水( 又は暖房水) が流
動する内部流路(114) が相互間の熱交換領域（面積）を
最大化するために鋸歯形状で互いにかみあっており、外
部流路(113) 及び内部流路(114) は、コイル形状で再生
器(2) の表面に巻かれる。FIG. 4 shows a heat exchanger for hot water supply on the regenerator side according to the present invention, an external flow path (113) formed by the regenerator (2) through which high-temperature refrigerant vapor flows, and hot water (or heating water). ) Flow through each other in a saw-tooth shape to maximize the heat exchange area (area) between them, and the external flow path (113) and the internal flow path (114) are coiled. It is wound on the surface of the regenerator (2) in shape.
【００２６】また、冷媒蒸気流入管(115) 及び冷媒蒸気
流出管(116) は、外部流路(113) に連結されており、給
湯水( 又は暖房水) 流入管(117) 及び給湯水( 又は暖房
水)流出管(118) は、内部流路(114) に連結されてい
る。［第２実施態様］図５は、本発明の第２実施態様に
適用される溶液熱交換器として、既存の溶液熱交換器
(9) の構造を改善して給湯機能を具備するようにしたも
のである。The refrigerant vapor inflow pipe (115) and the refrigerant vapor outflow pipe (116) are connected to an external flow path (113), and the hot water (or heating water) inflow pipe (117) and the hot water ( The outlet pipe (118) is connected to the internal flow path (114). Second Embodiment FIG. 5 shows an existing solution heat exchanger as a solution heat exchanger applied to a second embodiment of the present invention.
(9) The structure of (9) is improved to have a hot water supply function.
【００２７】これは既存構造と殆ど同一であるが、溶液
熱交換器機能を行いながら給湯機能も共に行うように給
湯水流入口(123) 及び流出口(124) を備えており、この
点で従来技術とは区別される。先ず、その構造をみると
多数枚のプレート(120) が上下逆にして密着結合され、
その結合隙間には流体の流路が形成される。This is almost the same as the existing structure, except that a hot water supply inlet (123) and a hot water supply outlet (124) are provided so that the hot water supply function can be performed while performing the solution heat exchanger function. It is distinguished from technology. First, looking at the structure, many plates (120) are tightly joined upside down,
A fluid flow path is formed in the connection gap.
【００２８】プレート(120) の上下には、６個の流入/
出口(121〜126)が形成されるが、上部右側から高温部流
体流入口(121) 、給湯水流出口(124) 、低温部流体流出
口(126)(もし高温部流体と低温部流体の流れが同一の方
向であれば流入口となる) の順に配置されて、下部右側
から高温部流体流出口(122) 、給湯水流入口(123) 、低
温部流体流入口(125) の順に配置される。At the top and bottom of the plate (120), six inflow /
Outlets (121 to 126) are formed, but from the upper right side, the high temperature part fluid inlet (121), the hot water supply outlet (124), the low temperature part fluid outlet (126) (if the high temperature part fluid and the low temperature part fluid flow If they are in the same direction, they will be the inlets), and from the lower right side, the hot part fluid outlet (122), the hot water inlet (123), and the cold part fluid inlet (125) are arranged in this order. .
【００２９】上記各々の流体流入/ 出口(121〜126)は、
プレート(120) の結合隙間によって形成される流路に各
々連通されているが、高温部流体流路に隣接した流路に
は低温部流体及び給湯水が流動するように構成される。
また、各々の流入/ 出口(121〜126)は、プレート熱交換
器の反対面に別個に位置することもできる。Each of the fluid inlets / outlets (121-126) is
Each of the flow passages formed by the coupling gaps of the plate (120) communicates with each other, but the flow passage adjacent to the high temperature portion fluid passage is configured so that the low temperature portion fluid and the hot water flow.
Also, each inlet / outlet (121-126) can be located separately on the opposite side of the plate heat exchanger.
【００３０】このときも同様に、高温部流体流入口(12
1) には、再生器から発生された高温の低濃度溶液が、
給湯水流入口(123) には、給湯に使用される給湯水が、
低温部流体流入口(125) には、吸収器(7) から生成され
た高濃度溶液が流入される。また、給湯用三重熱交換器
(101) と再生器側給湯用熱交換器(112) 、又は改善され
た溶液熱交換器(119) と再生器側給湯用熱交換器(112)
は、互いに連動して作動するように構成される。At this time, similarly, the fluid inlet (12)
In 1), the high-temperature, low-concentration solution generated from the regenerator
At the hot water supply inlet (123), hot water used for hot water supply is
The high-concentration solution generated from the absorber (7) flows into the low-temperature fluid inlet (125). In addition, triple heat exchanger for hot water supply
(101) and heat exchanger for regenerator hot water supply (112), or improved solution heat exchanger (119) and heat exchanger for regenerator hot water supply (112)
Are configured to operate in conjunction with each other.
【００３１】図面の矢印→は、高温部流体の流れを、≫
は、低温部流体の流れを、⇒は、給湯水の流れをそれぞ
れ示す。以下、本発明の各実施態様の作用につき、上記
構成に基づいて詳説する。先ず、本発明の第１実施態様
である給湯用三重熱交換器(101) の作用を説明する。The arrow → in the drawing indicates the flow of the high temperature fluid,
Indicates the flow of the low temperature part fluid, and ⇒ indicates the flow of the hot water. Hereinafter, the operation of each embodiment of the present invention will be described in detail based on the above configuration. First, the operation of the hot water supply triple heat exchanger (101) according to the first embodiment of the present invention will be described.
【００３２】吸収器(7) から生成された高濃度溶液と、
給湯( 又は暖房) のための給湯水(又は暖房水) と、再
生器(2) から生成された低濃度溶液が各々の流入口(10
2)(104)(106) を通して給湯用三重熱交換器(101) の内
部に流入される。上記低濃度溶液はバフル板(111) によ
って形成された流路に従って上部からジグザグにずり落
ちるように流れ、高濃度溶液又は給湯水( 暖房水) は分
配板(110) によって各々の分岐管(108)(109)に分配され
る。A highly concentrated solution produced from the absorber (7);
Hot water (or heating water) for hot water (or heating) and the low-concentration solution generated from the regenerator (2) are supplied to each inlet (10
2) It flows into the hot water supply triple heat exchanger (101) through (104) and (106). The low-concentration solution flows in a zigzag manner from the top according to the flow path formed by the baffle plate (111), and the high-concentration solution or hot water (heating water) flows through each branch pipe (108) by the distribution plate (110). (109).
【００３３】このような過程を通して互いに熱伝達を行
った後、温度が上がった給湯水は、給湯水流出口(105)
を通して外部に吐出され、高濃度溶液は、低温部流体流
出口(107) を通して流出されて再生器(2) に流入され
て、面溶液は高温部流禮流出口(103) を通して流出され
て吸収器(7) に流入される。次に、本発明による再生器
側給湯用熱交換器(112) の動作を説明する。After heat is transferred to each other through such a process, the hot water whose temperature has increased is supplied to the hot water outlet (105).
The high-concentration solution flows out through the low-temperature part fluid outlet (107) and flows into the regenerator (2), while the surface solution flows out through the high-temperature part flow outlet (103) and is absorbed. Into the vessel (7). Next, the operation of the regenerator-side hot water supply heat exchanger (112) according to the present invention will be described.
【００３４】先ず、給湯水( 又は暖房水) が給湯水流入
管(117) を通して流入されて再生器(2) の表面に接触さ
れた内部流路(114) に従って流れながら再生器(2) 表面
の発散熱から熱を伝達して受けた後、給湯水流出管( Ｈ
8)を通して吐出される。一方、再生器(2) から生成され
た冷媒蒸気は、冷媒蒸気流入管(115) を通して流入され
て外部流路(113) に従って流れながら内部流路(114) に
従って流動する給湯水に熱を伝達した後、冷媒蒸気流出
管(116) を通して流出されて吸収器(7)に流入される。First, hot water (or heating water) flows through the hot water inflow pipe (117) and flows along the internal flow path (114) in contact with the surface of the regenerator (2) while flowing on the surface of the regenerator (2). After transmitting and receiving the heat from the radiated heat, the hot water outlet pipe (H
Discharged through 8). On the other hand, the refrigerant vapor generated from the regenerator (2) flows through the refrigerant vapor inflow pipe (115) and transfers heat to the hot water flowing along the internal flow path (114) while flowing along the external flow path (113). After that, the refrigerant flows out through the refrigerant vapor outflow pipe (116) and flows into the absorber (7).
【００３５】本発明の第２実施態様である改善された溶
液熱交換器(119) の動作は、本発明の第１実施態様であ
る給湯用三重熱交換器(101) の動作と殆ど同一である
が、各流体の流路構成面で差異があり、以下これを詳説
する。吸収器(7) から生成された高濃度溶液と、給湯(
又は暖房) のための給湯水(又は暖房水) と、再生器(2)
から発生された高温の低濃度溶液は、各々の流入口(12
1)(123)(125) を通して溶液熱交換器(119) の内部に流
入される。The operation of the improved solution heat exchanger (119) according to the second embodiment of the present invention is almost the same as that of the triple water heat exchanger (101) according to the first embodiment of the present invention. However, there are differences in the flow path configuration of each fluid, and this will be described in detail below. High-concentration solution generated from the absorber (7) and hot water (
Or heating) or hot water (or heating water) and a regenerator (2)
The hot, low-concentration solution generated from the
1) It flows into the solution heat exchanger (119) through (123) and (125).
【００３６】溶液熱交換器(119) 内部に流入された各々
の流体は、各々の流路を通って流れながらプレート(12
0) を間に挟んで離隔して隣接する流体と熱交換を行
う。しかるに、プレート(120) 間の結合隙間によって形
成される流路の構成として、低濃度溶液が流動する流路
に隣接した流路に、給湯水及び高濃度溶液が流れるよう
に構成されているので、高温部流体である低濃度溶液か
ら低温部流体である高濃度溶液と給湯水が共に熱交換プ
レート(120) を間に挟んで離隔して流れながら熱交換を
行うことになる。Each of the fluids flowing into the solution heat exchanger (119) flows through each of the flow passages while the plate (12) flows.
0) heat exchange with adjacent fluids separated by. However, since the configuration of the flow path formed by the coupling gap between the plates (120) is such that hot water and the high concentration solution flow in the flow path adjacent to the flow path in which the low concentration solution flows. In addition, heat exchange is performed while the low-concentration fluid, which is a high-temperature part fluid, and the high-concentration solution, which is a low-temperature part fluid, and hot water flow while being separated from each other with a heat exchange plate (120) therebetween.
【００３７】すなわち、１番目と２番目のプレートの間
に給湯水が流れ、２番目のプレートと３番目のプレート
の間には、高温部流体である低濃度溶液が流れ、３番目
のプレートと４番目のプレートの間には、低温部流体で
ある高濃度溶液が流れ、４番目のプレートと５番目のプ
レートの間には、高温部流体である低濃度溶液が流れ
る。That is, hot water flows between the first and second plates, and a low-concentration solution, which is a high-temperature fluid, flows between the second and third plates. A high-concentration solution as a low-temperature fluid flows between the fourth plate and a low-concentration solution as a high-temperature fluid flows between the fourth plate and the fifth plate.
【００３８】すなわち、給湯水、低濃度溶液、高濃度溶
液、低濃度溶液、給湯水、低濃度溶液、高濃度溶液
.....というような流路構成が形成される。このような
過程を通して各流体間で互いに熱伝達が行われた後、温
度が上がった給湯水は、給湯水流出口(124) を通して給
湯が必要な部分に供給され、高濃度溶液は、低温部流体
流出口(126) を通して流出されて再生器(2) に流入さ
れ、低濃度溶液は、高温部流体流出口(122) を通して流
出されて吸収器(7) に流入される。That is, hot water, low concentration solution, high concentration solution, low concentration solution, hot water, low concentration solution, high concentration solution
A channel configuration such as ..... is formed. After heat is transferred between the fluids through such a process, the hot water whose temperature has risen is supplied to a portion requiring hot water through a hot water outlet (124), and the high-concentration solution is supplied to the low-temperature portion fluid. The low concentration solution is discharged through the outlet (126) and flows into the regenerator (2), and the low concentration solution is discharged through the high temperature part fluid outlet (122) and flows into the absorber (7).
【００３９】このように本発明においては、モード切換
によって、冷暖房及び給湯同時運転、冷暖房運転、給湯
単独運転、というようにそれぞれを実行できる。以下こ
れを添付図面に基づいて詳細に説明する。先ず、冷暖房
及び給湯同時運転時には、図６に示すように、既存シス
テムで説明した冷暖房運転で凝縮器(4) から流出される
冷却水の全部を吸収器(7) に流入させて、これを冷暖房
モードによって室内外器に送るようになっている。給湯
水用水は、再生器側給湯用熱交換器(112) の内部流路(1
14) を通過し、さらに給湯用三重熱交換器(101) の給湯
水流路を流れながら高温箇所から熱を伝達して受けて給
湯水となり、室内の給湯配管( 図示せず）を通して供給
される。As described above, according to the present invention, the mode switching can execute each of the simultaneous cooling / heating and hot water supply operation, the cooling / heating operation, and the hot water supply independent operation. Hereinafter, this will be described in detail with reference to the accompanying drawings. First, at the time of simultaneous cooling and heating and hot water supply operation, as shown in FIG. 6, the entire cooling water flowing out of the condenser (4) in the cooling and heating operation described in the existing system is allowed to flow into the absorber (7). The air is sent to the indoor and outdoor units in the cooling and heating mode. The hot water is supplied to the internal flow passage (1) of the regenerator-side hot water heat exchanger (112).
14), and further flows through the hot water flow path of the hot water supply triple heat exchanger (101) to transfer and receive heat from the high temperature location to become hot water, which is supplied through the indoor hot water supply pipe (not shown). .
【００４０】その他の流体の流路は、既存の冷暖房運転
時と同様である。このとき、再生器(2) で発生された冷
媒蒸気は、再生器側給湯用熱交換器(112) に流入させず
に、従来のように凝縮器(4) に送られる。勿論再生器
(2) から発生された高温の低濃度溶液は、給湯用三重熱
交換器(101) の高温部流体流入口(102) を通して流入さ
れて低温部流体流入口(l06) を通して流入された低温の
高濃度溶液及び給湯水流入口(104) を通して流入される
給湯水と熱交換を行う。その後、各々の流出口(103)(10
5)(107) を通して流出され、低濃度溶液は、吸収器(7)
に流動し、高濃度溶液は、再生器(2) に流動する。The other fluid flow paths are the same as in the existing cooling and heating operation. At this time, the refrigerant vapor generated in the regenerator (2) is sent to the condenser (4) in the conventional manner without flowing into the regenerator-side hot water supply heat exchanger (112). Of course regenerator
The high-temperature low-concentration solution generated from (2) flows through the high-temperature fluid inlet (102) of the hot water supply triple heat exchanger (101) and flows through the low-temperature fluid inlet (l06). Heat exchange is performed with hot water supplied through the high concentration solution and hot water inlet (104). After that, each outlet (103) (10
5) The low-concentration solution discharged through (107) passes through the absorber (7).
And the highly concentrated solution flows to the regenerator (2).
【００４１】冷暖房運転時には、図７に示すように、既
存の冷暖房システムの流動流路と殆ど同じである。但
し、冷媒熱交換器(5) で流出される冷媒蒸気を再生器側
給湯用熱交換器(112) の外部流路(113) に流れるように
した後、吸収器(7) に流入されるようにして、再生器側
給湯用熱交換器(112) 内の給湯水が過熱されないように
した点が異なる。During the cooling / heating operation, as shown in FIG. 7, the flow path is almost the same as that of the existing cooling / heating system. However, the refrigerant vapor flowing out of the refrigerant heat exchanger (5) is allowed to flow to the external flow path (113) of the regenerator-side hot water supply heat exchanger (112), and then flows into the absorber (7). The difference is that the hot water in the regenerator-side hot water supply heat exchanger (112) is not overheated.
【００４２】これは本モードで給湯水が流れなくても再
生器側給湯用熱交換器(112) の外部流路(113) に流れる
冷媒蒸気がつづけて熱を取り上げるようにして流れない
給湯水が過熱されないようにしたものである。また、再
生器(2) から発生された低濃度溶液は、給湯用三重熱交
換器(101) の高温部流体流入口(102) を通して流入され
て低温部流体流入口(106) を通して流入された高濃度溶
液と熱交換を行う。In this mode, even if hot water does not flow in this mode, hot water does not flow as the refrigerant vapor flowing in the external flow path (113) of the regenerator-side hot water supply heat exchanger (112) continues to take up heat. Is not overheated. The low-concentration solution generated from the regenerator (2) flows through the high-temperature fluid inlet (102) of the hot water supply triple heat exchanger (101) and flows through the low-temperature fluid inlet (106). Heat exchange with highly concentrated solution.
【００４３】これによって、溶液熱交換器としての機能
を奏しながらも、低濃度溶液の熱を高濃度溶液がつづけ
て取り上げるので給湯水流路内に流れない給湯水が過熱
されなくなる。尚、安全のために給湯水流路に過圧防止
バルブ( 図示せず）を装着して、例えば、過熱によって
給湯水流路が高圧になった場合のその圧力を外部に排出
し得るように構成することができる。Thus, while functioning as a solution heat exchanger, the heat of the low-concentration solution is continuously taken up by the high-concentration solution, so that hot water that does not flow into the hot water flow path is not overheated. For safety, an overpressure prevention valve (not shown) is attached to the hot water supply passage so that, for example, when the hot water supply passage becomes high pressure due to overheating, the pressure can be discharged to the outside. be able to.
【００４４】その外の各々の流体流路は、既存のシステ
ムの流体流路と略同一である。給湯単独運転時にあって
は、図８に示すように、システム全体を動かす必要がな
いので、一旦再生器(2) から発生された低濃度溶液は、
給湯用三重熱交換器(101) の高温部流体流入口(102) に
送られ、冷媒蒸気は、再生器側給湯用熱交換器(112) に
送られ、その外部流路(113) に従って流れながら内部流
路(114) に従って流れる給湯水と熱交換し、以後凝縮さ
れた状態で再生器側給湯用熱交換器(112) から出て来て
膨張弁(10)によって減圧された後吸収器(7) に送られ
る。Each of the other fluid passages is substantially identical to the fluid passage of the existing system. At the time of hot water supply alone operation, as shown in FIG. 8, there is no need to move the entire system, so the low concentration solution once generated from the regenerator (2)
The refrigerant vapor is sent to the high-temperature part fluid inlet (102) of the hot water supply triple heat exchanger (101), and the refrigerant vapor is sent to the regenerator-side hot water supply heat exchanger (112) and flows along the external flow path (113). While exchanging heat with the hot water flowing along the internal flow path (114), and then coming out of the regenerator-side hot water supply heat exchanger (112) in a condensed state and decompressed by the expansion valve (10). Sent to (7).
【００４５】また、給湯水は、再生器側給湯用熱交換器
(112) の内部流路(114) に従って流れながら再生器(2)
の表面及び外部流路(113) に従って流れる冷媒蒸気から
熱を伝達して受ける状態でさらに給湯用三重熱交換器(1
01) に流入する。そこにおいて熱交換が起きて給湯水と
なり、その後室内の給湯配管を通して給湯が必要な部分
に供給される。給湯用三重熱交換器(101) から流出され
た低濃度溶液は、吸収器(7) に送られ、前述した冷媒蒸
気を吸収し、高濃度溶液になった後、低温部流体流入口
(106) を通して給湯用三重熱交換器(101) に流入され
る。The hot water is supplied to the heat exchanger for hot water supply on the regenerator side.
The regenerator (2) flowing along the internal flow path (114) of (112)
While receiving and transmitting heat from the refrigerant vapor flowing along the surface and the external flow path (113), the triple heat exchanger for hot water supply (1
01). There, heat exchange occurs and the hot water is supplied to the hot water supply section through a hot water supply pipe in the room. The low-concentration solution discharged from the hot water supply triple heat exchanger (101) is sent to the absorber (7), absorbs the refrigerant vapor described above, and becomes a high-concentration solution.
Through (106), it flows into the triple heat exchanger (101) for hot water supply.
【００４６】上記給湯用三重熱交換器(101) に流入され
る高濃度溶液は、低濃度溶液及び給湯水と熱交換して温
度が上昇した状態でさらに再生器(2) に流入され、この
ような動作が繰り返される。すなわち、凝縮器(5) と蒸
発器(6) での流体流動はなくなり、この箇所で作動され
るべき冷却水及び冷水ポンプ等も作動させる必要がなく
なる。The high-concentration solution flowing into the hot water supply triple heat exchanger (101) further exchanges heat with the low-concentration solution and hot water and flows into the regenerator (2) in a state where the temperature is increased. Such an operation is repeated. That is, there is no fluid flow in the condenser (5) and the evaporator (6), and there is no need to operate the cooling water and the chilled water pump to be operated at this point.
【００４７】以上の説明は、本発明の第１実施態様に関
するものである。本発明の第２実施態様である改善され
た溶液熱交換器(119) を採用した場合も、上記給湯用三
重熱交換器(101) の動作と同様であって、これも又冷暖
房モードの転換によって図９乃至図１１に示したような
冷暖房及び給湯同時運転、冷暖房運転、給湯単独運転の
各々を行うことができる。The above description relates to the first embodiment of the present invention. When the improved solution heat exchanger (119) according to the second embodiment of the present invention is employed, the operation is the same as that of the above-mentioned triple heat exchanger (101) for hot water supply, and this also switches the cooling / heating mode. Accordingly, the simultaneous cooling / heating and hot water supply operation, the cooling / heating operation, and the single hot water supply operation as shown in FIGS. 9 to 11 can be performed.
【００４８】以上説明したように、本発明は、給湯用装
置を別途設置することなく、それ自体に給湯機能を持た
せたので、製品全体の小型化を達成でき、また、生産原
価及び維持費等の節減を行うことができ、更にまた、再
生器側給湯用熱交換器を利用するによって高温表面の断
熱効果により熱損失を最小化できる、等の優れた作用・
効果を享受できる。As described above, according to the present invention, since a hot water supply function is provided to itself without separately installing a hot water supply device, the size of the entire product can be reduced, and production costs and maintenance costs can be reduced. And the use of a heat exchanger for hot water supply on the regenerator side to minimize heat loss due to the heat insulation effect of the hot surface.
You can enjoy the effect.
【００４９】また、各々の運転モードが同時又は個別に
作動可能となる。特に、給湯機能が単独で必要な際に、
システム全体を動かすことなく達成でき、省エネルギー
の面で大へん好ましい。Further, each operation mode can be operated simultaneously or individually. Especially when the hot water supply function is needed alone,
This can be achieved without moving the entire system, which is very favorable in terms of energy saving.
【図１】従来の吸収式冷暖房システムのサイクル図であ
る。FIG. 1 is a cycle diagram of a conventional absorption cooling and heating system.
【図２】従来の吸収式冷暖房システムのプレート熱交換
器の構成図であり、(a) は斜視図、(b) は断面図、(c)
は分解斜視図、(d) は(c) のA 部詳細図である。FIG. 2 is a configuration diagram of a plate heat exchanger of a conventional absorption type cooling and heating system, where (a) is a perspective view, (b) is a cross-sectional view, and (c).
3 is an exploded perspective view, and (d) is a detailed view of a part A of (c).
【図３】本発明の第１熱交換手段の第１実施態様の構成
図である。FIG. 3 is a configuration diagram of a first embodiment of a first heat exchange means of the present invention.
【図４】本発明の第２熱交換手段の構成図であり、(a)
は平面図、(b) は側面図、(c)は(b) のB 部詳細図であ
る。FIG. 4 is a configuration diagram of a second heat exchange means of the present invention, and (a)
2 is a plan view, (b) is a side view, and (c) is a detailed view of a portion B of (b).
【図５】本発明のによる第１熱交換手段の第２実施態様
の構成図であり、(a) は斜視図、(b) は断面図、(c) は
分解斜視図、(d) は(c) のC 部詳細図である。FIG. 5 is a configuration diagram of a second embodiment of the first heat exchange means according to the present invention, wherein (a) is a perspective view, (b) is a cross-sectional view, (c) is an exploded perspective view, and (d) is an exploded perspective view. FIG. 4C is a detailed view of a part C of FIG.
【図６】本発明の吸収式冷暖房システムの第１実施態様
の冷暖房及び給湯の同時運転時の動作状態図である。FIG. 6 is an operation state diagram at the time of simultaneous operation of cooling and heating and hot water supply of the first embodiment of the absorption type cooling and heating system of the present invention.
【図７】本発明の吸収式冷暖房システムの第１実施態様
の冷暖房運転時の動作状態図である。FIG. 7 is an operation state diagram of the first embodiment of the absorption cooling and heating system of the present invention during the cooling and heating operation.
【図８】本発明の吸収式冷暖房システムの第１実施態様
の給湯単独運転時の動作状態図である。FIG. 8 is an operation state diagram of the first embodiment of the absorption type cooling and heating system of the present invention at the time of hot water supply alone operation.
【図９】本発明の吸収式冷暖房システムの第２実施態様
の冷暖房及び給湯の同時運転時の動作状態図である。FIG. 9 is an operation state diagram of a second embodiment of the absorption type cooling and heating system of the present invention at the time of simultaneous operation of cooling and heating and hot water supply.
【図１０】本発明の吸収式冷暖房システムの第２実施態
様の冷暖房運転時の動作状態図である。FIG. 10 is an operation state diagram of a second embodiment of the absorption cooling and heating system of the present invention during the cooling and heating operation.
【図１１】本発明の吸収式冷暖房システムの第２実施態
様の給湯単独運転時の動作状態図である。FIG. 11 is an operation state diagram of the second embodiment of the absorption cooling and heating system of the present invention at the time of hot water supply alone operation.
101 …給湯用三重熱交換器 102 、121 …高温部流体流入口 103 、122 …高温部流体流出口 104 、123 …給湯水流入口 105 、124 …給湯水流出口 106 、125 …低温部流体流入口 107 、126 …低温部流体流出口 108 …低温部流体分岐管 109 …給湯水分岐管 110 …分配板 111 …バフル板 112 …再生器側給湯用熱交換器 113 …内部流路 114 …外部流路 115 …冷媒蒸気流入管 116 …冷媒蒸気流出管 117 …給湯水流入管 118 …給湯水流出管 119 …溶液熱交換器 120 …プレート 101: triple heat exchanger for hot water supply 102, 121: high temperature section fluid inlet 103, 122: high temperature section fluid outlet 104, 123: hot water inlet 105, 124 ... hot water outlet 106, 125: low temperature section fluid inlet 107 , 126 ... low temperature part fluid outlet 108 ... low temperature part fluid branch pipe 109 ... hot water supply branch pipe 110 ... distribution plate 111 ... baffle plate 112 ... regenerator side hot water supply heat exchanger 113 ... internal flow path 114 ... external flow path 115 … Refrigerant vapor inflow pipe 116… refrigerant vapor outflow pipe 117… hot water inflow pipe 118… hot water outflow pipe 119… solution heat exchanger 120… plate
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 平10−300261（ＪＰ，Ａ) 実開 昭48−12652（ＪＰ，Ｕ) 実開 昭52−80161（ＪＰ，Ｕ) 実開 昭48−70253（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.6，ＤＢ名) F25B 15/00 301 F25B 15/00 303 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-10-300261 (JP, A) Japanese Utility Model Showa 48-12652 (JP, U) Japanese Utility Model Showa 52-80161 (JP, U) Japanese Utility Model Showa 48- 70253 (JP, U) (58) Fields investigated (Int. Cl. 6 , DB name) F25B 15/00 301 F25B 15/00 303
Claims (13)
収器で生成されて再生器に流入される低温の高濃度溶液
との間の熱交換により必要熱量を得ることができるよう
に再生器と吸収器との間に設けられる第１熱交換手段
と、 再生器から発生された高温の冷媒蒸気及び再生器の外部
発散熱により必要熱量を得ることができるように再生器
の周囲に設けられる第２熱交換手段、 とを含んで給湯機能を具えることを特徴とする装置。In an absorption type air conditioner, heat is exchanged between a high-temperature low-concentration solution generated and discharged from a regenerator and a low-temperature high-concentration solution generated in an absorber and flowing into a regenerator. A first heat exchange means provided between the regenerator and the absorber so as to obtain a required amount of heat, and obtaining a required amount of heat by a high-temperature refrigerant vapor generated from the regenerator and heat radiated outside the regenerator. And a second heat exchange means provided around the regenerator so as to be able to perform the hot water supply function.
能を奏するために六面体形又は多面体形で構成され、上
記六面体形又は多面体形の各面部には、給湯水の流入/
出口、高温部流体の流入/ 出口、及び低温部流体の流入
/ 出口が設けられることを特徴とする請求項１記載の装
置。2. The first heat exchange means is formed in a hexahedral or polyhedral shape so as to perform a hot water supply heat exchanger function.
Outlet, inflow / outlet of high temperature fluid, and inflow of low temperature fluid
2. The device according to claim 1, wherein an outlet is provided.
間を延長させるようにジグザグ形状で形成されたバフル
と、 側面部又は前面部に流入される各流体の流路を形成する
ように前後面又は両側面に形成された分岐管と、 側面部又は前面部に流入される流体を各分岐管に分岐さ
せるための分配板、 とを含むことを特徴とする請求項１又は２記載の装置。3. A baffle formed in a zigzag shape so as to extend a heat exchange time while forming a flow path of a fluid flowing into the upper part, and a first heat exchange means, A branch pipe formed on the front and rear surfaces or both side faces so as to form a flow path for each fluid to be flowed in, and a distribution plate for branching the fluid flowing into the side face or the front face into each branch pipe. Apparatus according to claim 1 or 2, comprising:
に形成される分岐管のうちの一方向側の分岐管は、熱交
換領域を大きく確保するために湾曲した形状に形成さ
れ、他方向側の分岐管は、最大限の空間利用のために前
記一方向側の分岐管の湾曲した部分に入り込んでいるよ
うな相互位置関係を有して配設されることを特徴とする
請求項３記載の装置。4. A branch pipe on one side among branch pipes formed on the front and rear surfaces or both side surfaces of the first heat exchange means is formed in a curved shape to secure a large heat exchange area, The branch pipes in the other direction are disposed in such a manner that the branch pipes in the other direction enter the curved portions of the branch pipes in the one direction for maximum space utilization. Item 3. The apparatus according to Item 3.
トが積層式に結合されその結合隙間に流体の流路が形成
されて成るプレート熱交換器を含み、 プレート所定部位には、給湯水流入/ 出口、高温部流体
流入/ 出口、低温部流体流入/ 出口が設けられることを
特徴とする請求項１記載の装置。5. The first heat exchange means includes a plate heat exchanger in which a plurality of plates are connected in a stacked manner and a fluid passage is formed in a connection gap between the plates. 2. The apparatus according to claim 1, further comprising a water inlet / outlet, a hot section fluid inflow / outlet, and a cold section fluid inflow / outlet.
対応した流路が連結されることを特徴とする請求項５記
載の装置。6. The apparatus according to claim 5, wherein a flow path corresponding to each fluid is connected to the inflow / outlet of each fluid.
流路には、低温部流体又は給湯水が流動するように構成
したことを特徴とする請求項６記載の装置。7. The apparatus according to claim 6, wherein the low-temperature part fluid or the hot water flows in both side surfaces of the flow path in which the high-temperature part fluid flows.
体が流れる内部流路及び外部流路を含み、再生器の回り
にコイル状に設けられることを特徴とする請求項１記載
の装置。8. The apparatus according to claim 1, wherein the second heat exchange means includes an internal flow path and an external flow path through which different fluids flow, and is provided in a coil shape around the regenerator.
を流動する流体間の熱交換面積を大きくするように鋸歯
形状で互いにかみあっていることを特徴とする請求項８
記載の装置。9. The internal flow path and the external flow path are meshed with each other in a sawtooth shape so as to increase a heat exchange area between fluids flowing in the internal flow path and the external flow path.
The described device.
された冷媒蒸気が流れ、その後に該冷媒蒸気が吸収器に
流入し、 第１熱交換手段の高温部流体流路には、再生器から発生
された低濃度溶液が流れ、 低温部流体流路には、精留器から流出された高濃度溶液
が流れ、 第２熱交換手段の内部流路と第１熱交換手段の給湯水流
路には、給湯水が流れないことを特徴とする請求項１記
載の装置。10. In the cooling / heating operation mode, the refrigerant vapor flowing out of the refrigerant heat exchanger flows through the external flow path of the second heat exchange means, and then the refrigerant vapor flows into the absorber, The low-concentration solution generated from the regenerator flows through the high-temperature section fluid flow path of the first heat exchange means, the high-concentration solution discharged from the rectifier flows through the low-temperature section fluid flow path, The apparatus according to claim 1, wherein hot water does not flow through the internal flow path of the exchange means and the hot water flow path of the first heat exchange means.
は、 第２熱交換手段の内部流路には、給湯水が流れ、 第１熱交換手段の高温部流体流路には、再生器から発生
された低濃度溶液が流れ、 低温部流体流路には、精留器から流出された高濃度溶液
が流れ、 給湯水流路には、第２熱交換手段から流出された給湯水
が流れることを特徴とする請求項１記載の装置。11. In an operation mode of cooling and heating and hot water supply, hot water flows in an internal flow path of the second heat exchange means, and a high temperature part fluid flow path of the first heat exchange means from a regenerator. The generated low-concentration solution flows, the high-concentration solution flowing out of the rectifier flows in the low-temperature section fluid flow path, and the hot water flowing out of the second heat exchange means flows in the hot water flow path. The device according to claim 1, characterized in that:
その後に該冷媒蒸気が膨張弁を経て吸収器に流れ、 第１熱交換手段の高温部流体流路には、再生器から発生
された低濃度溶液が流れ、 低温部流体流路には、精留器から流出された高濃度溶液
が流れ、 給湯水流路には、給湯水が流れることを特徴とする請求
項１記載の装置。12. In the hot water supply operation mode, hot water flows in the internal flow path of the second heat exchange means, and refrigerant vapor flowing out of the regenerator flows in the external flow path.
Thereafter, the refrigerant vapor flows through the expansion valve to the absorber, the low-concentration solution generated from the regenerator flows through the high-temperature section fluid flow path of the first heat exchange means, and the low-temperature section fluid flow path passes through the low-temperature section fluid flow path. The apparatus according to claim 1, wherein the high-concentration solution flowing out of the retainer flows, and hot water flows in the hot water flow path.
じ得る高圧状態を解除するための外部解放用のバルブが
設けられることを特徴とする請求項１０記載の装置。13. The apparatus according to claim 10, wherein the hot water flow path is provided with an external release valve for releasing a high pressure state that may be caused by overheating.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1019970031133A KR100213781B1 (en) | 1997-07-04 | 1997-07-04 | Absorption type cooler system with water supply function |
| KR1019980000616A KR100315627B1 (en) | 1998-01-12 | 1998-01-12 | Absorption heating and cooling system having quick boiling function |
| KR31133/1997 | 1998-01-12 | ||
| KR616/1998 | 1998-01-12 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11182964A JPH11182964A (en) | 1999-07-06 |
| JP2951649B2 true JP2951649B2 (en) | 1999-09-20 |
Family
ID=26632910
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10187380A Expired - Fee Related JP2951649B2 (en) | 1997-07-04 | 1998-07-02 | Absorption air conditioner |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2951649B2 (en) |
| CN (1) | CN1168927C (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107543428B (en) * | 2017-09-07 | 2019-04-16 | 西安交通大学 | A kind of compact heat exchanger for Nuclear Power Industry |
-
1998
- 1998-07-02 JP JP10187380A patent/JP2951649B2/en not_active Expired - Fee Related
- 1998-07-03 CN CNB981025897A patent/CN1168927C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1168927C (en) | 2004-09-29 |
| JPH11182964A (en) | 1999-07-06 |
| CN1204752A (en) | 1999-01-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP3088830B1 (en) | Heat-pump-type outdoor device with plate heat exchanger | |
| KR102639580B1 (en) | Refrigeration system | |
| JP3438000B2 (en) | Air conditioner | |
| JPH0814702A (en) | Laminate type evaporator | |
| JP2002022374A (en) | Plate type heat exchanger and freezing air conditioning apparatus | |
| JP2951649B2 (en) | Absorption air conditioner | |
| JP3658677B2 (en) | Plate heat exchanger and refrigeration system | |
| JP2007514127A (en) | High-efficiency turbulence generator for absorption refrigerating / heating multistage regenerator | |
| KR100315627B1 (en) | Absorption heating and cooling system having quick boiling function | |
| JPH10300260A (en) | Absorption water cooler-heater | |
| JPH05264115A (en) | Absorption heat pump device | |
| JP2023512160A (en) | Heat exchanger, cooling system and method | |
| KR100213780B1 (en) | Water supply system of absortion type cooler | |
| JPH1082594A (en) | Plate type heat exchanger and absorption cooling-heating apparatus using the same | |
| JP2001133172A (en) | Heat exchanger and refrigeration air conditioner | |
| JP3485731B2 (en) | Absorption chiller / heater | |
| JP2002022309A (en) | Absorption type refrigerating machine | |
| KR100213781B1 (en) | Absorption type cooler system with water supply function | |
| KR100334933B1 (en) | Absorber of plate heat exchanger type in Absorption heating and cooling system | |
| JPH08271170A (en) | Plate-shaped heat exchanger | |
| JP2513324Y2 (en) | Heat exchanger | |
| CN117847829A (en) | Heat pump unit with plate-sleeve type condenser | |
| JP2559409B2 (en) | Refrigeration equipment | |
| KR20220154239A (en) | Liquid supercooling using phase-change composite thermal energy storage and phase-change composite thermal energy storage module for this | |
| JPH0354377Y2 (en) |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 19990608 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20070709 Year of fee payment: 8 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080709 Year of fee payment: 9 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080709 Year of fee payment: 9 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090709 Year of fee payment: 10 |
|
| LAPS | Cancellation because of no payment of annual fees |