JP3393398B2 - Absorption type cold heat generator - Google Patents

Absorption type cold heat generator

Info

Publication number
JP3393398B2
JP3393398B2 JP10081896A JP10081896A JP3393398B2 JP 3393398 B2 JP3393398 B2 JP 3393398B2 JP 10081896 A JP10081896 A JP 10081896A JP 10081896 A JP10081896 A JP 10081896A JP 3393398 B2 JP3393398 B2 JP 3393398B2
Authority
JP
Japan
Prior art keywords
refrigerant
evaporator
pressure
temperature
cold heat
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
Application number
JP10081896A
Other languages
Japanese (ja)
Other versions
JPH09287857A (en
Inventor
昇 小林
修一 山口
Original Assignee
大阪瓦斯株式会社
矢崎総業株式会社
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 大阪瓦斯株式会社, 矢崎総業株式会社 filed Critical 大阪瓦斯株式会社
Priority to JP10081896A priority Critical patent/JP3393398B2/en
Publication of JPH09287857A publication Critical patent/JPH09287857A/en
Application granted granted Critical
Publication of JP3393398B2 publication Critical patent/JP3393398B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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Classifications

    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02ATECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00Adapting or protecting infrastructure or their operation
    • Y02A30/27Relating to heating, ventilation or air conditioning [HVAC] technologies
    • YGENERAL 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
    • Y02TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02BCLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/62Absorption based systems

Description

【発明の詳細な説明】Detailed Description of the Invention

【0001】[0001]

【発明の属する技術分野】本発明は、吸収式冷熱発生装
置に係り、特に相変化をする流体を二次冷媒として用い
る蒸発器を有する吸収式冷熱発生装置に関するものであ
る。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an absorption-type cold heat generating device, and more particularly to an absorption-type cold heat generating device having an evaporator that uses a phase-changing fluid as a secondary refrigerant.

【0002】[0002]

【従来の技術】従来、吸収式冷熱発生装置の蒸発器蒸発
コイルの二次冷媒として顕熱を利用する水冷媒を用いる
ものは、何らかの原因により暖房の際に制御がきかなく
なっても、蒸発器蒸発コイル内が異常高圧になる恐れは
少なかったので蒸発器における自動復帰の異常圧監視制
御手段は設けられていなかった。
2. Description of the Related Art Conventionally, a device using a water refrigerant that utilizes sensible heat as a secondary refrigerant of an evaporator evaporation coil of an absorption type cold heat generator is an evaporator even if control cannot be performed during heating for some reason. Since there is little possibility that the inside of the evaporation coil will have an abnormally high pressure, no abnormal pressure monitoring control means for automatic recovery is provided in the evaporator.

【0003】[0003]

【発明が解決しようとする課題】しかしながら、上記水
冷媒を用いた従来の吸収式冷熱発生装置に対して、その
ままの構造で二次冷媒としてR134aのような二相流
体を使用すると、例えば暖房運転の際に二次冷媒を送る
冷媒ポンプの故障や急激な低負荷への負荷変動があった
場合、吸収式冷熱発生装置における蒸発器への二次液冷
媒が搬送されず、蒸発器で空焚となり、二次冷媒の圧力
が蒸発器の最大使用圧力を越えてしまい破損に至る恐れ
があった。
However, if a two-phase fluid such as R134a is used as the secondary refrigerant in the same structure as the conventional absorption type cold heat generator using the above water refrigerant, for example, heating operation is performed. In the event of a failure of the refrigerant pump that sends the secondary refrigerant or a sudden load change to a low load, the secondary liquid refrigerant is not transferred to the evaporator in the absorption cold heat generator, and the evaporator is empty. Therefore, the pressure of the secondary refrigerant exceeds the maximum working pressure of the evaporator, which may lead to damage.

【0004】つまり、燃焼制御は、出口ガス管温度(二
次冷媒の発生装置出口)で制御されているため、急激な
負荷変動のような場合、応答遅れが生じ、負荷がない状
態で過熱され、これにより蒸発器内圧力が上昇し、蒸発
器コイル強度限界圧力(或いは最大使用圧力)を越える
恐れがあった。
In other words, since the combustion control is controlled by the outlet gas pipe temperature (the outlet of the secondary refrigerant generator), in the case of a sudden load change, a response delay occurs and overheating occurs in the absence of a load. As a result, the internal pressure of the evaporator may rise and exceed the evaporator coil strength limit pressure (or maximum working pressure).

【0005】本発明の目的は、上記課題を解決し、相変
化をする二相流体を二次冷媒として用いる蒸発器を有す
る吸収式冷熱発生装置において、加熱運転の際に蒸発器
の二次冷媒の異常高圧による破損を未然に防止する吸収
式冷熱発生装置を提供することである。
An object of the present invention is to solve the above problems and to provide an absorption type cold heat generator having an evaporator which uses a two-phase fluid that undergoes phase change as a secondary refrigerant, and the secondary refrigerant of the evaporator during heating operation. It is an object of the present invention to provide an absorption-type cold heat generator that prevents damage due to abnormally high pressure.

【0006】[0006]

【課題を解決するための手段】上記目的を達成するため
本発明は、再生器、凝縮器、蒸発器、吸収器及び溶液循
環ポンプ等を接続して冷媒及び吸収溶液の循環回路を形
成した吸収式冷熱発生装置において、前記蒸発器は二相
流体の二次冷媒を内側に流す蒸発コイルを有すると共
に、前記蒸発器の二次冷媒による加熱運転の際に、前記
蒸発器の二次冷媒の温度又は圧力に基づいて前記吸収式
冷熱発生装置の加熱運転を制御し、前記蒸発器の二次冷
媒の圧力の異常高圧による前記蒸発器の破損を防止する
圧力制御手段を備えたものである。加熱運転の際に二次
冷媒の温度又は圧力に基づいて吸収式冷熱発生装置の加
熱運転を制御し、蒸発器二次冷媒の異常高圧による蒸発
器の破損を防止する圧力制御手段を備えたものは、蒸発
器の蒸発コイルの二次冷媒の温度又は圧力という比較的
捕らえ易い状態量によって二次冷媒の圧力を捕らえるこ
とが出来、この状態量を監視することにより二次冷媒の
異常高圧による蒸発器の破損を確実に未然に防止するこ
とが出来る。二次冷媒の温度と圧力の間には相関関係が
あるので、少なくともどちらかを捕らえる。
In order to achieve the above object, the present invention is an absorption system in which a regenerator, a condenser, an evaporator, an absorber, a solution circulation pump and the like are connected to form a circulation circuit for a refrigerant and an absorption solution. In the type cold heat generating device, the evaporator has an evaporation coil that causes a secondary refrigerant of a two-phase fluid to flow inward, and the temperature of the secondary refrigerant of the evaporator during the heating operation by the secondary refrigerant of the evaporator. Alternatively, pressure control means is provided for controlling the heating operation of the absorption cold heat generator based on the pressure and preventing damage to the evaporator due to abnormally high pressure of the secondary refrigerant in the evaporator. Controlling the heating operation of the absorption type cold heat generator based on the temperature or pressure of the secondary refrigerant during heating operation, and equipped with pressure control means for preventing damage to the evaporator due to abnormally high pressure of the evaporator secondary refrigerant Can capture the pressure of the secondary refrigerant by the relatively easy-to-understand state quantity such as the temperature or pressure of the secondary refrigerant in the evaporator coil of the evaporator, and by monitoring this state quantity, evaporation due to abnormally high pressure of the secondary refrigerant. It is possible to reliably prevent damage to the vessel. Since there is a correlation between the temperature and the pressure of the secondary refrigerant, at least one of them is captured.

【0007】更に、上記吸収式冷熱発生装置において、
前記圧力制御手段は、前記蒸発器の二次冷媒の温度又は
圧力を検知する温度又は圧力センサを有し、該温度又は
圧力センサが検知した温度又は圧力が、予め設定された
上限値に達した時に前記吸収式冷熱発生装置の加熱運転
を停止させるものである。圧力制御手段が、温度又は圧
力センサが検知した温度又は圧力と予め設定された上限
値とを比較し、上限値に達した時に吸収式冷熱発生装置
の加熱運転を停止させるものは、上記吸収式冷熱発生装
置の作用に加え、比較的単純な制御手段であり確実に制
御する。
Further, in the absorption type cold heat generating device,
The pressure control means has a temperature or pressure sensor that detects the temperature or pressure of the secondary refrigerant of the evaporator, and the temperature or pressure detected by the temperature or pressure sensor has reached a preset upper limit value. At this time, the heating operation of the absorption type cold heat generator is stopped. The pressure control means compares the temperature or pressure detected by the temperature or pressure sensor with a preset upper limit value, and when the upper limit value is reached, the heating operation of the absorption type cold heat generator is stopped is the above absorption type. In addition to the function of the cold heat generation device, it is a relatively simple control means and can be reliably controlled.

【0008】更に、上記いずれかの吸収式冷熱発生装置
において、前記圧力制御手段は、前記温度又は圧力セン
サが検知した温度又は圧力が、予め設定された下限値に
達した時に前記吸収式冷熱発生装置の加熱運転を自動復
帰させるものである。圧力制御手段が、温度又は圧力セ
ンサが検知した温度又は圧力と予め設定された下限値と
を比較し、下限値に達した時に吸収式冷熱発生装置の加
熱運転を自動復帰させるものは、上記いずれかの吸収式
冷熱発生装置の作用に加え、二次冷媒の下限温度又は圧
力により吸収式冷熱発生装置の負荷に対する加熱を一定
温度以上に維持する。
Further, in any of the absorption type cold heat generating device, the pressure control means generates the absorption type cold heat when the temperature or pressure detected by the temperature or pressure sensor reaches a preset lower limit value. The heating operation of the device is automatically returned. The pressure control means compares the temperature or pressure detected by the temperature or the pressure sensor with a preset lower limit value, and when the lower limit value is reached, the heating operation of the absorption chiller generator is automatically restored. In addition to the action of the absorption type cold heat generating device, heating to the load of the absorption type cold heat generating device is maintained at a certain temperature or more by the lower limit temperature or pressure of the secondary refrigerant.

【0009】更に、上記いずれかの吸収式冷熱発生装置
において、前記圧力制御手段は、吸収溶液を加熱して更
に冷媒蒸気を発生させる高温再生器及び該高温再生器で
生成した中間濃溶液を加熱して冷媒蒸気を発生させる低
温再生器を有する二重効用の吸収式冷熱発生装置に設け
られたものである。圧力制御手段が高温再生器及び低温
再生器を有する二重効用の吸収式冷熱発生装置に設けら
れたものは、上記いずれかの吸収式冷熱発生装置の作用
に加え、二重効用の吸収式冷熱発生装置の加熱能力を確
実に維持する。
Further, in any one of the absorption-type cold heat generators described above, the pressure control means heats the high-temperature regenerator for heating the absorption solution to further generate the refrigerant vapor and the intermediate concentrated solution generated by the high-temperature regenerator. It is provided in a double-effect absorption cold heat generator having a low temperature regenerator for generating a refrigerant vapor. What the pressure control means is provided in a double-effect absorption cold heat generator having a high-temperature regenerator and a low-temperature regenerator is a double-effect absorption cold heat generator in addition to the function of any one of the absorption cold heat generators described above. Ensure that the heating capacity of the generator is maintained.

【0010】そして、上記いずれかの吸収式冷熱発生装
置において、前記圧力制御手段は、前記二次冷媒が室内
に設けられた室内機の冷暖房用熱交換器に供給され、前
記蒸発器の蒸発コイルが前記室内機の冷暖房用熱交換器
の上方に配置され、暖房運転の際には前記二次冷媒が冷
媒ポンプによって前記室内機の冷暖房用熱交換器から前
記蒸発器の蒸発コイルに送られるものに設けられたもの
である。蒸発器の二次冷媒が室内機の冷暖房用熱交換器
に供給され、蒸発器の蒸発コイルが室内機の冷暖房用熱
交換器の上方に配置され、暖房運転の際には二次冷媒が
冷媒ポンプによって室内機の冷暖房用熱交換器から蒸発
器の蒸発コイルに送られるものに設けられた圧力制御手
段は、空調用吸収式冷熱発生装置の暖房運転において、
上記いずれかの吸収式冷熱発生装置の作用を有する。
In any one of the absorption-type cold heat generators described above, the pressure control means supplies the secondary refrigerant to a heat exchanger for cooling and heating of an indoor unit provided indoors, and an evaporation coil of the evaporator. Is disposed above the cooling / heating heat exchanger of the indoor unit, and during the heating operation, the secondary refrigerant is sent from the cooling / heating heat exchanger of the indoor unit to the evaporation coil of the evaporator by a refrigerant pump. It was installed in. The secondary refrigerant of the evaporator is supplied to the cooling / heating heat exchanger of the indoor unit, the evaporation coil of the evaporator is arranged above the cooling / heating heat exchanger of the indoor unit, and the secondary refrigerant is the refrigerant during the heating operation. In the heating operation of the absorption type cold heat generator for air conditioning, the pressure control means provided in the pump that is sent from the heat exchanger for heating and cooling of the indoor unit to the evaporation coil of the evaporator is
It has the function of any one of the absorption-type cold heat generating devices described above.

【0011】[0011]

【発明の実施の形態】図1は、本発明に係る吸収式冷熱
発生装置の一実施の形態を示す系統図である。本実施の
形態の吸収式冷熱発生装置Pは、空調用に利用される二
重効用のもので、冷却水管40、41で接続され冷却水
を冷却するクーリングタワー42と、前記冷却水管41
に介装され冷却水をクーリングタワー42から循環させ
る冷却水循環ポンプ13とを含む。
1 is a system diagram showing an embodiment of an absorption type cold heat generator according to the present invention. The absorption type cold heat generating device P of the present embodiment is a double-effect type used for air conditioning, and has a cooling tower 42 connected by cooling water pipes 40 and 41 to cool cooling water, and the cooling water pipe 41.
And a cooling water circulation pump 13 for circulating the cooling water from the cooling tower 42.

【0012】更に、吸収式冷熱発生装置Pは、燃料を燃
焼させその熱で吸収溶液である希溶液を加熱する高温再
生器1と、この高温再生器1で加熱された希溶液から冷
媒蒸気と中間濃溶液を分離する分離器2と、分離された
冷媒蒸気を熱源として前記中間濃溶液を加熱して更に冷
媒蒸気を発生させる低温再生器3と、該低温再生器3を
通過した冷媒蒸気及び該低温再生器3で発生した冷媒蒸
気を冷却して凝縮液化させ液冷媒を生成する凝縮器4
と、該凝縮器4で生成された液冷媒を内装した冷媒分配
器6Bから同じく内装した蒸発コイル6A上に滴下蒸発
させ該蒸発コイル6A中の二次冷媒を冷却する蒸発器6
と、該蒸発器6で蒸発した冷媒蒸気を濃溶液に吸収させ
希溶液を生成する吸収器5と、を備えている。
Further, the absorption type cold heat generator P has a high temperature regenerator 1 for burning a fuel and heating the diluted solution which is an absorbing solution by the heat, and a refrigerant vapor from the diluted solution heated by the high temperature regenerator 1. A separator 2 that separates the intermediate concentrated solution, a low-temperature regenerator 3 that heats the intermediate concentrated solution using the separated refrigerant vapor as a heat source to generate further refrigerant vapor, and a refrigerant vapor that has passed through the low temperature regenerator 3. A condenser 4 that cools the refrigerant vapor generated in the low temperature regenerator 3 to condense and liquefy it to generate a liquid refrigerant.
And an evaporator 6 for cooling the secondary refrigerant in the evaporation coil 6A by causing the liquid refrigerant generated in the condenser 4 to drop and evaporate from the refrigerant distributor 6B in which the liquid refrigerant is installed onto the evaporation coil 6A which is also installed.
And an absorber 5 that absorbs the refrigerant vapor evaporated in the evaporator 6 into a concentrated solution to produce a dilute solution.

【0013】更に、希溶液を加圧し低温溶液熱交換器
8、高温溶液熱交換器7の被加熱流体側を経て前記高温
再生器1に送りこむ溶液循環ポンプ9と、前記分離器2
の底部と前記蒸発器6の底部を冷暖切換弁10を介して
連通する管路10Aと、前記低温溶液熱交換器8の加熱
流体出側を前記吸収器5の上部に接続する濃溶液管8A
と、該濃溶液管8Aと前記吸収器5の下部を溶液バイパ
ス弁22を介して接続する管路22Aと、該濃溶液管8
Aと前記蒸発器5に内装された冷媒分配器6Bを凍結防
止弁12を介して連通する管路12Aと、前記冷媒分配
器6Bに装着され該冷媒分配器6B内の冷媒の温度を検
知する蒸発器温度センサ14と、前記凝縮器4から前記
冷媒分配器6Bに液冷媒を導く水冷媒管11Bと、該水
冷媒管11Bに並列に接続され水冷媒比例弁11を介装
する管路11Aと、を備える。
Further, the solution circulating pump 9 for pressurizing the dilute solution and sending it to the high temperature regenerator 1 through the fluid to be heated side of the low temperature solution heat exchanger 8 and the high temperature solution heat exchanger 7, and the separator 2.
10A for communicating the bottom of the evaporator 6 with the bottom of the evaporator 6 via a heating / cooling switching valve 10, and a concentrated solution pipe 8A for connecting the heating fluid outlet of the low temperature solution heat exchanger 8 to the upper part of the absorber 5.
A pipe line 22A for connecting the concentrated solution pipe 8A and the lower portion of the absorber 5 via a solution bypass valve 22, and the concentrated solution pipe 8
Detecting the temperature of the refrigerant inside the refrigerant distributor 6B, which is mounted on the refrigerant distributor 6B and a conduit 12A that connects A and the refrigerant distributor 6B installed in the evaporator 5 via an antifreezing valve 12 An evaporator temperature sensor 14, a water refrigerant pipe 11B for guiding a liquid refrigerant from the condenser 4 to the refrigerant distributor 6B, and a pipe line 11A connected in parallel with the water refrigerant pipe 11B and having a water refrigerant proportional valve 11 interposed therebetween. And

【0014】更に、分離器2で分離された中間濃溶液が
前記高温溶液熱交換器7の加熱流体側を経て前記低温再
生器3に導かれ、低温再生器3で冷媒を蒸発させて濃溶
液となった後、前記低温溶液熱交換器8の加熱流体側を
経て前記濃溶液管8Aに導かれるように管路が構成され
ている。前記吸収器5及び凝縮器4にはそれぞれ冷却水
コイルが内装され、吸収器5の冷却水コイルの出口は前
記凝縮器4の冷却水コイルの入口に接続されていて、吸
収器5の冷却水コイルの入口は前記冷却水管41に、凝
縮器4の冷却水コイルの出口は前記冷却水管40に、そ
れぞれ接続されている。
Further, the intermediate concentrated solution separated by the separator 2 is introduced into the low temperature regenerator 3 through the heating fluid side of the high temperature solution heat exchanger 7, and the refrigerant is evaporated in the low temperature regenerator 3 to form a concentrated solution. After that, the pipe line is configured to be guided to the concentrated solution pipe 8A through the heating fluid side of the low temperature solution heat exchanger 8. A cooling water coil is installed in each of the absorber 5 and the condenser 4, and an outlet of the cooling water coil of the absorber 5 is connected to an inlet of the cooling water coil of the condenser 4 to cool the cooling water of the absorber 5. The inlet of the coil is connected to the cooling water pipe 41, and the outlet of the cooling water coil of the condenser 4 is connected to the cooling water pipe 40.

【0015】上記吸収式冷熱発生装置Pにおいて、冷暖
切換弁10は、冷房と暖房の切り替えを行なうもので、
冷房時は閉、暖房時は開とされる。水冷媒比例弁11
は、蒸発器の温度(蒸発器温度センサ14の出力)を入
力として開度制御され、溶液濃度の調整を行なう弁であ
る。凍結防止弁12は、蒸発温度が低下して1℃になれ
ば開いて濃溶液を冷媒分配器6Bに流入させ、水である
水冷媒の凍結を防ぐ弁である。溶液バイパス弁22は、
冷房立上り時及び低負荷運転時に、蒸発器温度が低下し
たとき、凍結防止弁が作動する前に濃溶液を吸収器5の
下部にバイパスして吸収器5の吸収能力を低下させ、蒸
発器のそれ以上の温度低下を防ぐためのオン−オフ制御
弁である。
In the absorption type cold heat generator P, the cooling / heating switching valve 10 switches between cooling and heating.
It is closed during cooling and open during heating. Water-refrigerant proportional valve 11
Is a valve whose opening is controlled by inputting the temperature of the evaporator (output of the evaporator temperature sensor 14) to adjust the solution concentration. The antifreezing valve 12 is a valve that opens when the evaporation temperature decreases to 1 ° C. and causes the concentrated solution to flow into the refrigerant distributor 6B to prevent freezing of the water refrigerant that is water. The solution bypass valve 22 is
When the evaporator temperature decreases at the time of cooling start-up and low load operation, the concentrated solution is bypassed to the lower part of the absorber 5 before the antifreezing valve is activated to reduce the absorption capacity of the absorber 5, It is an on-off control valve for preventing further temperature drop.

【0016】更に、吸収式冷熱発生装置Pの外部には、
冷媒液管50及び冷媒蒸気管51で接続され空調対象空
間に配置されて該空間の空気との熱交換を行なう空調用
室内機52、53と、前記冷媒液管50に介装され該冷
媒液管50に充填された二次冷媒を吸収式冷熱発生装置
Pと前記空調用室内機52、53の間で循環させる冷媒
ポンプ57と、を備えている。冷媒液管50、冷媒蒸気
管51の一端側は、蒸発コイル6Aの下端、上端にそれ
ぞれ接続され、冷媒液管50、冷媒蒸気管51の他端側
は、蒸発コイル6Aよりも下方に配置された室内機の数
だけ(本実施の形態においては2基)分岐されており、
室内機52、53にそれぞれ内装された冷暖房用熱交換
器52A、53Aの上端及び下端入口の膨張弁54、5
5にそれぞれ接続されている。冷媒液管50の蒸発コイ
ル6Aとの接続部近傍には、先に述べた二次冷媒の温度
を検出して電気信号としてコントローラ59に出力する
冷媒液温度センサ21が装着されている。
Further, outside the absorption type cold heat generator P,
Air-conditioning indoor units 52 and 53 connected by a refrigerant liquid pipe 50 and a refrigerant vapor pipe 51 and arranged in an air-conditioned space to exchange heat with the air in the space, and the refrigerant liquid interposed between the refrigerant liquid pipe 50 and the refrigerant liquid. A refrigerant pump 57 that circulates the secondary refrigerant filled in the pipe 50 between the absorption-type cold heat generating device P and the air conditioning indoor units 52 and 53 is provided. One ends of the refrigerant liquid pipe 50 and the refrigerant vapor pipe 51 are connected to the lower end and the upper end of the evaporation coil 6A, respectively, and the other ends of the refrigerant liquid pipe 50 and the refrigerant vapor pipe 51 are arranged below the evaporation coil 6A. The number of indoor units (two in the present embodiment) is branched,
Expansion valves 54, 5 at the upper and lower inlets of the cooling / heating heat exchangers 52A, 53A respectively installed in the indoor units 52, 53
5 are connected respectively. In the vicinity of the connection portion of the refrigerant liquid pipe 50 with the evaporation coil 6A, the refrigerant liquid temperature sensor 21 that detects the temperature of the secondary refrigerant and outputs it as an electric signal to the controller 59 is mounted.

【0017】冷媒液管50は、途中に室内機52、53
よりも低い位置に配置された部分があり、そこに冷媒液
を加圧して蒸発コイル6Aに送りこむ冷媒ポンプ57が
装着されている。冷媒ポンプ57の吐出側には逆止弁5
8が設けられ、この逆止弁58の出口側と冷媒ポンプ5
7の吸い込み側は、冷暖切換弁56を介して接続されて
いる。相変化する二次冷媒として、HFC−134aが
冷媒液管に充填されている。蒸発コイル6Aには二次冷
媒の温度又は圧力を検知する温度センサ又は圧力センサ
16が装着されている。
The refrigerant liquid pipe 50 is connected to the indoor units 52 and 53 on the way.
There is a portion arranged at a lower position than the above, and a refrigerant pump 57 that pressurizes the refrigerant liquid and sends it to the evaporation coil 6A is attached thereto. The check valve 5 is provided on the discharge side of the refrigerant pump 57.
8 is provided, and the outlet side of the check valve 58 and the refrigerant pump 5 are provided.
The suction side of 7 is connected via a cooling / heating switching valve 56. HFC-134a is filled in the refrigerant liquid pipe as a secondary refrigerant that undergoes a phase change. A temperature sensor or pressure sensor 16 that detects the temperature or pressure of the secondary refrigerant is attached to the evaporation coil 6A.

【0018】この吸収式冷熱発生装置Pは、冷房運転時
に機内の水冷媒が凍結して晶析運転されること、低負荷
時に二次冷媒回路が凍結破損すること、又、暖房運転時
には、蒸発器蒸発コイル内の圧力が異常に上昇し蒸発器
を破損させること、が最もダメージが大きい。これらの
状況になるのを防ぐために二次冷媒出口温度及び蒸発器
内各種温度に基づく保護制御がなされている。冷房運
転、暖房運転どちらの際にも、吸収式冷熱発生装置Pと
室内機52、53との間で循環して熱を搬送する二次冷
媒に相変化を行なわせることにより、単位流量あたりの
熱搬送量を増加させている。
In this absorption type cold heat generator P, the water refrigerant in the machine freezes during the cooling operation to perform the crystallization operation, the secondary refrigerant circuit freezes and breaks when the load is low, and the evaporation occurs during the heating operation. The damage is greatest when the pressure inside the evaporator coil rises abnormally and damages the evaporator. In order to prevent these situations, protection control is performed based on the secondary refrigerant outlet temperature and various temperatures inside the evaporator. In both the cooling operation and the heating operation, the secondary refrigerant that circulates between the absorption-type cold heat generating device P and the indoor units 52 and 53 to transfer heat causes a phase change, so that Increasing the heat transfer rate.

【0019】次に、吸収式冷熱発生装置Pの冷房時の動
作は次の通りである。冷房時には、冷暖切換弁56は開
かれている。冷媒蒸気(HFC−134a)は、蒸発器
6の蒸発コイルで冷却凝縮されて冷媒液となり、重力に
より、冷媒液管50を下方に流れ、膨張弁54、55を
経て各室内機52、53の熱交換器52A、53Aに流
入する。熱交換器52A、53Aに流入した冷媒液は、
空調対象空間の空気の熱を奪って蒸発し、冷媒蒸気とな
って冷媒蒸気管51を経て上昇し蒸発器6の蒸発コイル
6Aに流入する。室外機である吸収式冷熱発生装置Pは
冷房モードで運転されているから、蒸発器の蒸発コイル
6Aは、その表面に滴下される水冷媒の蒸発により冷却
され、蒸発コイル6Aに流入してきた冷媒蒸気(HFC
−134a)は、凝縮液化する。この凝縮液化により、
蒸発コイル6A内部の圧力が低下し、室内機の熱交換器
52A、53Aで蒸発した冷媒蒸気は蒸発器6に吸引さ
れる。蒸発コイル6A内部で凝縮液化した冷媒液は重力
で室内機52、53に流入するから、冷房時の冷媒(H
FC−134a)は、自然循環し、ポンプによる冷媒の
駆動を行なう必要がない。
Next, the operation of the absorption-type cold heat generator P during cooling is as follows. The cooling / heating switching valve 56 is opened during cooling. The refrigerant vapor (HFC-134a) is cooled and condensed in the evaporation coil of the evaporator 6 to become a refrigerant liquid, flows downward in the refrigerant liquid pipe 50 due to gravity, and flows through the expansion valves 54 and 55 into the indoor units 52 and 53. It flows into the heat exchangers 52A and 53A. The refrigerant liquid flowing into the heat exchangers 52A and 53A is
The heat of the air in the air-conditioned space is taken to evaporate and become a refrigerant vapor, which rises via the refrigerant vapor pipe 51 and flows into the evaporation coil 6A of the evaporator 6. Since the absorption-type cold heat generator P, which is an outdoor unit, is operated in the cooling mode, the evaporator coil 6A of the evaporator is cooled by the evaporation of the water refrigerant dropped on the surface of the evaporator coil 6A and flows into the evaporator coil 6A. Steam (HFC
-134a) is condensed and liquefied. By this condensation liquefaction,
The pressure inside the evaporation coil 6A decreases, and the refrigerant vapor evaporated in the heat exchangers 52A and 53A of the indoor unit is sucked into the evaporator 6. The refrigerant liquid condensed and liquefied inside the evaporation coil 6A flows into the indoor units 52 and 53 by gravity, so that the refrigerant (H
FC-134a) circulates naturally and it is not necessary to drive the refrigerant by a pump.

【0020】冷房運転が開始されると、先に述べたよう
に、蒸発コイル6A内部の圧力が低下し、冷媒蒸気管5
1内の飽和冷媒蒸気が圧力差により蒸発コイル6A内に
流入する。蒸発コイル6A内で凝縮して生成された冷媒
液は、冷媒液管50内を自重で流下し、冷媒液のヘッド
(液柱)が上昇してくる。先に述べた冷媒の自然循環が
成立するためには、(冷媒の液ヘッド−冷媒ガスヘッ
ド)が冷媒循環経路の全圧力損失以上であればよい。
When the cooling operation is started, as described above, the pressure inside the evaporation coil 6A decreases, and the refrigerant vapor pipe 5
The saturated refrigerant vapor in 1 flows into the evaporation coil 6A due to the pressure difference. The refrigerant liquid condensed and generated in the evaporation coil 6A flows down in the refrigerant liquid pipe 50 by its own weight, and the head (liquid column) of the refrigerant liquid rises. In order for the above-mentioned natural circulation of the refrigerant to be established, it is sufficient that (refrigerant liquid head-refrigerant gas head) is not less than the total pressure loss of the refrigerant circulation path.

【0021】暖房運転時には、冷暖切換弁56は閉じら
れ、リモコン61によりコントローラ59を通して運転
を指示される。それを受けて吸収式冷熱発生装置Pは、
暖房モードで運転開始し、高温再生器1で燃料が燃焼さ
れ、希溶液が加熱されて分離器2に送られ、蒸発器6に
は分離器2で分離された高温の希溶液が管路10A及び
冷暖切替弁10を介して導かれ、蒸発コイル6Aはこの
熱により加熱される。蒸発コイル6Aの外で水冷媒が温
められ、一方、二次冷媒のHFC−R134aは、蒸発
コイル6A内でガス化されて冷媒蒸気となり、冷媒蒸気
管51を通って室内機52、53の冷暖房用熱交換器5
2A、53Aに流入する。冷暖房用熱交換器52A、5
3Aに流入した冷媒蒸気は、空調対象空間の空気に保有
熱を与えて凝縮液化し、冷媒液となって冷媒液管50を
下方に流れて重力差により低い位置に設置している冷媒
ポンプ57手前のレシーバタンク62に入る。更に、冷
媒液は冷媒ポンプ57で加圧され、蒸発器の蒸発コイル
6Aに流入して上記のサイクルを繰り返す。
During heating operation, the cooling / heating switching valve 56 is closed, and the remote controller 61 instructs the controller 59 to operate. In response to this, the absorption cold heat generator P
The operation is started in the heating mode, the high temperature regenerator 1 burns the fuel, the diluted solution is heated and sent to the separator 2, and the evaporator 6 receives the high temperature diluted solution separated by the separator 2 in the conduit 10A. And, the evaporation coil 6A is guided through the cooling / heating switching valve 10 and heated by this heat. The water refrigerant is warmed outside the evaporation coil 6A, while the secondary refrigerant HFC-R134a is gasified in the evaporation coil 6A to become refrigerant vapor, and passes through the refrigerant vapor pipe 51 to cool and heat the indoor units 52, 53. Heat exchanger 5
It flows into 2A and 53A. Air-conditioning heat exchangers 52A, 5A
The refrigerant vapor that has flowed into 3A gives heat in the air in the air-conditioned space to condense and liquefy, and becomes a refrigerant liquid that flows downward in the refrigerant liquid pipe 50 and is installed at a lower position due to the difference in gravity due to the difference in gravity. Enter the receiver tank 62 in the front. Further, the refrigerant liquid is pressurized by the refrigerant pump 57, flows into the evaporation coil 6A of the evaporator, and repeats the above cycle.

【0022】しかしながら、冷媒ポンプ57が故障し暖
房運転中にもかかわらず、冷媒液が蒸発器6に戻らなく
なった場合或いは全負荷から急激な部分負荷になった場
合、即ち、室内機52、53の膨張弁54、55が閉と
なり冷媒液がレシーバタンク62に戻る量が極端に少な
くなりレシーバタンク62内の液レベルのリミットスイ
ッチが働き冷媒ポンプ57の運転時間が極端に少なくな
ると、蒸発器6内で空焚状態となって異常高圧となり、
蒸発器の破損を招く恐れがある。
However, even if the refrigerant pump 57 fails and heating operation is being performed, the refrigerant liquid does not return to the evaporator 6 or the full load suddenly changes to a partial load, that is, the indoor units 52, 53. When the expansion valves 54 and 55 of the above are closed and the amount of the refrigerant liquid returning to the receiver tank 62 is extremely small and the limit switch of the liquid level in the receiver tank 62 operates and the operating time of the refrigerant pump 57 is extremely short, the evaporator 6 It becomes an empty state inside and becomes abnormally high pressure,
This may damage the evaporator.

【0023】この蒸発器の異常高圧による蒸発器の破損
を防止するため、本実施の形態の吸収式冷熱発生装置P
は、蒸発器6の二次冷媒の温度又は圧力に基づいて吸収
式冷熱発生装置Pの暖房運転を制御し、蒸発器6の二次
冷媒の圧力の異常高圧による蒸発器6の破損を防止する
圧力制御手段15を備えている。圧力制御手段15は、
蒸発コイル6Aの二次冷媒の温度(又は圧力)を検知す
る温度(又は圧力)センサ16と、この温度(又は圧
力)センサ16の検知した温度(又は圧力)信号が入力
され、吸収式冷熱発生装置Pの暖房運転を制御するコン
トローラ59と、を有する。
In order to prevent damage to the evaporator due to the abnormally high pressure of the evaporator, the absorption-type cold heat generator P of this embodiment is used.
Controls the heating operation of the absorption cold heat generator P based on the temperature or pressure of the secondary refrigerant of the evaporator 6, and prevents damage to the evaporator 6 due to abnormally high pressure of the secondary refrigerant of the evaporator 6. The pressure control means 15 is provided. The pressure control means 15 is
A temperature (or pressure) sensor 16 for detecting the temperature (or pressure) of the secondary refrigerant in the evaporation coil 6A and a temperature (or pressure) signal detected by the temperature (or pressure) sensor 16 are input to generate absorption cold heat. The controller 59 that controls the heating operation of the device P.

【0024】図2は、図1の実施の形態の暖房運転時に
おける蒸発器6の二次冷媒の温度制御を示す線図であ
る。蒸発器6の破損を未然に防止するために上記圧力制
御手段15は、温度(又は圧力)センサ16が検知した
温度(又は圧力)が、予め設定された上限値17である
67℃(相当圧力20.4kgf/cm2)に達した時
に吸収式冷熱発生装置Pの加熱運転を停止させる。更
に、圧力制御手段15は、温度(又は圧力)センサ16
が検知した温度(又は圧力)が、予め設定された下限値
18である57℃(相当圧力14.9kgf/cm2
に達した時に吸収式冷熱発生装置Pの暖房運転を自動復
帰させる。
FIG. 2 is a diagram showing the temperature control of the secondary refrigerant of the evaporator 6 during the heating operation of the embodiment shown in FIG. In order to prevent the evaporator 6 from being damaged, the pressure control means 15 detects that the temperature (or pressure) detected by the temperature (or pressure) sensor 16 is a preset upper limit value of 67 ° C. (equivalent pressure). When it reaches 20.4 kgf / cm 2 ), the heating operation of the absorption cold heat generator P is stopped. Further, the pressure control means 15 includes a temperature (or pressure) sensor 16
The temperature (or pressure) detected by is 57 ° C (equivalent pressure 14.9 kgf / cm 2 ) which is the preset lower limit value 18.
When it reaches, the heating operation of the absorption cold heat generator P is automatically returned.

【0025】以上の構成を有する本実施の形態の吸収式
冷熱発生装置Pは次のように作用する。即ち、暖房運転
の際に、温度又は圧力センサ16が検知した温度又は圧
力によって予め設定された上限値17に達した時に吸収
式冷熱発生装置Pの暖房運転を停止させ、蒸発器二次冷
媒の圧力の異常高圧による蒸発器の破損を防止する圧力
制御手段15を備えたものは、温度又は圧力という比較
的捕らえ易い状態量によって二次冷媒の圧力を捕らえる
ことが出来、比較的単純な制御手段により確実に制御す
る。この状態量を監視することにより二次冷媒の異常高
圧による蒸発器6の破損を確実に未然に防止することが
出来る。二次冷媒の温度と圧力の間には相関関係がある
ので、少なくともどちらかを捕らえる。
The absorption-type cold heat generating device P of the present embodiment having the above structure operates as follows. That is, during the heating operation, when the temperature or pressure detected by the temperature or pressure sensor 16 reaches the preset upper limit value 17, the heating operation of the absorption cooling heat generation device P is stopped, and the evaporator secondary refrigerant is cooled. The one provided with the pressure control means 15 for preventing the damage of the evaporator due to the abnormally high pressure can capture the pressure of the secondary refrigerant by the relatively easy-to-understand state quantity such as the temperature or the pressure, and the relatively simple control means. To ensure control. By monitoring this state quantity, it is possible to reliably prevent damage to the evaporator 6 due to abnormally high pressure of the secondary refrigerant. Since there is a correlation between the temperature and the pressure of the secondary refrigerant, at least one of them is captured.

【0026】更に、圧力制御手段15が、温度又は圧力
センサが検知した温度又は圧力と予め設定された下限値
18とを比較し、下限値18に達した時に吸収式冷熱発
生装置Pの暖房運転を自動復帰させるものは、二次冷媒
の下限温度又は圧力により吸収式冷熱発生装置Pの負荷
に対する暖房を一定以上に維持する。
Further, the pressure control means 15 compares the temperature or pressure detected by the temperature or pressure sensor with a preset lower limit value 18, and when the lower limit value 18 is reached, the heating operation of the absorption cold heat generator P is performed. Is automatically restored, the heating to the load of the absorption cold heat generator P is maintained at a certain level or more by the lower limit temperature or pressure of the secondary refrigerant.

【0027】[0027]

【発明の効果】本発明の吸収式冷熱発生装置によれば、
二次冷媒による加熱運転の際に蒸発器の二次冷媒の温度
又は圧力という比較的捕らえ易い状態量によって二次冷
媒の圧力を捕らえることが出来、この状態量を監視する
ことにより二次冷媒の異常高圧による蒸発器の破損を未
然に防止することが出来る。
According to the absorption type cold heat generating device of the present invention,
During heating operation with the secondary refrigerant, the pressure of the secondary refrigerant can be captured by a relatively easy-to-understand state quantity such as the temperature or pressure of the secondary refrigerant of the evaporator, and by monitoring this state quantity, the secondary refrigerant It is possible to prevent damage to the evaporator due to abnormally high pressure.

【図面の簡単な説明】[Brief description of drawings]

【図1】本発明に係る吸収式冷熱発生装置の一実施の形
態を示す系統図である。
FIG. 1 is a system diagram showing an embodiment of an absorption-type cold heat generating device according to the present invention.

【図2】図1の実施の形態の暖房運転時における蒸発器
二次冷媒の温度制御を示す線図である。
FIG. 2 is a diagram showing temperature control of an evaporator secondary refrigerant during heating operation in the embodiment of FIG.

【符号の説明】[Explanation of symbols]

P 吸収式冷熱発生装置 1 高温再生器(再生器) 3 低温再生器(再生器) 4 凝縮器 5 吸収器 6 蒸発器 6A 蒸発コイル 9 溶液循環ポンプ 15 圧力制御手段 16 温度センサ又は圧力センサ 17 上限値 18 下限値 52、53 室内機 52A、53A 冷暖房用熱交換器 57 冷媒ポンプ P absorption type cold heat generator 1 High temperature regenerator (regenerator) 3 Low temperature regenerator (regenerator) 4 condenser 5 absorber 6 evaporator 6A evaporation coil 9 Solution circulation pump 15 Pressure control means 16 Temperature sensor or pressure sensor 17 upper limit 18 lower limit 52,53 Indoor unit 52A, 53A Air conditioner heat exchanger 57 Refrigerant pump

フロントページの続き (56)参考文献 特開 平1−219454(JP,A) 特開 昭62−80461(JP,A) 特開 昭64−14562(JP,A) 特開 昭63−105374(JP,A) 特開 平7−301433(JP,A) 特開 平3−194368(JP,A) 特開 平6−159871(JP,A) 特開 平3−194369(JP,A) 実開 昭51−41162(JP,U) (58)調査した分野(Int.Cl.7,DB名) F25B 49/04 F24F 5/00 101 F25B 15/00 F25B 15/00 306 Continuation of the front page (56) Reference JP-A 1-219454 (JP, A) JP-A 62-80461 (JP, A) JP-A 64-14562 (JP, A) JP-A 63-105374 (JP , A) JP-A-7-301433 (JP, A) JP-A-3-194368 (JP, A) JP-A-6-159871 (JP, A) JP-A-3-194369 (JP, A) 51-41162 (JP, U) (58) Fields investigated (Int.Cl. 7 , DB name) F25B 49/04 F24F 5/00 101 F25B 15/00 F25B 15/00 306

Claims (5)

    (57)【特許請求の範囲】(57) [Claims]
  1. 【請求項1】 再生器、凝縮器、蒸発器、吸収器及び溶
    液循環ポンプ等を接続して冷媒及び吸収溶液の循環回路
    を形成した吸収式冷熱発生装置において、前記蒸発器は
    二相流体の二次冷媒を内側に流す蒸発コイルを有すると
    共に、前記蒸発器の二次冷媒による加熱運転の際に、前
    記蒸発器の二次冷媒の温度又は圧力に基づいて前記吸収
    式冷熱発生装置の加熱運転を制御し、前記蒸発器の二次
    冷媒の圧力の異常高圧による前記蒸発器の破損を防止す
    る圧力制御手段を備えたものであることを特徴とする吸
    収式冷熱発生装置。
    1. In an absorption type cold heat generating device, wherein a regenerator, a condenser, an evaporator, an absorber, a solution circulation pump and the like are connected to form a circulation circuit for a refrigerant and an absorption solution, wherein the evaporator is a two-phase fluid. A heating operation of the absorption cold heat generating device is provided based on the temperature or pressure of the secondary refrigerant of the evaporator when the heating operation of the evaporator is performed by the secondary refrigerant while having an evaporation coil for flowing the secondary refrigerant inward. The absorption-type cold heat generating device according to claim 1, further comprising a pressure control means for controlling the above, and preventing damage to the evaporator due to an abnormally high pressure of the secondary refrigerant in the evaporator.
  2. 【請求項2】 請求項1において、前記圧力制御手段
    は、前記蒸発器の二次冷媒の温度又は圧力を検知する温
    度又は圧力センサを有し、該温度又は圧力センサが検知
    した温度又は圧力が、予め設定された上限値に達した時
    に前記吸収式冷熱発生装置の加熱運転を停止させるもの
    であることを特徴とする吸収式冷熱発生装置。
    2. The pressure control means according to claim 1, wherein the pressure control means has a temperature or pressure sensor for detecting the temperature or pressure of the secondary refrigerant of the evaporator, and the temperature or pressure detected by the temperature or pressure sensor is The absorption type cold heat generating device, wherein the heating operation of the absorption type cold heat generating device is stopped when the preset upper limit value is reached.
  3. 【請求項3】 請求項1又は2において、前記圧力制御
    手段は、前記温度又は圧力センサが検知した温度又は圧
    力が、予め設定された下限値に達した時に前記吸収式冷
    熱発生装置の加熱運転を自動復帰させるものであること
    を特徴とする吸収式冷熱発生装置。
    3. The heating operation of the absorption type cold heat generating device as defined in claim 1, wherein the pressure control means operates when the temperature or pressure detected by the temperature or pressure sensor reaches a preset lower limit value. An absorption-type cold heat generator characterized by being automatically returned.
  4. 【請求項4】 請求項1乃至3のいずれかにおいて、前
    記圧力制御手段は、吸収溶液を加熱して冷媒蒸気を発生
    させる高温再生器及び該高温再生器で生成した中間濃溶
    液を加熱して更に冷媒蒸気を発生させる低温再生器を有
    する二重効用の吸収式冷熱発生装置に設けられたもので
    あることを特徴とする吸収式冷熱発生装置。
    4. The high temperature regenerator according to claim 1, wherein the pressure control means heats the absorbing solution to generate a refrigerant vapor, and heats the intermediate concentrated solution generated by the high temperature regenerator. Further, the absorption cold heat generating device is provided in a double effect absorption cold heat generating device having a low temperature regenerator for generating a refrigerant vapor.
  5. 【請求項5】 請求項1乃至4のいずれかにおいて、前
    記圧力制御手段は、前記二次冷媒が室内に設けられた室
    内機の冷暖房用熱交換器に供給され、前記蒸発器の蒸発
    コイルが前記室内機の冷暖房用熱交換器の上方に配置さ
    れ、暖房運転の際には前記二次冷媒が冷媒ポンプによっ
    て前記室内機の冷暖房用熱交換器から前記蒸発器の蒸発
    コイルに送られるものに設けられたものであることを特
    徴とする吸収式冷熱発生装置。
    5. The pressure control means according to claim 1, wherein the pressure control means supplies the secondary refrigerant to a heat exchanger for cooling and heating of an indoor unit provided indoors, and an evaporation coil of the evaporator is provided. It is arranged above the cooling / heating heat exchanger of the indoor unit, and during the heating operation, the secondary refrigerant is sent from the cooling / heating heat exchanger of the indoor unit to the evaporation coil of the evaporator by the refrigerant pump. An absorption-type cold heat generator characterized in that it is provided.
JP10081896A 1996-04-23 1996-04-23 Absorption type cold heat generator Expired - Fee Related JP3393398B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP10081896A JP3393398B2 (en) 1996-04-23 1996-04-23 Absorption type cold heat generator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP10081896A JP3393398B2 (en) 1996-04-23 1996-04-23 Absorption type cold heat generator

Publications (2)

Publication Number Publication Date
JPH09287857A JPH09287857A (en) 1997-11-04
JP3393398B2 true JP3393398B2 (en) 2003-04-07

Family

ID=14283933

Family Applications (1)

Application Number Title Priority Date Filing Date
JP10081896A Expired - Fee Related JP3393398B2 (en) 1996-04-23 1996-04-23 Absorption type cold heat generator

Country Status (1)

Country Link
JP (1) JP3393398B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106091187A (en) * 2016-06-08 2016-11-09 东南大学 The low-temperature heat source absorption coupling air-conditioning device of a kind of dehumidification solution condensation heat regeneration and regulation and control method

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106091187A (en) * 2016-06-08 2016-11-09 东南大学 The low-temperature heat source absorption coupling air-conditioning device of a kind of dehumidification solution condensation heat regeneration and regulation and control method
CN106091187B (en) * 2016-06-08 2019-03-19 东南大学 A kind of absorption coupling air-conditioning device of low-temperature heat source and regulation method

Also Published As

Publication number Publication date
JPH09287857A (en) 1997-11-04

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