Deprecated: The each() function is deprecated. This message will be suppressed on further calls in /home/zhenxiangba/zhenxiangba.com/public_html/phproxy-improved-master/index.php on line 456
JPS602586B2 - Absorption heat pump - Google Patents
[go: Go Back, main page]

JPS602586B2 - Absorption heat pump - Google Patents

Absorption heat pump

Info

Publication number
JPS602586B2
JPS602586B2 JP2833880A JP2833880A JPS602586B2 JP S602586 B2 JPS602586 B2 JP S602586B2 JP 2833880 A JP2833880 A JP 2833880A JP 2833880 A JP2833880 A JP 2833880A JP S602586 B2 JPS602586 B2 JP S602586B2
Authority
JP
Japan
Prior art keywords
heat
temperature
air
evaporator
absorber
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
Application number
JP2833880A
Other languages
Japanese (ja)
Other versions
JPS56124863A (en
Inventor
功 竹下
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
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 Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Priority to JP2833880A priority Critical patent/JPS602586B2/en
Priority to US06/240,591 priority patent/US4368624A/en
Priority to DE8181300911T priority patent/DE3167021D1/en
Priority to EP81300911A priority patent/EP0035873B1/en
Publication of JPS56124863A publication Critical patent/JPS56124863A/en
Publication of JPS602586B2 publication Critical patent/JPS602586B2/en
Expired legal-status Critical Current

Links

Landscapes

  • Sorption Type Refrigeration Machines (AREA)

Description

【発明の詳細な説明】 本発明は吸収式ヒートポンプの改良に関する。[Detailed description of the invention] The present invention relates to improvements in absorption heat pumps.

一般に、吸収式の冷凍サイクルを冷房に使用すると共に
ヒートポンプとして暖房にも使用できるようにすること
はヒートポンプの省エネルギー性から、時代の要請とし
て注目されている技術である。この場合「媒体の濃度お
よび循環量など動作条件を変えないとすればト蒸発温度
など冷房に最適な条件に作られた装置が暖房に使用され
た時も外気温度の広い範囲においてヒートポンプとして
十分に作動するとはかぎらない。すなわち蒸発温度が十
分低くないので少し外気温が下がると蒸発器から熱が取
りこめなくなる。逆にヒートポンプの時に十分外気温が
低くとも作動するように蒸発温度を下げた濃度条件にす
ると、暖房時の蒸発器に結氷する危険が増大するばかり
でなく勺給房時の蒸発温度が低くなりすぎ〜成績係数が
悪くなる。この問題を解決する方法としても数収器の袷
却水を室内熱交換器で放熱した水をそのま》鷲いるので
はなくへ途中に災気と熱交換を行う放熱器を経て吸収器
冷却水入口に至るようにすることによりt外気濁の低下
に伴って吸収器冷却水温を下げることができも従って吸
収器での溶液の最低温度もそれだけ下りt その結果蒸
発温度が下るので、外気温度のかなり低い時でもヒート
ポンプとして働かすことができるという方法が考えられ
ている。
Generally, using an absorption refrigeration cycle for air conditioning and also using it as a heat pump for heating is a technology that is attracting attention as a requirement of the times due to the energy saving properties of heat pumps. In this case, ``If operating conditions such as the concentration of the medium and the amount of circulation are not changed, even when a device made under the optimal conditions for cooling, such as the evaporation temperature, is used for heating, it will not work well as a heat pump over a wide range of outside air temperatures.'' In other words, the evaporation temperature is not low enough, so if the outside temperature drops slightly, heat cannot be taken in from the evaporator.On the other hand, when using a heat pump, the concentration condition is such that the evaporation temperature is lowered so that it will work even if the outside temperature is low enough. Not only does this increase the risk of freezing on the evaporator during heating, but the evaporation temperature during heating becomes too low and the coefficient of performance deteriorates.One way to solve this problem is to reduce the number of evaporators. Water that has radiated heat with an indoor heat exchanger is not directly poured into the water, but instead passes through a radiator that exchanges heat with the water before reaching the absorber cooling water inlet, thereby reducing outdoor air turbidity. As a result, the temperature of the absorber cooling water can be lowered, and the minimum temperature of the solution in the absorber is also lowered accordingly.As a result, the evaporation temperature is lowered, so it can be used as a heat pump even when the outside air temperature is quite low. It is considered.

第亀図はこのような改良を行った吸収式ヒ肌トポンブの
原理図‐乙ある。この図においてtl尊ま発生器でバー
ナー2でガスなどを燃焼せしめて加熱を行うとも港嬢を
吸収液に吸収させて溶液3から袷煤蒸気が発生し、配管
4を経て被暖房空間6に設けられた凝縮熱軸こおいて凝
縮しト凝縮熱はファン孔こよって作られた風によって室
内空気を暖めるのに供せられる。ここで凝縮した液化玲
煤は、配管8を経て「被暖房空間5の外に出、減圧弁9
を経て戸外に設けられた蒸発器菅愚もこ送られる。蒸発
温度をTeとし「外気温度をTamとすれば「Te<T
amならば外気から熱をうばつて蒸発器軍鰹内で玲嬢は
蒸発する。蒸発器官9‘ま外気との熱交換をよくするよ
うに「ファン電竜により強制的に蒸発器に空気が送られ
る。
Figure 2 shows the principle of an absorbent skin pump that has undergone such improvements. In this figure, when heating is performed by burning gas or the like with a burner 2 in a tlsonma generator, soot vapor is generated from the solution 3 by absorbing the minatojo into the absorption liquid and flowing into the heated space 6 via piping 4. The heat of condensation condenses in the provided condensing heat shaft and is used to warm the indoor air by the wind generated by the fan hole. The liquefied soot condensed here goes out of the heated space 5 through the piping 8, and is transferred to the pressure reducing valve 9.
After that, it is sent to the evaporator Sugamoko, which is installed outdoors. If the evaporation temperature is Te and the outside temperature is Tam, then Te<T
If it is am, Rei-jo will evaporate inside the evaporator by drawing heat from the outside air. Air is forcibly sent to the evaporator by a fan to improve heat exchange with the outside air.

蒸発した冷嬢蒸気は配管軍芝を経て吸収驚喜3に流入す
る。一方t吸収器骨鍬こは発生器官員こおいて冷煤蒸気
を放出しト溶媒含有量の減少した高温の希溶液がも配管
亀年を経て熱交換器9議を通り後述の濃溶液と熱交換す
ることによめも温度を下げて流量調整弁官亀を通りも薮
収器軍選内に淳がれる8叉吸収器肉には伶却水管官官が
あげも溶液を袴却することができる。
The evaporated Reijo steam flows into the absorption shock 3 via the piping gun lawn. On the other hand, the t-absorber bone hoe releases cold soot vapor from the generator, and the high-temperature dilute solution with reduced solvent content also passes through 9 heat exchangers after many years of piping and becomes the concentrated solution described below. Through heat exchange, the water temperature is lowered and the liquid is passed through the flow rate regulator turtle, and the water is poured into the eight-pronged absorber. I can do it.

吸収器13に注がれた希溶液は冷煤蒸気を吸収し、溶液
は濃溶液となるが、この際多量の吸収熱を発生する。こ
の吸収熱は冷却水管17中を流れる水に奪われる。すな
わち水は加熱されて吸収器を出る。この温水は配管18
を通って被暖房空間5内に設けた熱交換器19もこ送ら
れ、ファン281こよって作られた風によって熱を室内
空気に与え、水は冷却されて配管21、水ポンプ22を
経て吸収器に戻ってくる。一方吸収器の中で袷媒蒸気を
吸収し、冷却水で冷却された濃溶液は配管23を通り〜
溶液ポンプ24で加圧され、熱交換器15で高温の希溶
液と熱交換することにより温められ発生器1内に送りこ
まれサイクルが完結する。以上の説明から明らかなごと
く、吸収式ヒートポンプにおいては発生器におし、バー
ナーにより与えられた熱以外に蒸発器において外気から
与えられた熱が、凝縮器6および熱交換器19において
被暖房空間5内の空気に移し与えられることになるから
、暖房出力はこの両者の和であり、有償の熱入力はバー
ナー2の熱入力のみであるから、成績係数すなわち暖房
出力を加熱入力で割った値は1より大となり、省エネル
ギー機器として今日きわめて注目されている。以上の説
明で熱交換器25の機能についてのべなかったが、この
部分がはじめに述べた改良された部分であって〜吸収器
冷却水管17にもどる水は外気と熱交換を行う熱交換器
25を通るため、外気温が下がるほどここでの放熱が増
加し、吸収器13にもどる水温が下り、それだけ蒸発温
度が下ることになり、外気から熱を取りこむことができ
る温度城を低温側に延ばすことができる。
The dilute solution poured into the absorber 13 absorbs the cold soot vapor and becomes a concentrated solution, but at this time a large amount of absorption heat is generated. This absorbed heat is taken away by the water flowing through the cooling water pipe 17. That is, the water leaves the absorber heated. This hot water is pipe 18
The heat exchanger 19 installed in the heated space 5 is also sent through the air, and the air generated by the fan 281 gives heat to the indoor air, and the water is cooled and sent to the absorber via the piping 21 and the water pump 22. come back to. On the other hand, the concentrated solution that absorbs the medium vapor in the absorber and is cooled with cooling water passes through the pipe 23 ~
The solution is pressurized by the solution pump 24, heated by exchanging heat with a high-temperature dilute solution in the heat exchanger 15, and fed into the generator 1, completing the cycle. As is clear from the above explanation, in the absorption heat pump, in addition to the heat given by the generator and the burner, the heat given from the outside air in the evaporator is used in the condenser 6 and heat exchanger 19 to heat the heated space. Since the heating output is the sum of these two, and the only paid heat input is the heat input of burner 2, the coefficient of performance is the value obtained by dividing the heating output by the heating input. is greater than 1, and it is attracting much attention today as an energy-saving device. Although the function of the heat exchanger 25 was not mentioned in the above explanation, this part is the improved part mentioned at the beginning. As the outside air temperature decreases, the heat dissipated here increases, and the temperature of the water returning to the absorber 13 decreases, which lowers the evaporation temperature accordingly, extending the temperature castle where heat can be taken in from the outside air to the lower temperature side. be able to.

空気熱源のヒートポンプを外気温の低い時に使用する場
合のもう1つの問題点は蒸発器の結氷である。これは蒸
発温度が0℃以下であれば或る程度避けることはできな
い。本発明は上記先行発明をもとにし、この点を改善す
ることを目的としたものである。すなわち熱源となる外
気温が低下し、それに応じて蒸発温度も下り、0℃以下
になれば「大気の湿度にもよるが、蒸発器に結氷を生ず
る。
Another problem when using an air-source heat pump when the outside temperature is low is ice formation in the evaporator. This cannot be avoided to some extent if the evaporation temperature is below 0°C. The present invention is based on the above prior invention and aims to improve this point. In other words, as the outside temperature, which is the heat source, falls, the evaporation temperature also falls accordingly, and if it falls below 0°C, ice will form in the evaporator, depending on the humidity of the atmosphere.

しかし蒸発器に導かれる空気の温度が高ければたとえ蒸
発温度が000以下であっても結氷しないから、少しで
も空気の温度を上げることができればそれだけ結氷の問
題を緩和することができる。所で先に述べた改良された
ヒートポンプにおいて外気温が低下すると熱交換器25
によって外気に捨てる熱量が増加しそれによって蒸発温
度を下げているから「こ)で捨てる熱を利用することは
極めて有意義である。第2図a,bは上記システムの外
気温度の変化に対する蒸発温度、外気温度と蒸発温度の
差、吸収器入口水温、および吸収熱の利用率の一例を示
すグラフである。
However, if the temperature of the air introduced into the evaporator is high, no freezing will occur even if the evaporation temperature is below 000, so if the temperature of the air can be raised even a little, the problem of freezing can be alleviated. By the way, in the improved heat pump mentioned earlier, when the outside temperature drops, the heat exchanger 25
This increases the amount of heat discarded to the outside air, thereby lowering the evaporation temperature, so it is extremely meaningful to utilize the heat discarded in this way. , is a graph showing an example of the difference between the outside air temperature and the evaporation temperature, the absorber inlet water temperature, and the utilization rate of absorbed heat.

このグラフから明らかなごとく吸収熱の利用率は外気温
の低下に伴って低下しており、(1一利用率)だけの率
で吸収器で発生する熱量の一部が空気中に捨てられるこ
とになる。例えば利用率が70%になれば30%は捨て
られているわけである。一方蒸発器が必要とする熱量は
、そのシステムの成績係数によるが、吸収器の発生熱量
の60〜70%程度であるから、この空気中に捨ててい
る熱量を蒸発器にまわすことができれ‘よ、先の数値例
の場合「蒸発器の必要熱量の約半分が先に捨てた熱量で
まかなえることになる。
As is clear from this graph, the utilization rate of absorbed heat decreases as the outside temperature decreases, and a portion of the heat generated in the absorber is discarded into the air at a rate of (1 - utilization rate). become. For example, if the usage rate is 70%, 30% will be thrown away. On the other hand, the amount of heat required by the evaporator depends on the coefficient of performance of the system, but is about 60 to 70% of the amount of heat generated by the absorber, so the amount of heat that is wasted in the air can be transferred to the evaporator. 'Yo, in the numerical example above, ``About half of the heat required by the evaporator can be covered by the heat discarded earlier.

例えばその時の外気温が8び○であったとして、蒸発器
を通過しこれに熱を与えた後の空気の温度は−2℃であ
ったとすれば、この場合結氷はまぬがれえない。しかし
、必要な熱量の半分が熱交換器25から供給されている
とすれば、熱交換器25を通過する空気と、蒸発器10
を通過する空気が同一ならば{8o−(一2o)}÷2
=5o熱交換器25を通過した後で空気の温度は上るこ
とになる。すなわち、8℃の空気はl3qoに暖められ
る。従ってこの空気を引き続いて蒸発器を通過させると
10こ○温度が下り、結局3℃で蒸発器を出ることにな
るから、この場合は結氷しないと考えてよい。そのため
の構成として本発明は、少なくとも発生器と、凝縮器と
、蒸発器と、吸収器とで吸収式ヒ,−トポンプサィクル
を形成し「前記吸収器の冷却液の頭熱を暖房などに供し
、被加熱空間に放熱後の冷却液を吸収器に戻す区間に、
外気と熱交換する熱交換器を設け、前記熱交換器と熱交
換を行った空気を前記蒸発器をも通過する手段を設けた
も,のである。
For example, if the outside temperature at that time was 80°C, but the temperature of the air after passing through the evaporator and giving it heat was -2°C, freezing would be inevitable in this case. However, if half of the required heat is supplied from the heat exchanger 25, the air passing through the heat exchanger 25 and the evaporator 10
If the air passing through is the same, {8o-(-2o)}÷2
=5o After passing through the heat exchanger 25, the temperature of the air will rise. That is, air at 8°C is heated to 13qo. Therefore, if this air is subsequently passed through the evaporator, the temperature will drop by 10 degrees, and it will eventually leave the evaporator at 3 degrees Celsius, so it can be considered that no ice will form in this case. As a configuration for this purpose, the present invention forms an absorption type heat pump cycle with at least a generator, a condenser, an evaporator, and an absorber, and ``uses the head heat of the coolant of the absorber for heating etc.'' In the section where the cooling liquid is returned to the absorber after heat dissipation into the heated space,
A heat exchanger for exchanging heat with outside air is provided, and a means is provided for allowing the air that has undergone heat exchange with the heat exchanger to also pass through the evaporator.

この構成により本願発明は、吸収熱の一部を捨てること
により、蒸発温度を外気によって自動的に変化しうるご
とくした吸収式ヒートポンプの拾てた熱を再利用するこ
とにより、結氷を防ぐのが本発明の根本的な考え方で、
さらに第3図に示した一実施例について詳しく説明する
With this configuration, the present invention can prevent freezing by reusing the heat picked up by the absorption heat pump, which allows the evaporation temperature to be automatically changed depending on the outside air by discarding a part of the absorbed heat. The fundamental idea of the present invention is to
Further, one embodiment shown in FIG. 3 will be explained in detail.

第3図において13は吸収器で弁16を通って希溶液が
流入、又膨脹弁9を通って蒸発器10に流入した液化冷
媒はファン11によって吹き付けられる空気から熱をう
ばつて蒸発し、気化した冷煤は管12を通って吸収器1
川こ流入し「希溶液に吸収されて濃溶液となり、配管2
3、溶液ポンプ24を経て発生器に送られる。
In Fig. 3, reference numeral 13 denotes an absorber, into which the dilute solution flows through the valve 16, and the liquefied refrigerant that flows into the evaporator 10 through the expansion valve 9 absorbs heat from the air blown by the fan 11, evaporates, and vaporizes. The cooled soot passes through the pipe 12 to the absorber 1.
The river flows into the river, is absorbed by the dilute solution, becomes a concentrated solution, and flows into pipe 2.
3. The solution is sent to the generator via the solution pump 24.

冷媒蒸気が希溶液に吸収される時に発生する吸収熱は吸
収器冷却水管17の中を流れる水に与えられる水の中を
流れる水に与えられ、管18を通った温水は被暖房空間
5の中に設けられた熱交換器19に送られ、ファン2川
こよって作られた風によって熱を大気に与え、水は冷却
されて配管21、水ポンプ22をへて熱交換器25を通
り、さらに冷却され、吸収器冷却水入口から再び吸収器
内の冷却水管17に入り、温められる。ここで熱交換器
25を通る空気はダクト26とその中に設けられたファ
ン11によって蒸発器101こ吹き付けられるようにな
っている。このような構成とすることにより熱交換器2
5において、空気中に放出された熱はそのま)蒸発器で
回収されているので「先にも説明したごとく蒸発器を出
る空気の温度はあまり下らないですみ、蒸発器10の結
氷を緩和してくれる。以上詳述したごとく本発明によれ
ば吸収式ヒートポンプの蒸発温度を外気温度により可変
とする発明をさらに改善し蒸発器の結氷の問題を解決し
たもので、実用上の価値は極めて大きいものである。
The absorption heat generated when the refrigerant vapor is absorbed into the dilute solution is given to the water flowing in the absorber cooling water pipe 17, and the hot water passing through the pipe 18 is transferred to the heated space 5. The water is sent to a heat exchanger 19 installed inside, and the air generated by two fans gives heat to the atmosphere, and the water is cooled and passes through piping 21, water pump 22, and heat exchanger 25. It is further cooled, enters the cooling water pipe 17 in the absorber again from the absorber cooling water inlet, and is warmed. Here, air passing through the heat exchanger 25 is blown onto the evaporator 101 by a duct 26 and a fan 11 provided therein. With such a configuration, the heat exchanger 2
In step 5, the heat released into the air is directly recovered in the evaporator, so the temperature of the air exiting the evaporator does not drop much as explained earlier, and the ice formation in the evaporator 10 is alleviated. As detailed above, the present invention further improves the invention of making the evaporation temperature of an absorption heat pump variable depending on the outside air temperature and solves the problem of freezing in the evaporator, and has extremely great practical value. It is something.

【図面の簡単な説明】[Brief explanation of the drawing]

第1図は外気温によって蒸発温度を可変とした吸収式ヒ
ートポンプの構成図、第2図a,bはそれぞれ第1図に
示した吸収式ヒートポンプの蒸発温度、吸収器冷却水温
、外気温度−蒸発温度と外気温度の関係を示す特性図、
熱利用率の外気温度の関係を示す特性図、第3図は本発
明の一実施例のヒートポンプの構成図である。 5・…・・被暖房空間、9…・・・減圧弁、10・・…
・蒸発器、11,20・・・・・・ファン、12,21
,23……配管「 13・・・…吸収器、16……流量
調整弁、17…・・・冷却水管「 18・・・・・・配
管、19・・・・・・熱交換器、22・・・・・・ポン
プ、25・・・・・・熱交換器、26・・…・ダクト。 第1図第2図 第3図
Figure 1 is a block diagram of an absorption heat pump with variable evaporation temperature depending on the outside temperature. Figures 2a and b are the evaporation temperature, absorber cooling water temperature, and outside air temperature - evaporation of the absorption heat pump shown in Figure 1, respectively. Characteristic diagram showing the relationship between temperature and outside temperature,
FIG. 3 is a characteristic diagram showing the relationship between the heat utilization rate and the outside air temperature, and is a configuration diagram of a heat pump according to an embodiment of the present invention. 5... Heated space, 9... Pressure reducing valve, 10...
・Evaporator, 11, 20...Fan, 12, 21
, 23... Piping " 13... Absorber, 16... Flow rate adjustment valve, 17... Cooling water pipe " 18... Piping, 19... Heat exchanger, 22 ... Pump, 25 ... Heat exchanger, 26 ... Duct. Figure 1 Figure 2 Figure 3

Claims (1)

【特許請求の範囲】[Claims] 1 発生器と、凝縮器と、蒸発器と、吸収器とで吸収式
ヒートポンプサイクルを形成し、前記吸収器の冷却液の
顕熱を加熱に供し、被加熱空間に放熱後の冷却液を吸収
器に戻す区間に、外気と熱交換する熱交換器を設け、前
記熱交換器と熱交換を行った空気を前記蒸発器をも通過
する手段を設けた吸収式ヒートポンプ。
1 An absorption heat pump cycle is formed by a generator, a condenser, an evaporator, and an absorber, and the sensible heat of the coolant of the absorber is used for heating, and the coolant after heat radiation is absorbed into the space to be heated. An absorption heat pump that is provided with a heat exchanger for exchanging heat with outside air in a section where the air is returned to the container, and is provided with means for causing the air that has undergone heat exchange with the heat exchanger to also pass through the evaporator.
JP2833880A 1980-03-05 1980-03-05 Absorption heat pump Expired JPS602586B2 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2833880A JPS602586B2 (en) 1980-03-05 1980-03-05 Absorption heat pump
US06/240,591 US4368624A (en) 1980-03-05 1981-03-04 Absorption type heat pump having indoor and outdoor radiators connected in series in a water flow circuit during heat mode
DE8181300911T DE3167021D1 (en) 1980-03-05 1981-03-04 Absorption type heat pump having radiators
EP81300911A EP0035873B1 (en) 1980-03-05 1981-03-04 Absorption type heat pump having radiators

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2833880A JPS602586B2 (en) 1980-03-05 1980-03-05 Absorption heat pump

Publications (2)

Publication Number Publication Date
JPS56124863A JPS56124863A (en) 1981-09-30
JPS602586B2 true JPS602586B2 (en) 1985-01-22

Family

ID=12245812

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2833880A Expired JPS602586B2 (en) 1980-03-05 1980-03-05 Absorption heat pump

Country Status (1)

Country Link
JP (1) JPS602586B2 (en)

Also Published As

Publication number Publication date
JPS56124863A (en) 1981-09-30

Similar Documents

Publication Publication Date Title
GB2166856A (en) Coupled dual loop absorption heat pump
US6487874B2 (en) Absorption refrigerator
JP2000018762A (en) Absorption refrigeration equipment
US4509336A (en) Air conditioning apparatus
JPS602586B2 (en) Absorption heat pump
JPS6045328B2 (en) heating device
JP3859566B2 (en) Hybrid air conditioner
CN115111802A (en) Coupling compression and absorption type high-temperature heat pump system and method thereof
JPS6145144B2 (en)
JPS5849872A (en) heat pump equipment
JP2002089366A (en) Cogeneration system
CN112413925A (en) Low-temperature heat source refrigerating device
JPS6024894B2 (en) Absorption heat pump device
KR0136205Y1 (en) Absorption air conditioner
JPS5935755A (en) Heat pump type hot-water supply apparatus
KR0139349Y1 (en) Circulation of condensed water of evaporator for absorption type refrigerator
JPS61167429A (en) Regenerating method of liquid moisture-absorbent in air-conditioning equipment
JP3549905B2 (en) Air conditioning method and apparatus using absorption chiller
JPS602582B2 (en) Absorption refrigeration equipment
KR0137580Y1 (en) Liquid refrigerant chiller of absorption chiller, heater
JPS6135900Y2 (en)
KR0173495B1 (en) Absorptive type air conditioner
JPS58178162A (en) Absorption type heat pump device
JPH0350373Y2 (en)
JPH0253702B2 (en)