JPH0253702B2 - - Google Patents
Info
- Publication number
- JPH0253702B2 JPH0253702B2 JP56188641A JP18864181A JPH0253702B2 JP H0253702 B2 JPH0253702 B2 JP H0253702B2 JP 56188641 A JP56188641 A JP 56188641A JP 18864181 A JP18864181 A JP 18864181A JP H0253702 B2 JPH0253702 B2 JP H0253702B2
- Authority
- JP
- Japan
- Prior art keywords
- heat
- absorber
- heat exchanger
- generator
- heating
- 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 - Lifetime
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 38
- 239000006096 absorbing agent Substances 0.000 claims description 26
- 238000010438 heat treatment Methods 0.000 claims description 24
- 239000003507 refrigerant Substances 0.000 claims description 24
- 238000010521 absorption reaction Methods 0.000 claims description 18
- 238000001816 cooling Methods 0.000 claims description 16
- 230000006835 compression Effects 0.000 claims description 12
- 238000007906 compression Methods 0.000 claims description 12
- 239000007788 liquid Substances 0.000 description 16
- 238000004378 air conditioning Methods 0.000 description 5
- 238000009833 condensation Methods 0.000 description 5
- 239000000498 cooling water Substances 0.000 description 5
- 230000005494 condensation Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 230000005855 radiation Effects 0.000 description 3
- 238000007796 conventional method Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000009413 insulation Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- VJHXXNYZXFPCGL-UHFFFAOYSA-N [Li].Br Chemical compound [Li].Br VJHXXNYZXFPCGL-UHFFFAOYSA-N 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000004090 dissolution Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005338 heat storage Methods 0.000 description 1
- 238000002844 melting Methods 0.000 description 1
- 230000008018 melting Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 239000011877 solvent mixture Substances 0.000 description 1
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
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
Landscapes
- Sorption Type Refrigeration Machines (AREA)
- Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
Description
【発明の詳細な説明】
本発明は冷暖房装置に関し、太陽熱を熱源とし
て作動する吸収式冷凍装置を用いて、暖房給湯を
必要とする場合に太陽熱を有効に収集して室内を
暖房しようとするものである。[Detailed Description of the Invention] The present invention relates to a heating and cooling system, and uses an absorption refrigeration system that operates using solar heat as a heat source to effectively collect solar heat to heat a room when heating and hot water supply is required. It is.
従来太陽熱を利用する冷暖房装置としては、太
陽熱集熱器に水などの熱媒体を循環させ、顕熱と
して熱を取出し、この熱により冷房期にはその熱
を吸収式冷凍機のガス発生器に供給し、この熱に
より冷媒を蒸発させて冷房も行ない、一方、暖房
期には太陽熱集熱器で集められた熱により熱媒体
を介して暖房を行なうものがあつた。 Conventional air-conditioning systems that utilize solar heat circulate a heat medium such as water through a solar collector, extract heat as sensible heat, and use this heat to feed the gas generator of an absorption chiller during the cooling season. This heat is used to evaporate the refrigerant and perform air conditioning. On the other hand, during the heating season, some systems use the heat collected by solar collectors to perform heating via a heat medium.
第１図は従来の冷暖房装置の一例を示してい
る。１は太陽熱集熱器、２は温水循環ポンプ、３
は水臭化リチウム系吸収式冷凍機、４は吸収式冷
凍機３の加熱温水入口、５は加熱温水出口であ
り、６は吸収式冷凍機３で作られた冷水の出口、
７は冷水の帰り口である。また８は室内熱交換
器、９，１０，１１，１２，１３，１４は弁であ
る。 FIG. 1 shows an example of a conventional heating and cooling system. 1 is a solar heat collector, 2 is a hot water circulation pump, 3
is a lithium hydrobromide-based absorption refrigerator, 4 is a heating hot water inlet of the absorption refrigerator 3, 5 is a heating hot water outlet, 6 is an outlet of cold water produced by the absorption refrigerator 3,
7 is the return point for cold water. Further, 8 is an indoor heat exchanger, and 9, 10, 11, 12, 13, and 14 are valves.
冷房に際しては、弁９，１０を閉じ、弁１１，
１２，１３，１４を開けば太陽熱により加熱され
た温水は吸収式冷凍機３を作動させて、冷水が出
口６より出て室内熱交換器８に通じ、ここで室内
が冷房される。 When cooling, valves 9 and 10 are closed, and valves 11 and 10 are closed.
12, 13, and 14 are opened, the hot water heated by solar heat operates the absorption refrigerator 3, and the cold water exits from the outlet 6 and passes through the indoor heat exchanger 8, where the room is cooled.
暖房に際しては、弁１１，１２，１３，１４を
閉じ、弁９，１０を開けば、太陽熱により加熱さ
れた温水は、室内熱交換器８に導かれて室内を暖
房し、温度の低下した水はポンプ２により太陽熱
集熱器１に帰される。 For heating, when valves 11, 12, 13, and 14 are closed and valves 9 and 10 are opened, the hot water heated by solar heat is led to the indoor heat exchanger 8 to heat the room, and the water whose temperature has decreased is is returned to the solar heat collector 1 by the pump 2.
しかしこのような冷暖房装置では、冷房の場
合、温水を介して吸収式冷凍機の発生器を加熱す
るため、発生器の要求する温度よりさらに10℃以
上高い加熱温水が必要となり、熱損失も増加する
ばかりでなく、温水循環ポンプなど補助動力が余
分に必要である。 However, in this type of air conditioning system, since the generator of the absorption chiller is heated via hot water, heated water that is at least 10°C higher than the temperature required by the generator is required, which also increases heat loss. Not only that, but additional auxiliary power such as a hot water circulation pump is required.
この問題を解決する一方法として直接に太陽熱
集熱器を吸収式冷凍機の発生器とすることが考え
られている。 One way to solve this problem is to directly use a solar heat collector as a generator for an absorption refrigerator.
第２図はこの原理による吸収式冷凍機を示して
いる。１５は太陽熱集熱器であるが、これは同時
に吸収式冷凍機の発生器である。１６は気液分離
器、１７は凝縮器、１８は膨脹弁、１９は蒸発
器、２０は吸収器、２１は液循環ポンプ、２２は
溶液熱交換器である。 FIG. 2 shows an absorption refrigerator based on this principle. 15 is a solar heat collector, which is also a generator for an absorption refrigerator. 16 is a gas-liquid separator, 17 is a condenser, 18 is an expansion valve, 19 is an evaporator, 20 is an absorber, 21 is a liquid circulation pump, and 22 is a solution heat exchanger.
この作用を説明すると、発生器１５に、冷媒を
多量に溶かした濃溶液が流入すると、太陽幅射を
受けて温度が上昇し、冷媒ガスを蒸発させ、液は
稀溶液となる。気液分離器１６で冷媒ガスと稀溶
液は分離され、冷媒ガスは管２３を通つて凝縮器
１７に至り、水または空気で冷されて液化し、液
化冷媒は室内に導かれて、膨脹弁１８により膨脹
させられ、冷媒液は蒸発して、その蒸発熱は蒸発
器１９において室内空気と熱交換し、室内を冷却
する。 To explain this effect, when a concentrated solution in which a large amount of refrigerant is dissolved flows into the generator 15, the temperature rises due to solar radiation, evaporates the refrigerant gas, and the liquid becomes a dilute solution. The refrigerant gas and the dilute solution are separated in the gas-liquid separator 16, and the refrigerant gas passes through the pipe 23 to the condenser 17, where it is cooled with water or air and liquefied.The liquefied refrigerant is led indoors and passes through the expansion valve. 18, the refrigerant liquid evaporates, and the heat of evaporation is exchanged with indoor air in the evaporator 19 to cool the room.
そして蒸発した気体冷媒は吸収器２０に導かれ
る。一方気液分離器１６において分離された稀溶
液は、管２４を通り溶液熱交換器２２に入る。こ
れは発生器１５に送られる冷えた濃溶液と熱い稀
溶液を熱交換させるもので、稀溶液は冷却されて
吸収器２０に入る。この稀溶液は上記冷媒ガスを
吸収し濃溶液となるが、同時に発熱するので水ま
たは空気により冷却されるための濃溶液の温度は
水または空気の温度に近い。または吸収器２０内
は発生器１５内に比べて圧力が低いため、この濃
溶液を発生器１５に送るには、循環ポンプ２１が
必要である。液循環ポンプ２１を出た液は上記溶
液熱交換器２２において加熱され発生器１５に送
られて１つのサイクルが完成する。 The evaporated gas refrigerant is then led to the absorber 20. On the other hand, the dilute solution separated in the gas-liquid separator 16 passes through the pipe 24 and enters the solution heat exchanger 22 . This causes a heat exchange between the cold concentrated solution sent to the generator 15 and the hot dilute solution, which is cooled and enters the absorber 20. This dilute solution absorbs the refrigerant gas and becomes a concentrated solution, but at the same time it generates heat, so the temperature of the concentrated solution, which is cooled by water or air, is close to that of water or air. Alternatively, since the pressure inside the absorber 20 is lower than that inside the generator 15, a circulation pump 21 is required to send this concentrated solution to the generator 15. The liquid exiting the liquid circulation pump 21 is heated in the solution heat exchanger 22 and sent to the generator 15, completing one cycle.
この吸収式冷凍機は熱の有効利用がはかられ、
補助動力が液循環ポンプのみでよいというすぐれ
た利点を持つているが、冷房システムであつて暖
房期に暖房を目的として使用することはできな
い。しかし圧縮式冷房装置の凝縮器と蒸発器を逆
にすることによつてヒートポンプとして暖房に使
用できるように、上記吸収式の装置においても同
様な使い方が不可能ではない。しかし暖房を必要
とする季節には太陽熱が弱く気温が低いため、発
生器の温度は十分上らず、一方凝縮器は被暖房空
間に置かれており、凝縮温度は夏に比べて低くは
ないから、満足に動作させることは難しい。 This absorption chiller makes effective use of heat,
Although it has the advantage of requiring only a liquid circulation pump as auxiliary power, it is a cooling system and cannot be used for heating purposes during the heating season. However, just as a compression type air conditioner can be used as a heat pump for heating by reversing the condenser and evaporator, it is not impossible to use the absorption type device in the same way. However, in the season when heating is required, the solar heat is weak and the temperature is low, so the temperature of the generator does not rise sufficiently.On the other hand, the condenser is placed in the space to be heated, so the condensing temperature is not lower than in summer. Therefore, it is difficult to operate satisfactorily.
本発明はこの点を改善し、太陽熱集熱器に冷媒
溶媒混合溶液を直接循環させる太陽熱吸収冷房装
置において、暖房期には太陽熱を効率よく室内に
輸送し、暖房を行わせるように改善したものであ
る。 The present invention improves this point and improves the solar heat absorption cooling device that directly circulates a refrigerant solvent mixture solution to a solar heat collector so that solar heat is efficiently transported indoors during the heating season to perform heating. It is.
以下、本発明をその一実施例を示す第３図を参
考に説明する。２５は太陽熱を集熱する集熱器兼
ガス発生器、２６は気液分離器、２７は凝縮器、
２８は膨脹弁、２９は室内熱交換器、３０は水冷
式の吸収器、３１はその冷却水入口、３２は同出
口である。３３は液送ポンプ、３４は熱交換器で
あり、３５は冷媒ガス通路３６と凝縮器２７に設
けた弁、３７は室内熱交換器２９と吸収器３０の
間に設けた弁である。弁３５と気液分離器２６の
区間から、弁３７と吸収器３０の区間を結ぶ配管
３８は途中にこの通路を開閉する弁３９と、流量
を調整するスロツトル弁４０が設けられる。又４
１は圧縮式冷凍機、４２は水冷式の室外熱交換
器、４３は室内熱交換器、４４は四方切換弁、４
５は吸収器３０及び室外熱交換器４２の冷却水入
口、４６は同出口、４７は水循環ポンプであり、
吸収器冷却水出口３２は水冷式室外熱交換器をへ
て水循環ポンプ４７を介して吸収器冷却水入口に
連結されている。又、膨脹弁４８は室外熱交換器
４２と室内熱交換器４３とを結ぶ管路に取り付け
られている。しかして、冷房時の動作は、第２図
に示したと全く同様で、吸収器３０で生じた濃溶
液は液送ポンプ３３により熱交換器３４を通り集
熱器兼ガス発生器２５に入り、冷媒ガスを発生す
る。冷媒ガスは気液分離器２６、通路３６を通る
が、冷房時は弁３９を閉じ、弁３５を開く結果、
冷媒ガスは凝縮器２７に入り液化し、膨脹弁２８
より室内熱交換器２９に入る。そして弁３７を開
けば、蒸発した冷媒ガスは弁３７より吸収器３０
に入る。一方ガスを放出した稀溶液は、熱交換器
３４を通り吸収器３０に入つてサイクルが閉じ
る。又、室内熱交換器２９に十分な冷房出力が得
られない時には、圧縮式冷凍機４１を運転し、室
内熱交換器４３にて冷房出力を補助する。 Hereinafter, the present invention will be explained with reference to FIG. 3 showing one embodiment thereof. 25 is a heat collector and gas generator that collects solar heat, 26 is a gas-liquid separator, 27 is a condenser,
28 is an expansion valve, 29 is an indoor heat exchanger, 30 is a water-cooled absorber, 31 is a cooling water inlet thereof, and 32 is an outlet thereof. 33 is a liquid feed pump, 34 is a heat exchanger, 35 is a valve provided between the refrigerant gas passage 36 and the condenser 27, and 37 is a valve provided between the indoor heat exchanger 29 and the absorber 30. A pipe 38 connecting a section between the valve 35 and the gas-liquid separator 26 and a section between the valve 37 and the absorber 30 is provided with a valve 39 for opening and closing this passage and a throttle valve 40 for adjusting the flow rate. Also 4
1 is a compression refrigerator, 42 is a water-cooled outdoor heat exchanger, 43 is an indoor heat exchanger, 44 is a four-way switching valve, 4
5 is a cooling water inlet of the absorber 30 and the outdoor heat exchanger 42, 46 is an outlet thereof, 47 is a water circulation pump,
The absorber cooling water outlet 32 is connected to the absorber cooling water inlet via a water circulation pump 47 via a water-cooled outdoor heat exchanger. Further, the expansion valve 48 is attached to a conduit connecting the outdoor heat exchanger 42 and the indoor heat exchanger 43. Therefore, the operation during cooling is exactly the same as shown in FIG. Generates refrigerant gas. Refrigerant gas passes through the gas-liquid separator 26 and the passage 36, but during cooling, the valve 39 is closed and the valve 35 is opened.
The refrigerant gas enters the condenser 27 and is liquefied, and the expansion valve 28
It then enters the indoor heat exchanger 29. Then, when the valve 37 is opened, the evaporated refrigerant gas is transferred from the valve 37 to the absorber 30.
to go into. Meanwhile, the dilute solution that has released gas passes through the heat exchanger 34 and enters the absorber 30 to close the cycle. Furthermore, when sufficient cooling output cannot be obtained from the indoor heat exchanger 29, the compression refrigerator 41 is operated and the indoor heat exchanger 43 assists the cooling output.
暖房あるいは給湯の必要な時には、弁３５，３
７を閉じ、弁３９を開き、弁４０を調整して発生
器２５と吸収器３０の間に0.5Kg／cm2程度の圧力
差を生ぜじめると、発生した冷媒ガスは、集熱器
兼ガス発生器２５から気液分離器２６、通路３８
を経て吸収器３０に流入する。一方稀溶液は、集
熱器兼ガス発生器２５と吸収器３０の間の圧力差
によつて吸収器３０を流入し、冷媒ガスと混合し
溶解するため、集熱器兼ガス発生器２５で冷媒ガ
スを蒸発せしめるに要した熱量にほぼ等しい熱量
を、溶解の際に放出するが、吸収器３０は冷水入
口３１より冷却水が流入しているので、この水
が、この溶解熱によつて加熱され、温水出口３２
より温水を得ることができる。ここで、四方切換
弁４４にて圧縮式冷凍機４１、室内熱交換器４
３、膨脹弁４８、室外熱交換器４２に連ねる管路
にてヒートポンプサイクルを構成し、温水出口３
２より得られた温水を水循環ポンプ４７にて室外
熱交換器４２に流し、圧縮式冷凍機４１を運転す
ると、吸収器３０の吸収熱は温水を介してヒート
ポンプサイクルの冷媒蒸気に汲み上げられて、室
内熱交換器４３にてさらに高い温度で凝縮し、大
きな暖房出力、高温度の温風が得られ、住宅の暖
房に供することができる。この時、温水温度は、
直接暖房に使用する事ができる温度40〜50℃より
低くできるため、太陽熱集熱発生器２５は低い温
度で運転でき、集熱効率も大きくでき、少ない太
陽日射でも十分大なる熱入力を得ることができる
結果、高効率である。 When heating or hot water supply is required, valves 35, 3
7 is closed, valve 39 is opened, and valve 40 is adjusted to create a pressure difference of about 0.5 Kg/cm 2 between generator 25 and absorber 30, the generated refrigerant gas is transferred to the collector. From the double gas generator 25 to the gas-liquid separator 26 and the passage 38
It flows into the absorber 30 through the. On the other hand, the dilute solution flows into the absorber 30 due to the pressure difference between the collector and gas generator 25 and the absorber 30, mixes with the refrigerant gas, and dissolves in the collector and gas generator 25. An amount of heat approximately equal to the amount of heat required to evaporate the refrigerant gas is released during melting, but since cooling water flows into the absorber 30 from the cold water inlet 31, this water is absorbed by the heat of dissolution. heated, hot water outlet 32
You can get hotter water. Here, the four-way switching valve 44 connects the compression refrigerator 41 and the indoor heat exchanger 4.
3. The expansion valve 48 and the pipe line connected to the outdoor heat exchanger 42 constitute a heat pump cycle, and the hot water outlet 3
When the hot water obtained in step 2 is passed through the outdoor heat exchanger 42 by the water circulation pump 47 and the compression refrigerator 41 is operated, the absorbed heat of the absorber 30 is pumped up to the refrigerant vapor of the heat pump cycle through the hot water. The air is condensed at a higher temperature in the indoor heat exchanger 43, resulting in a large heating output and high temperature hot air, which can be used to heat a house. At this time, the hot water temperature is
Since the temperature can be lower than the 40 to 50°C that can be used for direct heating, the solar heat collection generator 25 can be operated at a low temperature, the heat collection efficiency can be increased, and a sufficiently large heat input can be obtained even with low solar radiation. The result is high efficiency.
又、温水温度は、外気温度に比して高いので、
室外熱交換器４２で蒸発する冷媒蒸気圧力は高く
なり、圧縮式冷凍機４１の吸入圧力を上昇させる
ので、わずかの圧力の加圧でよく、従つて圧縮式
冷凍機の消費電力はわずかですむ。 Also, since the hot water temperature is higher than the outside air temperature,
The refrigerant vapor pressure evaporated in the outdoor heat exchanger 42 becomes high, which increases the suction pressure of the compression refrigerator 41, so a slight increase in pressure is required, and therefore the power consumption of the compression refrigerator is small. .
又、太陽日射の得られない夜間などは、この温
水を蓄熱槽に貯め、必要に応じて室外熱交換器４
２に流して圧縮式冷凍機４１を運転すれば、低い
温水温度でも高い温風温度が得られるので長時
間、温水出力を有効に利用できる。 In addition, at night when solar radiation is not available, this hot water is stored in a heat storage tank and used as needed in the outdoor heat exchanger 4.
2 to operate the compression refrigerator 41, high hot air temperature can be obtained even with low hot water temperature, so hot water output can be effectively utilized for a long time.
この手段を従来の水の顕熱で熱輸送を行う方法
と比べると、従来の手段の場合は、風等で冷却さ
れ易い屋外で高温の湯を循環させねばならず、十
分な断熱工事を施さないかぎり、輸送中の損失が
非常に大きなものとなる。これに反し、この新し
い手段によれば、熱の輸送は主としてガスによつ
て行われ、熱の授受は、冷媒ガスの蒸発と吸収に
より行われるもので、少い物質の移動で大きな熱
量が搬ばれるため、輸送中の損失が極めて少い。 Comparing this method with the conventional method of transporting heat using the sensible heat of water, in the case of the conventional method, high-temperature hot water must be circulated outdoors where it is easily cooled by wind, etc., and sufficient insulation work is not required. Otherwise, losses during transportation will be very large. On the other hand, with this new method, heat is mainly transported by gas, and heat is exchanged by evaporation and absorption of refrigerant gas, so a large amount of heat is transferred with a small amount of material movement. The amount of loss during transportation is extremely low.
これを又、比較的類似の手段である純粋な冷媒
物質の蒸発、凝縮で熱を輸送する手段と比較して
も、同一の凝縮温度又は吸収温度の条件の下で、
蒸発凝縮のサイクルは、蒸発吸収のサイクルより
はるかにガスの圧力が高くなるため、配管途中に
凝縮器の温度より低い温度の部分が存在すると、
そこで凝縮がおこり、熱を放出してしまう危険が
あつた。しかし本発明の場合は、途中の管壁温度
が吸収器３０よりはるかに低い温度にならないか
ぎり途中での凝縮は生じないため、あまり厳重な
断熱をガス配管に施こす必要がないので実施がき
わめて容易である。 This can also be compared with a relatively similar means of transporting heat by evaporation or condensation of pure refrigerant material, under the same condensation or absorption temperature conditions.
In the evaporation-condensation cycle, the gas pressure is much higher than in the evaporation-absorption cycle, so if there is a part of the pipe with a temperature lower than the condenser temperature,
There was a danger that condensation would occur and heat would be released. However, in the case of the present invention, condensation does not occur in the middle unless the pipe wall temperature in the middle becomes much lower than that of the absorber 30, so there is no need to provide very strict insulation to the gas pipe, making it extremely difficult to implement. It's easy.
以上のように本発明は、太陽熱利用技術の中で
最も重要な熱輸送中の熱損失を極めて少くした直
熱型の冷暖房装置において、さらに熱損失の問題
が重要な冬期に、非常に少い熱損失で熱輸送で
き、高い温風温度の暖房が効率よく得られ、優れ
た効果を奏するものである。 As described above, the present invention is a direct heating type air-conditioning system that extremely reduces heat loss during heat transport, which is the most important solar heat utilization technology, and also in winter when the issue of heat loss is extremely important. Heat can be transported through heat loss, heating with high hot air temperature can be efficiently achieved, and excellent effects can be achieved.
第１図は従来の冷暖房装置の構成図、第２図は
従来の直熱型冷房装置の説明図、第３図は本発明
の一実施例を示す冷暖房装置の構成図である。
２５は集熱器兼ガス発生器、２６は気液分離
器、２７は凝縮器、２８は膨脹弁、２９は冷房用
室内熱交換器（蒸発器）、３０は吸収器、３３は
液送ポンプ、３４は熱交換器、３５，３７，３９
は弁、４０は流量調整弁、４１は圧縮式冷凍機、
４２は室外熱交換器、４３は室内熱交換器、４４
は四方切換弁、４７は循環ポンプ、４８は膨脹弁
である。
FIG. 1 is a configuration diagram of a conventional air conditioning system, FIG. 2 is an explanatory diagram of a conventional direct heating type cooling system, and FIG. 3 is a configuration diagram of a heating and cooling system showing an embodiment of the present invention. 25 is a heat collector/gas generator, 26 is a gas-liquid separator, 27 is a condenser, 28 is an expansion valve, 29 is an indoor heat exchanger for cooling (evaporator), 30 is an absorber, and 33 is a liquid feed pump. , 34 is a heat exchanger, 35, 37, 39
is a valve, 40 is a flow rate adjustment valve, 41 is a compression refrigerator,
42 is an outdoor heat exchanger, 43 is an indoor heat exchanger, 44
4 is a four-way switching valve, 47 is a circulation pump, and 48 is an expansion valve.
Claims (1)
器、膨脹弁およびポンプを連結し、前記発生器と
前記吸収器の間に、前記凝縮器、膨脹弁、蒸発器
をバイパスさせるようにした、開閉可能な弁を有
する冷媒管路を設けた吸収式冷凍機の吸収器と、
別系統の圧縮式ヒートポンプの室外熱交換器を水
回路で連結し、冷房時には前記バイパス管路を閉
じ、前記吸収器と前記熱交換器を前記水回路で冷
却して吸収式冷凍機と圧縮式ヒートポンプの冷房
出力を得られるようにし、暖房時には前記冷媒管
路の弁を開いて発生器と吸収器を短絡させて吸収
器の熱を前記水回路より、前記熱交換器に送り圧
縮式ヒートポンプにより暖房するようにした冷暖
房装置。1 At least a generator, a condenser, an evaporator, an absorber, an expansion valve, and a pump are connected, and the condenser, expansion valve, and evaporator are bypassed between the generator and the absorber. an absorber of an absorption refrigerator with a refrigerant line having a valve capable of
The outdoor heat exchanger of a compression type heat pump in a separate system is connected by a water circuit, and during cooling, the bypass pipe is closed, and the absorber and the heat exchanger are cooled by the water circuit, thereby connecting an absorption chiller and a compression type heat pump. The cooling output of the heat pump is obtained, and during heating, the valve of the refrigerant pipe is opened to short-circuit the generator and absorber, and the heat of the absorber is sent from the water circuit to the heat exchanger by the compression heat pump. A heating and cooling device designed to provide heating.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56188641A JPS5888576A (en) | 1981-11-24 | 1981-11-24 | Air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56188641A JPS5888576A (en) | 1981-11-24 | 1981-11-24 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5888576A JPS5888576A (en) | 1983-05-26 |
| JPH0253702B2 true JPH0253702B2 (en) | 1990-11-19 |
Family
ID=16227262
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56188641A Granted JPS5888576A (en) | 1981-11-24 | 1981-11-24 | Air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5888576A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60255528A (en) * | 1984-05-31 | 1985-12-17 | Mitsubishi Electric Corp | Cooler for car |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5563364A (en) * | 1978-11-08 | 1980-05-13 | Kogyo Gijutsuin | High temperature heat pump system |
| JPS5599565A (en) * | 1979-01-25 | 1980-07-29 | Matsushita Electric Ind Co Ltd | Solar heat absorption type cooling* heating and hot water supply equipment |
-
1981
- 1981-11-24 JP JP56188641A patent/JPS5888576A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5563364A (en) * | 1978-11-08 | 1980-05-13 | Kogyo Gijutsuin | High temperature heat pump system |
| JPS5599565A (en) * | 1979-01-25 | 1980-07-29 | Matsushita Electric Ind Co Ltd | Solar heat absorption type cooling* heating and hot water supply equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5888576A (en) | 1983-05-26 |
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