JPH10110976A - Natural circulating type heat transfer device - Google Patents
Natural circulating type heat transfer deviceInfo
- Publication number
- JPH10110976A JPH10110976A JP8286008A JP28600896A JPH10110976A JP H10110976 A JPH10110976 A JP H10110976A JP 8286008 A JP8286008 A JP 8286008A JP 28600896 A JP28600896 A JP 28600896A JP H10110976 A JPH10110976 A JP H10110976A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat transfer
- cold
- hot water
- evaporator
- 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.)
- Pending
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 89
- 239000007788 liquid Substances 0.000 claims abstract description 17
- 239000007791 liquid phase Substances 0.000 claims abstract description 7
- 238000000034 method Methods 0.000 claims abstract description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 20
- 238000001816 cooling Methods 0.000 abstract description 7
- 238000010438 heat treatment Methods 0.000 abstract description 7
- NBVXSUQYWXRMNV-UHFFFAOYSA-N fluoromethane Chemical compound FC NBVXSUQYWXRMNV-UHFFFAOYSA-N 0.000 abstract 1
- 238000010276 construction Methods 0.000 description 5
- 230000005484 gravity Effects 0.000 description 5
- LVGUZGTVOIAKKC-UHFFFAOYSA-N 1,1,1,2-tetrafluoroethane Chemical compound FCC(F)(F)F LVGUZGTVOIAKKC-UHFFFAOYSA-N 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 230000001143 conditioned effect Effects 0.000 description 2
- UJPMYEOUBPIPHQ-UHFFFAOYSA-N 1,1,1-trifluoroethane Chemical compound CC(F)(F)F UJPMYEOUBPIPHQ-UHFFFAOYSA-N 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- GTLACDSXYULKMZ-UHFFFAOYSA-N pentafluoroethane Chemical compound FC(F)C(F)(F)F GTLACDSXYULKMZ-UHFFFAOYSA-N 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0401—Refrigeration circuit bypassing means for the compressor
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、自然循環式熱移動
装置に関する。The present invention relates to a natural circulation heat transfer device.
【０００２】[0002]
【従来の技術】一般に、例えばフロンＲ１３４ａからな
る冷媒を、熱移動サイクル内で気液相変化させることに
より自然循環させるヒートパイプ方式を用いた自然循環
式熱移動装置は知られている（例えば、特許第２５１１
０８１号公報）。2. Description of the Related Art In general, there is known a natural circulation type heat transfer device using a heat pipe system in which a refrigerant made of, for example, Freon R134a is naturally circulated by changing a gas-liquid phase in a heat transfer cycle (for example, see, for example, Japanese Patent Application Laid-Open Publication No. HEI 9-163191). Patent No. 2511
081).
【０００３】この種のものでは、サイクル内での大容量
の熱移動をスムーズに行うために、冷媒管内の圧力損失
を極力抑える対策が講じられる。この対策としては、従
来例えば、冷媒ガス管の管径を大きく設定したり（例え
ば、φ５０．８ｍｍ）、蒸発器のパス数を多く設定した
りすることが行われている。In this type, measures are taken to minimize the pressure loss in the refrigerant pipe in order to smoothly transfer a large amount of heat in a cycle. As a countermeasure for this, conventionally, for example, the diameter of the refrigerant gas pipe is set large (for example, φ50.8 mm), and the number of passes of the evaporator is set large.
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、従来の
対策では、熱移動サイクル内の圧力損失は抑えることは
できるが、配管サイズが大きい分だけ施工費用が高くな
り、また蒸発器のパス数が多い分だけ、蒸発器の設計自
由度が少なくなる等の問題がある。However, according to the conventional measures, the pressure loss in the heat transfer cycle can be suppressed, but the construction cost is increased due to the large piping size, and the number of evaporator passes is large. However, there is a problem that the degree of freedom of design of the evaporator is reduced.
【０００５】そこで、本発明の目的は、上記課題を解消
するために、配管の施工費用を低く抑え、また蒸発器の
設計自由度を向上し、更に熱移動サイクル内の圧力損失
を極力抑えることのできる自然循環式熱移動装置を提供
することにある。[0005] Therefore, an object of the present invention is to solve the above-mentioned problems by suppressing the construction cost of piping, improving the degree of freedom in designing the evaporator, and further suppressing the pressure loss in the heat transfer cycle as much as possible. It is an object of the present invention to provide a natural circulation type heat transfer device which can be used.
【０００６】[0006]
【課題を解決するための手段】請求項１に記載の発明
は、凝縮器、蒸発器を備え、これら凝縮器、蒸発器の間
を冷媒液管、及び冷媒ガス管でつないで熱移動サイクル
を形成し、この熱移動サイクル内には冷媒を封入した自
然循環式熱移動装置において、前記冷媒には、蒸気密度
の大きいフロンＲ４０４Ａからなる冷媒を選択し、この
蒸気密度の大きい冷媒を気液相変化させることにより当
該冷媒を前記熱移動サイクル内で自然循環させることを
特徴とするものである。According to a first aspect of the present invention, there is provided a condenser and an evaporator, and the condenser and the evaporator are connected by a refrigerant liquid pipe and a refrigerant gas pipe to execute a heat transfer cycle. In the natural circulation heat transfer device in which a refrigerant is sealed in the heat transfer cycle, a refrigerant made of Freon R404A having a high vapor density is selected as the refrigerant, and the refrigerant having a high vapor density is separated into a gas-liquid phase. By changing the temperature, the refrigerant is naturally circulated in the heat transfer cycle.
【０００７】請求項２に記載の発明は、凝縮器、蒸発器
を備え、これら凝縮器、蒸発器の間を冷媒液管、及び冷
媒ガス管でつないで熱移動サイクルを形成し、この熱移
動サイクル内には冷媒を封入した自然循環式熱移動装置
において、前記冷媒には、蒸気密度の大きいフロンＲ４
０４Ａからなる冷媒を選択し、この蒸気密度の大きい冷
媒を気液相変化させることにより当該冷媒を前記熱移動
サイクル内で自然循環させ、且つ冷媒ガス管の管径を小
さく、及び／又は蒸発器のパス数を少なく設定したこと
を特徴とするものである。According to a second aspect of the present invention, a condenser and an evaporator are provided, and the condenser and the evaporator are connected by a refrigerant liquid pipe and a refrigerant gas pipe to form a heat transfer cycle. In a natural circulation type heat transfer device in which a refrigerant is sealed in a cycle, the refrigerant may include Freon R4 having a high vapor density.
04A refrigerant is selected, and the refrigerant having a high vapor density undergoes a gas-liquid phase change, whereby the refrigerant is naturally circulated in the heat transfer cycle, and the diameter of the refrigerant gas pipe is reduced, and / or an evaporator is provided. Is set to be small.
【０００８】請求項３に記載の発明は、請求項１又は２
に記載のものにおいて、前記冷媒を循環させるためのブ
ースタポンプを備えたことを特徴とするものである。[0008] The invention according to claim 3 is the invention according to claim 1 or 2.
Wherein a booster pump for circulating the refrigerant is provided.
【０００９】これらの発明によれば、熱移動サイクル内
にフロンＲ４０４Ａからなる冷媒が封入されるので、従
来のようにフロンＲ１３４ａ（ＣＨ2ＦＣＦ3；テトラフ
ロロエタン）が封入される場合に比べて、蒸発温度が７
℃では「蒸気密度」が約２倍になる。従って、フロンＲ
１３４ａを使用する場合に比べて、冷媒ガス管を通過す
る冷媒の圧損は小さくなるので、その分だけ、冷媒ガス
管の管径を小さく（例えば、φ４４．５ｍｍ）すること
ができ、また同様の理由から、蒸発器のパス数を減少す
ることができるので、蒸発器の設計自由度が向上する。According to these inventions, the refrigerant consisting of Freon R404A is sealed in the heat transfer cycle, so that compared to the case where Freon R134a (CH 2 FCF 3 ; tetrafluoroethane) is sealed as in the prior art. , Evaporation temperature is 7
At ℃, the “vapor density” doubles. Therefore, Freon R
Since the pressure loss of the refrigerant passing through the refrigerant gas pipe is smaller than when 134a is used, the pipe diameter of the refrigerant gas pipe can be reduced by that much (for example, φ44.5 mm). For this reason, since the number of passes of the evaporator can be reduced, the degree of freedom in designing the evaporator is improved.
【００１０】[0010]
【発明の実施の形態】以下、本発明の一実施の形態を図
面に基づいて説明する。An embodiment of the present invention will be described below with reference to the drawings.
【００１１】図１において、１は吸収式の熱源機を示し
ている。この熱源機１には当該熱源機１の熱により冷温
水を生成する冷温水機３がつながれており、この冷温水
機３には熱源側熱交換器５が収納されている。この熱源
側熱交換器５は、後述するように、冷温水機３が冷水で
満たされる場合には凝縮器として作用するとともに、温
水で満たされる場合には蒸発器として作用する。In FIG. 1, reference numeral 1 denotes an absorption type heat source device. The heat source unit 1 is connected to a cold / hot water unit 3 that generates cold / hot water by the heat of the heat source unit 1, and the cold / hot water unit 3 houses a heat source side heat exchanger 5. As will be described later, the heat source side heat exchanger 5 functions as a condenser when the cold / hot water machine 3 is filled with cold water, and acts as an evaporator when filled with hot water.
【００１２】この冷温水機３には冷媒液管７、及び冷媒
ガス管９を介して複数の冷暖房用の利用側ユニット１０
がつながれ、熱移動サイクルが形成されている。そし
て、この熱移動サイクルの内部には、蒸気密度の大きい
フロンＲ４０４ＡからなるＨＦＣ系の冷媒が封入されて
いる。The chiller / heater 3 has a plurality of cooling / heating use side units 10 via a refrigerant liquid pipe 7 and a refrigerant gas pipe 9.
Are connected to form a heat transfer cycle. An HFC-based refrigerant made of Freon R404A having a high vapor density is sealed in the heat transfer cycle.
【００１３】このフロンＲ４０４Ａは、Ｒ１２５（ＣＨ
Ｆ2ＣＦ3；ペンタフロロエタン）と、Ｒ１４３ａ（ＣＨ
3ＣＦ3；トリフロロエタン）と、Ｒ１３４ａ（ＣＨ2Ｆ
ＣＦ3；テトラフロロエタン）とからなり、その成分比
率は、Ｒ１２５／Ｒ１４３ａ／Ｒ１３４ａ＝４４／５２
／４ｗｔ％である。This Freon R404A is composed of R125 (CH
F 2 CF 3 ; pentafluoroethane) and R143a (CH
3 CF 3 ; trifluoroethane) and R134a (CH 2 F)
CF 3 ; tetrafluoroethane), and the component ratio is R125 / R143a / R134a = 44/52.
/ 4 wt%.
【００１４】前記利用側ユニット１０には、利用側熱交
換器１１が収納されている。この利用側熱交換器１１
は、熱源側熱交換器５が凝縮器となる場合には蒸発器と
なり、蒸発器となる場合には凝縮器となる。１３は冷媒
調整弁、１５は冷暖房切換弁、１７はブースタポンプ、
１８は暖房時に運転されるポンプユニットである。The use side unit 10 houses a use side heat exchanger 11. This use side heat exchanger 11
Is an evaporator when the heat source side heat exchanger 5 is a condenser, and is a condenser when it is an evaporator. 13 is a refrigerant regulating valve, 15 is a cooling / heating switching valve, 17 is a booster pump,
Reference numeral 18 denotes a pump unit that operates during heating.
【００１５】このシステムでは、冷温水機３は、例えば
ビルの屋上などの高所に配置され、利用側ユニット１０
は、冷温水機３よりも低いビルの各室に配置され、前記
ポンプユニット１８は、利用側ユニット１０よりも更に
低所に配置される。In this system, the chiller / heater 3 is disposed at a high place such as the roof of a building,
Are disposed in each room of the building lower than the chiller / heater 3, and the pump unit 18 is disposed further lower than the use side unit 10.
【００１６】この自然循環式システムの動作を説明す
る。The operation of the natural circulation system will be described.
【００１７】冷房運転時には、熱源機１が運転して、冷
温水機３には冷水が与えられる。すると、この冷温水機
３に収容される熱源側熱交換器５では、フロンＲ４０４
Ａからなる冷媒が凝縮し、比重の大きい液冷媒となっ
て、冷媒液管７を通じて冷媒の自重により高所より低所
に、すなわち冷媒調整弁１３を経て、利用側ユニット１
０に流れる。この時、冷暖房切換弁１５の弁開度は全開
である。During the cooling operation, the heat source unit 1 is operated, and the cold / hot water unit 3 is supplied with cold water. Then, in the heat source-side heat exchanger 5 housed in the water heater / heater 3, Freon R404
A is condensed to become a liquid refrigerant having a large specific gravity, and is moved from a higher place to a lower place by a refrigerant's own weight through the refrigerant liquid pipe 7, that is, through the refrigerant regulating valve 13, and the use side unit 1
Flows to zero. At this time, the opening degree of the cooling / heating switching valve 15 is fully open.
【００１８】冷媒調整弁１３で冷媒量を適正に調整され
た冷媒は、利用側ユニット１０の利用側熱交換器１１に
流入し、この利用側熱交換器１１では液冷媒が蒸発し、
被調和室が冷房される。この過程では、液冷媒は比重の
極めて小さなガス冷媒となり、このガス冷媒は自重の軽
さゆえに、冷温水機３の熱源側熱交換器５に冷媒ガス管
９を通じて戻される。すなわちこのシステムでは、フロ
ンＲ４０４Ａからなる冷媒が熱移動サイクル内で気液相
変化することにより、自然循環することになる。The refrigerant whose amount has been properly adjusted by the refrigerant regulating valve 13 flows into the use side heat exchanger 11 of the use side unit 10, where the liquid refrigerant evaporates,
The conditioned room is cooled. In this process, the liquid refrigerant becomes a gas refrigerant having a very small specific gravity, and the gas refrigerant is returned to the heat source side heat exchanger 5 of the water heater 3 through the refrigerant gas pipe 9 because of its light weight. That is, in this system, the refrigerant composed of Freon R404A naturally circulates due to the gas-liquid phase change in the heat transfer cycle.
【００１９】暖房運転時には、図２を参照して、冷暖房
切換弁１５が全閉にされる。また、熱源機１が運転し
て、冷温水機３には温水が与えられる。During the heating operation, referring to FIG. 2, the cooling / heating switching valve 15 is fully closed. In addition, the heat source unit 1 is operated, and the hot and cold water machine 3 is supplied with hot water.
【００２０】すると、冷温水機３に収容される熱源側熱
交換器５では、フロンＲ４０４Ａからなる冷媒が蒸発
し、比重の極めて小さいガス冷媒となって、冷媒ガス管
９を通じて、冷媒の自重により利用側ユニット１０に流
れる。この利用側ユニット１０の利用側熱交換器１１で
は、フロンＲ４０４Ａからなる冷媒が凝縮し、これによ
り被調和室が暖房される。この過程では、ガス冷媒は比
重の大きい液冷媒となり、この液冷媒は、前述した冷媒
液管７、及び分岐管７ａを通じて、自重によりポンプユ
ニット１８に流れる。このポンプユニット１８は、レシ
ーバタンク２１とポンプ２３とを有し、レシーバタンク
２１に溜まり込む液冷媒は、ポンプ２３により汲み上げ
られて、熱源側熱交換器５に戻される。Then, in the heat source side heat exchanger 5 housed in the chiller / heater 3, the refrigerant composed of Freon R404A evaporates and becomes a gas refrigerant having a very small specific gravity. It flows to the use side unit 10. In the use side heat exchanger 11 of the use side unit 10, the refrigerant composed of Freon R404A is condensed, and thereby the conditioned room is heated. In this process, the gas refrigerant becomes a liquid refrigerant having a large specific gravity, and the liquid refrigerant flows to the pump unit 18 by its own weight through the refrigerant liquid pipe 7 and the branch pipe 7a. The pump unit 18 has a receiver tank 21 and a pump 23, and the liquid refrigerant accumulated in the receiver tank 21 is pumped up by the pump 23 and returned to the heat source side heat exchanger 5.
【００２１】この実施の形態によれば、熱移動サイクル
内に封入される冷媒がフロンＲ４０４Ａであるため、フ
ロンＲ１３４ａ（ＣＨ2ＦＣＦ3；テトラフロロエタン）
が封入される場合に比べて、図３に示すように、冷媒が
７℃蒸発した時の密度を示す「蒸気密度」が１８．０６
Ｋｇ／ｍ3から３７．２７Ｋｇ／ｍ3に、即ち約２倍にな
る。従って、従来のようにフロンＲ１３４ａを使用する
場合に比べて、冷媒ガス管９を通過する冷媒の圧損は小
さくなる。According to this embodiment, since the refrigerant sealed in the heat transfer cycle is Freon R404A, Freon R134a (CH 2 FCF 3 ; tetrafluoroethane)
As shown in FIG. 3, the “vapor density” indicating the density when the refrigerant evaporates at 7 ° C. is 18.06, as compared with the case where
From kg / m 3 to 37.27 Kg / m 3, that is, about twice. Therefore, the pressure loss of the refrigerant passing through the refrigerant gas pipe 9 is smaller than in the case where the Freon R134a is used as in the related art.
【００２２】これによれば、従来のものに比べて「蒸気
密度」が大きくなる分だけ、圧損が減少するので、フロ
ンＲ１３４ａを使用する場合に比べて、冷媒ガス管９の
管径を小さく（例えば、φ４４．５ｍｍ）することがで
きる。According to this, the pressure loss is reduced as much as the "steam density" is increased as compared with the conventional one, so that the pipe diameter of the refrigerant gas pipe 9 is reduced as compared with the case where Freon R134a is used. For example, φ44.5 mm).
【００２３】従って、冷媒ガス管９の配管サイズが小さ
くなる分だけ、配管施工などの工事が容易になり、施工
費用が安くなるとともに、まったく同様の理由から、蒸
発器（利用側熱交換器１１）のパス数を減少することが
できるので、蒸発器の設計自由度を向上させることがで
きる。Accordingly, since the pipe size of the refrigerant gas pipe 9 is reduced, the work such as piping work is facilitated, the construction cost is reduced, and for exactly the same reason, the evaporator (use side heat exchanger 11) is used. ) Can be reduced, so that the degree of freedom in designing the evaporator can be improved.
【００２４】このような自然循環システムでは、液冷媒
とガス冷媒の比重の差に従ってサイクル内における冷媒
を自然循環させる。従って、本来であれば、冷房運転時
には循環用ポンプなどは不要である。しかし、この自然
循環システムを施工するに当たり、凝縮器と蒸発器との
間に落差をとりにくい場合がある。この場合に、一つの
例として、０．５ｋｇ／ｃｍ2程度のブースタポンプ１
７が用いられる。In such a natural circulation system, the refrigerant in the cycle is naturally circulated according to the difference in specific gravity between the liquid refrigerant and the gas refrigerant. Therefore, a circulating pump or the like is not required during the cooling operation. However, when implementing this natural circulation system, it may be difficult to make a drop between the condenser and the evaporator. In this case, as one example, a booster pump 1 of about 0.5 kg / cm 2 is used.
7 is used.
【００２５】[0025]
【発明の効果】本発明によれば、熱移動サイクル内にフ
ロンＲ４０４Ａからなる冷媒が封入されるので、フロン
Ｒ１３４ａが封入される場合に比べて、冷媒が蒸発した
時の密度を示す「蒸気密度」が大きくなる。従って、フ
ロンＲ１３４ａを使用する場合に比べて、冷媒ガス管を
通過する冷媒の圧損は小さくなるので、その分だけ、冷
媒ガス管の管径を小さくすることができ、配管施工など
の工事が容易になり、施工費用が抑制されるとともに、
同様の理由から、蒸発器のパス数を減少することができ
るので、蒸発器の設計自由度を向上させることができ
る。According to the present invention, since the refrigerant composed of Freon R404A is sealed in the heat transfer cycle, the "vapor density" indicating the density when the refrigerant evaporates is compared with the case where Freon R134a is sealed. Is larger. Therefore, the pressure loss of the refrigerant passing through the refrigerant gas pipe is smaller than in the case where Freon R134a is used, so that the pipe diameter of the refrigerant gas pipe can be reduced by that much, facilitating construction such as piping work. And the construction cost is reduced,
For the same reason, the number of passes of the evaporator can be reduced, so that the degree of freedom in designing the evaporator can be improved.
【図１】本発明による自然循環式熱移動装置の一実施の
形態を示す回路図である。FIG. 1 is a circuit diagram showing an embodiment of a natural circulation heat transfer device according to the present invention.
【図２】同じく回路図である。FIG. 2 is a circuit diagram of the same.
【図３】飽和蒸気圧と蒸気密度との関係を示す図であ
る。FIG. 3 is a diagram showing a relationship between a saturated vapor pressure and a vapor density.
１ 熱源機 ３ 冷温水機 ５ 熱源側熱交換器（凝縮器） ７ 冷媒液管 ９ 冷媒ガス管 １０ 利用側ユニット １１ 利用側熱交換器（蒸発器） １３ 冷媒調整弁 １５ 冷暖房切換弁 １７ ブースタポンプ １８ ポンプユニット REFERENCE SIGNS LIST 1 heat source unit 3 chiller / heater 5 heat source side heat exchanger (condenser) 7 refrigerant liquid pipe 9 refrigerant gas pipe 10 user side unit 11 user side heat exchanger (evaporator) 13 refrigerant adjustment valve 15 air conditioning switching valve 17 booster pump 18 Pump unit
Claims (3)
蒸発器の間を冷媒液管、及び冷媒ガス管でつないで熱移
動サイクルを形成し、この熱移動サイクル内には冷媒を
封入した自然循環式熱移動装置において、 前記冷媒には、蒸気密度の大きいフロンＲ４０４Ａから
なる冷媒を選択し、この蒸気密度の大きい冷媒を気液相
変化させることにより当該冷媒を前記熱移動サイクル内
で自然循環させることを特徴とする自然循環式熱移動装
置。1. A condenser, comprising: a condenser and an evaporator;
A refrigerant liquid pipe and a refrigerant gas pipe are connected between evaporators to form a heat transfer cycle, and in this heat transfer cycle, in a natural circulation heat transfer device in which a refrigerant is sealed, the refrigerant has a vapor density of A natural-circulation heat transfer apparatus characterized in that a refrigerant composed of a large Freon R404A is selected, and the refrigerant having a high vapor density is changed in gas-liquid phase so that the refrigerant is naturally circulated in the heat transfer cycle.
蒸発器の間を冷媒液管、及び冷媒ガス管でつないで熱移
動サイクルを形成し、この熱移動サイクル内には冷媒を
封入した自然循環式熱移動装置において、 前記冷媒には、蒸気密度の大きいフロンＲ４０４Ａから
なる冷媒を選択し、この蒸気密度の大きい冷媒を気液相
変化させることにより当該冷媒を前記熱移動サイクル内
で自然循環させ、且つ冷媒ガス管の管径を小さく、及び
／又は蒸発器のパス数を少なく設定したことを特徴とす
る自然循環式熱移動装置。2. The method according to claim 1, further comprising a condenser and an evaporator.
A refrigerant liquid pipe and a refrigerant gas pipe are connected between evaporators to form a heat transfer cycle, and in this heat transfer cycle, in a natural circulation heat transfer device in which a refrigerant is sealed, the refrigerant has a vapor density of A refrigerant composed of a large Freon R404A is selected, and the refrigerant having a high vapor density undergoes a gas-liquid phase change, whereby the refrigerant is naturally circulated in the heat transfer cycle, and the diameter of the refrigerant gas pipe is reduced, and / or A natural circulation heat transfer device characterized in that the number of passes of the evaporator is set small.
ンプを備えたことを特徴とする請求項１又は２に記載の
自然循環式熱移動装置。3. The natural circulation heat transfer device according to claim 1, further comprising a booster pump for circulating the refrigerant.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8286008A JPH10110976A (en) | 1996-10-08 | 1996-10-08 | Natural circulating type heat transfer device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8286008A JPH10110976A (en) | 1996-10-08 | 1996-10-08 | Natural circulating type heat transfer device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH10110976A true JPH10110976A (en) | 1998-04-28 |
Family
ID=17698814
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8286008A Pending JPH10110976A (en) | 1996-10-08 | 1996-10-08 | Natural circulating type heat transfer device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH10110976A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011510248A (en) * | 2008-01-11 | 2011-03-31 | ジョンソン コントロールズ テクノロジー カンパニー | Vapor compression system |
| CN105333543A (en) * | 2015-07-03 | 2016-02-17 | 方颖 | Multifunctional central air-conditioning system and running control method thereof |
| JP2020012610A (en) * | 2018-07-19 | 2020-01-23 | 株式会社デンソー | Air conditioner |
-
1996
- 1996-10-08 JP JP8286008A patent/JPH10110976A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011510248A (en) * | 2008-01-11 | 2011-03-31 | ジョンソン コントロールズ テクノロジー カンパニー | Vapor compression system |
| JP2013092365A (en) * | 2008-01-11 | 2013-05-16 | Johnson Controls Technology Co | Vapor compression system |
| US10317117B2 (en) | 2008-01-11 | 2019-06-11 | Johnson Controls Technology Company | Vapor compression system |
| CN105333543A (en) * | 2015-07-03 | 2016-02-17 | 方颖 | Multifunctional central air-conditioning system and running control method thereof |
| JP2020012610A (en) * | 2018-07-19 | 2020-01-23 | 株式会社デンソー | Air conditioner |
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