JPH0719627A - Heat exchanger for non-azeotrope refrigerant - Google Patents
Heat exchanger for non-azeotrope refrigerantInfo
- Publication number
- JPH0719627A JPH0719627A JP16126293A JP16126293A JPH0719627A JP H0719627 A JPH0719627 A JP H0719627A JP 16126293 A JP16126293 A JP 16126293A JP 16126293 A JP16126293 A JP 16126293A JP H0719627 A JPH0719627 A JP H0719627A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat exchanger
- tube
- pipe
- azeotropic mixed
- 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
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、冷媒としてフロンＲ２
２に替えて非共沸の混合冷媒を用いる熱交換器に関す
る。BACKGROUND OF THE INVENTION The present invention relates to Freon R2 as a refrigerant.
The present invention relates to a heat exchanger using a non-azeotropic mixed refrigerant instead of 2.
【０００２】[0002]
【従来の技術】従来、フロンＲ２２(ＣＨＣlＦ2)を冷媒
に用い、冷暖房運転と除湿運転が可能な空気調和装置と
して、例えば図５に示すようなものが知られている。こ
の空気調和装置は、圧縮機３１,四路切換弁３２,室外熱
交換器３３,膨張弁３４および室内熱交換器３５を順次
管路３６a〜３６fで接続している。室内熱交換器３５
は、除湿運転を可能にすべく第１,第２の熱交換器３５
a,３５bに分割され、両熱交換器３５a,３５bの間に、キ
ャピラリチューブ３８と開閉弁３９を互いに並列接続し
てなるドライ時減圧機構３７を介設するとともに、電磁
弁４１を介設したバイパス管路４０により、圧縮機３１
の吐出口側の管路３６aと、膨張弁３４と第１室内熱交
換器３５aの間の管路３６dとを接続している。上記開閉
弁３９は、詳細は図示しないが、弁室内に摺動自在に嵌
装した弁体を、低温,高温冷媒に接して夫々収縮,伸長す
る形状記憶ばねにより、弁座に向けて付勢してなり、冷
暖房運転の際に開成し、除湿運転の際に閉成する。 2. Description of the Related Art Conventionally, an air conditioner as shown in FIG. 5, for example, is known as an air conditioner which uses Freon R22 (CHClF 2 ) as a refrigerant and is capable of cooling and heating operation and dehumidifying operation. In this air conditioner, a compressor 31, a four-way switching valve 32, an outdoor heat exchanger 33, an expansion valve 34 and an indoor heat exchanger 35 are sequentially connected by pipelines 36a to 36f. Indoor heat exchanger 35
Is the first and second heat exchangers 35 to enable the dehumidifying operation.
It is divided into a and 35b, and a dry decompression mechanism 37 in which a capillary tube 38 and an on-off valve 39 are connected in parallel to each other is provided between both heat exchangers 35a and 35b, and an electromagnetic valve 41 is provided. Bypass line 40 allows compressor 31
The discharge passage side pipe 36a is connected to the pipe 36d between the expansion valve 34 and the first indoor heat exchanger 35a. Although not shown in detail, the on-off valve 39 urges a valve body slidably fitted in a valve chamber toward a valve seat by a shape memory spring that contracts and expands in contact with a low temperature refrigerant and a high temperature refrigerant, respectively. It opens during air-conditioning operation and closes during dehumidification operation.
【０００３】上記空気調和装置において、冷房運転を行
なうには、電磁弁４１を閉じ、膨張弁３４を所定開度に
して、圧縮機３１から吐出された冷媒を、図５の実線矢
印の如く循環させ、室外熱交換器３３で凝縮させた後、
室内熱交換器３５で蒸発させる。このとき、第１,第２
の室内熱交換器３５a,３５bの間の開閉弁３９は、実線
矢印の如く流入する低温冷媒により開成し、両熱交換器
３５a,３５bが、共に蒸発器として働いて、室内を冷房
する。逆に、暖房運転を行なうには、四路切換弁３２を
切り換えて吐出冷媒を、図５の破線矢印のように循環さ
せる。すると、開閉弁３９は、破線矢印に如く流入する
高温冷媒で形状記憶ばねが伸長するが、弁体の上下流間
の圧力差とバイアスばねの力により開成し、両熱交換器
３５a,３５bが、共に凝縮器として働いて、室内を暖房
する。In the above air conditioner, in order to perform the cooling operation, the electromagnetic valve 41 is closed, the expansion valve 34 is opened to a predetermined opening, and the refrigerant discharged from the compressor 31 is circulated as indicated by the solid arrow in FIG. And after condensing with the outdoor heat exchanger 33,
It is evaporated in the indoor heat exchanger 35. At this time, the first and second
The on-off valve 39 between the indoor heat exchangers 35a, 35b is opened by the low temperature refrigerant flowing in as indicated by the solid line arrow, and both heat exchangers 35a, 35b work as an evaporator to cool the room. On the contrary, in order to perform the heating operation, the four-way switching valve 32 is switched to circulate the discharged refrigerant as shown by the broken line arrow in FIG. Then, in the on-off valve 39, the shape memory spring expands due to the high-temperature refrigerant flowing in as indicated by the broken line arrow, but the shape difference spring is opened by the pressure difference between the upstream and downstream of the valve body and the force of the bias spring, and the two heat exchangers 35a and 35b are opened. , Work together as a condenser to heat the room.
【０００４】一方、除湿運転の際は、膨張弁３４を全閉
にし、電磁弁４１を開いてバイパス管路４０を経て圧縮
機３１からの高温の冷媒ガスを、図５の一点鎖線矢印の
如く第１室内熱交換器３５aに直接圧送する。すると、
開閉弁３９は、高温冷媒による形状記憶ばねの伸長と弁
体の上下流間の圧力差によって閉成する。これにより、
冷媒は、総てキャピラリチューブ３８を流れてここで膨
張,減圧されるので、上流側の第１室内熱交換器３５aが
凝縮器として、下流側の第２室内熱交換器３５bが蒸発
器として夫々働く。そして、図示しない室内ファンで循
環せしめられる室内空気は、まず第２熱交換器３５bを
通って冷却されて除湿され、次いで第１熱交換器３５a
を通って室温程度まで加熱されて除湿空気となる。On the other hand, during the dehumidifying operation, the expansion valve 34 is fully closed, the electromagnetic valve 41 is opened, and the high temperature refrigerant gas from the compressor 31 is passed through the bypass pipe 40, as shown by the one-dot chain line arrow in FIG. The pressure is directly fed to the first indoor heat exchanger 35a. Then,
The on-off valve 39 is closed by the expansion of the shape memory spring by the high temperature refrigerant and the pressure difference between the upstream and downstream of the valve element. This allows
Since all the refrigerant flows through the capillary tube 38 and is expanded and depressurized here, the upstream first indoor heat exchanger 35a serves as a condenser and the downstream second indoor heat exchanger 35b serves as an evaporator. work. The indoor air circulated by an indoor fan (not shown) is first cooled through the second heat exchanger 35b to be dehumidified, and then the first heat exchanger 35a.
It is heated up to about room temperature and becomes dehumidified air.
【０００５】[0005]
【発明が解決しようとする課題】図６は、上述の暖房運
転時における蒸発器となる室外熱交換器３３の冷媒配管
に沿った冷媒Ｒ２２の温度および圧力損失の分布を、白
丸を連ねた直線Ｌ1,Ｌ2で夫々示している。図中の直線
Ｌ1から判るように、単一組成の冷媒Ｒ２２の蒸発温度
は、上記冷媒配管の入口から出口に向かって低下し、圧
力損失も図中の直線Ｌ2の如く出口に向かって僅に低下
する。また、冷媒配管の外部に沿って流れる吸込空気の
温度は、図中の直線Ｌ3の如く配管出口に向かって低下
する。ところで、最近、フロンＲ２２等の冷媒は、オゾ
ン層を破壊することから大きな環境問題を生じており、
これに替わる有力な冷媒として、例えばＲ３２／Ｒ１３
４aの２種、あるいはＲ３２／Ｒ１３４a／Ｒ１２５の３
種の冷媒を混合した非共沸の混合冷媒が注目されてい
る。FIG. 6 shows the distribution of the temperature and pressure loss of the refrigerant R22 along the refrigerant pipe of the outdoor heat exchanger 33 serving as the evaporator during the heating operation described above, which is a straight line with white circles. L 1 and L 2 are shown respectively. As can be seen from the straight line L 1 in the figure, the evaporation temperature of the single composition refrigerant R22 decreases from the inlet to the outlet of the refrigerant pipe, and the pressure loss also moves toward the outlet as the straight line L 2 in the figure. Slightly lower. Further, the temperature of the suction air flowing along the outside of the refrigerant pipe decreases toward the pipe outlet as indicated by a straight line L 3 in the figure. By the way, recently, refrigerants such as Freon R22 have caused a great environmental problem because they destroy the ozone layer.
As a powerful alternative to this, for example, R32 / R13
2 of 4a or 3 of R32 / R134a / R125
Non-azeotropic mixed refrigerants in which different kinds of refrigerants are mixed have attracted attention.
【０００６】ところが、これらの非共沸混合冷媒は、組
成冷媒が任意の混合比で混じり合う全率可溶混合物で、
組成を横軸,温度を縦軸にとった平衡状態図が、上側の
気相線と下側の液相線とでレンズ状を呈するものであ
り、単一組成のＲ２２とは物性が著しく異なる。そのた
め、上記非共沸混合冷媒をそのまま図５の空気調和装置
に用いると、暖房運転時における室外熱交換器３３での
冷媒の蒸発温度は、ＪＩＳで規定される暖房条件(外気
乾球温度７℃,外気湿球温度６℃、室温２０℃)下でも、
図６の黒丸を連ねた直線Ｌ1'で示すように、冷媒配管の
入口側で低くて図中のハッチングで示す着霜域に入り、
出口に向かって上昇する。なお、上記非共沸混合冷媒の
圧力損失は、図中の直線Ｌ2'の如く、物性値の差により
直線Ｌ2で示すＲ２２に比して小さい。 従って、ＪＩ
Ｓの暖房条件下でも室外熱交換器３３の入口側で凍結,
着霜が生じるばかりでなく、出口に向かうほど空気温度
Ｌ3と冷媒の蒸発温度Ｌ1'との温度差が取れない、つま
り対数平均温度差が小さくなるため、蒸発熱交換性能が
低下し、圧縮機３１がインバータ式の場合には、動作係
数が低下するという問題がある。However, these non-azeotropic mixed refrigerants are all-soluble mixtures in which the composition refrigerants are mixed at an arbitrary mixing ratio,
The equilibrium diagram with composition on the horizontal axis and temperature on the vertical axis shows a lens shape between the upper vapor phase line and the lower liquidus line, and the physical properties are significantly different from R22 of a single composition. . Therefore, when the above non-azeotropic mixed refrigerant is used as it is in the air conditioner of FIG. 5, the evaporation temperature of the refrigerant in the outdoor heat exchanger 33 during the heating operation is the heating condition (the outside air dry bulb temperature 7 ℃, outside air wet bulb temperature 6 ℃, room temperature 20 ℃),
As shown by the straight line L 1 'that connects the black circles in FIG. 6, the temperature is low at the inlet side of the refrigerant pipe and enters the frosted region indicated by the hatching in the figure,
Ascend to the exit. The pressure loss of the non-azeotropic mixed refrigerant is smaller than that of R22 indicated by the straight line L 2 due to the difference in the physical properties, as indicated by the straight line L 2 ′ in the figure. Therefore, JI
Even under the heating condition of S, freezing at the inlet side of the outdoor heat exchanger 33,
Not only does frost form, but a temperature difference between the air temperature L 3 and the evaporation temperature L 1 ′ of the refrigerant cannot be taken toward the outlet, that is, the logarithmic average temperature difference is small, so the evaporation heat exchange performance is deteriorated, When the compressor 31 is an inverter type, there is a problem that the coefficient of operation is lowered.
【０００７】そこで、本発明の目的は、非共沸混合冷媒
の非等温性をうまく利用して、熱交換器の配管に沿う冷
媒蒸発温度の分布を略均一にすることによって、凍結,
着霜を回避し、熱交換性能と動作係数の向上を図ること
ができる非共沸混合冷媒用の熱交換器を提供することに
ある。Therefore, an object of the present invention is to make good use of the non-isothermal property of the non-azeotropic mixed refrigerant to make the distribution of the refrigerant evaporation temperature along the pipe of the heat exchanger substantially uniform, thereby freezing,
It is an object of the present invention to provide a heat exchanger for a non-azeotropic mixed refrigerant capable of avoiding frost formation and improving the heat exchange performance and the coefficient of operation.
【０００８】[0008]
【課題を解決するための手段】上記目的を達成するた
め、本発明の非共沸混合冷媒用の熱交換器１は、図１に
例示するように、非共沸の混合冷媒が貫流する配管に沿
って、冷媒入口から冷媒出口に向かう冷媒の蒸発温度の
分布が、略均一または出口側に向かって低下するよう
に、上記配管の中間部４に、流路断面積が減少する狭窄
部２a,２b;３a,３b;５;７を設けたことを特徴とする。In order to achieve the above object, a heat exchanger 1 for a non-azeotropic mixed refrigerant of the present invention has a pipe through which a non-azeotropic mixed refrigerant flows, as illustrated in FIG. The narrowed portion 2a in which the flow passage cross-sectional area decreases in the intermediate portion 4 of the pipe so that the distribution of the evaporation temperature of the refrigerant flowing from the refrigerant inlet to the refrigerant outlet along the pipe is substantially uniform or decreases toward the outlet side. , 2b; 3a, 3b; 5; 7 are provided.
【０００９】上記狭窄部を、図１(Ａ)に例示するよう
に、２分割された熱交換器の前部１aと後部１bを接続す
る配管４に介設された膨張弁２a,２bで構成してもよ
い。また、上記狭窄部を、図２(Ｂ),(Ｃ)に例示するよ
うに、上記熱交換器１の配管の中間部４に作り込まれた
キャピラリチューブ３a,３bまたはオリフィス５で構成
してもよい。さらに、上記狭窄部を、図３(Ａ)に例示す
るように、冷媒入口側の所定径の第１チューブ６から複
数に分岐する第１チューブ６よりも細径の第２チューブ
７と、この第２チューブ７より細径で、各第２チューブ
７の先端から複数に分岐した後に冷媒出口側の所定径の
第４チューブ１０に合流する第３チューブ８で構成し、
蒸発しつつ出口側に向かって流れる非共沸混合冷媒に対
する実質的な流路断面が、夫々上記第１チューブ６で
大,第２チューブ７で小,第３チューブ８で中になるよう
にすることもできる。As shown in FIG. 1 (A), the narrowed portion is constituted by expansion valves 2a and 2b provided in a pipe 4 connecting a front portion 1a and a rear portion 1b of a heat exchanger divided into two parts. You may. In addition, as shown in FIGS. 2 (B) and 2 (C), the narrowed portion is constituted by the capillary tubes 3a, 3b or the orifice 5 built in the intermediate portion 4 of the pipe of the heat exchanger 1. Good. Further, as shown in FIG. 3 (A), the narrowed portion includes a second tube 7 having a diameter smaller than that of the first tube 6 branched from the first tube 6 having a predetermined diameter on the refrigerant inlet side, The third tube 8 has a smaller diameter than the second tubes 7 and is branched into a plurality of tips from the respective second tubes 7 and then joins with a fourth tube 10 having a predetermined diameter on the refrigerant outlet side.
The substantial flow passage cross sections for the non-azeotropic mixed refrigerant flowing toward the outlet side while evaporating are set such that the first tube 6 is large, the second tube 7 is small, and the third tube 8 is medium. You can also
【００１０】[0010]
【作用】冷媒配管の中間部４に狭窄部２a,２b;３a,３b;
５;７を設けた熱交換器を室外熱交換器１とし、圧縮機
３１から吐出した非共沸の混合冷媒ガスを、室内熱交換
器３５で凝縮させ、膨張弁３４を経て絞り膨張させて上
記室外熱交換器１にて蒸発させ、圧縮機３１へ循環させ
る。絞り膨張後に室外熱交換器１の配管入口に達した冷
媒の状態は、上に凸な飽和限界線をもつこの冷媒のＰ-h
線図中で台形をなす冷凍サイクル線図上の左下隅に相当
する。しかし、蒸発器である室外熱交換器１には、中間
部４に流路断面積が減少する狭窄部２a,２b;３a,３b;
５;７があるので、上記左下隅からの蒸発過程は通常の
冷凍サイクル線図のように水平線とはならず、右下がり
の線となって、圧力は入口側で高く,出口側で低くな
る。従って、圧力に相当する冷媒の飽和温度も、入口側
で高く,出口側で低くなって、入口側は湿り気味の,出口
側は乾き気味の冷媒状態となる。その結果、上記狭窄部
２a,２b;３a,３b;５;７がなければ、ＪＩＳの暖房条件
下でも配管入口側が着霜温度以下になり,出口側に向か
って上昇する冷媒温度の分布が、略均一または出口側に
向かって低下するようになって、室外熱交換器１の入口
側での凍結,着霜が防止され、熱交換性能と動作係数の
向上が図られる。Function: Constrictions 2a, 2b; 3a, 3b;
The heat exchanger provided with 5 and 7 is used as the outdoor heat exchanger 1, the non-azeotropic mixed refrigerant gas discharged from the compressor 31 is condensed in the indoor heat exchanger 35, and expanded and expanded through the expansion valve 34. It is evaporated in the outdoor heat exchanger 1 and circulated to the compressor 31. The state of the refrigerant that has reached the pipe inlet of the outdoor heat exchanger 1 after the expansion by expansion is Ph of this refrigerant having an upwardly convex saturation limit line.
It corresponds to the lower left corner of the trapezoidal refrigeration cycle diagram. However, in the outdoor heat exchanger 1 which is an evaporator, the narrowed portions 2a, 2b; 3a, 3b;
Since there are 5 and 7, the evaporation process from the lower left corner does not become a horizontal line like the normal refrigeration cycle diagram, but becomes a line descending to the right, the pressure is high on the inlet side and low on the outlet side. . Therefore, the saturation temperature of the refrigerant, which corresponds to the pressure, is also high on the inlet side and low on the outlet side, so that the inlet side is in a wet state and the outlet side is in a dry state. As a result, if the narrowed portions 2a, 2b; 3a, 3b; 5; 7 are not present, the distribution of the refrigerant temperature that is below the frosting temperature on the pipe inlet side and rises toward the outlet side even under the JIS heating condition is By becoming substantially uniform or decreasing toward the outlet side, freezing and frost formation at the inlet side of the outdoor heat exchanger 1 are prevented, and the heat exchange performance and the coefficient of operation are improved.
【００１１】上記狭窄部を、２分割された熱交換器の前
部１aと後部１bを接続する配管４に介設した膨張弁２a,
２bで構成すれば、使用する非共沸混合冷媒の種類に応
じて膨張弁２a,２bの開度を最適に調整でき、汎用性に
優れる。上記狭窄部を、熱交換器１の配管の中間部４に
作り込まれたキャピラリチューブ３a,３bまたはオリフ
ィス５で構成すれば、汎用性には劣るが、熱交換器のコ
ンパクト化を図ることができる。また、上記狭窄部を、
種々の径,本数の第１〜第４チューブ６〜１０を組み合
わせて構成すれば、コンパクト化を図りつつ、種々の非
共沸混合冷媒に適合させることができる。An expansion valve 2a, in which the narrowed portion is provided in a pipe 4 connecting the front portion 1a and the rear portion 1b of the heat exchanger divided into two parts.
If it is constituted by 2b, the opening degree of the expansion valves 2a, 2b can be optimally adjusted according to the type of the non-azeotropic mixed refrigerant used, and it is excellent in versatility. If the narrowed portion is composed of the capillary tubes 3a, 3b or the orifice 5 formed in the intermediate portion 4 of the pipe of the heat exchanger 1, the versatility is poor, but the heat exchanger can be made compact. it can. In addition, the narrowed portion,
If the first to fourth tubes 6 to 10 having various diameters and numbers are combined and configured, it can be made compact and can be adapted to various non-azeotropic mixed refrigerants.
【００１２】[0012]
【実施例】以下、本発明を図示の実施例により詳細に説
明する。図１(Ａ)は、本発明の非共沸混合冷媒用の熱交
換器を室外熱交換器として用いた空気調和装置の一例を
示す冷媒回路図である。この空気調和装置は、図５で述
べた冷媒回路の室内熱交換器のドライ時減圧機構３７を
省略して単一の室内熱交換器３５とし、電磁弁４１を介
設したバイパス管路４０を省略する一方、図５の室外熱
交換器３３を前部１aと後部１bに分割し、両者１a,１b
の間に流路断面積が減少する狭窄部としての１対の膨張
弁２a,２bを並列に設けて室外熱交換器１を構成してい
る。その他の部材は、図５で述べたものと同じであり、
同じ部材に同一番号を付して説明を省略する。図１(Ｂ)
は、上記室外熱交換器の他の実施例を示しており、この
実施例では、室外熱交換器１の前部１aと後部１bの間
に、狭窄部として１対のキャピラリチューブ３a,３bを
並列に設けている。The present invention will be described in detail below with reference to the embodiments shown in the drawings. FIG. 1 (A) is a refrigerant circuit diagram showing an example of an air conditioner using the heat exchanger for non-azeotropic mixed refrigerant of the present invention as an outdoor heat exchanger. In this air conditioner, the dry-time depressurization mechanism 37 of the indoor heat exchanger of the refrigerant circuit described in FIG. 5 is omitted to form a single indoor heat exchanger 35, and the bypass pipe 40 having the solenoid valve 41 is provided. While omitting, the outdoor heat exchanger 33 of FIG. 5 is divided into a front part 1a and a rear part 1b, and
The outdoor heat exchanger 1 is configured by arranging a pair of expansion valves 2a and 2b, which are narrowed portions in which the cross-sectional area of the flow passage decreases, in parallel. The other members are the same as those described in FIG. 5,
The same members are designated by the same reference numerals and the description thereof is omitted. Figure 1 (B)
Shows another embodiment of the outdoor heat exchanger, and in this embodiment, a pair of capillary tubes 3a, 3b are provided as a narrowed portion between the front portion 1a and the rear portion 1b of the outdoor heat exchanger 1. They are provided in parallel.
【００１３】上記キャピラリチューブ３a,３bは、図２
（Ｃ)に示すような形状を有し、図１(Ａ)の膨張弁２a,
２bと異なり、室外熱交換器１を２分割することなく、
図２(Ａ)に示す冷媒配管の中間部４に埋め込んで設けら
れる。また、この中間部４に、狭窄部としてキャピラリ
チューブ３a,３bに代えて図２(Ｂ)に示すようなオリフ
ィス５を設けることもできる。The capillary tubes 3a and 3b are shown in FIG.
The expansion valve 2a of FIG. 1 (A) has a shape as shown in FIG.
Unlike 2b, without dividing the outdoor heat exchanger 1 into two
It is provided by being embedded in the intermediate portion 4 of the refrigerant pipe shown in FIG. Further, the intermediate portion 4 may be provided with an orifice 5 as shown in FIG. 2B instead of the capillary tubes 3a and 3b as a narrowed portion.
【００１４】図３(Ａ)は、狭窄部の他の実施例を示して
おり、この実施例では、室外熱交換器１の冷媒配管の入
口側を直径9.5mmの１本の第１チューブ６、中間部を２
本に分岐する直径8.0mmの第２チューブ７、ヘッダー９
の手前を直径７mmの４本の第３チューブ８、出口側を直
径9.5mmの１本の第４チューブ１０で夫々構成して、入
口から矢印の如く液成分に富んだ状態で流入し、蒸発し
つつ出口側に向かう非共沸混合冷媒に対して、実質的な
流路断面積が、夫々第１チューブ６で大,第２チューブ
７で小,第３チューブ８で中となるようにしている。そ
して、第４チューブ１０からは、ガス成分に富んだ非共
沸混合冷媒が矢印の如く流出する。図３(Ｂ)は、上記実
施例の変形例を示しており、この変形例では、室外熱交
換器１の外部を矢印Ａの如く流れる外気に対して、冷媒
を矢印Ｂの如く前面から背面に２列に循環させ、前面を
２本の直径７mmのチューブで、背面を１本の直径9.5mm
のチューブで夫々構成している。また、図３(Ｃ)の変形
例では、矢印Ａの如く流れる外気に対して、冷媒を矢印
Ｂの如く同様に前面から背面に２列に循環させ、かつ前
面,背面をともに下段と上段に分けて、各種直径のチュ
ーブを組み合わせて、実質的な流路断面積が、夫々前面
下段で大,前面と背面の上段で小,背面下段で中になるよ
うにしている。FIG. 3A shows another embodiment of the narrowed portion. In this embodiment, the inlet side of the refrigerant pipe of the outdoor heat exchanger 1 has one first tube 6 having a diameter of 9.5 mm. , Middle part 2
A second tube 7 with a diameter of 8.0 mm that branches into a book, a header 9
Is composed of four third tubes 8 with a diameter of 7 mm and one fourth tube 10 with a diameter of 9.5 mm on the outlet side, and flows in from the inlet in a state rich in liquid components as shown by the arrow and evaporates. For the non-azeotropic mixed refrigerant flowing toward the outlet side, the substantial flow passage cross-sectional areas are set to be large in the first tube 6, small in the second tube 7 and medium in the third tube 8, respectively. There is. Then, the non-azeotropic mixed refrigerant rich in gas components flows out from the fourth tube 10 as indicated by an arrow. FIG. 3 (B) shows a modified example of the above embodiment. In this modified example, with respect to the outside air flowing outside the outdoor heat exchanger 1 as indicated by arrow A, the refrigerant is changed from the front to the back as indicated by arrow B. 2 tubes with a diameter of 7 mm on the front side and a diameter of 9.5 mm on the back side.
Each is made up of tubes. Further, in the modified example of FIG. 3C, with respect to the outside air flowing as indicated by arrow A, the refrigerant is similarly circulated in two rows from the front surface to the back surface as shown by arrow B, and the front surface and the back surface are both in the lower and upper stages. Separately, tubes of various diameters are combined so that the substantial flow passage cross-sectional area is large in the front lower stage, small in the front and rear upper stages, and medium in the rear lower stage.
【００１５】上記各実施例の狭窄部２a,２b;３a,３b;
５;７を有する室外熱交換器１に、フロンＲ２２に代わ
って貫流する非共沸の混合冷媒は、Ｒ３２／Ｒ１３４a
の２種、またはＲ３２／Ｒ１３４a／Ｒ１２５の３種の
冷媒を混合したものであり、上記いずれの狭窄部の寸法
および形状も、その狭窄部をもつ冷媒配管に上記混合冷
媒を流したとき、この冷媒配管に沿って冷媒入口から冷
媒出口に向かう上記混合冷媒の蒸発温度の分布が、略均
一または出口側に向かって低下するように設計されてい
る(図４の直線Ｌ１参照)。また、膨張弁２a,２b(図１
(Ａ)参照)は、分離した前部１aと後部１bを継なぐ配管
の中間部４に介設された流路断面積が可変の狭窄部であ
り、非共沸混合冷媒の種類に合わせてその開度を調整で
きるが、残りのキャピラリチューブ３a,３b(図２(Ｃ)参
照)、オリフィス５(図２(Ｂ)参照)および組合せ配管(図
３(Ａ)参照)は、一体の熱交換器１の配管の中間部４に
埋め込まれた流路断面積が固定の狭窄部であり、使用で
きる非共沸混合冷媒の種類が限定される。The narrowed portions 2a, 2b; 3a, 3b;
The non-azeotropic mixed refrigerant that flows through the outdoor heat exchanger 1 having 5 and 7 instead of the fluorocarbon R22 is R32 / R134a.
2 or R32 / R134a / R125 three kinds of refrigerants are mixed, and the size and shape of any of the above constrictions are the same when the above mixed refrigerant is flown into the refrigerant pipe having the constriction. The distribution of the evaporation temperature of the mixed refrigerant flowing from the refrigerant inlet to the refrigerant outlet along the refrigerant pipe is designed to be substantially uniform or to decrease toward the outlet side (see the straight line L1 in FIG. 4). Further, the expansion valves 2a and 2b (see FIG.
(Refer to (A)) is a constriction part having a variable flow passage cross-sectional area, which is provided in an intermediate part 4 of a pipe connecting the separated front part 1a and rear part 1b. Although its opening can be adjusted, the remaining capillary tubes 3a and 3b (see FIG. 2C), the orifice 5 (see FIG. 2B) and the combination pipe (see FIG. 3A) are integrated into one unit. The flow passage cross-sectional area embedded in the intermediate portion 4 of the pipe of the exchanger 1 is a narrowed portion having a fixed flow passage area, and the types of non-azeotropic mixed refrigerant that can be used are limited.
【００１６】上記構成の非共沸混合冷媒用の熱交換器
は、次のように作用する。狭窄部として膨張弁２a,２b
をもつ室外熱交換器１を用いた図１(Ａ)に示す空気調和
装置において、膨張弁２a,２bの開度を使用する非共沸
混合冷媒に合わせて調整した後、図中の破線矢印で示す
ように、圧縮機３１から吐出した非共沸混合冷媒のガス
を、室内熱交換器３５で凝縮させ、膨張弁３４を経て絞
り膨張させて室外熱交換器１に送って蒸発させ、圧縮機
３１へ循環させて暖房運転を行なう。膨張弁３４での絞
り(等エンタルピ)膨張の後に室外熱交換器１aの配管入
口に達した冷媒の状態は、上に凸な飽和限界線をもつこ
の冷媒のＰ-h線図上で台形をなす冷凍サイクル線図上の
左下隅に相当する。しかし、蒸発器である室外熱交換器
１には、中間部４に流路断面積が減少する膨張弁２a,２
bがあるので、上記左下隅から右横へ向かう蒸発過程
は、通常の冷凍サイクル線図のように水平線とはなら
ず、右下がりの線となって、冷媒の蒸気圧は入口側で高
く,出口側で低くなる。従って、蒸気圧に相当する冷媒
の飽和温度も、入口側で高く,出口側で低くなって、入
口側は湿り気味,出口側は乾き気味の冷媒状態となる。The heat exchanger for a non-azeotropic mixed refrigerant having the above-described structure operates as follows. Expansion valves 2a, 2b as constrictions
In the air conditioner shown in FIG. 1 (A) using the outdoor heat exchanger 1 having the following, after adjusting the opening degree of the expansion valves 2a, 2b according to the non-azeotropic mixed refrigerant to be used, the broken line arrow in the figure As shown by, the gas of the non-azeotropic mixed refrigerant discharged from the compressor 31 is condensed in the indoor heat exchanger 35, and is squeezed and expanded through the expansion valve 34 to be sent to the outdoor heat exchanger 1 to be evaporated and compressed. The heating operation is performed by circulating the air to the machine 31. The state of the refrigerant that has reached the pipe inlet of the outdoor heat exchanger 1a after the expansion (isoenthalpy) expansion in the expansion valve 34 is trapezoidal on the Ph diagram of this refrigerant having a convex saturation limit line. It corresponds to the lower left corner of the eggplant refrigeration cycle diagram. However, in the outdoor heat exchanger 1 which is an evaporator, the expansion valves 2a, 2
Since there is b, the evaporation process from the lower left corner to the right side does not become a horizontal line like a normal refrigeration cycle diagram, but becomes a line descending to the right, and the vapor pressure of the refrigerant is high on the inlet side, It becomes lower on the exit side. Therefore, the saturation temperature of the refrigerant corresponding to the vapor pressure is also high on the inlet side and low on the outlet side, so that the inlet side is in a moist state and the outlet side is in a slightly dry state.
【００１７】その結果、膨張弁２a,２bがなければ、Ｊ
ＩＳの暖房条件(外気乾球温度７℃,外気湿球温度６℃、
室温２０℃)下でも配管入口側が、図４の直線Ｌ1'(図６
のＬ1')で示すように、ハッチング域の着霜温度以下に
なり、出口側に向かって上昇する冷媒温度の分布が、図
４の直線Ｌ１で示すように、略均一(水平)なって室外熱
交換器１の入口側での凍結,着霜が防止される。一方、
配管に沿う冷媒の圧力損失の分布は、図４の直線Ｌ２で
示すように、直線Ｌ2'で示す膨張弁２a,２bがない場合
よりも小さくなる。また、冷媒の温度分布Ｌ１が略均一
になるので、冷媒温度Ｌ１と空気温度Ｌ3との温度差,つ
まり対数平均温度差が、配管出口に向かってさほど減少
しないから、蒸発熱交換性能が向上し、インバータ式の
圧縮機３１の動作係数も上昇する。このように、代替の
ための非共沸混合冷媒は、従来の単一組成の冷媒Ｒ２２
に比べて、蒸発による圧力損失への影響が小さい反面、
物性による温度への影響が大きいので、この非等温性を
冷媒配管の中間部４に狭窄部を設けることによって利用
して、対数平均温度差を大きくとるように改善している
のである。さらに、キャピラリチューブ３a,３b(図２
(Ｃ)参照)、オリフィス５(図２(Ｂ)参照)および組合せ
配管(図３参照)からなる固定形の狭窄部の場合は、可変
形の膨張弁２a,２bに比して、使用冷媒が限定されると
いう不利はあるものの、一体の熱交換器１内に埋め込ん
でコンパクト化を図れるという利点がある。As a result, if there is no expansion valve 2a, 2b, J
IS heating conditions (outside air dry bulb temperature 7 ° C, outside air wet bulb temperature 6 ° C,
Even at room temperature of 20 ° C., the pipe inlet side is straight line L 1 ′ in FIG.
As shown by L 1 '), the distribution of the refrigerant temperature that becomes lower than the frosting temperature in the hatching area and rises toward the outlet side becomes substantially uniform (horizontal) as shown by the straight line L1 in FIG. Freezing and frost formation on the inlet side of the outdoor heat exchanger 1 are prevented. on the other hand,
The distribution of the pressure loss of the refrigerant along the pipe is smaller than that without the expansion valves 2a and 2b indicated by the straight line L 2 ′, as indicated by the straight line L2 in FIG. Further, since the temperature distribution L1 of the coolant is substantially uniform, the temperature difference between the refrigerant temperature L1 and air temperature L 3, i.e. the logarithmic mean temperature difference, do not decrease much towards the pipe outlet, improve evaporative heat exchange performance However, the operating coefficient of the inverter type compressor 31 also increases. As described above, the alternative non-azeotropic mixed refrigerant is the conventional single composition refrigerant R22.
Compared with, the effect of evaporation on pressure loss is small, but
Since the physical properties have a great influence on the temperature, this non-isothermal property is utilized by providing a narrowed portion in the intermediate portion 4 of the refrigerant pipe to improve the logarithmic average temperature difference. Further, the capillary tubes 3a and 3b (see FIG.
(See (C)), orifice 5 (see FIG. 2 (B)) and combination pipe (see FIG. 3), in the case of a fixed constriction part, compared to the variable expansion valves 2a, 2b, the refrigerant used However, there is an advantage that it can be embedded in the integrated heat exchanger 1 to achieve compactness.
【００１８】なお、組合せ配管による狭窄部は、図３
(Ａ)に示す実施例の配管直径や本数に限られず、非共沸
混合冷媒の配管に沿う温度分布を略均一にするように別
の直径および本数の配管を用いて構成でき、これによっ
て種々の非共沸混合冷媒に適合させることができる。ま
た、上記狭窄部による冷媒の蒸発温度分布は、図４の直
線Ｌ１の如く略均一(水平)でなくて、ハッチングの着霜
域に入らない限りで配管出口に向かって低下(右下がり)
するものでもよい。さらに、上記実施例では、暖房運転
における室外熱交換器の凍結,着霜防止について説明し
たが、本発明の狭窄部をもつ熱交換器を冷房運転におけ
る室内熱交換器に用いることもでき、この場合も、上述
と同じく着霜の防止,熱交換性能および動作係数の向上
を図ることができる。The narrowed portion formed by the combined piping is shown in FIG.
The pipe diameter and the number of pipes of the embodiment shown in (A) are not limited, and pipes of different diameters and numbers can be used so as to make the temperature distribution along the pipe of the non-azeotropic mixed refrigerant substantially uniform. The non-azeotropic mixed refrigerant can be adapted. Further, the evaporation temperature distribution of the refrigerant due to the narrowed portion is not substantially uniform (horizontal) as shown by the straight line L1 in FIG. 4, and decreases toward the pipe outlet (downward right) unless it enters the hatched frosted region.
You can do it. Further, in the above embodiment, the freezing of the outdoor heat exchanger in the heating operation, the prevention of frost formation was explained, but the heat exchanger having the constriction portion of the present invention can also be used for the indoor heat exchanger in the cooling operation, Also in this case, it is possible to prevent frost formation, improve heat exchange performance, and improve the coefficient of operation as in the case described above.
【００１９】[0019]
【発明の効果】以上の説明で明らかなように、本発明の
非共沸混合冷媒用の熱交換器は、非共沸混合冷媒が貫流
する配管に沿って、冷媒入口から冷媒出口に向かう冷媒
の蒸発温度の分布が、略均一または出口側に向かって低
下するように、上記配管の中間部に、流路断面積が減少
する狭窄部を設けているので、この狭窄部により非共沸
混合冷媒の非等温性を利用して、蒸発冷媒を入口側で湿
り気味,出口側で乾き気味に制御できて、熱交換器の入
口側での着霜が防止でき、対数平均温度差が大きくとれ
て、熱交換性能と動作係数を向上させることができる。
なお、上記狭窄部を、熱交換器の前部と後部を接続する
配管に介設した膨張弁で構成すれば、非共沸混合冷媒の
種類に応じて上記膨張弁の開度を調整することにより、
汎用性を向上させることができる。また、上記狭窄部
を、冷媒配管の中間部に作り込まれたキャピラリチュー
ブやオリフィスで構成すれば、熱交換器のコンパクト化
を図ることができる。さらに、上記狭窄部を、種々の
径,本数のチューブを組み合わせて構成すれば、コンパ
クト化を図りつつ、種々の非共沸混合冷媒に適合させる
ことができる。As is apparent from the above description, the heat exchanger for a non-azeotropic mixed refrigerant of the present invention has a refrigerant flowing from the refrigerant inlet to the refrigerant outlet along the pipe through which the non-azeotropic mixed refrigerant flows. Since the distribution of the evaporation temperature of is almost uniform or decreases toward the outlet side, a constriction part with a reduced flow passage cross-sectional area is provided in the middle part of the pipe. By utilizing the non-isothermal nature of the refrigerant, the evaporated refrigerant can be controlled to be moist on the inlet side and dry on the outlet side, frost formation on the inlet side of the heat exchanger can be prevented, and a large logarithmic mean temperature difference can be obtained. Thus, the heat exchange performance and the coefficient of operation can be improved.
If the narrowed portion is formed by an expansion valve provided in a pipe connecting the front part and the rear part of the heat exchanger, the opening degree of the expansion valve can be adjusted according to the type of the non-azeotropic mixed refrigerant. Due to
The versatility can be improved. Further, if the narrowed portion is composed of a capillary tube or an orifice formed in the middle portion of the refrigerant pipe, the heat exchanger can be made compact. Furthermore, if the narrowed portion is constructed by combining tubes having various diameters and numbers, it is possible to make it compact and adapt it to various non-azeotropic mixed refrigerants.
【図１】 本発明の非共沸混合冷媒用の熱交換器を用い
た空気調和装置の一例を示す冷媒回路図および上記熱交
換器の他の実施例を示す図である。FIG. 1 is a refrigerant circuit diagram showing an example of an air conditioner using a heat exchanger for a non-azeotropic mixed refrigerant of the present invention, and a diagram showing another embodiment of the heat exchanger.
【図２】 上記熱交換器の狭窄部を示す斜視図およびこ
の狭窄部の例を示す断面図である。FIG. 2 is a perspective view showing a narrowed portion of the heat exchanger and a cross-sectional view showing an example of the narrowed portion.
【図３】 上記狭窄部の他の実施例を示す図である。FIG. 3 is a diagram showing another embodiment of the narrowed portion.
【図４】 上記熱交換器の配管に沿う冷媒温度および圧
力損失の分布を示す図である。FIG. 4 is a diagram showing distributions of refrigerant temperature and pressure loss along the pipe of the heat exchanger.
【図５】 冷媒Ｒ２２を用いた従来の空気調和装置の冷
媒回路図である。FIG. 5 is a refrigerant circuit diagram of a conventional air conditioner using a refrigerant R22.
【図６】 上記従来の空気調和装置の室外熱交換器の配
管に沿う冷媒温度および圧力損失の分布を示す図であ
る。FIG. 6 is a view showing distributions of refrigerant temperature and pressure loss along the pipe of the outdoor heat exchanger of the conventional air conditioner.
１…室外熱交換器、１ａ…前部、１b…後部、２a,２b…
膨張弁、３a,３b…キャピラリチューブ、４…中間部、
５…オリフィス、７…第２チューブ。1 ... Outdoor heat exchanger, 1a ... Front part, 1b ... Rear part, 2a, 2b ...
Expansion valve, 3a, 3b ... Capillary tube, 4 ... Intermediate part,
5 ... Orifice, 7 ... 2nd tube.
Claims (4)
共沸混合冷媒用の熱交換器(１)において、 上記配管に沿って冷媒入口から冷媒出口に向かう冷媒の
蒸発温度の分布が、略均一または出口側に向かって低下
するように、上記配管の中間部(４)に、流路断面積が減
少する狭窄部(２a,２b;３a,３b;５;７)を設けたことを
特徴とする非共沸混合冷媒用の熱交換器。1. In a heat exchanger (1) for a non-azeotropic mixed refrigerant in which a non-azeotropic mixed refrigerant flows through a pipe, the distribution of the evaporation temperature of the refrigerant from the refrigerant inlet to the refrigerant outlet along the pipe. However, a narrowed portion (2a, 2b; 3a, 3b; 5; 7) having a reduced flow passage cross-sectional area is provided in the intermediate portion (4) of the above-mentioned pipe so as to be substantially uniform or to decrease toward the outlet side. A heat exchanger for a non-azeotropic mixed refrigerant.
前部(１a)と後部(１b)を接続する配管(４)に介設された
膨張弁(２a,２b)である請求項１に記載の非共沸混合冷
媒用の熱交換器。2. The narrowed portion is an expansion valve (2a, 2b) interposed in a pipe (4) connecting a front portion (1a) and a rear portion (1b) of a heat exchanger divided into two parts. Item 2. A heat exchanger for a non-azeotropic mixed refrigerant according to Item 1.
の中間部(４)に作り込まれたキャピラリチューブ(３a,
３b)またはオリフィス(５)である請求項１に記載の非共
沸混合冷媒用の熱交換器。3. The narrowed portion is a capillary tube (3a, 3a, 3a, 3b formed in the intermediate portion (4) of the pipe of the heat exchanger (1).
A heat exchanger for a non-azeotropic mixed refrigerant according to claim 1, which is 3b) or an orifice (5).
１チューブ(６)から複数に分岐する第１チューブ(６)よ
りも細径の第２チューブ(７)と、この第２チューブ(７)
より細径で、各第２チューブ(７)の先端から複数に分岐
した後に冷媒出口側の所定径の第４チューブ(１０)に合
流する第３チューブ(８)からなり、蒸発しつつ出口側に
向かって流れる非共沸混合冷媒に対する実質的な流路断
面が、夫々上記第１チューブ(６)で大,第２チューブ
(７)で小,第３チューブ(８)で中になるようにした請求
項１に記載の非共沸冷媒用の熱交換器。4. The narrowed portion includes a second tube (7) having a diameter smaller than that of the first tube (6) branched from the first tube (6) having a predetermined diameter on the refrigerant inlet side into a plurality of tubes. Tube (7)
It is composed of a third tube (8) having a smaller diameter, which branches into a plurality of branches from the tip of each second tube (7) and then joins with a fourth tube (10) of a predetermined diameter on the refrigerant outlet side. The flow passage cross sections for the non-azeotropic mixed refrigerant flowing toward the large tube are large in the first tube (6) and the second tube is large in the second tube.
The heat exchanger for a non-azeotropic refrigerant according to claim 1, wherein the heat exchanger (7) is small and the third tube (8) is centered.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16126293A JPH0719627A (en) | 1993-06-30 | 1993-06-30 | Heat exchanger for non-azeotrope refrigerant |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16126293A JPH0719627A (en) | 1993-06-30 | 1993-06-30 | Heat exchanger for non-azeotrope refrigerant |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0719627A true JPH0719627A (en) | 1995-01-20 |
Family
ID=15731761
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16126293A Pending JPH0719627A (en) | 1993-06-30 | 1993-06-30 | Heat exchanger for non-azeotrope refrigerant |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0719627A (en) |
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10339511A (en) * | 1997-06-09 | 1998-12-22 | Yoriyuki Oguri | Heat pump system of air conditioner |
| JP2001050616A (en) * | 1999-08-06 | 2001-02-23 | Mitsubishi Electric Corp | Refrigeration cycle device and air conditioner |
| WO2019124146A1 (en) * | 2017-12-18 | 2019-06-27 | ダイキン工業株式会社 | Refrigeration cycle |
| CN111479896A (en) * | 2017-12-18 | 2020-07-31 | 大金工业株式会社 | Refrigeration cycle |
| US11365335B2 (en) | 2017-12-18 | 2022-06-21 | Daikin Industries, Ltd. | Composition comprising refrigerant, use thereof, refrigerating machine having same, and method for operating said refrigerating machine |
| US11435118B2 (en) | 2017-12-18 | 2022-09-06 | Daikin Industries, Ltd. | Heat source unit and refrigeration cycle apparatus |
| US11441819B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| US11441802B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Air conditioning apparatus |
| US11493244B2 (en) | 2017-12-18 | 2022-11-08 | Daikin Industries, Ltd. | Air-conditioning unit |
| US11492527B2 (en) | 2017-12-18 | 2022-11-08 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
| US11506425B2 (en) | 2017-12-18 | 2022-11-22 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| US11549695B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Heat exchange unit |
| US11549041B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
| US11820933B2 (en) | 2017-12-18 | 2023-11-21 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| US11906207B2 (en) | 2017-12-18 | 2024-02-20 | Daikin Industries, Ltd. | Refrigeration apparatus |
-
1993
- 1993-06-30 JP JP16126293A patent/JPH0719627A/en active Pending
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10339511A (en) * | 1997-06-09 | 1998-12-22 | Yoriyuki Oguri | Heat pump system of air conditioner |
| JP2001050616A (en) * | 1999-08-06 | 2001-02-23 | Mitsubishi Electric Corp | Refrigeration cycle device and air conditioner |
| WO2019124146A1 (en) * | 2017-12-18 | 2019-06-27 | ダイキン工業株式会社 | Refrigeration cycle |
| CN111479896A (en) * | 2017-12-18 | 2020-07-31 | 大金工业株式会社 | Refrigeration cycle |
| US11365335B2 (en) | 2017-12-18 | 2022-06-21 | Daikin Industries, Ltd. | Composition comprising refrigerant, use thereof, refrigerating machine having same, and method for operating said refrigerating machine |
| US11435118B2 (en) | 2017-12-18 | 2022-09-06 | Daikin Industries, Ltd. | Heat source unit and refrigeration cycle apparatus |
| US11441819B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| US11441802B2 (en) | 2017-12-18 | 2022-09-13 | Daikin Industries, Ltd. | Air conditioning apparatus |
| US11493244B2 (en) | 2017-12-18 | 2022-11-08 | Daikin Industries, Ltd. | Air-conditioning unit |
| US11492527B2 (en) | 2017-12-18 | 2022-11-08 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
| US11506425B2 (en) | 2017-12-18 | 2022-11-22 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| US11535781B2 (en) | 2017-12-18 | 2022-12-27 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| US11549695B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Heat exchange unit |
| US11549041B2 (en) | 2017-12-18 | 2023-01-10 | Daikin Industries, Ltd. | Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator |
| US11820933B2 (en) | 2017-12-18 | 2023-11-21 | Daikin Industries, Ltd. | Refrigeration cycle apparatus |
| US11906207B2 (en) | 2017-12-18 | 2024-02-20 | Daikin Industries, Ltd. | Refrigeration apparatus |
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