JPH09145187A - Air conditioner - Google Patents
Air conditionerInfo
- Publication number
- JPH09145187A JPH09145187A JP30546495A JP30546495A JPH09145187A JP H09145187 A JPH09145187 A JP H09145187A JP 30546495 A JP30546495 A JP 30546495A JP 30546495 A JP30546495 A JP 30546495A JP H09145187 A JPH09145187 A JP H09145187A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- outdoor
- refrigerant
- heat transfer
- outdoor heat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Other Air-Conditioning Systems (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は非共沸混合冷媒を用
いた空気調和装置に関する。TECHNICAL FIELD The present invention relates to an air conditioner using a non-azeotropic mixed refrigerant.
【０００２】[0002]
【従来の技術】従来、圧縮機，四方弁，室内熱交換器，
減圧装置，室外熱交換器を接続し、室外熱交換器に送風
する室外ファンを設けた空気調和装置は、例えば、特開
平5−133564号公報に示されるように、圧縮機を室外ユ
ニットの底面に横向きに設置し、電装品箱を室外ユニッ
トの天井面に設置するような構造となっていた。さらに
熱交換器の伝熱管が複数パスにより構成されている場合
は、各パスの流量が等しくなるように、各パスの段数を
同一とし流路抵抗を等しくしていた。そして分配不適正
が生じる場合は、特開平5−118682 号公報に示されるよ
うに、各パスの流路入口に冷媒流量の制御手段を備える
ものであった。2. Description of the Related Art Conventionally, compressors, four-way valves, indoor heat exchangers,
An air conditioner provided with an outdoor fan that connects a decompression device and an outdoor heat exchanger and blows air to the outdoor heat exchanger is, for example, as shown in JP-A-5-133564, a compressor is installed on the bottom surface of the outdoor unit. It was installed sideways and the electrical equipment box was installed on the ceiling surface of the outdoor unit. Further, when the heat transfer tube of the heat exchanger is constituted by a plurality of passes, the number of stages in each pass is made the same and the flow path resistance is made equal so that the flow rate of each pass becomes equal. When an improper distribution occurs, as shown in Japanese Patent Laid-Open No. 5-118682, a means for controlling the flow rate of the refrigerant is provided at the flow path inlet of each path.
【０００３】[0003]
【発明が解決しようとする課題】しかし上記従来例で
は、ユニット内に設けられた仕切板や電装品収納箱が通
風抵抗となり、複数パスの室外熱交換器を通過する空気
は、風速分布に偏りが生じてしまっていた。そのため空
気調和装置の性能や信頼性が低下し、さらに冷媒に非共
沸混合冷媒を用いるとさらに性能が低下してしまうこと
が問題であった。However, in the above-mentioned conventional example, the partition plate and the electrical equipment storage box provided in the unit serve as ventilation resistance, and the air passing through the outdoor heat exchangers of a plurality of paths has a biased wind speed distribution. Had happened. Therefore, there is a problem that the performance and reliability of the air conditioner are deteriorated, and the performance is further deteriorated when a non-azeotropic mixed refrigerant is used as the refrigerant.
【０００４】すなわち、例えば、図２の左に示すよう
に、下側パスの風速が上側パスの風速より低い場合、そ
れに伴い交換熱量も小さくなるので下側パスの出口部分
の温度は、図２の右に示すように、上側パスの出口温度
と大きく異なるので、乾き度も異なり、熱交換器の性能
が低下し、圧縮機へ液冷媒が戻ってしまい圧縮機が破壊
する場合があった。さらに図３の左に示すように、出口
部分の乾き度をあわせるために一方のパスの冷媒入口部
分に、絞り弁やキャピラリなどの抵抗を設けて、冷媒分
配量を適正化しても、非共沸混合冷媒の場合には性能が
低下した。これは非共沸混合冷媒は、凝縮あるいは蒸発
過程の二相域では、一定圧力下で露点温度と沸点温度が
異なるため、乾き度が小さいほど温度が低い、つまり蒸
発器入口温度が最も低くなるためで、たとえば冷媒流量
の大きすぎるパスの入口部分に抵抗を設けると、図３の
右に示すようにその流路抵抗によりさらに入口温度は低
下し、着霜や凍結がさらに起こりやすくなるためであ
る。That is, for example, as shown on the left side of FIG. 2, when the wind speed of the lower path is lower than the wind speed of the upper path, the amount of heat exchanged also decreases accordingly, so the temperature at the outlet of the lower path is as shown in FIG. As shown on the right side of the figure, since the temperature is significantly different from the outlet temperature of the upper path, the degree of dryness is also different, the performance of the heat exchanger is deteriorated, and the liquid refrigerant returns to the compressor, which may destroy the compressor. Further, as shown on the left side of FIG. 3, even if a refrigerant distribution amount is optimized by providing a resistance such as a throttle valve or a capillary at the refrigerant inlet portion of one path in order to adjust the dryness of the outlet portion, In the case of the boiling mixed refrigerant, the performance deteriorated. This is because the non-azeotropic mixed refrigerant has a different dew point temperature and boiling point temperature under constant pressure in the two-phase region of the condensation or evaporation process, so the lower the dryness, the lower the temperature, that is, the evaporator inlet temperature becomes the lowest. Therefore, for example, if a resistance is provided at the entrance of a path where the flow rate of the refrigerant is too large, the entrance temperature further decreases due to the flow path resistance as shown in the right side of FIG. 3, and frost and freezing are more likely to occur. is there.
【０００５】また非共沸混合冷媒では風速分布があるパ
スでは、暖房時の冷媒入口が風速の小さい部分にあると
着霜量が多くなってしまった。これは図４に示すよう
に、非共沸混合冷媒は乾き度が小さいほど温度は低いの
で、入口付近の風速が小さいと交換熱量が小さいので相
変化も小さく、冷媒温度が上昇せず、伝熱管の着霜範囲
が長くなってしまうためである。In the non-azeotropic mixed refrigerant, the amount of frost is increased when the refrigerant inlet at the time of heating is located in a portion where the wind speed is low in the path having the wind speed distribution. As shown in FIG. 4, the non-azeotropic mixed refrigerant has a lower temperature as the dryness is smaller.Therefore, if the wind velocity near the inlet is small, the amount of heat exchanged is small, so the phase change is small and the refrigerant temperature does not rise. This is because the frosting range of the heat tube becomes longer.
【０００６】また風速分布が均一であっても、蒸発器入
口温度が低くなる非共沸混合冷媒はパスの前半では着霜
が生じやすかった。Even if the wind velocity distribution is uniform, the non-azeotropic mixed refrigerant in which the temperature at the inlet of the evaporator is low is likely to form frost in the first half of the pass.
【０００７】また図５に示すように、蒸発器で凝縮した
ドレン水は、重力の影響により落下し、最下段付近にシ
ャーベット状に溜まってしまうので、この部分から上方
のフィンに付着しているドレン水が下方に流れず霜や氷
が成長してしまい、性能低下の要因となっていた。Further, as shown in FIG. 5, the drain water condensed in the evaporator falls under the influence of gravity and accumulates in a sherbet shape in the vicinity of the lowermost stage, so that it is attached to the upper fins from this portion. Drain water did not flow downward, and frost and ice grew, which was a factor of performance degradation.
【０００８】本発明の目的は、冷媒に非共沸混合冷媒を
用いる空気調和装置の性能向上にある。An object of the present invention is to improve the performance of an air conditioner that uses a non-azeotropic mixed refrigerant as the refrigerant.
【０００９】[0009]
【課題を解決するための手段】上記の目的は、室外熱交
換器への流入風速が平均より低いパスの伝熱管の本数
を、室外熱交換器への流入風速が平均より高いパスの伝
熱管の本数より多くすることにより達成される。[Means for Solving the Problems] The above-mentioned object is to determine the number of heat transfer tubes in a path in which the inflow air velocity into the outdoor heat exchanger is lower than the average, and It is achieved by making the number of lines larger than.
【００１０】また上記の目的は、室外熱交換器の風速分
布があるパスの暖房時の冷媒入口を、そのパス内で最も
風速の低い部分の伝熱管以外の伝熱管に接続することで
達成される。Further, the above object is achieved by connecting the refrigerant inlet at the time of heating of the path having the wind speed distribution of the outdoor heat exchanger to the heat transfer tubes other than the heat transfer tube at the lowest wind speed in the path. It
【００１１】また上記の目的は、第２の減圧装置を室内
熱交換器と減圧装置との間に設け、減圧装置と第２の減
圧装置間の冷媒が、室外熱交換器の最下段の伝熱管に流
れるようにすることで達成される。Another object of the present invention is to provide a second decompression device between the indoor heat exchanger and the decompression device so that the refrigerant between the decompression device and the second decompression device is transferred to the lowest stage of the outdoor heat exchanger. This is achieved by allowing it to flow into the heat tube.
【００１２】また上記の目的は、室外熱交換器への流入
風速が平均より高い部分に、補助熱交換器を設けること
で達成される。Further, the above object can be achieved by providing the auxiliary heat exchanger at a portion where the wind velocity flowing into the outdoor heat exchanger is higher than average.
【００１３】また上記の目的は、室外熱交換器の底面の
設置高さを、圧縮機の設置高さより高くすることで達成
される。The above object is also achieved by making the installation height of the bottom surface of the outdoor heat exchanger higher than the installation height of the compressor.
【００１４】また上記の目的は、室外熱交換器あるいは
室内熱交換器を蒸発器として用いたときの前半パスの熱
伝達率を後半パスの熱伝達率より大きくすることで達成
される。Further, the above object can be achieved by making the heat transfer coefficient of the first half path larger than that of the second half path when the outdoor heat exchanger or the indoor heat exchanger is used as an evaporator.
【００１５】[0015]
【発明の実施の形態】本発明の第１の実施例を図１を用
いて説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIG.
【００１６】図１で、１は圧縮機、２は四方弁、３は室
内熱交換器、４は膨張弁、７はパス数が三つの室外熱交
換器で伝熱管５，フィン６から構成されていて、各パス
の伝熱管の本数は上側から６本，８本，１０本の計２４
本である。これらは順に配管接続され、さらに８の室内
送風ファン、９の室外送風ファンとともに空気調和装置
が構成されている。ここで圧縮機１は室外ユニット１０
の底部に仕切板１２とともに設置され、この影響により
図１左側に示すような風速分布となっている。冷媒には
たとえばＨＦＣ−３２／１２５／１３４ａやＨＦＣ−３
２／１３４ａ非共沸混合冷媒が封入されている。In FIG. 1, 1 is a compressor, 2 is a four-way valve, 3 is an indoor heat exchanger, 4 is an expansion valve, 7 is an outdoor heat exchanger having three passes, and is composed of a heat transfer tube 5 and fins 6. However, the number of heat transfer tubes in each path is 6, 8 and 10 from the top, totaling 24.
It is a book. These are sequentially connected by pipes, and an air conditioner is configured with 8 indoor ventilation fans and 9 outdoor ventilation fans. Here, the compressor 1 is the outdoor unit 10
It is installed together with the partition plate 12 at the bottom of the, and due to this effect, the wind velocity distribution is as shown on the left side of FIG. Examples of the refrigerant include HFC-32 / 125 / 134a and HFC-3.
A 2 / 134a non-azeotropic mixed refrigerant is enclosed.
【００１７】このように構成された空気調和装置の動作
について、暖房を例に取り説明する。The operation of the thus-configured air conditioner will be described by taking heating as an example.
【００１８】圧縮機１で圧縮された高温高圧の冷媒ガス
は、四方弁２を通り、室内熱交換器３で室内送風ファン
８により送風される空気に放熱して凝縮し、膨張弁４で
減圧され、３パスに分かれて室外熱交換器７に、全パス
ともパス内でもっとも風速の大きい伝熱管（上側パスか
は１段目、中側パスは７段目、下側パスは１５段目）か
ら入る。ここで冷媒は室外送風ファン９により送風され
る空気から吸熱して蒸発するが、ここでの各パスの伝熱
管の本数は、下側パスの方が多いので、下側パスの方が
伝熱面積は大きい。しかし下側パスほど空気風速は小さ
いため、各パスでの交換熱量の差は小さくなり、各パス
部での出口付近での過熱度の差は小さくなる。すなわち
各パスの空気の風速に適した伝熱面積となっている。そ
して冷媒は四方弁２を通り、再び圧縮機１へ戻る。The high-temperature and high-pressure refrigerant gas compressed by the compressor 1 passes through the four-way valve 2, radiates heat to the air blown by the indoor blower fan 8 in the indoor heat exchanger 3 and condenses, and decompresses by the expansion valve 4. The heat transfer tube with the highest wind speed in all the paths is divided into 3 passes and the outdoor heat exchanger 7 (the upper pass is the first stage, the middle pass is the 7th stage, the lower pass is the 15th stage). ). Here, the refrigerant absorbs heat from the air blown by the outdoor blower fan 9 and evaporates, but since the number of heat transfer tubes in each path is larger in the lower path, the lower path transfers heat. The area is large. However, since the air velocity is lower in the lower path, the difference in the amount of heat exchanged in each path is small, and the difference in the degree of superheat near the outlet in each path is small. That is, the heat transfer area is suitable for the wind velocity of the air in each pass. Then, the refrigerant passes through the four-way valve 2 and returns to the compressor 1 again.
【００１９】ここで伝熱管の本数について図６を用いて
説明する。図６右は本実施例における各パスの交換熱量
である。交換熱量は熱交換器の伝熱面積と熱伝達率に比
例する。そのため各パスの伝熱管の本数の最適値はその
熱交換器の風速分布により異なり、伝熱管の本数はこの
点を考慮して決定している。Here, the number of heat transfer tubes will be described with reference to FIG. The right side of FIG. 6 shows the amount of heat exchanged in each pass in this embodiment. The amount of heat exchanged is proportional to the heat transfer area and heat transfer coefficient of the heat exchanger. Therefore, the optimum value of the number of heat transfer tubes in each pass depends on the wind speed distribution of the heat exchanger, and the number of heat transfer tubes is determined in consideration of this point.
【００２０】そのため図６左に示すような各パスの伝熱
管の本数が同じ場合より熱交換効率は向上する。また従
来用いていた冷媒分配適正化のために暖房時のパスの冷
媒入口部分に設ける絞り弁やキャピラリなどの抵抗を、
不要かあるいは小さくできるので流路抵抗を少なくで
き、その圧力低下に伴う温度低下がなくなり、蒸発器入
口部温度が上昇し着霜や凍結を少なくできる。Therefore, the heat exchange efficiency is improved as compared with the case where the number of heat transfer tubes in each path is the same as shown in the left side of FIG. In addition, in order to optimize the distribution of the refrigerant that has been used conventionally, the resistance of the throttle valve and capillaries, etc., provided at the refrigerant inlet part of the path during heating,
Since it is unnecessary or can be made small, the flow path resistance can be reduced, the temperature drop due to the pressure drop is eliminated, the evaporator inlet temperature rises, and frosting and freezing can be reduced.
【００２１】さらに上下パスとも、暖房時の冷媒入口
を、最も風速の低い伝熱管以外の伝熱管に接続している
ので、伝熱管の低温部の長さを短くでき、着霜を少なく
でき、空気調和装置の性能を向上することができる。Further, in both the upper and lower paths, the refrigerant inlet at the time of heating is connected to the heat transfer tubes other than the heat transfer tube having the lowest wind speed, so that the length of the low temperature portion of the heat transfer tube can be shortened and frost formation can be reduced. The performance of the air conditioner can be improved.
【００２２】また冷房の場合は、圧縮機で圧縮された高
温高圧の冷媒ガスは、四方弁２を通り、３パスに分かれ
て室外熱交換器７に入る。ここで冷媒は室外送風ファン
９により送風される空気に放熱して凝縮する。暖房時と
同様に、ここでの各パスの伝熱管の本数は、上側から６
本，８本，１０本と、下側パスほど伝熱面積は大きい。
しかし下側ほど空気風速は小さいため、各パスの交換熱
量の差は小さくなり、各パス部での出口付近での過冷却
度の差は小さくなり、熱交換器効率が良い。そして冷媒
は膨張弁４で減圧され、室内熱交換器３で送風ファン８
により送風される空気から吸熱して蒸発し、四方弁２を
通り、再び圧縮機１へ戻る。Further, in the case of cooling, the high-temperature and high-pressure refrigerant gas compressed by the compressor passes through the four-way valve 2 and is divided into three paths to enter the outdoor heat exchanger 7. Here, the refrigerant radiates heat to the air blown by the outdoor blower fan 9 to be condensed. As with heating, the number of heat transfer tubes in each pass is 6 from the top.
The heat transfer area is larger for lower paths, such as eight, ten, and ten.
However, since the air wind speed is lower toward the lower side, the difference in the amount of heat exchanged between the passes is small, the difference in the degree of subcooling near the outlet in each pass is small, and the heat exchanger efficiency is good. Then, the refrigerant is decompressed by the expansion valve 4 and blown by the blower fan 8 by the indoor heat exchanger 3.
Heat is absorbed from the air blown by and is evaporated, passes through the four-way valve 2, and returns to the compressor 1 again.
【００２３】以上のように暖房時と同様にパスごとに熱
交換を行う空気の風速が異なっても、各パスの段数を増
減したことで風速に適した伝熱面積となっているので、
各パスの段数が同じ場合より熱交換効率は向上する。さ
らに従来用いていた冷媒分配適正化のために設ける絞り
弁やキャピラリなどの抵抗を不要かあるいは小さくでき
る。As described above, even if the wind speed of the air for heat exchange is different for each pass as in the case of heating, the heat transfer area suitable for the wind speed can be obtained by increasing or decreasing the number of stages in each pass.
The heat exchange efficiency is improved compared to the case where the number of stages in each pass is the same. Further, the resistance of the throttle valve, the capillary, etc., which is conventionally used for optimizing the distribution of the refrigerant, can be eliminated or reduced.
【００２４】本発明の第２の実施例を図７を用いて説明
する。A second embodiment of the present invention will be described with reference to FIG.
【００２５】図７で１１は第２の減圧装置としての膨張
弁、７はパス数が四つの室外熱交換器で伝熱管５，フィ
ン６から構成されていて、各パスの伝熱管の本数は上側
から６本，８本，８本，２本の計２４本である。これら
は図７に示されるように配管接続され、さらに８の室内
送風ファン，９の室外送風ファン，１２の仕切板ととも
に空気調和装置が構成されている。ここで圧縮機１は室
外ユニット１０の底部に仕切板１２とともに設置され、
この影響により図７左側に示すような風速分布となって
いる。冷媒にはたとえばＨＦＣ−３２／１２５／１３４
ａやＨＦＣ−３２／１３４ａ非共沸混合冷媒が封入され
ている。In FIG. 7, 11 is an expansion valve as a second pressure reducing device, 7 is an outdoor heat exchanger having four passes and is composed of heat transfer tubes 5 and fins 6. The number of heat transfer tubes in each pass is There are a total of 24, which are 6, 8, 8 and 2 from the upper side. These are connected by pipes as shown in FIG. 7, and an air conditioner is configured with an indoor ventilation fan 8 and an outdoor ventilation fan 9 and a partition plate 12. Here, the compressor 1 is installed on the bottom of the outdoor unit 10 together with the partition plate 12,
Due to this effect, the wind velocity distribution is as shown on the left side of FIG. 7. As the refrigerant, for example, HFC-32 / 125/134
a and HFC-32 / 134a non-azeotropic mixed refrigerant are enclosed.
【００２６】このように構成された空気調和装置の動作
について暖房を例に取り説明する。圧縮機１で圧縮され
た高温高圧の冷媒ガスは、四方弁２を通り、室内熱交換
器３で室内送風ファン８により送風される空気に放熱し
て凝縮し、キャピラリチューブ４で減圧され、室外熱交
換器７の最下段に入り、室外送風ファン９により送風さ
れる空気に放熱して凝縮し、最下段から２段目から膨張
弁１１に入りさらに減圧される。ここでキャピラリチュ
ーブ４の長さと膨張弁１１の開度は最下段パスの冷媒の
温度が０℃以上になるように調節されている。そして冷
媒は３パスに分かれ、各パス内で最も風速の大きい伝熱
管（上側パスは上から１段目、中側パスは上から７段
目、下側パスは上から１５段目）から入り、室外送風フ
ァン９により送風される空気から吸熱して蒸発するが、
ここでの各パスの伝熱管の本数は、下のパスほど多いの
で、下のパスの方が伝熱面積は大きい。しかし下ほど通
過する空気風速は小さいため、各パス間の交換熱量差は
小さくなり、各パス部での出口付近での過熱度の差は小
さくなる。すなわち各パスの空気の風速に適した伝熱面
積となっている。そして冷媒は四方弁２を通り、再び圧
縮機１へ戻る。また、室外熱交換器で凝縮したドレン水
は重力の影響によりドレン水が降下するが、最下段パス
の温度は０℃以上であるので着霜や凍結はしない。よっ
てドレン水はそのまま底板に流れていくので、それより
上方のフィンに付着しているドレン水も下方に流れやす
くなり、着霜や凍結がしにくくなる。The operation of the thus-configured air conditioner will be described taking heating as an example. The high-temperature and high-pressure refrigerant gas compressed by the compressor 1 passes through the four-way valve 2, radiates heat to the air blown by the indoor blower fan 8 in the indoor heat exchanger 3 to be condensed, and is decompressed by the capillary tube 4 to be exposed outdoors. It enters the lowermost stage of the heat exchanger 7, radiates heat to the air blown by the outdoor blower fan 9 and condenses, and enters the expansion valve 11 from the second stage from the lowermost stage to further reduce the pressure. Here, the length of the capillary tube 4 and the opening degree of the expansion valve 11 are adjusted so that the temperature of the refrigerant in the lowermost path is 0 ° C. or higher. The refrigerant is divided into three passes, and enters from the heat transfer tube with the highest wind speed in each pass (upper pass is the first stage from the top, middle pass is the seventh stage from the top, lower pass is the fifteenth stage from the top). , Which absorbs heat from the air blown by the outdoor blower fan 9 and evaporates,
Since the number of heat transfer tubes in each pass is larger in the lower pass, the lower pass has a larger heat transfer area. However, since the velocity of the passing air is lower toward the bottom, the difference in the amount of heat exchanged between the passes is small, and the difference in the degree of superheat near the outlets of the passes is small. That is, the heat transfer area is suitable for the wind velocity of the air in each pass. Then, the refrigerant passes through the four-way valve 2 and returns to the compressor 1 again. Further, the drain water condensed in the outdoor heat exchanger drops due to the influence of gravity, but since the temperature of the lowermost path is 0 ° C or higher, frosting or freezing does not occur. Therefore, since the drain water flows to the bottom plate as it is, the drain water attached to the fins above it also easily flows downward, and frosting and freezing are less likely to occur.
【００２７】さらに上下パスとも、暖房時の冷媒入口
を、最も風速の低い伝熱管以外の伝熱管に接続している
ので、伝熱管の低温部の長さを短くでき、着霜を少なく
でき、空気調和装置の性能を向上することができる。Further, in both the upper and lower paths, the refrigerant inlet at the time of heating is connected to the heat transfer tubes other than the heat transfer tube having the lowest wind speed, so that the length of the low temperature portion of the heat transfer tube can be shortened and frost formation can be reduced. The performance of the air conditioner can be improved.
【００２８】冷房時は、膨張弁１１を全開にする。すな
わち、圧縮機１で圧縮された高温高圧の冷媒ガスは、四
方弁２を通り、３パスに分かれて室外熱交換器７に入
る。ここで冷媒は室外送風ファン９により送風される空
気に放熱して凝縮する。暖房時と同様に、ここでの各パ
スの伝熱管の本数は、上側から６本，８本，８本で下側
ほど伝熱面積は大きい。しかし下側ほど空気風速は小さ
いため、各パス間での交換熱量差は小さく、各パス部で
の出口付近での過冷却度の差は小さくなり、熱交換器効
率が良い。そして冷媒は１パスに合流して膨張弁１１に
入るが、膨張弁１１は全開であるので減圧されないま
ま、下パスの最上段（下から２段目）に入り、室外送風
ファン９により送風される空気に放熱してさらに凝縮か
過冷却し、最下段から出て、キャピラリチューブ４に入
る。キャピラリチューブ４で冷媒は減圧され、室内熱交
換器３に入り、室内送風ファン８により送風される空気
から吸熱して蒸発し、四方弁２を通り、再び圧縮機１へ
戻る。During cooling, the expansion valve 11 is fully opened. That is, the high-temperature and high-pressure refrigerant gas compressed by the compressor 1 passes through the four-way valve 2 and is divided into three paths to enter the outdoor heat exchanger 7. Here, the refrigerant radiates heat to the air blown by the outdoor blower fan 9 to be condensed. Similar to heating, the number of heat transfer tubes in each path is 6, 8, and 8 from the upper side, and the heat transfer area is larger toward the lower side. However, since the air velocity is lower toward the lower side, the difference in the amount of heat exchanged between the passes is small, the difference in the degree of supercooling near the outlet in each pass is small, and the heat exchanger efficiency is good. Then, the refrigerant merges into one path and enters the expansion valve 11, but since the expansion valve 11 is fully opened, it enters the uppermost stage (second stage from the bottom) of the lower path without being decompressed, and is blown by the outdoor blower fan 9. It radiates heat to the air and further condenses or supercools, exits from the bottom and enters the capillary tube 4. The refrigerant is decompressed in the capillary tube 4, enters the indoor heat exchanger 3, absorbs heat from the air blown by the indoor blower fan 8 to evaporate, passes through the four-way valve 2, and returns to the compressor 1 again.
【００２９】以上のように膨張弁１１で減圧は行わない
ので、暖房時に最下段パスの耐着霜・凍結制御を行って
も、冷房時に性能が低下することはなく、熱交換器の能
力を最大限利用できる。As described above, since the expansion valve 11 does not perform decompression, even if the frost-proof / freezing control of the lowermost path is performed during heating, the performance does not decrease during cooling, and the capacity of the heat exchanger is improved. Maximum available.
【００３０】本発明の第３の実施例を図８を用いて説明
する。A third embodiment of the present invention will be described with reference to FIG.
【００３１】図８で、７は室外熱交換器で伝熱管５，フ
ィン６から構成されている。また１３は補助熱交換器と
してのサブクーラで、室外熱交換器７の上方に取り付け
られている。これらは図８に示されるように配管接続さ
れ、さらに８の室内送風ファン，９の室外送風ファン，
１２の仕切板とともに空気調和装置が構成されている。
ここで圧縮機１は室外ユニット１０の底部に仕切板１２
とともに設置されている。冷媒にはたとえばＨＦＣ−３
２／１２５／１３４ａやＨＦＣ−３２／134a非共沸混合
冷媒が封入されている。In FIG. 8, an outdoor heat exchanger 7 is composed of heat transfer tubes 5 and fins 6. Further, 13 is a subcooler as an auxiliary heat exchanger, which is attached above the outdoor heat exchanger 7. These are connected by pipes as shown in FIG. 8, and further, an indoor ventilation fan 8 and an outdoor ventilation fan 9 are provided.
An air conditioner is configured with 12 partition plates.
Here, the compressor 1 has a partition plate 12 at the bottom of the outdoor unit 10.
It is installed together with. For the refrigerant, for example, HFC-3
2/125 / 134a or HFC-32 / 134a non-azeotropic mixed refrigerant is enclosed.
【００３２】このように構成された空気調和装置の室外
熱交換器の風速分布について説明する。The wind velocity distribution of the outdoor heat exchanger of the air conditioner thus configured will be described.
【００３３】図１０は本実施例の風速分布である。室外
熱交換器７の下側は仕切版１２が通風抵抗となっている
が、上側もサブクーラ１３が通風抵抗となっているた
め、図９に示すサブクーラ１３がない場合より風速分布
は小さくなっている。FIG. 10 shows the wind velocity distribution of this embodiment. The partition plate 12 has ventilation resistance on the lower side of the outdoor heat exchanger 7, but the subcooler 13 also has ventilation resistance on the upper side, so the wind speed distribution becomes smaller than that without the subcooler 13 shown in FIG. There is.
【００３４】次に動作について暖房を例にとり説明す
る。Next, the operation will be described taking heating as an example.
【００３５】圧縮機１で圧縮された高温高圧の冷媒ガス
は、四方弁２を通り、室内熱交換器３で室内送風ファン
８により送風される空気に放熱して凝縮し、膨張弁４で
減圧され、サブクーラ１３を通り、３パスに分かれて室
外熱交換器７に入る。サブクーラ１３と室外熱交換器７
で冷媒は室外送風ファン９により送風される空気から吸
熱して蒸発し、四方弁２を通り、再び圧縮機１に戻る。The high-temperature and high-pressure refrigerant gas compressed by the compressor 1 passes through the four-way valve 2, radiates heat to the air blown by the indoor blower fan 8 in the indoor heat exchanger 3 and condenses, and decompresses by the expansion valve 4. Then, it passes through the subcooler 13 and enters the outdoor heat exchanger 7 in three passes. Subcooler 13 and outdoor heat exchanger 7
Then, the refrigerant absorbs heat from the air blown by the outdoor blower fan 9 and evaporates, passes through the four-way valve 2 and returns to the compressor 1 again.
【００３６】ここで室外熱交換器７の風速分布の偏りは
図１０に示すように小さいので、各パスの交換熱量はほ
ぼ同等となり、またサブクーラの分の伝熱面積が増える
ので、熱交換効率は向上する。また従来用いていた冷媒
分配適正化のための暖房時のパスの冷媒入口部分に設け
る絞り弁やキャピラリなどの抵抗を、不要かあるいは小
さくできるので流通抵抗を少なくでき、その圧力低下に
伴う温度降下がなくなり、蒸発器入口部温度が上昇し着
霜や凍結を少なくできる。Here, since the deviation of the wind speed distribution of the outdoor heat exchanger 7 is small as shown in FIG. 10, the heat exchange amount of each path is almost the same, and the heat transfer area for the subcooler increases, so that the heat exchange efficiency is increased. Will improve. In addition, the resistance of the throttle valve and capillaries, etc. provided at the refrigerant inlet part of the path during heating for proper refrigerant distribution, which is conventionally used, is either unnecessary or can be made small so that the flow resistance can be reduced and the temperature drop due to the pressure drop. The temperature at the inlet of the evaporator rises and frost and freezing can be reduced.
【００３７】また冷房の場合は圧縮機１で圧縮された高
温高圧の冷媒ガスは、四方弁２を通り、３パスに分かれ
て室外熱交換器７に入り、室外ファン９により送風され
る空気に放熱して凝縮する。ここで暖房時と同様に室外
熱交換器７の風速分布の偏りは図１０に示すように小さ
くなっている。そして冷媒は１パスになり、サブクーラ
１３で過冷却され、膨張弁４で減圧され、室内熱交換器
３で室内送風ファン８により送風される空気から吸熱し
て蒸発し、四方弁２を通り再び圧縮機１に戻る。In the case of cooling, the high-temperature and high-pressure refrigerant gas compressed by the compressor 1 passes through the four-way valve 2 and is divided into three passes into the outdoor heat exchanger 7 to be the air blown by the outdoor fan 9. It dissipates heat and condenses. Here, as in the case of heating, the deviation of the wind speed distribution of the outdoor heat exchanger 7 is small as shown in FIG. Then, the refrigerant becomes one pass, is supercooled by the subcooler 13, is decompressed by the expansion valve 4, absorbs heat from the air blown by the indoor blower fan 8 in the indoor heat exchanger 3, evaporates, and passes through the four-way valve 2 again. Return to compressor 1.
【００３８】以上のように暖房時同様、室外熱交換器７
の風速分布の偏りは図９に示すように小さいので、各パ
スの交換熱量はほぼ同等となり、熱交換効率は向上す
る、またサブクーラにより冷媒の過冷却域が増え、機器
の効率は向上する。また従来用いていた冷媒分配適正化
のための暖房時のパスの冷媒入口部分に設ける絞り弁や
キャピラリなどの抵抗を、不要かあるいは小さくできる
ので流通抵抗を少なくできる。As described above, the outdoor heat exchanger 7 is used as in heating.
Since the deviation of the wind speed distribution is small as shown in FIG. 9, the heat exchange amount of each path is almost the same, the heat exchange efficiency is improved, and the subcooler increases the supercooling region of the refrigerant to improve the device efficiency. Further, the resistance of the throttle valve, the capillary, etc. provided at the refrigerant inlet portion of the path at the time of heating for proper refrigerant distribution, which is conventionally used, is unnecessary or can be reduced, so that the flow resistance can be reduced.
【００３９】本発明の第４の実施例を図１１を用いて説
明する。A fourth embodiment of the present invention will be described with reference to FIG.
【００４０】図１１で、１４は電装品収納箱で、これら
から室外ユニット１０が構成されている。室外熱交換器
７の底面の設置高さは、圧縮機１の設置高さよりｈ（ｈ
＞圧縮機直径）だけ上方にあり、通風路内に圧縮機や電
装品箱等はない。In FIG. 11, 14 is an electrical equipment storage box, from which the outdoor unit 10 is constructed. The installation height of the bottom surface of the outdoor heat exchanger 7 is more than the installation height of the compressor 1 by h (h
There is no compressor or electrical equipment box in the ventilation passage.
【００４１】そのため室外熱交換器の風速分布の偏りは
小さく、室外ユニット１０を用いる空気調和装置は、本
発明の第３の実施例同様に各パスの交換熱量はほぼ同等
となり、熱交換効率は向上する。また従来用いていた冷
媒分配適正化のための暖房時のパスの冷媒入口部分に設
ける絞り弁やキャピラリなどの抵抗を、不要かあるいは
小さくできるので流通抵抗を少なくできる。さらに通風
路に圧縮機や電装品収納箱がないので、室外ファンの径
を大きくできるので、同一風量を得るためのファンの回
転数は小さくなり、ファンを駆動するモータの消費電力
を小さくでき、ファン騒音も小さくできる。Therefore, the deviation of the wind velocity distribution of the outdoor heat exchanger is small, and in the air conditioner using the outdoor unit 10, the heat exchange amount of each path is almost the same as in the third embodiment of the present invention, and the heat exchange efficiency is high. improves. Further, the resistance of the throttle valve, the capillary, etc. provided at the refrigerant inlet portion of the path at the time of heating for proper refrigerant distribution, which is conventionally used, is unnecessary or can be reduced, so that the flow resistance can be reduced. Furthermore, since there is no compressor or electrical component storage box in the ventilation passage, the diameter of the outdoor fan can be increased, so the number of rotations of the fan for obtaining the same air volume is reduced, and the power consumption of the motor that drives the fan can be reduced. Fan noise can also be reduced.
【００４２】[0042]
【発明の効果】本発明によれば、圧縮機，四方弁，室内
熱交換器，減圧装置，複数パスの室外熱交換器を接続
し、冷媒に非共沸混合冷媒を封入し、室外熱交換器に送
風する室外ファンを設けた空気調和装置で、室外熱交換
器の風速分布に偏りがあっても、風速が低いパスの伝熱
管の本数を多くすることで、各パスの風速に適した伝熱
面積にでき、性能を向上することができる。According to the present invention, the compressor, the four-way valve, the indoor heat exchanger, the pressure reducing device, and the plural-pass outdoor heat exchangers are connected to each other, the non-azeotropic mixed refrigerant is sealed in the refrigerant, and the outdoor heat exchange is performed. This is an air conditioner equipped with an outdoor fan that blows air into the air conditioner, and even if the wind speed distribution of the outdoor heat exchanger is uneven, by increasing the number of heat transfer tubes in the low wind speed path, it is suitable for the wind speed of each path. The heat transfer area can be set and the performance can be improved.
【００４３】あるいはパス内で最も温度の低くなる冷媒
入口が、風速の低い部分にないので、伝熱管の温度の低
い部分を短くでき、着霜を少なくすることができる。Alternatively, since the refrigerant inlet having the lowest temperature in the path does not exist in the low wind speed portion, the low temperature portion of the heat transfer tube can be shortened and frost formation can be reduced.
【００４４】あるいは室外熱交換器で最もドレン水の溜
まりやすい熱交換器の最下段部付近が冷媒により加熱さ
れるので、着霜や凍結が起こらず、室外熱交換器全体の
水切り性能も向上し、空気調和器の性能が向上する。Alternatively, since the vicinity of the lowermost part of the heat exchanger in which the drain water is most likely to be collected in the outdoor heat exchanger is heated by the refrigerant, frosting and freezing do not occur and the drainage performance of the entire outdoor heat exchanger is improved. , The performance of the air conditioner is improved.
【００４５】あるいは室外熱交換器への流入風速の風速
分布が均一あるいは偏りが小さくなり、熱交換器の効率
が向上する。Alternatively, the wind velocity distribution of the wind velocity flowing into the outdoor heat exchanger becomes uniform or has a small deviation, and the efficiency of the heat exchanger is improved.
【図１】本発明の第１の実施例を示す説明図。FIG. 1 is an explanatory view showing a first embodiment of the present invention.
【図２】風速分布に偏りがある熱交換器冷媒温度分布
図。FIG. 2 is a heat exchanger refrigerant temperature distribution diagram in which the wind speed distribution is biased.
【図３】冷媒分配を変更するために抵抗を設けた熱交換
器冷媒温度分布図。FIG. 3 is a heat exchanger refrigerant temperature distribution diagram in which a resistance is provided to change the refrigerant distribution.
【図４】熱交換器の着霜範囲を示す説明図。FIG. 4 is an explanatory view showing a frosting range of the heat exchanger.
【図５】熱交換器ドレン水付着状態の説明図。FIG. 5 is an explanatory diagram of a heat exchanger drain water adhesion state.
【図６】熱交換器の交換熱量の説明図。FIG. 6 is an explanatory diagram of the amount of heat exchanged by the heat exchanger.
【図７】本発明の第２の実施例を示す説明図。FIG. 7 is an explanatory view showing a second embodiment of the present invention.
【図８】本発明の第３の実施例を示す説明図。FIG. 8 is an explanatory diagram showing a third embodiment of the present invention.
【図９】従来の室外熱交換器風速分布図。FIG. 9 is a wind velocity distribution map of a conventional outdoor heat exchanger.
【図１０】本発明の第３の実施例での室外熱交換器風速
分布図。FIG. 10 is an outdoor heat exchanger wind velocity distribution diagram in the third embodiment of the present invention.
【図１１】本発明の第４の実施例を示す説明図。FIG. 11 is an explanatory diagram showing a fourth embodiment of the present invention.
１…圧縮機、２…四方弁、３…室内熱交換器、４…減圧
装置、５…伝熱管、６…フィン、７…室外熱交換器、８
…室内送風ファン、９…室外送風ファン、１０…室外ユ
ニット、１１…第２の減圧装置、１２…仕切板、１３…
サブクーラ、１４…電装品収納箱。DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Four-way valve, 3 ... Indoor heat exchanger, 4 ... Decompression device, 5 ... Heat transfer tube, 6 ... Fin, 7 ... Outdoor heat exchanger, 8
... indoor blower fan, 9 ... outdoor blower fan, 10 ... outdoor unit, 11 ... second pressure reducing device, 12 ... partition plate, 13 ...
Subcooler, 14 ... Electrical equipment storage box.
Claims (5)
る室内熱交換器，減圧装置、前記複数パスの伝熱管から
なる室外熱交換器を接続し、冷媒に非共沸混合冷媒を用
い、前記室外熱交換器に送風する室外ファンと、前記室
内熱交換器に送風する室内ファンを設けた空気調和装置
において、前記室外熱交換器あるいは前記室内熱交換器
の流入風速が平均より低いパスの伝熱管の本数を、流入
風速が平均より高いパスの伝熱管の本数より多くするこ
とを特徴とする空気調和装置。1. A non-azeotropic mixed refrigerant is connected to a refrigerant by connecting a compressor, a four-way valve, an indoor heat exchanger including a plurality of heat transfer tubes, a pressure reducing device, and an outdoor heat exchanger including a plurality of heat transfer tubes. In an air conditioner provided with an outdoor fan that blows air to the outdoor heat exchanger and an indoor fan that blows air to the indoor heat exchanger, the inflow speed of the outdoor heat exchanger or the indoor heat exchanger is lower than average. An air conditioner characterized in that the number of heat transfer tubes in a path is set to be greater than the number of heat transfer tubes in a path having an inflow wind speed higher than average.
る室内熱交換器，減圧装置、前記複数パスの伝熱管から
なる室外熱交換器を接続し、冷媒に非共沸混合冷媒を用
い、前記室外熱交換器に送風する室外ファンと、前記室
内熱交換器に送風する室内ファンを設けた空気調和装置
において、前記室外熱交換器あるいは前記室内熱交換器
の風速分布があるパスの、蒸発器として用いたときの冷
媒入口を、そのパス内で最も風速の低い部分の伝熱管以
外の伝熱管に接続することを特徴とする空気調和装置。2. A non-azeotropic mixed refrigerant is connected to a refrigerant by connecting a compressor, a four-way valve, an indoor heat exchanger including a plurality of heat transfer tubes, a pressure reducing device, and an outdoor heat exchanger including a plurality of heat transfer tubes. Use, in an air conditioner provided with an outdoor fan that blows air to the outdoor heat exchanger and an indoor fan that blows air to the indoor heat exchanger, a path having a wind speed distribution of the outdoor heat exchanger or the indoor heat exchanger. An air conditioner characterized in that the refrigerant inlet when used as an evaporator is connected to a heat transfer tube other than the heat transfer tube in the lowest wind speed portion in the path.
置，複数パスの伝熱管からなる室外熱交換器を接続し、
冷媒に非共沸混合冷媒を用い、前記室外熱交換器に送風
する室外ファンと前記室内熱交換器に送風する室内ファ
ンを設けた空気調和装置において、第２の減圧装置を前
記室内熱交換器と前記減圧装置との間に設け、前記減圧
装置と前記第２の減圧装置間の冷媒が、前記室外熱交換
器の最下段の伝熱管に流れるように配管したことを特徴
とする空気調和装置。3. A compressor, a four-way valve, an indoor heat exchanger, a pressure reducing device, and an outdoor heat exchanger consisting of a plurality of heat transfer tubes are connected,
A non-azeotropic mixed refrigerant is used as a refrigerant, and in an air conditioner provided with an outdoor fan that blows air to the outdoor heat exchanger and an indoor fan that blows air to the indoor heat exchanger, a second decompression device is provided for the indoor heat exchanger. Between the pressure reducing device and the second pressure reducing device, and the refrigerant between the pressure reducing device and the second pressure reducing device is arranged so as to flow to the lowermost heat transfer pipe of the outdoor heat exchanger. .
置，室外熱交換器を接続し、冷媒に非共沸混合冷媒を用
い、前記室外熱交換器に送風する室外ファンと、前記室
外熱交換器に送風する室外ファンを設けた空気調和装置
において、前記室外熱交換器あるいは前記室内熱交換器
への流入風速が平均より高い部分の凝縮器として用いた
ときの冷媒出口に、補助熱交換器を設けることを特徴と
する空気調和装置。4. An outdoor fan, which is connected to a compressor, a four-way valve, an indoor heat exchanger, a pressure reducing device, and an outdoor heat exchanger, uses a non-azeotropic mixed refrigerant as a refrigerant, and blows to the outdoor heat exchanger, In an air conditioner provided with an outdoor fan that blows air to the outdoor heat exchanger, a refrigerant outlet when used as a condenser in a portion where the wind velocity flowing into the outdoor heat exchanger or the indoor heat exchanger is higher than the average, an auxiliary An air conditioner comprising a heat exchanger.
置，室外熱交換器を接続し、冷媒に非共沸混合冷媒を用
い、前記室外熱交換器に送風する室外ファンを設けた空
気調和装置において、前記室外熱交換器の底面の設置高
さを、前記圧縮機の設置高さより高くしたことを特徴と
する空気調和装置。5. A compressor, a four-way valve, an indoor heat exchanger, a pressure reducing device, and an outdoor heat exchanger are connected, a non-azeotropic mixed refrigerant is used as a refrigerant, and an outdoor fan for blowing air to the outdoor heat exchanger is provided. In the air conditioner, an installation height of a bottom surface of the outdoor heat exchanger is set higher than an installation height of the compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30546495A JPH09145187A (en) | 1995-11-24 | 1995-11-24 | Air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30546495A JPH09145187A (en) | 1995-11-24 | 1995-11-24 | Air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09145187A true JPH09145187A (en) | 1997-06-06 |
Family
ID=17945468
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP30546495A Pending JPH09145187A (en) | 1995-11-24 | 1995-11-24 | Air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09145187A (en) |
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