JP2001194015A - Freezing apparatus - Google Patents
Freezing apparatusInfo
- Publication number
- JP2001194015A JP2001194015A JP2000222450A JP2000222450A JP2001194015A JP 2001194015 A JP2001194015 A JP 2001194015A JP 2000222450 A JP2000222450 A JP 2000222450A JP 2000222450 A JP2000222450 A JP 2000222450A JP 2001194015 A JP2001194015 A JP 2001194015A
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- refrigerant
- dryness
- temperature
- superheat
- 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.)
- Granted
Links
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
- F25B2400/12—Inflammable refrigerants
-
- 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
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、低ＧＷＰ(地球
温暖化係数)に対応し、かつ、省エネルギーで低コスト
でオゾン層保護およびリサイクルを達成できる冷凍装置
に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerating apparatus which can cope with low GWP (global warming potential), and can achieve ozone layer protection and recycling at low cost with energy saving.
【０００２】[0002]
【従来の技術】従来、たとえば、Ｒ２２を使用した装置
では、高圧ドームタイプの圧縮機の吸入側での冷媒乾き
度Ｘが０.９７である場合には、吐出温度が９０℃に達
し、低圧ドームタイプの圧縮機では、吸入側での冷媒乾
き度Ｘが０.９７である場合には、吐出温度が７０℃に
達する。Ｒ３２冷媒は、圧損が小さくＣＯＰ(成績係数)
向上を図れる一方、冷媒物性上、Ｒ２２,Ｒ４１０Ａや
Ｒ４０７に比して、吐出温度が理論上は１５℃上昇、実
測で１０〜１５℃だけ上昇する。このため、Ｒ２２,Ｒ
４１０ＡやＲ４０７を使用している装置について、冷媒
をＲ３２に入れ換え、冷凍機油をＲ３２用に変更しただ
けでは、信頼性や性能が低下してしまうという問題があ
る。2. Description of the Related Art Conventionally, for example, in an apparatus using R22, when the dryness X of refrigerant on the suction side of a high-pressure dome type compressor is 0.97, the discharge temperature reaches 90 ° C. In the dome type compressor, when the dryness X of the refrigerant on the suction side is 0.97, the discharge temperature reaches 70 ° C. R32 refrigerant has small pressure loss and COP (coefficient of performance)
On the other hand, the discharge temperature rises theoretically by 15 ° C. compared to R22, R410A and R407, and rises by 10 to 15 ° C. in actual measurement, due to the physical properties of the refrigerant. Therefore, R22, R
Regarding the apparatus using 410A or R407, there is a problem that the reliability and performance are reduced only by replacing the refrigerant with R32 and changing the refrigerating machine oil for R32.
【０００３】信頼性については、圧縮機が高温化する
と、材料劣化および油劣化が進み、長期信頼性が低下す
ることが懸念される。特に、圧縮機モータは、温度によ
る劣化(減磁力の低下)が大きいとされており、使用する
材料によってはＤＣモータは注意が必要である。With respect to reliability, when the temperature of the compressor rises, there is a concern that the deterioration of the material and the oil will progress, and the long-term reliability will decrease. In particular, compressor motors are considered to be greatly deteriorated (decrease in demagnetizing force) due to temperature, and care must be taken for DC motors depending on the material used.
【０００４】また、性能面については、吐出管温度,各
種センサによる冷媒制御および電流制御が従来と同じな
らば、能力低下や運転エリアが狭まるという問題点があ
る。[0004] In terms of performance, if the refrigerant control and the current control using the discharge pipe temperature and various sensors are the same as in the past, there is a problem that the capacity is reduced and the operation area is narrowed.
【０００５】[0005]
【発明が解決しようとする課題】そこで、この発明の目
的は、信頼性や性能の低下を回避しつつ、省エネルギー
と低ＧＷＰを実現できる冷凍装置を提供することにあ
る。SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a refrigeration apparatus which can realize energy saving and low GWP while avoiding deterioration in reliability and performance.
【０００６】[0006]
【課題を解決するための手段】図４のＰ-Ｈ線図に示す
ように、一般に、冷凍サイクルにおける最高温度は、圧
縮機の吐出側の温度である。As shown in the PH diagram of FIG. 4, the maximum temperature in the refrigerating cycle is generally the temperature on the discharge side of the compressor.
【０００７】本発明者らは、Ｒ３２冷媒を使用した場合
には、図５のＰ−Ｈ線図における(Ｔｄ３−Ｔcu３)ライ
ンのように、従来の(Ｔｄ１−Ｔcu１)ラインに比べて、
スーパーヒートＳＨを小さくして、湿り度を大きくして
も、圧縮機の信頼性を確保できることを実験で確かめる
ことができた。図５に示すように、圧縮機吸込側での湿
り度を大きくすれば、圧縮機の吐出側の温度ＴｄがＴｄ
１からＴｄ３に低下して、信頼性の低下や能力低下を回
避できる。なお、湿り度をｘとすると、湿り度ｘ＝１.
０のときに完全ガス状態であり、湿り度ｘ＝０のときに
液状態であり、ｘ＝０.５,０.６,０.９などでは２相域
での流動様式になっていることを表す。また、乾き度を
ｙとすると、ｙ＝１−ｘである。The present inventors have found that when the R32 refrigerant is used, as compared with the conventional (Td1-Tcu1) line, as indicated by the (Td3-Tcu3) line in the PH diagram of FIG.
Experiments have confirmed that the reliability of the compressor can be ensured even when the superheat SH is reduced and the wetness is increased. As shown in FIG. 5, if the wetness on the compressor suction side is increased, the temperature Td on the discharge side of the compressor becomes Td.
From 1 to Td3, it is possible to avoid a decrease in reliability and a decrease in performance. When the wetness is x, the wetness x = 1.
When 0, it is in a completely gaseous state, when wetness x = 0, it is in a liquid state, and when x = 0.5, 0.6, 0.9, etc., it should be in a two-phase flow mode. Represents When the dryness is y, y = 1-x.
【０００８】図３の信頼性試験結果に示すように、従来
のＲ２２冷媒を使用した場合では、圧縮機吸入側での乾
き度を０.９０以上にしないと、圧縮機の信頼性が使用
不可のレベルであったが、Ｒ３２冷媒では、圧縮機吸入
側での乾き度が０.６０以上であれば、圧縮機の信頼性
が使用可能なレベルとなることを実験で確認できた。As shown in the reliability test results in FIG. 3, when the conventional R22 refrigerant is used, the reliability of the compressor cannot be used unless the dryness on the compressor suction side is set to 0.90 or more. However, it was confirmed by experiments that the reliability of the compressor reached a usable level when the dryness on the compressor suction side was 0.60 or more with the R32 refrigerant.
【０００９】したがって、請求項１の発明の冷凍装置
は、圧縮機が、乾き度０.６５以上のＲ３２冷媒、もし
くはＲ３２を少なくとも７０重量％以上含む乾き度が
０.６５以上の混合冷媒を吸入して圧縮することを特徴
としている。Therefore, in the refrigeration apparatus according to the first aspect of the present invention, the compressor sucks the R32 refrigerant having a dryness of 0.65 or more or the mixed refrigerant containing at least 70% by weight of R32 and having a dryness of 0.65 or more. It is characterized by compression.
【００１０】この請求項１の発明では、圧縮機が、乾き
度０.６５以上のＲ３２冷媒を吸入して圧縮するように
なっているから、図３の試験結果から分かるように、圧
縮機の信頼性を低下させることなく、Ｒ３２冷媒の使用
が可能になり、信頼性や性能の低下を回避しつつ、省エ
ネルギーと低ＧＷＰを実現できる。なお、圧縮機が、Ｒ
３２を少なくとも７０重量％以上含む乾き度が０.６５
以上の混合冷媒を吸入する場合にも、同様の効果が得ら
れる。According to the first aspect of the present invention, since the compressor sucks and compresses the R32 refrigerant having a dryness of 0.65 or more, as can be seen from the test results of FIG. The use of the R32 refrigerant is possible without lowering the reliability, and energy saving and low GWP can be realized while avoiding deterioration in reliability and performance. Note that the compressor is R
32 containing at least 70% by weight or more and having a dryness of 0.65
Similar effects can be obtained when the above mixed refrigerant is sucked.
【００１１】また、請求項２の発明の冷凍装置は、圧縮
機が、乾き度０.７０以上のＲ３２冷媒、もしくは、Ｒ
３２を少なくとも７０重量％以上含む乾き度が０.７０
以上の混合冷媒を吸入して圧縮することを特徴としてい
る。Further, in the refrigeration apparatus according to the second aspect of the present invention, the compressor includes an R32 refrigerant having a dryness of 0.70 or more or an R32 refrigerant.
32 containing at least 70% by weight or more and having a dryness of 0.70
The mixed refrigerant is sucked and compressed.
【００１２】この請求項２の発明では、圧縮機が、乾き
度０.７０以上のＲ３２冷媒を吸入するから、圧縮機の
信頼性を一層向上できる。なお、圧縮機が、Ｒ３２を少
なくとも７０重量％以上含む乾き度が０.７０以上の混
合冷媒を吸入する場合にも、同様の効果が得られる。す
なわち、Ｒ３２を少なくとも７０重量％以上含んだ混合
冷媒であれば、擬似共沸となり、Ｒ２２冷媒に対するＲ
３２冷媒のメリット(省エネルギー,低ＧＷＰ)を発揮で
きる。According to the second aspect of the present invention, since the compressor sucks the R32 refrigerant having a dryness of 0.70 or more, the reliability of the compressor can be further improved. The same effect can be obtained when the compressor sucks a mixed refrigerant containing R32 of at least 70% by weight or more and having a dryness of 0.70 or more. That is, if the mixed refrigerant contains at least 70% by weight of R32, it becomes pseudo-azeotropic and the R22 relative to the R22 refrigerant
The advantages of 32 refrigerants (energy saving, low GWP) can be exhibited.
【００１３】また、請求項３の発明の冷凍装置は、圧縮
機が、乾き度０.７５以上のＲ３２冷媒、もしくは、Ｒ
３２を少なくとも７０重量％以上含む乾き度が０.７０
以上の混合冷媒を吸入して圧縮することを特徴としてい
る。Further, in the refrigeration apparatus according to the third aspect of the present invention, the compressor includes an R32 refrigerant having a dryness of 0.75 or more or an R32 refrigerant.
32 containing at least 70% by weight or more and having a dryness of 0.70
The mixed refrigerant is sucked and compressed.
【００１４】この請求項３の発明では、圧縮機が、乾き
度０.７５以上のＲ３２冷媒を吸入するから、図３の試
験結果から分かるように、圧縮機の信頼性を最高レベル
まで高めることができる。なお、圧縮機が、Ｒ３２を少
なくとも７０重量％以上含む乾き度が０.７５以上の混
合冷媒を吸入する場合にも、同様の効果が得られる。According to the third aspect of the present invention, since the compressor sucks the R32 refrigerant having a dryness of 0.75 or more, the reliability of the compressor is increased to the highest level as can be seen from the test results of FIG. Can be. The same effect can be obtained when the compressor sucks a mixed refrigerant containing at least 70% by weight of R32 and having a dryness of 0.75 or more.
【００１５】また、請求項４の発明は、請求項１乃至３
のいずれか１つに記載の冷凍装置において、上記圧縮機
の吐出管温度を検出し、この吐出管温度に基づいて、圧
縮機が吸入する冷媒の乾き度を制御する制御手段を備え
たことを特徴としている。[0015] The invention of claim 4 is the invention of claims 1 to 3
The refrigerating apparatus according to any one of the above, further comprising a control unit that detects a discharge pipe temperature of the compressor and controls a dryness of refrigerant sucked by the compressor based on the discharge pipe temperature. Features.
【００１６】この請求項４の発明では、圧縮機の吐出管
温度に基づいて、圧縮機吸入冷媒の乾き度を制御するか
ら、簡単な制御手段で乾き度の制御が可能になる。According to the fourth aspect of the present invention, the dryness of the refrigerant drawn into the compressor is controlled based on the discharge pipe temperature of the compressor. Therefore, the dryness can be controlled by a simple control means.
【００１７】また、請求項５の発明は、請求項１乃至３
のいずれか１つに記載の冷凍装置において、スーパーヒ
ートを検出し、このスーパーヒートに基づいて、圧縮機
が吸入する冷媒の乾き度を制御する制御手段を備えたこ
とを特徴としている。Further, the invention of claim 5 provides the invention according to claims 1 to 3
The refrigerating apparatus according to any one of the above, further comprising control means for detecting superheat and controlling the dryness of the refrigerant drawn by the compressor based on the superheat.
【００１８】この請求項５の発明では、スーパーヒート
に基づいて、圧縮機が吸入する冷媒の乾き度を制御する
から、より精度良く吸入側の乾き度を制御でき、信頼性
の向上を図れる。According to the fifth aspect of the present invention, since the dryness of the refrigerant sucked by the compressor is controlled based on the superheat, the dryness on the suction side can be controlled more accurately, and the reliability can be improved.
【００１９】また、請求項６の発明は、請求項１乃至３
のいずれか１つに記載の冷凍装置において、サブクール
度を検出し、このサブクール度に基づいて、圧縮機が吸
入する冷媒の乾き度を制御する制御手段を備えたことを
特徴としている。Further, the invention of claim 6 is the invention of claims 1 to 3
The refrigerating apparatus according to any one of the above, further comprising a control unit that detects a subcool degree and controls the dryness of the refrigerant sucked by the compressor based on the subcool degree.
【００２０】この請求項６の発明では、サブクール度に
基づいて、圧縮機が吸入する冷媒の乾き度を制御するか
ら、より精度良く吸入側の乾き度を制御でき、信頼性の
向上を図れる。According to the sixth aspect of the present invention, since the dryness of the refrigerant sucked by the compressor is controlled based on the subcool degree, the dryness on the suction side can be controlled more accurately, and the reliability can be improved.
【００２１】また、請求項７の発明は、請求項１乃至３
のいずれか１つに記載の冷凍装置において、蒸発器の出
口の過熱度を制御する制御手段を備えたことを特徴とし
ている。Further, the invention of claim 7 provides the invention according to claims 1 to 3
The refrigerating apparatus according to any one of the above, further comprising control means for controlling the degree of superheat at the outlet of the evaporator.
【００２２】この請求項７の発明では、蒸発器の出口の
加熱度を制御して、蒸発器出口での湿り度を増やすこと
によって、蒸発器(室内機)のファンロータが結露するこ
とを防止できる。また、請求項８の発明は、圧縮機が高
圧ドームタイプであり、暖房の低温運転時(例えば、外
気(−５℃)以下)に、この圧縮機は、乾き度０.６８以上
のＲ３２冷媒、もしくは、Ｒ３２を少なくとも７０重量
％以上含む乾き度が０.６８以上の混合冷媒を吸入して
圧縮し、この圧縮機の吐出温度を、８０〜９０℃に設定
することを特徴としている。この請求項８の発明では、
高圧ドームタイプの圧縮機の吸入側でのＲ３２冷媒の乾
き度を０.６８以上にし、吐出温度を８０〜９０℃にす
るから、圧縮機の信頼性を低下させることなく、Ｒ３２
冷媒の使用が可能になり、信頼性や性能の低下を回避し
つつ、省エネルギーと低ＧＷＰを実現できる。また、請
求項９の発明は、圧縮機が低圧ドームタイプであり、暖
房の低温運転時(例えば、外気(−５℃)以下)に、この圧
縮機は、乾き度０.６５以上のＲ３２冷媒、もしくは、
Ｒ３２を少なくとも７０重量％以上含む乾き度が０.６
５以上の混合冷媒を吸入して圧縮し、この圧縮機の吐出
温度を、６０〜７０℃に設定することを特徴としてい
る。この請求項９の発明では、低圧ドームタイプの圧縮
機の吸入側でのＲ３２冷媒の乾き度を０.６５以上に
し、吐出温度を６０〜７０℃にするから、圧縮機の信頼
性を低下させることなく、Ｒ３２冷媒の使用が可能にな
り、信頼性や性能の低下を回避しつつ、省エネルギーと
低ＧＷＰを実現できる。According to the seventh aspect of the present invention, the degree of heating at the outlet of the evaporator is controlled to increase the degree of wetness at the outlet of the evaporator, thereby preventing condensation on the fan rotor of the evaporator (indoor unit). it can. Further, the invention of claim 8 is characterized in that the compressor is a high-pressure dome type, and when the compressor is operated at a low temperature for heating (for example, outside air (-5 ° C) or less), the compressor has an R32 refrigerant having a dryness of 0.68 or more. Alternatively, a mixed refrigerant containing at least 70% by weight or more of R32 and having a dryness of 0.68 or more is sucked and compressed, and the discharge temperature of the compressor is set at 80 to 90 ° C. In the invention of claim 8,
Since the dryness of the R32 refrigerant at the suction side of the high-pressure dome type compressor is 0.68 or more and the discharge temperature is 80 to 90 ° C, the R32 refrigerant can be used without lowering the reliability of the compressor.
The use of a refrigerant becomes possible, and energy saving and low GWP can be realized while avoiding a decrease in reliability and performance. In a ninth aspect of the present invention, the compressor is a low-pressure dome type, and at the time of low-temperature operation of heating (for example, outside air (−5 ° C.) or less), this compressor uses an R32 refrigerant having a dryness of 0.65 or more Or
The dryness containing at least 70% by weight of R32 is 0.6
It is characterized in that five or more mixed refrigerants are sucked and compressed, and the discharge temperature of the compressor is set at 60 to 70 ° C. According to the ninth aspect of the present invention, the dryness of the R32 refrigerant at the suction side of the low-pressure dome type compressor is 0.65 or more, and the discharge temperature is 60 to 70 ° C., thereby lowering the reliability of the compressor. Without the use of the R32 refrigerant, energy saving and low GWP can be realized while avoiding a decrease in reliability and performance.
【００２３】[0023]
【発明の実施の形態】以下、この発明を図示の実施の形
態により詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.
【００２４】図１に、この発明の冷凍装置の実施形態と
しての空気調和機の冷媒回路を示す。この実施形態は、
Ｒ３２冷媒を使用し、圧縮機１,四路切換弁４,室外熱交
換器２,膨張弁３,バルブ２６,室内熱交換器５,バルブ２
５,気液分離器６,アキュムレータ７が順に接続された冷
媒回路を備える。なお、室外熱交換器２を有する室外ユ
ニット２１は、連絡配管で室内ユニット２２に接続され
ている。FIG. 1 shows a refrigerant circuit of an air conditioner as an embodiment of a refrigeration apparatus of the present invention. This embodiment is
Using R32 refrigerant, compressor 1, four-way switching valve 4, outdoor heat exchanger 2, expansion valve 3, valve 26, indoor heat exchanger 5, valve 2
5, a gas-liquid separator 6, and an accumulator 7 are sequentially provided with a refrigerant circuit. Note that the outdoor unit 21 having the outdoor heat exchanger 2 is connected to the indoor unit 22 by a communication pipe.
【００２５】また、この実施形態は、マイクロコンピュ
ータからなる制御部８を備え、この制御部８は、圧縮機
１の吸入側配管に取り付けた温度センサ１３と、吐出側
配管に取り付けた温度センサ１２と、室外熱交換器２に
取り付けた温度センサ１７と、室内熱交換器５に取り付
けた温度センサ１５、および室外の気温を検出する温度
センサ１１と室内の温度を検出する温度センサ１６に接
続されている。Further, this embodiment includes a control unit 8 composed of a microcomputer. The control unit 8 includes a temperature sensor 13 attached to the suction pipe of the compressor 1 and a temperature sensor 12 attached to the discharge pipe. And a temperature sensor 17 attached to the outdoor heat exchanger 2, a temperature sensor 15 attached to the indoor heat exchanger 5, a temperature sensor 11 for detecting outdoor air temperature, and a temperature sensor 16 for detecting indoor temperature. ing.
【００２６】この実施形態の制御部８の動作を、図２の
フローチャートを参照しながら説明する。まず、ステッ
プＳ１で、この空気調和機が、Ｒ３２冷媒を使用してい
るか否かを判断し、Ｒ３２冷媒を使用していると判断し
たときには、次のステップＳ２に進む。このＲ３２冷媒
を使用しているか否かの判断は、予め入力された情報に
基づいて判断するものであってもよい。また、ステップ
Ｓ１で否と判断した場合には、ステップＳ５に進み、従
来制御を引き続いて実行する。この従来制御とは、例え
ば、温度センサ１２から得た吐出管温度Ｔdisに基づい
て行なう圧縮機１と膨張弁３の制御である。The operation of the control section 8 of this embodiment will be described with reference to the flowchart of FIG. First, in step S1, it is determined whether or not the air conditioner is using the R32 refrigerant. When it is determined that the air conditioner is using the R32 refrigerant, the process proceeds to the next step S2. The determination as to whether or not the R32 refrigerant is used may be based on information input in advance. On the other hand, if it is determined as NO at step S1, the process proceeds to step S5, and the conventional control is continuously executed. The conventional control is, for example, control of the compressor 1 and the expansion valve 3 performed based on the discharge pipe temperature Tdis obtained from the temperature sensor 12.
【００２７】次に、上記ステップＳ２では、吐出管温度
Ｔdisが１３５℃〜１２５℃の内の所定値以上になった
か否かを判断し、上記所定値以上になったと判断すれ
ば、ステップＳ３に進み、上記所定値以上になっていな
いと判断すれば、ステップＳ５に進む。Next, in step S2, it is determined whether or not the discharge pipe temperature Tdis has become equal to or higher than a predetermined value in the range of 135 ° C. to 125 ° C. If it is determined that the temperature has become equal to or higher than the predetermined value, the process proceeds to step S3. The process proceeds to step S5 if it is determined that the value does not exceed the predetermined value.
【００２８】ステップＳ３では、スーパーヒートＳＨ
(図５参照)を検出することで、圧縮機１の吸入側での冷
媒の湿り度を検出する。すなわち、温度センサ１３から
得た圧縮機１の吸入側の温度Ｔsucと、温度センサ１７
あるいは１５から得た蒸発器の温度(冷房時は室内熱交
換器５の温度Ｔin)との差であるスーパーヒートＳＨを
検出する。そして、圧縮機１の回転数を増加させる操作
または膨張弁３を開く操作の少なくとも一方の操作を実
行して、スーパーヒートＳＨを減少させて、湿り度を増
やす。これにより、圧縮機吐出側の冷媒温度を下げて、
信頼性の低下や能力低下を回避する。In step S3, the super heat SH
By detecting (see FIG. 5), the degree of wetness of the refrigerant on the suction side of the compressor 1 is detected. That is, the temperature Tsuc on the suction side of the compressor 1 obtained from the temperature sensor 13 and the temperature sensor 17
Alternatively, the superheat SH, which is the difference from the temperature of the evaporator obtained in step 15 (the temperature Tin of the indoor heat exchanger 5 during cooling), is detected. Then, at least one of the operation of increasing the rotation speed of the compressor 1 and the operation of opening the expansion valve 3 is executed to reduce the superheat SH and increase the wetness. This reduces the refrigerant temperature on the compressor discharge side,
Avoid loss of reliability and performance.
【００２９】次に、ステップＳ４に進み、上記スーパー
ヒートＳＨが０.８５〜０.７５の内の所定値以上である
か否かを判断し、上記所定値以上であると判断すれば、
ステップＳ５に進んで、上記従来制御を引き続いて実行
する。Then, the process proceeds to a step S4, wherein it is determined whether or not the superheat SH is equal to or more than a predetermined value of 0.85-0.75.
Proceeding to step S5, the above-described conventional control is continuously executed.
【００３０】一方、ステップＳ４で、上記スーパーヒー
トＳＨが０.８５〜０.７５の内の上記所定値以上でない
(湿り度が過剰)と判断すれば、ステップＳ６に進んで、
圧縮機１の回転数を減少させて、冷媒の循環量を減少さ
せる。これにより、上記スーパーヒートＳＨを所定の値
だけ増加させて、湿り度を減少させ、乾き度を適正値
(０.８５〜０.７５)に保つ。On the other hand, in step S4, the superheat SH is not greater than the predetermined value of 0.85-0.75.
If it is determined that (wetness is excessive), the process proceeds to step S6,
The number of rotations of the compressor 1 is reduced to reduce the circulation amount of the refrigerant. As a result, the superheat SH is increased by a predetermined value, the wetness is reduced, and the dryness is adjusted to an appropriate value.
(0.85-0.75).
【００３１】次に、ステップＳ７に進んで、再度ステッ
プＳ３,Ｓ４を実行し、スーパーヒートを所定値だけ減
少させて、吐出管温度を下げる操作を行ない、スーパー
ヒートが適正値(０.８５〜０.７５)を下回っている場合
には、ステップＳ６に戻って、スーパーヒートを増加さ
せる。一方、ステップＳ７において、スーパーヒートが
上記適正値(０.８５〜０.７５)以上になっていると判断
すれば、ステップＳ８に進み、膨張弁３を絞って、スー
パーヒートを減少させ、湿り度を増加させて吐出温度Ｔ
disを下げてから、ステップＳ９に進む。Next, proceeding to step S7, steps S3 and S4 are executed again, an operation for reducing the superheat by a predetermined value and lowering the discharge pipe temperature is performed, and the superheat is set to a proper value (0.85-85). If it is below 0.75), the flow returns to step S6 to increase the superheat. On the other hand, if it is determined in step S7 that the superheat is equal to or more than the appropriate value (0.85 to 0.75), the process proceeds to step S8, where the expansion valve 3 is squeezed to reduce the superheat and reduce the wetness. Discharge temperature T
After lowering dis, the process proceeds to step S9.
【００３２】ステップＳ９では、再び、ステップＳ３と
Ｓ４の動作を行なう。すなわち、スーパーヒートＳＨを
減少させる操作を行なって、吐出管温度を下げてから、
スーパーヒートＳＨが信頼性が十分になる所定値(０.８
５〜０.７５)以上であれば、ステップＳ５に進み、スー
パーヒートＳＨが上記所定値に達していなければ、ステ
ップＳ６に戻って、再度、スーパーヒートを増加させる
操作を実行する。In step S9, the operations in steps S3 and S4 are performed again. That is, after performing the operation of reducing the superheat SH and lowering the discharge pipe temperature,
A predetermined value (0.8) at which the reliability of the superheat SH is sufficient.
If it is 5 to 0.75 or more, the process proceeds to step S5. If the superheat SH has not reached the predetermined value, the process returns to step S6, and the operation of increasing the superheat is performed again.
【００３３】このように、この実施形態では、吐出管温
度が所定値以上になると、スーパーヒートＳＨを減じ
て、湿り度を増やし、吐出管温度を下げる(ステップＳ
２,Ｓ３)。次に、このスーパーヒートＳＨが不足したと
判断すれば、圧縮機１の回転数を減らして、圧縮機１の
信頼性を十分に確保できる適正値(０.８５〜０.７５)ま
で、スーパーヒートを増加させて乾き度を増加させる。As described above, in this embodiment, when the discharge pipe temperature exceeds a predetermined value, the superheat SH is reduced, the wetness is increased, and the discharge pipe temperature is lowered (step S10).
2, S3). Next, if it is determined that the superheat SH is insufficient, the number of revolutions of the compressor 1 is reduced, and the superheat SH is reduced to an appropriate value (0.85-0.75) that can sufficiently secure the reliability of the compressor 1. Increase heat to increase dryness.
【００３４】この制御によって、圧縮機１が吸入するＲ
３２冷媒の乾き度を、圧縮機１の信頼性を十分に確保で
きる範囲において、乾き度(スーパーヒート)を低減し
て、吐出温度を下げることができ、信頼性(圧縮機潤滑
性,摩耗など)の低下や能力(暖房低温性能)低下を回避し
つつ、省エネルギーと低ＧＷＰを実現できる。By this control, R
As long as the dryness of the refrigerant 32 is within the range that the reliability of the compressor 1 can be sufficiently ensured, the dryness (superheat) can be reduced, the discharge temperature can be reduced, and the reliability (compressor lubricity, wear, etc.) can be reduced. ) And performance (low-temperature heating performance) can be avoided, and energy saving and low GWP can be realized.
【００３５】尚、上記実施形態では、乾き度(スーパー
ヒート)の適正値を、０.８５〜０.７５の範囲に設定し
たが、０.６５以上もしくは、０.７０以上または０.７
５以上に設定してもよい。また、上記実施形態では、ス
ーパーヒートに基づいて、圧縮機１と膨張弁３を制御し
たが、圧縮機の吐出管温度あるいはサブクール度(ＳＣ)
に基づいて、圧縮機と膨張弁を制御してもよい。また、
上記実施形態では、Ｒ３２冷媒単体を使用したが、Ｒ３
２を少なくとも７０重量％以上含んだ混合冷媒を使用す
る場合にも同様の効果が得られる。すなわち、Ｒ３２を
少なくとも７０重量％以上含んだ混合冷媒であれば、擬
似共沸となり、Ｒ２２冷媒に対するＲ３２冷媒のメリッ
ト(省エネルギー,低ＧＷＰ)を発揮できる。また、圧縮
機としては、高圧ドームタイプと低圧ドームタイプとが
ある。高圧ドームタイプとは、圧縮機のモータが吐出ガ
スなどの高圧雰囲気にあるものを言い、低圧ドームタイ
プとは、圧縮機のモータが低圧ガスまたは液などの低圧
雰囲気下にある状態の圧縮機形式を言う。低圧ドームタ
イプの圧縮機を採用した場合には、高圧ドームタイプの
圧縮機を採用した場合に比べて、圧縮機の吐出温度が１
５℃〜２０℃だけ低い。したがって、Ｒ３２冷媒を採用
した空気調和機において、低圧ドームタイプの圧縮機を
採用した場合には、圧縮機が吸入する冷媒の乾き度を、
０.６５〜０.９５に設定して、圧縮機の吐出温度を、６
０〜７０℃に制御する。これにより、圧縮機の信頼性や
性能の低下を回避しつつ、低ＧＷＰおよび省エネルギー
で低コストな空気調和機を実現できる。In the above embodiment, the appropriate value of the degree of dryness (superheat) is set in the range of 0.85 to 0.75, but it is 0.65 or more, 0.70 or more, or 0.7.
It may be set to 5 or more. In the above embodiment, the compressor 1 and the expansion valve 3 are controlled based on the superheat. However, the discharge pipe temperature of the compressor or the subcool degree (SC) is controlled.
May control the compressor and the expansion valve. Also,
In the above embodiment, the R32 refrigerant alone was used.
The same effect can be obtained when a mixed refrigerant containing at least 70% by weight of 2 is used. That is, a mixed refrigerant containing at least 70% by weight or more of R32 becomes pseudo-azeotropic, and can exhibit the merits (energy saving, low GWP) of the R32 refrigerant over the R22 refrigerant. As the compressor, there are a high pressure dome type and a low pressure dome type. The high-pressure dome type is a compressor type in which the compressor motor is in a high-pressure atmosphere such as discharge gas, and the low-pressure dome type is a compressor type in which the compressor motor is in a low-pressure atmosphere such as low-pressure gas or liquid. Say When a low-pressure dome-type compressor is used, the discharge temperature of the compressor is 1 compared to when a high-pressure dome-type compressor is used.
Lower by 5 ° C to 20 ° C. Therefore, in the air conditioner employing the R32 refrigerant, when a low-pressure dome type compressor is employed, the dryness of the refrigerant sucked by the compressor is determined by:
0.65 to 0.95, and set the discharge temperature of the compressor to 6
Control at 0-70 ° C. Thus, it is possible to realize a low GWP, energy-saving and low-cost air conditioner while avoiding a decrease in the reliability and performance of the compressor.
【００３６】また、上記実施形態において、制御部８
は、蒸発器となる室内熱交換器５の出口での冷媒の過熱
度を制御して、室内熱交換器５出口での冷媒の湿り度を
増やし、室内熱交換器５のファンロータが結露すること
を防止するようにしてもよい。なお、この結露防止制御
は、Ｒ３２とＲ１２５を、５０ｗｔ％ずつ含有した混合
冷媒にも適用でき、Ｒ４０７Ｃ(Ｒ３２/Ｒ１２５/Ｒ１
３４ａ：２３/２５/５２ｗｔ％)を使用する場合にも適
用可能である。In the above embodiment, the control unit 8
Controls the degree of superheat of the refrigerant at the outlet of the indoor heat exchanger 5 serving as an evaporator, increases the wettability of the refrigerant at the outlet of the indoor heat exchanger 5, and causes the fan rotor of the indoor heat exchanger 5 to condense. This may be prevented. Note that this dew condensation prevention control can be applied to a mixed refrigerant containing R32 and R125 in an amount of 50 wt% each, and R407C (R32 / R125 / R1
34a: 23/25/52 wt%).
【００３７】[0037]
【発明の効果】以上より明らかなように、請求項１の発
明の冷凍装置は、圧縮機が、乾き度０.６５以上のＲ３
２冷媒(もしくはＲ３２を少なくとも７０重量％以上含
む混合冷媒)を吸入して圧縮するから、図３の試験結果
から分かるように、圧縮機の信頼性を低下させることな
く、Ｒ３２冷媒の使用が可能になり、信頼性や性能の低
下を回避しつつ、省エネルギーと低ＧＷＰを実現でき
る。As is apparent from the above description, in the refrigeration apparatus according to the first aspect of the present invention, the compressor has an R3 with a dryness of 0.65 or more.
Since two refrigerants (or a refrigerant mixture containing at least 70% by weight of R32) are sucked and compressed, as can be seen from the test results in FIG. 3, the R32 refrigerant can be used without reducing the reliability of the compressor. Thus, energy saving and low GWP can be realized while avoiding a decrease in reliability and performance.
【００３８】また、請求項２の発明の冷凍装置は、圧縮
機が、乾き度０.７０以上のＲ３２冷媒(もしくはＲ３２
を少なくとも７０重量％以上含む混合冷媒)を吸入する
から、圧縮機の信頼性を一層向上できる。Further, in the refrigeration apparatus according to the second aspect of the present invention, the compressor includes an R32 refrigerant (or R32 refrigerant) having a dryness of 0.70 or more.
(A mixed refrigerant containing at least 70% by weight or more), the reliability of the compressor can be further improved.
【００３９】また、請求項３の発明の冷凍装置は、圧縮
機が、乾き度０.７５以上のＲ３２冷媒(もしくはＲ３２
を少なくとも７０重量％以上含む混合冷媒)を吸入する
から、図３の試験結果から分かるように、圧縮機の信頼
性を最高レベルまで高めることができる。Further, in the refrigeration apparatus according to the third aspect of the present invention, the compressor includes an R32 refrigerant (or R32 refrigerant) having a dryness of 0.75 or more.
), The reliability of the compressor can be increased to the highest level, as can be seen from the test results in FIG.
【００４０】また、請求項４の発明は、請求項１乃至３
のいずれか１つに記載の冷凍装置において、上記圧縮機
の吐出管温度を検出し、この吐出管温度に基づいて、圧
縮機が吸入する冷媒の乾き度を制御する制御手段を備え
た。この請求項４の発明では、圧縮機の吐出管温度に基
づいて、圧縮機吸入冷媒の乾き度を制御するから、簡単
な制御手段で乾き度の制御が可能になる。Further, the invention of claim 4 is the invention of claims 1 to 3
The refrigerating apparatus according to any one of the above, further comprising a control means for detecting a discharge pipe temperature of the compressor, and controlling a dryness of refrigerant sucked by the compressor based on the discharge pipe temperature. According to the fourth aspect of the present invention, since the dryness of the refrigerant drawn into the compressor is controlled based on the temperature of the discharge pipe of the compressor, the dryness can be controlled by simple control means.
【００４１】また、請求項５の発明は、請求項１乃至３
のいずれか１つに記載の冷凍装置において、スーパーヒ
ートを検出し、このスーパーヒートに基づいて、圧縮機
が吸入する冷媒の乾き度を制御する制御手段を備えた。
この請求項５の発明では、スーパーヒートに基づいて、
圧縮機が吸入する冷媒の乾き度を制御するから、より精
度良く吸入側の乾き度を制御でき、信頼性の向上を図れ
る。Further, the invention of claim 5 is the invention of claims 1 to 3
The refrigerating apparatus according to any one of the above, further comprising control means for detecting superheat and controlling the dryness of the refrigerant sucked by the compressor based on the superheat.
In the invention of claim 5, based on the superheat,
Since the dryness of the refrigerant sucked by the compressor is controlled, the dryness on the suction side can be more accurately controlled, and reliability can be improved.
【００４２】また、請求項６の発明は、請求項１乃至３
のいずれか１つに記載の冷凍装置において、サブクール
度を検出し、このサブクール度に基づいて、圧縮機が吸
入する冷媒の乾き度を制御する制御手段を備えた。この
請求項６の発明では、サブクール度に基づいて、圧縮機
が吸入する冷媒の乾き度を制御するから、より精度良く
吸入側の乾き度を制御でき、信頼性の向上を図れる。Further, the invention of claim 6 relates to claims 1 to 3
The refrigerating apparatus according to any one of the above, further comprising control means for detecting the degree of subcooling and controlling the degree of dryness of the refrigerant drawn by the compressor based on the degree of subcooling. According to the sixth aspect of the invention, since the dryness of the refrigerant sucked by the compressor is controlled based on the subcool degree, the dryness on the suction side can be more accurately controlled, and the reliability can be improved.
【００４３】また、請求項７の発明は、請求項１乃至３
のいずれか１つに記載の冷凍装置において、蒸発器の出
口の過熱度を制御する制御手段を備えた。この請求項７
の発明では、蒸発器の出口の加熱度を制御して、蒸発器
出口での湿り度を増やすことによって、蒸発器(室内機)
のファンロータが結露することを防止できる。また、請
求項８の発明は、高圧ドームタイプの圧縮機の吸入側で
のＲ３２冷媒の乾き度を０.６８以上にし、吐出温度を
８０〜９０℃にするから、圧縮機の信頼性を低下させる
ことなく、Ｒ３２冷媒の使用が可能になり、信頼性や性
能の低下を回避しつつ、省エネルギーと低ＧＷＰを実現
できる。また、請求項９の発明は、低圧ドームタイプの
圧縮機の吸入側でのＲ３２冷媒の乾き度を０.６５以上
にし、吐出温度を６０〜７０℃にするから、圧縮機の信
頼性を低下させることなく、Ｒ３２冷媒の使用が可能に
なり、信頼性や性能の低下を回避しつつ、省エネルギー
と低ＧＷＰを実現できる。Further, the invention of claim 7 is the first to third aspects of the present invention.
The refrigerating apparatus according to any one of the above, further comprising control means for controlling the degree of superheat at the outlet of the evaporator. This claim 7
In the invention of the evaporator (indoor unit) by controlling the degree of heating at the outlet of the evaporator to increase the degree of wetness at the outlet of the evaporator
Of the fan rotor can be prevented. According to the invention of claim 8, since the dryness of the R32 refrigerant at the suction side of the high-pressure dome type compressor is 0.68 or more and the discharge temperature is 80 to 90 ° C, the reliability of the compressor is reduced. Without the use of the R32 refrigerant, it is possible to use the R32 refrigerant, thereby realizing energy saving and low GWP while avoiding deterioration in reliability and performance. According to the ninth aspect of the present invention, the dryness of the R32 refrigerant at the suction side of the low-pressure dome type compressor is 0.65 or more, and the discharge temperature is 60 to 70 ° C. Without the use of the R32 refrigerant, it is possible to use the R32 refrigerant, thereby realizing energy saving and low GWP while avoiding deterioration in reliability and performance.
【図１】 この発明の冷凍機の実施の形態としての空気
調和機の実施形態の冷媒回路図である。FIG. 1 is a refrigerant circuit diagram of an embodiment of an air conditioner as an embodiment of a refrigerator of the present invention.
【図２】 上記実施形態の制御部の動作を説明するフロ
ーチャートである。FIG. 2 is a flowchart illustrating an operation of a control unit according to the embodiment.
【図３】 冷媒の乾き度毎の圧縮機の信頼性評価試験結
果を示す図表である。FIG. 3 is a table showing the results of a reliability evaluation test of a compressor for each degree of dryness of a refrigerant.
【図４】 実際の冷凍機におけるモリエル線図の一例を
示す図である。FIG. 4 is a diagram showing an example of a Mollier diagram in an actual refrigerator.
【図５】 モリエル線図におけるスーパーヒートＳＨと
サブクール度ＳＣを示す図である。FIG. 5 is a diagram showing a superheat SH and a subcool degree SC in a Mollier diagram.
１…圧縮機、２…室外熱交換器、３…膨張弁、４…四路
切換弁、５…室内熱交換器、８…制御部、１１,１２,１
３,１５,１６,１７…温度センサ。DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Outdoor heat exchanger, 3 ... Expansion valve, 4 ... Four-way switching valve, 5 ... Indoor heat exchanger, 8 ... Control part, 11, 12, 1
3, 15, 16, 17 ... temperature sensors.
Claims (9)
３２冷媒、もしくは、Ｒ３２を少なくとも７０重量％以
上含む乾き度が０.６５以上の混合冷媒を吸入して圧縮
することを特徴とする冷凍装置。The compressor (1) has a dryness of 0.65 or more.
32. A refrigerating apparatus, wherein 32 refrigerants or a refrigerant mixture containing at least 70% by weight or more of R32 and having a dryness of 0.65 or more is sucked and compressed.
３２冷媒、もしくは、Ｒ３２を少なくとも７０重量％以
上含む乾き度が０.７０以上の混合冷媒を吸入して圧縮
することを特徴とする冷凍装置。2. A compressor (1) having a dryness of 0.70 or more.
A refrigerating apparatus, wherein 32 refrigerants or a refrigerant mixture containing at least 70% by weight or more of R32 and having a dryness of 0.70 or more is sucked and compressed.
３２冷媒、もしくは、Ｒ３２を少なくとも７０重量％以
上含む乾き度が０.７５以上の混合冷媒を吸入して圧縮
することを特徴とする冷凍装置。3. A compressor (1) having a dryness of 0.75 or more.
A refrigerating apparatus, wherein 32 refrigerants or a mixed refrigerant containing at least 70% by weight or more of R32 and having a dryness of 0.75 or more is sucked and compressed.
冷凍装置において、上記圧縮機(１)の吐出管温度を検出
し、この吐出管温度に基づいて、圧縮機が吸入する冷媒
の乾き度を制御する制御手段(８)を備えたことを特徴と
する冷凍装置。4. The refrigerating apparatus according to claim 1, wherein a temperature of a discharge pipe of the compressor (1) is detected, and a refrigerant sucked by the compressor is detected based on the temperature of the discharge pipe. A refrigerating apparatus comprising a control means (8) for controlling the degree of dryness.
冷凍装置において、スーパーヒート(ＳＨ)を検出し、こ
のスーパーヒートに基づいて、圧縮機(１)が吸入する冷
媒の乾き度を制御する制御手段(８)を備えたことを特徴
とする冷凍装置。5. The refrigerating apparatus according to claim 1, wherein a superheat (SH) is detected, and based on the superheat, the dryness of the refrigerant sucked by the compressor (1). A refrigerating apparatus comprising control means (8) for controlling the temperature of the refrigerating machine.
冷凍装置において、サブクール度(ＳＣ)を検出し、この
サブクール度に基づいて、圧縮機(１)が吸入する冷媒の
乾き度を制御する制御手段(８)を備えたことを特徴とす
る冷凍装置。6. The refrigerating apparatus according to claim 1, wherein a subcool degree (SC) is detected, and based on the subcool degree, the dryness of the refrigerant sucked by the compressor (1). A refrigerating apparatus comprising control means (8) for controlling the temperature of the refrigerating machine.
冷凍装置において、蒸発器(５,２)の出口の過熱度を制
御する制御手段(８)を備えたことを特徴とする冷凍装
置。7. The refrigeration apparatus according to claim 1, further comprising control means (8) for controlling the degree of superheat at the outlet of the evaporator (5, 2). Refrigeration equipment.
圧縮機は、乾き度０.６８以上のＲ３２冷媒、もしく
は、Ｒ３２を少なくとも７０重量％以上含む乾き度が
０.６８以上の混合冷媒を吸入して圧縮し、 この圧縮機の吐出温度を、８０〜９０℃に設定すること
を特徴とする冷凍装置。8. The compressor is of a high-pressure dome type, and this compressor uses an R32 refrigerant having a dryness of 0.68 or more or a mixed refrigerant having a dryness of 0.68 or more containing at least 70% by weight of R32. A refrigerating apparatus characterized in that the compressor is sucked and compressed, and the discharge temperature of the compressor is set at 80 to 90 ° C.
くは、Ｒ３２を少なくとも７０重量％以上含む乾き度が
０.６５以上の混合冷媒を吸入して圧縮し、 この圧縮機の吐出温度を、６０〜７０℃に設定すること
を特徴とする冷凍装置。9. The compressor is a low-pressure dome type compressor, and the compressor uses an R32 refrigerant having a dryness of 0.65 or more, or a mixed refrigerant having a dryness of 0.65 or more containing at least 70% by weight of R32. A refrigerating apparatus characterized in that the compressor is sucked and compressed, and the discharge temperature of the compressor is set at 60 to 70 ° C.
Priority Applications (13)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000222450A JP3956589B2 (en) | 1999-10-18 | 2000-07-24 | Refrigeration equipment |
| ES06025814.2T ES2620815T3 (en) | 1999-10-18 | 2000-10-12 | Cooling device |
| EP06025814.2A EP1762794B1 (en) | 1999-10-18 | 2000-10-12 | Refrigerating device |
| EP00966426A EP1225400B1 (en) | 1999-10-18 | 2000-10-12 | Refrigerating device |
| KR10-2002-7004959A KR100482539B1 (en) | 1999-10-18 | 2000-10-12 | Refrigerating device |
| PCT/JP2000/007067 WO2001029489A1 (en) | 1999-10-18 | 2000-10-12 | Refrigerating device |
| AT00966426T ATE380987T1 (en) | 1999-10-18 | 2000-10-12 | REFRIGERATOR |
| ES00966426T ES2296645T3 (en) | 1999-10-18 | 2000-10-12 | REFRIGERATION DEVICE |
| CNB031603777A CN100449224C (en) | 1999-10-18 | 2000-10-12 | Freezing equipment |
| US10/110,930 US6581397B1 (en) | 1999-10-18 | 2000-10-12 | Refrigerating device |
| AU76841/00A AU773284B2 (en) | 1999-10-18 | 2000-10-12 | Refrigerating device |
| CNB008145148A CN1149366C (en) | 1999-10-18 | 2000-10-12 | Refrigerating device |
| DE60037445T DE60037445T2 (en) | 1999-10-18 | 2000-10-12 | COOLING DEVICE |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11-295258 | 1999-10-18 | ||
| JP29525899 | 1999-10-18 | ||
| JP2000222450A JP3956589B2 (en) | 1999-10-18 | 2000-07-24 | Refrigeration equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2001194015A true JP2001194015A (en) | 2001-07-17 |
| JP3956589B2 JP3956589B2 (en) | 2007-08-08 |
Family
ID=26560185
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000222450A Expired - Lifetime JP3956589B2 (en) | 1999-10-18 | 2000-07-24 | Refrigeration equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3956589B2 (en) |
Cited By (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2006028218A1 (en) * | 2004-09-09 | 2006-03-16 | Daikin Industries, Ltd. | Refrigerating apparatus |
| JP2007225264A (en) * | 2006-02-27 | 2007-09-06 | Mitsubishi Electric Corp | Air conditioner |
| WO2013088638A1 (en) * | 2011-12-14 | 2013-06-20 | パナソニック株式会社 | Refrigerating cycle device |
| WO2013146731A1 (en) | 2012-03-28 | 2013-10-03 | ダイキン工業株式会社 | Refrigeration device |
| JP2014129941A (en) * | 2012-12-28 | 2014-07-10 | Daikin Ind Ltd | Refrigeration device |
| JP2014129987A (en) * | 2012-12-28 | 2014-07-10 | Daikin Ind Ltd | Refrigeration device |
| JP2014129986A (en) * | 2012-12-28 | 2014-07-10 | Daikin Ind Ltd | Refrigeration device |
| WO2014119149A1 (en) | 2013-01-29 | 2014-08-07 | ダイキン工業株式会社 | Air conditioner |
| EP2765370A1 (en) | 2013-02-08 | 2014-08-13 | Panasonic Corporation | Refrigeration cycle apparatus and hot water generator provided with the same |
| WO2014129473A1 (en) * | 2013-02-19 | 2014-08-28 | 三菱電機株式会社 | Air conditioning device |
| WO2014155545A1 (en) * | 2013-03-27 | 2014-10-02 | 日立アプライアンス株式会社 | Air conditioner |
| WO2014156313A1 (en) * | 2013-03-27 | 2014-10-02 | 日立アプライアンス株式会社 | Air conditioner and method for operating air conditioner |
| JP2015042009A (en) * | 2013-08-20 | 2015-03-02 | 日立アプライアンス株式会社 | Permanent magnet type motor, compressor employing the same, and refrigeration cycle device |
| JP2015075294A (en) * | 2013-10-10 | 2015-04-20 | 日立アプライアンス株式会社 | Air conditioner |
| JP2015081722A (en) * | 2013-10-23 | 2015-04-27 | 日立アプライアンス株式会社 | Air conditioner |
| WO2015174054A1 (en) | 2014-05-12 | 2015-11-19 | パナソニックＩｐマネジメント株式会社 | Refrigeration cycle device |
| JP2015218959A (en) * | 2014-05-19 | 2015-12-07 | リンナイ株式会社 | Heat pump heating device |
| JP2016080331A (en) * | 2014-10-22 | 2016-05-16 | 東芝キヤリア株式会社 | Refrigeration cycle device |
| JP2016183859A (en) * | 2016-07-28 | 2016-10-20 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Air conditioner |
| JP2017138096A (en) * | 2017-03-09 | 2017-08-10 | 三菱電機株式会社 | Refrigeration cycle device |
| CN114608181A (en) * | 2022-03-21 | 2022-06-10 | 青岛海尔空调电子有限公司 | Control method and device of electronic expansion valve, medium and air source heat pump unit |
| JP7089153B2 (en) | 2018-01-15 | 2022-06-22 | ダイキン工業株式会社 | Ice making system |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014066471A (en) * | 2012-09-27 | 2014-04-17 | Daikin Ind Ltd | Air conditioning equipment |
| JP6000053B2 (en) | 2012-10-15 | 2016-09-28 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Air conditioner |
| JP5927633B2 (en) | 2012-11-06 | 2016-06-01 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Air conditioner |
| US10247459B2 (en) | 2015-05-13 | 2019-04-02 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus |
-
2000
- 2000-07-24 JP JP2000222450A patent/JP3956589B2/en not_active Expired - Lifetime
Cited By (45)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1795833A4 (en) * | 2004-09-09 | 2014-12-24 | Daikin Ind Ltd | Refrigerating apparatus |
| EP1795833A1 (en) * | 2004-09-09 | 2007-06-13 | Daikin Industries, Ltd. | Refrigerating apparatus |
| AU2005280900B2 (en) * | 2004-09-09 | 2009-03-05 | Daikin Industries, Ltd. | Refrigeration apparatus |
| WO2006028218A1 (en) * | 2004-09-09 | 2006-03-16 | Daikin Industries, Ltd. | Refrigerating apparatus |
| JP2007225264A (en) * | 2006-02-27 | 2007-09-06 | Mitsubishi Electric Corp | Air conditioner |
| JP4619303B2 (en) * | 2006-02-27 | 2011-01-26 | 三菱電機株式会社 | Air conditioner |
| JP2013124800A (en) * | 2011-12-14 | 2013-06-24 | Panasonic Corp | Refrigerating cycle device |
| WO2013088638A1 (en) * | 2011-12-14 | 2013-06-20 | パナソニック株式会社 | Refrigerating cycle device |
| WO2013146731A1 (en) | 2012-03-28 | 2013-10-03 | ダイキン工業株式会社 | Refrigeration device |
| US20150075202A1 (en) * | 2012-03-28 | 2015-03-19 | Daikin Industries, Ltd. | Refrigeration device |
| JP2014129941A (en) * | 2012-12-28 | 2014-07-10 | Daikin Ind Ltd | Refrigeration device |
| JP2014129987A (en) * | 2012-12-28 | 2014-07-10 | Daikin Ind Ltd | Refrigeration device |
| JP2014129986A (en) * | 2012-12-28 | 2014-07-10 | Daikin Ind Ltd | Refrigeration device |
| WO2014119149A1 (en) | 2013-01-29 | 2014-08-07 | ダイキン工業株式会社 | Air conditioner |
| US20150362199A1 (en) * | 2013-01-29 | 2015-12-17 | Daikin Industries, Ltd. | Air conditioning apparatus |
| JP2014167381A (en) * | 2013-01-29 | 2014-09-11 | Daikin Ind Ltd | Air conditioning device |
| AU2013375955B2 (en) * | 2013-01-29 | 2016-04-07 | Daikin Industries, Ltd. | Air conditioning apparatus |
| US10234151B2 (en) | 2013-01-29 | 2019-03-19 | Daikin Industries, Ltd. | Air conditioning apparatus |
| JP2014169854A (en) * | 2013-02-08 | 2014-09-18 | Panasonic Corp | Refrigeration cycle device and hot water generation device including the same |
| EP2765370A1 (en) | 2013-02-08 | 2014-08-13 | Panasonic Corporation | Refrigeration cycle apparatus and hot water generator provided with the same |
| WO2014129473A1 (en) * | 2013-02-19 | 2014-08-28 | 三菱電機株式会社 | Air conditioning device |
| WO2014128830A1 (en) * | 2013-02-19 | 2014-08-28 | 三菱電機株式会社 | Air conditioning device |
| JP5992089B2 (en) * | 2013-02-19 | 2016-09-14 | 三菱電機株式会社 | Air conditioner |
| CN104838219B (en) * | 2013-02-19 | 2017-03-15 | 三菱电机株式会社 | Conditioner |
| US10107533B2 (en) | 2013-02-19 | 2018-10-23 | Mitsubishi Electric Corporation | Air-conditioning apparatus with subcooling heat exchanger |
| CN104838219A (en) * | 2013-02-19 | 2015-08-12 | 三菱电机株式会社 | Air conditioning device |
| WO2014155545A1 (en) * | 2013-03-27 | 2014-10-02 | 日立アプライアンス株式会社 | Air conditioner |
| JP2014190632A (en) * | 2013-03-27 | 2014-10-06 | Hitachi Appliances Inc | Air conditioner and air conditioner operation method |
| CN106839499A (en) * | 2013-03-27 | 2017-06-13 | 江森自控日立空调技术（香港）有限公司 | The method of operation of air conditioner and air conditioner |
| JPWO2014155545A1 (en) * | 2013-03-27 | 2017-02-16 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Air conditioner |
| WO2014156313A1 (en) * | 2013-03-27 | 2014-10-02 | 日立アプライアンス株式会社 | Air conditioner and method for operating air conditioner |
| CN106839499B (en) * | 2013-03-27 | 2019-05-21 | 日立江森自控空调有限公司 | The method of operation of air conditioner and air conditioner |
| CN105074353A (en) * | 2013-03-27 | 2015-11-18 | 日立空调·家用电器株式会社 | Air conditioner and method for operating air conditioner |
| CN105074353B (en) * | 2013-03-27 | 2017-03-15 | 江森自控日立空调技术（香港）有限公司 | Air conditioner and the method for operation of air conditioner |
| JP2015042009A (en) * | 2013-08-20 | 2015-03-02 | 日立アプライアンス株式会社 | Permanent magnet type motor, compressor employing the same, and refrigeration cycle device |
| JP2015075294A (en) * | 2013-10-10 | 2015-04-20 | 日立アプライアンス株式会社 | Air conditioner |
| JP2015081722A (en) * | 2013-10-23 | 2015-04-27 | 日立アプライアンス株式会社 | Air conditioner |
| WO2015174054A1 (en) | 2014-05-12 | 2015-11-19 | パナソニックＩｐマネジメント株式会社 | Refrigeration cycle device |
| JP2015218959A (en) * | 2014-05-19 | 2015-12-07 | リンナイ株式会社 | Heat pump heating device |
| JP2016080331A (en) * | 2014-10-22 | 2016-05-16 | 東芝キヤリア株式会社 | Refrigeration cycle device |
| JP2016183859A (en) * | 2016-07-28 | 2016-10-20 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Air conditioner |
| JP2017138096A (en) * | 2017-03-09 | 2017-08-10 | 三菱電機株式会社 | Refrigeration cycle device |
| JP7089153B2 (en) | 2018-01-15 | 2022-06-22 | ダイキン工業株式会社 | Ice making system |
| CN114608181A (en) * | 2022-03-21 | 2022-06-10 | 青岛海尔空调电子有限公司 | Control method and device of electronic expansion valve, medium and air source heat pump unit |
| CN114608181B (en) * | 2022-03-21 | 2023-12-26 | 青岛海尔空调电子有限公司 | Control method and device for electronic expansion valve, medium and air source heat pump unit |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3956589B2 (en) | 2007-08-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2001194015A (en) | Freezing apparatus | |
| EP1762794B1 (en) | Refrigerating device | |
| US11415345B2 (en) | Refrigeration apparatus | |
| JP3598809B2 (en) | Refrigeration cycle device | |
| JP6847299B2 (en) | Refrigeration cycle equipment | |
| JP5759017B2 (en) | Air conditioner | |
| US20160146521A1 (en) | Refrigeration cycle apparatus | |
| US20240085044A1 (en) | Air-conditioning apparatus | |
| WO2016181529A1 (en) | Refrigeration cycle device | |
| JP2004361036A (en) | Air conditioning system | |
| JP2001032772A (en) | Compressor, and freezing device | |
| WO2016121068A1 (en) | Refrigeration cycle device | |
| JP2000292037A (en) | Air conditioner | |
| JP6902390B2 (en) | Refrigeration cycle equipment | |
| JP3160130B2 (en) | Air conditioner | |
| JPH11159895A (en) | Air conditioner | |
| JPWO2019021464A1 (en) | Air conditioner | |
| JP4096862B2 (en) | Refrigeration unit and refrigerator | |
| JPH10325624A (en) | Refrigerating cycle device | |
| JP2001355928A (en) | Refrigerating device | |
| WO2017122264A1 (en) | Air conditioner | |
| JP6537629B2 (en) | Air conditioner | |
| JPH1068555A (en) | Circulating refrigerant composition detection method of refrigeration cycle and refrigerating apparatus using the detection method | |
| JP3601134B2 (en) | Refrigeration equipment | |
| JP2000018685A (en) | Multi-room type air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20040524 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20070116 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20070319 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20070417 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20070430 |
|
| R151 | Written notification of patent or utility model registration |
Ref document number: 3956589 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R151 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100518 Year of fee payment: 3 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110518 Year of fee payment: 4 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120518 Year of fee payment: 5 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130518 Year of fee payment: 6 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130518 Year of fee payment: 6 |
|
| EXPY | Cancellation because of completion of term |