JPH07120083A - Controller for refrigerating cycle - Google Patents
Controller for refrigerating cycleInfo
- Publication number
- JPH07120083A JPH07120083A JP5264669A JP26466993A JPH07120083A JP H07120083 A JPH07120083 A JP H07120083A JP 5264669 A JP5264669 A JP 5264669A JP 26466993 A JP26466993 A JP 26466993A JP H07120083 A JPH07120083 A JP H07120083A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- temperature
- amount
- compressor
- refrigeration cycle
- 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
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
Landscapes
- Air Conditioning Control Device (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、冷媒として沸点が異な
る２種類以上の冷媒を所定の比率で混合した非共沸混合
冷媒を用いた冷凍サイクルの制御装置に関するものであ
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration cycle control device using a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio.
【０００２】[0002]
【従来の技術】近年、地球環境保護の立場から、オゾン
層を破壊するフロンに対する規制が強化されてきてお
り、特に破壊力が大きなＣＦＣ（クロロフルオロカーボ
ン）については１９９５年末に全廃が決定しており、ま
た破壊力が比較的小さなＨＣＦＣ（ハイドロクロロフル
オロカーボン）についても１９９６年より総量規制が開
始され、将来的には全廃されることが決定している。し
たがって、冷媒としてフロンを用いた機器について、そ
の代替冷媒の開発が進められており、オゾン層を破壊し
ないＨＦＣ（ハイドロフルオロカーボン）が検討されて
いるが、冷凍機や空調機に用いられているＨＣＦＣの代
替冷媒として単独で用いることのできるものはＨＦＣの
中には見あたらず、したがって２種類以上のＨＦＣ系冷
媒を混合させた非共沸の混合冷媒が有望視されている。2. Description of the Related Art In recent years, from the standpoint of protecting the global environment, regulations on CFCs that destroy the ozone layer have been strengthened, and it has been decided to abolish CFC (chlorofluorocarbon), which has a particularly high destructive power, at the end of 1995. Also, regarding the FCFC (hydrochlorofluorocarbon), which has a relatively small destructive power, the total amount regulation was started in 1996, and it has been decided that it will be completely abolished in the future. Therefore, for devices that use CFCs as refrigerants, alternative refrigerants are being developed, and HFCs (hydrofluorocarbons) that do not destroy the ozone layer are being studied, but HCFCs used in refrigerators and air conditioners are being investigated. No substitute refrigerant that can be used alone in HFC is found, and therefore a non-azeotropic mixed refrigerant obtained by mixing two or more kinds of HFC refrigerants is considered promising.
【０００３】従来、ＣＦＣやＨＣＦＣ等の単一冷媒を用
いた冷凍機や空気調和機等の冷凍サイクルは、ＣＯＰ
（成績係数）を向上させ、圧縮機の信頼性を確保するた
めにスーパーヒート制御を行っていた。Conventionally, a refrigeration cycle such as a refrigerator or an air conditioner using a single refrigerant such as CFC or HCFC has a COP
Superheat control was performed to improve the (coefficient of performance) and ensure the reliability of the compressor.
【０００４】以下、図面を参照しながら従来の冷凍サイ
クルの制御について説明する。図１３は、従来の冷凍機
や空気調和機等の冷凍サイクル図である。同図におい
て、１は圧縮機、２は凝縮器、３はステッピングモータ
を用いて弁開度をパルス制御可能とした電動膨張弁、４
は蒸発器であり、これらは順に環状に連結されている。
また、５は凝縮器２と電動膨張弁３とを結ぶ管路に一端
を接続し、他端を蒸発器４と圧縮機１とを結ぶ管路に接
続したバイパス回路であり、このバイパス回路５には補
助絞り６が設けられている。さらに、バイパス回路５お
よび圧縮機１の吸入側の管路上にそれぞれ温度センサ
８、９が配設されており、この温度センサ８、９によっ
て検出された温度から弁開度演算回路１２にて電動膨張
弁３の弁開度を演算して弁開度信号を送出し、この弁開
度信号を受けて膨張弁駆動回路１３にて電動膨張弁３の
弁開度を制御する。Control of a conventional refrigeration cycle will be described below with reference to the drawings. FIG. 13 is a refrigeration cycle diagram of a conventional refrigerator, air conditioner, or the like. In the figure, 1 is a compressor, 2 is a condenser, 3 is an electric expansion valve whose valve opening can be pulse-controlled by using a stepping motor, 4
Are evaporators, which are in turn connected in a ring.
Reference numeral 5 denotes a bypass circuit having one end connected to a pipe line connecting the condenser 2 and the electric expansion valve 3 and the other end connected to a pipe line connecting the evaporator 4 and the compressor 1. Is provided with an auxiliary aperture 6. Further, temperature sensors 8 and 9 are provided on the bypass circuit 5 and the suction-side pipelines of the compressor 1, respectively, and the valve opening calculation circuit 12 electrically drives the temperature sensors 8 and 9 based on the temperatures detected by the temperature sensors 8 and 9. The valve opening degree of the expansion valve 3 is calculated, a valve opening degree signal is sent out, and the expansion valve drive circuit 13 receives the valve opening degree signal to control the valve opening degree of the electric expansion valve 3.
【０００５】図１４は、この冷凍サイクルをＰ−ｈ（モ
リエル）線図上にあらわしたもので、同図におけるＡ、
Ｂ、Ｃの記号のポイントは、図１３のＡ、Ｂ、Ｃの位置
の冷媒の状態を示す。同図から明らかなように、ポイン
トＣでは気液２相状態であるため、冷媒の温度はポイン
トＢの冷媒の飽和蒸気温度ＴＳである。したがって、温
度センサ８で検出した温度ＴＳと温度センサ９で検出し
た温度Ｔ２の差（Ｔ２−ＴＳ）が、圧縮機１に吸入され
る冷媒のスーパーヒート量△Ｔをあらわす。FIG. 14 shows this refrigeration cycle on the P-h (Moriel) diagram.
The points indicated by the symbols B and C indicate the states of the refrigerant at the positions A, B and C in FIG. As is clear from the figure, since the point C is in the gas-liquid two-phase state, the temperature of the refrigerant is the saturated vapor temperature TS of the refrigerant at the point B. Therefore, the difference (T2-TS) between the temperature TS detected by the temperature sensor 8 and the temperature T2 detected by the temperature sensor 9 represents the superheat amount ΔT of the refrigerant sucked into the compressor 1.
【０００６】次に、この冷凍サイクルの制御を説明す
る。図１５は、スーパーヒート量△Ｔと電動膨張弁３の
弁開度変更量との関係を示す図であり、温度センサ８と
９で検出した温度信号ＴＳ、Ｔ２より所定周期毎に弁開
度演算回路１２でスーパーヒート量△Ｔを算出し、図１
５に示す関係にしたがって（スーパーヒート量△Ｔが設
定値より大きい場合は弁開度を大きくし、設定値より小
さい場合は弁開度を小さくする）、電動膨張弁３の弁開
度信号を膨張弁駆動回路１３に送出し、膨張弁駆動回路
１３にて電動膨張弁３の弁開度を制御してスーパーヒー
ト量△Ｔを設定値に保つ。Next, the control of this refrigeration cycle will be described. FIG. 15 is a diagram showing the relationship between the superheat amount ΔT and the valve opening change amount of the electric expansion valve 3, in which the valve opening is determined at predetermined intervals based on the temperature signals TS and T2 detected by the temperature sensors 8 and 9. The calculation circuit 12 calculates the superheat amount ΔT, and FIG.
According to the relationship shown in 5 (when the superheat amount ΔT is larger than the set value, the valve opening is increased, and when the superheat amount ΔT is smaller than the set value, the valve opening is decreased). It is sent to the expansion valve drive circuit 13, and the expansion valve drive circuit 13 controls the valve opening of the electric expansion valve 3 to maintain the superheat amount ΔT at a set value.
【０００７】[0007]
【発明が解決しようとする課題】しかしながら、上記従
来の冷凍サイクルの制御装置には以下のような課題があ
った。However, the above conventional refrigeration cycle control device has the following problems.
【０００８】すなわち、圧縮機吸入冷媒が過熱蒸気の時
はスーパーヒート量△Ｔを算出することができるが、湿
り蒸気となった場合は吸入冷媒の乾き度が変化しても常
にスーパーヒート量△Ｔ＝０となってしまう。したがっ
て、吸入冷媒が過熱蒸気の場合は上記制御によりスーパ
ーヒート量△Ｔに応じた制御が可能であるが、湿り蒸気
となった場合は乾き度による制御は不可能であり、スー
パーヒート量の設定値が小さく飽和蒸気温度に近い場合
には制御性が悪く、また吸入冷媒の乾き度を所定値に保
つような制御は不可能であった。That is, the superheat amount ΔT can be calculated when the compressor suction refrigerant is superheated steam, but when it becomes wet steam, the superheat amount ΔT is always maintained even if the dryness of the suction refrigerant changes. T = 0. Therefore, when the intake refrigerant is superheated steam, the control according to the superheat amount ΔT can be performed by the above control, but when it becomes wet steam, the control by the dryness is not possible, and the superheat amount is set. When the value is small and close to the saturated vapor temperature, the controllability is poor, and it is impossible to control the dryness of the suction refrigerant to a predetermined value.
【０００９】また、図１６は、冷媒として非共沸混合冷
媒を用いた場合の冷凍サイクルをＰ−ｈ（モリエル）線
図上にあらわしたもので、同図におけるＡ、Ｂ、Ｃの記
号のポイントは、図１３のＡ、Ｂ、Ｃの位置の冷媒の状
態を示す。ここで、ポイントＢにおけるスーパーヒート
量は、ポイントＢの温度とその飽和蒸気温度（ポイント
Ｅ）との差で求めることができる。ここで、単一冷媒の
場合は図１４に示すようにポイントＣの温度は飽和蒸気
温度と同じであるが、非共沸混合冷媒の場合は図１６に
示すように、２相域での等温線は右下がりの線となって
いるため、ポイントＣの温度は飽和蒸気温度（ポイント
Ｅ）の温度よりも低い。したがって、温度センサ８と９
で検出した温度信号Ｔ１、Ｔ２から算出した△Ｔは真の
スーパーヒート量よりも大きな値となってしまい、この
状態で設定値に保つ制御を行うために冷媒は、実際のス
ーパーヒート量が設定値よりも低い状態か若しくは湿り
蒸気の状態で圧縮機に吸入される。FIG. 16 shows a refrigeration cycle in the case of using a non-azeotropic mixed refrigerant as a refrigerant on the Ph (Mollier) diagram, and the symbols A, B and C in FIG. Points indicate the states of the refrigerant at the positions A, B, and C in FIG. Here, the amount of superheat at the point B can be obtained by the difference between the temperature at the point B and the saturated steam temperature (point E). Here, in the case of a single refrigerant, the temperature at point C is the same as the saturated vapor temperature as shown in FIG. 14, but in the case of a non-azeotropic mixed refrigerant, as shown in FIG. Since the line is a line descending to the right, the temperature at point C is lower than the temperature at the saturated steam temperature (point E). Therefore, the temperature sensors 8 and 9
The ΔT calculated from the temperature signals T1 and T2 detected in step 3 becomes larger than the true superheat amount, and in order to perform control to keep the set value in this state, the actual superheat amount is set for the refrigerant. It is sucked into the compressor at a value lower than the value or in the state of wet steam.
【００１０】このため、液圧縮による圧縮機信頼性の低
下やＣＯＰの低下を招くおそれがあった。Therefore, there is a possibility that the compressor reliability and COP may be lowered due to the liquid compression.
【００１１】本発明の冷凍サイクルの制御装置は上記課
題に鑑み、非共沸混合冷媒を用いた冷凍サイクルにおい
て、冷凍サイクルの構成を複雑にすることなく圧縮機吸
入冷媒の冷媒状態を精度よく検出することを目的とし、
これにより最適な冷凍サイクル制御の実現を図るもので
ある。In view of the above problems, the refrigeration cycle control device of the present invention accurately detects the refrigerant state of the compressor suction refrigerant in a refrigeration cycle using a non-azeotropic mixed refrigerant without complicating the structure of the refrigeration cycle. For the purpose of
This is intended to realize the optimum refrigeration cycle control.
【００１２】また、本発明の他の冷凍サイクルの制御装
置は、非共沸混合冷媒を用いた冷凍サイクルにおいて、
圧縮機吸入冷媒スーパーヒート量若しくは乾き度を用い
て減圧量可変減圧器の制御を行うことを目的とし、これ
により最適な冷凍サイクル制御の実現を図るものであ
る。Another refrigeration cycle control device of the present invention is a refrigeration cycle using a non-azeotropic mixed refrigerant,
The purpose of this is to control the variable pressure reducing variable pressure reducer by using the superheat amount or dryness of the compressor suction refrigerant, and thereby realize the optimum refrigeration cycle control.
【００１３】[0013]
【課題を解決するための手段】上記課題を解決するため
に本発明の冷凍サイクルの制御装置は、冷媒として沸点
が異なる２種類以上の冷媒を所定の比率で混合した非共
沸混合冷媒を用い、圧縮機、凝縮器、減圧器、蒸発器を
順に配管にて環状に連結して冷媒回路を構成し、凝縮器
出口から減圧器出口に至る管路に一端を接続し、他端を
蒸発器出口から圧縮機入口に至る管路に接続したバイパ
ス回路を配設し、このバイパス回路に上流側から順に補
助減圧器、冷媒加熱手段、バイパス回路冷媒温度検出手
段を設け、冷媒加熱手段の加熱量を制御する加熱量制御
手段、バイパス回路冷媒温度検出手段により冷媒温度を
所定周期で検出してその変化量より飽和蒸気温度を判別
する判別手段を有し、蒸発器出口から圧縮機入口に至る
管路に圧縮機吸入冷媒温度検出手段を設け、この圧縮機
吸入冷媒温度検出手段とバイパス回路冷媒温度検出手段
で検出された温度を用いて圧縮機吸入冷媒が過熱蒸気の
時はスーパーヒート量を算出し、湿り蒸気の時は乾き度
を算出する冷媒状態算出手段を有し、この冷媒状態算出
手段により算出された冷媒状態を用いて冷凍サイクルの
制御を行う制御手段を有するものである。In order to solve the above problems, the refrigerating cycle control device of the present invention uses a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio as the refrigerant. , A compressor, a condenser, a decompressor, and an evaporator are sequentially connected in an annular shape by pipes to form a refrigerant circuit, one end of which is connected to a pipeline from the condenser outlet to the decompressor outlet, and the other end is an evaporator. A bypass circuit connected to the pipeline from the outlet to the compressor inlet is provided, and an auxiliary decompressor, refrigerant heating means, bypass circuit refrigerant temperature detection means are provided in this bypass circuit in order from the upstream side, and the heating amount of the refrigerant heating means is set. Control means for controlling the amount of heat, bypass circuit refrigerant temperature detecting means for detecting the refrigerant temperature in a predetermined cycle to determine the saturated vapor temperature from the amount of change, the pipe from the evaporator outlet to the compressor inlet Compressor suction into the road A medium temperature detection means is provided, and when the compressor suction refrigerant is superheated steam, the superheat amount is calculated using the temperature detected by the compressor suction refrigerant temperature detection means and the bypass circuit refrigerant temperature detection means, and At the time, it has a refrigerant state calculating means for calculating the dryness, and a control means for controlling the refrigeration cycle using the refrigerant state calculated by the refrigerant state calculating means.
【００１４】また、本発明の他の冷凍サイクルの制御装
置は、冷媒として沸点が異なる２種類以上の冷媒を所定
の比率で混合した非共沸混合冷媒を用い、圧縮機、凝縮
器、減圧器、蒸発器を順に配管にて環状に連結して冷媒
回路を構成し、凝縮器出口から減圧器出口に至る管路に
一端を接続し、他端を蒸発器出口から圧縮機入口に至る
管路に接続したバイパス回路を配設し、このバイパス回
路に上流側から順に減圧量可変の補助減圧器、バイパス
回路冷媒温度検出手段を設け、補助減圧器出口から冷媒
温度検出手段設置位置に至る管路の一部と前記圧縮機出
口から前記凝縮器入口に至る管路の一部とを熱交換的に
接続し、前記補助減圧器の減圧量を制御する減圧量制御
手段、バイパス回路冷媒温度検出手段により冷媒温度を
所定周期で検出してその変化量より飽和蒸気温度を判別
する判別手段を有し、蒸発器出口から圧縮機入口に至る
管路に圧縮機吸入冷媒温度検出手段を設け、この圧縮機
吸入冷媒温度検出手段とバイパス回路冷媒温度検出手段
で検出された温度を用いて圧縮機吸入冷媒が過熱蒸気の
時はスーパーヒート量を算出し、湿り蒸気の時は乾き度
を算出する冷媒状態算出手段を有し、この冷媒状態算出
手段により算出された冷媒状態を用いて冷凍サイクルの
制御を行う制御手段を有するものである。Further, another refrigeration cycle control device of the present invention uses a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio as a refrigerant, and uses a compressor, a condenser, and a pressure reducer. , The evaporator is sequentially connected by a pipe to form a refrigerant circuit, and one end is connected to the conduit from the condenser outlet to the pressure reducer outlet, and the other end is connected from the evaporator outlet to the compressor inlet. A bypass circuit connected to the bypass circuit, and an auxiliary decompressor with variable decompression amount and a bypass circuit refrigerant temperature detecting means are provided in this bypass circuit in order from the upstream side, and a pipe line from the auxiliary decompressor outlet to the refrigerant temperature detecting means installation position. And a part of the conduit from the compressor outlet to the condenser inlet in a heat exchange manner to control the pressure reduction amount of the auxiliary pressure reducer, a bypass circuit refrigerant temperature detecting means. The refrigerant temperature is detected by The saturated suction vapor temperature is determined from the amount of change, and the compressor suction refrigerant temperature detection means is provided in the pipeline from the evaporator outlet to the compressor inlet. Using the temperature detected by the temperature detection means, there is a refrigerant state calculation means for calculating the superheat amount when the compressor suction refrigerant is superheated steam and for calculating the dryness when it is wet steam, and this refrigerant state calculation It has a control means for controlling the refrigeration cycle using the refrigerant state calculated by the means.
【００１５】また、本発明の他の冷凍サイクルの制御装
置は、冷媒として沸点が異なる２種類以上の冷媒を所定
の比率で混合した非共沸混合冷媒を用い、圧縮機、凝縮
器、減圧器、蒸発器を順に配管にて環状に連結して冷媒
回路を構成し、凝縮器出口から減圧器出口に至る管路に
一端を接続し、他端を蒸発器出口から圧縮機入口に至る
管路に接続したバイパス回路を配設し、このバイパス回
路に上流側から順に減圧量可変の補助減圧器、バイパス
回路冷媒温度検出手段を設け、補助減圧器出口からバイ
パス回路冷媒温度検出手段設置位置に至る管路の一部を
前記蒸発器内に配設し、前記補助減圧器の減圧量を制御
する減圧量制御手段、バイパス回路冷媒温度検出手段に
より冷媒温度を所定周期で検出してその変化量より飽和
蒸気温度を判別する判別手段を有し、蒸発器出口から圧
縮機入口に至る管路に圧縮機吸入冷媒温度検出手段を設
け、この圧縮機吸入冷媒温度検出手段とバイパス回路冷
媒温度検出手段で検出された温度を用いて圧縮機吸入冷
媒が過熱蒸気の時はスーパーヒート量を算出し、湿り蒸
気の時は乾き度を算出する冷媒状態算出手段を有し、こ
の冷媒状態算出手段により算出された冷媒状態を用いて
冷凍サイクルの制御を行う制御手段を有するものであ
る。In another refrigeration cycle control device of the present invention, a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as a refrigerant, and a compressor, a condenser and a decompressor are used. , The evaporator is sequentially connected by a pipe to form a refrigerant circuit, and one end is connected to the conduit from the condenser outlet to the pressure reducer outlet, and the other end is connected from the evaporator outlet to the compressor inlet. A bypass circuit connected to the bypass circuit is provided, and an auxiliary decompressor with variable decompression amount and bypass circuit refrigerant temperature detecting means are provided in this bypass circuit in order from the upstream side, and the auxiliary circuit decompressor outlet reaches the bypass circuit refrigerant temperature detecting means installation position. A part of the pipeline is arranged in the evaporator, and the pressure reduction amount control means for controlling the pressure reduction amount of the auxiliary pressure reducer, the bypass circuit refrigerant temperature detection means detects the refrigerant temperature in a predetermined cycle, and the change amount Determine saturated steam temperature A compressor suction refrigerant temperature detecting means is provided in a pipeline from the evaporator outlet to the compressor inlet, and the temperature detected by the compressor suction refrigerant temperature detecting means and the bypass circuit refrigerant temperature detecting means is used. The compressor suction refrigerant has a refrigerant state calculation means for calculating the superheat amount when the refrigerant is superheated steam, and the dryness when it is wet steam, using the refrigerant state calculated by this refrigerant state calculation means. It has a control means for controlling the refrigeration cycle.
【００１６】また、本発明の他の冷凍サイクルの制御装
置は、冷媒として沸点が異なる２種類以上の冷媒を所定
の比率で混合した非共沸混合冷媒を用い、圧縮機、凝縮
器、減圧器、蒸発器を順に配管にて環状に連結して冷媒
回路を構成し、蒸発器出口から圧縮機入口に至る管路に
圧縮機吸入冷媒温度検出手段および圧縮機吸入冷媒圧力
検出手段を設け、この圧縮機吸入冷媒温度検出手段によ
り検出された温度と圧縮機吸入冷媒圧力検出手段により
検出された圧力を用いて圧縮機吸入冷媒が過熱蒸気の時
はスーパーヒート量を算出し、湿り蒸気の時は乾き度を
算出する冷媒状態算出手段を有し、この冷媒状態算出手
段により算出された冷媒状態を用いて冷凍サイクルの制
御を行う制御手段を有するものである。Further, another refrigeration cycle control device of the present invention uses a non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio as a refrigerant, and a compressor, a condenser and a pressure reducer are used. , The evaporator is sequentially connected in an annular shape by a pipe to form a refrigerant circuit, and a compressor suction refrigerant temperature detection means and a compressor suction refrigerant pressure detection means are provided in a pipeline extending from the evaporator outlet to the compressor inlet. When the compressor suction refrigerant is superheated steam, the superheat amount is calculated using the temperature detected by the compressor suction refrigerant temperature detection means and the pressure detected by the compressor suction refrigerant pressure detection means. It has a refrigerant state calculating means for calculating the dryness, and a control means for controlling the refrigeration cycle using the refrigerant state calculated by the refrigerant state calculating means.
【００１７】また、本発明の他の冷凍サイクルの制御装
置は、減圧器を減圧量可変減圧器とし、この減圧量可変
減圧器の減圧量を制御する主減圧量制御手段を設け、冷
媒状態算出手段により算出されたスーパーヒート量若し
くは乾き度を用いて主減圧量制御手段により減圧量可変
減圧器の減圧量を、スーパーヒート量若しくは乾き度が
所定値となるように制御するものである。Further, in another refrigeration cycle control device of the present invention, the pressure reducer is a variable pressure reducer, and main pressure reducing amount control means for controlling the pressure reducing amount of the variable pressure reducing variable pressure reducer is provided to calculate the refrigerant state. The amount of superheat or the degree of dryness calculated by the means is used to control the amount of depressurization of the variable pressure reduction amount decompressor by the main amount of decompression amount control means so that the amount of superheat or the degree of dryness becomes a predetermined value.
【００１８】[0018]
【作用】本発明は、上記手段により次のような作用を有
する。The present invention has the following actions due to the above means.
【００１９】すなわち、凝縮器出口から減圧器出口に至
る管路に一端を接続し、他端を蒸発器出口から圧縮機入
口に至る管路に接続したバイパス回路を配設し、このバ
イパス回路に上流側から順に補助減圧器、冷媒加熱手
段、バイパス回路冷媒温度検出手段を設け、冷媒加熱手
段の加熱量を制御する加熱量制御手段、バイパス回路冷
媒温度検出手段により冷媒温度を所定周期で検出してそ
の変化量より飽和蒸気温度を判別する判別手段を有し、
蒸発器出口から圧縮機入口に至る管路に圧縮機吸入冷媒
温度検出手段を設け、この圧縮機吸入冷媒温度検出手段
とバイパス回路冷媒温度検出手段で検出された温度を用
いて圧縮機吸入冷媒が過熱蒸気の時はスーパーヒート量
を算出し、湿り蒸気の時は乾き度を算出する冷媒状態算
出手段を有し、この冷媒状態算出手段により算出された
冷媒状態を用いて冷凍サイクルの制御を行う制御手段を
有することで、非共沸混合冷媒を用いた冷凍サイクルに
おいて、冷凍サイクルの構成を複雑にすることなく圧縮
機吸入冷媒の状態を精度よく検出することができ、これ
により最適な冷凍サイクル制御の実現を図ることができ
る。That is, a bypass circuit having one end connected to a conduit from the condenser outlet to the decompressor outlet and the other end connected to a conduit from the evaporator outlet to the compressor inlet is provided. Auxiliary decompressor, refrigerant heating means, bypass circuit refrigerant temperature detection means are provided in order from the upstream side, and a heating amount control means for controlling the heating amount of the refrigerant heating means and the bypass circuit refrigerant temperature detection means detect the refrigerant temperature in a predetermined cycle. Has a discriminating means for discriminating the saturated vapor temperature from the change amount,
A compressor suction refrigerant temperature detecting means is provided in a pipe line from the evaporator outlet to the compressor inlet, and the compressor suction refrigerant is detected by using the temperature detected by the compressor suction refrigerant temperature detecting means and the bypass circuit refrigerant temperature detecting means. It has a refrigerant state calculation means for calculating the superheat amount when it is superheated steam and a dryness when it is wet steam, and controls the refrigeration cycle using the refrigerant state calculated by this refrigerant state calculation means. By having a control means, in a refrigeration cycle using a non-azeotropic mixed refrigerant, it is possible to accurately detect the state of the compressor suction refrigerant without complicating the structure of the refrigeration cycle, and thus an optimal refrigeration cycle The control can be realized.
【００２０】また、凝縮器出口から減圧器出口に至る管
路に一端を接続し、他端を蒸発器出口から圧縮機入口に
至る管路に接続したバイパス回路を配設し、このバイパ
ス回路に上流側から順に減圧量可変の補助減圧器、バイ
パス回路冷媒温度検出手段を設け、補助減圧器出口から
冷媒温度検出手段設置位置に至る管路の一部と前記圧縮
機出口から前記凝縮器入口に至る管路の一部とを熱交換
的に接続し、前記補助減圧器の減圧量を制御する減圧量
制御手段、バイパス回路冷媒温度検出手段により冷媒温
度を所定周期で検出してその変化量より飽和蒸気温度を
判別する判別手段を有し、蒸発器出口から圧縮機入口に
至る管路に圧縮機吸入冷媒温度検出手段を設け、この圧
縮機吸入冷媒温度検出手段とバイパス回路冷媒温度検出
手段で検出された温度を用いて圧縮機吸入冷媒が過熱蒸
気の時はスーパーヒート量を算出し、湿り蒸気の時は乾
き度を算出する冷媒状態算出手段を有し、この冷媒状態
算出手段により算出された冷媒状態を用いて冷凍サイク
ルの制御を行う制御手段を有することで、冷凍サイクル
中の熱を利用することができるので新たに加熱手段を付
加することなく圧縮機吸入冷媒の状態を精度よく検出す
ることができ、これにより最適な冷凍サイクル制御の実
現を図ることができる。Further, a bypass circuit having one end connected to a conduit from the condenser outlet to the decompressor outlet and the other end connected to a conduit from the evaporator outlet to the compressor inlet is provided. Auxiliary decompressor with variable decompression amount from the upstream side, bypass circuit refrigerant temperature detection means are provided, and part of the pipeline from the auxiliary decompressor outlet to the refrigerant temperature detection means installation position and from the compressor outlet to the condenser inlet A pressure reduction amount control means for controlling a pressure reduction amount of the auxiliary pressure reducer by heat exchange connection with a part of the pipeline to reach, a refrigerant temperature is detected at a predetermined cycle by the bypass circuit refrigerant temperature detection means, and a change amount thereof is calculated. The compressor suction refrigerant temperature detection means is provided in the pipeline extending from the evaporator outlet to the compressor inlet, and the compressor suction refrigerant temperature detection means and the bypass circuit refrigerant temperature detection means are provided. was detected Has a refrigerant state calculation unit that calculates the superheat amount when the compressor intake refrigerant is superheated steam and calculates the dryness when it is wet steam, and the refrigerant state calculated by this refrigerant state calculation unit By having the control means for controlling the refrigeration cycle by using, it is possible to utilize the heat in the refrigeration cycle, so it is possible to accurately detect the state of the refrigerant sucked into the compressor without adding a new heating means. As a result, optimal refrigeration cycle control can be realized.
【００２１】また、凝縮器出口から減圧器出口に至る管
路に一端を接続し、他端を蒸発器出口から圧縮機入口に
至る管路に接続したバイパス回路を配設し、このバイパ
ス回路に上流側から順に減圧量可変の補助減圧器、バイ
パス回路冷媒温度検出手段を設け、補助減圧器出口から
冷媒温度検出手段設置位置に至る管路の一部を前記蒸発
器内に配設し、前記補助減圧器の減圧量を制御する減圧
量制御手段、バイパス回路冷媒温度検出手段により冷媒
温度を所定周期で検出してその変化量より飽和蒸気温度
を判別する判別手段を有し、蒸発器出口から圧縮機入口
に至る管路に圧縮機吸入冷媒温度検出手段を設け、この
圧縮機吸入冷媒温度検出手段とバイパス回路冷媒温度検
出手段で検出された温度を用いて圧縮機吸入冷媒が過熱
蒸気の時はスーパーヒート量を算出し、湿り蒸気の時は
乾き度を算出する冷媒状態算出手段を有し、この冷媒状
態算出手段により算出された冷媒状態を用いて冷凍サイ
クルの制御を行う制御手段を有することで、高温の加熱
源と熱交換せずにバイパス回路の冷媒を過熱蒸気にする
ことができるので、短時間で圧縮機吸入冷媒の状態を精
度よく検出することができ、これにより最適な冷凍サイ
クル制御の実現を図ることができる。Further, a bypass circuit having one end connected to a conduit from the condenser outlet to the decompressor outlet and the other end connected to a conduit from the evaporator outlet to the compressor inlet is provided. An auxiliary decompressor having a variable decompression amount from the upstream side, a bypass circuit refrigerant temperature detecting means are provided, and a part of the pipe line from the auxiliary decompressor outlet to the refrigerant temperature detecting means installation position is arranged in the evaporator, and A pressure reducing amount control means for controlling the pressure reducing amount of the auxiliary pressure reducer, a bypass circuit refrigerant temperature detecting means has a determining means for detecting the refrigerant temperature in a predetermined cycle and discriminating the saturated vapor temperature from the change amount thereof, from the evaporator outlet A compressor suction refrigerant temperature detecting means is provided in the pipeline leading to the compressor inlet, and the temperature detected by the compressor suction refrigerant temperature detecting means and the bypass circuit refrigerant temperature detecting means is used when the compressor suction refrigerant is superheated steam. Is super By having a refrigerant state calculating means for calculating the heat quantity and for calculating the dryness in the case of wet steam, and having a control means for controlling the refrigeration cycle using the refrigerant state calculated by the refrigerant state calculating means. Since the refrigerant in the bypass circuit can be turned into superheated steam without exchanging heat with a high-temperature heat source, the state of the refrigerant sucked into the compressor can be accurately detected in a short time, which enables optimum refrigeration cycle control. Can be realized.
【００２２】また、蒸発器出口から圧縮機入口に至る管
路に圧縮機吸入冷媒温度検出手段および圧縮機吸入冷媒
圧力検出手段を設け、この圧縮機吸入冷媒温度検出手段
により検出された温度と圧縮機吸入冷媒圧力検出手段に
より検出された圧力を用いて圧縮機吸入冷媒が過熱蒸気
の時はスーパーヒート量を算出し、湿り蒸気の時は乾き
度を算出する冷媒状態算出手段を有し、この冷媒状態算
出手段により算出された冷媒状態を用いて冷凍サイクル
の制御を行う制御手段を有することで、バイパス回路を
設けずに圧縮機吸入冷媒の状態を精度よく検出すること
ができ、これにより最適な冷凍サイクル制御の実現を図
ることができる。Further, a compressor suction refrigerant temperature detecting means and a compressor suction refrigerant pressure detecting means are provided in a pipe line from the evaporator outlet to the compressor inlet, and the temperature and the compression detected by the compressor suction refrigerant temperature detecting means. The compressor suction refrigerant using the pressure detected by the machine suction refrigerant pressure detection means calculates the superheat amount when the compressor suction refrigerant is superheated steam, and has a refrigerant state calculation means for calculating the dryness when it is wet steam. By having a control unit that controls the refrigeration cycle using the refrigerant state calculated by the refrigerant state calculation unit, the state of the compressor suction refrigerant can be accurately detected without providing a bypass circuit, which makes it optimal. It is possible to realize various refrigeration cycle control.
【００２３】また、減圧器を検圧量可変減圧器とし、こ
の減圧量可変減圧器の減圧量を制御する主減圧量制御手
段を設け、冷媒状態算出手段により算出されたスーパー
ヒート量若しくは乾き度を用いて主減圧量制御手段によ
り減圧量可変減圧器の減圧量を、スーパーヒート量若し
くは乾き度が所定値となるように制御することで、最適
な冷凍サイクル制御の実現を図ることができる。Further, the pressure reducer is a variable pressure detection variable pressure reducer, and main pressure reduction amount control means for controlling the pressure reduction amount of the pressure reduction variable pressure reduction device is provided, and the superheat amount or dryness calculated by the refrigerant state calculation means is provided. By controlling the pressure reduction amount of the variable pressure reduction variable pressure reducer by the main pressure reduction amount control means so that the superheat amount or the dryness becomes a predetermined value, it is possible to realize optimum refrigeration cycle control.
【００２４】[0024]
【実施例】以下、本発明の実施例について、図面を参考
に説明する。なお、従来の技術の項で説明したものと同
一の機能を有するものには同一の番号を付して詳細な説
明は省略する。Embodiments of the present invention will be described below with reference to the drawings. It should be noted that components having the same functions as those described in the section of the related art are designated by the same reference numerals and detailed description thereof will be omitted.
【００２５】図１は、本発明の第１の実施例における冷
凍サイクル図である。同図において、１は圧縮機、２は
凝縮器、３は電動膨張弁、４は蒸発器であり、これらは
順に環状に連結されており、冷媒として非共沸混合冷媒
を用いている。また、５は凝縮器２と電動膨張弁３とを
結ぶ管路に一端を接続し、他端を蒸発器４と圧縮機１と
を結ぶ管路に接続したバイパス回路であり、このバイパ
ス回路５には補助絞り６が設けられている。また、補助
絞り６の下流側には冷媒を加熱する加熱ヒータ７が取り
付けられている。さらに、バイパス回路５および圧縮機
１の吸入側の管路上にそれぞれ温度センサ８、９が配設
されている。１０は、加熱ヒータのオン、オフを制御す
る加熱ヒータ制御回路であり、１１は加熱ヒータ制御回
路１０へ制御信号を送出し、温度センサ８で検出した温
度Ｔ１より飽和蒸気温度ＴＳを算出する飽和蒸気温度算
出回路である。飽和蒸気温度算出回路１１で算出された
ＴＳと温度センサ９によって検出された温度Ｔ２とを弁
開度演算回路１２に送出し、ここでＴ２≧ＴＳならばス
ーパーヒート量を算出し、Ｔ２＜ＴＳならば湿り蒸気で
あると判断してその乾き度を算出し、算出したスーパー
ヒート量若しくは乾き度より電動膨張弁３の開度を演算
して弁開度信号を送出し、この弁開度信号を受けて膨張
弁駆動回路１３にて電動膨張弁３の弁開度を制御する。FIG. 1 is a refrigeration cycle diagram in the first embodiment of the present invention. In the figure, 1 is a compressor, 2 is a condenser, 3 is an electric expansion valve, and 4 is an evaporator, which are sequentially connected in an annular shape and use a non-azeotropic mixed refrigerant as a refrigerant. Reference numeral 5 denotes a bypass circuit having one end connected to a pipe line connecting the condenser 2 and the electric expansion valve 3 and the other end connected to a pipe line connecting the evaporator 4 and the compressor 1. Is provided with an auxiliary aperture 6. A heater 7 for heating the refrigerant is attached downstream of the auxiliary throttle 6. Further, temperature sensors 8 and 9 are arranged on the bypass side of the bypass circuit 5 and on the suction side of the compressor 1, respectively. Reference numeral 10 is a heating heater control circuit for controlling on / off of the heating heater, and 11 is a saturation signal which sends a control signal to the heating heater control circuit 10 to calculate a saturated vapor temperature TS from a temperature T1 detected by the temperature sensor 8. It is a steam temperature calculation circuit. The TS calculated by the saturated steam temperature calculation circuit 11 and the temperature T2 detected by the temperature sensor 9 are sent to the valve opening calculation circuit 12, where if T2 ≧ TS, the superheat amount is calculated, and T2 <TS If so, the degree of dryness is calculated by determining that it is wet steam, the opening degree of the electric expansion valve 3 is calculated from the calculated superheat amount or the dryness degree, and a valve opening degree signal is sent out. In response to this, the expansion valve drive circuit 13 controls the valve opening degree of the electric expansion valve 3.
【００２６】次に、この飽和蒸気温度算出回路１１での
飽和蒸気温度算出の方法について説明する。図２は、こ
の冷凍サイクルをＰ−ｈ（モリエル）線図上にあらわし
たもので、同図におけるＡ、Ｂの記号のポイントは、図
１のＡ、Ｂの位置の冷媒の状態を示す。ここで、加熱ヒ
ータ７がオフの場合、温度センサ８近傍の冷媒は図２の
ポイントＣの状態である。加熱ヒータ７をオンにする
と、冷媒は加熱されて冷媒の状態は矢印ａの方向に移動
し、ポイントＤの状態となる。ここで再び加熱ヒータ７
をオフにすると冷媒の状態は矢印ｂの方向に移動し、再
びポイントＣの状態となる。この時、図２に示す等温線
より明らかなように、加熱域を移動する時は温度低下の
速度が大きく、２相域に入ると温度低下の速度が急に緩
やかになる。図３は、温度センサ８で検出した冷媒温度
Ｔ１の時間変化を示す。同図のＴＣ、ＴＤは、図２の
Ｃ、Ｄのポイントの状態の冷媒温度である。同図から明
らかなように、加熱ヒータ７がオフになると冷媒温度は
急激に低下するが、２相域に入ると温度低下が急に緩や
かになる。この傾きが変化する時刻ｔｓａの温度が飽和
蒸気温度ＴＳである。したがって、加熱ヒータ７がオフ
になってから所定周期毎に温度センサ８で冷媒温度Ｔ１
を検出し、前回検出した冷媒温度Ｔ１との差の絶対値が
所定値以下になった時の温度を飽和蒸気温度とすること
で検出可能である。Next, a method of calculating the saturated steam temperature in the saturated steam temperature calculating circuit 11 will be described. FIG. 2 shows this refrigeration cycle on the P-h (Mollier) diagram, and the points indicated by the symbols A and B in the figure show the state of the refrigerant at the positions A and B in FIG. Here, when the heater 7 is off, the refrigerant in the vicinity of the temperature sensor 8 is in the state of point C in FIG. When the heater 7 is turned on, the refrigerant is heated and the state of the refrigerant moves in the direction of the arrow a to the state of point D. Here again the heater 7
When is turned off, the state of the refrigerant moves in the direction of arrow b and returns to the state of point C. At this time, as is clear from the isotherm shown in FIG. 2, the rate of temperature decrease is large when moving in the heating zone, and the rate of temperature decrease suddenly decreases when entering the two-phase zone. FIG. 3 shows a time change of the refrigerant temperature T1 detected by the temperature sensor 8. TC and TD in the figure are refrigerant temperatures at the points C and D in FIG. As is clear from the figure, when the heater 7 is turned off, the refrigerant temperature sharply drops, but when it enters the two-phase region, the temperature drop suddenly becomes gentle. The temperature at time tsa at which this slope changes is the saturated steam temperature TS. Therefore, after the heater 7 is turned off, the refrigerant temperature T1 is measured by the temperature sensor 8 every predetermined period.
Is detected, and the temperature at the time when the absolute value of the difference from the previously detected refrigerant temperature T1 becomes equal to or lower than a predetermined value is set as the saturated steam temperature, thereby enabling detection.
【００２７】また、飽和蒸気温度がわかると公知の冷媒
物性推算方法よりその時の冷媒圧力を算出することが可
能である。そして、図２より明らかなように、非共沸混
合冷媒の場合は、２相域では同一圧力でも乾き度によっ
てその温度が異なる。すなわち、２相域では圧力と温度
がわかれば、乾き度を算出することができる。したがっ
て、圧縮機吸入冷媒が湿り蒸気の場合、その乾き度をｘ
とするとｘは、飽和蒸気温度ＴＳと圧縮機吸入冷媒温度
Ｔ２の関数ｘ＝ｆ（ＴＳ，Ｔ２）であらわすことがで
き、あらかじめ、関数を作成しておけば、乾き度を算出
することが可能である。Further, if the saturated vapor temperature is known, the refrigerant pressure at that time can be calculated by a known refrigerant physical property estimation method. As is clear from FIG. 2, in the case of the non-azeotropic mixed refrigerant, the temperature varies in the two-phase region even with the same pressure depending on the dryness. That is, in the two-phase region, if the pressure and temperature are known, the dryness can be calculated. Therefore, when the compressor suction refrigerant is wet vapor, its dryness is x
Then, x can be expressed by a function x = f (TS, T2) of the saturated vapor temperature TS and the compressor suction refrigerant temperature T2, and the dryness can be calculated by creating the function in advance. Is.
【００２８】次に、この冷凍サイクルの制御装置におけ
る具体的な制御について説明する。図４および図５は、
この冷凍サイクルの制御装置の具体的な制御のフロー図
であり、図４は飽和蒸気温度算出回路１１での制御のフ
ローを、また図５は弁開度演算回路１２での制御のフロ
ーをそれぞれ示す。また、図６は、スーパーヒート量△
Ｔ、乾き度ｘと電動膨張弁３の弁開度変更量との関係図
を示す。まず、弁開度演算回路１２より所定周期毎にＴ
Ｓ送出の要求を受けると、加熱ヒータ７をオンとする。
そして、温度センサ８で検出した温度Ｔ１が図２に示す
ＴＤまで上昇すると、加熱ヒータ７をオフとして所定周
期ｔ１毎にＴ１を検出し、直前に検出した温度Ｔｍとの
差（変化量）の絶対値｜Ｔ１−Ｔｍ｜が所定値Ｋより小
さくなると、この時の冷媒温度Ｔ１が飽和蒸気温度ＴＳ
であると判断してＴＳ＝Ｔ１とし、ＴＳの温度信号を弁
開度演算回路１２に送出する。弁開度演算回路１２で
は、まず温度センサ９で検出した圧縮機吸入冷媒の温度
Ｔ２と飽和蒸気温度ＴＳを比較し、Ｔ２≧ＴＳならば過
熱蒸気であると判断してスーパーヒート量△Ｔを算出
し、Ｔ２＜ＴＳならば湿り蒸気であると判断してその乾
き度を算出し、算出したスーパーヒート量若しくは乾き
度より図６に示す関係にしたがって電動膨張弁３の開度
を演算して膨張弁駆動回路１３に弁開度信号を送出し、
この弁開度信号を受けて膨張弁駆動回路１３にて電動膨
張弁３の弁開度を制御する。Next, the specific control in this refrigeration cycle control device will be described. 4 and 5 show
[Fig. 4] Fig. 4 is a specific control flow chart of the control device of the refrigeration cycle, Fig. 4 shows a control flow in the saturated vapor temperature calculation circuit 11, and Fig. 5 shows a control flow in the valve opening calculation circuit 12. Show. In addition, FIG. 6 shows the amount of superheat Δ
5 shows a relationship diagram between T and dryness x and a valve opening change amount of the electric expansion valve 3. First, the valve opening calculation circuit 12 outputs T at predetermined intervals.
When the request for S delivery is received, the heater 7 is turned on.
Then, when the temperature T1 detected by the temperature sensor 8 rises to TD shown in FIG. 2, the heater 7 is turned off to detect T1 at every predetermined cycle t1, and the difference (change amount) from the temperature Tm detected immediately before is detected. When the absolute value | T1-Tm | becomes smaller than the predetermined value K, the refrigerant temperature T1 at this time is the saturated vapor temperature TS.
When TS = T1, the temperature signal of TS is sent to the valve opening calculation circuit 12. In the valve opening calculation circuit 12, first, the temperature T2 of the compressor suction refrigerant detected by the temperature sensor 9 is compared with the saturated steam temperature TS, and if T2 ≧ TS, it is judged that the steam is superheated and the superheat amount ΔT is calculated. If T2 <TS, it is determined that the steam is wet and the degree of dryness thereof is calculated, and the opening degree of the electric expansion valve 3 is calculated from the calculated superheat amount or the degree of dryness according to the relationship shown in FIG. Sending a valve opening signal to the expansion valve drive circuit 13,
In response to this valve opening signal, the expansion valve drive circuit 13 controls the valve opening of the electric expansion valve 3.
【００２９】このように、冷媒として非共沸混合冷媒を
用いた場合でも、冷凍サイクルの構成を複雑にすること
なく圧縮機吸入冷媒の飽和蒸気温度を精度よく検出する
ことができ、これにより最適な冷凍サイクル制御の実現
を図ることができる。さらに、圧縮機吸入冷媒が湿り蒸
気の場合には乾き度を求めることができるため、スーパ
ーヒート量の設定値が小さく飽和蒸気温度に近い場合で
も安定した制御を行うことができ、また吸入冷媒の乾き
度を所定値に保つような制御も可能である。As described above, even when the non-azeotropic mixed refrigerant is used as the refrigerant, the saturated vapor temperature of the refrigerant sucked into the compressor can be accurately detected without complicating the structure of the refrigeration cycle. It is possible to realize various refrigeration cycle control. Furthermore, since the dryness can be obtained when the compressor suction refrigerant is wet steam, stable control can be performed even when the set value of the superheat amount is small and close to the saturated steam temperature, and the suction refrigerant It is also possible to control the dryness to a predetermined value.
【００３０】次に、本発明の第２の実施例について、図
面を参照しながら説明する。図７は、本発明の第２の実
施例における冷凍サイクル図である。第１の実施例と異
なる点は、バイパス回路５上の補助絞り６、加熱ヒータ
７および加熱ヒータ制御回路１０をなくし、バイパス回
路５上に膨張弁駆動回路１３によって弁開度を制御可能
な電動膨張弁１４を設け、その下流側の管路の一部を圧
縮機１と凝縮器２とを結ぶ管路と熱交換可能な熱交換部
１５を設けたものである。Next, a second embodiment of the present invention will be described with reference to the drawings. FIG. 7 is a refrigeration cycle diagram in the second embodiment of the present invention. The difference from the first embodiment is that the auxiliary throttle 6, the heater 7 and the heater control circuit 10 on the bypass circuit 5 are eliminated, and the valve opening degree can be controlled on the bypass circuit 5 by the expansion valve drive circuit 13. The expansion valve 14 is provided, and a heat exchange section 15 capable of exchanging heat with a pipeline connecting the compressor 1 and the condenser 2 is provided in a part of the pipeline on the downstream side.
【００３１】この冷凍サイクルの制御装置における飽和
蒸気温度算出の方法について説明する。本実施例では、
圧縮機１から吐出された高温の冷媒ガスによりバイパス
回路５の冷媒を加熱するため、加熱量の制御はできな
い。したがって、電動膨張弁１４の弁開度を制御してバ
イパス回路５を流れる冷媒の循環量を制御して第１の実
施例と同様に飽和蒸気温度を算出する。すなわち、最初
に電動膨張弁１４の弁開度を小さくして、冷媒温度Ｔ１
を図３におけるＴＤまで上昇させる。Ｔ１がＴＤまで上
昇したら、次に所定周期毎に電動膨張弁１４の弁開度を
所定量ずつ大きくし、冷媒温度Ｔ１を検出する。そうす
ると、第１の実施例と同様に冷媒温度は急激に低下する
が、２相域に入ると温度低下が急に緩やかになる。この
傾きが変化する時刻ｔｓａの温度が飽和蒸気温度ＴＳで
ある。したがって、冷媒温度Ｔ１がＴＤまで到達した
後、所定周期毎に温度センサ８で冷媒温度Ｔ１を検出
し、前回検出した冷媒温度Ｔ１との差の絶対値が所定値
以下になった時の温度を飽和蒸気温度とすることで検出
可能である。A method of calculating the saturated steam temperature in the refrigeration cycle control device will be described. In this embodiment,
Since the refrigerant in the bypass circuit 5 is heated by the high temperature refrigerant gas discharged from the compressor 1, the amount of heating cannot be controlled. Therefore, the saturated steam temperature is calculated in the same manner as in the first embodiment by controlling the valve opening degree of the electric expansion valve 14 to control the circulation amount of the refrigerant flowing through the bypass circuit 5. That is, first, the valve opening degree of the electric expansion valve 14 is reduced to reduce the refrigerant temperature T1.
To TD in FIG. When T1 rises to TD, the valve opening degree of the electric expansion valve 14 is then increased by a predetermined amount every predetermined period, and the refrigerant temperature T1 is detected. Then, as in the first embodiment, the temperature of the refrigerant sharply drops, but when it enters the two-phase region, the temperature drop suddenly becomes gentle. The temperature at time tsa at which this slope changes is the saturated steam temperature TS. Therefore, after the coolant temperature T1 reaches TD, the coolant temperature T1 is detected by the temperature sensor 8 in every predetermined cycle, and the temperature at the time when the absolute value of the difference from the coolant temperature T1 detected last time becomes the predetermined value or less is determined. It can be detected by setting the saturated vapor temperature.
【００３２】次に、この冷凍サイクルの制御装置におけ
る具体的な制御について説明する。図８は、飽和蒸気温
度算出回路１１での制御のフロー図である。まず、弁開
度演算回路１２より所定周期毎にＴＳ送出の要求を受け
ると、温度センサ８で検出した温度Ｔ１が図２に示すＴ
Ｄに上昇するまで所定周期ｔ２毎に膨張弁駆動回路１３
に信号を発して電動膨張弁１４の弁開度をＫ２パルスず
つ絞っていく。そして、冷媒温度Ｔ１が図２に示すＴＤ
まで上昇すると、所定周期ｔ３毎に膨張弁駆動回路１３
に信号を発して電動膨張弁１４の弁開度を大きくしてい
くと共にＴ１を検出し、直前に検出した温度Ｔｍとの差
（変化量）の絶対値｜Ｔ１−Ｔｍ｜が所定値Ｋより小さ
くなると、この時の冷媒温度Ｔ１が飽和蒸気温度ＴＳで
あると判断してＴＳ＝Ｔ１とし、ＴＳの温度信号を弁開
度演算回路１２に送出する。弁開度演算回路１２では、
図５に示す第１の実施例の場合と同様にして電動膨張弁
３の開度を演算し、膨張弁駆動回路１３に弁開度信号を
送出し、この弁開度信号を受けて膨張弁駆動回路１３に
て電動膨張弁３の弁開度を制御する。Next, a specific control in this refrigeration cycle control device will be described. FIG. 8 is a flow chart of control in the saturated steam temperature calculation circuit 11. First, when a request for TS transmission is received from the valve opening calculation circuit 12 at predetermined intervals, the temperature T1 detected by the temperature sensor 8 is T shown in FIG.
Expansion valve drive circuit 13 at a predetermined cycle t2 until it rises to D.
To the electric expansion valve 14 to reduce the valve opening degree of the electric expansion valve 14 by K2 pulses. The refrigerant temperature T1 is TD shown in FIG.
Rises up to, the expansion valve drive circuit 13
A signal is sent to the electric expansion valve 14 to increase the valve opening degree and T1 is detected, and the absolute value | T1-Tm | of the difference (change amount) from the temperature Tm detected immediately before is greater than the predetermined value K. When it becomes smaller, it is judged that the refrigerant temperature T1 at this time is the saturated vapor temperature TS, TS = T1 is set, and the temperature signal of TS is sent to the valve opening calculation circuit 12. In the valve opening calculation circuit 12,
Similar to the case of the first embodiment shown in FIG. 5, the opening of the electric expansion valve 3 is calculated, a valve opening signal is sent to the expansion valve drive circuit 13, and the expansion valve receives the valve opening signal. The drive circuit 13 controls the valve opening degree of the electric expansion valve 3.
【００３３】このように、冷媒として非共沸混合冷媒を
用いた場合でも、冷凍サイクル中の熱を利用することが
できるので新たに加熱手段を付加することなく圧縮機吸
入冷媒の飽和蒸気温度を精度よく検出することができ、
これにより最適な冷凍サイクル制御の実現を図ることが
できる。さらに、圧縮機吸入冷媒が湿り蒸気の場合には
乾き度を求めることができるため、スーパーヒート量の
設定値が小さく飽和蒸気温度に近い場合でも安定した制
御を行うことができ、また吸入冷媒の乾き度を所定値に
保つような制御も可能である。As described above, even when the non-azeotropic mixed refrigerant is used as the refrigerant, the heat in the refrigeration cycle can be utilized, so that the saturated vapor temperature of the refrigerant sucked into the compressor can be increased without adding any additional heating means. Can be detected accurately,
This makes it possible to realize optimum refrigeration cycle control. Furthermore, since the dryness can be obtained when the compressor suction refrigerant is wet steam, stable control can be performed even when the set value of the superheat amount is small and close to the saturated steam temperature, and the suction refrigerant It is also possible to control the dryness to a predetermined value.
【００３４】次に、本発明の第３の実施例について、図
面を参照しながら説明する。図９は、本発明の第３の実
施例における冷凍サイクル図である。第２の実施例と異
なる点は、バイパス回路５上の電動膨張弁１４の下流側
の管路の一部を蒸発器４内を通過させて冷媒を蒸発させ
る補助蒸発器１６を設けたことである。Next, a third embodiment of the present invention will be described with reference to the drawings. FIG. 9 is a refrigeration cycle diagram in the third embodiment of the present invention. The difference from the second embodiment is that an auxiliary evaporator 16 is provided to evaporate the refrigerant by passing a part of the pipeline on the downstream side of the electric expansion valve 14 on the bypass circuit 5 through the evaporator 4. is there.
【００３５】この冷凍サイクルの制御装置における飽和
蒸気温度算出の方法について説明すると、まず最初に電
動膨張弁１４の弁開度を小さくして、冷媒温度Ｔ１を図
３におけるＴＤまで上昇させる。Ｔ１がＴＤまで上昇し
たら、次に所定周期毎に電動膨張弁１４の弁開度を所定
量ずつ大きくし、冷媒温度Ｔ１を検出し、以下第２の実
施例と同様にして飽和蒸気温度ＴＳを求め、ＴＳの温度
信号を弁開度演算回路１２に送出する。なお、具体的な
制御については図８に示す第２の実施例の制御のフロー
図と同じであるため説明は省略する。また、弁開度演算
回路１２では、図５に示す第１の実施例の場合と同様に
して電動膨張弁３の開度を演算し、膨張弁駆動回路１３
に弁開度信号を送出し、この弁開度信号を受けて膨張弁
駆動回路１３にて電動膨張弁３の弁開度を制御する。Explaining the method for calculating the saturated vapor temperature in the control device of the refrigeration cycle, first, the valve opening degree of the electric expansion valve 14 is reduced to raise the refrigerant temperature T1 to TD in FIG. When T1 rises to TD, the valve opening degree of the electric expansion valve 14 is increased by a predetermined amount every predetermined period, the refrigerant temperature T1 is detected, and the saturated vapor temperature TS is determined in the same manner as in the second embodiment. Then, the temperature signal of TS is sent to the valve opening calculation circuit 12. The specific control is the same as the control flow chart of the second embodiment shown in FIG. The valve opening calculation circuit 12 calculates the opening of the electric expansion valve 3 in the same manner as in the first embodiment shown in FIG.
A valve opening signal is sent to the valve, and the expansion valve drive circuit 13 receives the valve opening signal to control the valve opening of the electric expansion valve 3.
【００３６】第２の実施例においては、バイパス回路５
の冷媒は圧縮機１から吐出された高温の冷媒ガスにより
加熱されるため、図３に示すＴＤはかなり高温となるの
に対し、本実施例では冷媒を蒸発させるため、過熱域に
入っても雰囲気温度以上にはならず、したがって比較的
低温で安定する。そのため、冷媒温度がＴＤからＴＳに
到達するまでの時間が短く、短時間で飽和蒸気温度ＴＳ
を求めることができる。In the second embodiment, the bypass circuit 5
3 is heated by the high-temperature refrigerant gas discharged from the compressor 1, the TD shown in FIG. 3 is considerably high in temperature. It does not exceed the ambient temperature and is therefore stable at relatively low temperatures. Therefore, it takes a short time for the refrigerant temperature to reach TD from TS, and the saturated vapor temperature TS
Can be asked.
【００３７】このように、冷媒として非共沸混合冷媒を
用いた場合でも、冷凍サイクル中の熱を利用することが
できるので新たに加熱手段を付加することなく圧縮機吸
入冷媒の飽和蒸気温度を精度よく、しかも短時間で検出
することができ、これにより最適な冷凍サイクル制御の
実現を図ることができる。As described above, even when the non-azeotropic mixed refrigerant is used as the refrigerant, the heat in the refrigeration cycle can be utilized, so that the saturated vapor temperature of the compressor suction refrigerant can be changed without adding a new heating means. It is possible to detect with high accuracy and in a short time, and thus it is possible to realize optimum refrigeration cycle control.
【００３８】さらに、圧縮機吸入冷媒が湿り蒸気の場合
には乾き度を求めることができるため、スーパーヒート
量の設定値が小さく飽和蒸気温度に近い場合でも安定し
た制御を行うことができ、また吸入冷媒の乾き度を所定
値に保つような制御も可能である。Furthermore, since the dryness can be obtained when the compressor suction refrigerant is wet vapor, stable control can be performed even when the set value of the superheat amount is small and close to the saturated vapor temperature. It is also possible to control so that the dryness of the suctioned refrigerant is maintained at a predetermined value.
【００３９】次に、本発明の第４の実施例について、図
面を参照しながら説明する。図１０は、本発明の第４の
実施例における冷凍サイクル図である。第３の実施例と
異なる点はバイパス回路５およびバイパス回路５上の電
動膨張弁１４、補助蒸発器１６、温度センサ８をなく
し、圧縮機１の吸入側冷媒の圧力を検出する圧力センサ
１７を新たに設けたことである。Next, a fourth embodiment of the present invention will be described with reference to the drawings. FIG. 10 is a refrigeration cycle diagram in the fourth embodiment of the present invention. The difference from the third embodiment is that the bypass circuit 5, the electric expansion valve 14 on the bypass circuit 5, the auxiliary evaporator 16 and the temperature sensor 8 are eliminated, and the pressure sensor 17 for detecting the pressure of the refrigerant on the suction side of the compressor 1 is omitted. It is newly established.
【００４０】この冷凍サイクルの制御装置における飽和
蒸気温度算出の方法について、図１１を用いて説明す
る。図１１は、本実施例における制御のフロー図であ
る。まず、弁開度演算回路１２より所定周期毎にＴＳ送
出の要求を受けると、圧力センサ１７で、圧縮機吸入冷
媒の圧力ＰＳを検出する。冷媒圧力がわかると公知の冷
媒物性推算方法よりその時の飽和蒸気温度を算出するこ
とが可能である。したがってあらかじめ関数を作成して
おき、圧縮機吸入冷媒の圧力ＰＳより飽和蒸気温度ＴＳ
を算出し、ＴＳの温度信号を弁開度演算回路１２に送出
する。弁開度演算回路１２では、図５に示す第１の実施
例の場合と同様にして電動膨張弁３の開度を演算し、膨
張弁駆動回路１３に弁開度信号を送出し、この弁開度信
号を受けて膨張弁駆動回路１３にて電動膨張弁３の弁開
度を制御する。本実施例においては、圧力センサ１７を
配設することで、バイパス回路５をなくすことができる
ため、簡単な構成で圧縮機吸入冷媒の飽和蒸気温度を精
度よく、しかも短時間で算出することができ、これによ
り最適な冷凍サイクル制御の実現を図ることができる。A method for calculating the saturated vapor temperature in the refrigeration cycle control device will be described with reference to FIG. FIG. 11 is a flow chart of control in this embodiment. First, when the request for TS transmission is received from the valve opening calculation circuit 12 every predetermined period, the pressure sensor 17 detects the pressure PS of the refrigerant sucked into the compressor. When the refrigerant pressure is known, the saturated vapor temperature at that time can be calculated by a known refrigerant physical property estimation method. Therefore, a function is created in advance, and the saturated vapor temperature TS is calculated from the pressure PS of the compressor suction refrigerant.
Is calculated, and the temperature signal of TS is sent to the valve opening calculation circuit 12. The valve opening calculation circuit 12 calculates the opening of the electric expansion valve 3 in the same manner as in the first embodiment shown in FIG. 5, and sends a valve opening signal to the expansion valve drive circuit 13, Upon receiving the opening signal, the expansion valve drive circuit 13 controls the valve opening of the electric expansion valve 3. In this embodiment, since the bypass circuit 5 can be eliminated by disposing the pressure sensor 17, the saturated vapor temperature of the compressor suction refrigerant can be calculated accurately and in a short time with a simple configuration. As a result, optimal refrigeration cycle control can be realized.
【００４１】さらに、圧縮機吸入冷媒が湿り蒸気の場合
には乾き度を求めることができるため、スーパーヒート
量の設定値が小さく飽和蒸気温度に近い場合でも安定し
た制御を行うことができ、また吸入冷媒の乾き度を所定
値に保つような制御も可能である。Furthermore, since the dryness can be obtained when the compressor suction refrigerant is wet steam, stable control can be performed even when the set value of the superheat amount is small and close to the saturated steam temperature. It is also possible to control so that the dryness of the suctioned refrigerant is maintained at a predetermined value.
【００４２】なお、上記第１〜第４の実施例において、
ヒートポンプサイクルの場合は、四方弁を切り換えて蒸
発器と凝縮器が入れ替わっても、バイパス回路の一端を
常に凝縮器出口から減圧器出口に至る管路に接続するよ
うにしておけば、本発明の冷凍サイクルの制御装置を構
成することが可能である。例えば、減圧器を２つに分割
して２つの減圧器間へバイパス回路の一端を接続してお
けば、凝縮器と蒸発器が入れ替わっても常に中間圧の冷
媒をバイパス回路に流すことができる。また、図１２
は、本発明の冷凍サイクルの制御装置をヒートポンプサ
イクルに適用した場合の冷凍サイクル図の一例を示す。
同図において１８、１９は逆止弁であり、２０は四方弁
である。このような冷媒回路を組めば、熱交換器２ａが
凝縮器の時は冷媒は実線のように流れ、また熱交換器４
ａが凝縮器の時は冷媒は破線のように流れる。したがっ
て、常に高圧の液冷媒をバイパス回路に流すことがで
き、本発明の冷凍サイクルの制御装置を構成することが
可能である。In the above first to fourth embodiments,
In the case of the heat pump cycle, even if the four-way valve is switched and the evaporator and the condenser are switched, one end of the bypass circuit is always connected to the conduit from the condenser outlet to the decompressor outlet. It is possible to configure a control device for the refrigeration cycle. For example, if the pressure reducer is divided into two and one end of the bypass circuit is connected between the two pressure reducers, even if the condenser and the evaporator are exchanged, the intermediate pressure refrigerant can always flow to the bypass circuit. . In addition, FIG.
FIG. 3 shows an example of a refrigeration cycle diagram when the refrigeration cycle control device of the present invention is applied to a heat pump cycle.
In the figure, 18 and 19 are check valves, and 20 is a four-way valve. If such a refrigerant circuit is assembled, when the heat exchanger 2a is a condenser, the refrigerant flows as shown by the solid line, and the heat exchanger 4
When a is a condenser, the refrigerant flows as shown by the broken line. Therefore, the high-pressure liquid refrigerant can always flow through the bypass circuit, and the refrigeration cycle control device of the present invention can be configured.
【００４３】また、上記第１〜第４の実施例において
は、算出した圧縮機吸入冷媒のスーパーヒート量や乾き
度をスーパーヒート制御に利用した場合について説明し
たがそれに限定されるものではなく、例えば蒸発器の除
霜運転中は乾き度を所定値に保つ乾き度制御を行った
り、運転中の乾き度が所定値以下になった保護のために
圧縮機を停止する保護制御に利用する等、他の制御にも
利用可能である。In the first to fourth embodiments, the case where the calculated superheat amount or dryness of the compressor suction refrigerant is used for superheat control has been described, but the present invention is not limited thereto. For example, during defrosting operation of the evaporator, perform dryness control that keeps the dryness at a specified value, or use it for protection control that stops the compressor for protection when the dryness during operation falls below a specified value. It can also be used for other controls.
【００４４】また、上記第１〜第３の実施例において
は、バイパス回路５の一端を凝縮器２と減圧器（電動膨
張弁３）とを結ぶ管路の一部に接続したがこれに限定さ
れるものではなく、液冷媒の割合が多くて圧縮機１の吸
入側より高圧となるところであればよい。例えば減圧器
が２つに分割されている場合は２つの減圧器間へ接続し
てもよく、また減圧器がキャピラリチューブの場合なら
ば、キャピラリチューブの管路上のいずれかの位置へ接
続してもよい。In the first to third embodiments, one end of the bypass circuit 5 is connected to a part of the pipe line connecting the condenser 2 and the pressure reducer (electric expansion valve 3), but this is not the only option. Instead, it is sufficient if the proportion of the liquid refrigerant is large and the pressure becomes higher than that on the suction side of the compressor 1. For example, when the decompressor is divided into two, it may be connected between the two decompressors, and when the decompressor is a capillary tube, it may be connected to any position on the pipeline of the capillary tube. Good.
【００４５】また、上記第２および第３の実施例におい
ては、減圧量可変の補助減圧器については、電動膨張弁
を用いて説明したが、これに限定されるものではなく、
減圧量を制御できるものであれば、他の方式のものを用
いてもよい。In the second and third embodiments, the auxiliary decompressor with variable decompression amount has been described using the electric expansion valve, but the invention is not limited to this.
Other methods may be used as long as the amount of pressure reduction can be controlled.
【００４６】また、本発明の飽和蒸気温度検出回路は、
フロン系冷媒に限らず非共沸混合冷媒であれば、他の冷
媒にも適用可能である。Further, the saturated vapor temperature detection circuit of the present invention is
Not only the CFC-based refrigerant but also a non-azeotropic mixed refrigerant can be applied to other refrigerants.
【００４７】[0047]
【発明の効果】上記実施例より明らかなように本発明の
冷凍サイクルの制御装置は、凝縮器出口から減圧器出口
に至る管路に一端を接続し、他端を蒸発器出口から圧縮
機入口に至る管路に接続したバイパス回路を配設し、こ
のバイパス回路に上流側から順に補助減圧器、冷媒加熱
手段、バイパス回路冷媒温度検出手段を設け、冷媒加熱
手段の加熱量を制御する加熱量制御手段、バイパス回路
冷媒温度検出手段により冷媒温度を所定周期で検出して
その変化量より飽和蒸気温度を判別する判別手段を有
し、蒸発器出口から圧縮機入口に至る管路に圧縮機吸入
冷媒温度検出手段を設け、この圧縮機吸入冷媒温度検出
手段とバイパス回路冷媒温度検出手段で検出された温度
を用いて圧縮機吸入冷媒が過熱蒸気の時はスーパーヒー
ト量を算出し、湿り蒸気の時は乾き度を算出する冷媒状
態算出手段を有し、この冷媒状態算出手段により算出さ
れた冷媒状態を用いて冷凍サイクルの制御を行う制御手
段を有することで、非共沸混合冷媒を用いた冷凍サイク
ルにおいて、冷凍サイクルの構成を複雑にすることなく
圧縮機吸入冷媒の状態を精度よく検出することができ、
これにより最適な冷凍サイクル制御の実現を図ることが
できる。As is apparent from the above-described embodiment, the refrigerating cycle control device of the present invention has one end connected to the conduit from the condenser outlet to the pressure reducer outlet, and the other end from the evaporator outlet to the compressor inlet. A bypass circuit connected to the pipeline leading to is provided with an auxiliary decompressor, a refrigerant heating means, and a bypass circuit refrigerant temperature detection means in that order from the upstream side, and a heating amount for controlling the heating amount of the refrigerant heating means. The control means and the bypass circuit have a determination means for detecting the refrigerant temperature at a predetermined cycle by the refrigerant temperature detection means and determining the saturated vapor temperature based on the amount of change, and suck the compressor into the pipeline from the evaporator outlet to the compressor inlet. Refrigerant temperature detection means is provided, and when the compressor suction refrigerant is superheated steam, the superheat amount is calculated using the temperature detected by this compressor suction refrigerant temperature detection means and the bypass circuit refrigerant temperature detection means, and When it is air, it has a refrigerant state calculating means for calculating the dryness, and by having a control means for controlling the refrigeration cycle using the refrigerant state calculated by this refrigerant state calculating means, the non-azeotropic mixed refrigerant is In the refrigeration cycle used, it is possible to accurately detect the state of the compressor suction refrigerant without complicating the refrigeration cycle configuration,
This makes it possible to realize optimum refrigeration cycle control.
【００４８】また、凝縮器出口から減圧器出口に至る管
路に一端を接続し、他端を蒸発器出力から圧縮機入口に
至る管路に接続したバイパス回路を配設し、このバイパ
ス回路に上流側から順に減圧量可変の補助減圧器、バイ
パス回路冷媒温度検出手段を設け、補助減圧器出口から
冷媒温度検出手段設置位置に至る管路の一部と前記圧縮
機出口から前記凝縮器入口に至る管路の一部とを熱交換
的に接続し、前記補助減圧器の減圧量を制御する減圧量
制御手段、バイパス回路冷媒温度検出手段により冷媒温
度を所定周期で検出してその変化量より飽和蒸気温度を
判別する判別手段を有し、蒸発器出口から圧縮機入口に
至る管路に圧縮機吸入冷媒温度検出手段を設け、この圧
縮機吸入冷媒温度検出手段とバイパス回路冷媒温度検出
手段で検出された温度を用いて圧縮機吸入冷媒が過熱蒸
気の時はスーパーヒート量を算出し、湿り蒸気の時は乾
き度を算出する冷媒状態算出手段を有し、この冷媒状態
算出手段により算出された冷媒状態を用いて冷凍サイク
ルの制御を行う制御手段を有することで、冷凍サイクル
中の熱を利用することができるので新たに加熱手段を付
加することなく圧縮機吸入冷媒の状態を精度よく検出す
ることができ、これにより最適な冷凍サイクル制御の実
現を図ることができる。Further, a bypass circuit having one end connected to a conduit from the condenser outlet to the decompressor outlet and the other end connected to a conduit from the evaporator output to the compressor inlet is provided. Auxiliary decompressor with variable decompression amount from the upstream side, bypass circuit refrigerant temperature detection means are provided, and part of the pipeline from the auxiliary decompressor outlet to the refrigerant temperature detection means installation position and from the compressor outlet to the condenser inlet A pressure reduction amount control means for controlling a pressure reduction amount of the auxiliary pressure reducer by heat exchange connection with a part of the pipeline to reach, a refrigerant temperature is detected at a predetermined cycle by the bypass circuit refrigerant temperature detection means, and a change amount thereof is calculated. The compressor suction refrigerant temperature detection means is provided in the pipeline extending from the evaporator outlet to the compressor inlet, and the compressor suction refrigerant temperature detection means and the bypass circuit refrigerant temperature detection means are provided. was detected Has a refrigerant state calculation unit that calculates the superheat amount when the compressor intake refrigerant is superheated steam and calculates the dryness when it is wet steam, and the refrigerant state calculated by this refrigerant state calculation unit By having the control means for controlling the refrigeration cycle by using, it is possible to utilize the heat in the refrigeration cycle, so it is possible to accurately detect the state of the refrigerant sucked into the compressor without adding a new heating means. As a result, optimal refrigeration cycle control can be realized.
【００４９】また、凝縮器出口から減圧器出口に至る管
路に一端を接続し、他端を蒸発器出口から圧縮機入口に
至る管路に接続したバイパス回路を配設し、このバイパ
ス回路に上流側から順に減圧量可変の補助減圧器、バイ
パス回路冷媒温度検出手段を設け、補助減圧器出口から
冷媒温度検出手段設置位置に至る管路の一部を前記蒸発
器内に配設し、前記補助減圧器の減圧量を制御する減圧
量制御手段、バイパス回路冷媒温度検出手段により冷媒
温度を所定周期で検出してその変化量より飽和蒸気温度
を判別する判別手段を有し、蒸発器出口から圧縮機入口
に至る管路に圧縮機吸入冷媒温度検出手段を設け、この
圧縮機吸入冷媒温度検出手段とバイパス回路冷媒温度検
出手段で検出された温度を用いて圧縮機吸入冷媒が過熱
蒸気の時はスーパーヒート量を算出し、湿り蒸気の時は
乾き度を算出する冷媒状態算出手段を有し、この冷媒状
態算出手段により算出された冷媒状態を用いて冷凍サイ
クルの制御を行う制御手段を有することで、高温の加熱
源と熱交換せずにバイパス回路の冷媒を過熱蒸気にする
ことができるので、短時間で圧縮機吸入冷媒の状態を精
度よく検出することができ、これにより最適な冷凍サイ
クル制御の実現を図ることができる。Further, a bypass circuit having one end connected to a conduit from the condenser outlet to the decompressor outlet and the other end connected to a conduit from the evaporator outlet to the compressor inlet is provided. An auxiliary decompressor having a variable decompression amount from the upstream side, a bypass circuit refrigerant temperature detecting means are provided, and a part of the pipe line from the auxiliary decompressor outlet to the refrigerant temperature detecting means installation position is arranged in the evaporator, and A pressure reducing amount control means for controlling the pressure reducing amount of the auxiliary pressure reducer, a bypass circuit refrigerant temperature detecting means has a determining means for detecting the refrigerant temperature in a predetermined cycle and discriminating the saturated vapor temperature from the change amount thereof, from the evaporator outlet A compressor suction refrigerant temperature detecting means is provided in the pipeline leading to the compressor inlet, and the temperature detected by the compressor suction refrigerant temperature detecting means and the bypass circuit refrigerant temperature detecting means is used when the compressor suction refrigerant is superheated steam. Is super By having a refrigerant state calculating means for calculating the heat quantity and for calculating the dryness in the case of wet steam, and having a control means for controlling the refrigeration cycle using the refrigerant state calculated by the refrigerant state calculating means. Since the refrigerant in the bypass circuit can be turned into superheated steam without exchanging heat with a high-temperature heat source, the state of the refrigerant sucked into the compressor can be accurately detected in a short time, which enables optimum refrigeration cycle control. Can be realized.
【００５０】また、蒸発器出口から圧縮機入口に至る管
路に圧縮機吸入冷媒温度検出手段および圧縮機吸入冷媒
圧力検出手段を設け、この圧縮機吸入冷媒温度検出手段
により検出された温度と圧縮機吸入冷媒圧力検出手段に
より検出された圧力を用いて圧縮機吸入冷媒が過熱蒸気
の時はスーパーヒート量を算出し、湿り蒸気の時は乾き
度を算出する冷媒状態算出手段を有し、この冷媒状態算
出手段により算出された冷媒状態を用いて冷凍サイクル
の制御を行う制御手段を有することで、バイパス回路を
設けずに圧縮機吸入冷媒の状態を精度よく検出すること
ができ、これにより最適な冷凍サイクル制御の実現を図
ることができる。Further, a compressor suction refrigerant temperature detecting means and a compressor suction refrigerant pressure detecting means are provided in a pipe line extending from the evaporator outlet to the compressor inlet, and the temperature and compression detected by the compressor suction refrigerant temperature detecting means. The compressor suction refrigerant using the pressure detected by the machine suction refrigerant pressure detection means calculates the superheat amount when the compressor suction refrigerant is superheated steam, and has a refrigerant state calculation means for calculating the dryness when it is wet steam. By having a control unit that controls the refrigeration cycle using the refrigerant state calculated by the refrigerant state calculation unit, the state of the compressor suction refrigerant can be accurately detected without providing a bypass circuit, which makes it optimal. It is possible to realize various refrigeration cycle control.
【００５１】また、減圧器を減圧量可変減圧器とし、こ
の減圧量可変減圧器の減圧量を制御する主減圧量制御手
段を設け、冷媒状態算出手段により算出されたスーパー
ヒート量若しくは乾き度を用いて主減圧量制御手段によ
り減圧量可変減圧器の減圧量を、スーパーヒート量若し
くは乾き度が所定値となるように制御することで、最適
な冷凍サイクル制御の実現を図ることができる。Further, the decompressor is a variable decompression amount decompressor, and main decompression amount control means for controlling the decompression amount of this decompression amount variable decompression device is provided, and the superheat amount or dryness calculated by the refrigerant state calculation means is set. By using the main decompression amount control means to control the decompression amount of the variable decompression amount decompressor so that the superheat amount or the dryness becomes a predetermined value, optimal refrigeration cycle control can be realized.
【図１】本発明の冷凍サイクルの制御装置の第１の実施
例における冷凍サイクル図FIG. 1 is a refrigeration cycle diagram in a first embodiment of a refrigeration cycle control device of the present invention.
【図２】同実施例におけるＰ−ｈ線図上の冷凍サイクル
図FIG. 2 is a refrigeration cycle diagram on the Ph diagram in the example.
【図３】同実施例における冷媒温度の時間変化を示す特
性図FIG. 3 is a characteristic diagram showing the change over time of the refrigerant temperature in the same example.
【図４】同実施例における制御のフロー図FIG. 4 is a flow chart of control in the embodiment.
【図５】同実施例における制御のフロー図FIG. 5 is a flow chart of control in the embodiment.
【図６】スーパーヒート量、乾き度と電動膨張弁の弁開
度変更量との関係図FIG. 6 is a diagram showing the relationship between the superheat amount, the dryness, and the valve opening change amount of the electric expansion valve.
【図７】本発明の冷凍サイクルの制御装置の第２の実施
例における冷凍サイクル図FIG. 7 is a refrigeration cycle diagram in the second embodiment of the refrigeration cycle control device of the present invention.
【図８】同実施例における制御のフロー図FIG. 8 is a flow chart of control in the embodiment.
【図９】本発明の冷凍サイクルの制御装置の第３の実施
例における冷凍サイクル図FIG. 9 is a refrigeration cycle diagram in a third embodiment of the refrigeration cycle control device of the present invention.
【図１０】本発明の冷凍サイクルの制御装置の第４の実
施例における冷凍サイクル図FIG. 10 is a refrigeration cycle diagram in a fourth embodiment of the refrigeration cycle control device of the present invention.
【図１１】同実施例における制御のフロー図FIG. 11 is a flow chart of control in the same embodiment.
【図１２】本発明の冷凍サイクルの制御装置をヒートポ
ンプサイクルに適用した場合の冷凍サイクル図FIG. 12 is a refrigeration cycle diagram when the refrigeration cycle control device of the present invention is applied to a heat pump cycle.
【図１３】従来の冷凍サイクルの制御装置の冷凍サイク
ル図FIG. 13 is a refrigeration cycle diagram of a conventional refrigeration cycle control device.
【図１４】同冷凍サイクルの制御装置におけるＰ−ｈ線
図上の冷凍サイクル図FIG. 14 is a refrigeration cycle diagram on the Ph diagram in the refrigeration cycle control device.
【図１５】スーパーヒート量と電動膨張弁の弁開度変更
量との関係図FIG. 15 is a diagram showing the relationship between the superheat amount and the valve opening change amount of the electric expansion valve.
【図１６】従来の冷凍サイクルの制御装置における非共
沸混合冷媒を用いた場合のＰ−ｈ線図上の冷凍サイクル
図FIG. 16 is a refrigeration cycle diagram on the Ph diagram when a non-azeotropic mixed refrigerant is used in a conventional refrigeration cycle control device.
１ 圧縮機 ２ 凝縮器 ２ａ 熱交換器 ３ 電動膨張弁（減圧量可変減圧器） ４ 蒸発器 ４ａ 熱交換器 ５ バイパス回路 ６ 補助絞り（補助減圧器） ７ 加熱ヒータ（冷媒加熱手段） ８ 温度センサ（冷媒温度検出手段） ９ 温度センサ（圧縮機吸入冷媒温度検出手段） １０ 加熱ヒータ制御回路（加熱量制御手段） １１ 飽和蒸気温度算出回路（判別手段） １２ 弁開度演算回路（冷媒状態算出手段） １３ 膨張弁駆動回路（減圧量制御手段） １４ 電動膨張弁（減圧量可変の補助減圧器） １５ 熱交換部 １６ 補助蒸発器 １７ 圧力センサ（圧縮機吸入冷媒圧力検出手段） DESCRIPTION OF SYMBOLS 1 Compressor 2 Condenser 2a Heat exchanger 3 Electric expansion valve (Decompression amount variable pressure reducer) 4 Evaporator 4a Heat exchanger 5 Bypass circuit 6 Auxiliary throttle (Auxiliary pressure reducer) 7 Heating heater (Refrigerant heating means) 8 Temperature sensor (Refrigerant temperature detection means) 9 Temperature sensor (compressor suction refrigerant temperature detection means) 10 Heating heater control circuit (heating amount control means) 11 Saturated vapor temperature calculation circuit (determination means) 12 Valve opening calculation circuit (refrigerant state calculation means) ) 13 expansion valve drive circuit (decompression amount control means) 14 electric expansion valve (auxiliary decompressor with variable decompression amount) 15 heat exchange section 16 auxiliary evaporator 17 pressure sensor (compressor suction refrigerant pressure detection means)
フロントページの続き (51)Int.Cl.6 識別記号 庁内整理番号 ＦＩ 技術表示箇所 Ｆ２４Ｆ 11/02 １０２ Ｆ (72)発明者 小林 義典 大阪府門真市大字門真1006番地 松下電器 産業株式会社内Continuation of front page (51) Int.Cl. 6 Identification number Internal reference number FI Technical display location F24F 11/02 102 F (72) Inventor Yoshinori Kobayashi 1006 Kadoma, Kadoma, Osaka Prefecture Matsushita Electric Industrial Co., Ltd.
Claims (5)
を所定の比率で混合した非共沸混合冷媒を用い、圧縮
機、凝縮器、減圧器、蒸発器を順に配管にて環状に連結
して冷媒回路を構成し、凝縮器出口から減圧器出口に至
る管路に一端を接続し、他端を蒸発器出口から圧縮機入
口に至る管路に接続したバイパス回路を配設し、このバ
イパス回路に上流側から順に補助減圧器、冷媒加熱手
段、バイパス回路冷媒温度検出手段を設け、前記冷媒加
熱手段の加熱量を制御する加熱量制御手段、前記バイパ
ス回路冷媒温度検出手段により冷媒温度を所定周期で検
出してその変化量より飽和蒸気温度を判別する判別手段
を有し、前記蒸発器出口から前記圧縮機入口に至る管路
に圧縮機吸入冷媒温度検出手段を設け、この圧縮機吸入
冷媒温度検出手段と前記バイパス回路冷媒温度検出手段
で検出された温度を用いて圧縮機吸入冷媒が過熱蒸気の
時はスーパーヒート量を算出し、湿り蒸気の時は乾き度
を算出する冷媒状態算出手段を有し、この冷媒状態算出
手段により算出された冷媒状態を用いて冷凍サイクルの
制御を行う制御手段を有する冷凍サイクルの制御装置。1. A non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as a refrigerant, and a compressor, a condenser, a pressure reducer, and an evaporator are sequentially connected in an annular shape by pipes. A refrigerant circuit is constructed by connecting one end to the pipeline from the condenser outlet to the decompressor outlet, and the other end is connected to the pipeline from the evaporator outlet to the compressor inlet. An auxiliary pressure reducer, a refrigerant heating means, a bypass circuit refrigerant temperature detection means are provided in order from the upstream side in the circuit, and a heating amount control means for controlling the heating amount of the refrigerant heating means and a predetermined refrigerant temperature by the bypass circuit refrigerant temperature detection means. The compressor suction refrigerant temperature detection means is provided in the pipeline extending from the evaporator outlet to the compressor inlet, the discrimination means for detecting the saturated vapor temperature based on the amount of change in the cycle. Temperature detection means and before The bypass circuit refrigerant temperature detecting means has a refrigerant state calculating means for calculating the superheat amount when the compressor intake refrigerant is superheated steam using the temperature detected, and the dryness when it is wet steam. A refrigeration cycle control device having a control means for controlling the refrigeration cycle using the refrigerant state calculated by the refrigerant state calculation means.
を所定の比率で混合した非共沸混合冷媒を用い、圧縮
機、凝縮器、減圧器、蒸発器を順に配管にて環状に連結
して冷媒回路を構成し、凝縮器出口から減圧器出口に至
る管路に一端を接続し、他端を蒸発器出口から圧縮機入
口に至る管路に接続したバイパス回路を配設し、このバ
イパス回路に上流側から順に減圧量可変の補助減圧器、
バイパス回路冷媒温度検出手段を設け、前記補助減圧器
出口から前記バイパス回路冷媒温度検出手段設置位置に
至る管路の一部と前記圧縮機出口から前記凝縮器入口に
至る管路の一部とを熱交換的に接続し、前記補助減圧器
の減圧量を制御する減圧量制御手段、前記バイパス回路
冷媒温度検出手段により冷媒温度を所定周期で検出して
その変化量より飽和蒸気温度を判別する判別手段を有
し、前記蒸発器出口から前記圧縮機入口に至る管路に圧
縮機吸入冷媒温度検出手段を設け、この圧縮機吸入冷媒
温度検出手段と前記バイパス回路冷媒温度検出手段で検
出された温度を用いて圧縮機吸入冷媒が過熱蒸気の時は
スーパーヒート量を算出し、湿り蒸気の時は乾き度を算
出する冷媒状態算出手段を有し、この冷媒状態算出手段
により算出された冷媒状態を用いて冷凍サイクルの制御
を行う制御手段を有する冷凍サイクルの制御装置。2. A non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as a refrigerant, and a compressor, a condenser, a decompressor, and an evaporator are sequentially connected in an annular shape by pipes. A refrigerant circuit is constructed by connecting one end to the pipeline from the condenser outlet to the decompressor outlet, and the other end is connected to the pipeline from the evaporator outlet to the compressor inlet. Auxiliary decompressor with variable decompression amount in order from the upstream side to the circuit,
Bypass circuit refrigerant temperature detection means is provided, and a part of the pipeline from the auxiliary pressure reducer outlet to the bypass circuit refrigerant temperature detection means installation position and a portion of the pipeline from the compressor outlet to the condenser inlet. A pressure reduction amount control means for controlling the pressure reduction amount of the auxiliary pressure reducer connected by heat exchange, a refrigerant temperature detection means for detecting the refrigerant temperature in a predetermined cycle, and a determination for determining the saturated vapor temperature from the change amount. And a compressor suction refrigerant temperature detecting means is provided in a pipeline extending from the evaporator outlet to the compressor inlet, and the temperature detected by the compressor suction refrigerant temperature detecting means and the bypass circuit refrigerant temperature detecting means. Has a refrigerant state calculation means for calculating the superheat amount when the compressor suction refrigerant is superheated steam and for calculating the dryness when it is wet steam, and the cold state calculated by this refrigerant state calculation means. Control apparatus for a refrigeration cycle having a control unit for controlling the refrigeration cycle using the state.
を所定の比率で混合した非共沸混合冷媒を用い、圧縮
機、凝縮器、減圧器、蒸発器を順に配管にて環状に連結
して冷媒回路を構成し、凝縮器出口から減圧器出口に至
る管路に一端を接続し、他端を蒸発器出口から圧縮機入
口に至る管路に接続したバイパス回路を配設し、このバ
イパス回路に上流側から順に減圧量可変の補助減圧器、
バイパス回路冷媒温度検出手段を設け、前記補助減圧器
出口から前記バイパス回路冷媒温度検出手段設置位置に
至る管路の一部を前記蒸発器内に配設し、前記補助減圧
器の減圧量を制御する減圧量制御手段、前記バイパス回
路冷媒温度検出手段により冷媒温度を所定周期で検出し
てその変化量より飽和蒸気温度を判別する判別手段を有
し、前記蒸発器出口から前記圧縮機入口に至る管路に圧
縮機吸入冷媒温度検出手段を設け、この圧縮機吸入冷媒
温度検出手段と前記バイパス回路冷媒温度検出手段で検
出された温度を用いて圧縮機吸入冷媒が過熱蒸気の時は
スーパーヒート量を算出し、湿り蒸気の時は乾き度を算
出する冷媒状態算出手段を有し、この冷媒状態算出手段
により算出された冷媒状態を用いて冷凍サイクルの制御
を行う制御手段を有する冷凍サイクルの制御装置。3. A non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as a refrigerant, and a compressor, a condenser, a decompressor, and an evaporator are sequentially connected by a pipe in an annular shape. A refrigerant circuit is constructed by connecting one end to the pipeline from the condenser outlet to the decompressor outlet, and the other end is connected to the pipeline from the evaporator outlet to the compressor inlet. Auxiliary decompressor with variable decompression amount in order from the upstream side to the circuit,
A bypass circuit refrigerant temperature detecting means is provided, and a part of a pipe line from the auxiliary decompressor outlet to the bypass circuit refrigerant temperature detecting means installation position is provided in the evaporator to control the decompressing amount of the auxiliary decompressor. Depressurizing amount control means, the bypass circuit refrigerant temperature detecting means for detecting the refrigerant temperature in a predetermined cycle to have a judging means for judging the saturated vapor temperature from the change amount, from the evaporator outlet to the compressor inlet A compressor suction refrigerant temperature detecting means is provided in the pipe, and the superheat amount is used when the compressor suction refrigerant temperature detecting means and the bypass circuit refrigerant temperature detecting means use the temperature detected by the compressor suction refrigerant. And has a refrigerant state calculating means for calculating the dryness in the case of wet steam, and a control means for controlling the refrigeration cycle using the refrigerant state calculated by the refrigerant state calculating means. The control device of the refrigeration cycle.
を所定の比率で混合した非共沸混合冷媒を用い、圧縮
機、凝縮器、減圧器、蒸発器を順に配管にて環状に連結
して冷媒回路を構成し、蒸発器出口から圧縮機入口に至
る管路に圧縮機吸入冷媒温度検出手段および圧縮機吸入
冷媒圧力検出手段を設け、この圧縮機吸入冷媒温度検出
手段により検出された温度と圧縮機吸入冷媒圧力検出手
段により検出された圧力を用いて圧縮機吸入冷媒が過熱
蒸気の時はスーパーヒート量を算出し、湿り蒸気の時は
乾き度を算出する冷媒状態算出手段を有し、この冷媒状
態算出手段により算出された冷媒状態を用いて冷凍サイ
クルの制御を行う制御手段を有する冷凍サイクルの制御
装置。4. A non-azeotropic mixed refrigerant in which two or more kinds of refrigerants having different boiling points are mixed at a predetermined ratio is used as a refrigerant, and a compressor, a condenser, a decompressor, and an evaporator are sequentially connected in an annular shape by pipes. A refrigerant circuit, and a compressor suction refrigerant temperature detection means and a compressor suction refrigerant pressure detection means are provided in the pipeline from the evaporator outlet to the compressor inlet, and the temperature detected by the compressor suction refrigerant temperature detection means And a refrigerant state calculation means for calculating the superheat amount when the compressor suction refrigerant is superheated vapor and the dryness when the compressor suction refrigerant is superheated vapor by using the pressure detected by the compressor suction refrigerant pressure detection means. A refrigeration cycle control device having control means for controlling the refrigeration cycle using the refrigerant state calculated by the refrigerant state calculation means.
量可変減圧器の減圧量を制御する主減圧量制御手段を設
け、冷媒状態算出手段により算出されたスーパーヒート
量若しくは乾き度を用いて主減圧量制御手段により減圧
量可変減圧器の減圧量を、スーパーヒート量若しくは乾
き度が所定値となるように制御する請求項１〜請求項４
のいずれかに記載の冷凍サイクルの制御装置。5. A decompressor is a decompression variable decompressor, main decompression amount control means for controlling the decompression amount of this decompression amount variable decompression device is provided, and the superheat amount or dryness calculated by the refrigerant state calculation means is provided. 5. The main decompression amount control means is used to control the decompression amount of the decompression amount variable decompressor so that the superheat amount or the dryness becomes a predetermined value.
The control device for the refrigeration cycle according to any one of 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP26466993A JP3178192B2 (en) | 1993-10-22 | 1993-10-22 | Refrigeration cycle control device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP26466993A JP3178192B2 (en) | 1993-10-22 | 1993-10-22 | Refrigeration cycle control device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH07120083A true JPH07120083A (en) | 1995-05-12 |
| JP3178192B2 JP3178192B2 (en) | 2001-06-18 |
Family
ID=17406567
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP26466993A Expired - Fee Related JP3178192B2 (en) | 1993-10-22 | 1993-10-22 | Refrigeration cycle control device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3178192B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010106817A1 (en) | 2009-03-19 | 2010-09-23 | ダイキン工業株式会社 | Air conditioning device |
| KR101150949B1 (en) * | 2009-10-21 | 2012-05-29 | 위니아만도 주식회사 | Drying machine of use heat pump and method of controlling the same |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112714854B (en) * | 2018-09-28 | 2022-03-29 | 三菱电机株式会社 | Refrigeration cycle device |
-
1993
- 1993-10-22 JP JP26466993A patent/JP3178192B2/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010106817A1 (en) | 2009-03-19 | 2010-09-23 | ダイキン工業株式会社 | Air conditioning device |
| CN102356285A (en) * | 2009-03-19 | 2012-02-15 | 大金工业株式会社 | Air conditioning device |
| KR101150949B1 (en) * | 2009-10-21 | 2012-05-29 | 위니아만도 주식회사 | Drying machine of use heat pump and method of controlling the same |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3178192B2 (en) | 2001-06-18 |
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|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |