JP2856160B2 - Refrigeration device control method and refrigeration device - Google Patents
Refrigeration device control method and refrigeration deviceInfo
- Publication number
- JP2856160B2 JP2856160B2 JP8194481A JP19448196A JP2856160B2 JP 2856160 B2 JP2856160 B2 JP 2856160B2 JP 8194481 A JP8194481 A JP 8194481A JP 19448196 A JP19448196 A JP 19448196A JP 2856160 B2 JP2856160 B2 JP 2856160B2
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat exchanger
- expansion valve
- temperature
- sub
- 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.)
- Expired - Fee Related
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
- F25B2400/13—Economisers
-
- 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
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
-
- 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
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2117—Temperatures of an evaporator
- F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、過冷却回路の過
冷却度を制御して、能力やＣＯＰ（成績係数)を向上さ
せる冷凍装置の制御方法および冷凍装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration system control method and a refrigeration system for controlling the degree of supercooling of a subcooling circuit to improve the capacity and COP (coefficient of performance).
【０００２】[0002]
【従来の技術】従来、冷凍装置としては、図５に示すよ
うに、凝縮器１０１とメイン膨張弁１０２との間に接続
された過冷却用熱交換器１０３と、上記凝縮器１０１と
上記過冷却用熱交換器１０３との間に接続されて上記過
冷却用熱交換器１０３に過冷却用冷媒を供給するサブ膨
張弁１０５とが構成する過冷却回路１０６を備えたもの
がある。2. Description of the Related Art Conventionally, as a refrigerating apparatus, as shown in FIG. 5, a supercooling heat exchanger 103 connected between a condenser 101 and a main expansion valve 102; Some include a subcooling circuit 106 that is connected between the cooling heat exchanger 103 and a sub-expansion valve 105 that supplies the subcooling refrigerant to the subcooling heat exchanger 103.
【０００３】この冷凍装置は、凝縮器１０１から分岐し
サブ膨張弁１０５を経て冷却された冷媒を、上記過冷却
用熱交換器１０３の冷却管１０３ａに通し、メイン膨張
弁１０２および蒸発器１０７をバイパスして圧縮機１０
８の手前でメイン冷媒路１１０に合流させている。In this refrigerating apparatus, a refrigerant branched from a condenser 101 and cooled through a sub-expansion valve 105 is passed through a cooling pipe 103a of the supercooling heat exchanger 103, and a main expansion valve 102 and an evaporator 107 are cooled. Bypass compressor 10
8 and is merged with the main refrigerant passage 110.
【０００４】一方、上記凝縮器１０１から過冷却用熱交
換器１０３の被冷却管１０３ｂに至った冷媒は、冷却管
１０３ａを通る冷媒で冷やされてからメイン膨張弁１１
１に至る。この過冷却用熱交換器１０３の働きによっ
て、上記冷媒の過冷却が増加される。On the other hand, the refrigerant that has reached the cooled pipe 103b of the supercooling heat exchanger 103 from the condenser 101 is cooled by the refrigerant passing through the cooling pipe 103a, and then cooled by the main expansion valve 11b.
Leads to 1. By the operation of the subcooling heat exchanger 103, the supercooling of the refrigerant is increased.
【０００５】図６に、上記過冷却用熱交換器１０３があ
る場合のモリエル線図を破線で示し、上記過冷却用熱交
換器１０３がない場合のモリエル線図を実線で示す。図
６から分かるように、過冷却が増加することによって、
(蒸発器入口圧力が同じ場合)蒸発器１０７入口での冷媒
温度がＴｅ0からＴｅ1に低下し、空気との温度差が大き
くなる。したがって、蒸発器の蒸発能力が向上する。し
たがって、能力とＣＯＰが向上する。FIG. 6 shows a Mollier diagram with the supercooling heat exchanger 103 by a broken line, and a Mollier diagram without the supercooling heat exchanger 103 by a solid line. As can be seen from FIG. 6, the increase in supercooling
(When the evaporator inlet pressure is the same) The refrigerant temperature at the evaporator 107 inlet decreases from Te 0 to Te 1 , and the temperature difference with the air increases. Therefore, the evaporating capability of the evaporator is improved. Therefore, capacity and COP are improved.
【０００６】もっとも、上記過冷却用熱交換器１０３を
用いる場合には、冷媒の一部が蒸発器１０７をバイパス
することになるから、蒸発器１０７を循環する冷媒量は
減少する。しかし、この蒸発器を循環する冷媒量が減少
することによって、図６に示すように、蒸発側の圧損が
低下して圧縮機１０８の吸入圧力が高くなる。したがっ
て、圧縮機１０８を循環する冷媒量が増大する。したが
って、能力とＣＯＰが向上する。However, when the supercooling heat exchanger 103 is used, a part of the refrigerant bypasses the evaporator 107, so that the amount of the refrigerant circulating through the evaporator 107 is reduced. However, as the amount of the refrigerant circulating in the evaporator decreases, the pressure loss on the evaporation side decreases and the suction pressure of the compressor 108 increases as shown in FIG. Therefore, the amount of the refrigerant circulating in the compressor 108 increases. Therefore, capacity and COP are improved.
【０００７】[0007]
【発明が解決しようとする課題】ところが、上記従来の
冷凍装置では、上記過冷却回路１０６による過冷却度を
制御することができないから、冷凍装置の運転条件によ
っては、過冷却度を適性な値に制御できず、能力やＣＯ
Ｐを確実に向上させることができないという問題があ
る。However, in the conventional refrigeration system, the degree of supercooling by the supercooling circuit 106 cannot be controlled. Therefore, depending on the operating conditions of the refrigeration system, the degree of supercooling is set to an appropriate value. Control and capacity and CO
There is a problem that P cannot be reliably improved.
【０００８】そこで、この発明の目的は、過冷却回路に
よる過冷却度を適正な値に制御でき、能力やＣＯＰを確
実に向上させることができる冷凍装置の制御方法および
冷凍装置を提供することにある。It is an object of the present invention to provide a refrigeration apparatus control method and a refrigeration apparatus that can control the degree of supercooling by a subcooling circuit to an appropriate value and can surely improve the capacity and COP. is there.
【０００９】[0009]
【課題を解決するための手段】上記目的を達成するた
め、請求項１の発明の冷凍装置の制御方法は、凝縮器と
メイン膨張弁との間に接続された過冷却用熱交換器と、
上記凝縮器と上記過冷却用熱交換器との間に接続されて
上記過冷却用熱交換器に過冷却用冷媒を供給するサブ膨
張弁とが構成する分岐型の過冷却回路を有する冷凍装置
の制御方法であって、蒸発器の入口での冷媒温度Ｔｅを
Ｔｅ温度センサで検出し、上記過冷却用熱交換器の出口
での冷媒温度ＴscをＴｓｃ温度センサで検出し、上記蒸
発器の入口での冷媒温度Ｔｅが、上記入口での冷媒の乾
き度が略零になる冷媒温度になるように、上記蒸発器の
入口での冷媒温度Ｔｅと過冷却用熱交換器の出口での冷
媒温度Ｔｓｃに基づいて、上記サブ膨張弁の開度を制御
することを特徴としている。According to a first aspect of the present invention, there is provided a method for controlling a refrigerating apparatus, comprising: a supercooling heat exchanger connected between a condenser and a main expansion valve;
A refrigeration apparatus having a branch-type subcooling circuit connected between the condenser and the subcooling heat exchanger and configured by a sub-expansion valve configured to supply a subcooling refrigerant to the subcooling heat exchanger. Control method, the refrigerant temperature Te at the inlet of the evaporator is detected by a Te temperature sensor, the refrigerant temperature Tsc at the outlet of the supercooling heat exchanger is detected by a Tsc temperature sensor, The refrigerant temperature Te at the inlet of the evaporator and the refrigerant temperature at the outlet of the supercooling heat exchanger are set so that the refrigerant temperature Te at the inlet becomes a refrigerant temperature at which the dryness of the refrigerant at the inlet becomes substantially zero. The opening degree of the sub expansion valve is controlled based on the temperature Tsc.
【００１０】この発明の制御方法によれば、蒸発器の入
口での冷媒温度Ｔｅと、過冷却用熱交換器の出口での冷
媒温度Ｔｓｃとを検出して、このＴｅとＴｓｃとに基づ
いて、サブ膨張弁の開度を調節して、蒸発器の入口での
冷媒温度Ｔｅを、上記入口での冷媒の乾き度が略零にな
る温度にする。[0010] According to the control method of the present invention, the refrigerant temperature Te at the inlet of the evaporator and the refrigerant temperature Tsc at the outlet of the subcooling heat exchanger are detected, and based on the detected Te and Tsc. By adjusting the opening of the sub expansion valve, the refrigerant temperature Te at the inlet of the evaporator is set to a temperature at which the dryness of the refrigerant at the inlet becomes substantially zero.
【００１１】したがって、蒸発器の運転効率を確実に向
上させて、ＣＯＰを確実に向上できる。同時に、低圧側
での圧力を上昇させて、圧縮機の吸入圧力を高くして、
能力を確実に向上できる。Therefore, the operating efficiency of the evaporator can be reliably improved, and the COP can be reliably improved. At the same time, raise the pressure on the low pressure side, raise the suction pressure of the compressor,
The ability can be surely improved.
【００１２】また、請求項２の発明の冷凍装置は、凝縮
器とメイン膨張弁との間に接続された過冷却用熱交換器
と、上記凝縮器と上記過冷却用熱交換器との間に接続さ
れ上記過冷却用熱交換器に過冷却用冷媒を供給するサブ
膨張弁とが構成する分岐型の過冷却回路を有する冷凍装
置であって、蒸発器の入口での冷媒温度Ｔｅを検出する
Ｔｅ温度センサと、上記過冷却用熱交換器の出口での冷
媒温度Ｔscを検出するＴsc温度センサと、上記蒸発器の
入口での冷媒温度が、上記入口での冷媒の乾き度が略零
になる冷媒温度になるように、上記蒸発器の入口での冷
媒温度Ｔｅと過冷却用熱交換器の出口での冷媒温度Ｔｓ
ｃに基づいて、上記サブ膨張弁の開度を制御するサブ膨
張弁制御手段を備えていることを特徴としている。Further, according to a second aspect of the present invention, there is provided a refrigerating apparatus, comprising: a supercooling heat exchanger connected between a condenser and a main expansion valve; and a supercooling heat exchanger connected between the condenser and the supercooling heat exchanger. And a sub-expansion valve configured to supply a sub-cooling refrigerant to the sub-cooling heat exchanger and connected to the sub-cooling heat exchanger, wherein a refrigerant temperature Te at an inlet of the evaporator is detected. A Te temperature sensor, a Tsc temperature sensor for detecting a refrigerant temperature Tsc at the outlet of the supercooling heat exchanger, and a refrigerant temperature at the inlet of the evaporator, where the dryness of the refrigerant at the inlet is substantially zero. And the refrigerant temperature Ts at the outlet of the subcooling heat exchanger so that the refrigerant temperature becomes
The sub-expansion valve control means for controlling the opening of the sub-expansion valve on the basis of c.
【００１３】この冷凍装置によれば、サブ膨張弁制御手
段が、蒸発器の入口での冷媒温度Ｔｅと、過冷却用熱交
換器の出口での冷媒温度Ｔｓｃとを検出して、このＴｅ
とＴｓｃとに基づいて、サブ膨張弁の開度を調節して、
蒸発器の入口での冷媒温度Ｔｅを、上記入口での冷媒の
乾き度が略零になる温度にする。According to this refrigeration system, the sub-expansion valve control means detects the refrigerant temperature Te at the inlet of the evaporator and the refrigerant temperature Tsc at the outlet of the subcooling heat exchanger, and detects this Te.
And Tsc, the opening degree of the sub expansion valve is adjusted,
The refrigerant temperature Te at the inlet of the evaporator is set to a temperature at which the dryness of the refrigerant at the inlet becomes substantially zero.
【００１４】したがって、蒸発器の運転効率を確実に向
上させて、ＣＯＰを確実に向上できる。同時に、低圧側
での圧力を上昇させて、圧縮機の吸入圧力を高くして、
能力を確実に向上できる。Therefore, the operating efficiency of the evaporator can be reliably improved, and the COP can be reliably improved. At the same time, raise the pressure on the low pressure side, raise the suction pressure of the compressor,
The ability can be surely improved.
【００１５】[0015]
【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.
【００１６】図１に、この発明の冷凍装置の実施の形態
を示す。この実施の形態は、凝縮機としての室外熱交換
器１と分岐型の過冷却回路２とメイン電動膨張弁３と蒸
発器としての室内熱交換器５と圧縮機６と四路切替弁７
とを有している。上記過冷却回路２は、主路８から分岐
した分岐路１０に接続されたサブ電動膨張弁１１と、室
外熱交換器１とメイン電動膨張弁３との間に接続された
過冷却用熱交換器としての２重管熱交換器１２とを有す
る。上記サブ電動膨張弁３から上記２重管熱交換器１２
に供給された冷却用冷媒は、上記主路８から上記２重管
熱交換器１２に供給された冷媒と熱交換して、上記冷媒
を過冷却する。一方、上記２重管熱交換器１２を通り抜
けた冷却用冷媒は主路８に合流してアキュムレータ１３
に至る。FIG. 1 shows an embodiment of a refrigeration apparatus according to the present invention. In this embodiment, an outdoor heat exchanger 1 as a condenser, a branch type supercooling circuit 2, a main electric expansion valve 3, an indoor heat exchanger 5 as an evaporator, a compressor 6, and a four-way switching valve 7
And The subcooling circuit 2 includes a sub-electric expansion valve 11 connected to a branch path 10 branched from the main path 8, and a subcooling heat exchange connected between the outdoor heat exchanger 1 and the main electric expansion valve 3. And a double tube heat exchanger 12 as a vessel. From the sub electric expansion valve 3 to the double pipe heat exchanger 12
The cooling refrigerant supplied to the heat exchanger exchanges heat with the refrigerant supplied from the main path 8 to the double-pipe heat exchanger 12 to supercool the refrigerant. On the other hand, the cooling refrigerant that has passed through the double-tube heat exchanger 12 joins the main path 8 and enters the accumulator 13.
Leads to.
【００１７】また、この実施形態は、上記２重管熱交換
器１２の出口での冷媒温度Ｔｓｃを検出するＴｓｃ温度
センサ１５と、上記室内熱交換器５の入口での冷媒温度
Ｔｅを検出するＴｅ温度センサ１６を有している。ま
た、この実施形態は、圧縮機６が吐出する冷媒の温度Ｔ
Qを検出する吐出温度センサ１７と、室外熱交換器１の
入口での冷媒温度Ｔｃを検出するＴｃ温度センサ１８と
を有する。In this embodiment, a Tsc temperature sensor 15 for detecting the refrigerant temperature Tsc at the outlet of the double-tube heat exchanger 12 and a refrigerant temperature Te at the inlet of the indoor heat exchanger 5 are detected. It has a Te temperature sensor 16. In this embodiment, the temperature T of the refrigerant discharged from the compressor 6 is set to T.
It has a discharge temperature sensor 17 for detecting Q, and a Tc temperature sensor 18 for detecting the refrigerant temperature Tc at the entrance of the outdoor heat exchanger 1.
【００１８】そして、この実施形態は、上記各温度セン
サ１５,１６,１７,１８からの温度検出信号が入力さ
れ、この検出信号に基づいてサブ電動膨張弁２およびメ
イン電動膨張弁３の開度を調整する膨張弁制御部２０を
有している。In this embodiment, the temperature detection signals from the temperature sensors 15, 16, 17, and 18 are input, and the opening degrees of the sub-electric expansion valve 2 and the main electric expansion valve 3 are determined based on the detection signals. Is provided.
【００１９】上記冷凍装置の動作を、図２および図３に
示したフローチャートに沿って説明する。The operation of the refrigerating apparatus will be described with reference to the flowcharts shown in FIGS.
【００２０】まず、ステップＳ１で、上記膨張弁制御部
２０は、上記サブ電動膨張弁２を全閉にする。First, in step S1, the expansion valve control section 20 fully closes the sub electric expansion valve 2.
【００２１】次に、ステップＳ２に進む。このステップ
Ｓ２では、上記膨張弁制御部２０は、メイン電動膨張弁
３の開度を調節することによって、圧縮機６の吸込口で
の冷媒の過熱度ＳＨを制御する。すなわち、上記膨張弁
制御部２０は、Ｔｅ温度センサ１６，Ｔｃ温度センサ１
８から入力された信号によって冷媒温度Ｔｅ，Ｔｃを得
る。そして、この制御部２０は、この冷媒温度Ｔｅ,Ｔ
ｃと、圧縮機６単体のエネルギ効率によって決定される
図２のモリエル線図上の傾きＫとから、上記過熱度ＳＨ
を適性値ＳＨｍにするような圧縮機６の吐出温度ＴQの
目標値ＴQｍを算出する。次に、上記膨張弁制御部２０
は、上記吐出温度センサ１７から入力された信号によっ
て圧縮機６が吐出する冷媒の温度ＴQを得て、この吐出
冷媒温度ＴQが上記目標値ＴQｍになるように、メイン電
動弁３の開度を調節する。このようにメイン電動弁３の
開度を制御することによって、過熱度ＳＨを適性値ＳＨ
ｍにすることができ、圧縮機６の手前で確実に冷媒を蒸
発させて、圧縮機６の信頼性を確保できる。Next, the process proceeds to step S2. In step S2, the expansion valve control unit 20 controls the degree of superheat SH of the refrigerant at the suction port of the compressor 6 by adjusting the opening of the main electric expansion valve 3. That is, the expansion valve control unit 20 includes the Te temperature sensor 16 and the Tc temperature sensor 1
The refrigerant temperatures Te and Tc are obtained based on the signal input from 8. Then, the control unit 20 determines the refrigerant temperatures Te, T
c and the slope K on the Mollier diagram in FIG. 2 determined by the energy efficiency of the compressor 6 alone, the superheat degree SH
The calculated target value T Q m of discharge temperature T Q of the compressor 6 so as to suitability value SHm. Next, the expansion valve control unit 20
Obtains the temperature T Q of the refrigerant discharged from the compressor 6 based on the signal input from the discharge temperature sensor 17, and sets the main electric valve 3 so that the discharged refrigerant temperature T Q becomes the target value T Qm. Adjust the opening of. By controlling the opening degree of the main motor-operated valve 3 in this manner, the degree of superheat SH is reduced to the appropriate value SH.
m, and the refrigerant can be reliably evaporated before the compressor 6 to ensure the reliability of the compressor 6.
【００２２】次に、ステップＳ３に進む。このステップ
Ｓ３では、上記膨張弁制御部２０は、サブ電動膨張弁１
１の開度を調節することによって、メイン電動膨張弁３
の入口での過冷却度ＳＣを制御する。このサブ電動膨張
弁１１の制御を、図３のフローチャートを参照しながら
説明する。Next, the process proceeds to step S3. In step S3, the expansion valve control unit 20 controls the sub-electric expansion valve 1
By adjusting the opening of the main electric expansion valve 3
The degree of supercooling SC at the inlet of is controlled. The control of the sub electric expansion valve 11 will be described with reference to the flowchart of FIG.
【００２３】まず、ステップＳ１１で、上記膨張弁制御
部２０は、上記Ｔｅ温度センサ１６からの信号によっ
て、上記室内熱交換器５の入口での冷媒温度Ｔｅを得
る。図２のＴｅは、サブ電動膨張弁全閉での入口冷媒温
度を示す。次に、ステップＳ１２に進み、上記冷媒温度
Ｔｅを２重管熱交換器１２の出口での冷媒温度Ｔｓｃの
目標値Ｔscmにする。次に、ステップＳ１３に進み、上
記Ｔｓｃ温度センサ１５からの信号によって、冷媒温度
Ｔｓｃを得て、ステップＳ１４で、この冷媒温度Ｔｓｃ
が上記目標値Ｔscmになるような、サブ電動膨張弁１１
の開度を算出して、サブ電動膨張弁１１に与えるべきパ
ルス信号を算出する。次に、ステップＳ１５に進み、上
記算出したパルス信号を上記サブ電動膨張弁１１に出力
してから、ステップＳ１１に戻る。First, in step S11, the expansion valve control section 20 obtains the refrigerant temperature Te at the inlet of the indoor heat exchanger 5 based on the signal from the Te temperature sensor 16. Te in FIG. 2 indicates the inlet refrigerant temperature when the sub electric expansion valve is fully closed. Next, the process proceeds to step S12, in which the refrigerant temperature Te is set to a target value Tscm of the refrigerant temperature Tsc at the outlet of the double tube heat exchanger 12. Next, in step S13, the refrigerant temperature Tsc is obtained from the signal from the Tsc temperature sensor 15, and in step S14, the refrigerant temperature Tsc is obtained.
Is smaller than the target value Tscm.
Is calculated, and a pulse signal to be given to the sub electric expansion valve 11 is calculated. Next, the process proceeds to step S15, where the calculated pulse signal is output to the sub electric expansion valve 11, and then returns to step S11.
【００２４】このような過冷却度ＳＣの制御によって、
図２に破線で示すように、室内熱交換器５の入口での冷
媒の乾き度を略零にすることができるから、室内熱交換
器５の運転効率が良くなり、能力とＣＯＰを確実に向上
できる。また、図２に破線で示すように、低圧側での圧
力が上昇するから、圧縮機６の吸入圧力を高くして、能
力とＣＯＰを確実に向上させることができる。By controlling the degree of supercooling SC,
As shown by the dashed line in FIG. 2, since the dryness of the refrigerant at the inlet of the indoor heat exchanger 5 can be made substantially zero, the operation efficiency of the indoor heat exchanger 5 is improved, and the capacity and COP are surely reduced. Can be improved. Further, as indicated by the broken line in FIG. 2, the pressure on the low pressure side increases, so that the suction pressure of the compressor 6 can be increased, and the capacity and COP can be reliably improved.
【００２５】[0025]
【発明の効果】以上より明らかなように、請求項１の発
明の冷凍装置の制御方法は、蒸発器の入口での冷媒温度
Ｔｅと、過冷却用熱交換器の出口での冷媒温度Ｔｓｃと
を検出して、このＴｅとＴｓｃとに基づいて、サブ膨張
弁の開度を調節して、蒸発器の入口での冷媒温度Ｔｅ
を、上記入口での冷媒の乾き度が略零になる温度にす
る。As is clear from the above, the control method of the refrigerating apparatus according to the first aspect of the present invention relates to a method of controlling the temperature of the refrigerant Te at the inlet of the evaporator and the temperature Tsc of the refrigerant at the outlet of the subcooling heat exchanger. Is detected, and the opening degree of the sub-expansion valve is adjusted based on the Te and Tsc, and the refrigerant temperature Te at the inlet of the evaporator is adjusted.
At a temperature at which the dryness of the refrigerant at the inlet becomes substantially zero.
【００２６】したがって、蒸発器の運転効率を確実に向
上させて、ＣＯＰを確実に向上できる。同時に、低圧側
での圧力を上昇させて、圧縮機の吸入圧力を高くして、
能力を確実に向上できる。Therefore, the operating efficiency of the evaporator can be reliably improved, and the COP can be reliably improved. At the same time, raise the pressure on the low pressure side, raise the suction pressure of the compressor,
The ability can be surely improved.
【００２７】また、請求項２の発明の冷凍装置は、サブ
膨張弁制御手段が、蒸発器の入口での冷媒温度Ｔｅと、
過冷却用熱交換器の出口での冷媒温度Ｔｓｃとを検出し
て、このＴｅとＴｓｃとに基づいて、サブ膨張弁の開度
を調節して、蒸発器の入口での冷媒温度Ｔｅを、上記入
口での冷媒の乾き度が略零になる温度にする。Further, in the refrigeration apparatus according to the second aspect of the present invention, the sub-expansion valve control means controls the refrigerant temperature Te at the inlet of the evaporator,
The refrigerant temperature Tsc at the outlet of the subcooling heat exchanger is detected, and based on the Te and Tsc, the opening degree of the sub-expansion valve is adjusted, and the refrigerant temperature Te at the inlet of the evaporator is calculated as follows. The temperature at which the dryness of the refrigerant at the inlet is substantially zero.
【００２８】したがって、蒸発器の運転効率を確実に向
上させて、ＣＯＰを確実に向上できる。同時に、低圧側
での圧力を上昇させて、圧縮機の吸入圧力を高くして、
能力を確実に向上できる。Therefore, the operating efficiency of the evaporator can be reliably improved, and the COP can be reliably improved. At the same time, raise the pressure on the low pressure side, raise the suction pressure of the compressor,
The ability can be surely improved.
【図１】 この発明の冷凍装置の実施形態のブロック図
である。FIG. 1 is a block diagram of an embodiment of a refrigeration apparatus of the present invention.
【図２】 上記実施形態の動作を説明するモリエル線図
である。FIG. 2 is a Mollier diagram for explaining the operation of the embodiment.
【図３】 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. 3 is a flowchart illustrating an operation of a control unit of the embodiment.
【図４】 上記実施形態のサブ電動弁制御を説明するフ
ローチャートである。FIG. 4 is a flowchart illustrating a sub motor-operated valve control of the embodiment.
【図５】 従来の冷凍装置のブロック図である。FIG. 5 is a block diagram of a conventional refrigeration apparatus.
【図６】 上記従来の冷凍装置の動作を説明するモリエ
ル線図である。FIG. 6 is a Mollier diagram for explaining the operation of the conventional refrigeration apparatus.
１…室外熱交換器、２…過冷却回路、３…メイン電動膨
張弁、５…室内熱交換器、６…圧縮機、７…四路切替
弁、８…主路、１０…分岐路、１１…サブ電動膨張弁、
１２…２重管熱交換器、１３…アキュムレータ、１５…
Ｔｓｃ温度センサ、１６…Ｔｅ温度センサ、１７…吐出
温度センサ、１８…Ｔｃ温度センサ、２０…膨張弁制御
部。DESCRIPTION OF SYMBOLS 1 ... Outdoor heat exchanger, 2 ... Subcooling circuit, 3 ... Main electric expansion valve, 5 ... Indoor heat exchanger, 6 ... Compressor, 7 ... Four-way switching valve, 8 ... Main path, 10 ... Branch path, 11 … Sub electric expansion valve,
12 ... double tube heat exchanger, 13 ... accumulator, 15 ...
Tsc temperature sensor, 16: Te temperature sensor, 17: discharge temperature sensor, 18: Tc temperature sensor, 20: expansion valve control unit.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 繁永 昌弥 滋賀県草津市岡本町字大谷1000番地の２ ダイキン工業株式会社滋賀製作所内 (56)参考文献 実開 昭53−65053（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.6，ＤＢ名) F25B 1/00 F25B 13/00──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Masaya Shigenaga, 1000 Oya, Okamoto-cho, Kusatsu-shi, Shiga 2 Daiga Industries Co., Ltd. Shiga Works (56) Reference Reference 58) Field surveyed (Int.Cl. 6 , DB name) F25B 1/00 F25B 13/00
Claims (2)
接続された過冷却用熱交換器(１２)と、上記凝縮器(１)
と上記過冷却用熱交換器(１２)との間に接続されて上記
過冷却用熱交換器(１２)に過冷却用冷媒を供給するサブ
膨張弁(１１)とが構成する分岐型の過冷却回路(２)を有
する冷凍装置の制御方法であって、 蒸発器(５)の入口での冷媒温度ＴｅをＴｅ温度センサ
(１６)で検出し、 上記過冷却用熱交換器(１２)の出口での冷媒温度Ｔscを
Ｔｓｃ温度センサ(１５)で検出し、 上記蒸発器(５)の入口での冷媒温度Ｔｅが、上記入口で
の冷媒の乾き度が略零になる冷媒温度になるように、上
記蒸発器(５)の入口での冷媒温度Ｔｅと過冷却用熱交換
器(１２)の出口での冷媒温度Ｔｓｃに基づいて、上記サ
ブ膨張弁(１１)の開度を制御することを特徴とする冷凍
装置の制御方法。1. A supercooling heat exchanger (12) connected between a condenser (1) and a main expansion valve (3), and the condenser (1).
And a sub-expansion valve (11) connected between the sub-cooling heat exchanger (12) and the sub-expansion valve (11) for supplying the sub-cooling refrigerant to the sub-cooling heat exchanger (12). A method for controlling a refrigerating apparatus having a cooling circuit (2), comprising: detecting a refrigerant temperature Te at an inlet of an evaporator (5) by a Te temperature sensor;
(16), the refrigerant temperature Tsc at the outlet of the supercooling heat exchanger (12) is detected by the Tsc temperature sensor (15), and the refrigerant temperature Te at the inlet of the evaporator (5) is: The refrigerant temperature Te at the inlet of the evaporator (5) and the refrigerant temperature Tsc at the outlet of the subcooling heat exchanger (12) are adjusted so that the refrigerant has a temperature at which the dryness of the refrigerant at the inlet becomes substantially zero. And controlling the opening degree of the sub-expansion valve (11) based on the control method.
接続された過冷却用熱交換器(１２)と、上記凝縮器(１)
と上記過冷却用熱交換器(１２)との間に接続され上記過
冷却用熱交換器(１２)に過冷却用冷媒を供給するサブ膨
張弁(１１)とが構成する分岐型の過冷却回路(２)を有す
る冷凍装置であって、 蒸発器(５)の入口での冷媒温度Ｔｅを検出するＴｅ温度
センサ(１６)と、 上記過冷却用熱交換器(１２)の出口での冷媒温度Ｔscを
検出するＴsc温度センサ(１５)と、 上記蒸発器(５)の入口での冷媒温度が、上記入口での冷
媒の乾き度が略零になる冷媒温度になるように、上記蒸
発器(５)の入口での冷媒温度Ｔｅと過冷却用熱交換器
(１２）の出口での冷媒温度Ｔｓｃに基づいて、上記サ
ブ膨張弁(１１)の開度を制御するサブ膨張弁制御手段
(２０)を備えていることを特徴とする冷凍装置。2. A supercooling heat exchanger (12) connected between a condenser (1) and a main expansion valve (3), and the condenser (1).
And a sub-expansion valve (11) connected between the subcooling heat exchanger (12) and the subcooling heat exchanger (12) for supplying the subcooling refrigerant to the subcooling heat exchanger (12). A refrigeration apparatus having a circuit (2), a Te temperature sensor (16) for detecting a refrigerant temperature Te at an inlet of an evaporator (5), and a refrigerant at an outlet of the supercooling heat exchanger (12). A Tsc temperature sensor (15) for detecting the temperature Tsc; and the evaporator so that the refrigerant temperature at the inlet of the evaporator (5) becomes a refrigerant temperature at which the dryness of the refrigerant at the inlet becomes substantially zero. (5) Refrigerant temperature Te at inlet and subcooling heat exchanger
(12) a sub-expansion valve control means for controlling the opening of the sub-expansion valve (11) based on the refrigerant temperature Tsc at the outlet
A refrigeration apparatus comprising (20).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8194481A JP2856160B2 (en) | 1996-07-24 | 1996-07-24 | Refrigeration device control method and refrigeration device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8194481A JP2856160B2 (en) | 1996-07-24 | 1996-07-24 | Refrigeration device control method and refrigeration device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH1038399A JPH1038399A (en) | 1998-02-13 |
| JP2856160B2 true JP2856160B2 (en) | 1999-02-10 |
Family
ID=16325263
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8194481A Expired - Fee Related JP2856160B2 (en) | 1996-07-24 | 1996-07-24 | Refrigeration device control method and refrigeration device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2856160B2 (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3440910B2 (en) * | 2000-02-17 | 2003-08-25 | ダイキン工業株式会社 | Refrigeration equipment |
| EP1762794B1 (en) * | 1999-10-18 | 2017-03-22 | Daikin Industries, Ltd. | Refrigerating device |
| KR100618212B1 (en) * | 2003-10-16 | 2006-09-01 | 엘지전자 주식회사 | Control system and method for refrigerant temperature of air conditioner |
| KR101114325B1 (en) | 2004-05-11 | 2012-02-14 | 엘지전자 주식회사 | Air conditioner |
| KR100624639B1 (en) | 2004-12-17 | 2006-09-21 | 이태한 | A heat pump system |
| JP4696634B2 (en) * | 2005-03-28 | 2011-06-08 | アイシン精機株式会社 | Engine driven air conditioner |
| KR101227475B1 (en) | 2005-08-31 | 2013-01-30 | 엘지전자 주식회사 | Air conditioner |
| JP2007085706A (en) * | 2005-09-26 | 2007-04-05 | Sanyo Electric Co Ltd | Refrigerating device |
| JP5144959B2 (en) * | 2007-05-25 | 2013-02-13 | 三菱重工業株式会社 | Heat source machine and control method thereof |
| JP2011179697A (en) * | 2010-02-26 | 2011-09-15 | Panasonic Corp | Refrigerating cycle device and water heating/cooling device |
| WO2021192074A1 (en) * | 2020-03-25 | 2021-09-30 | 日立ジョンソンコントロールズ空調株式会社 | Air conditioner |
-
1996
- 1996-07-24 JP JP8194481A patent/JP2856160B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH1038399A (en) | 1998-02-13 |
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