JP4269397B2 - Refrigeration equipment - Google Patents

Refrigeration equipment Download PDF

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Publication number
JP4269397B2
JP4269397B2 JP07369999A JP7369999A JP4269397B2 JP 4269397 B2 JP4269397 B2 JP 4269397B2 JP 07369999 A JP07369999 A JP 07369999A JP 7369999 A JP7369999 A JP 7369999A JP 4269397 B2 JP4269397 B2 JP 4269397B2
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expansion valve
electric expansion
sub
main
circuit
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JP2000274859A (en
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明紀 中井
徹 鈴木
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Daikin Industries Ltd
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Daikin Industries Ltd
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    • 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

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  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Description

【０００１】
【発明の属する技術分野】
この発明は、過冷却回路とインジェクション回路を備えた冷凍装置に関する。
【０００２】
【従来の技術】
従来、この種の冷凍装置としては、図４に示すものがある。この冷凍装置は、圧縮機５１と凝縮器５２と過冷却熱交換器５３と主電動膨張弁５４と蒸発器５５とアキュムレータ５６が順に接続された主回路５７を有する。上記凝縮器５２と過冷却熱交換器５３との間で主回路５７から分岐した分岐管６０は、上記過冷却熱交換器５３の内管５３Ａに接続されている。
【０００３】
この内管５３Ａは、外管６１内を主流の下流から上流へ延びて、インジェクション配管６２に接続されている。上記分岐管６０は副電動膨張弁６３を有している。上記インジェクション配管６２は、圧縮機５１の中間圧の部分５１Ａに接続されている。
【０００４】
この冷凍装置は、過冷却熱交換器５３,分岐管６０,副電動膨張弁６３が構成する過冷却回路によって、凝縮器５２から主電動膨張弁５４に向かう冷媒を過冷却して、冷凍効率の向上を図る。さらに、過冷却熱交換器５３で吸熱した分岐管６０からの分岐冷媒をインジェクション配管６２から圧縮機５１の中間圧の部分５１Ａに注入することによって、冷凍効率の向上を図っている。
【０００５】
【発明が解決しようとする課題】
ところで、インジェクション回路に電動弁などの減圧機構を持つ冷媒回路によって冷媒制御を行う場合、インジェクション用副電動膨張弁６３が流す流量を主電動膨張弁５４が流す流量より少なくする必要がある。何故ならば、副電動膨張弁６３が流す冷媒量が、主電動膨張弁５４が流す冷媒量よりも多いと、過冷却熱交換器５３で冷媒が蒸発しきれず、過度の液冷媒が圧縮機５１に注入されるからである。過度の液冷媒が圧縮機５１に注入されると、液圧縮の恐れがあり、また、メイン側熱交換器である蒸発器５５への流量減となり、性能ダウンにつながる。
【０００６】
上記従来の冷凍装置では、主電動膨張弁５４と副電動膨張弁６３を、運転周波数やサーミスタ温度によって、各々独立して制御していたので、過渡状態では上記のような過度のインジェクションが発生する恐れがあった。
【０００７】
そこで、この発明の目的は、過度のインジェクションを防止できる過冷却回路とインジェクション回路を備えた冷凍装置を提供することにある。
【０００８】
【課題を解決するための手段】
上記目的を達成するため、この発明の請求項１の発明の冷凍装置は、凝縮器と主膨張機構との間に順に設けた副膨張機構と過冷却熱交換器を有する過冷却回路と、上記過冷却熱交換器からのガス冷媒を圧縮機の中間圧部分に注入するインジェクション回路を備える冷凍装置であって、
上記主,副膨張機構は、主,副電動膨張弁からなり、
上記副電動膨張弁が冷媒を流す能力が、上記主電動膨張弁が冷媒を流す能力よりも小さくなるように、副電動膨張弁の上限の開度を制御する膨張弁制御手段を備え、
上記膨張弁制御手段は、
上記過冷却回路における冷媒温度に基づいて、上記副電動膨張弁の目標開度を算出し、
上記主電動膨張弁の開度よりも小さな上記副電動膨張弁の上限開度を算出し、
上記副電動膨張弁の目標開度と上記上限開度とを比較し、上記副電動膨張弁の目標開度が上記上限開度よりも大きいときは、上記副電動膨張弁の上記目標開度を上記上限開度に修正して、上記副電動膨張弁の開度を上記上限開度に修正した目標開度にすることを特徴としている。
【０００９】
この請求項１の発明の冷凍装置では、膨張弁制御手段が、副電動膨張弁の上限の開度を制御して、副電動膨張弁が冷媒を流す能力を、主電動膨張弁が冷媒を流す能力よりも小さくする。したがって、この発明によれば、過度のインジェクションを回避して圧縮機の信頼性向上を果たしつつ、過冷却回路とインジェクション回路によって冷凍効率を向上できる。
【００１０】
また、請求項２の発明は、請求項１に記載の冷凍装置において、上記主電動膨張弁と副電動膨張弁は、構造,寸法が同一の電動膨張弁からなることを特徴としている。
【００１１】
この請求項２の発明では、主電動膨張弁と副電動膨張弁は、構造,寸法が同一の電動膨張弁からなるから、部品を共通化でき、コストダウンを図れる。
【００１２】
【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。
【００１３】
図１に、この発明の冷凍装置の実施の形態としての空気調和機を示す。この実施形態は、圧縮機１,四路切換弁２,室外熱交換器３,整流回路５,室内熱交換器６が順に接続された冷媒回路を有する。上記室内熱交換器６は、アキュムレータ７ａ,７ｂを経由して圧縮機１の吸入側に接続されている。
【００１４】
上記整流回路５は、第１,第２逆止弁１１,１２の直列接続回路と第３,第４逆止弁１３,１４の直列接続回路とが並列に接続された回路である。第１逆止弁１１と第２逆止弁１２は、それらの接続点Ｐ１に向かって順方向になるように接続されており、第３逆止弁１３と第４逆止弁１４は、それらの接続点Ｐ２に向かって逆方向になるように接続されている。
【００１５】
そして、上記整流回路５の接続点Ｐ１とＰ２の間に、過冷却回路８と主電動膨張弁９およびインジェクション回路１０が接続されている。
【００１６】
過冷却回路８は、過冷却熱交換器１５とインジェクション用副電動膨張弁１６とで構成されている。この過冷却熱交換器１５は、接続点Ｐ１と主電動弁９の間に接続されている。また、インジェクション用副電動膨張弁１６は、接続点Ｐ１から分岐して過冷却熱交換器１５内の内管２１の入口２１ａに接続されている。そして、この内管２１の出口２１ｂはインジェクション配管２２に接続されており、このインジェクション配管２２は、上記圧縮機１の中間圧の箇所１aに接続されている。
【００１７】
次に、上記構成の空気調和機の基本動作を説明する。なお、図３には、図１の冷媒回路の各部Ｑ１〜Ｑ８でのモリエル線図上での状態を示している。まず、四路切換弁２が、図１に破線で示す経路を連通させ、冷房位置にあるときには、圧縮機１が吐出した冷媒は、室外熱交換器３で凝縮されて、整流回路５の第１逆止弁１１に流入し、接続点Ｐ１でインジェクション用副電動膨張弁１６へのサブ流と過冷却熱交換器１５へのメイン流とに分かれる。上記メイン流は、この過冷却熱交換器１５で過冷却されてから、主電動弁９で膨張して、接続点Ｐ２,第４逆止弁１４を通って、室内熱交換器６に至る。そして、室内熱交換器６で蒸発したメイン流は、四路切換弁２,アキュムレータ７ａ,７ｂを経て、圧縮機１の吸入側に戻る。
【００１８】
一方、上記サブ流は、上記インジェクション用副電動膨張弁１６で膨張されてから、過冷却熱交換器１５の内管２１を通って、吸熱してから、インジェクション配管２２を通って、圧縮機１の中間圧の箇所１ａに注入される。
【００１９】
また、上記四路切換弁２が、図１に実線で示す経路を連通させて、暖房位置にあるときには、圧縮機１が吐出した冷媒は、室内熱交換器６で凝縮されて、整流回路５の第２逆止弁１２に流入し、接続点Ｐ１でインジェクション用副電動膨張弁１６へのサブ流と過冷却熱交換器１５へのメイン流とに分かれる。上記メイン流は、過冷却熱交換器１５で過冷却されてから、主電動膨張弁９で膨張して、接続点Ｐ２,第３逆止弁１３を通って、室外熱交換器３に至る。そして、室外熱交換器３で蒸発したメイン流は、四路切換弁２,アキュムレータ７ａ,７ｂを経て、圧縮機１の吸入側に戻る。一方、上記サブ流は、インジェクション用副電動膨張弁１６で膨張されてから、過冷却熱交換器１５の内管２１を通って吸熱してから、インジェクション配管２２を通って、圧縮機１の中間圧の箇所１ａに注入される。
【００２０】
このように、この実施の形態によれば、整流回路５の働きによって、冷房時にも暖房時にも、過冷却および、圧縮機１の中間圧の箇所１ａへのガス冷媒の注入を行える。したがって、冷暖両方において、過冷却とガスインジェクションによる効率の向上を図ることができる。
【００２１】
また、この実施形態によれば、インジェクション用副電動膨張弁１６を全閉にすることで、インジェクション回路１０のインジェクション動作をオフにできる。また、副電動膨張弁１６の開度を所望の開度に制御することによって、過冷却回路８による過冷却度およびインジェクション回路１０による注入量を所望の値に設定できる。
【００２２】
次に、この実施形態でのインジェクション用副電動膨張弁１６の制御動作を、図２のフローチャートを参照しながら説明する。なお、この制御を行う装置としては、ここでは、マイクロコンピュータで構成した制御部１０１を用いた。
【００２３】
まず、ステップＳ１では、制御部１０１は、過冷却熱交換器１５の内管２１の入口に接続された配管３１に取り付けられた温度センサ３３から内管２１の入口付近の冷媒温度ｔ１を得て、この冷媒温度ｔ１に基づいて、副電動膨張弁１６の目標開度ＥＶＭＫＢを算出する。次に、ステップＳ２に進み、制御部１０１は、主電動膨張弁９の現在の開度ＥＶＲＬＡを読み込む。この主電動膨張弁９の開度ＥＶＲＬＡは、圧縮機１の吐出管に取り付けた温度センサ３５,室内熱交換器６に取り付けた温度センサ３６,室外熱交換器３に取り付けた温度センサ３７からそれぞれ得た温度ｔ２,ｔ３,ｔ４に基づいて制御される。
【００２４】
次に、ステップＳ３に進み、副電動膨張弁１６の開度上限値を、次式(１)で算出する。
【００２５】
上限開度＝(ＥＶＲＬＡ)×α＋β ………(１)
α＜１，βは、上限開度を(ＥＶＲＬＡ)よりも小さくするような値
次に、ステップＳ４に進み、目標開度ＥＶＭＫＢが、上記上限開度よりも大きいか否かを判断する。目標開度ＥＶＭＫＢが、上記上限開度よりも大きいと判断すれば、ステップＳ５に進み、上記目標開度ＥＶＭＫＢを上記上限開度に修正する。一方、目標開度ＥＶＭＫＢが、上記上限開度よりも大きくないと判断すれば、ステップＳ６に進み、制御部１０１は、副電動膨張弁１６に信号を送り、目標開度ＥＶＭＫＢにする。
【００２６】
この実施形態では、膨張弁制御部１０１が、副電動膨張弁１６の上限の開度を制御して、副電動膨張弁１６が冷媒を流す能力を、主電動膨張弁９が冷媒を流す能力よりも小さくする。したがって、この実施形態によれば、副電動膨張弁１６の開き過ぎによる過度のインジェクションを回避して圧縮機１の故障を回避しつつ、過冷却回路８とインジェクション回路によって空気調和効率を向上できる。
【００２７】
なお、上記主電動膨張弁９と副電動膨張弁１６を、構造,寸法が同一の電動膨張弁で構成した場合には、部品を共通化でき、コストダウンを図れる。
【００２８】
【発明の効果】
以上より明らかなように、この請求項１の発明の冷凍装置は、凝縮器と主膨張機構との間に順に設けた副膨張機構と過冷却熱交換器を有する過冷却回路と、上記過冷却熱交換器からのガス冷媒を圧縮機の中間圧部分に注入するインジェクション回路を備える冷凍装置であって、主,副膨張機構は、主,副電動膨張弁からなり、副電動膨張弁が冷媒を流す能力が、主電動膨張弁が冷媒を流す能力よりも小さくなるように、副電動膨張弁の上限の開度を制御する膨張弁制御手段を備えた。
【００２９】
この請求項１の発明の冷凍装置では、膨張弁制御手段が、副電動膨張弁の上限の開度を制御して、副電動膨張弁が冷媒を流す能力を、主電動膨張弁が冷媒を流す能力よりも小さくする。したがって、この発明によれば、過度のインジェクションを回避して圧縮機の信頼性向上を果たしつつ、過冷却回路とインジェクション回路によって冷凍効率を向上できる。
【００３０】
また、請求項２の発明は、請求項１に記載の冷凍装置において、上記主電動膨張弁と副電動膨張弁は、構造,寸法が同一の電動膨張弁からなる。この請求項２の発明では、主電動膨張弁と副電動膨張弁は、構造,寸法が同一の電動膨張弁からなるから、部品を共通化でき、コストダウンを図れる。
【図面の簡単な説明】
【図１】 この発明の冷凍装置の実施の形態としての空気調和機の冷媒回路図である。
【図２】 上記空気調和機のインジェクション用電動式膨張弁の制御動作を説明するフローチャートである。
【図３】 上記空気調和機の動作を説明するモリエル線図である。
【図４】 従来の冷凍装置の冷媒回路図である。
【符号の説明】
１…圧縮機、１ａ…中間圧の箇所、２…四路切換弁、３…室外熱交換器、
５…整流回路、６…室内熱交換器、７…アキュムレータ、８…過冷却回路、
９…主電動弁、１０…インジェクション回路、１１…第１逆止弁、
１２…第２逆止弁、１３…第３逆止弁、１４…第４逆止弁、
１５…過冷却熱交換器、１６…インジェクション用電動式膨張弁、
２１…内管、２１ａ…入口、２１ｂ…出口、２２…インジェクション配管、
Ｐ１,Ｐ２…接続点、３３,３５,３６,３７…温度センサ、
１０１…膨張弁制御部。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a refrigeration apparatus including a supercooling circuit and an injection circuit.
[0002]
[Prior art]
Conventionally, this type of refrigeration apparatus is shown in FIG. This refrigeration apparatus has a main circuit 57 in which a compressor 51, a condenser 52, a supercooling heat exchanger 53, a main electric expansion valve 54, an evaporator 55, and an accumulator 56 are connected in order. A branch pipe 60 branched from the main circuit 57 between the condenser 52 and the supercooling heat exchanger 53 is connected to the inner pipe 53 </ b> A of the supercooling heat exchanger 53.
[0003]
The inner pipe 53 </ b> A extends in the outer pipe 61 from the mainstream downstream to the upstream, and is connected to the injection pipe 62. The branch pipe 60 has a sub electric expansion valve 63. The injection pipe 62 is connected to the intermediate pressure portion 51 </ b> A of the compressor 51.
[0004]
This refrigeration apparatus supercools the refrigerant from the condenser 52 to the main electric expansion valve 54 by the subcooling circuit formed by the subcooling heat exchanger 53, the branch pipe 60, and the auxiliary electric expansion valve 63, thereby improving the refrigeration efficiency. Improve. Furthermore, the refrigeration efficiency is improved by injecting the branched refrigerant from the branch pipe 60 that has absorbed heat in the supercooling heat exchanger 53 into the intermediate pressure portion 51A of the compressor 51 from the injection pipe 62.
[0005]
[Problems to be solved by the invention]
By the way, when the refrigerant control is performed by a refrigerant circuit having a pressure reducing mechanism such as an electric valve in the injection circuit, it is necessary to make the flow rate of the auxiliary electric expansion valve 63 for injection smaller than the flow rate of the main electric expansion valve 54. This is because if the amount of refrigerant flowing through the auxiliary electric expansion valve 63 is larger than the amount of refrigerant flowing through the main electric expansion valve 54, the refrigerant cannot evaporate in the supercooling heat exchanger 53, and excessive liquid refrigerant flows into the compressor 51. It is because it is injected into. If excessive liquid refrigerant is injected into the compressor 51, there is a risk of liquid compression, and the flow rate to the evaporator 55, which is the main heat exchanger, is reduced, leading to performance degradation.
[0006]
In the conventional refrigeration apparatus, the main electric expansion valve 54 and the sub electric expansion valve 63 are controlled independently by the operating frequency and the thermistor temperature, and thus excessive injection as described above occurs in the transient state. There was a fear.
[0007]
Therefore, an object of the present invention is to provide a supercooling circuit capable of preventing excessive injection and a refrigeration apparatus including the injection circuit.
[0008]
[Means for Solving the Problems]
In order to achieve the above object, a refrigeration apparatus according to claim 1 of the present invention includes a subcooling circuit having a sub-expansion mechanism and a subcooling heat exchanger provided in this order between a condenser and a main expansion mechanism, A refrigeration apparatus comprising an injection circuit for injecting gas refrigerant from a supercooling heat exchanger into an intermediate pressure portion of a compressor,
The main and sub expansion mechanisms consist of main and sub electric expansion valves,
Ability to the secondary electric expansion valve flow refrigerant, so that the main electric expansion valve is smaller than the capability of flowing a coolant, Bei example an expansion valve control means for controlling the upper limit of the degree of opening of the sub-electric expansion valve,
The expansion valve control means includes
Based on the refrigerant temperature in the supercooling circuit, calculate the target opening of the auxiliary electric expansion valve,
Calculate the upper limit opening of the auxiliary electric expansion valve smaller than the opening of the main electric expansion valve,
The target opening of the sub electric expansion valve is compared with the upper limit opening, and when the target opening of the sub electric expansion valve is larger than the upper limit opening, the target opening of the sub electric expansion valve is The opening degree of the auxiliary electric expansion valve is corrected to the upper limit opening degree so that the opening degree is set to the target opening degree corrected to the upper limit opening degree .
[0009]
In the refrigeration apparatus according to the first aspect of the present invention, the expansion valve control means controls the upper opening of the auxiliary electric expansion valve so that the auxiliary electric expansion valve can flow the refrigerant, and the main electric expansion valve allows the refrigerant to flow. Make it smaller than ability. Therefore, according to the present invention, the refrigeration efficiency can be improved by the supercooling circuit and the injection circuit while avoiding excessive injection and improving the reliability of the compressor.
[0010]
According to a second aspect of the present invention, in the refrigeration apparatus according to the first aspect, the main electric expansion valve and the auxiliary electric expansion valve are composed of electric expansion valves having the same structure and dimensions.
[0011]
In the second aspect of the invention, the main electric expansion valve and the sub electric expansion valve are made of electric expansion valves having the same structure and dimensions, so that the parts can be made common and the cost can be reduced.
[0012]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.
[0013]
FIG. 1 shows an air conditioner as an embodiment of the refrigeration apparatus of the present invention. This embodiment has a refrigerant circuit in which a compressor 1, a four-way switching valve 2, an outdoor heat exchanger 3, a rectifier circuit 5, and an indoor heat exchanger 6 are connected in order. The indoor heat exchanger 6 is connected to the suction side of the compressor 1 via accumulators 7a and 7b.
[0014]
The rectifier circuit 5 is a circuit in which a series connection circuit of the first and second check valves 11 and 12 and a series connection circuit of the third and fourth check valves 13 and 14 are connected in parallel. The 1st check valve 11 and the 2nd check valve 12 are connected so that it may become a forward direction toward those connection points P1, and the 3rd check valve 13 and the 4th check valve 14 are those Are connected in the opposite direction toward the connection point P2.
[0015]
A supercooling circuit 8, a main electric expansion valve 9, and an injection circuit 10 are connected between connection points P1 and P2 of the rectifying circuit 5.
[0016]
The supercooling circuit 8 includes a supercooling heat exchanger 15 and an auxiliary electric expansion valve 16 for injection. The supercooling heat exchanger 15 is connected between the connection point P1 and the main motor-operated valve 9. The injection sub electric expansion valve 16 is branched from the connection point P <b> 1 and connected to the inlet 21 a of the inner pipe 21 in the supercooling heat exchanger 15. The outlet 21 b of the inner pipe 21 is connected to an injection pipe 22, and the injection pipe 22 is connected to the intermediate pressure location 1 a of the compressor 1.
[0017]
Next, the basic operation of the air conditioner having the above configuration will be described. FIG. 3 shows a state on the Mollier diagram at each part Q1 to Q8 of the refrigerant circuit of FIG. First, when the four-way switching valve 2 communicates the path indicated by the broken line in FIG. 1 and is in the cooling position, the refrigerant discharged from the compressor 1 is condensed in the outdoor heat exchanger 3 and the second rectifier circuit 5 1 flows into the check valve 11 and is divided into a sub-flow to the injection auxiliary electric expansion valve 16 and a main flow to the supercooling heat exchanger 15 at the connection point P1. The main flow is supercooled by the supercooling heat exchanger 15, then expanded by the main electric valve 9, and reaches the indoor heat exchanger 6 through the connection point P <b> 2 and the fourth check valve 14. The main flow evaporated in the indoor heat exchanger 6 returns to the suction side of the compressor 1 through the four-way switching valve 2 and the accumulators 7a and 7b.
[0018]
On the other hand, the sub-flow is expanded by the injection sub-electric expansion valve 16, passes through the inner pipe 21 of the supercooling heat exchanger 15, absorbs heat, passes through the injection pipe 22, and then passes through the compressor 1. The intermediate pressure is injected into the location 1a.
[0019]
Further, when the four-way switching valve 2 communicates the path shown by the solid line in FIG. 1 and is in the heating position, the refrigerant discharged from the compressor 1 is condensed in the indoor heat exchanger 6, and the rectifier circuit 5. The second check valve 12 is divided into a sub-flow to the injection sub-electric expansion valve 16 and a main flow to the supercooling heat exchanger 15 at the connection point P1. The main flow is supercooled by the supercooling heat exchanger 15, then expanded by the main electric expansion valve 9, and reaches the outdoor heat exchanger 3 through the connection point P <b> 2 and the third check valve 13. The main flow evaporated in the outdoor heat exchanger 3 returns to the suction side of the compressor 1 through the four-way switching valve 2 and the accumulators 7a and 7b. On the other hand, the sub-flow is expanded by the injection sub-electric expansion valve 16, then absorbs heat through the inner pipe 21 of the supercooling heat exchanger 15, passes through the injection pipe 22, and passes through the middle of the compressor 1. It is injected into the location 1a of pressure.
[0020]
Thus, according to this embodiment, the function of the rectifier circuit 5 allows supercooling and injection of gas refrigerant into the intermediate pressure location 1a of the compressor 1 during cooling and heating. Therefore, in both cooling and heating, it is possible to improve efficiency by supercooling and gas injection.
[0021]
Moreover, according to this embodiment, the injection operation of the injection circuit 10 can be turned off by fully closing the injection auxiliary electric expansion valve 16. Further, by controlling the opening degree of the auxiliary electric expansion valve 16 to a desired opening degree, the degree of supercooling by the supercooling circuit 8 and the injection amount by the injection circuit 10 can be set to desired values.
[0022]
Next, the control operation of the injection auxiliary electric expansion valve 16 in this embodiment will be described with reference to the flowchart of FIG. Here, as a device for performing this control, a control unit 101 constituted by a microcomputer is used.
[0023]
First, in step S1, the control unit 101 obtains the refrigerant temperature t1 near the inlet of the inner pipe 21 from the temperature sensor 33 attached to the pipe 31 connected to the inlet of the inner pipe 21 of the supercooling heat exchanger 15. Based on the refrigerant temperature t1, the target opening degree EVMKB of the auxiliary electric expansion valve 16 is calculated. Next, it progresses to step S2 and the control part 101 reads the present opening degree EVRLA of the main electric expansion valve 9. FIG. The opening EVRLA of the main electric expansion valve 9 is determined by a temperature sensor 35 attached to the discharge pipe of the compressor 1, a temperature sensor 36 attached to the indoor heat exchanger 6, and a temperature sensor 37 attached to the outdoor heat exchanger 3, respectively. Control is performed based on the obtained temperatures t2, t3, and t4.
[0024]
Next, it progresses to step S3 and the opening degree upper limit of the sub electric expansion valve 16 is calculated by following Formula (1).
[0025]
Upper limit opening = (EVRLA) × α + β (1)
α <1, β is a value that makes the upper limit opening smaller than (EVRLA). Then, the process proceeds to step S4, where it is determined whether the target opening EVMKB is larger than the upper limit opening. If it is determined that the target opening degree EVMKB is larger than the upper limit opening degree, the process proceeds to step S5, and the target opening degree EVMKB is corrected to the upper limit opening degree. On the other hand, if it is determined that the target opening degree EVMKB is not larger than the upper limit opening degree, the process proceeds to step S6, and the control unit 101 sends a signal to the auxiliary electric expansion valve 16 to set the target opening degree EVMKB.
[0026]
In this embodiment, the expansion valve control unit 101 controls the opening degree of the upper limit of the auxiliary electric expansion valve 16 so that the auxiliary electric expansion valve 16 allows the refrigerant to flow, and the main electric expansion valve 9 allows the refrigerant to flow. Also make it smaller. Therefore, according to this embodiment, air conditioning efficiency can be improved by the subcooling circuit 8 and the injection circuit while avoiding excessive injection due to excessive opening of the auxiliary electric expansion valve 16 and avoiding a failure of the compressor 1.
[0027]
If the main electric expansion valve 9 and the sub electric expansion valve 16 are constituted by electric expansion valves having the same structure and dimensions, the parts can be shared and the cost can be reduced.
[0028]
【The invention's effect】
As apparent from the above, the refrigeration apparatus according to the first aspect of the present invention includes a subcooling circuit having a sub-expansion mechanism and a subcooling heat exchanger provided in this order between the condenser and the main expansion mechanism, and the subcooling circuit. A refrigeration system including an injection circuit for injecting gas refrigerant from a heat exchanger into an intermediate pressure portion of a compressor, wherein the main and sub expansion mechanisms are composed of main and sub electric expansion valves, and the sub electric expansion valve is supplying refrigerant. Expansion valve control means for controlling the upper limit opening of the auxiliary electric expansion valve is provided so that the flow capacity is smaller than the capacity of the main electric expansion valve to flow the refrigerant.
[0029]
In the refrigeration apparatus according to the first aspect of the present invention, the expansion valve control means controls the upper opening of the auxiliary electric expansion valve so that the auxiliary electric expansion valve can flow the refrigerant, and the main electric expansion valve allows the refrigerant to flow. Make it smaller than ability. Therefore, according to the present invention, the refrigeration efficiency can be improved by the supercooling circuit and the injection circuit while avoiding excessive injection and improving the reliability of the compressor.
[0030]
According to a second aspect of the present invention, in the refrigeration apparatus according to the first aspect, the main electric expansion valve and the sub electric expansion valve are electric expansion valves having the same structure and dimensions. In the second aspect of the invention, the main electric expansion valve and the sub electric expansion valve are made of electric expansion valves having the same structure and dimensions, so that the parts can be made common and the cost can be reduced.
[Brief description of the drawings]
FIG. 1 is a refrigerant circuit diagram of an air conditioner as an embodiment of a refrigeration apparatus according to the present invention.
FIG. 2 is a flowchart for explaining a control operation of an electric expansion valve for injection of the air conditioner.
FIG. 3 is a Mollier diagram illustrating the operation of the air conditioner.
FIG. 4 is a refrigerant circuit diagram of a conventional refrigeration apparatus.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Compressor, 1a ... Location of intermediate pressure, 2 ... Four-way switching valve, 3 ... Outdoor heat exchanger,
5 ... Rectifier circuit, 6 ... Indoor heat exchanger, 7 ... Accumulator, 8 ... Supercooling circuit,
9 ... Main motor operated valve, 10 ... Injection circuit, 11 ... First check valve,
12 ... 2nd check valve, 13 ... 3rd check valve, 14 ... 4th check valve,
15 ... Supercooling heat exchanger, 16 ... Electric expansion valve for injection,
21 ... Inner pipe, 21a ... Inlet, 21b ... Outlet, 22 ... Injection pipe,
P1, P2 ... connection point, 33, 35, 36, 37 ... temperature sensor,
101: Expansion valve control unit.

Claims (2)

凝縮器(３,６)と主膨張機構(９)との間に順に設けた副膨張機構(１６)と過冷却熱交換器(１５)を有する過冷却回路(８)と、上記過冷却熱交換器(１５)からのガス冷媒を圧縮機(１)の中間圧部分(１ａ)に注入するインジェクション回路(１０)を備える冷凍装置であって、
上記主,副膨張機構は、主,副電動膨張弁(９,１６)からなり、
上記副電動膨張弁(１６)が冷媒を流す能力が、上記主電動膨張弁(９)が冷媒を流す能力よりも小さくなるように、副電動膨張弁(１６)の上限の開度を制御する膨張弁制御手段(１０１)を備え、
上記膨張弁制御手段 ( １０１ ) は、
上記過冷却回路における冷媒温度に基づいて、上記副電動膨張弁の目標開度を算出し、
上記主電動膨張弁の開度よりも小さな上記副電動膨張弁の上限開度を算出し、
上記副電動膨張弁の目標開度と上記上限開度とを比較し、上記副電動膨張弁の目標開度が上記上限開度よりも大きいときは、上記副電動膨張弁の上記目標開度を上記上限開度に修正して、上記副電動膨張弁の開度を上記上限開度に修正した目標開度にすることを特徴とする冷凍装置。A sub-cooling circuit (8) having a sub-expansion mechanism (16) and a sub-cooling heat exchanger (15) provided in order between the condenser (3, 6) and the main expansion mechanism (9); A refrigeration apparatus comprising an injection circuit (10) for injecting gas refrigerant from an exchanger (15) into an intermediate pressure part (1a) of a compressor (1),
The main and sub expansion mechanisms are composed of main and sub electric expansion valves (9, 16).
The upper opening of the auxiliary electric expansion valve (16) is controlled so that the ability of the auxiliary electric expansion valve (16) to flow refrigerant is smaller than the ability of the main electric expansion valve (9) to flow refrigerant. e Bei expansion valve control means (101),
The expansion valve control means (101),
Based on the refrigerant temperature in the supercooling circuit, calculate the target opening of the auxiliary electric expansion valve,
Calculate the upper limit opening of the auxiliary electric expansion valve smaller than the opening of the main electric expansion valve,
The target opening of the sub electric expansion valve is compared with the upper limit opening, and when the target opening of the sub electric expansion valve is larger than the upper limit opening, the target opening of the sub electric expansion valve is The refrigeration apparatus , wherein the opening degree is corrected to the upper limit opening degree, and the opening degree of the auxiliary electric expansion valve is set to the target opening degree corrected to the upper limit opening degree . 請求項１に記載の冷凍装置において、
上記主電動膨張弁(９)と副電動膨張弁(１６)は、構造,寸法が同一の電動膨張弁からなることを特徴とする冷凍装置。The refrigeration apparatus according to claim 1,
The main electric expansion valve (9) and the auxiliary electric expansion valve (16) are electric expansion valves having the same structure and dimensions.
JP07369999A 1999-03-18 1999-03-18 Refrigeration equipment Expired - Fee Related JP4269397B2 (en)

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JP4459776B2 (en) 2004-10-18 2010-04-28 三菱電機株式会社 Heat pump device and outdoor unit of heat pump device
JP2007240025A (en) * 2006-03-06 2007-09-20 Daikin Ind Ltd Refrigerating device
CN100554820C (en) 2006-03-27 2009-10-28 三菱电机株式会社 Refrigerating air-conditioning
JP4716935B2 (en) * 2006-06-27 2011-07-06 三洋電機株式会社 Refrigeration cycle apparatus and heat pump water heater
JP2009243881A (en) * 2009-07-30 2009-10-22 Mitsubishi Electric Corp Heat pump device and outdoor unit of heat pump device
JP4550153B2 (en) * 2009-07-30 2010-09-22 三菱電機株式会社 Heat pump device and outdoor unit of heat pump device
JP4767340B2 (en) * 2009-07-30 2011-09-07 三菱電機株式会社 Heat pump control device
JP5235925B2 (en) * 2010-03-03 2013-07-10 日立アプライアンス株式会社 Refrigeration equipment
JP2010159967A (en) * 2010-04-19 2010-07-22 Mitsubishi Electric Corp Heat pump device and outdoor unit for the heat pump device
CN102869929B (en) * 2010-04-30 2015-01-28 大金工业株式会社 Heat pump system
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