JPS6073260A - Refrigeration cycle - Google Patents
Refrigeration cycleInfo
- Publication number
- JPS6073260A JPS6073260A JP18020583A JP18020583A JPS6073260A JP S6073260 A JPS6073260 A JP S6073260A JP 18020583 A JP18020583 A JP 18020583A JP 18020583 A JP18020583 A JP 18020583A JP S6073260 A JPS6073260 A JP S6073260A
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- gas
- refrigeration cycle
- evaporator
- differential pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Saccharide Compounds (AREA)
- Fats And Perfumes (AREA)
- Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は、ガスバイパス回路、差圧式２方弁を用いた冷
凍サイクルに関するものであり、特に、冷凍サイクルの
消費電力の低減と、圧縮機の起動時における負荷軽減に
好適である。さらに、原価低減の面からも好適である。Detailed Description of the Invention [Field of Application of the Invention] The present invention relates to a refrigeration cycle using a gas bypass circuit and a differential pressure two-way valve. Suitable for reducing load at startup. Furthermore, it is suitable from the viewpoint of cost reduction.
従来の冷凍サイクルを第１図に示すと、圧縮機１、凝縮
器２．減圧器３．蒸発器４．逆止弁５゜ストップ用電磁
弁６、バランス用電磁弁７．を順次冷媒管で接続されて
いる。この冷凍サイクルにおいて、圧縮機ｌの運転中に
は、ストップ用電磁弁６は開き、バランス用電磁弁７は
閉じた状態となっており、圧縮１２１より吐出された冷
媒は、凝縮器２、減圧器３、蒸発器４、逆止弁５、の順
に循環して冷却を行う。圧縮（幾１の停止中には、スト
ップ用電磁弁６は閉じ、バランス用電磁弁７は開いた状
態となる。このような、弁制副を行うｉＪｆにより、圧
縮（幾１の運転を停止させる際、凝縮器２にあった冷媒
が蒸発器４に流入してしまい、圧縮機１運転開始直後に
凝縮器２から蒸発器４に冷媒が流れ込まず、冷え出しが
悪くなるという欠点、及び圧縮機１停市中に凝縮器２か
ら高温ガス冷媒が蒸発器４に流入して、蒸発器を温めて
しまうという欠点を無くしている。また、圧縮磯１停止
中にバランス用電磁弁７′を開く事により、圧縮機前後
の圧力差を無くし、圧縮機１の起動を軽くする事が可能
であるという特徴を有している。さらに、逆止弁５は圧
縮機１の停止中に、高圧ガス冷媒が蒸発器４に戻るのを
防止している。このような、冷凍サイクルにおいては、
効率が向上するという反１ｎｉ、電磁弁が２個必要とな
り、電磁弁通電中の電力消費と、原価上昇を招くという
大きな欠点があった。A conventional refrigeration cycle is shown in FIG. 1, which includes a compressor 1, a condenser 2. Pressure reducer 3. Evaporator 4. Check valve 5° stop solenoid valve 6, balance solenoid valve 7. are sequentially connected by refrigerant pipes. In this refrigeration cycle, while the compressor 1 is operating, the stop solenoid valve 6 is open and the balance solenoid valve 7 is closed, and the refrigerant discharged from the compressor 121 is transferred to the condenser 2, the depressurizer Cooling is performed by circulating in the order of the container 3, the evaporator 4, and the check valve 5. While the compression engine 1 is stopped, the stop solenoid valve 6 is closed and the balance solenoid valve 7 is open. When doing so, the refrigerant that was in the condenser 2 flows into the evaporator 4, and the refrigerant does not flow from the condenser 2 to the evaporator 4 immediately after the compressor 1 starts operating, resulting in poor cooling. This eliminates the disadvantage that high-temperature gas refrigerant flows from the condenser 2 into the evaporator 4 and warms the evaporator while the compressor 1 is stopped.Also, when the balance solenoid valve 7' is closed while the compressor 1 is stopped, By opening, the check valve 5 eliminates the pressure difference before and after the compressor, making it possible to start the compressor 1 more easily.Furthermore, the check valve 5 prevents high pressure while the compressor 1 is stopped. This prevents the gas refrigerant from returning to the evaporator 4. In such a refrigeration cycle,
Although the efficiency is improved, two solenoid valves are required, which has the major disadvantage of consuming electricity while the solenoid valves are energized and increasing the cost.
本発明の目的は、圧縮＠１が停止した際に、圧縮機１の
前後での圧力差を無くし、ホットガスの蒸発器４への流
入を防止する差圧式２方弁を有ししかも運転中の効率を
も低下させずに、消費電力の低減、圧縮機］の小形化、
起動装置の簡略化、原ｆ＋Ｉｆ低減を成し遂げる事の可
能な冷凍サイクルを提供することにある。The object of the present invention is to have a differential pressure type two-way valve that eliminates the pressure difference before and after the compressor 1 and prevents hot gas from flowing into the evaporator 4 when the compression @ 1 is stopped, and also during operation. reducing power consumption and downsizing the compressor without reducing its efficiency.
The object of the present invention is to provide a refrigeration cycle that can simplify the starting device and reduce the original f+If.
本発明によると、圧縮機運転中には、減圧器入口側にあ
るガス冷媒を蒸発器に流しても冷凍効果かないことから
、圧縮機の吸入側に戻し、圧縮機停止中には、ガスバラ
ンス回路によりホットガスを圧縮機吸込側にバイパスす
るため、圧縮機前後での圧ノＪはバランスする。さらｌ
こ、圧縮機停止時には、低圧側か高圧側と圧力バランス
する事によって発生する圧力」−昇により作動する差圧
式２方弁により、高圧側から蒸発器へのホットカス流入
を防ぎ、消電力効果を高めている。According to the present invention, even if the gas refrigerant on the inlet side of the pressure reducer flows into the evaporator during compressor operation, there is no refrigeration effect, so it is returned to the suction side of the compressor, and when the compressor is stopped, the gas Since the circuit bypasses the hot gas to the compressor suction side, the pressures before and after the compressor are balanced. Sara l
When the compressor is stopped, the differential pressure two-way valve is activated by increasing the pressure generated by balancing the pressure between the low-pressure side and the high-pressure side, preventing hot scum from flowing into the evaporator from the high-pressure side and reducing power consumption. It's increasing.
以下、本発明の−・実施例を第２図、第３図、第４図、
第５図により説明する。第２図は、圧縮機１が運転中の
状態を示し、１は圧縮機、２は凝縮器、３は減圧器、４
は蒸発器、５は逆止弁、８は気液分離２陣、９は差圧式
２方弁、１４は連通管、１５はカスバランス用毛細管、
１６は差圧引込用毛細管であり、これらは、第２図のよ
うに接続されて冷凍サイクルを構成している。かかる冷
凍サイクルにおいて、圧縮機１が運転を開始すると。Embodiments of the present invention are shown in FIGS. 2, 3, and 4 below.
This will be explained with reference to FIG. Figure 2 shows the compressor 1 in operation, with 1 being the compressor, 2 being the condenser, 3 being the pressure reducer, and 4 being the compressor.
is an evaporator, 5 is a check valve, 8 is two gas-liquid separation groups, 9 is a differential pressure type two-way valve, 14 is a communication pipe, 15 is a capillary tube for cass balance,
16 is a capillary tube for drawing in differential pressure, and these are connected as shown in FIG. 2 to constitute a refrigeration cycle. In this refrigeration cycle, when the compressor 1 starts operating.
差圧２方弁９における第１弁内室１０が低圧となり、第
２弁内室１１との間に差圧が生じ、その差圧力が板バネ
１８の力に打ち勝ち、ダイヤフラム１３を押し上げて、
ストップ用ボール１２がポートを開らく。また、気液分
離器８においては、ガス冷媒と液冷媒が分離され、ガス
冷媒は、ガスバランス用毛細管１５を辿り圧縮機１吸込
側にバイパスされる。一方、液冷媒は、開放状態となっ
ている差圧２方弁９を辿って減圧器３で減圧され、蒸発
器４へと流入する。ここで、ガス冷媒は蒸発器４におい
て何の冷却作用はもたず、蒸発器４で冷却される分がエ
ンタルピの損失となる。したがって、このような冷凍サ
イクルを用いると、上記エンタルピ差分だけ、冷却する
エンタルピが増加するという利点が生ずる。次に、第３
図は圧縮機１が停止にした状態を示す。圧縮機１が停止
すると。The pressure in the first valve internal chamber 10 of the differential pressure two-way valve 9 becomes low, and a differential pressure is generated between it and the second valve internal chamber 11. The differential pressure overcomes the force of the leaf spring 18 and pushes up the diaphragm 13.
A stop ball 12 opens the port. Further, in the gas-liquid separator 8, the gas refrigerant and the liquid refrigerant are separated, and the gas refrigerant follows the gas balance capillary tube 15 and is bypassed to the suction side of the compressor 1. On the other hand, the liquid refrigerant follows the differential pressure two-way valve 9 which is in an open state, is reduced in pressure by the pressure reducer 3, and flows into the evaporator 4. Here, the gas refrigerant has no cooling effect in the evaporator 4, and the amount cooled by the evaporator 4 results in enthalpy loss. Therefore, when such a refrigeration cycle is used, there is an advantage that the enthalpy for cooling increases by the enthalpy difference. Next, the third
The figure shows a state in which the compressor 1 is stopped. When compressor 1 stops.
カスバランス用毛細管を通じて、圧縮機１前後の高圧側
、低圧側のバランスが行なわれる。The high-pressure side and low-pressure side before and after the compressor 1 are balanced through the capillary for cass balancing.
すなわち、差圧引込管１６の連結しである圧縮（幾１の
吸込側の圧力が急速に」二がし、これまで開らいていた
差圧２方弁９のダイヤフラム１３を押し下げて、軸棒］
７に固定されたスト・ンプ用ボール１２がポートを閉じ
る。この結果、高圧側の凝縮器２より流入するホットガ
スが、蒸発器４へと流れるのを遮断する４丁ができる。That is, the pressure on the suction side of the connection of the differential pressure inlet pipe 16 is rapidly released, pushing down the diaphragm 13 of the differential pressure two-way valve 9, which had been open, and causing the shaft rod to open. ]
A strike ball 12 fixed to 7 closes the port. As a result, four pipes are formed that block hot gas flowing from the condenser 2 on the high pressure side from flowing to the evaporator 4.
以上の如く、本発明によれば、ガスバイパス用の気液分
離器８と。As described above, according to the present invention, the gas-liquid separator 8 for gas bypass.
差圧式２方弁９を用いる事により、圧縮機１の断続運転
中に、圧縮機１が停止した際、高圧側から蒸発器４への
ホットガス流入を防止して、消費電力量の低減を図り、
さらに、圧縮機１の吐出側と吸込側との間に発生ずる差
圧をバランスさせる小により、圧縮機１の起動トルクを
低減させる事がＦＵ能となる。すなわち、圧縮機１につ
いて、小形化、起動装置の簡略といった原価低減にも結
びつく。By using the differential pressure type two-way valve 9, when the compressor 1 is stopped during intermittent operation, hot gas is prevented from flowing into the evaporator 4 from the high pressure side, reducing power consumption. Planning,
Furthermore, by balancing the differential pressure generated between the discharge side and the suction side of the compressor 1, it becomes possible to reduce the starting torque of the compressor 1. That is, the compressor 1 can be made smaller and the starting device can be simplified, leading to cost reduction.
本発明によれば、断続運転中の冷凍サイクルにおいて、
圧縮機１が停止した時、差圧２方弁９が閉じる事により
、高圧側から蒸発器４へのホットカスの流入を防止でき
、冷蔵庫へ侵入する熱負荷を遮断できるので、消費電力
量が低減できる。さらに、気液分離器８によって、圧縮
機１の前後で発生した圧力差を短時間にバランスする事
ができ、圧縮機１の起動トルク・を低減する。すなわち
、圧縮機ｌの小形化、起動装置の簡略化といった原価低
減を図る事が可能となる。According to the present invention, in the refrigeration cycle during intermittent operation,
When the compressor 1 stops, the differential pressure two-way valve 9 closes to prevent hot scum from flowing into the evaporator 4 from the high pressure side, cutting off the heat load entering the refrigerator, reducing power consumption. can. Furthermore, the gas-liquid separator 8 can balance the pressure difference generated before and after the compressor 1 in a short time, reducing the starting torque of the compressor 1. That is, it is possible to reduce the cost by downsizing the compressor l and simplifying the starting device.
次に、圧縮機１の運転中には、気液分離器８により分離
されたガス冷媒が、ガスバイパス用毛細管１５によって
、圧縮機１吸込側へとバイパスされ、蒸発器４へ流入す
るガス冷媒が減少するため。Next, while the compressor 1 is operating, the gas refrigerant separated by the gas-liquid separator 8 is bypassed to the suction side of the compressor 1 by the gas bypass capillary 15, and the gas refrigerant flows into the evaporator 4. decreases.
ガス冷媒を蒸発器４温度まで下げる分の熱エネルギを損
失する事なく運転でき、消費電力量を低減する事ができ
る。The operation can be performed without losing the thermal energy required to lower the gas refrigerant to the evaporator 4 temperature, and power consumption can be reduced.
第１図は、従来の冷凍サイクルの構成図である。
第２図は、圧縮機運転中における本発明の冷凍サイクル
、第３図は、圧縮機停止中における本発明の冷凍サイク
ルの説明図である。第４図は、差圧式２方弁の断面図、
第５図は、本発明を説明するモリエル線図である。
■・・・圧縮機、２・・・凝縮器、３・・・減圧器、４
・・・蒸発器、５・・・逆止弁、６・・・ストップ用電
磁弁、７・・・バランス用電磁弁、８・・・気液分離器
、９・・・差圧式２式％
１２、・・ストップ用ポール、１３・・・ダイヤフラム
、１４・・・連通管、１５・・・ガスバランス用毛細管
、１６・・・差圧引込用毛細管、１７・・・軸棒、１訃
・・板ノくネ。
第１ 図
半２ 図
！
岑４図
半５（２）
エンタＪレヒも −FIG. 1 is a block diagram of a conventional refrigeration cycle. FIG. 2 is an explanatory diagram of the refrigeration cycle of the present invention while the compressor is in operation, and FIG. 3 is an explanatory diagram of the refrigeration cycle of the present invention while the compressor is stopped. Figure 4 is a sectional view of a differential pressure type two-way valve.
FIG. 5 is a Mollier diagram illustrating the present invention. ■... Compressor, 2... Condenser, 3... Pressure reducer, 4
... Evaporator, 5... Check valve, 6... Solenoid valve for stop, 7... Solenoid valve for balance, 8... Gas-liquid separator, 9... Differential pressure type 2 sets% 12... Stop pole, 13... Diaphragm, 14... Communication tube, 15... Capillary tube for gas balance, 16... Capillary tube for drawing in differential pressure, 17... Shaft rod, 1.・Itanokune. 1st figure and a half 2 figures!岑 4 zu 5 (2) Enter J Lehi too -
Claims (1)
成される冷凍サイクルにおいて、凝縮器出口に気液分離
器を設け、前記気液分離器上部よりガスバランス用毛細
管を圧縮機と逆止弁との間に接続し、さらに、前記気液
分離器と減圧器との間に、逆止弁と圧縮機の間より導か
れる差圧引込管を接続されている差圧式２方弁を設けた
ことを特徴とする冷凍サイクル。 ２ 圧縮機をロータリー形圧縮磯としたことを特徴とす
る特許請求の範囲第１項記載の冷凍サイクル。[Claims] ] In a refrigeration cycle formed by sequentially connecting a compressor, a condenser, a pressure reducer, and a check valve, a gas-liquid separator is provided at the outlet of the condenser, and A capillary tube for gas balance is connected between the compressor and the check valve, and a differential pressure lead-in pipe led from between the check valve and the compressor is further connected between the gas-liquid separator and the pressure reducer. A refrigeration cycle characterized by being equipped with a differential pressure type two-way valve. 2. The refrigeration cycle according to claim 1, wherein the compressor is a rotary compression rock.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18020583A JPS6073260A (en) | 1983-09-30 | 1983-09-30 | Refrigeration cycle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18020583A JPS6073260A (en) | 1983-09-30 | 1983-09-30 | Refrigeration cycle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6073260A true JPS6073260A (en) | 1985-04-25 |
Family
ID=16079232
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18020583A Pending JPS6073260A (en) | 1983-09-30 | 1983-09-30 | Refrigeration cycle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6073260A (en) |
-
1983
- 1983-09-30 JP JP18020583A patent/JPS6073260A/en active Pending
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