JPS58198653A - Refrigeration cycle - Google Patents
Refrigeration cycleInfo
- Publication number
- JPS58198653A JPS58198653A JP8155582A JP8155582A JPS58198653A JP S58198653 A JPS58198653 A JP S58198653A JP 8155582 A JP8155582 A JP 8155582A JP 8155582 A JP8155582 A JP 8155582A JP S58198653 A JPS58198653 A JP S58198653A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- refrigeration cycle
- evaporator
- refrigerant circuit
- condenser
- 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
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】
本発明は、車両用空調装置の冷凍サイクルの改良に関す
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a refrigeration cycle for a vehicle air conditioner.
第１図は、従来の車両用空調装置の略示的説明図である
が、同図において、１は走行用エンジン、２は圧縮機、
６は動力伝達ベルト、４は凝縮器、５は膨張弁、６は冷
媒配管、１１は蒸発器、１２は冷却弁ファンをそれぞれ
示し、圧縮機２はｆＬ行用エンジン１の駆動力を動力伝
達ベルト６を介して伝達されて駆動されるようになって
おり、該圧縮機２により圧縮された冷媒は、凝縮器４で
冷却液化され、膨張弁５にて低圧に絞られ、蒸発器１１
内で、該低圧液冷媒が蒸発して気化することＫより、冷
却が行なわれ、再び圧縮機２に吸入されるようになって
いる。そして上記各機器を図示の如（冷媒配管６で接続
して冷凍サーイクルを形成していて、冷却用ファン１２
にて車室内空気を蒸発器１１と熱交換させて冷却するも
のである。この場合の冷媒はＲ−１２を使用している。FIG. 1 is a schematic explanatory diagram of a conventional vehicle air conditioner, in which 1 is a driving engine, 2 is a compressor,
6 is a power transmission belt, 4 is a condenser, 5 is an expansion valve, 6 is a refrigerant pipe, 11 is an evaporator, 12 is a cooling valve fan, and the compressor 2 transmits the driving force of the engine 1 for the fL line. The refrigerant is transmitted and driven via a belt 6, and the refrigerant compressed by the compressor 2 is cooled and liquefied in a condenser 4, throttled to low pressure by an expansion valve 5, and then transferred to an evaporator 11.
The low-pressure liquid refrigerant is evaporated and vaporized within the refrigerant, thereby being cooled and sucked into the compressor 2 again. As shown in the figure, each of the above devices is connected with a refrigerant pipe 6 to form a refrigeration cycle, and a cooling fan 12
The air inside the vehicle is cooled by exchanging heat with the evaporator 11. The refrigerant used in this case is R-12.
上記冷凍サイクル中の冷媒として、冷媒Ｒ−１２よりも
蒸発潜熱の大きい冷媒Ｒ−２２を使用すれば、蒸発器１
１のコンパクト化を図ることができ、車室内の必要スに
一スの減少を図ることができるが、上記従来の冷凍サイ
クルでは、冷媒Ｒ−２２を使用するには、現状技術レベ
ルでは、不可能であるという問題点がある。If refrigerant R-22, which has a larger latent heat of vaporization than refrigerant R-12, is used as the refrigerant in the refrigeration cycle, the evaporator 1
However, in the conventional refrigeration cycle described above, it is difficult to use refrigerant R-22 at the current technological level. The problem is that it is possible.
本発明は、上記従来の冷凍サイクルの問題点を解決する
ことを目的として提案されたもので、圧縮機、凝縮器、
膨張弁及び満液式蒸発器で一次側冷媒回路を構成すると
ともに、上記満液式蒸発器内に内蔵された凝縮器、液ポ
°ンプ及び蒸発器で二次冷媒回路を構成したことを特徴
とする冷凍サイクルに係るものである。The present invention was proposed with the aim of solving the problems of the conventional refrigeration cycle described above, and includes a compressor, a condenser,
A primary refrigerant circuit is configured with an expansion valve and a flooded evaporator, and a secondary refrigerant circuit is configured with a condenser, a liquid pump, and an evaporator built into the flooded evaporator. This relates to a refrigeration cycle.
また、本発明は、上記第１項記載の冷凍サイクルにおい
て、二次側冷媒回路に一次側冷媒回路に充填された冷媒
の蒸発潜熱よりも大きな蒸発潜熱をもつ冷媒を充填して
なることを特徴とする冷凍サイクルに係るものである。Furthermore, the present invention is characterized in that, in the refrigeration cycle described in item 1 above, the secondary refrigerant circuit is filled with a refrigerant having a latent heat of evaporation larger than the latent heat of evaporation of the refrigerant filled in the primary refrigerant circuit. This relates to a refrigeration cycle.
以下、第２図に示す実施例により、本発明につき具体的
に説明する。同図において、１は走行用エンジン、２は
圧縮機、６は動力伝達ベルト、４は凝縮機、５は膨張弁
、２０は満液式蒸発器で、それら部材は一次側冷媒配管
６で接続されて、−次側冷媒回路を形成している。２０
ａは上記満液式蒸発器２０内に配設された二次側凝縮器
、１４は蒸発器で、それら二次側凝縮器２０ａと蒸発器
１４とは車室外に設置された液ボ／プ１０を介装された
二次側冷媒配管１３で接続されて二次側冷媒回路を形成
している。The present invention will be specifically explained below with reference to an embodiment shown in FIG. In the figure, 1 is a driving engine, 2 is a compressor, 6 is a power transmission belt, 4 is a condenser, 5 is an expansion valve, and 20 is a flooded evaporator, and these components are connected by a primary refrigerant pipe 6. and forms a downstream refrigerant circuit. 20
14 is an evaporator, and the secondary condenser 20a and the evaporator 14 are connected to a liquid tank installed outside the passenger compartment. 10 are connected by a secondary refrigerant pipe 13 interposed therebetween to form a secondary refrigerant circuit.
本発明の冷凍サイクルは、上記構成の一次側冷媒回路と
、二次側冷媒回路とを具備することを特徴とするもので
ある。The refrigeration cycle of the present invention is characterized by comprising a primary refrigerant circuit and a secondary refrigerant circuit configured as described above.
本発明の冷凍サイクルの運転を開始すると、第１図に示
す従来の冷凍サイクルの走行エンジン直結の圧縮機から
直膨式蒸発器へ冷媒を流す方式に比べて、本発明では満
液式蒸発器に液冷媒を流す方式であるため、車室内負荷
の変動及び圧縮機の回転数の変化に対して、直接冷媒の
状態変化が少なく、安定した冷媒ガスを圧縮機に吸込ま
せることができ、従って圧縮機の寿命及び装置の信頼性
、耐久性が向上する利点がある。When the refrigeration cycle of the present invention starts operating, compared to the conventional refrigeration cycle system shown in FIG. 1 in which the refrigerant flows from the compressor directly connected to the running engine to the direct expansion evaporator, the present invention uses a flooded evaporator. This method allows liquid refrigerant to flow through the compressor, so there is little direct change in the state of the refrigerant in response to changes in the load inside the vehicle or changes in the rotation speed of the compressor, allowing stable refrigerant gas to be sucked into the compressor. This has the advantage of improving the life of the compressor and the reliability and durability of the device.
また、車室内の負荷に対して圧縮機の回転数の変動に無
関係に、液ポンプで冷媒を負荷側に供給できるため、負
荷への応答性は迅速であり、安定した性能が保たれる利
点がある。In addition, because the liquid pump can supply refrigerant to the load side regardless of fluctuations in the compressor rotational speed relative to the load inside the vehicle, the response to the load is quick and stable performance is maintained. There is.
また、本発明は、二次側冷媒回路の冷媒を、−次側冷媒
回路の冷媒の蒸発潜熱より大きな蒸発潜熱をもつものを
用いた点を特徴とするものであるが、具体的には、−次
側冷媒回路においては、冷媒Ｒ−１２で冷凍サイクルを
作動させ、二次側冷媒回路においては、冷媒Ｒ−１２よ
°り蒸発潜熱が大きい冷媒Ｒ−２２で冷凍サイクルを作
動させるようになっている。Furthermore, the present invention is characterized in that the refrigerant in the secondary refrigerant circuit has a latent heat of vaporization larger than that of the refrigerant in the secondary refrigerant circuit, and specifically, - In the downstream refrigerant circuit, the refrigeration cycle is operated with refrigerant R-12, and in the secondary refrigerant circuit, the refrigeration cycle is operated with refrigerant R-22, which has a larger latent heat of vaporization than refrigerant R-12. It has become.
本発明の冷凍サイクルの一実施例は、上記のように構成
されており、走行用エンジン１により動力伝達用ばルト
６を介して駆動される圧縮機２により圧縮された冷媒ガ
スＲ−１２は、凝縮器４で冷却液化され、さらに膨張弁
５により低圧に絞られた液冷媒は、満液式蒸発器２０内
に貯えられる。One embodiment of the refrigeration cycle of the present invention is configured as described above, and the refrigerant gas R-12 compressed by the compressor 2 driven by the driving engine 1 via the power transmission bolt 6 is The liquid refrigerant that has been cooled and liquefied in the condenser 4 and further throttled to low pressure by the expansion valve 5 is stored in the flooded evaporator 20 .
該満液式蒸発器２０内には二次側凝縮器２０ａが内蔵さ
れており、上記のようにして満液式蒸発器２０内に貯え
られた液冷媒Ｒ−１２は、二次側凝縮器２０ａと熱交換
して蒸発して気化され、該気化された冷媒ガスは一次側
冷媒配管６を経て再び圧縮器２に吸入される。一方、二
次側冷媒回路の二次側凝縮器で冷却された液冷媒Ｒ−２
２を、液ポンプ１０にて蒸発器１４に供給する。そして
蒸発器１４と車室内空気とを冷却器用ファ／１５て熱交
換させることにより、蒸発器１４内部で冷媒Ｒ−２２を
蒸発させて該蒸発器１４を冷却する。A secondary condenser 20a is built in the flooded evaporator 20, and the liquid refrigerant R-12 stored in the flooded evaporator 20 as described above is transferred to the secondary condenser 20a. The refrigerant gas exchanges heat with the refrigerant 20a and is vaporized, and the vaporized refrigerant gas is sucked into the compressor 2 again through the primary refrigerant pipe 6. On the other hand, liquid refrigerant R-2 cooled in the secondary condenser of the secondary refrigerant circuit
2 is supplied to the evaporator 14 by the liquid pump 10. By exchanging heat between the evaporator 14 and the air inside the vehicle through the cooler fan 15, the refrigerant R-22 is evaporated inside the evaporator 14, thereby cooling the evaporator 14.
その際気化した冷媒Ｒ−２２は、二次側冷媒配管１３を
通って再び二次側凝縮器２０αに入り、満液式蒸発器２
０内の冷媒Ｒ−１２により冷却されて液化する。ここで
−次側冷媒回路は冷媒Ｒ−１２で冷凍サイクルを形成し
、また、二次側冷媒回路は冷媒Ｒ−２２で独立した冷凍
サイクルを形成する。すなわち、二次側冷凍サイクルに
おいては、ヒートパイプとして作動し、冷媒Ｒ−２２は
蒸発器１４から得た熱量を、二次側凝縮器２０ａへ運ぶ
役割を果している。At that time, the vaporized refrigerant R-22 passes through the secondary refrigerant pipe 13 and enters the secondary condenser 20α again, and then enters the flooded evaporator 2
It is cooled by the refrigerant R-12 in 0 and liquefied. Here, the secondary refrigerant circuit forms a refrigeration cycle with refrigerant R-12, and the secondary refrigerant circuit forms an independent refrigeration cycle with refrigerant R-22. That is, in the secondary side refrigeration cycle, the refrigerant R-22 operates as a heat pipe, and plays the role of carrying the amount of heat obtained from the evaporator 14 to the secondary side condenser 20a.
本発明の一実施例は、上記のように構成されており、二
次側冷媒回路の冷媒Ｒ−２２の蒸発潜熱（Ｅｔ＝５℃テ
４８．１ Ｋｃａｌ、Ａｇ ）が、−次（ＩＩＩ 冷媒
回路の冷媒Ｒ−１２の蒸発潜熱（Ｅｔ二５℃で６５６Ｋ
ｃａｌＡｇ）よりも大きいので、同一負荷条件で蒸発器
を設計する場合は、冷媒Ｒ−２２の蒸発器の方が、冷媒
Ｒ−１２のものよりも小さな蒸発器（熱交換器）で足り
る訳である。従って本発明によれば、上記従来の冷凍サ
イクルの蒸発器１１よりも、蒸発器１４の小型化を図る
ことができ、省ス投−ス化を図ることができ乙。An embodiment of the present invention is configured as described above, and the latent heat of vaporization (Et=48.1 Kcal, Ag at 5°C) of the refrigerant R-22 in the secondary refrigerant circuit is -th(III refrigerant) The latent heat of vaporization of the refrigerant R-12 in the circuit (Et2 656K at 5℃)
calAg), so when designing an evaporator under the same load conditions, a smaller evaporator (heat exchanger) for refrigerant R-22 is required than for refrigerant R-12. be. Therefore, according to the present invention, the evaporator 14 can be made smaller than the evaporator 11 of the conventional refrigeration cycle, and the cost and investment can be saved.
本発明は上記のような構成、作用を具有するものである
から、本発明によれば、車両内空調装置の車内側処納ス
は−スを減少できるという実用的効果を挙げることがで
きる。Since the present invention has the above-mentioned structure and operation, the present invention has the practical effect of reducing the amount of space inside the vehicle of the vehicle air conditioner.
第１図は従来の冷凍サイクルの、略示的説明図、第２図
は本発明の一実施例の概略説明図である。
１：走行用エンジン、 ２：圧縮機、
６：動力伝達用（ルト、４：凝縮器、
５：膨張弁（絞り）、 ６：−次側冷媒配管、１０：液
ポンプ、 １３：二次側冷媒配管、１４：蒸発器
（熱交換器）、１５：冷却用ファン、２０：満液式蒸発
器、 ２０σ：二次側凝縮器。FIG. 1 is a schematic explanatory diagram of a conventional refrigeration cycle, and FIG. 2 is a schematic explanatory diagram of an embodiment of the present invention. 1: Traveling engine, 2: Compressor, 6: Power transmission (rut, 4: Condenser, 5: Expansion valve (throttle), 6: Next side refrigerant piping, 10: Liquid pump, 13: Secondary side Refrigerant piping, 14: evaporator (heat exchanger), 15: cooling fan, 20: flooded evaporator, 20σ: secondary side condenser.
Claims (2)
側冷媒回路を構成するとともに、上記満液式蒸発器内に
内蔵された凝縮器、液ポ゛ンプ及び蒸発器で二次冷媒回
路を構成したことを特徴とする冷凍サイクル。(1) The compressor, condenser, expansion valve, and flooded evaporator constitute the primary refrigerant circuit, and the condenser, liquid pump, and evaporator built into the flooded evaporator constitute the secondary refrigerant circuit. A refrigeration cycle characterized by comprising a secondary refrigerant circuit.
冷媒回路に一次側冷媒回路に充填された冷媒の蒸発潜熱
よりも大きな蒸発潜熱をもつ冷媒を充填してなることを
特徴とする冷凍サイクル。(2) In the refrigeration cycle described in item 1 above, the secondary refrigerant circuit is filled with a refrigerant having a latent heat of evaporation greater than the latent heat of evaporation of the refrigerant filled in the primary refrigerant circuit. cycle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8155582A JPS58198653A (en) | 1982-05-17 | 1982-05-17 | Refrigeration cycle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8155582A JPS58198653A (en) | 1982-05-17 | 1982-05-17 | Refrigeration cycle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS58198653A true JPS58198653A (en) | 1983-11-18 |
Family
ID=13749528
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8155582A Pending JPS58198653A (en) | 1982-05-17 | 1982-05-17 | Refrigeration cycle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58198653A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62238951A (en) * | 1986-04-09 | 1987-10-19 | 松下冷機株式会社 | Air conditioner |
| WO2003095906A1 (en) * | 2002-05-13 | 2003-11-20 | Mayekawa Mfg.Co.,Ltd. | Thermo siphon chiller refrigerator for use in cold district |
-
1982
- 1982-05-17 JP JP8155582A patent/JPS58198653A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62238951A (en) * | 1986-04-09 | 1987-10-19 | 松下冷機株式会社 | Air conditioner |
| JP2529202B2 (en) * | 1986-04-09 | 1996-08-28 | 松下冷機株式会社 | Air conditioner |
| WO2003095906A1 (en) * | 2002-05-13 | 2003-11-20 | Mayekawa Mfg.Co.,Ltd. | Thermo siphon chiller refrigerator for use in cold district |
| US7293425B2 (en) | 2002-05-13 | 2007-11-13 | Mayekawa Mfg. Co., Ltd. | Thermo siphon chiller refrigerator for use in cold district |
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