JPS63161360A - Refrigeration cycle - Google Patents
Refrigeration cycleInfo
- Publication number
- JPS63161360A JPS63161360A JP30607086A JP30607086A JPS63161360A JP S63161360 A JPS63161360 A JP S63161360A JP 30607086 A JP30607086 A JP 30607086A JP 30607086 A JP30607086 A JP 30607086A JP S63161360 A JPS63161360 A JP S63161360A
- Authority
- JP
- Japan
- Prior art keywords
- condenser
- refrigerant
- gas
- heat transfer
- 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.)
- Pending
Links
- 238000005057 refrigeration Methods 0.000 title claims description 6
- 239000003507 refrigerant Substances 0.000 claims description 42
- 239000007788 liquid Substances 0.000 claims description 18
- 239000003638 chemical reducing agent Substances 0.000 claims description 2
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 238000000926 separation method Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Landscapes
- Fats And Perfumes (AREA)
- Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
- Saccharide Compounds (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】
〔産業上の利用分野〕
この発明は非共沸混合冷媒を用いた冷媒サイクルに関す
るものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a refrigerant cycle using a non-azeotropic mixed refrigerant.
特開昭５８−１３３５６８号によると、非共沸混合冷媒
を用いることにより、同一凝縮圧力の状態で二凝縮温度
が得られるようにした冷凍サイクルが示されている。す
なわち、この冷媒サイクルにおいては、圧縮機、第１の
凝縮器、気液分離器、第２の凝縮器、減圧器および蒸発
器を順次接続してなり、第１の凝縮器にて上記混合冷媒
の一部を凝縮し、気液分離器で残りのガス冷媒を抽出し
、それを第２の凝縮器にて凝縮するようにしている。JP-A-58-133568 discloses a refrigeration cycle in which two condensing temperatures can be obtained at the same condensing pressure by using a non-azeotropic mixed refrigerant. That is, in this refrigerant cycle, a compressor, a first condenser, a gas-liquid separator, a second condenser, a pressure reducer, and an evaporator are connected in sequence, and the mixed refrigerant is mixed in the first condenser. A part of the refrigerant is condensed, the remaining gas refrigerant is extracted with a gas-liquid separator, and it is condensed with a second condenser.
上記した冷媒サイクルによると、第１の凝縮器には圧縮
器から吐出される冷媒の全流量が流れ、他方、第２の凝
縮器には気液分離後のガス冷媒が流されることになるが
、従来では第１および第２の凝縮器はともに同一管径の
伝熱管を用いているため、二凝縮温度が得られるにして
も総合効率が悪いという問題があった。According to the refrigerant cycle described above, the entire flow rate of the refrigerant discharged from the compressor flows through the first condenser, while the gas refrigerant after gas-liquid separation flows through the second condenser. Conventionally, the first and second condensers both use heat exchanger tubes of the same diameter, so even if two condensing temperatures can be obtained, the overall efficiency is poor.
すなわち、この種の冷媒サイクルの総合効率は冷媒循環
量と冷媒速度とに依存する。一般に管径が細い場合には
流体速度が速くなって熱伝導率が大きくなるとともに液
溜りが少なくなり、したがって、熱通過率が大きく熱交
換上好ましい反面、圧力損失が増大し冷媒サイクルの総
合効率を悪くするという面を併せもつことになる。他方
、管径が太い場合には圧力損失は比較的低く抑えられる
が、熱交換器内の冷媒量が増大するとともに、特に出口
側の流体速度の遅い部分で液溜りが発生するため、これ
がコンプレッサを制約し、その小形軽量化の妨げとなり
、また、熱通過率も悪くなる。That is, the overall efficiency of this type of refrigerant cycle depends on the amount of refrigerant circulation and the refrigerant velocity. In general, when the pipe diameter is small, the fluid velocity increases, the thermal conductivity increases, and the amount of liquid pools decreases. Therefore, the heat passage rate is high and it is favorable for heat exchange, but on the other hand, the pressure loss increases and the overall efficiency of the refrigerant cycle increases. It also has the aspect of making things worse. On the other hand, if the pipe diameter is large, the pressure loss can be kept relatively low, but the amount of refrigerant in the heat exchanger increases and a pool of liquid occurs, especially at the outlet side where the fluid velocity is low. This restricts the size and weight of the product, and also impairs its heat transfer rate.
この発明は上記した事情に鑑みなされたもので、その目
的は、総合効率がよく、しかも凝縮器をより一層薄形化
し得るようにした非共沸混合冷媒による冷媒サイクルを
提供することにある。This invention was made in view of the above circumstances, and its purpose is to provide a refrigerant cycle using a non-azeotropic mixed refrigerant that has good overall efficiency and allows the condenser to be made even thinner.
上記した目的を達成するため、この発明においては、気
液分離後のガス冷媒が通される第２の凝縮器の伝熱管を
第１の凝縮器の伝熱管よりも小径のチューブとしている
。In order to achieve the above object, in the present invention, the heat transfer tube of the second condenser through which the gas refrigerant after gas-liquid separation passes is made smaller in diameter than the heat transfer tube of the first condenser.
上記した構成によれば、第１および第２の凝縮器ともに
その冷媒循環量と冷媒速度との関係が個別的に適正範囲
内におさめられるため、最適な総合効率がひき出される
。According to the above configuration, the relationship between the refrigerant circulation amount and the refrigerant speed of both the first and second condensers is individually kept within an appropriate range, so that the optimum overall efficiency can be achieved.
以下、この発明の実施例を添付図面を参照しながら詳細
に説明する。Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
まず第１図を参照してこの冷媒サイクルの構成を概略的
に説明する。First, the configuration of this refrigerant cycle will be schematically explained with reference to FIG.
同図において１は圧縮機であり、この圧縮機１からは過
熱ガス状態の非共沸混合冷媒が吐出される。この混合冷
媒は第１の凝縮器２ａにおいてその一部が液化されたの
ち気液分離器３に至る。この気液分離器３内において液
冷媒とガス冷媒とが分離され、ガス冷媒は第２の凝縮器
２ｂにて凝縮されて液冷媒となり、この液冷媒は先に気
液分離器３で分離された液冷媒とともにキャピラリーチ
ューブ４および蒸発器５を経て圧縮機１に戻される。In the figure, 1 is a compressor, and a non-azeotropic mixed refrigerant in a superheated gas state is discharged from the compressor 1. This mixed refrigerant is partially liquefied in the first condenser 2a and then reaches the gas-liquid separator 3. A liquid refrigerant and a gas refrigerant are separated in this gas-liquid separator 3, and the gas refrigerant is condensed into a liquid refrigerant in the second condenser 2b, and this liquid refrigerant is first separated in the gas-liquid separator 3. The liquid refrigerant is returned to the compressor 1 through the capillary tube 4 and the evaporator 5 together with the liquid refrigerant.
上記の如く、第２の凝縮器に流される冷媒は気液分離後
のガス冷媒であるため、その流量は当然のことながら第
１の凝縮器内に流される流量よりも少ない、そこでこの
発明においては、その冷媒流量に応じて第２の凝縮器２
ｂの伝熱管６を第１の凝縮器２ａの伝熱管７よりも細く
している。また、この両伝熱管６，７はともに同一のフ
ィン群８に挿通されていて、これにより第１および第２
の凝縮器２ａ、２ｂは外観上一つの凝縮器２を構成して
いる。As mentioned above, since the refrigerant flowing into the second condenser is a gas refrigerant after gas-liquid separation, its flow rate is naturally lower than the flow rate flowing into the first condenser. Therefore, in this invention, is the second condenser 2 depending on the refrigerant flow rate.
The heat exchanger tube 6 of b is made thinner than the heat exchanger tube 7 of the first condenser 2a. Further, both of the heat exchanger tubes 6 and 7 are inserted through the same fin group 8, so that the first and second
The condensers 2a and 2b constitute one condenser 2 in appearance.
上記した実施例の説明から明らかなように、この発明に
よれば、第１の凝縮器２ａの伝熱管７に比べて第２の凝
縮器２ｂの伝熱管６をその冷媒流量に応じて細管とした
ことにより、各凝縮器２ａ。As is clear from the description of the embodiments described above, according to the present invention, the heat transfer tubes 6 of the second condenser 2b are made into thin tubes depending on the refrigerant flow rate, compared to the heat transfer tubes 7 of the first condenser 2a. As a result, each condenser 2a.
２ｂにおける冷媒流量と冷媒速度の関係を個別的に調整
することができるため、冷媒サイクル全体の総合効率を
より一層高めることができる。また。Since the relationship between the refrigerant flow rate and the refrigerant speed in 2b can be adjusted individually, the overall efficiency of the entire refrigerant cycle can be further improved. Also.
第１および第２の凝縮器２ａ、２ｂのフィン群を共通に
して一体化したことにより、薄形化および製造コストの
低減が図れる。さらには、第２の凝縮器２ｂ側の伝熱管
６を小径にしたことより、凝縮器２自体の通風抵抗が減
少する。この効果はフィン群８を通れる空気の流動方向
からみて細い方の伝熱管６をその上流側、太い方の伝熱
管７を下流側に配置した場合により顕著であって、これ
により送風機能力および騒音対策上有利である。Since the fin groups of the first and second condensers 2a and 2b are shared and integrated, it is possible to reduce the thickness and manufacturing cost. Furthermore, by making the heat transfer tube 6 on the second condenser 2b side smaller in diameter, the ventilation resistance of the condenser 2 itself is reduced. This effect is more noticeable when the thinner heat transfer tube 6 is placed upstream and the thicker heat transfer tube 7 is placed downstream when viewed from the flow direction of the air passing through the fin group 8. This is advantageous in terms of countermeasures.
第１図はこの発明にしたがって構成された冷媒サイクル
の模式図、第２図は同冷媒サイクルの凝縮器を摘示した
斜視図である。
図中、１は圧縮機、２は凝縮器、２ａは第１の凝縮器、
２ｂは第２の凝縮器、３は気液分離器、４はキャピラリ
ーチューブ、５は蒸発器、６，７は伝熱管、８はフィン
群である。FIG. 1 is a schematic diagram of a refrigerant cycle constructed according to the present invention, and FIG. 2 is a perspective view showing a condenser of the refrigerant cycle. In the figure, 1 is a compressor, 2 is a condenser, 2a is a first condenser,
2b is a second condenser, 3 is a gas-liquid separator, 4 is a capillary tube, 5 is an evaporator, 6 and 7 are heat exchanger tubes, and 8 is a fin group.
Claims (3)
縮器、減圧器および蒸発器を順次接続してなり、上記第
１の凝縮器にて非共沸混合冷媒の一部を凝縮し、上記気
液分離器で残りのガス冷媒を抽出してこれを上記第２の
凝縮器にて凝縮するようにした冷凍サイクルにおいて、 上記第２の凝縮器には、上記第１の凝縮器の伝熱管より
も小径の伝熱管が用いられていることを特徴とする冷凍
サイクル。(1) A compressor, a first condenser, a gas-liquid separator, a second condenser, a pressure reducer, and an evaporator are connected in sequence, and one of the non-azeotropic mixed refrigerants is removed in the first condenser. In the refrigeration cycle, the remaining gas refrigerant is extracted by the gas-liquid separator and condensed by the second condenser, wherein the second condenser includes the first gas refrigerant. A refrigeration cycle characterized in that a heat transfer tube having a smaller diameter than that of the condenser is used.
び第２の凝縮器の各伝熱管は同一のフィン群に挿通され
ていることを特徴とする冷凍サイクル。(2) The refrigeration cycle according to claim (1), wherein each heat transfer tube of the first and second condensers is inserted through the same fin group.
を通過する気流方向を基準として上記第１の凝縮器側の
太い伝熱管はその下流側に配置され、他方、上記第２の
凝縮器側の細い伝熱管はその上流側に配置されることを
特徴とする冷凍サイクル。(3) In claim (2), the thick heat transfer tube on the first condenser side is arranged on the downstream side with respect to the direction of airflow passing through the fin group; A refrigeration cycle characterized in that the narrow side heat transfer tube is placed on the upstream side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30607086A JPS63161360A (en) | 1986-12-22 | 1986-12-22 | Refrigeration cycle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP30607086A JPS63161360A (en) | 1986-12-22 | 1986-12-22 | Refrigeration cycle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63161360A true JPS63161360A (en) | 1988-07-05 |
Family
ID=17952682
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP30607086A Pending JPS63161360A (en) | 1986-12-22 | 1986-12-22 | Refrigeration cycle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63161360A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10339511A (en) * | 1997-06-09 | 1998-12-22 | Yoriyuki Oguri | Heat pump system of air conditioner |
| JP2000193328A (en) * | 1998-12-25 | 2000-07-14 | Mitsubishi Electric Corp | Freezer |
| JP2002079821A (en) * | 2000-07-06 | 2002-03-19 | Denso Corp | Vehicular refrigerating cycle device |
| JP2009300021A (en) * | 2008-06-16 | 2009-12-24 | Mitsubishi Electric Corp | Refrigerating cycle device |
-
1986
- 1986-12-22 JP JP30607086A patent/JPS63161360A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10339511A (en) * | 1997-06-09 | 1998-12-22 | Yoriyuki Oguri | Heat pump system of air conditioner |
| JP4208982B2 (en) * | 1997-06-09 | 2009-01-14 | グリーンアース株式会社 | Heat pump air conditioner |
| JP2000193328A (en) * | 1998-12-25 | 2000-07-14 | Mitsubishi Electric Corp | Freezer |
| JP2002079821A (en) * | 2000-07-06 | 2002-03-19 | Denso Corp | Vehicular refrigerating cycle device |
| JP2009300021A (en) * | 2008-06-16 | 2009-12-24 | Mitsubishi Electric Corp | Refrigerating cycle device |
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