JPH0461262B2 - - Google Patents
Info
- Publication number
- JPH0461262B2 JPH0461262B2 JP19114582A JP19114582A JPH0461262B2 JP H0461262 B2 JPH0461262 B2 JP H0461262B2 JP 19114582 A JP19114582 A JP 19114582A JP 19114582 A JP19114582 A JP 19114582A JP H0461262 B2 JPH0461262 B2 JP H0461262B2
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- refrigerant passage
- liquid
- condenser
- liquid receiver
- 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
Links
- 239000003507 refrigerant Substances 0.000 claims description 79
- 239000007788 liquid Substances 0.000 claims description 38
- 239000007791 liquid phase Substances 0.000 claims description 15
- 238000005057 refrigeration Methods 0.000 claims description 11
- 239000012071 phase Substances 0.000 description 9
- 238000000034 method Methods 0.000 description 6
- 230000005494 condensation Effects 0.000 description 5
- 238000009833 condensation Methods 0.000 description 5
- 239000013526 supercooled liquid Substances 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 238000004781 supercooling Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 239000011555 saturated liquid Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 239000012808 vapor phase Substances 0.000 description 1
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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
Landscapes
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Description
【発明の詳細な説明】
本発明は冷凍装置の減圧装置入口において適度
に過冷却された液冷媒が得られるように凝縮器を
改良することにより、冷凍能力の向上をはかつた
冷凍装置に関するもので、例えば自動車空調用に
用いて好適である。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a refrigeration system that improves its refrigerating capacity by improving the condenser so that a suitably supercooled liquid refrigerant can be obtained at the inlet of the decompression device of the refrigeration system. Therefore, it is suitable for use in, for example, automobile air conditioning.
冷凍装置の冷凍能力を向上させる方法として、
従来より知られている一方法は、冷凍装置の減圧
装置である膨張弁入口において冷媒に過冷却度を
持たせることにより、蒸発器における冷媒の蒸発
前後のエンタルピ差をより大きくする方法があ
る。しかし、従来この方法を実施するには、受液
器の下流に更に別の凝縮器を設け、受液器から出
てくる液冷媒を再度冷却し、過冷却冷媒を得てい
た。従つて、この方法によれば、凝縮器の数が必
然的に多くなり、従つて高価なものとなるほか、
自動車用空調装置などにおいてはその設置場所に
も困難が伴うという欠点をもつている。 As a method to improve the refrigeration capacity of refrigeration equipment,
One conventionally known method is to increase the enthalpy difference before and after evaporation of the refrigerant in the evaporator by giving the refrigerant a degree of supercooling at the inlet of the expansion valve, which is a pressure reducing device of the refrigeration system. However, conventionally, in order to carry out this method, another condenser was provided downstream of the liquid receiver, and the liquid refrigerant coming out of the liquid receiver was cooled again to obtain supercooled refrigerant. Therefore, according to this method, the number of condensers is inevitably large, which makes it expensive.
Air conditioners for automobiles have the disadvantage of being difficult to locate.
本発明は上述した先行技術の欠点を克服して、
従来と同等の凝縮器を一個使用するだけで膨張弁
入口において過冷却された冷媒が得られる冷凍装
置を提供することを目的としている。 The present invention overcomes the drawbacks of the prior art mentioned above and
It is an object of the present invention to provide a refrigeration system that can obtain supercooled refrigerant at the inlet of an expansion valve by using only one condenser similar to the conventional one.
本発明の端緒となつたのは、近年自動車空調装
置において、冷媒通路を２分割し、並列に冷媒を
流す凝縮器が現れて来たことである。すなわち、
冷房に必要な動力を低減させるため、あるいは冷
房能力を向上させるために、凝縮器は大型化しそ
れに伴つて冷媒側圧力損失も増大した。この圧力
損失を減少させるために前記冷媒通路を２分割し
並列に通すことが考えられたのである。本発明は
後述するように、このような複数本の並列な冷媒
通路管を有する凝縮器を備えた冷凍装置を対象と
している。このことは複数本の並列な冷媒通路管
を有することが、本発明の過冷却冷媒を得るのに
役立つているだけではなく、上述の冷媒側圧力損
失を減少させることにも役立つており、本発明の
欠点には全くなつていないことを意味している。 The invention began in recent years with the appearance of condensers in automobile air conditioners that divide a refrigerant passage into two and allow refrigerant to flow in parallel. That is,
In order to reduce the power required for cooling or to improve cooling capacity, condensers have become larger and the pressure loss on the refrigerant side has also increased accordingly. In order to reduce this pressure loss, it was considered to divide the refrigerant passage into two and run them in parallel. As will be described later, the present invention is directed to a refrigeration system equipped with a condenser having a plurality of such parallel refrigerant passage pipes. This means that having a plurality of parallel refrigerant passage pipes not only helps in obtaining the supercooled refrigerant of the present invention, but also helps in reducing the above-mentioned pressure loss on the refrigerant side. This means that the drawbacks of the invention have not been addressed at all.
本発明の要点は、冷凍装置の凝縮器において、
複数本の並列な冷媒通路管を設け、各通路管の長
さを互いに適当な程度異ならせることにより、凝
縮器下流に設けられている受液器内に、適度に過
冷却された液冷媒を得ることにある。通常の１本
の冷媒通路管を使用した凝縮器と受液器との組合
せにおいては、受液器内には気液両相の冷媒が飽
和ガスおよび飽和液として存在している。従つて
受液器から膨張弁へと送られる液冷媒は過冷却状
態にあることはほとんどなく、その過冷却度は通
常２℃〜３℃以下である。一方、このような状態
にある受液器内の液相領域に、数十度の過冷却度
をもつ液冷媒を注入したとすると、当然受液器内
において、気液両相の冷媒間に熱交換が始まる
が、熱交換は気液境界面においてのみ行われるの
で熱的平衡に達するには時間を要し、普通の使用
状態においては、過冷却状態の液冷媒がそのまま
受液器から膨張弁へと送られることになる。上述
した過冷却液媒を得る方法として、凝縮器内にさ
らに冷媒通路管を追加し、その長さを他の通路管
に比して長くし、この長さの長い冷媒通路管を受
液器下部の液相部もしくは受液器の出口配管に接
続することが本発明の要点である。 The gist of the present invention is that in a condenser of a refrigeration system,
By providing a plurality of parallel refrigerant passage pipes and making the length of each passage pipe differ by an appropriate degree, it is possible to supply appropriately supercooled liquid refrigerant into the liquid receiver installed downstream of the condenser. It's about getting. In a conventional combination of a condenser and a liquid receiver using one refrigerant passage pipe, refrigerant in both gas and liquid phases exists in the liquid receiver as a saturated gas and a saturated liquid. Therefore, the liquid refrigerant sent from the liquid receiver to the expansion valve is rarely in a supercooled state, and the degree of supercooling is usually 2°C to 3°C or less. On the other hand, if a liquid refrigerant with a degree of supercooling of several tens of degrees is injected into the liquid phase region in the liquid receiver in such a state, naturally there will be a gap between the gas and liquid phase refrigerant in the receiver. Heat exchange begins, but since heat exchange occurs only at the gas-liquid interface, it takes time to reach thermal equilibrium. Under normal usage conditions, the supercooled liquid refrigerant expands from the liquid receiver as it is. It will be sent to the valve. As a method for obtaining the above-mentioned supercooled liquid medium, an additional refrigerant passage pipe is added to the condenser, the length of the refrigerant passage pipe is made longer than other passage pipes, and this long refrigerant passage pipe is used as a liquid receiver. The key point of the present invention is to connect it to the lower liquid phase section or the outlet pipe of the liquid receiver.
以下図面を参照しつつ本発明の実施例を説明す
る。第１図において、蒸発器５において気化した
冷媒は、圧縮機１に送られ、圧縮されて、高温高
圧の状態となり、さらに配管６を通り凝縮器２に
送られる。送られてきた気相冷媒は凝縮器２によ
り冷却され液化して配管９ａ，９ｂを通り受液器
３に貯蔵され、受液器３内の液相冷媒は減圧装置
をなす膨張弁４を通り膨張し、低温低圧の気液２
相状態の冷媒となつて蒸発器５に送られる。蒸発
器５において気化して冷房作用を行つた気相冷媒
は再び圧縮機１に送られこの循環行程を繰返す。
自動車用空調装置では蒸発器５で冷却された冷風
を車室内へ吹出して冷房作用を行うようにしてお
り、また圧縮機１は電磁クラツチ１ａを介して自
動車エンジンにより駆動される。 Embodiments of the present invention will be described below with reference to the drawings. In FIG. 1, the refrigerant vaporized in the evaporator 5 is sent to the compressor 1, compressed to a high temperature and high pressure state, and then sent to the condenser 2 through a pipe 6. The sent gas phase refrigerant is cooled and liquefied by the condenser 2, passes through pipes 9a and 9b, and is stored in the liquid receiver 3, and the liquid phase refrigerant in the liquid receiver 3 passes through the expansion valve 4, which forms a pressure reducing device. Expanding, low-temperature, low-pressure gas-liquid 2
The refrigerant becomes a phase refrigerant and is sent to the evaporator 5. The gas phase refrigerant that has been vaporized in the evaporator 5 to perform a cooling action is sent to the compressor 1 again and this circulation process is repeated.
In the automobile air conditioner, cold air cooled by an evaporator 5 is blown into the vehicle interior to effect cooling, and the compressor 1 is driven by the automobile engine via an electromagnetic clutch 1a.
次に、本発明の要部をなす凝縮器２に関して詳
しく説明する。 Next, the condenser 2, which forms the main part of the present invention, will be explained in detail.
第２図において、圧縮機１より来た配管６は分
岐部２ｃにおいて分岐し、延べ長さが短い方の冷
媒通路管より成る小凝縮器部２ａと、延べ長さが
長い方の冷媒通路管より成る大凝縮器部２ｂとに
分れ、小凝縮器２ａは配管９ａにより受液器３の
上部の入口配管３ａに接続されている。また、大
凝縮器部２ｂは受液器３の下部の液相部に接続さ
れている。上記２個の凝縮器部２ａ，２ｂの冷媒
通路管は凝縮器内を蛇行して往復し、本実施例に
おいては、平行して走る直線部分を、小凝縮器部
２ａは５本、大凝縮器部２ｂは７本有している。
冷媒通路管はアルミニウム材料でつくられ、偏平
な断面形状をもつている。また、平行に走る冷媒
通路管の間には同じくアルミニウム材料でつくら
れた多数のコルゲートフイン２ｄが介在し、冷媒
通路管にろう付されている。受液器３には出口配
管１０が接続されていて、受液器３内の液相冷媒
だけを膨張弁４に送るようになつている。なお、
１１は配管接続部である。 In FIG. 2, the pipe 6 coming from the compressor 1 branches at a branching part 2c, and a small condenser part 2a consisting of a refrigerant passage pipe with a shorter total length and a refrigerant passage pipe with a longer total length are formed. The small condenser 2a is connected to the upper inlet pipe 3a of the liquid receiver 3 through a pipe 9a. Further, the large condenser section 2b is connected to the lower liquid phase section of the liquid receiver 3. The refrigerant passage pipes of the two condenser sections 2a and 2b reciprocate in a meandering manner within the condenser, and in this embodiment, the straight section running parallel to the small condenser section 2a has five refrigerant passage pipes, and the large condenser section has five refrigerant passage pipes. The vessel part 2b has seven pieces.
The refrigerant passage pipe is made of aluminum material and has a flat cross-sectional shape. Further, a large number of corrugated fins 2d also made of aluminum are interposed between the refrigerant passage pipes running in parallel and are brazed to the refrigerant passage pipes. An outlet pipe 10 is connected to the liquid receiver 3 so that only the liquid phase refrigerant in the liquid receiver 3 is sent to the expansion valve 4. In addition,
11 is a piping connection part.
第３図により冷媒の気液相の推移状態を説明す
る。点で示す部分イが気相、破線で示す部分ロが
液相である。先づ小凝縮器部２ａについて見る
と、受液器３からは液相冷媒だけが膨張弁４へ送
られるので、気相冷媒が受液器３に連続して流入
して来ることは不可能である。従つて、小凝縮器
部２ａの出口において冷媒はほぼ凝縮を完了した
状態となつている。つぎに大凝縮器部２ｂについ
て見ると、その出口において少なくとも冷媒がほ
ぼ凝縮を完了していなければならぬことは小凝縮
器部２ａの場合と同じである。しかしながら両凝
縮器部２ａ，２ｂの各々を通れる冷媒流量を検討
すると、大凝縮器部２ｂにおいて凝縮完了の位置
が更に限定されることが判る。すなわち、各凝縮
器部２ａ，２ｂを流れる冷媒流量の割合は、各凝
縮器部２ａ，２ｂにおける冷媒圧力損失の大きさ
の比に依存し、冷媒圧力損失は主に気相域で大き
く凝縮するに従い小さくなり、液相域ではその値
はほとんど無視できる程度になる。いま、仮り
に、大凝縮器部２ｂにおいても小凝縮器部２ａと
同じく、丁度その出口において凝縮を完了すると
すると、大凝縮器部２ｂにおいては管長が長いだ
け、気相域も長く、冷媒圧力損失は大となり、し
たがつて大凝縮器部２ｂを流れる冷媒は、小凝縮
器部２ａを流れる冷媒より少なくなる。一方、凝
縮を完了する地点は、気相冷媒流量と、伝熱面の
断面長さに関係する。従つて、大凝縮器部２ｂを
流れる流量が小凝縮器部２ａを流れる流量より少
なければ、凝縮を完了するまでの気相域の長さは
より短かくなり上述の仮定と矛盾してくる。かく
て冷媒の流れは、両凝縮器部２ａ，２ｂを流れる
流量が相等しく、かつ両凝縮器部中の気相域の長
さが相等しくなつている状態で平衡を保つことが
理解されよう。この状態を示したのが第３図であ
る。図において大凝縮器部２ｂの（ｙ−ｘ）の部
分においても放熱が行われるためその出口におい
て過冷却冷媒が得られるのである。しかも、この
大凝縮器部２ｂで過冷却された液冷媒を配管９ｂ
によつて受液器３下部の液相部に直接混入するよ
うにしているから、この過冷却液冷媒を気相冷媒
との間で熱交換させることなく膨張弁４側に供給
できる。 The transition state of the gas-liquid phase of the refrigerant will be explained with reference to FIG. Part A indicated by a dot is the gas phase, and part B indicated by a broken line is the liquid phase. First, looking at the small condenser section 2a, only liquid phase refrigerant is sent from the liquid receiver 3 to the expansion valve 4, so it is impossible for vapor phase refrigerant to continuously flow into the liquid receiver 3. It is. Therefore, the refrigerant is almost completely condensed at the outlet of the small condenser section 2a. Next, regarding the large condenser section 2b, it is the same as the case of the small condenser section 2a that at least the refrigerant must have almost completely condensed at its outlet. However, when considering the flow rate of refrigerant that can pass through each of the two condenser sections 2a and 2b, it is found that the position at which condensation is completed in the large condenser section 2b is further limited. That is, the ratio of the refrigerant flow rate flowing through each condenser section 2a, 2b depends on the ratio of the magnitude of refrigerant pressure loss in each condenser section 2a, 2b, and the refrigerant pressure loss is largely condensed mainly in the gas phase region. In the liquid phase region, its value becomes almost negligible. Now, if we assume that condensation in the large condenser section 2b is completed at the outlet just like in the small condenser section 2a, the pipe length in the large condenser section 2b is longer, the gas phase region is also longer, and the refrigerant pressure is lower. The loss becomes large, and therefore the refrigerant flowing through the large condenser section 2b is less than the refrigerant flowing through the small condenser section 2a. On the other hand, the point at which condensation is completed is related to the flow rate of the gas phase refrigerant and the cross-sectional length of the heat transfer surface. Therefore, if the flow rate flowing through the large condenser section 2b is smaller than the flow rate flowing through the small condenser section 2a, the length of the gas phase region until condensation is completed becomes shorter, which contradicts the above assumption. It will be understood that the flow of the refrigerant is thus maintained in equilibrium in a state where the flow rates through both condensers 2a and 2b are equal and the lengths of the gas phase regions in both condensers are equal. . FIG. 3 shows this state. In the figure, since heat is also radiated in the section (y-x) of the large condenser section 2b, supercooled refrigerant is obtained at its outlet. Moreover, the liquid refrigerant supercooled in the large condenser section 2b is transferred to the pipe 9b.
Since the subcooled liquid refrigerant is directly mixed into the liquid phase portion at the lower part of the liquid receiver 3, the supercooled liquid refrigerant can be supplied to the expansion valve 4 side without heat exchange with the gaseous refrigerant.
本発明の効果は、実験によつて確認されてお
り、その結果を第４図に定量的に示している。実
験は両凝縮器部２ａ，２ｂの冷媒通路管の合計延
べ長さ（ｘ＋ｙ）を一定に保ち、すなわち凝縮器
部の放熱面積を一定にしその比ｙ／ｘだけを変化
させて、各々対応する冷凍能力Ｑと、ｘ＝ｙの場
合の能力Q1との比を示したものである。図から
判るように約ｙ／ｘ＝1.5において冷凍能力比
Ｑ／Q1は最大となり、約1.7を越すと、基準値よ
り低くなつている。これはｙ／ｘを余り大きくと
ると、小凝縮器部２ａの冷媒通路管の延べ長さが
短かくなり、ｘ＝ｙの場合に比して充分な伝熱面
積が得られず凝縮圧力が上昇することに起因する
ものと思われる。第４図において、SCは膨張弁
入口部における冷媒の過冷却度を示す。 The effects of the present invention have been confirmed through experiments, and the results are quantitatively shown in FIG. The experiment was conducted by keeping the total length (x+y) of the refrigerant passage pipes of both condensers 2a and 2b constant, that is, by keeping the heat dissipation area of the condensers constant and changing only the ratio y/x. It shows the ratio between the refrigerating capacity Q and the capacity Q1 when x=y. As can be seen from the figure, the refrigerating capacity ratio Q/Q 1 reaches its maximum at approximately y/x = 1.5, and becomes lower than the standard value when it exceeds approximately 1.7. This is because if y/x is too large, the total length of the refrigerant passage pipe in the small condenser section 2a will be shortened, and a sufficient heat transfer area will not be obtained compared to the case where x = y, and the condensation pressure will increase. This seems to be due to the increase in In FIG. 4, SC indicates the degree of supercooling of the refrigerant at the inlet of the expansion valve.
なお、上述の実施例では、大凝縮器部２ｂの出
口を配管９ｂにより受液器３下部の液相部に接続
しているが、配管９ｂにより受液器３の出口配管
１０に接続してもよいことは勿論である。 In the above-described embodiment, the outlet of the large condenser section 2b is connected to the liquid phase section at the lower part of the liquid receiver 3 by the pipe 9b, but it is connected to the outlet pipe 10 of the liquid receiver 3 by the pipe 9b. Of course, this is a good thing.
以上延べたように、本発明は延べ長さを異にす
る複数本の並列な冷媒通路管を凝縮器に設け、延
べ長さの短い冷媒通路管を従来通り受液器の入口
部に接続するとともに、延べ長さの長い冷媒通路
管を受液器下部の液相部もしくは受液器の出口配
管に接続しているから、凝縮器における冷媒圧力
損失の低減できるのみならず、膨張弁等の減圧装
置に供給する冷媒に適度な過冷却度を持たせるこ
とが可能となり、冷凍能力を向上できるという効
果が大である。 As described above, the present invention provides a condenser with a plurality of parallel refrigerant passage pipes with different total lengths, and connects the refrigerant passage pipes with short total lengths to the inlet of a receiver as in the conventional manner. In addition, since the long refrigerant passage pipe is connected to the liquid phase section at the bottom of the liquid receiver or the outlet pipe of the liquid receiver, it is possible to not only reduce the refrigerant pressure loss in the condenser, but also to reduce the pressure loss of the expansion valve, etc. It is possible to give the refrigerant supplied to the pressure reducing device an appropriate degree of subcooling, which has a great effect of improving the refrigerating capacity.
しかも、本発明の構成によれば、従来と同等の
大きさの凝縮器を１個使用するだけでよく、安価
であり、取付スペース等の点でも有利であるとい
う効果がある。 Moreover, according to the configuration of the present invention, it is only necessary to use one condenser of the same size as the conventional one, which is advantageous in that it is inexpensive and advantageous in terms of installation space and the like.
第１図は本発明の１実施例を示す冷凍装置サイ
クル図、第２図は第１図の凝縮器と受液器部分を
示す部分断面図、第３図は第２図の冷媒の気液状
態を示す模式図、第４図は２本の冷媒通路管の長
さの比に対応して変化する冷凍能力向上率を示す
特性図である。
図において、１……圧縮機、２……凝縮器、３
……受液器、４……膨張弁、５……蒸発器、２ａ
……小凝縮器部、２ｂ……大凝縮器部、ｘ……小
凝縮器部の冷媒通路管の延べ長さ、ｙ……大凝縮
器部の冷媒通路管の延べ長さ。
Fig. 1 is a refrigeration system cycle diagram showing one embodiment of the present invention, Fig. 2 is a partial sectional view showing the condenser and liquid receiver portions of Fig. 1, and Fig. 3 is a gas-liquid refrigerant of Fig. 2. FIG. 4, which is a schematic diagram showing the state, is a characteristic diagram showing the refrigerating capacity improvement rate that changes depending on the ratio of the lengths of the two refrigerant passage pipes. In the figure, 1... Compressor, 2... Condenser, 3
...Liquid receiver, 4...Expansion valve, 5...Evaporator, 2a
... Small condenser section, 2b... Large condenser section, x... Total length of the refrigerant passage pipe of the small condenser section, y... Total length of the refrigerant passage pipe of the large condenser section.
Claims (1)
この冷媒通路管の各々が繰返し往復する形状に形
成された凝縮器と、この凝縮器の下流に設けられ
た受液器とを有する冷凍装置において、 前記複数本の冷媒通路管の延べ長さを異なら
せ、延べ長さが大きい冷媒通路管の延べ長さを、
延べ長さが小さい冷媒通路管の延べ長さに比して
1.7倍以下とし、 更に前記延べ長さの小さい冷媒通路管の出口を
前記受液器の入口に接続するとともに、前記延べ
長さの大きい冷媒通路管を前記受液器下部の液相
部もしくは前記受液器の出口配管に接続したこと
を特徴とする冷凍装置。[Claims] 1. Having a plurality of functionally parallel refrigerant passage pipes,
In a refrigeration system having a condenser formed in a shape in which each of the refrigerant passage pipes reciprocates repeatedly, and a liquid receiver provided downstream of the condenser, the total length of the plurality of refrigerant passage pipes is The total length of the refrigerant passage pipe is different, and the total length of the refrigerant passage pipe is large.
The total length is small compared to the total length of the refrigerant passage pipe.
1.7 times or less, and furthermore, the outlet of the refrigerant passage pipe with the short total length is connected to the inlet of the liquid receiver, and the refrigerant passage pipe with the large total length is connected to the liquid phase part of the lower part of the liquid receiver or the above-mentioned liquid receiver. A refrigeration device characterized by being connected to the outlet piping of a liquid receiver.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19114582A JPS5981453A (en) | 1982-10-29 | 1982-10-29 | Refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19114582A JPS5981453A (en) | 1982-10-29 | 1982-10-29 | Refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5981453A JPS5981453A (en) | 1984-05-11 |
| JPH0461262B2 true JPH0461262B2 (en) | 1992-09-30 |
Family
ID=16269636
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19114582A Granted JPS5981453A (en) | 1982-10-29 | 1982-10-29 | Refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5981453A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH062970A (en) * | 1992-06-22 | 1994-01-11 | Nippondenso Co Ltd | Air conditioner for vehicle |
| WO2001061263A1 (en) * | 2000-02-15 | 2001-08-23 | Zexel Valeo Climate Control Corporation | Heat exchanger |
| JP4845711B2 (en) * | 2006-12-20 | 2011-12-28 | マルヤス工業株式会社 | Heat exchanger |
| JP5726485B2 (en) * | 2010-11-12 | 2015-06-03 | エスペック株式会社 | Temperature control device and constant temperature and humidity device |
-
1982
- 1982-10-29 JP JP19114582A patent/JPS5981453A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5981453A (en) | 1984-05-11 |
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