JP3158509B2 - Refrigerant condenser - Google Patents
Refrigerant condenserInfo
- Publication number
- JP3158509B2 JP3158509B2 JP19684191A JP19684191A JP3158509B2 JP 3158509 B2 JP3158509 B2 JP 3158509B2 JP 19684191 A JP19684191 A JP 19684191A JP 19684191 A JP19684191 A JP 19684191A JP 3158509 B2 JP3158509 B2 JP 3158509B2
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- receiver tube
- tube
- heat exchange
- section
- 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 - Lifetime
Links
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
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/044—Condensers with an integrated receiver
- F25B2339/0443—Condensers with an integrated receiver the receiver being positioned horizontally
-
- 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
- F25B2600/00—Control issues
- F25B2600/19—Refrigerant outlet condenser temperature
-
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
Description
【０００１】[0001]
【産業上の利用分野】本発明は、車両用空気調和装置の
冷凍サイクルに使用される冷媒凝縮器に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant condenser used in a refrigeration cycle of an air conditioner for a vehicle.
【０００２】[0002]
【従来の技術】乗用車の空気調和装置に用いられる冷凍
サイクルでは、冷媒凝縮器の下流にレシーバを設置して
サブクール（過冷度）を０℃に保っている。しかし、冷
凍サイクルの効率（ＣＯＰ）は、過冷度をとった方が良
いことから、バス用空気調和装置では、レシーバの下流
にスーパクーラ（過冷却用の熱交換器）を設置して過冷
度を持たせている。2. Description of the Related Art In a refrigeration cycle used in an air conditioner of a passenger car, a subcool (degree of supercooling) is maintained at 0 ° C. by installing a receiver downstream of a refrigerant condenser. However, the efficiency of the refrigeration cycle (COP) is better to take the degree of subcooling, so in a bus air conditioner, a supercooler (heat exchanger for supercooling) is installed downstream of the receiver to supercool. Have a degree.
【０００３】[0003]
【発明が解決しようとする課題】上記のレシーバサイク
ルに対して、レシーバのないサイクルでは、同じ負荷を
与えた場合に、冷媒封入量の増加に伴って、モリエル線
図上のサイクルバランスが、図４の実線で示す位置か
ら、破線で示す位置、一点鎖線で示す位置へと変化し、
過冷度も増加する。In contrast to the above-described receiver cycle, in a cycle without a receiver, when the same load is applied, the cycle balance on the Mollier diagram becomes larger as the amount of charged refrigerant increases. 4 changes from the position indicated by the solid line to the position indicated by the dashed line and the position indicated by the dashed line,
The degree of supercooling also increases.
【０００４】そのときサイクル効率は、図５に示すよう
に、ある過冷度で極大値（最適過冷度と呼ぶ）を示すこ
とが分かる。これを負荷を変えて実験してみると、図６
のように負荷が高い（流量が多い）ほど、最適過冷度が
大きくなることが分かった。つまり、負荷が高い程、冷
媒封入量を多くしてやれば良い。ところが、従来のバス
用空気調和装置に使用される冷凍サイクルでは、スーパ
クーラの大きさが一定であることから、負荷の変動に対
する過冷度の変化が小さく、あまり効率的であるとは言
えない。At that time, as shown in FIG. 5, the cycle efficiency shows a maximum value at a certain degree of supercooling (referred to as an optimum degree of supercooling). When this was experimented with different loads, Fig. 6
It was found that the higher the load (the larger the flow rate), the greater the optimal degree of subcooling. In other words, the higher the load, the greater the amount of refrigerant to be charged. However, in a refrigeration cycle used in a conventional bus air conditioner, the size of the supercooler is constant, so that the change in the degree of supercooling with respect to a change in load is small, and it cannot be said that the efficiency is very efficient.
【０００５】本発明は、上記事情に基づいて成されたも
ので、その目的は、負荷に対して最もサイクル効率の高
くなる過冷度を実現することのできる冷媒凝縮器を提供
することにある。The present invention has been made based on the above circumstances, and an object of the present invention is to provide a refrigerant condenser capable of realizing a supercooling degree at which a cycle efficiency is highest with respect to a load. .
【０００６】[0006]
【課題を解決するための手段】本発明は、上記目的を達
成するために、以下の技術的手段を採用する。 （請求項１の手段）左右両側に配置される 一組のヘッダ間に複数本の冷媒チ
ューブを並設して構成され、前記冷媒チューブを流れる
冷媒を空気との熱交換によって冷却する熱交換部と、前
記ヘッダを介して前記熱交換部の途中に介在されるレシ
ーバチューブとを備え、前記熱交換部は、前記レシーバ
チューブより上流側に、高温、高圧の気相冷媒を空気と
の熱交換により凝縮液化させる凝縮部を形成し、前記レ
シーバチューブより下流側に、前記レシーバチューブか
ら流出する液冷媒を過冷却させる過冷却部を形成し、且
つ上下方向において前記凝縮部の方が前記過冷却部より
下側に形成され、前記レシーバチューブは、前記冷媒チ
ューブより通路断面積が大きく設けられた１本の直管に
よって構成され、前記凝縮部で冷却された気液二相の冷
媒を気液分離して前記過冷却部へ送ることを特徴とす
る。 （請求項２の手段）請求項１に記載した 前記レシーバチューブは、前記冷媒
チューブと共に前記一組のヘッダ間に組み込まれて、前
記熱交換部と一体的に形成されていることを特徴とす
る。（請求項３の手段） 請求項１に記載した前記レシーバチューブは、前記熱交
換部と別体に設けられ、自身の両端がそれぞれ配管によ
って前記一組のヘッダに接続されていることを特徴とす
る 。The present invention employs the following technical means to achieve the above object. (Means of Claim 1) A heat exchanging part configured by arranging a plurality of refrigerant tubes in parallel between a pair of headers arranged on both right and left sides, and cooling a refrigerant flowing through the refrigerant tubes by heat exchange with air. When, a Relais sheet <br/> Bachubu is interposed in the middle of the heat exchanger through the header, the heat exchange unit, upstream of the receiver tube, a high temperature, the gas phase refrigerant of the high pressure by heat exchange with air to form a condensation section for condensing and liquefying a downstream side of the receiver tube, the liquid refrigerant flowing from the receiver tube to form a subcooling portion for subcooling, 且
In the vertical direction, the condensing section is more
Is formed on the lower side, the receiver tube, the refrigerant Ji
One straight pipe with a larger passage cross-sectional area than the tube
The gas-liquid two-phase refrigerant cooled by the condensing unit is separated into gas and liquid and sent to the supercooling unit. According to a second aspect of the present invention, the receiver tube according to the first aspect is integrated between the pair of headers together with the refrigerant tube and is formed integrally with the heat exchange portion. . (Means of claim 3) The receiver tube according to claim 1 is provided with the heat exchanger.
It is provided separately from the exchange part, and both ends of the
Connected to the set of headers.
You .
【０００７】[0007]
【作用】上記構成より成る本発明の冷媒凝縮器は、熱交
換部の凝縮部で、高温、高圧の気相冷媒が空気との熱交
換によって冷却され、ある乾き度まで液化された気液二
相状態の冷媒としてレシーバチューブ内へ流入する。 レ
シーバチューブ内を通過する冷媒は、レシーバチューブ
の通路断面積が冷媒チューブより大きいことから、殆ど
凝縮することなく、レシーバチューブの入口と略同じ乾
き度の状態でレシーバチューブより流出し、過冷却部へ
流入する。 過冷却部では、レシーバチューブで気相冷媒
から分離された液冷媒が更に冷却（過冷却）される。 The refrigerant condenser of the present invention having the above-described structure is capable of performing heat exchange.
The high-temperature, high-pressure gas-phase refrigerant exchanges heat with air
The gas-liquid mixture cooled by exchange and liquefied to a certain dryness
It flows into the receiver tube as a refrigerant in a phase state. Les
The refrigerant passing through the receiver in the tube, the receiver tube
The cross-sectional area of the passage is larger than the refrigerant tube, so it hardly condenses and flows out of the receiver tube with almost the same dryness as the inlet of the receiver tube, and goes to the supercooling section.
Inflow. In the subcooling section, the gas phase refrigerant is
Is further cooled (supercooled).
【０００８】[0008]
【実施例】次に、本発明の冷媒凝縮器の一実施例を図１
および図２を基に説明する。図１は冷媒凝縮器の全体図
である。本実施例の冷媒凝縮器１は、レシーバを有しな
い冷凍サイクルに適用されるもので、図１に示す様に、
左右両側に配置される一組のヘッダ５、６間に複数本の
偏平チューブ２（本発明の冷媒チューブ）を並設し、各
偏平チューブ２間にコルゲートフィン３を介在させて、
各偏平チューブ２を流れる冷媒を空気との熱交換によっ
て冷却する熱交換部と、ヘッダ５、６を介して熱交換部
の途中に介在された１本のレシーバチューブ４とを備え
ている。 熱交換部は、レシーバチューブ４より上流側
に、高温、高圧の気相冷媒を空気との熱交換により凝縮
液化させる凝縮部１Ａを形成し、レシーバチューブ４よ
り下流側に、レシーバチューブ４から流出する液冷媒を
過冷却させる過冷却部１Ｂを形成し、且つ上下方向にお
いて凝縮部１Ａの方が過冷却部１Ｂより下側に形成され
ている。偏平チューブ２は、内部に冷媒通路が形成され
て、左右両側のヘッダ５、６と連通されている。FIG. 1 shows an embodiment of a refrigerant condenser according to the present invention.
This will be described with reference to FIG. FIG. 1 is an overall view of the refrigerant condenser. The refrigerant condenser 1 of the present embodiment is applied to a refrigeration cycle having no receiver, and as shown in FIG.
A plurality of headers 5 and 6 are arranged between a pair of headers 5 and 6 arranged on both right and left sides.
The flat tubes 2 (refrigerant tubes of the present invention) are arranged side by side.
With the corrugated fins 3 interposed between the flat tubes 2,
The refrigerant flowing through each flat tube 2 is exchanged for heat with air.
Heat exchange section for cooling by heat and heat exchange section via headers 5 and 6
And one receiver tube 4 interposed in the middle of
ing. The heat exchange section is upstream of the receiver tube 4
Condenses high-temperature, high-pressure gas-phase refrigerant by heat exchange with air
The condensing section 1A to be liquefied is formed, and the receiver tube 4
Liquid refrigerant flowing out of the receiver tube 4
A supercooling section 1B for supercooling is formed, and
And the condensing section 1A is formed below the supercooling section 1B.
ing. The flat tube 2 has a refrigerant passage formed therein, and communicates with the headers 5 and 6 on the left and right sides .
【０００９】ヘッダ５、６の内部には、コア部を流れる
冷媒をＵターンさせるための仕切壁７、８、９が設けら
れている。一方のヘッダ５（図１の左側）に設けられた
仕切壁７は、レシーバチューブ４とその下側に位置する
偏平チューブ２との間を仕切るように配置されている。
他方のヘッダ６に設けられた仕切壁８、９は、レシーバ
チューブ４とその上側に位置する偏平チューブ２との
間、およびヘッダ６のほぼ中間部に配置されている。ま
た、他方のヘッダ６には、その下部および上部に冷媒の
流入口１０および流出口１１が設けられている。Inside the headers 5, 6, partition walls 7, 8, 9 for making a U-turn of the refrigerant flowing through the core portion are provided. A partition wall 7 provided on one header 5 (the left side in FIG. 1) is arranged so as to partition between the receiver tube 4 and the flat tube 2 located below the receiver tube 4.
The partition walls 8 and 9 provided on the other header 6 are arranged between the receiver tube 4 and the flat tube 2 located above the receiver tube 4 and at a substantially intermediate portion of the header 6. Further, the other header 6 is provided with an inlet 10 and an outlet 11 for the refrigerant at the lower part and the upper part.
【００１０】従って、流入口１０から流入した冷媒は、
図１の実線矢印で示すように、各ヘッダでＵターンしな
がらコア部を流れた後、流出口１１より流出する。Therefore, the refrigerant flowing from the inlet 10 is
As shown by the solid arrows in FIG. 1, after flowing through the core portion while making a U-turn at each header, it flows out from the outlet 11.
【００１１】レシーバチューブ４は、全長が偏平チュー
ブ２と同一である１本の直管（真っ直ぐな管）によって
構成され、その断面積が、偏平チューブ２の通路断面積
と比較してはるかに大きく設定されている。なお、レシ
ーバチューブ４は、熱交換部への組付け性やろう付け性
等を考慮して、断面矩形状に設けられている。 The receiver tube 4 is formed by a single straight pipe (straight pipe) having the same overall length as the flat tube 2 .
Is configured, the sectional area is set much larger than the cross-sectional area of the flat tube 2. In addition, the receiver tube 4 is provided in a rectangular cross section in consideration of the ease of assembly and brazing to the heat exchange section .
【００１２】図示しない冷媒圧縮機で圧縮された高温、
高圧のガス冷媒は、流入口１０より他方のヘッダ６に流
入し、凝縮部１Ａにおいて、各偏平チューブ２を流れる
際に、送風空気によって冷却される。つまり、凝縮部１
Ａでは、他方のヘッダ６へ流入した冷媒が、仕切壁９よ
り下側の各偏平チューブ２を通って一方のヘッダ５側へ
流れ、一方のヘッダ５でＵターンした後、仕切壁７と仕
切壁９との間の各偏平チューブ２を通って再び他方のヘ
ッダ６へ流入する。High temperature compressed by a refrigerant compressor (not shown),
The high-pressure gas refrigerant flows into the other header 6 from the inflow port 10, and flows through each flat tube 2 in the condensing section 1A.
At this time, it is cooled by the blowing air. That is, the condensing unit 1
In A, the refrigerant that has flowed into the other header 6, through each of the flat tubes 2 lower than the partition wall 9 to the one of the header 5 side <br/> stream is, after a U-turn in the header 5 of the hand , And flows into the other header 6 again through each flat tube 2 between the partition wall 7 and the partition wall 9.
【００１３】この時点では、各偏平チューブ２を通過す
る際に、クーリングファン（図示しない）の送風を受け
て外気と熱交換された冷媒が、ある乾き度まで凝縮液化
されて気液二相状態となっている。この気液二相の冷媒
は、レシーバチューブ４を流れて一方のヘッダ５に流入
するが、内容積の大きなレシーバチューブ４内ではほと
んど凝縮されず、レシーバチューブ４に流入する時とほ
ぼ同じ乾き度の状態でレシーバチューブ４を流出する。At this time, when passing through each flat tube 2, the refrigerant exchanged with the outside air by the air blown by the cooling fan (not shown) is condensed and liquefied to a certain degree of dryness and is in a gas-liquid two-phase state. It has become. The gas-liquid two-phase refrigerant flows through the receiver tube 4 and flows into one of the headers 5, but is hardly condensed in the receiver tube 4 having a large internal volume, and has almost the same dryness as when flowing into the receiver tube 4. Flows out of the receiver tube 4 in the state described above.
【００１４】その後、過冷却部１Ｂにおいて、各偏平チ
ューブ２を流れる際に、送風空気によって更に冷却され
る。つまり、過冷却部１Ｂでは、レシーバチューブ４か
ら一方のヘッダ５へ流入した冷媒が、一方のヘッダ５で
Ｕターンし、仕切壁８より上側の各偏平チューブ２を通
過して他方のヘッダ６へ流入した後、流出口１１より流
出する。ここで、各偏平チューブ２を通過する冷媒が完
全に液化され、さらに過冷却されて、過冷度を有した状
態で冷媒凝縮器を流出する。Thereafter, in the subcooling section 1B, each flat chip
When flowing through the tube 2, it is further cooled by the blast air.
You. That is, in the subcooling unit 1B, the receiver tube 4
The refrigerant that has flowed into one of the headers 5 makes a U-turn at one header 5, passes through the flat tubes 2 above the partition wall 8, flows into the other header 6, and then flows out of the outlet 11. Here, the refrigerant passing through each flat tube 2 is completely liquefied, further subcooled, and flows out of the refrigerant condenser in a state of having a subcooling degree.
【００１５】上記の作動において、レシーバチューブ４
に流入する気液二相の冷媒は、その冷媒流量が少ない時
には、重力の作用によってレシーバチューブ４の入口か
らすぐに上下方向に完全分離してレシーバチューブ４内
を流れることになる。このとき、気相冷媒の方が液相冷
媒より速く流れるため、レシーバチューブ４内には、液
冷媒が溜まりやすくなる。In the above operation, the receiver tube 4
When the flow rate of the refrigerant is small, the gas-liquid two-phase refrigerant flowing into the receiver tube 4 immediately and completely separates vertically from the inlet of the receiver tube 4 by the action of gravity and flows through the receiver tube 4. At this time, since the gas-phase refrigerant flows faster than the liquid-phase refrigerant, the liquid refrigerant tends to accumulate in the receiver tube 4.
【００１６】また、冷媒流量が多い時には、レシーバチ
ューブ４の入口からすぐに気液分離することなく、しば
らくは気相と液相とが混合した二相状態で流れる。この
ため、気相冷媒と液相冷媒とが等速で流れることから、
レシーバチューブ４内には、あまり液冷媒が溜まらな
い。Further, when the flow rate of the refrigerant is large, the gas flows from the inlet of the receiver tube 4 in a two-phase state in which a gas phase and a liquid phase are mixed for a while without being immediately gas-liquid separated. Because the gaseous refrigerant and the liquid refrigerant flow at a constant speed,
The liquid refrigerant does not accumulate much in the receiver tube 4.
【００１７】このレシーバチューブ４の作用により、他
のサイクル部品内の冷媒量は、高流量の時に多く、低流
量の時に少なくなる。つまり、負荷の高い時には、図２
に示すように、レシーバチューブ４内に液冷媒が少ない
分だけ、レシーバチューブ４より上流の凝縮部１Ａおよ
び下流の過冷却部１Ｂを流れる冷媒量が増えて、過冷度
が増加する。また、負荷が低い時には、レシーバチュー
ブ４内に液冷媒が多い分だけ、逆に過冷度は減少する。
なお、図２において、高負荷の状態を実線で示し、低負
荷の状態を破線で示す。Due to the operation of the receiver tube 4, the amount of refrigerant in the other cycle components is large when the flow rate is high and small when the flow rate is low. That is, when the load is high, FIG.
As shown in (2), the amount of the refrigerant flowing in the condensing portion 1A upstream of the receiver tube 4 and the subcooling portion 1B downstream of the receiver tube 4 increases by the amount of the liquid refrigerant in the receiver tube 4, and the degree of subcooling increases. On the other hand, when the load is low, the degree of supercooling is reduced by the amount of the liquid refrigerant in the receiver tube 4.
In FIG. 2, the state of high load is indicated by a solid line, and the state of low load is indicated by a broken line.
【００１８】このように、本実施例の冷媒凝縮器１で
は、負荷の変動に応じてレシーバチューブ４より下流の
過冷却域を流れる冷媒量が変化することにより、負荷に
対して最もサイクル効率の高くなる過冷度を実現するこ
とが可能となる。As described above, in the refrigerant condenser 1 of the present embodiment, the amount of the refrigerant flowing in the subcooling area downstream of the receiver tube 4 changes in accordance with the fluctuation of the load. It becomes possible to realize a high degree of supercooling.
【００１９】次に、本発明の第２実施例を説明する。図
３は、レシーバチューブ４を別体とした冷媒凝縮器１の
全体図である。この実施例は、レシーバチューブ４を凝
縮器本体１ａ（凝縮部１Ａ及び過冷却部１Ｂ）と別体に
設けた一例であり、レシーバチューブ４の両端がそれぞ
れ配管（図示しない）によって一組のヘッダに接続され
ている。従って、凝縮器本体１ａとレシーバチューブ４
とを配管で接続するために、レシーバチューブ４の両端
部と、一方のヘッダ５の仕切壁７より上部位置および他
方のヘッダ６の仕切壁８と仕切壁８との間には、それぞ
れ配管接続口１２、１３、１４、１５が設けられてい
る。なお、図３中に冷媒の流れを実線矢印で示す。本実
施例の場合には、レシーバチューブ４が別体であること
から、第１実施例のように組付け性やろう付け性を考慮
する必要がなく、従って、その形状の制約はない。Next, a second embodiment of the present invention will be described. FIG. 3 is an overall view of the refrigerant condenser 1 having the receiver tube 4 as a separate body. This embodiment is an example in which the receiver tube 4 is provided separately from the condenser main body 1a (condensing section 1A and supercooling section 1B), and both ends of the receiver tube 4 are respectively provided.
Connected to a set of headers by piping (not shown)
ing. Therefore, the condenser body 1a and the receiver tube 4
Are connected by pipes between the both ends of the receiver tube 4, the position above the partition wall 7 of one header 5 and between the partition walls 8 of the other header 6. Ports 12, 13, 14, 15 are provided. Note that the flow of the refrigerant is indicated by solid arrows in FIG. In the case of this embodiment, since the receiver tube 4 is a separate body, it is not necessary to consider the assembling property and brazing property as in the first embodiment, and therefore, there is no restriction on its shape.
【００２０】[0020]
【発明の効果】本発明では、冷媒通路の途中に内容積の
大きなチューブを設置したことにより、負荷の変動に応
じて過冷度をとるために費やされる冷媒凝縮器の面積を
可変することができる。その結果、負荷に対して最もサ
イクル効率の高くなる過冷度を実現することができる。According to the present invention, by installing a tube having a large internal volume in the middle of the refrigerant passage, it is possible to vary the area of the refrigerant condenser used for obtaining the degree of supercooling in accordance with the fluctuation of the load. it can. As a result, it is possible to realize a degree of supercooling with the highest cycle efficiency for the load.
【図１】冷媒凝縮器の全体図である。FIG. 1 is an overall view of a refrigerant condenser.
【図２】冷媒凝縮器内の冷媒量の変化を示す図である。FIG. 2 is a diagram illustrating a change in a refrigerant amount in a refrigerant condenser.
【図３】本発明の第２実施例を示す冷媒凝縮器の全体図
である。FIG. 3 is an overall view of a refrigerant condenser showing a second embodiment of the present invention.
【図４】冷媒封入量が変化した時のサイクルバランスを
モリエル線図上に示した図である。FIG. 4 is a diagram showing a cycle balance on a Mollier diagram when the amount of charged refrigerant changes.
【図５】過冷度とサイクル効率との関係を示すグラフで
ある。FIG. 5 is a graph showing the relationship between the degree of subcooling and cycle efficiency.
【図６】冷媒流量と最適過冷度との関係を示すグラフで
ある。FIG. 6 is a graph showing a relationship between a refrigerant flow rate and an optimal degree of subcooling.
１ 冷媒凝縮器１Ａ 凝縮部 １Ｂ 過冷却部 ２ 偏平チューブ（冷媒チューブ） ４ レシーバチューブ５ ヘッダ ６ ヘッダ DESCRIPTION OF SYMBOLS 1 Refrigerant condenser 1A Condensing part 1B Supercooling part 2 Flat tube ( refrigerant tube ) 4 Receiver tube 5 Header 6 Header
───────────────────────────────────────────────────── フロントページの続き (72)発明者 大原 敏夫 愛知県刈谷市昭和町１丁目１番地 日本 電装株式会社内 (56)参考文献 特開 平３−95368（ＪＰ，Ａ) 特開 昭55−134253（ＪＰ，Ａ) 実公 昭47−42049（ＪＰ，Ｙ１) (58)調査した分野(Int.Cl.7，ＤＢ名) F25B 39/04 ──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Toshio Ohara 1-1-1, Showa-cho, Kariya-shi, Aichi Japan Inside Denso Co., Ltd. (56) References JP-A-3-95368 (JP, A) JP-A-55- 134253 (JP, A) Jikken 47-42049 (JP, Y1) (58) Fields investigated (Int. Cl. 7 , DB name) F25B 39/04
Claims (3)
数本の冷媒チューブを並設して構成され、前記冷媒チュ
ーブを流れる冷媒を空気との熱交換によって冷却する熱
交換部と、 前記ヘッダを介して前記熱交換部の途中に介在されるレ
シーバチューブとを備え、 前記熱交換部は、前記レシーバチューブより上流側に、
高温、高圧の気相冷媒を空気との熱交換により凝縮液化
させる凝縮部を形成し、前記レシーバチューブより下流
側に、前記レシーバチューブから流出する液冷媒を過冷
却させる過冷却部を形成し、且つ上下方向において前記
凝縮部の方が前記過冷却部より下側に形成され、 前記レシーバチューブは、前記冷媒チューブより通路断
面積が大きく設けられた１本の直管によって構成され、
前記凝縮部で冷却された気液二相の冷媒を気液分離して
前記過冷却部へ送ることを特徴とする冷媒凝縮器。1. A heat exchange section comprising a plurality of refrigerant tubes arranged side by side between a pair of headers arranged on both left and right sides, and cooling a refrigerant flowing through the refrigerant tubes by heat exchange with air. a Relais <br/> receiver tube interposed in the middle of the heat exchanger through the header, the heat exchange unit, upstream of the receiver tube,
Forming a condensing section for condensing and liquefying the high-temperature, high-pressure gas-phase refrigerant by heat exchange with air, and forming a subcooling section for subcooling the liquid refrigerant flowing out of the receiver tube downstream of the receiver tube; And in the vertical direction
The condensing section is formed below the supercooling section, and the receiver tube has a passage cut off from the refrigerant tube.
It is composed of one straight pipe with a large area,
A refrigerant condenser, wherein the gas-liquid two-phase refrigerant cooled in the condenser is separated into gas and liquid and sent to the supercooler.
ブと共に前記一組のヘッダ間に組み込まれて、前記熱交
換部と一体的に形成されていることを特徴とする請求項
１記載の冷媒凝縮器。2. A refrigerant condenser according to claim 1, wherein said receiver tube is incorporated between said pair of headers together with said refrigerant tube, and is formed integrally with said heat exchange part. .
別体に設けられ、自身の両端がそれぞれ配管によって前Separately provided, both ends of which are fronted by pipes
記一組のヘッダに接続されていることを特徴とする請求Claims characterized by being connected to the set of headers
項１記載の冷媒凝縮器。Item 7. A refrigerant condenser according to Item 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19684191A JP3158509B2 (en) | 1991-08-06 | 1991-08-06 | Refrigerant condenser |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19684191A JP3158509B2 (en) | 1991-08-06 | 1991-08-06 | Refrigerant condenser |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0539969A JPH0539969A (en) | 1993-02-19 |
| JP3158509B2 true JP3158509B2 (en) | 2001-04-23 |
Family
ID=16364555
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19684191A Expired - Lifetime JP3158509B2 (en) | 1991-08-06 | 1991-08-06 | Refrigerant condenser |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3158509B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11304293A (en) * | 1997-07-10 | 1999-11-05 | Denso Corp | Refrigerant condenser |
| DE10018478A1 (en) * | 2000-04-14 | 2001-10-18 | Behr Gmbh & Co | Condenser for an air conditioning system, in particular for an air conditioning system of a motor vehicle |
| JP2002031436A (en) * | 2000-05-09 | 2002-01-31 | Sanden Corp | Sub-cooling type condenser |
| JP5664063B2 (en) * | 2010-09-21 | 2015-02-04 | 株式会社デンソー | Condenser |
| KR101674030B1 (en) * | 2010-09-27 | 2016-11-09 | 한온시스템 주식회사 | Condenser |
| JP6139093B2 (en) * | 2012-10-23 | 2017-05-31 | シャープ株式会社 | Parallel flow heat exchanger |
-
1991
- 1991-08-06 JP JP19684191A patent/JP3158509B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0539969A (en) | 1993-02-19 |
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