JPH0510633A - Condenser - Google Patents
CondenserInfo
- Publication number
- JPH0510633A JPH0510633A JP16446491A JP16446491A JPH0510633A JP H0510633 A JPH0510633 A JP H0510633A JP 16446491 A JP16446491 A JP 16446491A JP 16446491 A JP16446491 A JP 16446491A JP H0510633 A JPH0510633 A JP H0510633A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- condenser
- tube
- liquid
- refrigerant passage
- 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
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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、カーエアコン等に用い
られる凝縮器に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a condenser used for car air conditioners and the like.
【０００２】[0002]
【従来の技術】カーエアコン用の凝縮器として、例えば
実開平２−３８０５５号公報に示されるように、凝縮器
と受液器とを一体化した凝縮器が知られている。このも
のは、凝縮器の冷媒出口での過冷却度が常に零に制御さ
れている。2. Description of the Related Art As a condenser for a car air conditioner, there is known a condenser in which a condenser and a liquid receiver are integrated, as disclosed in Japanese Utility Model Laid-Open No. 38055/1990. In this case, the degree of supercooling at the refrigerant outlet of the condenser is always controlled to zero.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、このよ
うな従来の凝縮器によると、エンジンルーム内からの熱
等により凝縮器の冷媒出口に接続される配管途中で液冷
媒が加熱され、液冷媒中に気泡が発生し、この気泡が膨
張弁に入ると冷凍サイクルが不安定になり、十分な冷凍
能力が得られないだけでなく騒音をも発生するという問
題がある。However, according to such a conventional condenser, the liquid refrigerant is heated in the middle of the pipe connected to the refrigerant outlet of the condenser due to heat from the inside of the engine room and the like. When air bubbles are generated in the expansion valve and the air bubbles enter the expansion valve, the refrigeration cycle becomes unstable, which causes a problem that not only a sufficient refrigeration capacity is not obtained but also noise is generated.
【０００４】本発明は、このような問題点を解決するた
めになされたもので、凝縮器中で冷媒を過冷却すること
で冷凍能力および成績係数を向上し、安定した冷凍サイ
クルを形成可能な凝縮器を提供することを目的とする。The present invention has been made in order to solve such a problem, and it is possible to improve the refrigerating capacity and the coefficient of performance by supercooling the refrigerant in the condenser and to form a stable refrigerating cycle. The purpose is to provide a condenser.
【０００５】[0005]
【課題を解決するための手段】前記目的を達成するため
の本発明の第１発明による凝縮器は、冷媒通路を構成す
る冷媒通路管と、この冷媒通路管に接合されたフィンと
を備え、前記冷媒通路管内を流通する冷媒流を前記フィ
ンを介して放熱させることにより凝縮する凝縮器であっ
て、前記冷媒通路の途中に、前記冷媒通路の通路面積よ
り大きい通路面積を有するとともに、この冷媒通路を上
下二段の室に仕切りかつ上側の室と下側の室を連通する
穴をもつ仕切板を設けたレシーバチューブと、前記レシ
ーバチューブ内で前記下側の室に分離された冷媒流をさ
らに過冷却するように、冷媒通路を構成する冷媒通路管
と、この冷媒通路管に接合されたフィンとからなる補コ
ンデンサ部とを備えたことを特徴とする。A condenser according to a first aspect of the present invention for achieving the above object comprises a refrigerant passage pipe constituting a refrigerant passage, and a fin joined to the refrigerant passage pipe. A condenser that condenses by radiating heat through a flow of a refrigerant flowing through the refrigerant passage tube, the refrigerant passage having a passage area larger than the passage area of the refrigerant passage in the middle of the refrigerant passage, and the refrigerant. A receiver tube provided with a partition plate that divides the passage into upper and lower chambers and has a hole that communicates the upper chamber and the lower chamber, and the refrigerant flow separated into the lower chamber in the receiver tube. Further, it is characterized in that it is provided with a refrigerant passage pipe forming a refrigerant passage and an auxiliary condenser portion including fins joined to the refrigerant passage pipe so as to be supercooled.
【０００６】本発明の第１発明による凝縮器は、前記穴
が仕切板の中央部より冷媒流の下流側に形成されること
を特徴とする。The condenser according to the first aspect of the present invention is characterized in that the hole is formed downstream of the center of the partition plate in the refrigerant flow.
【０００７】[0007]
【作用】本発明の凝縮器によると、レシーバチューブで
冷媒を気液二相に分離するレシーバ機能をもつだけでな
く、補コンデンサ部で液冷媒を過冷却するサブクーラ機
能をもつため、冷凍能力ならびに成績係数ともに向上さ
せられる。According to the condenser of the present invention, not only has the receiver function of separating the refrigerant into gas-liquid two phases by the receiver tube, but also has the subcooler function of subcooling the liquid refrigerant in the auxiliary condenser section. Both the coefficient of performance can be improved.
【０００８】[0008]
【実施例】以下、本発明の実施例を図面にもとづいて説
明する。冷凍サイクルを構成する冷媒回路は、図２に示
すように、圧縮機１と凝縮器２と膨張弁３とエバポレー
タ４からなる。このうち凝縮器２は、積層型コンデンサ
で、凝縮機能と受液器の機能と過冷却の機能とを有す
る。Embodiments of the present invention will be described below with reference to the drawings. As shown in FIG. 2, the refrigerant circuit that constitutes the refrigeration cycle includes a compressor 1, a condenser 2, an expansion valve 3 and an evaporator 4. Of these, the condenser 2 is a laminated condenser and has a condensing function, a liquid receiver function, and a supercooling function.
【０００９】凝縮器２は、その構造が図１に示されるよ
うに、主コンデンサ部６と、気液分離部７と、補コンデ
ンサ部８とからなる。主コンデンサ部６は、ヘッダ型に
構成されており、冷媒チューブ１０ａと放熱用フィン１
２ａを交互に積層したコア部１３と、このコア部１３の
左右両側に連結されるヘッダ部１５、１７とからなる。
冷媒チューブ１０ａは、例えば単管扁平チューブまたは
内部を複数個の通路に区画した多孔扁平チューブにより
形成されており、放熱用フィン１２ａはプレートフィン
あるいはコルゲートフィンにより形成されている。放熱
用フィン１２ａは冷媒チューブ１０ａの側面にろう付け
あるいはハンダ付け等により接合される。またヘッダ部
１５には冷媒入口パイプ１６が接続され、ヘッダ部１５
の内部に仕切壁１４を設ける。ヘッダ部１７の内部には
仕切壁１８を設ける。As shown in FIG. 1, the condenser 2 comprises a main condenser portion 6, a gas-liquid separation portion 7, and an auxiliary condenser portion 8. The main condenser portion 6 is configured as a header type, and includes the refrigerant tube 10a and the heat radiation fin 1
The core portion 13 is formed by alternately laminating 2a, and the header portions 15 and 17 connected to both left and right sides of the core portion 13.
The refrigerant tube 10a is formed of, for example, a single tube flat tube or a porous flat tube whose inside is divided into a plurality of passages, and the heat radiation fins 12a are formed of plate fins or corrugated fins. The heat radiation fin 12a is joined to the side surface of the refrigerant tube 10a by brazing, soldering or the like. Further, the refrigerant inlet pipe 16 is connected to the header portion 15, and the header portion 15
A partition wall 14 is provided inside. A partition wall 18 is provided inside the header portion 17.
【００１０】気液分離部７は、主コンデンサ部６の冷媒
チューブ１０ａよりも径の大きい矩形型チューブよりな
るレシーバチューブ２６から構成され、主コンデンサ部
６からの冷媒を補コンデンサ部８へ送出する。レシーバ
チューブ２６は、図３、図４および図５に示すように、
矩形状のチューブ３０の内部を上下２段に仕切るプレー
ト３２が長手方向に嵌合されており、このプレート３２
によって上下に仕切られる上段の流路３１の右端に上側
キャップ３４が嵌合され、下段の流路３３の左端に下側
キャップ３６が嵌合されている。プレート３２の下流部
には内径約５ｍｍの４個の穴４０が長手方向に等間隔に
幅方向中央部に形成されている。これらの穴４０は図５
で中央部よりも右側に形成されている。これは中央部よ
りも右側に穴４０を形成すると液冷媒をガス冷媒に優先
して上段の流路３１から下段の流路３３に通すことがで
きるからである。プレート３２に形成する穴の個数、内
径、位置については前記述に限定されるものでない。The gas-liquid separating section 7 is composed of a receiver tube 26 which is a rectangular tube having a diameter larger than that of the refrigerant tube 10a of the main condenser section 6, and sends the refrigerant from the main condenser section 6 to the auxiliary condenser section 8. . The receiver tube 26, as shown in FIGS. 3, 4 and 5,
A plate 32 for partitioning the inside of the rectangular tube 30 into upper and lower two stages is fitted in the longitudinal direction.
The upper cap 34 is fitted to the right end of the upper flow path 31 partitioned by the upper and lower parts, and the lower cap 36 is fitted to the left end of the lower flow path 33. In the downstream portion of the plate 32, four holes 40 having an inner diameter of about 5 mm are formed in the widthwise central portion at equal intervals in the longitudinal direction. These holes 40 are shown in FIG.
It is formed on the right side of the central part. This is because when the hole 40 is formed on the right side of the central portion, the liquid refrigerant can be passed through the upper channel 31 to the lower channel 33 in preference to the gas refrigerant. The number, the inner diameter, and the position of the holes formed in the plate 32 are not limited to those described above.
【００１１】レシーバチューブ２６の製造方法について
図６〜図８にもとづいて説明する。アルミニウム材から
なる図６に示す断面矩形状のチューブ３０を押出成形に
より製作する。また図７に示すように、アルミニウム材
のプレート３２の長さ方向の中央部以降に数個の穴４０
を形成する。このプレート３２をチューブ３０の溝部３
０ａに挿入する。次いでアルミニウム材からなるキャッ
プ３４をチューブ３０の片側の端面の一通路側に嵌合し
ろう付けする。反対側の端面の反対の通路側にアルミウ
ム材からなるキャップ３６を嵌合しろう付けする。この
とき冷媒の流れる方向の後方に穴４０が来るようにし、
また穴４０側の端面でキャップ３４が上段側に来るよう
にする。A method of manufacturing the receiver tube 26 will be described with reference to FIGS. A tube 30 made of an aluminum material and having a rectangular cross section shown in FIG. 6 is manufactured by extrusion molding. Further, as shown in FIG. 7, several holes 40 are formed after the central portion of the aluminum plate 32 in the longitudinal direction.
To form. This plate 32 is used as the groove portion 3 of the tube 30.
Insert into 0a. Then, a cap 34 made of an aluminum material is fitted and brazed to one passage side of the end surface of the tube 30 on one side. A cap 36 made of an aluminum material is fitted and brazed to the passage side opposite to the opposite end face. At this time, the hole 40 should come to the rear of the direction in which the refrigerant flows,
Further, the cap 34 is arranged so as to come to the upper stage side at the end surface on the hole 40 side.
【００１２】次にヘッダ部の構造について図９および図
１０にもとづいて説明する。円筒状のヘッダ部１５、１
７に冷媒チューブ１０ａ、１０ｃを挿入可能な穴５２
と、レシーバチューブ２６を挿入可能な穴５４を形成
し、これらの穴５２、５４に冷媒チューブ１０ａ、１０
ｃ並びにレシーバチューブ２６を挿入し、これらヘッダ
部１５、１７、冷媒チューブ１０ａ、１０ｃおよびレシ
ーバチューブ２６を一体にろう付け接合する。ヘッダ部
は扁平状の形状にすることもできる。Next, the structure of the header portion will be described with reference to FIGS. 9 and 10. Cylindrical header part 15, 1
Hole 52 into which the refrigerant tubes 10a and 10c can be inserted
And holes 54 into which the receiver tubes 26 can be inserted are formed, and the refrigerant tubes 10a, 10
c and the receiver tube 26 are inserted, and the header portions 15 and 17, the refrigerant tubes 10a and 10c, and the receiver tube 26 are integrally brazed and joined. The header portion can also have a flat shape.
【００１３】補コンデンサ部８は、主コンデンサ部６と
同様にヘッダ型に構成されており、冷媒チューブ１０ｃ
と放熱用フィン１２ｃとを交互に積層したコア部１３
と、左右のヘッダ部２２、２０とからなる。補コンデン
サ部８は、気液分離部７からの冷媒流が凝縮された液冷
媒をさらに過冷却する機能をもつ。次に、冷媒の凝縮さ
れる様子を図１にもとづいて詳述する。The auxiliary condenser section 8 is of a header type like the main condenser section 6, and has a refrigerant tube 10c.
13 in which heat radiation fins 12c are alternately laminated
And left and right header parts 22 and 20. The auxiliary condenser section 8 has a function of further supercooling the liquid refrigerant in which the refrigerant flow from the gas-liquid separating section 7 is condensed. Next, how the refrigerant is condensed will be described in detail with reference to FIG.
【００１４】主コンデンサ部６のヘッダ部１５の内部に
は冷媒入口パイプ１６からガス冷媒が供給される。供給
されたガス冷媒は、ヘッダ部１５とヘッダ部１７を結ぶ
冷媒チューブ１０ａ内を流通し、この間に冷却されてヘ
ッダ部１７に至る。ガス冷媒は、主コンデンサ部１の冷
媒チューブ１０ａを通過する間に放熱用フィン１２ａを
介して外気と熱交換して放熱し、凝縮されて凝縮液（液
冷媒）と気体（ガス冷媒）との気液２相の状態となる。
そして凝縮液の占める割合が多くなって気液分離部７へ
と送出される。A gas refrigerant is supplied to the inside of the header portion 15 of the main condenser portion 6 from a refrigerant inlet pipe 16. The supplied gas refrigerant flows through the refrigerant tube 10a that connects the header portion 15 and the header portion 17, and is cooled during this period to reach the header portion 17. The gas refrigerant exchanges heat with the outside air through the heat radiating fins 12a to radiate heat while passing through the refrigerant tube 10a of the main condenser unit 1, and is condensed to form a condensed liquid (liquid refrigerant) and a gas (gas refrigerant). It becomes a gas-liquid two-phase state.
Then, the proportion of the condensed liquid increases and the condensed liquid is sent to the gas-liquid separation unit 7.
【００１５】主コンデンサ部６で凝縮液と気体の気液２
相状態となった冷媒流は、次に気液分離部７の冷媒通路
すなわちレシーバチューブ２６に導入される。このレシ
ーバチューブ２６内の冷媒は、気液２相で気液の流速比
はあるが、気液の割合は変化することなしに冷媒流はレ
シーバチューブ２６内を図１で右方向に流れる。その途
中でガスと液とが重力の影響で上下に分離されて、そし
てガス冷媒よりも液冷媒が優先的に上段の流路３１から
穴４０を通して下段の流路３３に落下し、この液冷媒が
ヘッダ部２０に送られる。この液冷媒は冷媒チューブ１
０ｃを通りヘッダ部２２に送出される。この液冷媒は、
補コンデンサ部８の冷媒チューブ１０ｃを通過する間に
放熱用フィン１２ｃを介して外気と熱交換して放熱し、
過冷却状態となり過冷却の液冷媒がヘッダ部２２に送出
される。In the main condenser section 6, the condensed liquid and the gas-liquid 2
The refrigerant flow in the phase state is then introduced into the refrigerant passage of the gas-liquid separating section 7, that is, the receiver tube 26. The refrigerant in the receiver tube 26 has a gas-liquid two-phase flow rate ratio of gas-liquid, but the refrigerant flow flows in the receiver tube 26 in the right direction in FIG. 1 without changing the gas-liquid ratio. On the way, the gas and the liquid are separated vertically due to the influence of gravity, and the liquid refrigerant preferentially drops from the gas refrigerant from the upper flow passage 31 through the hole 40 to the lower flow passage 33. Is sent to the header section 20. This liquid refrigerant is the refrigerant tube 1
It is sent to the header section 22 through 0c. This liquid refrigerant is
While passing through the refrigerant tube 10c of the auxiliary condenser portion 8, heat is exchanged with the outside air through the heat radiating fins 12c to radiate heat.
The supercooled state is established and the supercooled liquid refrigerant is sent to the header portion 22.
【００１６】次にこの冷媒の冷凍サイクルを図１１に示
すモリエル線図にもとづいて説明する。Ａ状態の乾き冷
媒蒸気は、図２に示す圧縮機１で圧縮され、Ｂ状態の高
温高圧になる。この高温高圧の冷媒蒸気は、主コンデン
サ部６で放熱して一部が液化し、気液２相のＣ状態とな
る。次いで気液分離部７に入り、気相と液相に分離し、
液冷媒が補コンデンサ部８に入る。このとき過冷却度が
零の状態であるが、これよりさらに補コンデンサ部８で
過冷却されＥ状態の過冷却域に来る。Ｅ状態では過冷却
された液冷媒の状態である。この液冷媒が膨張弁３を通
って絞り膨張し低温低圧の気液混合状態となりＦ状態と
なりエバポレータ４に入る。エバポレータ４では冷媒は
周囲の空気から熱を奪って気化し、過熱域のＡ状態とな
り再び圧縮機１に入り、以上の冷凍サイクルを繰り返
す。Next, the refrigerating cycle of this refrigerant will be explained based on the Mollier diagram shown in FIG. The dry refrigerant vapor in the A state is compressed by the compressor 1 shown in FIG. 2 and becomes high temperature and high pressure in the B state. This high-temperature, high-pressure refrigerant vapor radiates heat in the main condenser portion 6 and is partly liquefied to be in a gas-liquid two-phase C state. Next, it enters the gas-liquid separation section 7 and separates into a gas phase and a liquid phase,
The liquid refrigerant enters the auxiliary condenser section 8. At this time, the degree of supercooling is zero, but further subcooling is performed in the auxiliary condenser unit 8 to reach the supercooling region in the E state. In the E state, the liquid refrigerant is supercooled. This liquid refrigerant passes through the expansion valve 3 and squeezes and expands into a low-temperature low-pressure gas-liquid mixed state and enters the evaporator 4 into the F state. In the evaporator 4, the refrigerant takes heat from the surrounding air to be vaporized, enters the overheated region A state, enters the compressor 1 again, and repeats the above refrigeration cycle.
【００１７】従来の比較例では、前記Ｄ状態の位置の過
冷却度零の状態で止まりそれ以上過冷却されることはな
いがためにエバポレータ４での冷凍能力のエンタルピー
差（ｒ1 ）が小さい。これに対し前記実施例においては
エンタルピー差（ｒ2 ）が相対的に大きい。なおＷは圧
縮機の仕事量を示す。高負荷状態では冷凍サイクルの曲
線が右上に上昇した線図を描く。In the conventional comparative example, the enthalpy difference (r 1 ) of the refrigerating capacity in the evaporator 4 is small because it stops at the position of the D state where the degree of supercooling is zero and is not further cooled. . On the other hand, in the above embodiment, the enthalpy difference (r 2 ) is relatively large. Note that W indicates the work of the compressor. In the high load condition, the curve of the refrigeration cycle is drawn in the upper right.
【００１８】次に本発明の前記実施例による実験データ
を図１２〜図１４に示す。実験による負荷条件は、凝縮
器の温度３５℃、風速４．５ｍ／ｓ、エバポレータの温
度２７℃、湿度５０％、ブロア風量３００ｍ3 ／分、圧
縮機の回転数１８００ｒｐｍであった。過冷却度を０℃
から増していくと、図１２で圧縮機の動力はある範囲ま
ではあまり変わらないが、ある過冷却度を超すと、圧縮
機の動力は増加してしまう。また、図１３では、ある範
囲までは冷凍能力は向上するが、それ以上は向上しなく
なる。図１２と図１３から、ある過度な過冷却度をとれ
ば過冷却度が０℃よりも成績係数が向上することが理解
できる。Next, experimental data according to the above embodiment of the present invention are shown in FIGS. The experimental load conditions were a condenser temperature of 35 ° C., a wind speed of 4.5 m / s, an evaporator temperature of 27 ° C., a humidity of 50%, a blower air volume of 300 m 3 / min, and a compressor rotation speed of 1800 rpm. Supercooling degree 0 ℃
As shown in FIG. 12, the power of the compressor does not change so much to a certain range. However, if it exceeds a certain degree of supercooling, the power of the compressor increases. Further, in FIG. 13, the refrigerating capacity is improved up to a certain range, but it is not improved any further. It can be understood from FIGS. 12 and 13 that the coefficient of performance is improved when the supercooling degree is 0 ° C. when the supercooling degree is excessive.
【００１９】次に本発明をサーペンタイン型凝縮器に適
用した第２実施例を図１５および図１６に示す。この第
２実施例は、コルゲートチューブ型コンデンサであっ
て、パイプ状の冷媒チューブ６０を蛇行させ、途中にレ
シーバチューブ６２を設け、このレシーバチューブ６２
の下流端に補コンデンサ部７０からなる冷媒チューブ６
４を形成した例である。図１５において、主コンデンサ
部６６、気液分離部６８、補コンデンサ部７０が構成さ
れる。冷媒チューブ６０の隣り合う冷媒チューブ６０間
には放熱用フィン７２がろう付け、ハンダ付け等により
接合されている。レシーバチューブ６２は上下２段に仕
切り壁７４が形成され、この仕切り壁７４の下流側に数
個の穴７６が形成される。冷媒入口７８から入った冷媒
は主コンデンサ部６６で放熱し、気液混合状態となり気
液分離部６８に入り、そのうちの液冷媒が穴７６を通っ
て下段の流路に落ちて補コンデンサ部７０の冷媒チュー
ブ６４を流れ過冷却された液冷媒となり冷媒出口８２か
ら送出される。Next, a second embodiment in which the present invention is applied to a serpentine type condenser is shown in FIGS. 15 and 16. The second embodiment is a corrugated tube type condenser, in which a pipe-shaped refrigerant tube 60 is meandered and a receiver tube 62 is provided in the middle thereof.
Refrigerant tube 6 including an auxiliary condenser unit 70 at the downstream end of the
4 is an example in which No. 4 is formed. In FIG. 15, a main condenser unit 66, a gas-liquid separating unit 68, and a supplementary condenser unit 70 are configured. Radiating fins 72 are joined between the adjacent refrigerant tubes 60 of the refrigerant tubes 60 by brazing, soldering or the like. The receiver tube 62 has partition walls 74 formed in upper and lower two stages, and several holes 76 are formed on the downstream side of the partition walls 74. The refrigerant that has entered from the refrigerant inlet 78 radiates heat in the main condenser portion 66, becomes a gas-liquid mixed state, and enters the gas-liquid separation portion 68, and the liquid refrigerant thereof falls through the hole 76 into the lower flow path and the auxiliary condenser portion 70. Flowing through the refrigerant tube 64 to become a supercooled liquid refrigerant and is sent out from the refrigerant outlet 82.
【００２０】前記実施例で示したように、本発明では、
コンデンサ、レシーバ、補コンデンサ部を一体化させ、
レシーバチューブを特殊な形状にし２段に仕切ることで
液冷媒とガス冷媒とを効果的に分離する機能をもたせ
た。As shown in the above embodiment, according to the present invention,
Integrate the condenser, receiver and auxiliary condenser,
The receiver tube has a special shape and is divided into two stages to effectively separate the liquid refrigerant and the gas refrigerant.
【００２１】[0021]
【発明の効果】以上説明したように、本発明の凝縮器に
よれば、コンデンサ部と気液分離部と過冷却機能をもっ
た補コンデンサ部とを配管で繋ぐことなくこれら各部を
一体構造にした構成にしたため、冷凍サイクルの冷凍能
力および成績係数を向上させることができるとともに冷
媒回路の配管を無くすことにより省スペース化およびコ
ンパクト化を図ることができるという効果がある。As described above, according to the condenser of the present invention, the condenser portion, the gas-liquid separating portion, and the auxiliary condenser portion having a supercooling function are integrated into each other without connecting them by piping. With this configuration, the refrigerating capacity and the coefficient of performance of the refrigerating cycle can be improved, and there is an effect that space saving and compactness can be achieved by eliminating the piping of the refrigerant circuit.
【図１】本発明の第１実施例による凝縮器を示す概略構
成図である。FIG. 1 is a schematic configuration diagram showing a condenser according to a first embodiment of the present invention.
【図２】本発明の第１実施例による凝縮器を適用した冷
凍サイクルを示す冷媒回路図である。FIG. 2 is a refrigerant circuit diagram showing a refrigeration cycle to which the condenser according to the first embodiment of the present invention is applied.
【図３】本発明の第１実施例によるレシーバチューブを
示す縦断面図である。FIG. 3 is a vertical sectional view showing a receiver tube according to the first embodiment of the present invention.
【図４】（Ａ）は図３に示すＡ矢視図である。（Ｂ）は
図３に示すＢ矢視図である。FIG. 4A is a view on arrow A shown in FIG. (B) is a view on arrow B shown in FIG. 3.
【図５】図３に示すプレートのＣ矢視図である。5 is a view on arrow C of the plate shown in FIG. 3. FIG.
【図６】レシーバチューブの部分側面図である。FIG. 6 is a partial side view of a receiver tube.
【図７】レシーバチューブのチューブにプレートを取付
ける工程を示す説明図である。FIG. 7 is an explanatory diagram showing a step of attaching a plate to a tube of a receiver tube.
【図８】レシーバチューブのチューブにキャップを取付
ける状態を示す説明図である。FIG. 8 is an explanatory diagram showing a state in which a cap is attached to the tube of the receiver tube.
【図９】ヘッダ部を示す部分斜視図である。FIG. 9 is a partial perspective view showing a header portion.
【図１０】ヘッダ部を示す平面図である。FIG. 10 is a plan view showing a header section.
【図１１】本発明の第１実施例による冷凍サイクルと従
来の比較例による冷凍サイクルを対比したモリエル線図
である。FIG. 11 is a Mollier diagram comparing the refrigeration cycle according to the first embodiment of the present invention with the refrigeration cycle according to the conventional comparative example.
【図１２】本発明の第１実施例の実験データによる過冷
却度と圧縮機必要動力の関係を示す特性図である。FIG. 12 is a characteristic diagram showing the relationship between the degree of supercooling and the required power of the compressor according to the experimental data of the first embodiment of the present invention.
【図１３】本発明の第１実施例の実験データによる過冷
却度と冷凍能力の関係を示す特性図である。FIG. 13 is a characteristic diagram showing the relationship between the degree of supercooling and the refrigerating capacity according to the experimental data of the first embodiment of the present invention.
【図１４】本発明の第１実施例の実験データによる過冷
却度と成績係数の関係を示す特性図である。FIG. 14 is a characteristic diagram showing the relationship between the degree of supercooling and the coefficient of performance according to the experimental data of the first embodiment of the present invention.
【図１５】本発明の第２実施例による凝縮器を示す概略
構成図である。FIG. 15 is a schematic configuration diagram showing a condenser according to a second embodiment of the present invention.
【図１６】本発明の第２実施例による冷媒チューブとレ
シーバチューブとの取付け状態を示す部分斜視図であ
る。FIG. 16 is a partial perspective view showing a mounted state of a refrigerant tube and a receiver tube according to a second embodiment of the present invention.
６ 主コンデンサ部 ７ 気液分離部 ８ 補コンデンサ部 １０ａ、１０ｃ 冷媒チューブ（冷媒通路管） １２ａ、１２ｃ 放熱用フィン ２６ レシーバチューブ ３１、３３ 流路（室） ３２ プレート（仕切板） ４０ 穴 6 Main capacitor section 7 Gas-liquid separation section 8 Auxiliary capacitor section 10a, 10c Refrigerant tube (refrigerant passage tube) 12a, 12c Heat dissipation fin 26 receiver tube 31, 33 Channel (room) 32 plates (partition plate) 40 holes
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Continued front page (72) Inventor Toshio Ohara Nihonden, 1-1, Showa-cho, Kariya city, Aichi prefecture Sozo Co., Ltd.
Claims (2)
媒通路管に接合されたフィンとを備え、前記冷媒通路管
内を流通する冷媒流を前記フィンを介して放熱させるこ
とにより凝縮する凝縮器であって、 前記冷媒通路の途中に、前記冷媒通路の通路面積より大
きい通路面積を有するとともに、この冷媒通路を上下二
段の室に仕切りかつ上側の室と下側の室を連通する穴を
もつ仕切板を設けたレシーバチューブと、 前記レシーバチューブ内で前記下側の室に分離された冷
媒流をさらに過冷却するように、冷媒通路を構成する冷
媒通路管と、この冷媒通路管に接合されたフィンとから
なる補コンデンサ部とを備えたことを特徴とする凝縮
器。1. A condenser comprising a refrigerant passage pipe forming a refrigerant passage and fins joined to the refrigerant passage pipe, wherein the refrigerant flow flowing in the refrigerant passage pipe is radiated through the fins to condense to condense. And a hole having a passage area larger than the passage area of the refrigerant passage in the middle of the refrigerant passage and partitioning the refrigerant passage into upper and lower two-stage chambers and connecting the upper chamber and the lower chamber. A receiver tube provided with a partition plate having, a refrigerant passage tube that constitutes a refrigerant passage and a refrigerant passage tube that constitutes a refrigerant passage so as to further subcool the refrigerant flow separated into the lower chamber in the receiver tube. A condenser, comprising: an auxiliary condenser section including joined fins.
側に形成されることを特徴とする請求項１に記載の凝縮
器。2. The condenser according to claim 1, wherein the hole is formed on the downstream side of the refrigerant flow from the central portion of the partition plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16446491A JPH0510633A (en) | 1991-07-04 | 1991-07-04 | Condenser |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16446491A JPH0510633A (en) | 1991-07-04 | 1991-07-04 | Condenser |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0510633A true JPH0510633A (en) | 1993-01-19 |
Family
ID=15793677
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16446491A Pending JPH0510633A (en) | 1991-07-04 | 1991-07-04 | Condenser |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0510633A (en) |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1163741A (en) * | 1997-08-25 | 1999-03-05 | Denso Corp | Receiver in freezing cycle |
| FR2807824A1 (en) * | 2000-04-14 | 2001-10-19 | Behr Gmbh & Co | CONDENSER FOR AN AIR CONDITIONING SYSTEM, PARTICULARLY FOR AN AIR CONDITIONING SYSTEM OF A MOTOR VEHICLE |
| FR2808869A1 (en) | 2000-05-09 | 2001-11-16 | Sanden Corp | CONDENSER TYPE A SUB-COOLING |
| US6684662B2 (en) | 1999-07-06 | 2004-02-03 | Showa Denko K.K. | Refrigeration system, and condenser for use in decompressing-tube system |
| JP2004044873A (en) * | 2002-07-10 | 2004-02-12 | National Institute Of Advanced Industrial & Technology | Heat exchanger |
| WO2006070923A1 (en) * | 2004-12-28 | 2006-07-06 | Showa Denko K.K. | Heat exchanger |
| WO2006088247A1 (en) * | 2005-02-18 | 2006-08-24 | Showa Denko K.K. | Heat exchanger |
| DE4245046C8 (en) * | 1992-11-18 | 2008-08-21 | Behr Gmbh & Co. Kg | Condenser for an air conditioning system of a vehicle |
| JP2012067939A (en) * | 2010-09-21 | 2012-04-05 | Denso Corp | Condenser |
| CN103148642A (en) * | 2011-12-07 | 2013-06-12 | 现代自动车株式会社 | Condenser for vehicle |
| CN103206814A (en) * | 2013-04-12 | 2013-07-17 | 南京佳力图空调机电有限公司 | Supercooling device for magnetic suspension refrigerating system with natural cold source |
| KR101385029B1 (en) * | 2007-04-11 | 2014-04-14 | 한라비스테온공조 주식회사 | A Condenser |
| JP2016133268A (en) * | 2015-01-20 | 2016-07-25 | 株式会社デンソー | Condenser |
| CN117287875A (en) * | 2023-11-22 | 2023-12-26 | 广州全正汽车配件有限公司 | Double-layer condenser for automobile |
-
1991
- 1991-07-04 JP JP16446491A patent/JPH0510633A/en active Pending
Cited By (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4245046C8 (en) * | 1992-11-18 | 2008-08-21 | Behr Gmbh & Co. Kg | Condenser for an air conditioning system of a vehicle |
| JPH1163741A (en) * | 1997-08-25 | 1999-03-05 | Denso Corp | Receiver in freezing cycle |
| US6684662B2 (en) | 1999-07-06 | 2004-02-03 | Showa Denko K.K. | Refrigeration system, and condenser for use in decompressing-tube system |
| FR2807824A1 (en) * | 2000-04-14 | 2001-10-19 | Behr Gmbh & Co | CONDENSER FOR AN AIR CONDITIONING SYSTEM, PARTICULARLY FOR AN AIR CONDITIONING SYSTEM OF A MOTOR VEHICLE |
| FR2808869A1 (en) | 2000-05-09 | 2001-11-16 | Sanden Corp | CONDENSER TYPE A SUB-COOLING |
| US6470703B2 (en) | 2000-05-09 | 2002-10-29 | Sanden Corporation | Subcooling-type condenser |
| DE10122360B4 (en) * | 2000-05-09 | 2005-04-21 | Sanden Corp., Isesaki | While cooling condenser |
| JP2004044873A (en) * | 2002-07-10 | 2004-02-12 | National Institute Of Advanced Industrial & Technology | Heat exchanger |
| WO2006070923A1 (en) * | 2004-12-28 | 2006-07-06 | Showa Denko K.K. | Heat exchanger |
| WO2006088247A1 (en) * | 2005-02-18 | 2006-08-24 | Showa Denko K.K. | Heat exchanger |
| KR101385029B1 (en) * | 2007-04-11 | 2014-04-14 | 한라비스테온공조 주식회사 | A Condenser |
| JP2012067939A (en) * | 2010-09-21 | 2012-04-05 | Denso Corp | Condenser |
| CN103148642A (en) * | 2011-12-07 | 2013-06-12 | 现代自动车株式会社 | Condenser for vehicle |
| KR101326841B1 (en) * | 2011-12-07 | 2013-11-11 | 현대자동차주식회사 | Condenser for vehicle |
| CN103148642B (en) * | 2011-12-07 | 2016-09-14 | 现代自动车株式会社 | Condenser for vehicle |
| CN103206814A (en) * | 2013-04-12 | 2013-07-17 | 南京佳力图空调机电有限公司 | Supercooling device for magnetic suspension refrigerating system with natural cold source |
| JP2016133268A (en) * | 2015-01-20 | 2016-07-25 | 株式会社デンソー | Condenser |
| CN117287875A (en) * | 2023-11-22 | 2023-12-26 | 广州全正汽车配件有限公司 | Double-layer condenser for automobile |
| CN117287875B (en) * | 2023-11-22 | 2024-02-09 | 广州全正汽车配件有限公司 | Double-layer condenser for automobile |
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