JP2644900B2 - Heat exchanger - Google Patents
Heat exchangerInfo
- Publication number
- JP2644900B2 JP2644900B2 JP33721089A JP33721089A JP2644900B2 JP 2644900 B2 JP2644900 B2 JP 2644900B2 JP 33721089 A JP33721089 A JP 33721089A JP 33721089 A JP33721089 A JP 33721089A JP 2644900 B2 JP2644900 B2 JP 2644900B2
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat exchanger
- header
- insertion member
- heat transfer
- 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 - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
Description
【発明の詳細な説明】 産業上の利用分野 本発明は空気調和，冷凍，冷蔵機器等に用いられる熱
交換器に関するものである。Description: TECHNICAL FIELD The present invention relates to a heat exchanger used for air conditioning, refrigeration, refrigeration equipment and the like.
従来の技術 近年、熱交換器の高効率化や工法改善に伴い、冷媒管
の細径丸管や薄型偏平管の利用が盛んになってきた。こ
れにともない、管内圧力損失の関係上、冷媒回路の多パ
ス化が進んできている。こうした技術は特開昭63−1319
93号公報や実開昭63−243688号公報にも示されている。2. Description of the Related Art In recent years, with the increase in efficiency of heat exchangers and improvement of construction methods, the use of small-diameter round tubes and thin flat tubes as refrigerant tubes has become popular. Along with this, the number of refrigerant circuit paths has been increasing due to the pressure loss in the pipe. Such a technique is disclosed in JP-A-63-1319.
It is also disclosed in JP-A-93-93 and JP-A-63-243688.
以下従来の熱交換器を第５図，第６図を用いて説明す
る。第５図は従来の熱交換器の断面図、第６図は従来の
熱交換器の平面図である。１は熱交換器、2aから2hまで
は伝熱管、３は伝熱フィン、４は中間ヘッダーで略円筒
状管の上下端はキャップ5a,5bにより封止されている。
６は出入口ヘッダーで上下端は中間ヘッダー４と同様キ
ャップ9a,9bにより封止されており、さらに、その略中
央部で仕切板10にて上部ヘッダー部８と下部ヘッダー部
７に分離されている。各部品はアルミニウムより成形さ
れており、炉中にて一体ロー付され熱交換器１を構成し
ている。Hereinafter, a conventional heat exchanger will be described with reference to FIGS. 5 and 6. FIG. FIG. 5 is a cross-sectional view of a conventional heat exchanger, and FIG. 6 is a plan view of the conventional heat exchanger. 1 is a heat exchanger, 2a to 2h are heat transfer tubes, 3 is a heat transfer fin, 4 is an intermediate header, and upper and lower ends of a substantially cylindrical tube are sealed by caps 5a and 5b.
Reference numeral 6 denotes an entrance header, the upper and lower ends of which are sealed with caps 9a and 9b as in the case of the intermediate header 4. Further, a substantially central portion thereof is separated into an upper header section 8 and a lower header section 7 by a partition plate 10. . Each part is formed of aluminum, and is integrally brazed in a furnace to form the heat exchanger 1.
従来の熱交換器１は凝縮器として使用される場合は、
接続管12より高温高圧ガス冷媒が出入口ヘッダー６の上
部ヘッダー部８に流入し、伝熱管2e,2f,2g,2hを通り、
中間ヘッダー４にて一旦合流した後、伝熱管2a,2b,2c,2
d,2dに分流して、下部ヘッダー部７に流入し、接続管11
より流出する。この際、冷媒は伝熱管2a,2b,2c,2d,2e,2
f,2g,2h内を流れる間に伝熱フィン３間を流れる空気と
熱交換し、冷媒は徐々に凝縮し、接続管11より流出する
際には冷媒のすべて液化している。When the conventional heat exchanger 1 is used as a condenser,
High-temperature and high-pressure gas refrigerant flows into the upper header section 8 of the inlet / outlet header 6 from the connection pipe 12, passes through the heat transfer pipes 2e, 2f, 2g, and 2h,
After merging once at the intermediate header 4, the heat transfer tubes 2a, 2b, 2c, 2
d, 2d, flows into the lower header section 7, and is connected to the connection pipe 11
More outflow. At this time, the refrigerant flows into the heat transfer tubes 2a, 2b, 2c, 2d, 2e, 2
The heat exchanges with the air flowing between the heat transfer fins 3 while flowing through the f, 2g, and 2h, and the refrigerant gradually condenses.
また、従来の熱交換器１が蒸発器として使用される場
合、冷媒の流れは凝縮器の場合と逆になる。すなわち、
減圧された冷媒は接続管11より出入口ヘッダー６の下部
ヘッダー部７に流入し、伝熱管2a,2b,2c,2dへ分流す
る。冷媒は、伝熱フィン３間を流れる空気と熱交換しつ
つ、徐々に乾き度を大きくしながら気液２相状態で中間
ヘッダー４内へ流入する。中間ヘッダー４内で一旦合流
した冷媒は、伝熱管2e,2f,2g,2h内へ分流して流れ込
み、ここでも、冷媒は徐々に蒸発しながら、上部ヘッダ
ー部８へ流入する。上部ヘッダー部８へ流入する際に冷
媒は、ほぼ蒸発しきっており、接続管12からは低圧ガス
状態で流出していく。Also, when the conventional heat exchanger 1 is used as an evaporator, the flow of the refrigerant is opposite to that of the condenser. That is,
The depressurized refrigerant flows into the lower header section 7 of the entrance header 6 from the connection pipe 11, and is diverted to the heat transfer pipes 2a, 2b, 2c, 2d. The refrigerant flows into the intermediate header 4 in a gas-liquid two-phase state while gradually increasing the dryness while exchanging heat with the air flowing between the heat transfer fins 3. The refrigerant once merged in the intermediate header 4 is split and flows into the heat transfer tubes 2e, 2f, 2g, and 2h. Here, the refrigerant also flows into the upper header portion 8 while gradually evaporating. When flowing into the upper header portion 8, the refrigerant has almost completely evaporated, and flows out of the connection pipe 12 in a low-pressure gas state.
発明が解決しようとする課題 しかしながら、上記した従来の熱交換器１を蒸発器と
して用いる場合、下部ヘッダー部7,中間ヘッダー4,上部
ヘッダー部８において、その内容積が大きく、冷媒流速
が低下しているため、重力の影響を受け易く、冷媒の気
相部と液相部の分離が起こり易い。よって伝熱管2a,2b,
2c,2d間および伝熱管2e,2f,2g,2h間で冷媒流量の偏りが
おこり、熱交換器の本来持っている熱交換能力を十分に
発揮できていなかった。また、中間ヘッダー４および出
入口ヘッダー６内へ挿入された伝熱管2aから2hの両端
は、中間ヘッダー４及び出入口ヘッダー６内へ大きく突
出するため、中間ヘッダー４及び出入口ヘッダー６内を
通る冷媒の流れの抵抗となっており、蒸発圧力の上昇や
凝縮圧力の低下を招き熱交換能力を低下させる原因とな
っていた。However, when the above-described conventional heat exchanger 1 is used as an evaporator, the lower header portion 7, the intermediate header 4, and the upper header portion 8 have large internal volumes and a low flow rate of the refrigerant. Therefore, the refrigerant is susceptible to the influence of gravity, and the refrigerant is likely to be separated into a gaseous phase part and a liquid phase part. Therefore, the heat transfer tubes 2a, 2b,
The refrigerant flow was biased between 2c and 2d and between the heat transfer tubes 2e, 2f, 2g and 2h, and the heat exchange capacity inherent in the heat exchanger was not fully exhibited. Further, since both ends of the heat transfer tubes 2a to 2h inserted into the intermediate header 4 and the entrance / exit header 6 largely protrude into the intermediate header 4 and the entrance / exit header 6, the flow of the refrigerant passing through the intermediate header 4 and the entrance / exit header 6 is performed. , Which causes an increase in the evaporation pressure and a decrease in the condensation pressure, thereby reducing the heat exchange capacity.
本発明は前記課題に鑑み、各伝熱管間の冷媒偏流を少
なくするとともに、冷媒流路の圧力損失を少なくし、熱
交換器のもつ熱交換能力を最大限発揮させる熱交換器を
提供するものである。The present invention has been made in view of the above problems, and provides a heat exchanger that reduces a refrigerant drift between respective heat transfer tubes, reduces a pressure loss in a refrigerant passage, and maximizes a heat exchange capability of the heat exchanger. It is.
課題を解決するための手段 上記課題を解決するため本発明は、両端を略円弧状に
切断した複数の伝熱管と、内部に１個あるいは直列に複
数配列した管状挿入部材が配設され、管状挿入部材との
間に冷媒流路を形成するヘッダー分流器から熱交換器を
構成するものである。Means for Solving the Problems In order to solve the above problems, the present invention provides a plurality of heat transfer tubes, both ends of which are cut in a substantially arc shape, and a tubular insertion member in which one or a plurality of tubes are arranged in series. The heat exchanger is composed of a header flow divider that forms a refrigerant flow passage between the heat exchanger and the insertion member.
作用 本発明はかかる構成により、ヘッダー内の冷媒流路を
十分に確保し、冷媒の気液混合を促すことによって、各
伝熱管間での冷媒偏流を小さくし、また各ヘッダー内で
の冷媒圧力損失を不必要に大きくしない。Function The present invention has a configuration in which the refrigerant flow path in the header is sufficiently ensured, and the refrigerant is mixed with heat by promoting gas-liquid mixing, thereby reducing the refrigerant drift between the heat transfer tubes and the refrigerant pressure in each header. Do not increase losses unnecessarily.
実 施 例 以下、本発明の実施例を第１図から第４図を用いて説
明する。第１図は本発明の熱交換器の断面図であり、第
２図はその平面図である。第３図は各部品の組立状態を
示す斜視図であり、第４図は第１図のＸ−Ｘ′断面図で
ある。Embodiment Hereinafter, an embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a sectional view of a heat exchanger of the present invention, and FIG. 2 is a plan view thereof. FIG. 3 is a perspective view showing an assembled state of each part, and FIG. 4 is a sectional view taken along line XX 'of FIG.
第１図から第４図において、21は本発明の熱交換器
で、22a,22b,22c,22d,22e,22f,22g,22hは伝熱管で内部
に複数の流路を有し、その両端は略円弧状に切断されて
いる。23は伝熱フィンで伝熱管22a,22b,22c,22d,22e,22
f,22g,22hに接合されている。24は中間ヘッダーで、伝
熱管22a,22b,22c,22d,22e,22f,22g,22hを接合している
外管25と、外管25内部に配設されている管状挿入部材26
とから構成している。管状挿入部材26の両端26a,26bは
外管25の内径まで拡管されており、炉中ロー付により外
管25と接合することにより、中間ヘッダー24内冷媒流路
Ｂを形成する。1 to 4, reference numeral 21 denotes a heat exchanger of the present invention, 22a, 22b, 22c, 22d, 22e, 22f, 22g, 22h are heat transfer tubes having a plurality of flow passages therein, and both ends thereof. Are cut in a substantially arc shape. 23 is a heat transfer fin and heat transfer tubes 22a, 22b, 22c, 22d, 22e, 22
f, 22g, 22h. 24 is an intermediate header, an outer tube 25 joining the heat transfer tubes 22a, 22b, 22c, 22d, 22e, 22f, 22g, 22h, and a tubular insertion member 26 arranged inside the outer tube 25.
It is composed of Both ends 26a and 26b of the tubular insertion member 26 are expanded to the inner diameter of the outer tube 25, and are joined to the outer tube 25 by brazing in a furnace to form a refrigerant flow path B in the intermediate header 24.
28は出入口ヘッダーで、中間ヘッダー24同様伝熱管22
a,22b,22c,22d,22e,22f,22g,22hを接合している外管29
と、外管29内部に配設されている上部管状挿入部材30,
下部管状挿入部材31とから構成しており、管状挿入部材
30,31の両端は外管内径まで拡管されており、炉中にて
一体ロー付により外管29と接合されている。特に、上部
管状挿入部材30下端の拡管部30bと下部管状挿入部材31
上端の拡管部31aは、出入口ヘッダー28を上部28aと下部
28bとに区切り、冷媒流路A,Cを形成し、熱交換器21のパ
ス構成を決定する。Reference numeral 28 denotes an entrance header, similar to the intermediate header 24.
outer tube 29 joining a, 22b, 22c, 22d, 22e, 22f, 22g, 22h
And an upper tubular insertion member 30, disposed inside the outer tube 29,
And a lower tubular insertion member 31.
Both ends of 30, 31 are expanded to the inner diameter of the outer tube, and are joined to the outer tube 29 by integral brazing in the furnace. In particular, the expanded portion 30b at the lower end of the upper tubular insertion member 30 and the lower tubular insertion member 31
The pipe expansion section 31a at the upper end connects the entrance header 28 with the upper part 28a and the lower part.
28b, the refrigerant flow paths A and C are formed, and the path configuration of the heat exchanger 21 is determined.
また、出入口ヘッダー28内部の上部管状挿入部材30の
外径Dc、下部管状挿入部材31の外径Db、中間ヘッダー24
内部の管状挿入部材26の外径DaはDc＜Da＜Dbである。The outer diameter D c of the inlet and outlet header 28 inside the upper tubular insertion member 30, the outer diameter D b of the lower tubular insertion member 31, the intermediate headers 24
Outer diameter D a of the interior of the tubular insertion member 26 is D c <D a <D b .
本熱交換器21を蒸発器として用いる際は、減圧された
冷媒が、接続管15より出入口ヘッダー28の冷媒流路Ａへ
流入し伝熱管22a,22b,22c,22dを経て中間ヘッダー26内
の冷媒流路Ｂへ流れ込み、冷媒は中間ヘッダー26上部に
移動し再度伝熱管22e,22f,22g,22hに分流し、最後に接
続管16より流出する。出入口ヘッダー28の冷媒流路A,C
内や中間ヘッダー24の冷媒流路Ｂ内では、重力の影響で
冷媒は気相部と液相部に分離し易く、各パスの中で低い
位置にある伝熱管22a,22bや22e,22fに冷媒が多く流れが
ちである。しかし各管状挿入部材26,30,31によって、冷
媒流路A,B,Cの断面積は比較的小さく、冷媒の流速が速
く保たれるため、重力の影響が小さくなって伝熱管22c,
22dや22g,22hにも冷媒は流れ易くなる。When the present heat exchanger 21 is used as an evaporator, the depressurized refrigerant flows into the refrigerant flow path A of the inlet / outlet header 28 from the connection pipe 15 and passes through the heat transfer pipes 22a, 22b, 22c, and 22d, and flows through the intermediate header 26. The refrigerant flows into the refrigerant flow path B, moves to the upper part of the intermediate header 26, flows again into the heat transfer pipes 22e, 22f, 22g, and 22h, and finally flows out from the connection pipe 16. Refrigerant flow paths A and C of entrance header 28
Inside and in the refrigerant flow path B of the intermediate header 24, the refrigerant is easily separated into a gas phase portion and a liquid phase portion by the influence of gravity, and the heat transfer tubes 22a, 22b and 22e, 22f located at lower positions in each path. A large amount of refrigerant tends to flow. However, the cross-sectional areas of the refrigerant flow paths A, B, and C are relatively small, and the flow velocity of the refrigerant is kept high.
Refrigerant also flows easily to 22d, 22g, and 22h.
また、伝熱管22a,22b,22c,22d,22e,22f,22g,22hの両
端は第３図，第４図に示すように略円弧状に切断されて
いるため、各ヘッダー内での不必要な冷媒の圧力損失が
ない。また、管状挿入部材26,30,31の管径が流入側から
流出側へ行くにしたがい小さくなり、ヘッダー内の流路
断面積が大きくなってきているので、徐々に冷媒の乾き
度が大きくなっても必要以上に冷媒流速が速くならず、
冷媒圧力損失増大を抑えることができる。凝縮器として
用いる場合は、蒸発器とは逆に、管状挿入部材の管径が
流入側から流出側へ行くにしたがい大きくすることが、
冷媒圧力損失を必要限度内にとどめることに効果的であ
る。Further, since both ends of the heat transfer tubes 22a, 22b, 22c, 22d, 22e, 22f, 22g, and 22h are cut into a substantially circular arc shape as shown in FIGS. 3 and 4, unnecessary portions in each header are unnecessary. No refrigerant pressure loss. In addition, the pipe diameter of the tubular insertion members 26, 30, 31 decreases from the inflow side to the outflow side, and the flow path cross-sectional area in the header increases, so that the dryness of the refrigerant gradually increases. Even if the refrigerant flow rate is not faster than necessary,
An increase in refrigerant pressure loss can be suppressed. When used as a condenser, contrary to the evaporator, the tube diameter of the tubular insertion member may be increased from the inflow side to the outflow side,
This is effective in keeping the refrigerant pressure loss within a necessary limit.
以上のように本実施例によれば、両端を略円弧状に切
断した複数の伝熱管と、１個あるいは直列に複数配列し
た管状挿入部材が内部に配設され、前記管状挿入部材の
拡管した端部と接合することによって管状挿入部材との
間に冷媒流路を形成するヘッダー分流器から構成した熱
交換器によって、冷媒圧力損失が必要以上に大きくなら
ず、かつ熱交換器の持つ熱交換能力を最大限発揮させる
ことができるようになる。As described above, according to the present embodiment, a plurality of heat transfer tubes, both ends of which are cut in a substantially arc shape, and one or a plurality of tubular insert members arranged in series are disposed inside, and the tubular insert members are expanded. The heat exchanger composed of a header flow divider that forms a refrigerant flow passage between the tubular insertion member and the end portion by joining the end portion ensures that the refrigerant pressure loss does not become unnecessarily large and that the heat exchange of the heat exchanger has You will be able to maximize your ability.
発明の効果 以上のように本発明は、両端を略円弧状に切断した複
数の伝熱管と、１個あるいは直列に複数配列した管状挿
入部材が内部に配設され、前記管状挿入部材の拡管した
端部と接合することによって管状挿入部材との間に冷媒
流路を形成するヘッダー分流器から構成した熱交換器に
よって、各伝熱管間の冷媒偏流を少なくし冷媒流路の圧
力損失も必要以上に大きくせずに、熱交換器のもつ熱交
換能力を最大限発揮させることができる。Effect of the Invention As described above, in the present invention, a plurality of heat transfer tubes whose both ends are cut in a substantially arc shape, and one or a plurality of tubular insertion members arranged in series are disposed inside, and the tubular insertion member is expanded. A heat exchanger composed of a header splitter that forms a refrigerant flow passage between the tubular insertion member and the end by joining the end portion reduces the refrigerant drift between the heat transfer tubes, and the pressure loss of the refrigerant flow passage is also more than necessary. The heat exchange capacity of the heat exchanger can be maximized without increasing the size.
第１図は本発明の実施例の熱交換器の断面図、第２図は
同熱交換器の平面図、第３図は本発明の実施例の組立状
態を示す部分斜視図、第４図は第１図のＸ−Ｘ′線断面
図、第５図は従来の熱交換器の断面図、第６図は第５図
の平面図である。 22a,22b,22c,22d,22e,22f,22g,22h……伝熱管、26,30,3
1……管状挿入部材、26a,26b,30a,30b,31a,31b……管状
挿入部材端部、A,B,C……冷媒流路、24,28……ヘッダ
ー。1 is a sectional view of a heat exchanger according to an embodiment of the present invention, FIG. 2 is a plan view of the heat exchanger, FIG. 3 is a partial perspective view showing an assembled state of the embodiment of the present invention, FIG. Is a sectional view taken along line XX 'of FIG. 1, FIG. 5 is a sectional view of a conventional heat exchanger, and FIG. 6 is a plan view of FIG. 22a, 22b, 22c, 22d, 22e, 22f, 22g, 22h ... Heat transfer tubes, 26,30,3
1 ... tubular insert member, 26a, 26b, 30a, 30b, 31a, 31b ... tubular insert member end, A, B, C ... refrigerant flow path, 24, 28 ... header.
Claims (3)
と、１個あるいは直列に複数配列した管状挿入部材が内
部に配設され、前記管状挿入部材との間に冷媒流路を形
成するヘッダー分流器から構成された熱交換器。1. A plurality of heat transfer tubes, both ends of which are cut in a substantially arc shape, and one or a plurality of tubular insert members arranged in series, are disposed inside, and a refrigerant flow path is formed between the tubular insert members. Heat exchanger composed of a header shunt.
内側にロー付接合し、外管と管状挿入部材との間に冷媒
流路を形成するヘッダー分流器で構成された特許請求の
範囲の範囲第１項記載の熱交換器。2. A header distributor, wherein the expanded ends of each tubular insertion member are brazed to the inside of the outer tube and a refrigerant flow path is formed between the outer tube and the tubular insertion member. 2. The heat exchanger according to claim 1, wherein
流れる冷媒の乾き度が大きいところほど順次小さくなる
管状挿入部材を設けた特許請求の範囲第１項記載の熱交
換器。3. The heat exchanger according to claim 1, further comprising a tubular insertion member in which the outer diameter of each tubular insertion member is gradually reduced as the degree of dryness of the refrigerant flowing inside the heat exchanger increases.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33721089A JP2644900B2 (en) | 1989-12-26 | 1989-12-26 | Heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33721089A JP2644900B2 (en) | 1989-12-26 | 1989-12-26 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03195872A JPH03195872A (en) | 1991-08-27 |
| JP2644900B2 true JP2644900B2 (en) | 1997-08-25 |
Family
ID=18306474
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP33721089A Expired - Fee Related JP2644900B2 (en) | 1989-12-26 | 1989-12-26 | Heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2644900B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2807152B1 (en) * | 2000-03-28 | 2002-12-06 | Cie Ind D Applic Thermiques Ci | PLATE HEAT EXCHANGER |
| KR101826365B1 (en) * | 2012-05-04 | 2018-03-22 | 엘지전자 주식회사 | A heat exchanger |
| JP2014009868A (en) * | 2012-06-28 | 2014-01-20 | Denso Corp | Heat pump cycle |
| JP6155412B1 (en) * | 2016-09-12 | 2017-06-28 | 三菱電機株式会社 | Header, heat exchanger and air conditioner |
| US11326815B2 (en) * | 2017-06-30 | 2022-05-10 | Mitsubishi Electric Corporation | Heat exchanger and refrigeration cycle apparatus |
| CN107228508B (en) * | 2017-07-06 | 2023-02-28 | 仲恺农业工程学院 | Evaporator capable of automatically adjusting double-dryness flow distribution |
-
1989
- 1989-12-26 JP JP33721089A patent/JP2644900B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03195872A (en) | 1991-08-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101657689B (en) | Multi-channel flat tube evaporator with improved condensate drainage | |
| US5765393A (en) | Capillary tube incorporated into last pass of condenser | |
| US20060054310A1 (en) | Evaporator using micro-channel tubes | |
| US9651317B2 (en) | Heat exchanger and air conditioner | |
| US8333088B2 (en) | Heat exchanger design for improved performance and manufacturability | |
| US5099913A (en) | Tubular plate pass for heat exchanger with high volume gas expansion side | |
| JPH05118706A (en) | Evaporator | |
| CN101600932B (en) | Multi-channel heat exchanger with improved condensate drainage | |
| EP3290851B1 (en) | Layered header, heat exchanger, and air conditioner | |
| KR100612765B1 (en) | Heat exchanger having fins formed thereon | |
| JPH109713A (en) | Refrigerant condensing device and refrigerant condenser | |
| JP2002130866A (en) | Condenser for air conditioning | |
| KR20170031556A (en) | Heat exchanger | |
| KR101837046B1 (en) | Heat exchanger | |
| CN113587250A (en) | Air conditioner | |
| JPH0886591A (en) | Heat exchanger and refrigerant evaporator | |
| JP2644900B2 (en) | Heat exchanger | |
| CN113587251A (en) | Air conditioner | |
| JP2574488B2 (en) | Heat exchanger | |
| JPH0531432Y2 (en) | ||
| JPH10267462A (en) | Evaporator | |
| JP2002350002A (en) | Condenser | |
| JP3158509B2 (en) | Refrigerant condenser | |
| JPH0642885Y2 (en) | Refrigerator Evaporator | |
| JPH06129732A (en) | Refrigerant condenser |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |