JP2002062077A - Refrigerant tube for heat exchanger - Google Patents
Refrigerant tube for heat exchangerInfo
- Publication number
- JP2002062077A JP2002062077A JP2001202455A JP2001202455A JP2002062077A JP 2002062077 A JP2002062077 A JP 2002062077A JP 2001202455 A JP2001202455 A JP 2001202455A JP 2001202455 A JP2001202455 A JP 2001202455A JP 2002062077 A JP2002062077 A JP 2002062077A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- refrigerant pipe
- heat exchanger
- fins
- tube
- 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
- 239000003507 refrigerant Substances 0.000 title claims abstract description 90
- 230000002093 peripheral effect Effects 0.000 claims abstract description 9
- 238000001816 cooling Methods 0.000 claims abstract description 6
- 238000012546 transfer Methods 0.000 abstract description 8
- 230000000694 effects Effects 0.000 abstract description 3
- 238000000034 method Methods 0.000 abstract description 3
- 238000004519 manufacturing process Methods 0.000 description 6
- 239000007788 liquid Substances 0.000 description 4
- 238000002474 experimental method Methods 0.000 description 3
- 238000007796 conventional method Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 238000010008 shearing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は熱交換器の冷媒管に
係り、特に管の内周面に多数のフィンが螺旋状に突出
し、冷媒が流れながら熱交換される空気調和器用熱交換
器の冷媒管に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant pipe for a heat exchanger, and more particularly to a heat exchanger for an air conditioner, in which a number of fins project spirally from the inner peripheral surface of the pipe and heat is exchanged while a refrigerant flows. It relates to a refrigerant pipe.
【０００２】[0002]
【従来の技術】一般的な空気調和器用熱交換器は、図３
に示すように、内部に冷媒が流れる冷媒管１１と、前記
冷媒管１１が貫いた状態に取り付けられた多数の冷却フ
ィン３とからなり、前記冷媒管１１を流れる冷媒と冷媒
管１１の周囲の空気とが熱交換されるように構成されて
いる。2. Description of the Related Art A general heat exchanger for an air conditioner is shown in FIG.
As shown in FIG. 3, the refrigerant pipe 11 includes a refrigerant pipe 11 through which a refrigerant flows, and a number of cooling fins 3 attached in a state where the refrigerant pipe 11 penetrates. It is configured to exchange heat with air.
【０００３】従来の熱交換器に用いられる冷媒管１１
は、図４及び図５に示すように、７ｍｍまたは９ｍｍの
外径を有し、その内周面に多数のフィン１３が突出し、
前記フィン１３同士の間にグルーブがそれぞれ設けら
れ、前記フィン１３とグルーブ１５によって冷媒管１１
内部の熱伝達面積が増大し、温度境界層が撹乱され、冷
媒管１１を流れる冷媒と冷媒管１１の周囲の空気との熱
交換を促進させる。[0003] Refrigerant pipe 11 used in a conventional heat exchanger
Has an outer diameter of 7 mm or 9 mm as shown in FIG. 4 and FIG.
Grooves are respectively provided between the fins 13, and the refrigerant tubes 11 are formed by the fins 13 and the grooves 15.
The internal heat transfer area increases, the temperature boundary layer is disturbed, and heat exchange between the refrigerant flowing through the refrigerant pipe 11 and the air around the refrigerant pipe 11 is promoted.
【０００４】即ち、前記フィン１３とグルーブ１５によ
って液状または蒸気状の冷媒と接触する冷媒管１１の面
積が増大し、低流速の冷媒においても毛細管効果と剪断
力によって管内に形成された液膜の乱流の強度も増加し
て熱交換効果が増大するが、前記フィン１３の個数及び
形状によって、冷媒と管壁面との接触面積、液膜の乱流
化度及び液膜の膜厚などが可変される。[0004] That is, the area of the refrigerant pipe 11 contacting the liquid or vapor state refrigerant is increased by the fins 13 and the grooves 15, and the liquid film formed in the pipe by the capillary effect and the shearing force even in the low flow rate refrigerant. Although the intensity of turbulence also increases and the heat exchange effect increases, the contact area between the refrigerant and the pipe wall, the degree of turbulence of the liquid film, the film thickness of the liquid film, etc. are variable depending on the number and shape of the fins 13. Is done.
【０００５】従って、前記冷媒管１１を製造する際に
は、前記フィン１３がそれぞれの用途に合わせて最適化
されるようにフィンの個数、フィンの高さ、フィンの突
出角、フィンのねじれ角などの加工変数を選定しなけれ
ばならない。前記フィンの形状を設計する方式には定型
化されたものが未だ存在していないので、実験によって
最適の組合を見出す方式で行われている実情である。Therefore, when manufacturing the refrigerant pipe 11, the number of the fins, the height of the fins, the projection angle of the fins, and the twist angle of the fins are set so that the fins 13 are optimized for each application. Processing variables such as must be selected. Since there is no standardized method for designing the shape of the fin, a method for finding an optimal combination by an experiment is used.
【０００６】つまり、前記フィンは各加工変数を変更し
ながら行う実験によって冷媒量や冷媒の種類、外部環境
などの熱交換器の使用条件から最適の組合を見出す方式
で設計されている。このような方式で設計された従来の
熱交換器に用いられる冷媒管１１は、７ｍｍまたは９ｍ
ｍの外径と０.２７ｍｍの管厚ｔ1を有するように形成さ
れたもので、その内周面に突出しているフィン１３は６
０個からなり、０.１５ｍｍの高さＨ1、５６°の突出角
β1、１８°のねじれ角α1を有する。In other words, the fins are designed in such a manner that an optimum combination is found from the use conditions of the heat exchanger such as the amount of the refrigerant, the type of the refrigerant, the external environment, and the like, by experiments performed while changing each processing variable. The refrigerant pipe 11 used in the conventional heat exchanger designed in this manner has a diameter of 7 mm or 9 m.
m having an outer diameter of 0.2 m and a tube thickness t 1 of 0.27 mm.
It has a height H 1 of 0.15 mm, a projection angle β 1 of 56 ° and a twist angle α 1 of 18 °.
【０００７】ところで、最近、熱交換器の製造コストと
空気側の圧力損失を低減させるために、前記冷媒管１１
の外径を縮小して製造する必要性が台頭している。しか
し、前記冷媒管１１の外径を縮小しながら、従来の冷媒
管１１に形成していたフィン１３の形状をそのまま適用
すると、むしろ前記冷媒の圧力損失が増加して熱交換効
率が低減するだけでなく、フィン１３が加工可能な寸法
を外れてしまい冷媒管１１の製造が難しくなるという問
題がある。Recently, in order to reduce the production cost of the heat exchanger and the pressure loss on the air side, the refrigerant pipe 11
There is an increasing need to reduce the outer diameter. However, if the shape of the fins 13 formed in the conventional refrigerant pipe 11 is applied as it is while reducing the outer diameter of the refrigerant pipe 11, the pressure loss of the refrigerant is increased and the heat exchange efficiency is reduced. In addition, there is a problem that the dimensions of the fins 13 deviate from the dimensions that can be processed, which makes it difficult to manufacture the refrigerant pipe 11.
【０００８】また、上述した従来の熱交換器に用いられ
る冷媒管１１は、冷媒を代替冷媒に変更する場合を考慮
せずに設計したものなので、前記冷媒を変更すれば、冷
媒の圧力損失及び熱伝達係数が変化され、性能を十分発
揮できなくなるという問題がある。従って、前記冷媒管
の外径を縮小させながら、前記冷媒管に設けられたフィ
ンの形状及び個数を最適化することにより、冷媒の圧力
損失を低減させると共に熱伝達係数のような熱伝達性能
を向上させることができる冷媒管の開発が求められる。Further, since the refrigerant pipe 11 used in the above-described conventional heat exchanger is designed without considering the case where the refrigerant is changed to an alternative refrigerant, if the refrigerant is changed, the pressure loss and the pressure loss of the refrigerant will be reduced. There is a problem that the heat transfer coefficient is changed and the performance cannot be sufficiently exhibited. Therefore, by optimizing the shape and number of the fins provided in the refrigerant pipe while reducing the outer diameter of the refrigerant pipe, the pressure loss of the refrigerant is reduced and the heat transfer performance such as the heat transfer coefficient is improved. There is a need to develop a refrigerant pipe that can be improved.
【０００９】[0009]
【発明が解決しようとする課題】本発明はかかる問題点
を解決するためのもので、その目的は冷媒管の外径を縮
小させながら、冷媒管の内周面に突出しているフィンを
縮小された外径の冷媒管に最も適するように形成するこ
とにより、熱交換器のコスト低減及び小型化と空気側の
圧力損失減少のような細径管の長所を有すると共に、熱
伝達効率を向上させて熱交換性能を極大化させることが
可能な冷媒管を提供することにある。SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and has as its object to reduce the outer diameter of the refrigerant tube while reducing the fins projecting from the inner peripheral surface of the refrigerant tube. By forming it most suitable for a refrigerant pipe with a reduced outer diameter, it has the advantages of a small-diameter pipe such as a reduction in cost and size of the heat exchanger and a reduction in pressure loss on the air side, and an improvement in heat transfer efficiency. And to provide a refrigerant pipe capable of maximizing heat exchange performance.
【００１０】[0010]
【課題を解決するための手段】上記目的を達成するため
の本発明では、多数の冷却フィンが結合され、冷媒と空
気とを熱交換させる熱交換器の冷媒管において、前記冷
媒管は５.３ｍｍ以下の外径を有し、内周面に多数のフ
ィンが螺旋状に突設されている。According to the present invention, in order to achieve the above-mentioned object, in a refrigerant pipe of a heat exchanger in which a number of cooling fins are connected to exchange heat between a refrigerant and air, the refrigerant pipe is composed of 5. It has an outer diameter of 3 mm or less, and has a number of fins projecting spirally on the inner peripheral surface.
【００１１】また、本発明に係る冷媒管は０.１６ｍｍ
〜０.２ｍｍの管厚を有する。また、本発明に係る冷媒
管は、内周面に突出しているフィンの個数が４０〜５０
個、フィンのねじれ角が６〜２０°、フィンの高さが
０.１５〜０.１８ｍｍ、フィンの突出角が３８〜４２°
である。The refrigerant pipe according to the present invention has a diameter of 0.16 mm.
Has a tube thickness of ~ 0.2 mm. Further, in the refrigerant pipe according to the present invention, the number of fins projecting from the inner peripheral surface is 40 to 50.
The fin has a torsion angle of 6 to 20 °, a fin height of 0.15 to 0.18 mm, and a fin protrusion angle of 38 to 42 °
It is.
【００１２】[0012]
【発明の実施の形態】以下、本発明の実施例を添付図に
基づいて説明する。図１は本発明に係る熱交換器の冷媒
管構造を示す一部切欠図、図２は本発明に係る冷媒管を
拡大して示す一部断面図である。図１及び図２に示すよ
うに、本発明による熱交換器の冷媒管では、多数の冷却
フィン（図示せず）を貫いた状態に取り付けられた冷媒
管において、前記冷媒管５１は５.３ｍｍ以下の外径を
有し、内周面に多数のフィン５３が突出しており、前記
フィン５３同士の間にグルーブ５５がそれぞれ形成され
ている。DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is a partially cutaway view showing a refrigerant pipe structure of a heat exchanger according to the present invention, and FIG. 2 is a partially sectional view showing an enlarged refrigerant pipe according to the present invention. As shown in FIG. 1 and FIG. 2, in the refrigerant pipe of the heat exchanger according to the present invention, the refrigerant pipe 51 is 5.3 mm in a refrigerant pipe mounted so as to penetrate a number of cooling fins (not shown). A large number of fins 53 have the following outer diameter and protrude from the inner peripheral surface. Grooves 55 are formed between the fins 53, respectively.
【００１３】ここで、前記冷媒管５１は０.１６〜０.２
ｍｍの管厚ｔを有するように形成され、前記フィン５３
は冷媒管５１の内周面に４０〜５０個突設されると共
に、ねじれ角（α）６〜２０°、高さ（Ｈ）０.１５〜
０．１８ｍｍ、突出角（β）３８〜４２°を有する。前
記フィンのねじれ角αは６〜１０°もしくは１６〜２０
°とすることが好ましい。Here, the refrigerant pipe 51 has a diameter of 0.16 to 0.2.
fin 53
Are protruded from the inner peripheral surface of the refrigerant pipe 51, and the torsion angle (α) is 6 to 20 ° and the height (H) is 0.15 to
0.18 mm, with a projection angle (β) of 38-42 °. The twist angle α of the fin is 6 to 10 ° or 16 to 20
° is preferable.
【００１４】このような本発明による冷媒管を用いた熱
交換器では、冷媒管５１の外径が５.３ｍｍに縮小され
て７ｍｍまたは９ｍｍの管径を有する冷媒管を使用した
熱交換器に比べて、同一冷媒流量における冷媒側圧力損
失が増加し且つ管厚ｔが減少するので、このような冷媒
側圧力損失及び管厚ｔの減少を考慮し、縮小された外径
の冷媒管に適するようにフィン５３が設計された。その
結果、実験により、前記冷媒管５１の冷媒側圧力損失が
減少して熱交換性能が向上し、冷媒管５１製造時のフィ
ンの公差管理が可能となることが分った。In the heat exchanger using the refrigerant pipe according to the present invention, the outer diameter of the refrigerant pipe 51 is reduced to 5.3 mm, and the heat exchanger using the refrigerant pipe having a pipe diameter of 7 mm or 9 mm is used. In comparison, since the refrigerant-side pressure loss at the same refrigerant flow rate increases and the tube thickness t decreases, the refrigerant-side pressure loss and the decrease in the tube thickness t are taken into consideration, so that the refrigerant tube is suitable for a refrigerant tube having a reduced outer diameter. The fin 53 was designed as follows. As a result, it was found from an experiment that the pressure loss on the refrigerant side of the refrigerant pipe 51 was reduced, the heat exchange performance was improved, and the fin tolerance during the production of the refrigerant pipe 51 could be managed.
【００１５】また、前記冷媒管５１の構造を同一にした
状態で冷媒を代替冷媒に変更しても、その圧力損失及び
熱伝達係数が変化するので、代替冷媒の使用も考慮して
前記フィン５３の形状が設計された。Further, even if the refrigerant is changed to the alternative refrigerant with the same structure of the refrigerant pipe 51, the pressure loss and the heat transfer coefficient are changed. The shape was designed.
【００１６】[0016]
【発明の効果】以上説明したように、本発明による熱交
換器の冷媒管は、冷媒管の外径が縮小され、縮小された
外径の冷媒管に適するようにフィンが形成され、熱交換
器の製造コストの低減及び小型化と空気側の圧力損失減
少のような細径管の長所を全て生かしながら、前記冷媒
管による熱伝達効率を向上させて熱交換の性能を極大化
させる利点がある。特に、本発明による冷媒管は、細径
管に適した形態でフィンが設計され、前記フィンによる
冷媒側圧力損失が最小化されると共に、冷媒管製造時の
公差管理が容易であるという利点がある。As described above, in the refrigerant tube of the heat exchanger according to the present invention, the outer diameter of the refrigerant tube is reduced, and the fin is formed so as to be suitable for the refrigerant tube having the reduced outer diameter. It has the advantage of improving the heat transfer efficiency by the refrigerant tube and maximizing the heat exchange performance, while taking advantage of all the advantages of the small-diameter tube such as reduction of the manufacturing cost and miniaturization of the vessel and reduction of the pressure loss on the air side. is there. In particular, the refrigerant tube according to the present invention has the advantage that the fin is designed in a form suitable for a small-diameter tube, the refrigerant-side pressure loss due to the fin is minimized, and the tolerance management during the production of the refrigerant tube is easy. is there.
【図１】本発明の実施形態による熱交換器の冷媒管構造
を示す一部切欠図である。FIG. 1 is a partially cutaway view showing a refrigerant pipe structure of a heat exchanger according to an embodiment of the present invention.
【図２】本発明の実施形態による熱交換器の冷媒管を拡
大して示す一部断面図である。FIG. 2 is an enlarged partial cross-sectional view showing a refrigerant pipe of the heat exchanger according to the embodiment of the present invention.
【図３】一般的な熱交換器を示す斜視図である。FIG. 3 is a perspective view showing a general heat exchanger.
【図４】従来の技術による熱交換器の冷媒管構造を示す
一部切欠図である。FIG. 4 is a partially cutaway view showing a refrigerant pipe structure of a heat exchanger according to a conventional technique.
【図５】従来の技術による熱交換器の冷媒管を拡大して
示す一部断面図である。FIG. 5 is an enlarged partial cross-sectional view showing a refrigerant pipe of a heat exchanger according to a conventional technique.
５１…冷媒管 ５３…フィン ５５…グルーブ ｔ…冷媒管の管厚 Ｈ…フィンの高さ α…フィンのねじれ角 β…フィンの突出角 51: refrigerant pipe 53: fin 55: groove t: thickness of refrigerant pipe H: height of fin α: twist angle of fin β: projection angle of fin
───────────────────────────────────────────────────── フロントページの続き (72)発明者 オー セ ヨーン 大韓民国，ソウル 158−077，ヤンチュン −ク，シンチュン７−ドン 326，モクド ン アパートメント ナンバー1204−506 (72)発明者 リー ウーク ヨン 大韓民国，キュンキ−ド 423−060，クワ ンミュン−シ，ハーン−ドン，チュコン アパートメント ナンバー1008−909 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor O-Se-Young, Republic of Korea, Seoul 158-077, Yangchun-ku, Sinchon 7-Don 326, Mokdong Apartment No. 1204-506 (72) Inventor Lee Wook-yong, Korea, Kunki -De 423-060, Kwangmung-Shi, Haan-Don, Chukon Apartment No. 1008-909
Claims (5)
れる冷媒と周辺の空気とを熱交換させる熱交換器の冷媒
管において、 前記冷媒管は５.３ｍｍ以下の外径を有し、内周面に多
数のフィンが螺旋状に突出していることを特徴とする熱
交換器の冷媒管。1. A refrigerant pipe of a heat exchanger, in which a number of cooling fins are connected to exchange heat between a refrigerant flowing therein and surrounding air, wherein the refrigerant pipe has an outer diameter of 5.3 mm or less. A refrigerant tube for a heat exchanger, wherein a number of fins project spirally on a peripheral surface.
厚を有することを特徴とする請求項１記載の熱交換器の
冷媒管。2. The refrigerant pipe according to claim 1, wherein the refrigerant pipe has a thickness of 0.16 to 0.2 mm.
個数は４０〜５０個、フィンの高さは０.１５〜０．１
８ｍｍ、フィンの突出角は３８〜４２°、フィンのねじ
れ角は６〜２０°であることを特徴とする請求項１記載
の熱交換器の冷媒管。3. The number of fins protruding from the inner surface of the refrigerant pipe is 40 to 50, and the height of the fins is 0.15 to 0.1.
The refrigerant pipe of a heat exchanger according to claim 1, wherein the fin has a protrusion angle of 38 to 42 degrees and a fin twist angle of 6 to 20 degrees.
ることを特徴とする請求項３記載の熱交換器の冷媒管。4. The refrigerant pipe according to claim 3, wherein the fin has a twist angle of 6 to 10 °.
あることを特徴とする請求項３記載の熱交換器の冷媒
管。5. The refrigerant pipe according to claim 3, wherein the fin has a twist angle of 16 to 20 °.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR38501/2000 | 2000-07-06 | ||
| KR10-2000-0038501A KR100382341B1 (en) | 2000-07-06 | 2000-07-06 | Heat exchanger |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2004006819U Continuation JP3110197U (en) | 2000-07-06 | 2004-11-22 | Refrigerant tube of heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002062077A true JP2002062077A (en) | 2002-02-28 |
Family
ID=19676520
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001202455A Pending JP2002062077A (en) | 2000-07-06 | 2001-07-03 | Refrigerant tube for heat exchanger |
| JP2004006819U Expired - Lifetime JP3110197U (en) | 2000-07-06 | 2004-11-22 | Refrigerant tube of heat exchanger |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2004006819U Expired - Lifetime JP3110197U (en) | 2000-07-06 | 2004-11-22 | Refrigerant tube of heat exchanger |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20020011332A1 (en) |
| JP (2) | JP2002062077A (en) |
| KR (1) | KR100382341B1 (en) |
| CN (1) | CN1188652C (en) |
| ES (1) | ES2228189A1 (en) |
| IT (1) | ITRM20010384A1 (en) |
| TW (1) | TW526322B (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100885499B1 (en) * | 2002-07-15 | 2009-02-26 | 한라공조주식회사 | Heat exchanger |
| US10683865B2 (en) | 2006-02-14 | 2020-06-16 | Air Squared, Inc. | Scroll type device incorporating spinning or co-rotating scrolls |
| US11047389B2 (en) | 2010-04-16 | 2021-06-29 | Air Squared, Inc. | Multi-stage scroll vacuum pumps and related scroll devices |
| US20130232975A1 (en) | 2011-08-09 | 2013-09-12 | Robert W. Saffer | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
| US20140224464A1 (en) * | 2012-06-05 | 2014-08-14 | Golden Dragon Precise Copper Tube Group Inc. | Enhanced condensation heat-transfer tube |
| WO2014175928A2 (en) * | 2013-04-23 | 2014-10-30 | Air Squared, Inc. | Compact energy cycle construction utilizing some combination of a scroll type expander, pump, and compressor for operating according to a rankine, an organic rankine, heat pump, or combined organic rankine and heat pump cycle |
| US10508543B2 (en) | 2015-05-07 | 2019-12-17 | Air Squared, Inc. | Scroll device having a pressure plate |
| US10865793B2 (en) | 2016-12-06 | 2020-12-15 | Air Squared, Inc. | Scroll type device having liquid cooling through idler shafts |
| CN111886459A (en) * | 2018-03-20 | 2020-11-03 | 三菱电机株式会社 | Heat exchanger, refrigeration cycle device, and air conditioner |
| US11454241B2 (en) | 2018-05-04 | 2022-09-27 | Air Squared, Inc. | Liquid cooling of fixed and orbiting scroll compressor, expander or vacuum pump |
| US20200025199A1 (en) | 2018-07-17 | 2020-01-23 | Air Squared, Inc. | Dual drive co-rotating spinning scroll compressor or expander |
| US11067080B2 (en) | 2018-07-17 | 2021-07-20 | Air Squared, Inc. | Low cost scroll compressor or vacuum pump |
| US11530703B2 (en) | 2018-07-18 | 2022-12-20 | Air Squared, Inc. | Orbiting scroll device lubrication |
| US11473572B2 (en) | 2019-06-25 | 2022-10-18 | Air Squared, Inc. | Aftercooler for cooling compressed working fluid |
| CN111141068A (en) * | 2020-02-21 | 2020-05-12 | 顺德职业技术学院 | Condenser with variable-pipe-diameter composite tooth-shaped internal thread reinforced pipe |
| CN111156745A (en) * | 2020-02-21 | 2020-05-15 | 顺德职业技术学院 | Variable-pipe-diameter composite-tooth-shaped internal thread reinforced pipe evaporator |
| US11898557B2 (en) | 2020-11-30 | 2024-02-13 | Air Squared, Inc. | Liquid cooling of a scroll type compressor with liquid supply through the crankshaft |
| US11885328B2 (en) | 2021-07-19 | 2024-01-30 | Air Squared, Inc. | Scroll device with an integrated cooling loop |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0723115B2 (en) * | 1986-07-24 | 1995-03-15 | 海洋科学技術センタ− | Submarine object collection device |
| JPH01299707A (en) * | 1988-05-27 | 1989-12-04 | Sumitomo Light Metal Ind Ltd | Manufacture of small and thin wall thickness heat transfer tube |
| MY110330A (en) * | 1991-02-13 | 1998-04-30 | Furukawa Electric Co Ltd | Heat-transfer small size tube and method of manufacturing the same |
| JPH08174044A (en) * | 1994-12-28 | 1996-07-09 | Kobe Steel Ltd | Production of small-diameter heat transfer tube with groove on inside surface |
| JPH09101093A (en) * | 1995-10-02 | 1997-04-15 | Mitsubishi Shindoh Co Ltd | Heat transfer pipe with inner surface groove |
-
2000
- 2000-07-06 KR KR10-2000-0038501A patent/KR100382341B1/en not_active IP Right Cessation
-
2001
- 2001-07-03 IT IT2001RM000384A patent/ITRM20010384A1/en unknown
- 2001-07-03 JP JP2001202455A patent/JP2002062077A/en active Pending
- 2001-07-05 ES ES200101568A patent/ES2228189A1/en active Pending
- 2001-07-05 CN CNB011200235A patent/CN1188652C/en not_active Expired - Fee Related
- 2001-07-06 US US09/899,101 patent/US20020011332A1/en not_active Abandoned
- 2001-07-06 TW TW090116555A patent/TW526322B/en not_active IP Right Cessation
-
2004
- 2004-11-22 JP JP2004006819U patent/JP3110197U/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| CN1188652C (en) | 2005-02-09 |
| ITRM20010384A1 (en) | 2002-01-07 |
| ES2228189A1 (en) | 2005-04-01 |
| KR20020004526A (en) | 2002-01-16 |
| TW526322B (en) | 2003-04-01 |
| KR100382341B1 (en) | 2003-05-01 |
| ITRM20010384A0 (en) | 2001-07-03 |
| CN1332356A (en) | 2002-01-23 |
| JP3110197U (en) | 2005-06-16 |
| US20020011332A1 (en) | 2002-01-31 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2002062077A (en) | Refrigerant tube for heat exchanger | |
| JP2534450B2 (en) | Heat exchanger tubes | |
| US20040194935A1 (en) | Heat Exchanger | |
| JP2004019999A (en) | Heat exchanger with fin, and manufacturing method therefor | |
| JPH0961081A (en) | Fin for integral type heat exchanger | |
| JP2002235993A (en) | Spiral fin tube and refrigeration air conditioning device | |
| JPH02166394A (en) | Heat exchanger with fin | |
| JP2001251079A (en) | Method for producing heat sink using heat pipe and method for producing heat pipe | |
| KR20030088169A (en) | Heat exchanger | |
| JP3747974B2 (en) | Internal grooved heat transfer tube | |
| KR20140013752A (en) | Heat exchanger and method for manufacturing thereof | |
| KR20010108605A (en) | Louver fin of heat exchanger | |
| JPH04260792A (en) | Small-diameter heat transfer tube | |
| JPH0734949B2 (en) | Heat transfer tube manufacturing method | |
| JP2003021485A (en) | Fin tube heat exchanger | |
| KR100357131B1 (en) | heat-exechanger is made up of pipe is formed of small diameter | |
| KR20040087308A (en) | A tube for heat exchange with a capillary-type heat pipe | |
| JP2603224Y2 (en) | Heat exchanger | |
| KR100468397B1 (en) | A Falling Film Enhanced Tub | |
| KR200368444Y1 (en) | Heat exchange pipe with fin having prominence and depression part | |
| JPS63197886A (en) | Finned heat exchanger | |
| JPS59202397A (en) | Internally grooved pipe and manufacture thereof | |
| JPH07109354B2 (en) | Heat exchanger | |
| KR20030065942A (en) | Tube of heat exchanger | |
| JPH11270980A (en) | Heat transfer pipe for evaporator |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20040106 |
|
| A601 | Written request for extension of time |
Free format text: JAPANESE INTERMEDIATE CODE: A601 Effective date: 20040405 |
|
| A602 | Written permission of extension of time |
Free format text: JAPANESE INTERMEDIATE CODE: A602 Effective date: 20040408 |
|
| A521 | Request for written amendment filed |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20040706 |
|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20040824 |