CN102112839B - Grooved tube for heat exchanger - Google Patents
Grooved tube for heat exchanger Download PDFInfo
- Publication number
- CN102112839B CN102112839B CN2009801301592A CN200980130159A CN102112839B CN 102112839 B CN102112839 B CN 102112839B CN 2009801301592 A CN2009801301592 A CN 2009801301592A CN 200980130159 A CN200980130159 A CN 200980130159A CN 102112839 B CN102112839 B CN 102112839B
- Authority
- CN
- China
- Prior art keywords
- heat
- heat exchanger
- ridge
- heat sink
- pipe
- 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.)
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Links
- 229910000881 Cu alloy Inorganic materials 0.000 claims abstract description 7
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 claims description 16
- 229910002092 carbon dioxide Inorganic materials 0.000 claims description 8
- 239000001569 carbon dioxide Substances 0.000 claims description 8
- 230000006835 compression Effects 0.000 claims description 4
- 238000007906 compression Methods 0.000 claims description 4
- 238000005057 refrigeration Methods 0.000 description 8
- 230000006378 damage Effects 0.000 description 6
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 5
- 229910052802 copper Inorganic materials 0.000 description 4
- 239000010949 copper Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000005764 inhibitory process Effects 0.000 description 2
- 230000008719 thickening Effects 0.000 description 2
- 239000012080 ambient air Substances 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 239000012467 final product Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
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
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
- B21C1/00—Manufacture of metal sheets, metal wire, metal rods, metal tubes by drawing
- B21C1/16—Metal drawing by machines or apparatus in which the drawing action is effected by other means than drums, e.g. by a longitudinally-moved carriage pulling or pushing the work or stock for making metal sheets, bars, or tubes
- B21C1/22—Metal drawing by machines or apparatus in which the drawing action is effected by other means than drums, e.g. by a longitudinally-moved carriage pulling or pushing the work or stock for making metal sheets, bars, or tubes specially adapted for making tubular articles
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D17/00—Forming single grooves in sheet metal or tubular or hollow articles
-
- 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
Abstract
The present invention discloses a grooved tube for a heat exchanger, wherein the grooved tube for a heat exchanger is made of 0.2% of a copper alloy having proof strength of 40 N/mm2 or more and is configured so as to satisfy the relationship of 8<bN/t<20, wherein b is the width of each of the heat sink strips, N is the number of the heat sink strips, and t is the bottom wall thickness of each of the grooves.
Description
Technical field
The present invention relates to a kind of grooved tube for heat exchanger, the measure that the groove when particularly how to suppress expander damages.
Background technology
Up to now, the heat-transfer pipe as the heat exchanger (so-called tube type heat exchanger) of refrigerating plant etc. uses to be formed with a plurality of grooves on pipe internal surface in order to improve the tube having inner surface trough of heat transfer property more.For example, on the inner surface of the tube having inner surface trough of patent documentation 1, be formed with the heat sink strip of a lot of spiral extensions on tube axial direction, be formed with groove between these heat sink strips.Thus, compare than the so-called smooth tubes that there is no heat sink strip or groove, pipe internal surface is long-pending to be increased, and heat transfer effect is promoted.
Patent documentation 1: Japanese Laid-Open Patent communique Unexamined Patent 8-174044 communique
Summary of the invention
-invent technical problem to be solved-
Yet when the assembled heat interchanger, the tube having inner surface trough that passes many fin plates in order to allow is adjacent to fin plate, and expander is inserted in tube having inner surface trough with instrument, and tube having inner surface trough is carried out expander.When this, the heat sink strip top of pipe internal surface is subject to expander with the extruding of instrument, can be destroyed.
At this, when the critical pressure that the high pressure that is used in kind of refrigeration cycle when tube having inner surface trough surpasses cold-producing medium is so-called supercritical refrigeration cycle, its operating pressure is high when being used in subcritical refrigeration cycle than this tube having inner surface trough, think that the intensity of guaranteeing pipe just needs to increase thickness.Yet if increase thickness, the expander power in the time of certainly will increasing expander again will cause that thus the pipe internal surface heat sink strip can suffer larger destruction.The problem of obvious damage heat transfer property will appear in its result.
The present invention completes in view of above each point.Its purpose is: the grooved pipe (tube having inner surface trough) that the inhibition heat exchanger is used is because expander destroys heat sink strip.
-be the technical solution problem technical scheme-
The invention of first aspect is to reach the grooved tube for heat exchanger of a plurality of ridges adjacent with this groove as prerequisite to form a plurality of grooves on inner surface.And grooved tube for heat exchanger of the present invention is by 0.2% endurance 40N/mm
2Above copper alloy is made, and the relation between the cardinal extremity width b of described ridge, described ridge quantity N and described thickness of groove bottom t satisfies 8＜bN/t＜20.
In described invention, because used the endurance copper alloy higher than existing phosphorized copper as material, so can reduce thickness of groove bottom t (valley bottom thickness t as shown in Figure 3) for identical design pressure (fluid pressure in pipe).Having, in the present invention, is to form the relation of ridge cardinal extremity width b, ridge quantity N (being the quantity of groove) and thickness of groove bottom t before expander to satisfy bN/t greater than 8 and less than 20 grooved pipe again.As shown in Figure 6, have this relation by making it, the ridge after expander (heat sink strip) height is with respect to the ratio (h/h of the ridge before expander (heat sink strip) height
0) be about more than 0.8.That is to say, suppressed the ridge damage degree that expander causes.
The invention of second aspect is in the invention of described first aspect, is used in carbon dioxide and reaches in the refrigerating circuit of the steam compression type refrigerating circulation more than the critical pressure of carbon dioxide as the cold-producing medium high pressure that circulates.
In described invention, carrying out high pressure in refrigerating circuit, to reach overcritical pressure be so-called supercritical steam cycle.Therefore, the grooved pipe design pressure of heat exchanger uprises.Even if this situation also can reduce the thickness of groove bottom t of grooved pipe, the relation of 8＜bN/t＜20 is easily set up.
-invention effect-
Therefore, according to the present invention, be 40N/mm because be with 0.2% endurance
2Above copper alloy is made, so can reduce thickness of groove bottom t, because be that the relation that constitutes between ridge cardinal extremity width b, ridge quantity N and thickness of groove bottom t satisfies 8＜bN/t＜20, wreck so really suppress ridge (heat sink strip) in the time of can carrying out expander at the pipe to any size again.
At this, according to Fig. 6, wreck for suppressing the ridge height, as long as increase as much as possible described bN/t.Thick t is determined by design pressure due to the pipe diapire, so in order to increase bN/t, as long as increase ridge cardinal extremity width b and ridge quantity N.Yet if increase ridge cardinal extremity width b, pipe internal surface is long-pending to diminish, and heat transfer property will reduce; And if increase ridge quantity N, pipe internal surface is long-pending can be increased, but can cause weight to increase and the pressure loss increases.So in the present invention, the viewpoint that is damaged from suppressing the ridge height is set as the value of bN/t greater than 8; From guaranteeing that suitable pipe internal surface is long-pending and suppress the viewpoint that weight increases and the pressure loss increases, the value of bN/t is set as less than 20.Therefore, according to the present invention, guaranteeing that suitably pipe internal surface is long-pending and not causing in the scope that weight increases and the pressure loss increases, really can suppress ridge and wreck.Its result can provide heat transfer property high grooved pipe, and then the heat exchanger that uses this grooved pipe is provided.
Also have, as the invention of second aspect, compare with the situation that is used in common subcritical refrigeration cycle, carry out the refrigerating circuit of supercritical refrigeration cycle in the situation that be used in the carbon dioxide circulation, high pressure is higher, design pressure is also high, but can suppress thickness of groove bottom t thickening, and the relation of 8＜bN/t＜20 is necessarily set up.Thus, just can suppress ridge wrecks.Its result just can access high heat-transfer performance.
Description of drawings
Fig. 1 means the heat-transfer pipe rip cutting profile that embodiment is related.
Fig. 2 means the heat-transfer pipe crosscut profile that embodiment is related.
Fig. 3 means the crosscut profile at the heat-transfer pipe main position that embodiment is related.
Fig. 4 means enlarged areas rate and the hot curve map that transmits promotion rate relation in evaporimeter.
Fig. 5 means enlarged areas rate and the hot curve map that transmits promotion rate relation in radiator.
Fig. 6 means that bN/t and heat sink strip height change are than the curve map of relation.
-symbol description-
1 heat-transfer pipe (grooved tube for heat exchanger);
2 grooves;
3 heat sink strips (ridge)
The specific embodiment
Below, describe embodiments of the present invention in detail based on accompanying drawing.In addition, following embodiment is preferred example in essence, has no intention to limit the present invention and applicable thing thereof, or its purposes scope.
The grooved tube for heat exchanger of present embodiment, as the heat-transfer pipe use of the heat exchanger (so-called section of jurisdiction type heat exchanger) that is arranged at refrigerating plant etc., cold-producing medium is in internal flow.Flow through the cold-producing medium of this grooved tube for heat exchanger (hereinafter referred to as heat-transfer pipe 1), and flow through pipe ambient air or water and carry out heat exchange and evaporate or condensation.Also have, the heat-transfer pipe 1 of present embodiment is used for carbon dioxide carries out the refrigerating circuit of steam compression type refrigerating circulation as refrigerant circulation radiator or evaporimeter.And this refrigerating circuit is to carry out high pressure to be compressed to the above supercritical refrigeration cycle of the critical pressure of carbon dioxide.
As Fig. 1～shown in Figure 3, be formed with a plurality of heat sink strips 3 that extend spirally along tube axial direction on the inner surface of described heat-transfer pipe 1.This heat sink strip 3 constitutes section and forms the mountain top shape ridge that the top attenuates.And, be formed with adjacent groove 2 between described each heat sink strip 3.The section of this groove 2 forms inverted trapezoidal.These grooves 2 and heat sink strip 3, parallel formation, and with respect to only the tilt helical pitch angle [alpha] of regulation of tube axial direction.
At this, in the process of the heat exchanger that assembling is used as radiator or evaporimeter, closely engage with fin plate for making the described heat-transfer pipe 1 that has passed many fin plates, with expanding tool, heat-transfer pipe 1 is carried out the expander operation.The heat sink strip 3 of heat-transfer pipe 1 inner surface more or less can suffer the destruction of this expander operation.Particularly, under the supercritical steam cycle condition, high pressure is very high, think the intensity of guaranteeing heat-transfer pipe 1, just be necessary to make valley bottom thickness t (with reference to Fig. 3) thicker than common subcritical cycle situation.If in the time of can making the expander operation so again, necessary expander power increases, heat sink strip 3 further wrecks, and heat transfer property significantly descends.
So the heat-transfer pipe 1 of present embodiment is to be 40N/mm with 0.2% endurance
2Above copper alloy is made.That is to say, the material that the heat-transfer pipe 1 of present embodiment uses is endurance than existing material: the good material of phosphorized copper (C1220-OL).Thus, just can reduce valley bottom thickness t for identical design pressure (flowing through the design pressure of the cold-producing medium of heat-transfer pipe 1).
Also have, the relation that the heat-transfer pipe 1 of present embodiment constitutes between the valley bottom thickness t of heat sink strip width b, heat sink strip 3 quantity N and groove 2 satisfies 8＜bN/t＜20.Heat sink strip width b consists of ridge cardinal extremity width involved in the present invention.The quantity N of heat sink strip 3 consists of ridge quantity involved in the present invention.Valley bottom thickness t consists of base thickness degree involved in the present invention.
As shown in Figure 6, by above formation, because expander makes the variation ratio of heat sink strip height h for approximately more than 0.8.This changes ratio, is heat sink strip height h after the expander heat sink strip height h before than expander
0(h/h
0), its value is larger namely more near " 1 ", has been subject to inhibition with regard to representing the degree that the heat sink strip height wrecks.Value at bN/t approximately reaches in 10 these scopes, and this changes than (h/h
0) proportionally increase with this value, should change than (h/h afterwards
0) substantially certain.Like this, by bN/t being set as than 8 large values, just can suitably suppress expander to the destruction of heat sink strip 3.Thus, reduction that just can the killer tube internal surface area, and then suppress the reduction of heat transfer property.
Its result as Fig. 4 and shown in Figure 5, is compared with the heat-transfer pipe under the prior art that is formed by phosphorized copper, can improve heat and transmit promotion rate η.Specifically, in arbitrary heat exchanger of evaporimeter (Fig. 4) and radiator (Fig. 5), although compare with the enlarged areas rate σ (shown in enclosing in vain in figure) before expander, heat-transfer pipe 1 enlarged areas rate σ after expander (in figure black triangle shown in) has reduced, but it is like that little not reduce to heat-transfer pipe under prior art (in figure shown in stain).That is, compared with prior art, can suppress the reduction of enlarged areas rate σ.Therefore, also just can suppress the reduction that heat is transmitted promotion rate η.In addition, enlarged areas rate σ is the long-pending increment rate of amassing as the pipe internal surface of benchmark of pipe internal surface take the smooth tubes of slotless.Therefore, the enlarged areas rate σ before expander is the highest.And the heat transmission promotion rate η of heat-transfer pipe 1 is heat transfer property, and is basic and enlarged areas rate σ is in direct ratio.
Also have, the value that makes bN/t is less than 20 the reasons are as follows.Wreck in order to suppress the heat sink strip height, as shown in Figure 6, set the value of bN/t to such an extent that get final product more greatly as much as possible.Because valley bottom thickness t is determined by design pressure, so will set bN/t larger, will increase in fact the quantity N of heat sink strip width b and heat sink strip.Yet if heat sink strip width b is increased, pipe internal surface is long-pending to diminish, and heat transfer property will reduce.And if the quantity N of heat sink strip is increased, pipe internal surface is long-pending to be increased, but can cause weight to increase and the pressure loss increases.So, in present embodiment, amass and suppress the viewpoint that weight increases and the pressure loss increases from guaranteeing suitable pipe internal surface, the value of bN/t is set as less than 20.In addition, the value of the phosphorized copper heat-transfer pipe bN/t under prior art is set at more than 20.
The effect of-embodiment-
According to present embodiment as above, be to be 40N/mm with 0.2% endurance
2Above copper alloy is made, so can reduce valley bottom thickness t, also have, the quantity N and the valley bottom thickness t that constitute heat sink strip width b, heat sink strip satisfy the relation of 8＜bN/t＜20, so guaranteed that suitably pipe internal surface amasss and within not causing weight increase and pressure loss increase scope, can positively suppress heat sink strip 3 and wreck.Its result just can provide the high heat-transfer pipe of heat transfer property 1, and then the heat exchanger of evaporimeter and radiator etc. is provided.
Also have, be used for the carbon dioxide circulation and carry out the refrigerating circuit of supercritical refrigeration cycle, also uprise than the design pressure of the high pressure high heat transfer pipe 1 of common subcritical refrigeration cycle, but can valley bottom thickness t thickening.Thus, just can effectively suppress the fail in compression of heat sink strip 3.Its result just can obtain high heat-transfer performance.
Practicality on-industry-
In sum, the present invention is useful to the grooved tube for heat exchanger that has a plurality of grooves on inner surface.
Claims (2)
1. a grooved tube for heat exchanger, be formed with a plurality of grooves and a plurality of ridge on the inner surface of this grooved tube for heat exchanger, and described groove and described ridge are arranged alternately, and it is characterized in that:
This grooved pipe is 40N/mm by 0.2% yield strength
2Above copper alloy is made,
In order to suppress because expander destroys ridge, the quantity N of the cardinal extremity width b of described ridge, described ridge and described thickness of groove bottom t satisfy and concern 8＜bN/t＜20.
2. grooved tube for heat exchanger according to claim 1 is characterized in that:
This grooved tube for heat exchanger is used for carbon dioxide as the refrigerating circuit of the circulation of the steam compression type refrigerating more than the critical pressure that cold-producing medium circulates, high pressure reaches carbon dioxide.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2008-200582 | 2008-08-04 | ||
| JP2008200582A JP5446163B2 (en) | 2008-08-04 | 2008-08-04 | Grooved tube for heat exchanger |
| PCT/JP2009/003554 WO2010016198A1 (en) | 2008-08-04 | 2009-07-28 | Grooved tube for heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102112839A CN102112839A (en) | 2011-06-29 |
| CN102112839B true CN102112839B (en) | 2013-06-05 |
Family
ID=41663427
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009801301592A Active CN102112839B (en) | 2008-08-04 | 2009-07-28 | Grooved tube for heat exchanger |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US20110132589A1 (en) |
| EP (1) | EP2320188A4 (en) |
| JP (1) | JP5446163B2 (en) |
| KR (1) | KR20110031241A (en) |
| CN (1) | CN102112839B (en) |
| AU (1) | AU2009278653B2 (en) |
| WO (1) | WO2010016198A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103765152A (en) * | 2011-08-04 | 2014-04-30 | 株式会社Uacj | Seamless pipe, level wound coil, cross fin tube-type heat exchanger, and method for producing cross fin tube-type heat exchanger |
| KR101881659B1 (en) * | 2016-11-14 | 2018-07-24 | 경희대학교 산학협력단 | Heat transfer tube having rare-earth oxide superhydrophobic surface and manufacturing method therefor |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1148686A (en) * | 1995-07-12 | 1997-04-30 | 三洋电机株式会社 | Heat exchanger of refrigerating circulation |
| JP2000199023A (en) * | 1999-01-07 | 2000-07-18 | Mitsubishi Materials Corp | Electric resistance welded copper alloy tube for heat exchanger excellent in 0.2% proof stress and fatigue strength |
| CN2622656Y (en) * | 2003-04-03 | 2004-06-30 | 河南金龙精密铜管股份有限公司 | Slim tooth internal thread seamoless high efficiency heat transfer tube |
| JP3964244B2 (en) * | 2002-03-27 | 2007-08-22 | 株式会社コベルコ マテリアル銅管 | Internal grooved tube |
| JP2007271123A (en) * | 2006-03-30 | 2007-10-18 | Kobelco & Materials Copper Tube Inc | Inner face-grooved heat transfer tube |
| JP2008020166A (en) * | 2006-07-14 | 2008-01-31 | Kobelco & Materials Copper Tube Inc | Inner surface grooved heat-transfer tube for evaporator |
| CA2474558C (en) * | 2002-03-12 | 2011-03-08 | Trefimetaux | Slotted tube with reversible usage for heat exchangers |
Family Cites Families (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2839662B2 (en) * | 1990-07-12 | 1998-12-16 | 株式会社東芝 | High thermal conductive copper alloy and heat exchanger using this copper alloy |
| MY110330A (en) * | 1991-02-13 | 1998-04-30 | Furukawa Electric Co Ltd | Heat-transfer small size tube and method of manufacturing the same |
| US6164370A (en) * | 1993-07-16 | 2000-12-26 | Olin Corporation | Enhanced heat exchange tube |
| US5381600A (en) * | 1993-10-06 | 1995-01-17 | Ford Motor Company | Heat exchanger and method of making the same |
| JPH085278A (en) * | 1994-06-20 | 1996-01-12 | Mitsubishi Shindoh Co Ltd | Heat transfer tube with inner surface grooves |
| JPH08174044A (en) | 1994-12-28 | 1996-07-09 | Kobe Steel Ltd | Production of small-diameter heat transfer tube with groove on inside surface |
| JP3794341B2 (en) * | 2002-03-28 | 2006-07-05 | 株式会社コベルコ マテリアル銅管 | Internal grooved tube and manufacturing method thereof |
| JP4096824B2 (en) * | 2003-06-19 | 2008-06-04 | 株式会社デンソー | Vapor compression refrigerator |
| JP4339665B2 (en) * | 2003-10-31 | 2009-10-07 | 住友軽金属工業株式会社 | Manufacturing method of heat exchanger |
| DE102006013384B4 (en) * | 2006-03-23 | 2009-10-22 | Wieland-Werke Ag | Use of a heat exchanger tube |
| JP5006155B2 (en) * | 2006-10-19 | 2012-08-22 | 古河電気工業株式会社 | Heat transfer tube |
| ES2427863T3 (en) * | 2008-04-24 | 2013-11-04 | Mitsubishi Electric Corporation | Heat exchanger and air conditioning that uses the same |
-
2008
- 2008-08-04 JP JP2008200582A patent/JP5446163B2/en active Active
-
2009
- 2009-07-28 EP EP09804685.7A patent/EP2320188A4/en not_active Withdrawn
- 2009-07-28 CN CN2009801301592A patent/CN102112839B/en active Active
- 2009-07-28 AU AU2009278653A patent/AU2009278653B2/en active Active
- 2009-07-28 US US13/057,304 patent/US20110132589A1/en not_active Abandoned
- 2009-07-28 WO PCT/JP2009/003554 patent/WO2010016198A1/en active Application Filing
- 2009-07-28 KR KR1020117003585A patent/KR20110031241A/en not_active Application Discontinuation
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1148686A (en) * | 1995-07-12 | 1997-04-30 | 三洋电机株式会社 | Heat exchanger of refrigerating circulation |
| JP2000199023A (en) * | 1999-01-07 | 2000-07-18 | Mitsubishi Materials Corp | Electric resistance welded copper alloy tube for heat exchanger excellent in 0.2% proof stress and fatigue strength |
| CA2474558C (en) * | 2002-03-12 | 2011-03-08 | Trefimetaux | Slotted tube with reversible usage for heat exchangers |
| JP3964244B2 (en) * | 2002-03-27 | 2007-08-22 | 株式会社コベルコ マテリアル銅管 | Internal grooved tube |
| CN2622656Y (en) * | 2003-04-03 | 2004-06-30 | 河南金龙精密铜管股份有限公司 | Slim tooth internal thread seamoless high efficiency heat transfer tube |
| JP2007271123A (en) * | 2006-03-30 | 2007-10-18 | Kobelco & Materials Copper Tube Inc | Inner face-grooved heat transfer tube |
| JP2008020166A (en) * | 2006-07-14 | 2008-01-31 | Kobelco & Materials Copper Tube Inc | Inner surface grooved heat-transfer tube for evaporator |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5446163B2 (en) | 2014-03-19 |
| CN102112839A (en) | 2011-06-29 |
| US20110132589A1 (en) | 2011-06-09 |
| AU2009278653A1 (en) | 2010-02-11 |
| JP2010038417A (en) | 2010-02-18 |
| EP2320188A1 (en) | 2011-05-11 |
| KR20110031241A (en) | 2011-03-24 |
| AU2009278653B2 (en) | 2013-02-07 |
| EP2320188A4 (en) | 2014-03-12 |
| WO2010016198A1 (en) | 2010-02-11 |
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| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |