EP1608928A1 - Heat exchanger tubes - Google Patents
Heat exchanger tubesInfo
- Publication number
- EP1608928A1 EP1608928A1 EP04721949A EP04721949A EP1608928A1 EP 1608928 A1 EP1608928 A1 EP 1608928A1 EP 04721949 A EP04721949 A EP 04721949A EP 04721949 A EP04721949 A EP 04721949A EP 1608928 A1 EP1608928 A1 EP 1608928A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tube
- channels
- tube according
- channel
- ratio
- 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.)
- Granted
Links
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
- F28D1/053—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 the conduits being straight
- F28D1/0535—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 the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
- F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel 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
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
-
- 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
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
- F28F1/045—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular with assemblies of stacked elements
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0073—Gas coolers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
- F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded
Definitions
- the present invention relates to heat exchanger tub&s, and in particular to heat exchanger tubes for use in automotive heat exchangers, particularly ⁇ automotive HVAC heat exchangers.
- Carbon dioxide has been shown to be one of the most promising candidates for an environmentally friendly refrigerant.
- CO 2 has " been used before the adoption of CFC refrigerant and it is still used as a refrigerant in deep freezing industry today. Due to the particular thermophysical properties of carbon dio xide (its low critical temperature of about 31 °C), however, when used for mobile air conditioning, it has to be operated, in a transcritical cycle in most mobile air conditioning usage, when the ambient air temperature is likely to be high. Thus in a mobile C0 2 air conditioning system, the heat exchanger that dissipates heat to the ambient air (also known as gas cooler) has to operate in a high pressure supercritical state, usually over 10O " bar.
- the present invention provides a substantially flat tube for an automotive heat exchanger, the tube comprising a plurality of flow channels extending in ttie longitudinal direction of the tube, the channels having substantially non-circular cros s- sectional geometry.
- the present invention provides flat tube designs with non-circular cross-section channel geometry, that are narrow to reduce airside pressure drop, strong to withstand high pressur-e, of light weight and that also offer higher heat conductance and lower pressure drop compared to flat tube with circular cross-section channel with the same tube cross-section size.
- the tube is extruded, the channels preferably being formed in the extrusion process.
- the tube is preferably used in an HVAC gas cooler having a working fluid operating in a substantially supercritical state.
- the tube material is aluminium.
- thue refrigerant is C0 2 .
- the ratio of the maximum channel dimension in section in the tube minor axis direction to the txibe minor axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress: H/Ltminor ⁇ A ⁇ yeild /( ⁇ yeild + Pburst);
- .A is a safety factor and A ⁇ 1.
- the ratio of the sum of the length of all the channel widths to the tube major axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress:
- B is a safety factor and B ⁇ 1.
- Figure 1 is a schematic sectional view of a tube in accordance with a first embodiment of tlie invention (triangular cross-section channels);
- Figure 2 is a graphic representation of effects on channel width on performance compared with a comparable circular section channel tube
- Figure 3 is a schematic sectional view of a tube in accordance with a second embodiment of the invention (rectangular cross-section channels);
- Figure 4 is a graphic representation of effect on channel width for the second embodiment of tube (rectangular section channels) compared with a comparable circular section channel tub «;
- Figure 5 is a schematic sectional view of a tube in accordance with a further embodiment of the invention (waisted rectangular cross-section channel);
- Figure 6 is a graphic representation of effect on channel width for the further embodiment of the invention compared to a comparable circular section channel tube; and Figure 7 is a graphic comparison between refrigerant temperature in a triangular cross-section channel tube and a comparable circular cross-section channel tube.
- a heat exchange tube (1) typically of extruded aluminium material is provided with a series of substantially parallel working fluid (refrigerant) channels 2.
- working fluid typically the tubes extend between headers and are stacked in a row having air-gaps between adjacent tubes.
- An airway or fin matrix may be provided in thermal contact with adjacent spaced tubes in order to maximise heat transfer.
- the heat exchanger is brazed together.
- One of the prefened realisations of the indention is a flat tube 1 with multiple channels 2 of triangular cross-section.
- the second realisation is a flat tube of multiple channels of rectangular cross-section and yet a third realisation is a flat tube of multiple channels with a shape modified from rectangular cross-section.
- the performance of the three realisations are compared to the benchmark round channel flat tubes under the same overall tube cross-section size.
- the maximum channel dimension in the tube minor axis direction is fixed as the same as the round channel diameter.
- the variation of the total heat conductance for each tube, incorporating a typical airside surface design and airside flow condition, and of the pressure drop through one tube, for a fixed tube length, are calculated with the variation of the channel width.
- the merits of each design are judged by these two performance parameters compared to the benchmark circular cro ss-section channel flat tube.
- the maximisation of total channel cross- section area needs also to result in a tube design having sufficient structural robustness. Therefore, the maximum dimension of the channel in the tube minor axis direction should be no more than a fixed fraction of the tube minor axis dimension. Similarly, over any intersection line between the tube end surface and any plane perpendicular to the tube end surface, the ratio of the total length falling into the channels to the total line length should not be greater than a fixed fraction. The exact value of these fraction numbers should ideally be a function of the desired burst pressure an trie yield stress of the tube material.
- Figure 7 shows the result of the refrigerant temperatures in a flat tube of prefened triangular channel and in a benchmark circular cross-section channel flat tube. It can be seen that prefened triangular channel tube is more effective and cools the refrigerant to the same extent as a circular cross-section channel tube of a third longer length. For the same length, the new triangular channel tube will give a heat transfer rate about 7°/ ⁇ higher.
- Figure 3 shows the second realisation with rectangular channel.
- the total channel cross-section area is increased by 27% compared to the benchmark round channel case and conespondingly the weight of the tube is reduced significantly.
- the limitation on the two ratios as discussed in first realisation still t ⁇ olds.
- the performance of the flat tube of the second realisation versus the channel width, compared again to the benchmark round channel tube is shown in Figure 4.
- the optimal performance range, offering better or equivalent under the same or much lower pressure drop, is 0.5 ⁇ w H ⁇ 2.2.
- a further and third realisation is schematically shown in Figure 5.
- the rectangular channel in the second realisation is modified to improve structural robustness of the rectangular channel. This design still offers weight reduction compared to the benchmark round channel flat tube. To maintain the structural robustness, again the limitation on the two ratios a_s discussed in first realisation still holds.
- the ratio of the maximum channel dimension in section in the tube minor axis direction to the tube minor axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress:
- A is a safety factor and A ⁇ 1.
- the ratio of the sum of the length of alL the channel widths to the tube major axis dimension is less than a factor of the ratio between. the bursting pressure and the tube material yield stress:
- B is a safety factor and B ⁇ 1.
Abstract
A substantially flat tube (1) for an automotive heat exchanger, the tube (1) comprising a plurality of flow channels (2) extending in the longitudinal direction of the tube (1), the channels (2) having substantially non-circular cross-sectional geometry.
Description
Heat Exchanger- Tubes
The present invention relates to heat exchanger tub&s, and in particular to heat exchanger tubes for use in automotive heat exchangers, particularly^ automotive HVAC heat exchangers.
Automotive air-conditioning industry has been experiencing significant changes in recent years due to environmental concerns. Concerns about the damaging impact of the ctiloro flurocarbon refrigerant (CFC) to the ozone layer have led to its complete replacement by the hydro flurocarbon refrigerant (HFC) R134a. Althiough HFC refrigerant is known to have limited ozone depleting effects, it still has a significantly high global warming potential, about 1 ,300 times higher than carbon dioxide gas of the same amount. This is increa.singly becoming environmentally unacceptable. Such environmental pressure has led to international treaties, protocols and proposed, legislation in some countries to either ban completely the use of HFC refrigerants over a short period of time, or to penalise its usage by levying a hefty environmental tax. Therefore, increased efforts and investment have been made by the automotive industry to seek new alternative refrig&xants, which can eliminate or alleviate the environmental impacts of mobile HVAC system.
Carbon dioxide has been shown to be one of the most promising candidates for an environmentally friendly refrigerant. CO2 has "been used before the adoption of CFC refrigerant and it is still used as a refrigerant in deep freezing industry today. Due to the particular thermophysical properties of carbon dio xide (its low critical temperature of about 31 °C), however, when used for mobile air conditioning, it has to be operated, in a transcritical cycle in most mobile air conditioning usage, when the ambient air temperature is likely to be high. Thus in a mobile C02 air conditioning system, the heat exchanger that dissipates heat to the ambient air (also known as gas cooler) has to operate in a high pressure supercritical state, usually over 10O "bar. Its operation in supercritical state also means that in part of the gas cooler the temperature tends to be very high and that the refrigerant temperature varies significantly (known as temperature slide) througlx the gas cooler.
It is known that in a transcritical air-conditioning cycle, the cooling capacity and energy efficiency, known as coefficient of performance, which is defined as the ratio of cooling capacity to the power consumed, depends stroixgly on high gas cooler effectiveness and low gas cooler pressure loss. This can only be realized through careful refrigerant tube design and optimal combination of tube with the airside heat transfer surfaces such as louvered airways.
Flat tubes with multiple circular section geometry channels have been designed for both tlie conventional and CO2 air conditioning systems. While the circular section geometry chanttel offers good strength characteristics, it is not most effective in maximizing heat transfer conductance for the same tube cross-section.
An improved arrangement has now been devised.
According to a first aspect, the present invention provides a substantially flat tube for an automotive heat exchanger, the tube comprising a plurality of flow channels extending in ttie longitudinal direction of the tube, the channels having substantially non-circular cros s- sectional geometry.
The present invention provides flat tube designs with non-circular cross-section channel geometry, that are narrow to reduce airside pressure drop, strong to withstand high pressur-e, of light weight and that also offer higher heat conductance and lower pressure drop compared to flat tube with circular cross-section channel with the same tube cross-section size.
It is preferred that the tube is extruded, the channels preferably being formed in the extrusion process. The tube is preferably used in an HVAC gas cooler having a working fluid operating in a substantially supercritical state. Preferably the tube material is aluminium. Preferably thue refrigerant is C02.
For optimum performance, it has been found that the ratio of the maximum channel dimension in section in the tube minor axis direction to the txibe minor axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress:
H/Ltminor <A σyeild /(σyeild + Pburst);
where .A is a safety factor and A < 1.
For optimum performance, it has also been found that the ratio of the sum of the length of all the channel widths to the tube major axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress:
Swi/Ltmajor < B σyeild /(σ;yeild + Pburst);
where B is a safety factor and B < 1.
The invention will now be further described, in specific embodiments, by way of example only and with reference to the accompanying drawings, in which:
Figure 1 is a schematic sectional view of a tube in accordance with a first embodiment of tlie invention (triangular cross-section channels);
Figure 2 is a graphic representation of effects on channel width on performance compared with a comparable circular section channel tube;
Figure 3 is a schematic sectional view of a tube in accordance with a second embodiment of the invention (rectangular cross-section channels);
Figure 4 is a graphic representation of effect on channel width for the second embodiment of tube (rectangular section channels) compared with a comparable circular section channel tub«;
Figure 5 is a schematic sectional view of a tube in accordance with a further embodiment of the invention (waisted rectangular cross-section channel);
Figure 6 is a graphic representation of effect on channel width for the further embodiment of the invention compared to a comparable circular section channel tube; and
Figure 7 is a graphic comparison between refrigerant temperature in a triangular cross-section channel tube and a comparable circular cross-section channel tube.
In the embodiment refened to, a heat exchange tube (1), typically of extruded aluminium material is provided with a series of substantially parallel working fluid (refrigerant) channels 2. Typically the tubes extend between headers and are stacked in a row having air-gaps between adjacent tubes. An airway or fin matrix may be provided in thermal contact with adjacent spaced tubes in order to maximise heat transfer. Typically, where aluminium is used, the heat exchanger is brazed together.
One of the prefened realisations of the indention is a flat tube 1 with multiple channels 2 of triangular cross-section. The second realisation is a flat tube of multiple channels of rectangular cross-section and yet a third realisation is a flat tube of multiple channels with a shape modified from rectangular cross-section.
The performance of the three realisations are compared to the benchmark round channel flat tubes under the same overall tube cross-section size. The maximum channel dimension in the tube minor axis direction is fixed as the same as the round channel diameter. The variation of the total heat conductance for each tube, incorporating a typical airside surface design and airside flow condition, and of the pressure drop through one tube, for a fixed tube length, are calculated with the variation of the channel width. The merits of each design are judged by these two performance parameters compared to the benchmark circular cro ss-section channel flat tube.
To achieve light weight, under a fixed overall tube cross-section, it is necessary to maximize total channel cross-section area, this maximisation of total channel area also helps in reducing the refrigerant pressure drop. Compared to the benchmark circular cross-section channel tube, all three realisations result in increased total channel cross-section area and therefore provide a lighter tube design.
The maximisation of total channel cross- section area needs also to result in a tube design having sufficient structural robustness. Therefore, the maximum dimension of the channel in
the tube minor axis direction should be no more than a fixed fraction of the tube minor axis dimension. Similarly, over any intersection line between the tube end surface and any plane perpendicular to the tube end surface, the ratio of the total length falling into the channels to the total line length should not be greater than a fixed fraction. The exact value of these fraction numbers should ideally be a function of the desired burst pressure an trie yield stress of the tube material.
The performance of this realisation, compared to the round channel case, is shown in Figure 2. It shows that for a fixed tube width illustrated here, a channel width (triangle base dimension) greater than 0.5 mm offers improved heat transfer conductance at the same or very slight increase in pressure drop. Considering, however, the structural requirements, the ratio of channel width to the triangle height should be limited by a maximum of about 3. Thus the optimal range of channel dimension should give 30° < oc < 65°.
To verify the prefened triangular channel design, some three dimension CFD simulations have been done to compare with the benchmark round channel flat tube. Figure 7 shows the result of the refrigerant temperatures in a flat tube of prefened triangular channel and in a benchmark circular cross-section channel flat tube. It can be seen that prefened triangular channel tube is more effective and cools the refrigerant to the same extent as a circular cross-section channel tube of a third longer length. For the same length, the new triangular channel tube will give a heat transfer rate about 7°/ό higher.
Figure 3 shows the second realisation with rectangular channel. In this realisation the total channel cross-section area is increased by 27% compared to the benchmark round channel case and conespondingly the weight of the tube is reduced significantly. To maintain the structural robustness, the limitation on the two ratios as discussed in first realisation still tαolds.
As in Figure 2, the performance of the flat tube of the second realisation versus the channel width, compared again to the benchmark round channel tube is shown in Figure 4. The optimal performance range, offering better or equivalent under the same or much lower pressure drop, is 0.5 < w H <2.2.
A further and third realisation is schematically shown in Figure 5. The rectangular channel in the second realisation is modified to improve structural robustness of the rectangular channel. This design still offers weight reduction compared to the benchmark round channel flat tube. To maintain the structural robustness, again the limitation on the two ratios a_s discussed in first realisation still holds.
The performance of the flat tube of the third realisation versus the channel width is shown in Figure 6. Again a optimal ratio of channel width to the maximum channel height is identified as between 0.6 and 1.6.
In general, for optimum performance, it has been found that the ratio of the maximum channel dimension in section in the tube minor axis direction to the tube minor axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress:
H/Ltminor <A σyeild /(σyeild + Pburst);
where A is a safety factor and A < 1.
For optimum performance, it has also been found that the ratio of the sum of the length of alL the channel widths to the tube major axis dimension is less than a factor of the ratio between. the bursting pressure and the tube material yield stress:
Swi/Ltmajor < B σyeild /(σyeild + Pburst);
where B is a safety factor and B < 1.
Claims
1. A substantially flat tube for an automotive heat exchanger, the tube comprising a plurality of flow channels extending in the longitudinal direction of the tube, the channels having substantially non-circular cross-sectional geometry.
2. A tube according to claim 1, Λvherein the tube is extruded.
3. A tube according to claim 1 or claim 2, used in an HVAC gas cooler having a working fluid operating in a substantially supercritical state.
4. A tube according to any preceding claim used in an HVAC gas cooler having CO2 as a working fluid operating in a substantially supercritical state-
5. A tube according to any preceding claim, wherein the tube is o f aluminium material.
6. A tube according to any preceding claim, wherein the minor axis dimension of the tube is substantially in the range 1 mm to 2.5 mm.
7. A tube according to any preceding claim, wherein the ratio of the maximum channel dimension in section in the tube minor axis direction to the tube minor axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield stress:
H/Ltminor <A σyeild /(σyeild + Pburst);
where A is a safety factor and A < 1.
8. A tube according to any preceding claim, wherein the ratio of the sum of the length of all the channel widths to the tube major axis dimension is less than a factor of the ratio between the bursting pressure and the tube material yield, stress: Swi/Ltmajor < B σyeild /(σyeild + Pburst);
where B is a safety factor and B < 1.
9. A tube according to any preceding claim, wherein the operational pressure of the fluid in the tube is substantially at or above 100 bar.
10. A tube according to any preceding claim., wherein the channels comprise substantially triangular section channels.
11. A tube according to claim 10, wherein the substantially triangular section channels are arranged in tessellating relationship substantially side-by-side in a row.
12. A tube according to claim 10 or claim 11, wherein the triangular section of the channels confonns substantially to an isosceles triangle with the conesp onding base angles (o ) substantially in the range 30° ≤ < 65°.
13. A tube according to any of claims 1 to 10, wherem the channels comprise substantially rectangular section channels.
14. A tube according to claim 13, wherein the channel width (w) to height (H) ratio is substantially in the range 0.5 < w/H ≤ 2.2.
15. A tube according to any of claims 1 to 10, wherein the channels comprise channels conforming substantially to a rectangular section having nanowed waisted mid- channel along its width.
16. A tube according to claim 15, wherein the ratio of channel width (w) to maximum channel height (H) is substantially in the range 0.6 < w/H < 1.6.
17. An automotive heat exchanger including a plurality of spaced tubes according to any preceding claim.
18. An extruded aluminium tube for an automotive air conditioning heat exchauiger, the tube comprising a plurality of spaced flow channels formed by extrusion of the tube and extending in the longitudinal direction of the tube, the channels having substantially non-circular cross-sectional geometry.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0306269A GB2399623A (en) | 2003-03-19 | 2003-03-19 | Flat tube heat exchanger for a vehicle air conditioning system |
| GB0306269 | 2003-03-19 | ||
| PCT/GB2004/001215 WO2004083762A1 (en) | 2003-03-19 | 2004-03-19 | Heat exchanger tubes |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1608928A1 true EP1608928A1 (en) | 2005-12-28 |
| EP1608928B1 EP1608928B1 (en) | 2010-09-29 |
Family
ID=9955060
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP04721949A Expired - Fee Related EP1608928B1 (en) | 2003-03-19 | 2004-03-19 | Method for providing flat tube designs for an automotive heat exchanger |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP1608928B1 (en) |
| DE (1) | DE602004029338D1 (en) |
| GB (1) | GB2399623A (en) |
| WO (1) | WO2004083762A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3492853A1 (en) * | 2017-11-29 | 2019-06-05 | Lennox Industries Inc. | Microchannel heat exchanger |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005016540A1 (en) * | 2005-04-08 | 2006-10-12 | Behr Gmbh & Co. Kg | Multichannel flat tube |
| EP1983272A1 (en) * | 2007-04-18 | 2008-10-22 | Aic S.A. | Fired heat exchanger bundle |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2694080B1 (en) * | 1992-07-24 | 1996-06-21 | Furukawa Electric Co Ltd | FLAT AND POROUS CONDENSER TUBE. |
| JP3113100B2 (en) * | 1992-11-05 | 2000-11-27 | 株式会社デンソー | Multi-hole tube extrusion die and multi-hole tube |
| JPH06300473A (en) * | 1993-04-19 | 1994-10-28 | Sanden Corp | Flat refrigerant pipe |
| JPH0972680A (en) * | 1995-09-05 | 1997-03-18 | Akutoronikusu Kk | Structure of porous flat tube and manufacture thereof |
| JPH1144498A (en) | 1997-05-30 | 1999-02-16 | Showa Alum Corp | Flat porous tube for heat exchanger and heat exchanger using the tube |
| US6216776B1 (en) * | 1998-02-16 | 2001-04-17 | Denso Corporation | Heat exchanger |
| JP2000046421A (en) * | 1998-07-27 | 2000-02-18 | Calsonic Corp | Heat exchanger for carbon dioxide refrigeration cycle |
| DE19845336A1 (en) | 1998-10-01 | 2000-04-06 | Behr Gmbh & Co | Multi-channel flat tube |
| DE19921407A1 (en) * | 1999-05-08 | 2000-11-09 | Behr Gmbh & Co | Tubular panel structure for heat exchanger has pre-positioned solder in grooves at mid-point between adjacent chambers, reducing subsequent assembly costs |
-
2003
- 2003-03-19 GB GB0306269A patent/GB2399623A/en not_active Withdrawn
-
2004
- 2004-03-19 DE DE602004029338T patent/DE602004029338D1/en not_active Expired - Lifetime
- 2004-03-19 WO PCT/GB2004/001215 patent/WO2004083762A1/en active Application Filing
- 2004-03-19 EP EP04721949A patent/EP1608928B1/en not_active Expired - Fee Related
Non-Patent Citations (1)
| Title |
|---|
| See references of WO2004083762A1 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3492853A1 (en) * | 2017-11-29 | 2019-06-05 | Lennox Industries Inc. | Microchannel heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2399623A (en) | 2004-09-22 |
| EP1608928B1 (en) | 2010-09-29 |
| DE602004029338D1 (en) | 2010-11-11 |
| GB0306269D0 (en) | 2003-04-23 |
| WO2004083762A1 (en) | 2004-09-30 |
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