CN1624413A - Flow duct - Google Patents
Flow duct Download PDFInfo
- Publication number
- CN1624413A CN1624413A CN200410096811.2A CN200410096811A CN1624413A CN 1624413 A CN1624413 A CN 1624413A CN 200410096811 A CN200410096811 A CN 200410096811A CN 1624413 A CN1624413 A CN 1624413A
- Authority
- CN
- China
- Prior art keywords
- pipeline
- heat exchanger
- fin
- projection
- fluid
- 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
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
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
Abstract
The present invention relates to a duct for conducting a flowing primary fluid, having a thermally conductive wall with exterior ribs having an exterior side through which a secondary fluid can pass, at least partially, whereby the duct wall comprises a structured surface on its exterior side in addition to the ribs. The invention further relates to a heat exchanger with an inventive duct and an air condenser, particularly a natural-draught condenser, with inventive heat exchangers.
Description
Technical field
The present invention relates to pipeline, heat exchanger and aerial condenser.
Background technology
In various fluids are used, i.e. liquid, gas or the mixture of the two, for example water, steam or air are used for transfer heat.Heat transmitter is also referred to as heat exchanger, is used for heat is sent to transportation and storage medium.Heat exchanger has a pipeline usually at least, carries first fluid by this pipeline, hereinafter referred to as elementary fluid.Elementary fluid sees through tube wall and environment carries out heat exchange.Environment can be the parts that directly link to each other, and also can be second fluid, for the purpose of difference, hereinafter referred to as secondary fluid.
In power station technology, elementary fluid is hot water or steam normally, and be guided the primary side of heat exchanger, is also referred to as steam side, and is for example inner.And secondary fluid normally is centered around the gas of heat exchanger outside (air side or primary side) and circulation.In the case, it is external that tube wall removes the guiding primary flow, also is used for carrying out between elementary fluid and secondary fluid heat exchange.
The heat exchanger that has extraordinary pipeline has multiple use in the field, power station, can be used for extracting rudimental energy from the elementary fluid of handling through heat energy, and then cool off elementary fluid.For example, the heat exchanger in the aerial condenser is used for from turbine waste vapour recovery boiler water.Behind turbine, condense into water in the heat exchanger of steam in aerial condenser, water is back to boiler again.Finish boiler water cycle like this.
Heat exchanger used existing plumbing installation in power station comprises the smooth tube wall of inner surface usually, and is less so that elementary fluid is met the resistance in road when flowing in pipeline.In this way, can farthest reduce the mobile required energy of the elementary fluid of maintenance.This type of heat-exchanger pipeline generally has fin (ribs) so that increase the heat transfer sheet area in the outside of contact secondary fluid.These fins normally are welded to the aluminum strip of outer surface of tube body.Body reaches the aluminium lamination that wraps up at least outside by withstand voltage steel pipe usually and forms.
Ducted fluid may be in laminar flow or turbulent condition, and flow regime is decided according to the stickiness and the other factors of mean flow rate, pipeline section shape, elementary fluid.Elementary fluid laminar boundary layer appears at the tube wall district, even also be like this in turbulent condition.Because this boundary layer, the heat exchange between elementary fluid and the tube wall is only just fully carried out in the zone near tube wall.Therefore, most heat of providing of elementary fluid can not be used effectively.
So DESCRIPTION OF THE PRIOR ART will provide obstacle in pipeline, destroy laminar flow, form turbulent flow, the better mixing of independent elementary fluid components of flow is provided.Can realize significant improvement in this way to the utilization of primary flow body heat content.But the result can cause the remarkable increase of pipeline flow resistance.Therefore, elementary fluid is flowed and keep the required expenditure of flow regime to enlarge markedly.This has significant negative effect in hot spiral and heat exchanger, because efficient obviously descends.
The optimal performance of heat exchanger is decided according to the flow resistance in transferable heat, the heat-exchanger pipeline and other factors.This causes the demand of flowing relation in the heat exchanger conflict to occur.In other words, in order farthest to reduce flow losses, wish that ducted fluid major part is a laminar flow, and little part there is deviation.On the other hand, wish to have turbulent flow, because turbulent flow can make the heat exchange performance of elementary fluid better.
Existing heat exchanger only partly satisfies these demands.The heat exchanger that occurs the little pressure loss owing to its most laminar flow has only a spot of heat exchange usually, and therefore, most heat of the elementary fluid of process distributes very slowly.On the other hand, with its tangible turbulent flow and the heat exchanger that may have a good heat exchange ability depends on the first fluid that possesses high pressure, high pressure can compensate pipe interior extraneous component or structure (forming different turbulent flows) and the big pressure loss that causes.Usually need provide the device that increases pressure, for example compressor, pump etc.
Summary of the invention
The objective of the invention is to be a kind of extraordinary pipeline of heat exchanger designs, under the situation that little pressure reduces, improve the heat exchange between the secondary fluid outside the elementary fluid and pipeline in the pipeline.
Realize this goal by the pipeline of claim 1 indication, the heat exchanger of claim 13 indication and the aerial condenser of claim 16 indication.Preferred development sources is to dependent claims.
Therefore, the present invention proposes to be used to guide the pipeline of band tube wall of primary flow body of flowing, and heat exchanges between elementary fluid and tube wall.The tube wall of high-termal conductivity also has extra patterned surface at its outer surface that contacts secondary fluid originally except that traditional fin.
Therefore, suppose it is smooth inwall, heat exchange occurs between elementary fluid and the tube wall.Compare with existing pipeline, heat exchanger and aerial condenser, can significantly reduce the pressure loss in the elementary fluid.By the heat exchange on the pipeline external surface (strengthen even surmount by the turbulent flow in the secondary fluid), compensation originally exchanges relevant initial minimizing with the primary flow body heat.By forming the structure of turbulent flow, the secondary fluid between the fin is through expressly stronger mixing, thereby increased the heat exchange between elementary fluid and the secondary fluid.
In power station heat exchanger or air can condensers, thisly dispose significant especially positive influences, for example cooling stack in this device, adopts the very little air of internal friction as secondary fluid usually.In cooling stack and industrial heat exchanger, flowing by similar self-forming strengthens these positive influences, and under the help of physical effect, air can show these characteristics usually; As a result, form turbulent surface texture and can also can not require to improve the thrust of pump the significant negative effect of mobile generation of secondary fluid.Therefore, if heat exchanger adopts the pipeline of this design, can ignore expensive devices such as pump in the primary flow body loop.Under lower production cost, the performance of this contrive equipment thereby be able to remarkable lifting.
Can all or partly dispose the surface texture that forms turbulent flow at the fin of pipeline, or only the outer wall area between cooling fin is configured.Importantly these structures are not simple fins, but spread all over the raised or sunken fillet structure of pipeline external surface.This special shape has the following advantages: form very low flow resistance relatively, but generate good turbulent flow simultaneously in secondary fluid.
At first, this mode can be improved the demand of conflicting that has of heat exchange between convection cell and the tube wall.Based on patterned surface, have slightly at elementary fluid under the situation of pressure decline, might significantly promote thermal heat transfer capability.
By patterned surface, can increase the turbulent flow of tube wall zone secondary fluid, thereby improve heat transmission.Can also reduce the boundary layer in the outer wall area.Simultaneously, with the position of uniqueness be shaped as the basis, can to greatest extent turbulent flow be reduced to the degree that the pressure loss in the secondary fluid can obviously not increase.
Can form patterned surface by tube wall self or by coating.But preferably the fin by pipeline forms patterned surface.For example, can suppress fin, all form patterned surface in both sides.Tube wall, fin or coating can have high friction coefficient for secondary fluid, so that form necessary turbulent flow.The fluid that the characteristic of tube wall and the character of patterned surface help passing through, thereby can realize optimum efficiency.For example, can provide very tiny surface texture, for low viscous fluid provides coarse structure for the high viscosity fluid.Flow rate of fluid also can influence patterned surface, must take into account.
Can provide patterned surface partially in a side of contacting with fluid.It is also favourable when patterned surface spreads all over whole length of pipeline and/or periphery.Also favourable when equally, being arranged in position for heat transmission particular importance.Therefore, in the zone that only is used for propelling fluid, pipeline can comprise smooth surface; In the zone that is used for heat exchange, can use Promethean surface.
In exploitation of the present invention, the suggestion patterned surface comprises projection (formations).These are raised with to be beneficial in tube wall and form, and protrude in the secondary fluid.They also increase the surface area of tube wall.Select size, quantity and the configuration of projection, so that ignore the influence that pressure in the secondary fluid is descended with respect to another projection.Simultaneously, projection causes the turbulent flow of tube wall zone inner fluid between fin.Can form this surface cheaply by existing method.
Further the suggestion patterned surface comprises depression (depressions).By depression and protrude into projection in the fluid, can increase the turbulent flow of secondary fluid in the tube wall zone.Also further increase the exterior surface area of pipeline, thus the heat exchange of enhancing and secondary fluid.In addition, the manufacturing expense of pipeline that has external concavity is also very low, for example, only need get final product in the outer surface of tube wall embossing.
Further projection and depression are alternately arranged in suggestion on the flow direction of secondary fluid.In the king-sized secondary steam of turbulent flow, can realize useful especially heat exchange.Particularly when alternately arranging projection with depression, decide, can significantly promote thermal heat transfer capability according to the flow mechanism of fluid according to the fluid Consideration.
Further suppose projection and/or be recessed to form unified pattern.Therefore, for example, can be on flow direction stagger arrangement raised or sunken.The shape that can adjust projection and/or depression is with the heat-exchange capacity of the best of obtaining.Therefore, shape can be spherical segment, taper shape, pyramid etc.
In exploitation of the present invention, suggestion projection and/or depression depart from a few tenths of millimeter of center line of the tube wall of contacting with fluid.This mode can further reduce pressure and descend.
Further supposition projection and/or depression depart from centre of surface line percent several millimeters of contacting with fluid.Can further reduce pressure descends.Distance that can comprehensive raised or sunken disalignment and raised or sunken shape.
In preferred development of the present invention, the permeable meander structure of a thermal conductivity is vertically arranged in suggestion along pipeline at least one pipeline, and pipeline at least partly carries out heat exchange with adjacent cover plate at its rollback point.The meander structure refers to that the optimum that spreads all over whole width of pipeline and length unifies the fold steel bar.The groove line of steel bar fold forms contact wire, steel bar by contact wire welding or gluing to body.At opposite side, the summit of fold forms the contact wire with stacked cover plate.From side view, observe, a streamlined flow passage that runs through the structure of meandering occurs along the secondary fluid flow direction, and the waveform fin moves ahead to and fro uniformly with curve form.
Adopt this mode to strengthen heating surface easily.In addition, also can provide the meander structure that has body structure surface, further increase heat-transfer capability.Can realize thermally coupled by welding, welding, viscose glue or this type of form.
This invention further proposes to have the heat exchanger of pipeline, and liquid can pass through pipeline, and heat exchange mutually wherein provides a kind of novelty pipeline at least.
Adopt this mode to increase the heat-transfer capability of novelty heat exchanger easily, need not strengthen its planform and/or accept the more high pressure drop of elementary fluid.Therefore, existing equipment can be reequiped the novelty heat exchanger that heat-transfer capability is higher, do not need exceptional space.In addition, the heat converter structure shape that exchange capability of heat is identical can be littler, to save the existing equipment space.Because elementary fluid pressure drop keeps basic identical or even reduce, need not adopt other measure, extra compressor and so on for example is provided.
In addition, by the body structure surface mode, can increase rigidity with this type of surperficial pipeline and heat exchanger outer cover.Therefore can bear the mechanical strain of increase.
Further propose to have at least a part of pipeline to constitute tabular duct arrangement.By fixing tabular duct arrangement, can form the easy adapter structure shape of heat exchanger.
According to further exploitation, heat exchanger is made of many stacked tabular duct arrangement, and different liquids can be alternately by contiguous tabular pipeline configuration.Therefore, can realize that according to stacked, performance-adjustable is good by the high capacity of heat transfer of different duct arrangement from a kind of liquid to another kind of liquid.
Condensed steam is further proposed in this invention, the aerial condenser of power plant's turbine steam particularly, wherein need the steam of condensation to be delivered to heat exchanger by steam suppling tube road and configuration, the jet chimney that provides is used to remove condensate and shifts noble gas, and heat exchanger is a kind of novelty heat exchanger with above-mentioned advantage.Because heat-transfer capability improves, the aerial condenser planform may be littler, and production cost efficient is higher.
As mentioned above, the preferred unit of novelty aerial condenser is a cooling stack, because can represent above-mentioned advantage especially like this.
Description of drawings
Describe the present invention in detail in conjunction with the one exemplary embodiment of expression in the accompanying drawings now.Basic identical assembly distributes same reference numerals.Icon is as follows:
Fig. 1 is a heat exchanger part perspective view of the present invention;
Fig. 2 is first embodiment with fin of the present invention of surface texture;
Fig. 3 is second embodiment with fin of the present invention of surface texture; And
Fig. 4 is the IV-IV cross section of the 3rd embodiment of the fin of the present invention by having surface texture shown in Figure 2.
The specific embodiment
Fig. 1 represents to have the part of the novelty heat exchanger 1 of pipeline 2 of the present invention, is used to conduct elementary fluid.Pipeline 2 is made of wide flat bed shape tube wall 3, adopts the two blocks of parallel-plates 4 and 5 be spaced from each other certain distance to form, and two blocks of parallel-plates laterally connect semicircular pipe 6 and 7.The tube wall 3 of pipeline 2 is made of the withstand voltage anticorrosion aluminum steel in outside.
The planar side 4 and 5 of tube wall 3 is two fold aluminium strips 8 and 9, forms the exterior ribs of pipeline 2, is also referred to as fin.Article two, fold fin 8 and 9 outer counter turning point 10 are respectively two overlays 11 and 12.Overlay 11 and 12 increases the rigidity of fin 8 and 9, increases the heat exchange surface of pipeline 2, can easily stacked (stack) several pipelines 2 or contiguous the placement.Therefore, constitute heat exchanger plates 1 easily, stepped construction is easily installed in and reaches in the cooling tower from wherein removing.
At inner counter turning point 13, fold band or fin 8 and 9 and the outer surface level 4 and 5 of the heat conductive wall 3 of pipeline 2 carry out heat exchange.In this example, adopt thermostable heat-conductive glue to connect and realize thermo-contact.Also can adopt welding or soldered to realize this contact.The same with overlay 11 and 12, fin 8 and 9 is made by aluminium, also can use other good material of thermal conductivity.
Cover fin 8 and 9 based on corrugated, the flow channel 14 of many secondary fluid is arranged on the base.On cross section, continuous-flow passage 14 and the fin 8 that moves ahead back and forth and 9 form two structures 15 and 16 of meandering respectively with overlay 11 and 12.
Based on perpendicular to the fin 8 of primary flow direction of flow and 9 aligning, elementary fluid and secondary fluid can the cross-current form by pipeline 2.Steam can pass through pipeline 2 by elementary fluid form, and air can the secondary fluid form pass through external channel 14.Therefore, pipeline 2 that elementary fluid passes through and tube wall 3 thereof and flow channel 14 are separated by a distance, and two kinds of fluids can not mix.
Externally, the tube wall 3 of pipeline 2 shown in Figure 2 comprises the fin 7 with body structure surface 17.Body structure surface 17 is made of square and triangular structure, wherein substitutes projection 18 and depression 19 and forms unified pattern along elementary flow direction.Projection 18 and depression 19 are separately staggered.
Show partly that as the 3rd alternative embodiment fin 8 also can be made of circular protrusions 18 and depression 19 by body structure surface 17 shown in Figure 4.Before being pressed into corrugated and being fixed to tube wall 3, can adopt spherical embossing die (embossing die) that these projectioies are pressed in the fin 8.With respect to the fin surface, the height of fin 8 internal projection 18 or the degree of depth are approximately 0.3 millimeter.
One exemplary embodiment shown in the figure is only with explaining, and is not used for limiting the present invention.Particularly concave shape and duct arrangement thereof can change.
Claims (17)
1, is used to conduct the pipeline (2) of mobile elementary fluid, has the heat conductive wall (3) of band exterior ribs (8,9), secondary fluid can is characterized in that partly by its outside at least, removes fin (8,9) in addition, tube wall (3) comprises the body structure surface (17) in its outside.
2, pipeline as claimed in claim 1 is characterized in that,
This body structure surface (17) to small part is positioned on the fin (8,9).
3, pipeline as claimed in claim 1 or 2 is characterized in that,
This body structure surface (17) comprises projection (18).
4, the described pipeline of one of claim as described above is characterized in that,
This body structure surface (17) comprises depression (19).
5, the described pipeline of one of claim as described above is characterized in that,
This body structure surface (17) is aimed at the secondary fluid flow direction, and projection (18) and depression (19) longshore current are to alternately arranging like this.
6, the described pipeline of one of claim as described above is characterized in that,
Projection (18) and/or depression (19) constitute unified pattern.
7, the described pipeline of one of claim as described above is characterized in that,
Equal a few tenths of millimeter along the projection (18) of secondary fluid flow direction and/or the size of depression (19).
8, the described pipeline of one of claim as described above is characterized in that,
Equal a few percent millimeter along the projection (18) of secondary fluid flow direction and/or the size of depression (19).
9, the described pipeline of one of claim as described above is characterized in that,
Many fins are made of fold fin (8,9).
10, the described pipeline of one of claim as described above is characterized in that,
Fold fin (8,9) is along pipeline (2) longitudinal extension.
11, the described pipeline of one of claim as described above is characterized in that,
Fold fin (8,9) is covered at the overlay (11,12) with tube wall (3) opposite side, and forms the meander structure (15,16) that secondary fluid can be passed through.
12, the described pipeline of one of claim as described above is characterized in that,
Fold fin (8,9) turning point (10,13) welding and/or be glued to tube wall (3) and overlay (11,12) on.
13, heat exchanger (1) has one at least as the described pipeline of one of claim 1 to 12 (2).
14, heat exchanger as claimed in claim 13 is characterized in that,
Comprise and have the meander structure (15,16) that to pass through and the pipeline (2) of outside cover plate (11,12), form laminar stackable pipeline configuration.
15, as the described heat exchanger in one of claim 13 or 14, it is characterized in that,
Comprise many stacked tabular pipeline configurations, thereby different liquids can be alternately by contiguous tabular pipeline configuration.
16, be used for condensed steam, particularly the aerial condenser of power plant's turbine steam wherein needs the steam of condensation to be delivered to heat exchanger (1) by steam suppling tube road and configuration, and provides pipeline to be used to remove condensate and transfer inert gas, it is characterized in that
At least one heat exchanger (1) is the heat exchanger according to one of aforementioned claim 13 to 16.
17, aerial condenser as claimed in claim 16 is characterized in that,
Aerial condenser is a cooling stack.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP03027584.6 | 2003-12-01 | ||
| EP03027584A EP1538415A1 (en) | 2003-12-01 | 2003-12-01 | Flow duct |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010110676A Division CN101846478A (en) | 2003-12-01 | 2004-12-01 | Pipeline |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1624413A true CN1624413A (en) | 2005-06-08 |
Family
ID=34442924
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200410096811.2A Pending CN1624413A (en) | 2003-12-01 | 2004-12-01 | Flow duct |
| CN201010110676A Pending CN101846478A (en) | 2003-12-01 | 2004-12-01 | Pipeline |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010110676A Pending CN101846478A (en) | 2003-12-01 | 2004-12-01 | Pipeline |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20050211424A1 (en) |
| EP (1) | EP1538415A1 (en) |
| CN (2) | CN1624413A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103093929A (en) * | 2013-01-27 | 2013-05-08 | 大连世有电力科技有限公司 | Condensation cover for transformer respirator |
| CN103567585A (en) * | 2012-08-09 | 2014-02-12 | 摩丁制造公司 | Heat exchanger tube, heat exchanger tube assembly, and methods of making the same |
| CN104533538A (en) * | 2014-12-15 | 2015-04-22 | 厦门大学 | Heat exchange channel wall with rib structure |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100690891B1 (en) * | 2005-05-26 | 2007-03-09 | 엘지전자 주식회사 | Heat exchanger for a drier and condensing type drier utilizing the same |
| CN108590776A (en) * | 2018-04-24 | 2018-09-28 | 厦门大学 | A kind of turbine blade cooling method using triangular pyramid vortex generator |
Family Cites Families (31)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1726360A (en) * | 1925-09-25 | 1929-08-27 | Arthur B Modine | Radiator construction |
| US2011756A (en) * | 1931-09-30 | 1935-08-20 | Nicholas S Diamant | Radiator core structure |
| US2083671A (en) * | 1935-01-19 | 1937-06-15 | Gen Motors Corp | Radiator |
| US2090222A (en) * | 1935-04-20 | 1937-08-17 | Frank A Neveu | Radiator core |
| US2252211A (en) * | 1939-10-18 | 1941-08-12 | Mccord Radiator & Mfg Co | Heat exchange core |
| US2651505A (en) * | 1950-05-27 | 1953-09-08 | Phelps M Freer | Automobile heater |
| US2778606A (en) * | 1952-01-02 | 1957-01-22 | Gen Motors Corp | Heat exchangers |
| US3298432A (en) * | 1964-05-22 | 1967-01-17 | Przyborowski Stanislaus | Radiators |
| US3664928A (en) * | 1969-12-15 | 1972-05-23 | Aerojet General Co | Dimpled heat transfer walls for distillation apparatus |
| US3684007A (en) * | 1970-12-29 | 1972-08-15 | Union Carbide Corp | Composite structure for boiling liquids and its formation |
| CH610395A5 (en) * | 1976-08-11 | 1979-04-12 | Escher Wyss Gmbh | |
| US4258783A (en) * | 1977-11-01 | 1981-03-31 | Borg-Warner Corporation | Boiling heat transfer surface, method of preparing same and method of boiling |
| JPS56155391A (en) * | 1980-04-30 | 1981-12-01 | Nippon Denso Co Ltd | Corrugated fin type heat exchanger |
| DE3238943A1 (en) * | 1982-10-21 | 1984-04-26 | kabelmetal electro GmbH, 3000 Hannover | HEAT EXCHANGER, ESPECIALLY FOR SOLAR COLLECTORS |
| JPS6029593A (en) * | 1983-07-27 | 1985-02-14 | Hitachi Ltd | Construction of single-phase flow heat-transfer pipe |
| JPS6066096A (en) * | 1983-09-20 | 1985-04-16 | Matsushita Electric Ind Co Ltd | Heat transfer pipe |
| JPS6066097A (en) * | 1983-09-20 | 1985-04-16 | Matsushita Electric Ind Co Ltd | Heat transfer pipe |
| JPS6115088A (en) * | 1984-06-28 | 1986-01-23 | Matsushita Electric Ind Co Ltd | Heat transfer tube for boiling |
| JPS61175485A (en) * | 1985-01-30 | 1986-08-07 | Kobe Steel Ltd | Heat transfer tube and manufacture thereof |
| JPS61175486A (en) * | 1985-01-31 | 1986-08-07 | Matsushita Electric Ind Co Ltd | Heat transfer tube for boiling |
| US5224538A (en) * | 1991-11-01 | 1993-07-06 | Jacoby John H | Dimpled heat transfer surface and method of making same |
| US5377746A (en) * | 1993-04-26 | 1995-01-03 | Fintube Limited Partnership | Texturized fin |
| KR0134557B1 (en) * | 1993-07-07 | 1998-04-28 | 가메다카 소키치 | Heat exchanger tube for falling film evaporator |
| EP0697090B1 (en) * | 1994-03-03 | 1998-06-10 | GEA LUFTKÜHLER GmbH | Finned tube heat exchanger |
| US5697430A (en) * | 1995-04-04 | 1997-12-16 | Wolverine Tube, Inc. | Heat transfer tubes and methods of fabrication thereof |
| US5738169A (en) * | 1995-11-07 | 1998-04-14 | Livernois Research & Development Co. | Heat exchanger with turbulated louvered fin, manufacturing apparatus and method |
| US5681661A (en) * | 1996-02-09 | 1997-10-28 | Board Of Supervisors Of Louisiana State University And Agricultural And Mechanical College | High aspect ratio, microstructure-covered, macroscopic surfaces |
| IT1283468B1 (en) * | 1996-07-19 | 1998-04-21 | Alcan Alluminio S P A | LAMINATE FOR THE CONSTRUCTION OF HEAT EXCHANGERS AND RELATED PRODUCTION METHOD |
| KR100297189B1 (en) * | 1998-11-20 | 2001-11-26 | 황해웅 | High efficiency modular OEL heat exchanger with heat transfer promoting effect |
| CN1161586C (en) * | 1998-12-25 | 2004-08-11 | 株式会社神户制钢所 | Tube having inner surface trough, and method for producing same |
| JP3864916B2 (en) * | 2002-08-29 | 2007-01-10 | 株式会社デンソー | Heat exchanger |
-
2003
- 2003-12-01 EP EP03027584A patent/EP1538415A1/en not_active Withdrawn
-
2004
- 2004-11-30 US US10/998,828 patent/US20050211424A1/en not_active Abandoned
- 2004-12-01 CN CN200410096811.2A patent/CN1624413A/en active Pending
- 2004-12-01 CN CN201010110676A patent/CN101846478A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103567585A (en) * | 2012-08-09 | 2014-02-12 | 摩丁制造公司 | Heat exchanger tube, heat exchanger tube assembly, and methods of making the same |
| CN103567585B (en) * | 2012-08-09 | 2017-04-12 | 摩丁制造公司 | Heat exchanger tube, heat exchanger tube assembly, and methods of making the same |
| CN103093929A (en) * | 2013-01-27 | 2013-05-08 | 大连世有电力科技有限公司 | Condensation cover for transformer respirator |
| CN103093929B (en) * | 2013-01-27 | 2015-10-28 | 大连世有电力科技有限公司 | The condensing cover of transformer breather |
| CN104533538A (en) * | 2014-12-15 | 2015-04-22 | 厦门大学 | Heat exchange channel wall with rib structure |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1538415A1 (en) | 2005-06-08 |
| US20050211424A1 (en) | 2005-09-29 |
| CN101846478A (en) | 2010-09-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN2869738Y (en) | Aluminium inner-finned-tube heat exchanger | |
| JP6128492B2 (en) | Finned tube heat exchanger and manufacturing method thereof | |
| US20100230084A1 (en) | Tube-fin type heat exchange unit with high pressure resistance | |
| CN102062501A (en) | Heat exchanger structure and assembly method thereof | |
| CN112696950A (en) | Micro-fin heat exchange device | |
| CN1902455A (en) | Fin for heat exchanger and heat exchanger equipped with such fins | |
| CN105371684A (en) | Sheet space structure for heat exchanger | |
| CN1624413A (en) | Flow duct | |
| CN101782347B (en) | Heat exchanger and fin thereof | |
| CN102042770A (en) | Heat exchanger consisting of internal and external fin heat exchange tubes | |
| CN201034431Y (en) | Finned tube for air cooling condensator | |
| CN114199068B (en) | Continuous H-shaped finned tube with airflow partition | |
| CN2580573Y (en) | Sheet type heat radiator for transformer | |
| CN214308296U (en) | Micro-fin heat exchange device | |
| CN212931106U (en) | Heat exchange plate sheet of plate heat exchanger for steam condensation | |
| CN110530179B (en) | Symmetrical bubbling type plate heat transfer element | |
| CN212378563U (en) | Corrugated plate gas-gas heat exchanger | |
| CN201527213U (en) | High-efficient strengthened turbulent corrugated radiating fin | |
| CN205505792U (en) | Corrugated fin type finned plate heat exchanger that chevron shape is straight | |
| CN209763802U (en) | Novel micro-channel flat tube heat exchanger with internal teeth | |
| RU200477U1 (en) | HEAT EXCHANGER PLATE | |
| CN2852024Y (en) | Energy-saving pipe type oil cooler | |
| CN104006693A (en) | Opposite-rounded-corner oblique-breaking-type finned tube non-contact thermal resistance heat transmission element | |
| CN218600377U (en) | Plate type heat exchange sheet | |
| CN2562159Y (en) | Spiral baffle bead heat exchange tube bundle heat exchanger |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| ASS | Succession or assignment of patent right |
Owner name: SPIRIT2GO LIMITED LIABILITY COMPANY Free format text: FORMER OWNER: DUERR BALCKE GMBH Effective date: 20050722 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20050722 Address after: The Federal Republic of Germany in Ratingen Applicant after: SPX Cooling Technologies GmbH Address before: The Federal Republic of Germany in Oberhausen Applicant before: Duerr Balcke GmbH |
|
| C12 | Rejection of a patent application after its publication | ||
| RJ01 | Rejection of invention patent application after publication |
Open date: 20050608 |