EP2101136B1 - Metallisches Wärmeaustauscherrohr - Google Patents

Metallisches Wärmeaustauscherrohr Download PDF

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Publication number
EP2101136B1
EP2101136B1 EP09002560.2A EP09002560A EP2101136B1 EP 2101136 B1 EP2101136 B1 EP 2101136B1 EP 09002560 A EP09002560 A EP 09002560A EP 2101136 B1 EP2101136 B1 EP 2101136B1
Authority
EP
European Patent Office
Prior art keywords
groove
material projections
primary
spacing
heat exchange
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.)
Active
Application number
EP09002560.2A
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German (de)
English (en)
French (fr)
Other versions
EP2101136A3 (de
EP2101136A2 (de
Inventor
Andreas Knöpfler
Andreas Schwitalla
Andreas Dr. Beutler
Jean Dr. El Hajal
Ronald Lutz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wieland Werke AG
Original Assignee
Wieland Werke AG
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Publication date
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Publication of EP2101136A2 publication Critical patent/EP2101136A2/de
Publication of EP2101136A3 publication Critical patent/EP2101136A3/de
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Publication of EP2101136B1 publication Critical patent/EP2101136B1/de
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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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • 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
    • 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
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals

Definitions

  • the invention relates to a metallic heat exchanger tube with on the outside of the tube helically encircling, integrally molded ribs according to the preamble of claim 1.
  • Such metallic heat exchanger tubes are used in particular for the evaporation of liquids from pure substances or mixtures on the outside of the tube.
  • Evaporation occurs in many areas of refrigeration and air conditioning technology as well as in process and energy technology.
  • shell-and-tube heat exchangers are used in which liquids of pure substances or mixtures evaporate on the outside of the pipe, cooling a brine or water on the inside of the pipe.
  • Such apparatuses are referred to as flooded evaporators.
  • the size of the evaporator can be greatly reduced. As a result, the production costs of such apparatuses decrease.
  • the necessary filling quantity of refrigerant which can account for a not inconsiderable share of the total investment costs in the chlorine-free safety refrigerants that are predominantly used today, is decreasing. In the case of toxic or flammable refrigerants, the risk potential can also be reduced by reducing the filling quantity.
  • the standard high-performance pipes are about four times more efficient than smooth pipes of the same diameter.
  • Integrally rolled finned tubes are understood to mean finned tubes in which the fins are formed from the wall material of a smooth tube.
  • various methods are known with which the channels located between adjacent ribs are closed in such a way that connections between the channel and the environment remain in the form of pores or slits.
  • substantially closed channels are formed by bending or flipping the ribs (FIG.
  • the most powerful commercially available finned tube finned tubes have on the tube exterior a ribbed structure with a fin density of 55 to 60 fins per inch ( US 5,669,441 ; US 5,697,430 ; DE 197 57 526 C1 ). This corresponds to a rib pitch of about 0.45 to 0.40 mm.
  • a rib pitch of about 0.45 to 0.40 mm.
  • a smaller rib division inevitably requires equally finer tools. However, finer tools are subject to a higher risk of breakage and faster wear.
  • the currently available tools enable the safe production of finned tubes with rib densities of up to 60 ribs per inch. Further, as the rib pitch decreases, the production rate of the tubes becomes smaller, and hence the manufacturing cost becomes higher.
  • performance-enhanced evaporation structures can be produced at the same rib density on the outside of the tube by introducing additional structural elements in the region of the groove bottom between the ribs. Since the temperature of the rib is higher in the area of the groove base than in the area of the fin tip, structural elements for intensifying the formation of bubbles in this area are particularly effective.
  • EP 0 222 100 B1 US 5,186,252 ; JP 04039596A and US 2007/0151715 A1 to find.
  • These inventions have in common that the structural elements have no undercut shape at the groove bottom, which is why they do not sufficiently intensify the formation of bubbles.
  • EP 1 223 400 B1 It is proposed to produce at the groove bottom between the ribs undercut secondary grooves which extend continuously along the primary groove. The cross section of these secondary grooves can remain constant or varied at regular intervals.
  • the invention has for its object to provide a performance-enhanced heat exchanger tube for the evaporation of liquids on the outside of the tube with the same tube-side heat transfer and pressure drop.
  • the invention includes a metallic heat exchanger tube with on the outside of the tube helically encircling, integrally formed and continuously formed ribs, the fin foot protrudes substantially radially from the tube wall, as well as located between each adjacent ribs primary grooves.
  • At least one undercut secondary groove is arranged in the region of the groove bottom of the primary grooves. This secondary groove is limited to the primary groove by a pair of opposing material projections formed from material of respectively adjacent rib feet. These material projections extend continuously along the primary groove.
  • the cross section of the secondary groove is varied at regular intervals without affecting the shape of the ribs. There is a gap between the opposed material projections, this distance being varied at regular intervals, whereby local cavities are formed.
  • the invention is based on the consideration that to increase the heat transfer during evaporation of the process of bubbling is intensified.
  • the formation of bubbles begins at germinal sites. These germinal sites are usually small gas or steam inclusions. When the growing bubble reaches a certain size, it detaches from the surface. If the germinal site is flooded with fluid in the course of bladder detachment, the germinal site is deactivated.
  • the surface must therefore be designed in such a way that when the bubble is detached, a small bubble remains, which then serves as a germinal point for a new bubble formation cycle. This is achieved by applying cavities with openings on the surface. The opening of the cavity tapers in relation to the cavity located below the opening. Through the opening of the exchange of liquid and steam.
  • a connection between the primary and secondary groove is realized by the distance between the opposite material projections, so that the exchange of liquid and vapor between the primary groove and the secondary groove is made possible.
  • the particular advantage of the invention is that the effect of the undercut secondary groove on the formation of bubbles is particularly great when the distance between opposing material projections according to the invention is varied at regular intervals. As a result, the exchange of liquid and vapor is controlled specifically and prevents the flooding of the bubble nucleation site in the cavity.
  • the location of the cavities in the vicinity of the primary groove base is particularly favorable for the evaporation process, since at the groove bottom, the heat overtemperature is greatest and therefore there is the highest driving temperature difference for the bubble formation available.
  • the distance between the opposite material protrusions can assume the value zero at regular intervals.
  • the secondary groove is closed in certain areas relative to the primary groove. In these areas, the opposite material projections touch, without that it comes to a material conclusion.
  • the bubbles in turn escape through the cavities which are opened into the center of the primary groove, and the liquid preferably flows from the side into the cavity near the closed regions of the secondary groove.
  • the escaping bubble is not hindered by the inflowing liquid working medium and can expand undisturbed in the primary groove.
  • the respective flow zones for the liquid and the steam are spatially separated from each other.
  • a small channel is left between the cavities, which, however, has no connection to the primary groove. Nevertheless, for example, pressure differences between the mutually adjacent cavities can be compensated via these channels.
  • the secondary groove may be substantially pressed.
  • the maximum distance between the opposite material projections 0.03 mm to 0.1 mm.
  • the maximum distance between the opposite material projections 0.06 mm to 0.09 mm.
  • the length of the areas in the circumferential direction, in which the distance of the opposite material projections does not assume the value zero be between 0.2 mm and 0.5 mm.
  • the rib tips may be deformed such that they cover the primary grooves in the radial direction and partially close and thus a helically encircling, partially closed Form cavity.
  • the rib tips may have, for example, a substantially T-shaped cross section with pore-like recesses through which the vapor bubbles can escape.
  • Fig. 1 shows a view of the outside of a pipe section according to the invention.
  • the integrally rolled finned tube 1 has, on the outside of the tube, helical circumferential ribs 2, between which a primary groove 6 is formed.
  • the ribs 2 extend continuously without interruption along a helix line on the tube outside.
  • the ribbed foot 3 projects essentially radially from the tube wall 5.
  • a finned tube 1 is proposed, in which an undercut secondary groove extends in the region of the groove bottom 7, which extends between two respective adjacent ribs 2 located primary grooves 6 8 is arranged. This secondary groove 8 is limited to the primary groove 6 through a pair of opposed, formed of material respectively adjacent rib feet 3 shaped material protrusions 9.
  • These material projections 9 extend continuously along the primary groove 6, wherein a distance S is formed between opposite material projections 9, which is varied at regular intervals. With variation of the cross section of the secondary groove 8, the shape of the ribs 2 is not affected. Due to the change in cross-section in conjunction with the variation of the distance S, cavities 10 form locally, which favor bubble nucleation in particular.
  • the exchange of liquid and vapor between the primary groove 6 and secondary groove 8 is controlled by liquid supply and vapor discharge take place in separate areas.
  • tubes of the prior art for example, the after EP 1 223 400 B1 are made, not on, since here, although the cross-sectional shape of the secondary groove 8 is varied, but not their opening width and thus no preferred areas exist respectively for liquid supply and steam outlet.
  • the extent of the secondary groove 8 in the radial direction is measured from the groove bottom 7 in the areas with a large distance between the material projections 9 maximum 15% of the height H of the ribs 2.
  • the fin height H is measured on the finished finned tube 1 from the lowest point of the groove bottom 7 to the fin tip 4 of the fully formed finned tube.
  • Fig. 2 shows a front view of the pipe section according to Fig. 1 , In this partial view, the ribs 2 which extend helically on the outside of the pipe run into the plane of the drawing. Between the ribs 2, the primary groove 6 is formed. The ribbed foot 3 projects essentially radially from the tube wall 5. In the region of the groove bottom 7, which extends between each two adjacent ribs 2 located primary grooves 6, the undercut secondary groove 8 is formed. This secondary groove 8 is separated from the primary groove 6 by the opposing material projections 9.
  • These material projections 9 extend continuously along the primary groove 6 perpendicular to the plane of the drawing, wherein a distance S is formed between opposite material projections 9, which is varied at regular intervals. In different planes, S assumes the minimum value S min in the region between the cavities 10 and the value S max at the highest point of a cavity 10. By virtue of this change in cross-section, cavities 10 having an opening width are formed locally, which favor bubble nucleation in particular.
  • Fig. 3 shows a view of the outside of a pipe section 1 according to the invention with partially closed secondary groove 8.
  • the secondary groove 8 is completely closed at regular intervals to the primary groove 6 out. This corresponds to the case that in certain areas, the distance between the material projections 9 is reduced to zero.
  • the secondary groove 8 then has only in the respective intermediate areas openings to the primary groove 6 down, whereby the width of these openings is reduced at the respective edges.
  • Fig. 4 shows a front view of the pipe section according to Fig. 3 ,
  • the bubbles in turn escape through the cavities 10 which are opened into the center of the primary groove 6. Liquid flows into the cavity at the edges of the openings. In the closed region of the secondary groove 8, a small channel is maintained between the cavities 10, which has no connection to the primary groove 6. However, for example, pressure differences between the mutually adjacent cavities 10 can be compensated via these channels.
  • the length L of the regions in which the secondary groove is not closed is advantageously between 0.2 mm and 0.5 mm.
  • Fig. 5 shows a partial view of the outside of a pipe section according to the invention with fully closed secondary groove between the cavities.
  • the material projections 9 it also proves to be advantageous in the areas in which the distance between the material projections 9 is reduced to the value zero, the material projections 9 to deform so far that they are displaced to the bottom of the secondary 8 and thus the Secondary groove 8 is pressed in this area.
  • cavities 10 which are located in the intermediate regions and which are completely limited in their circumference are produced as undercut cavities at the bottom of the primary groove 6.
  • These cavities 10 act as extremely effective nucleation sites, since in these structures the subsequent flow of liquid can be very controlled and even especially small bubbles can not be displaced.
  • the bubbles in turn escape through the cavities 10 which are opened into the center of the primary groove 6. Liquid flows into the cavity at the edges of the openings.
  • the length L of the regions in which the secondary groove is not closed is advantageously between 0.2 mm and 0.5 mm.
  • Fig. 6 shows a front view of the pipe section according to Fig. 5 , As shown, it is once again clarified how in the regions in which the distance between the material projections 9 is reduced to the value zero, the material projections 9 are deformed. These are displaced to the bottom of the secondary groove 8, whereby the secondary groove 8 is pressed in this area.
  • the distance S between the opposing material projections 9 varies between 0 mm and 0.1 mm. In the ranges in which this distance assumes its maximum value S max , this value is typically between 0.03 mm and 0.1 mm, preferably between 0.06 mm and 0.09 mm.
  • the rib tips are expediently deformed as a distal region 4 of the ribs 2 such that they partially close the primary grooves 6 in the radial direction and thus form a partially closed cavity.
  • the connection between the primary groove 6 and the environment is configured in the form of pores 11 or slots, so that vapor bubbles can escape from the primary groove 6.
  • the deformation of the rib tips 4 is done with methods that can be found in the prior art.
  • the primary grooves 6 then represent even undercut grooves.
  • a structure By combining the cavities 10 according to the invention with a primary groove 6 which is closed except for pores 11 or slots, a structure is obtained which is further characterized in that it has a very high efficiency in the evaporation of liquids over a very wide range of operating conditions. In particular, when the heat flow density or the driving temperature difference is varied, the heat transfer coefficient of the structure at a high level remains almost constant.
  • the solution according to the invention relates to structured tubes in which the heat transfer coefficient is increased on the tube outside.
  • the heat transfer coefficient on the inside can also be intensified by a suitable internal structuring.
  • the heat exchanger tubes for shell and tube heat exchangers usually have at least one structured area and smooth end pieces and possibly smooth spacers.
  • the smooth end or intermediate pieces limit the structured areas. So that the tube can be easily installed in the shell and tube heat exchanger, the outer diameter of the structured areas must not be greater than the outer diameter of the smooth end and intermediate pieces.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Rigid Pipes And Flexible Pipes (AREA)
EP09002560.2A 2008-03-12 2009-02-24 Metallisches Wärmeaustauscherrohr Active EP2101136B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008013929A DE102008013929B3 (de) 2008-03-12 2008-03-12 Verdampferrohr mit optimierten Hinterschneidungen am Nutengrund

Publications (3)

Publication Number Publication Date
EP2101136A2 EP2101136A2 (de) 2009-09-16
EP2101136A3 EP2101136A3 (de) 2013-08-07
EP2101136B1 true EP2101136B1 (de) 2015-01-14

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EP09002560.2A Active EP2101136B1 (de) 2008-03-12 2009-02-24 Metallisches Wärmeaustauscherrohr

Country Status (9)

Country Link
US (1) US8281850B2 (pt)
EP (1) EP2101136B1 (pt)
JP (1) JP5684456B2 (pt)
KR (1) KR20090097773A (pt)
CN (1) CN101532795B (pt)
BR (1) BRPI0900816B1 (pt)
DE (1) DE102008013929B3 (pt)
MX (1) MX2009001692A (pt)
PT (1) PT2101136E (pt)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016006914A1 (de) 2016-06-01 2017-12-07 Wieland-Werke Ag Wärmeübertragerrohr

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CN101603793B (zh) * 2009-07-16 2010-09-01 江苏萃隆精密铜管股份有限公司 一种强化冷凝管
WO2014011372A2 (en) * 2012-06-19 2014-01-16 The Board Of Trustees Of The University Of Illinois, A Body Corporate And Politic Of The State Of Illinois Refrigerant repelling surfaces
CN102980432A (zh) * 2012-11-12 2013-03-20 沃林/维兰德传热技术有限责任公司 带空心腔体的蒸发传热管
CN102980431A (zh) * 2012-11-12 2013-03-20 沃林/维兰德传热技术有限责任公司 蒸发传热管
DE102014002829A1 (de) 2014-02-27 2015-08-27 Wieland-Werke Ag Metallisches Wärmeaustauscherrohr
EP3377838B1 (en) * 2015-11-17 2022-02-23 Arvind Jaikumar Pool boiling enhancement with feeder channels supplying liquid to nucleating regions
KR20230098133A (ko) 2020-10-31 2023-07-03 빌란트-베르케악티엔게젤샤프트 금속 열교환기 튜브
DE202020005625U1 (de) 2020-10-31 2021-11-10 Wieland-Werke Aktiengesellschaft Metallisches Wärmeaustauscherrohr

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016006914A1 (de) 2016-06-01 2017-12-07 Wieland-Werke Ag Wärmeübertragerrohr
WO2017207089A1 (de) 2016-06-01 2017-12-07 Wieland-Werke Ag Wärmeübertragerrohr
DE102016006914B4 (de) 2016-06-01 2019-01-24 Wieland-Werke Ag Wärmeübertragerrohr
US10996005B2 (en) 2016-06-01 2021-05-04 Wieland-Werke Ag Heat exchanger tube

Also Published As

Publication number Publication date
EP2101136A3 (de) 2013-08-07
DE102008013929B3 (de) 2009-04-09
PT2101136E (pt) 2015-04-22
MX2009001692A (es) 2009-10-05
CN101532795B (zh) 2013-07-24
JP5684456B2 (ja) 2015-03-11
BRPI0900816A2 (pt) 2010-01-19
CN101532795A (zh) 2009-09-16
US8281850B2 (en) 2012-10-09
US20090229807A1 (en) 2009-09-17
KR20090097773A (ko) 2009-09-16
JP2009216374A (ja) 2009-09-24
EP2101136A2 (de) 2009-09-16
BRPI0900816B1 (pt) 2020-11-10

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