EP3850293A1 - Wärmeübertrager mit oberflächenelementen mit konvexen aussparungen und integrierten materialaufdickungen - Google Patents
Wärmeübertrager mit oberflächenelementen mit konvexen aussparungen und integrierten materialaufdickungenInfo
- Publication number
- EP3850293A1 EP3850293A1 EP19805232.6A EP19805232A EP3850293A1 EP 3850293 A1 EP3850293 A1 EP 3850293A1 EP 19805232 A EP19805232 A EP 19805232A EP 3850293 A1 EP3850293 A1 EP 3850293A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- tube
- heat exchanger
- partition
- reinforcing beads
- surface elements
- 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
- 239000000463 material Substances 0.000 title description 15
- 230000008719 thickening Effects 0.000 title description 4
- 239000011324 bead Substances 0.000 claims abstract description 78
- 230000003014 reinforcing effect Effects 0.000 claims abstract description 65
- 238000005192 partition Methods 0.000 claims abstract description 50
- 239000012530 fluid Substances 0.000 claims abstract description 43
- 238000012546 transfer Methods 0.000 description 16
- 239000007789 gas Substances 0.000 description 11
- 230000002787 reinforcement Effects 0.000 description 10
- 239000007788 liquid Substances 0.000 description 6
- 238000001816 cooling Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 4
- 239000002184 metal Substances 0.000 description 4
- 239000002826 coolant Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 210000002816 gill Anatomy 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
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
- F28F1/12—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
- F28F1/24—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 transversely
- F28F1/26—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 transversely the means being integral with the 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
- 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
- F28F1/24—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 transversely
- F28F1/30—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 transversely the means being attachable to the 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
- F28F2215/00—Fins
- F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2225/00—Reinforcing means
- F28F2225/06—Reinforcing means for fins
Definitions
- the invention relates to a heat exchanger with at least one partition, from which surface elements projecting on at least one side are arranged, around which a fluid can flow.
- heat exchangers are used in various designs for the transfer of heat from one medium to another medium, the two media remaining physically separate.
- heat exchangers can be subdivided, for example, into liquid-gas heat exchangers, liquid-liquid heat exchangers and into gas-gas heat exchangers.
- tube bundle heat exchangers with finned tubes are known, which are also referred to as finned tube heat exchangers.
- the liquid flows inside the tube and the gas flows around the tube on the outside.
- the heat transfer coefficients of liquids are one to two orders of magnitude larger than those of gases.
- the surface of the tube is therefore enlarged on the outside by means of ribs, as a result of which there is a reduced heat transfer resistance on the gas side of this heat exchanger.
- the heat transfer resistances for both media are small.
- the fins of finned tubes are often designed as voluminous approaches which are connected to the partition wall of the heat exchanger. Large volumes of the fins are coupled with high material costs in the manufacture and a large weight of the heat exchangers. High weights can be disadvantageous and undesirable, for example when used in vehicles. A high material consumption is disadvantageously associated with correspondingly high costs.
- fin thickness A large wall thickness of the individual fins, hereinafter referred to as fin thickness, results in a lower number of fins per finned tube than in the case of thinner fins, with the same spacing between the fins. Limited heat transfer surfaces and low overall thermal outputs are associated with a large fin thickness.
- GB 436 656 A discloses a heat exchanger with finned tubes, in which three-dimensionally designed fins are arranged on the fins, which extend essentially perpendicular to the base area of the fins.
- the fins have a peg-shaped cross section and not all fins are adjacent to the wall of the tube which separates the fluids from one another.
- a disadvantage of these finned tubes is the increase in mass, which is proportional to the volume of the three-dimensional fins, and a limited overall thermal output of the heat exchangers.
- a further disadvantage is that the fins are vertical to the direction of flow of the Fluid flowing around fins aligned and hardly affect the heat conduction within the fin away from the pipe or towards the pipe.
- CH 435 436 A discloses a finned tube consisting of a core tube and a plurality of sheet metal fins arranged on the core tube with a rectangular outline as ribs.
- the sheet metal fins each have beads - that is, depressions - which extend from the core tube and increase the rigidity.
- a disadvantage of such fins is that the heat-conducting cross-sectional area increases with distance from the core tube and thus leads to cooling of the fin, as a result of which the temperature difference between the fin and the medium flowing around it decreases and the heat transfer performance decreases.
- DE 160 351 A describes a heat exchanger in which further pipes are arranged radially on the surface of a heating or cooling body pipe.
- fins can be arranged perpendicular to the heating or cooling element tube axis, the fins being able to be arranged as a separate layer between two layers of radial tubes or within a layer of radial tubes for reasons of stiffening.
- DE 42 07 597 A1 discloses a heat exchange element for fixation on a medium-flow tube with a plurality of radially projecting heat exchanger fins.
- the heat exchanger fins extend along the longitudinal axis of the tube in the direction of flow of the fluid flowing through the tube and do not form any surface perpendicular to the direction of flow of the fluid in the tube.
- DE 70 20 851 U discloses a heat exchanger such as that which is designed as the rear wall of a refrigerator.
- Such single-wall heat exchangers consist of a pipe coil for receiving the heating or cooling medium and a sheet metal wall with expressed rows of gills and grooves or beads for receiving the pipe sections. Flaps punched out of the sheet metal wall overlap the pipe sections for fastening. The flaps can have beads for greater stability. The sheet and the punched-out tabs are aligned along the direction of flow of the heating or cooling medium through the tube.
- WO 02/048 595 A1 describes a sewer pipe for media transport made of plastic, which enables the media to be transported in the pipe without loss of pressure, even if the sewer pipe is laid in a curved manner.
- the sewer pipe has an undulating shape in the flow direction of the pipe Wall on.
- US 3 31 1 163 discloses a heat exchanger consisting of a metallic tube and a plurality of rectangular metallic fins, which are fixed on the outside of the metallic tube.
- the fins have parallel vertical embossments to compensate for the lateral thermal expansion of the tube and the fins. These embossments are aligned vertically to the direction of flow of the fluid through the tube
- the object of the invention is to provide a low-mass heat exchanger with high thermal output and a homogeneous temperature profile along the ribs.
- the heat exchanger contains a dividing wall and at least one surface element projecting from one side of the dividing wall and enlarging the surface of the dividing wall, around which a fluid can flow.
- the surface elements have reinforcing beads and surface areas located between the reinforcing beads, the reinforcing beads extending from the partition and having a circular or oval cross-sectional shape.
- the reinforcing beads extend from the partition over at least part of the height of the surface element.
- the surface elements have a large number of convex recesses, each of the convex recesses being arranged in one of the surface regions between two reinforcing beads and extending from an outer edge of the surface element.
- the apex of the respective recess is at a height greater than or equal to 30% and less than or equal to 70% of the height of the surface element. The height is measured starting from the partition.
- the thickness of the surface elements also referred to as the wall thickness, is small compared to the surface of the surface elements, the thickness being measured parallel to the partition and perpendicular to the surface of the surface elements.
- the surface elements preferably extend perpendicularly from the partition.
- the surface elements are rigidly connected to the partition and are also rigid in themselves.
- the surface elements serving as ribs of the heat exchanger are divided into thin-walled surface areas with a correspondingly small volume and low mass. The thickness of the surface areas corresponds to the wall thickness of the surface elements. The division is made by reinforcement beads with larger cross sections for increased heat conduction.
- the reinforcing beads have a greater thickness than the wall thickness of the surface elements.
- the reinforcing beads thus form material thickenings that are solid and therefore not hollow.
- the cross-section of the surface element in the area of a reinforcing bead thus consists entirely of the material of the surface element, which completely fills the cross-section.
- the reinforcing beads are oriented such that they conduct the heat to or from the partition wall between the two fluids, depending on how the temperature gradient is.
- the height of the surface elements is the extension of the surface elements starting from the partition along the surface of the surface elements to the outer edge of the surface elements in an area that is not a convex recess.
- the height of the surface elements is the radius of the surface elements starting from the partition.
- the outer edge of the surface element is the side of the surface element that does not adjoin the partition.
- Convex recess means that the recess has a convex shape that has its greatest width at the outer edge of the surface element and whose width decreases along the surface element in the direction of the partition. The width is measured along the surface of the surface element.
- a recess is the complete absence of the material of the surface element, i.e. the recess extends over the entire thickness of the surface element and does not only represent a thinning of the surface element in a certain area.
- the convex recesses advantageously reduce the surface area of the surface element with increasing distance from the partition, so that the heat-conducting cross-sectional area of the surface element is reduced.
- the heat flow concentrates on a smaller area of the surface element, as a result of which cooling of the fin, as is known from the prior art, is avoided.
- This improves the effectiveness of heat transfer.
- the reduced surface area of the surface elements advantageously offers a low loss of frictional pressure in the flowing fluid.
- the Mass of the surface element is reduced by the lower material consumption or an execution of the surface element is made possible without increasing the mass of the surface element by the reinforcing beads or by a greater thickness of the surface element.
- the reinforcing beads contribute locally to improving the heat conduction.
- the combination of the plurality of convex recesses and intervening reinforcement beads improves the temperature profile along the surface element and contributes to homogenizing the temperature of the surface element and increasing the heat transfer performance.
- the heat exchanger can be a liquid-gas heat exchanger, for example a water-air heat exchanger.
- the heat exchanger can be designed as a finned tube heat exchanger as described in the introduction, the partition between the first fluid (e.g. water) and the second fluid (e.g. air) being formed by the tube wall of the tube or tubes.
- the fluids water and air are to be understood as pure examples, which can also stand for other liquid and gaseous fluids.
- the inside of the tube can be in contact with a liquid, first fluid.
- the heat transfer resistance at this interface is small due to the liquid state of the first fluid. Accordingly, no surface enlargement is required on the inside of the tubes.
- a gas flow is conducted in cross flow, the main flow direction of which is perpendicular to the pipe axis.
- the interfaces on the outer sides of the tubes, which are in contact with the gaseous, second fluid, have a higher heat transfer resistance per unit area of the partition wall surface.
- the surface of the partition wall of the heat exchanger according to the invention is enlarged on at least this side by ribs in the form of the surface elements described.
- Such surface-enlarging surface elements can also be arranged in other heat exchangers according to the invention on both sides of the partition, for example in a gas-gas heat exchanger.
- the following explanations relate mainly to a liquid-gas heat exchanger with a surface enlarged only on one side on the gas side. With corresponding modifications, however, the explanations also apply to other heat exchangers with surfaces of the partition wall enlarged on both sides, for which no exemplary embodiment is explicitly named.
- the surface elements can have any shape. For example, square, round or oval shapes of the surface elements are common.
- the shape of the surface element can be adapted to the cross section of the tube, so tubes with a circular cross section can have surface elements with a round circular shape.
- the reinforcement beads extend over the entire height of the surface element, i.e. up to the outer edge of the surface element.
- the reinforcing beads taper along the height of the surface elements from the partition. “Tapering” means that the cross-sectional area of the reinforcing beads starts from the partition wall along the height of the surface element to the outer edge of the surface element. The cross-sectional shape of the reinforcement beads is retained.
- the apex of the convex recesses is 40% of the total height of the surface element.
- the convex recesses are parabolic.
- the heat-conducting cross section of the surface element increases square with the radius of the surface element, so that the area of the surface elements is effectively reduced by parabolic recesses.
- the heat exchanger is a finned tube heat exchanger with at least one tube for the flow of a first fluid inside the tube and with surface elements which enlarge the surface of the tube and around which a second fluid can flow in cross flow to the first fluid.
- the tube forms the partition of the heat exchanger.
- the surface elements of finned tube heat exchangers are called fins.
- the surface elements or ribs protrude from the tube and have reinforcing beads, the reinforcing beads extending away from the tube.
- the thermal conductivity of the fins of finned tubes is a material property of the material used to manufacture the fins.
- a large cross-sectional area transverse to the direction of heat conduction is required for a large heat flow.
- the heat exchanger according to the invention uses surface elements as the ribs, which have spaced-apart reinforcing beads and surface areas of reduced thickness between the reinforcing beads. Because of their small thickness, these surface areas have a high thermal conductivity.
- the reinforcement beads on the other hand, have a larger cross-section and a low thermal conductivity, which is also sufficiently small for heat transport over longer lengths.
- the cross-section of the reinforcing beads is in contact with the pipe or the pipe wall or other partition and extends away from the pipe. In other words, the reinforcing beads are arranged orthogonally or at an angle to the tube wall, but not parallel or otherwise spaced apart from the tube wall.
- the reinforcing beads extend orthogonally to the surface of the tube.
- the reinforcing beads can extend radially and, in the case of flat partition walls, orthogonally to the partition wall, so that the heat is conducted along a short path away from the partition wall or to the partition wall.
- the reinforcing beads can also run differently towards the pipe for geometric or fluidic reasons.
- the diameter of the circular cross section of the reinforcing beads on the partition is at least twice as large as the thickness of the surface element.
- the reinforcing beads and the convex recesses of adjacent surface elements are arranged offset from one another, forming an offset in a flow direction of the second fluid between the surface elements.
- the wave-shaped fluid flow can also be regarded as a flow-favorable turbulence, whereby an increased convective heat transfer from the surface elements and partition walls to the flowing fluid or vice versa is achieved.
- the good heat conduction due to the presence of the reinforcing beads and the convex recesses leads to a relatively large temperature difference between the surface element and that of the surface element surrounding medium. As a result of the large temperature difference, a large heat flow between the surface element and the surrounding medium and, consequently, a large thermal output of the heat exchanger according to the invention are achieved.
- Adjacent surface elements can be attached to a partition, for example on a pipe. However, surface elements emanating from adjacent partition walls can also encompass each other like a comb.
- the tube of the finned tube heat exchanger is designed as an oval tube, the cross section of which is formed from two semicircles and two straight lines connecting the semicircles.
- the surface elements have an oval shape and are arranged in a plane orthogonal to a longitudinal axis of the tube. Adjacent surface elements are arranged parallel to one another along the longitudinal axis of the tube
- the reinforcing beads can be positioned almost perpendicular to the flow, parallel and at a constant distance from each other. Maximized convective heat transfer between adjacent surface elements can be achieved. Due to the offset reinforcing beads in opposing, i.e. a wave-like flow can be formed to adjacent surface elements, which further improves the heat transfer.
- the length of the straight line of the cross section of the oval tube is at least once as large as the diameter of the semicircle of the cross section of the oval tube, in particular 2.5 times as large.
- FIG. 3 is a view of the finned tube heat exchanger according to the invention in the viewing direction along the tube,
- Fig. 4 is a view of the finned tube heat exchanger according to the invention in the viewing direction transverse to the tube and
- Fig. 5 is a schematic representation of experimentally determined heat flow densities.
- Fig. 1 shows an embodiment of the heat exchanger 1 according to the invention, specifically a finned tube heat exchanger, in sections in a perspective view.
- the oval tube 2 can be seen.
- the walls of the tube 2 are partition walls between a first fluid inside the tube 2 and a second fluid outside the tube 2. Heat is exchanged between the first and the second fluid through the partition wall or the tube wall, without the first and the second Fluid come into contact with each other.
- the tube has 2 surface-enlarging fins, which give the finned tube heat exchanger its name.
- the fins connected to the tube are designed as low-volume and essentially two-dimensional surface elements 3.
- the surface elements 3 have pin-shaped reinforcing beads 4 with a round cross section. These reinforcing beads 4 extend from the tube 2 to the outer edge 31 of the surface elements 3. Between the reinforcing beads 4, the surface element 3 has surface areas 5 which have a smaller thickness than the reinforcing beads 4.
- the reinforcing beads 4 are massive material thickenings of the material of the surface element 3, which in the exemplary embodiment shown extend over the entire height of the surface element 3 to the outer edge 31 and taper outwards.
- the reinforcing beads 4 thus have a large cross-sectional diameter directly at the interface to the tube 2, while the diameter of the reinforcing beads 4 on the outer edge 31 of the surface element 3 is the same or only slightly larger than the thickness of the surface areas 5.
- the reinforcing beads 4 improve the heat transport within the surface element 3 from the tube 2 to the outer edge 31 or vice versa, as is exemplified by the arrows in three reinforcing beads 4.
- the direction of heat transport depends in a known manner on which of the two fluids is warmer inside the tube 2 and outside the tube 2.
- the surface element 3 has convex recesses 6 in the area of some of the surface areas 5, which extend from the outer edge 31 of the surface element 3 in the direction of the tube 2 and thereby reduce their width.
- the width of one of the recesses 6 is measured along the planar extent of the surface element 2 and thus perpendicular to the thickness of the surface element 3.
- the recesses 6 represent the complete absence of the material of the surface element 3 in the region of the recesses.
- the recesses 6 do not extend to the tube 2, but only up to a defined height within the surface element 3, the height starting from the outer surface of the Tube 2 is measured.
- the apex of the recess 6 thus lies at this defined height, which is greater than or equal to 30% and less than or equal to 70% of the height of the surface element 3.
- the height of the surface element 3 is the maximum height of the outer edge 31 of the surface element 3.
- the cutouts 6 are parabolic and extend to a height of approximately 40% of the height of the surface element 3.
- the convex recesses 6 serve to reduce the heat-transmitting surface of the surface element 3 with the height starting from the tube 2. This avoids an increase in the heat-conducting cross-sectional area of the surface element with increasing height. Since such an increase in the heat-conducting cross-sectional area occurs primarily in areas of the surface element 3 which adjoin round areas of the tube 2, the cutouts 6 are mainly formed in these areas in the exemplary embodiment shown. On the other hand, the increase in cross-sectional area does not occur or only occurs to a small extent in surface areas 5 that adjoin the straight areas of the oval tube 2 used here, so that these surface areas 5 cannot have any cutouts 6. In the exemplary embodiment shown, this is the case for at least some of the surface areas 5. FIG.
- FIG. 2 shows a section of the heat exchanger from FIG. 1 schematically in a side view of the pipe 2.
- the side view shown shows two surface elements 3 arranged parallel to one another, the reinforcing beads 4 and in the straight region 21 also the surface regions 5 being clearly visible, while the cutouts are not visible.
- the flow of the second fluid outside the tube 2 is shown schematically in FIG. 2 using flow lines 7.
- the reinforcing beads 4 and the recesses disrupt a laminar flow between adjacent surface elements 3 by causing turbulence. The turbulence improves the heat transfer between the second fluid and the surface element 3.
- the reinforcing beads 4 of adjacent surface elements 3 are each arranged with an offset 8 to one another in the flow direction, which runs from bottom to top in the illustration. Due to the offset 8, the turbulence on the individual reinforcement beads 4 and the cutouts overlap to form the flow-favorable wave profile outlined with the flow lines 7.
- FIGS. 3 and 4 show a very specific dimensioning example of the finned tube heat exchanger from FIGS. 1 and 2 in two different views along the tube 2 and transversely thereto.
- the tube 2 is designed here as an oval tube, which opposes the flow shown in FIG. 2 with the streamlines 7, with the same cross-section, a lower resistance than a round tube of the same cross-sectional size.
- the concrete oval tube has an outer diameter 9 of 16 mm of its semicircular areas and a length 10 of the straight side areas 21 of 18 mm.
- the ratio of the straight length 10 to the diameter 9 is greater than 1, in the present case 1, 125.
- the exact size of this ratio can be used as an optimization parameter when designing the heat exchanger on the basis of predetermined framework conditions.
- the surface element 3 has a height 11 of 44.5 mm, which is measured from the outer surface of the tube 2 in the Geiad area 21 to the outer edge 31 of the surface element 3.
- the recesses 6 have a width 12 of 21 mm on the outer edge 31 of the surface element 3 and extend from the outer edge 31 over a length 13 of 26.5 mm in the direction of the tube 2. The apex of the recesses 6 is thus approximately 40% of the amount 1 1.
- the reinforcing beads 4 have a diameter 14 of 4 mm at the interface with the tube 2, which diameter continuously decreases towards the outer edge 31 of the surface element 3.
- the surface areas 5 have a small thickness 15 of only 1 mm and the reinforcing beads 4 with a maximum diameter of 4 mm have a larger cross section than the surface areas 5 or a thickness four times as large.
- the ratio of the maximum diameter of a reinforcement bead to the thickness of a surface area can also be different, although it should be greater than or equal to 2.
- Two adjacent surface elements 3 are arranged parallel to one another along the tube 2, ie along the direction of flow of the fluid inside the tube 2, at a distance 16 of 12 mm. It can be seen in the detail from FIG. 4 that the left surface element 3 has three reinforcing beads 4 in the flat surface area, the Straight region 21, the oval tube 2 has.
- the right-hand surface element 3, on the other hand, has only two reinforcing beads 4 in the same cutout, the reinforcing beads 4 on the adjacent surface elements being arranged offset to one another. This offset of the reinforcing beads 4 and also of the cutouts, which cannot be seen in FIG. 4, continues over the entire extent of the two surface elements 3.
- the reinforcing beads, surface areas and recesses of the surface element which is arranged behind the front surface element in the viewing direction, are at least partially visible in the recesses 6 of the front surface element 3.
- the flow profile outlined in FIG. 2 is realized with the flow lines 7 by the offset. Furthermore, the offset 8 of the cutouts 6 and the reinforcing beads 4 leads to large temperature differences between the fluid 2 and the surface element 3, which has no cutout at any given location. As a result, large heat flow densities are possible.
- FIG. 5 shows the heat flow density that was achieved with the aid of a finned tube with 18 surface elements for a given inflow velocity of the fluid that flows around the finned tube and the surface elements.
- the curve with the full boxes shows the measured heat flow density for a manufactured finned tube with conventional surface elements, i.e. with surface elements without reinforcing beads and without recesses, while the curve with the empty boxes shows the measured heat flux density for a prototype finned tube with surface elements according to the present invention, the outer dimensions of the tube and the surface elements and the material used being the same in each case.
- the heat flow density is up to 90% higher than when using conventional surface elements.
- adjacent surface elements 3 are mounted on a tube 2.
- adjacent upper surface elements 3 are mounted on adjacent tubes 2 and the ribs of adjacent tubes intermesh like a comb.
- a person skilled in the art can derive further exemplary embodiments from the examples above in adaptation to a given task.
Landscapes
- Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Geometry (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102018129788.2A DE102018129788B3 (de) | 2018-11-26 | 2018-11-26 | Wärmeübertrager mit konvexen Aussparungen der Rippenflächen und integrierten Materialaufdickungen |
PCT/EP2019/081270 WO2020109013A1 (de) | 2018-11-26 | 2019-11-14 | Wärmeübertrager mit oberflächenelementen mit konvexen aussparungen und integrierten materialaufdickungen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3850293A1 true EP3850293A1 (de) | 2021-07-21 |
EP3850293B1 EP3850293B1 (de) | 2022-05-25 |
Family
ID=68105511
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19805232.6A Active EP3850293B1 (de) | 2018-11-26 | 2019-11-14 | Wärmeübertrager mit oberflächenelementen mit konvexen aussparungen und integrierten materialaufdickungen |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3850293B1 (de) |
DE (1) | DE102018129788B3 (de) |
WO (1) | WO2020109013A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112312752B (zh) * | 2020-11-27 | 2024-04-16 | 浙江工业大学 | 一种可用于大功率机车的管片式散热器的优化结构 |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE160351C (de) | 1904-04-07 | 1905-05-10 | Heiz- oder kuhlkörper | |
GB436656A (en) | 1934-04-16 | 1935-10-16 | Francis William Green | Improvements in heat-exchange tubes |
US2402262A (en) * | 1943-08-30 | 1946-06-18 | American Coils Co | Heat exchange fin |
DE1910549U (de) * | 1964-12-11 | 1965-02-25 | Chester H Kirk | Lamellenrohr fuer heiz- und kuehlzwecke. |
CH435346A (de) | 1964-12-11 | 1967-05-15 | Howard Kirk Chester | Lamellenrohr für Heiz- oder Kühlzwecke |
US3311163A (en) | 1965-06-25 | 1967-03-28 | Twin Temp Inc | Heat exchanger |
CH435436A (it) | 1966-04-22 | 1967-05-15 | Thomson Italiana Societa Per A | Dispositivo elettronico per la frenatura mista di motori elettrici trifasi per mezzo di condensatori e di corrente continua |
DE7020851U (de) | 1970-06-04 | 1970-09-03 | Benteler Werke Ag | Waermeaustauscher fuer heiz- und kuehlgeraete. |
DD283299A7 (de) * | 1988-07-25 | 1990-10-10 | Veb Schwermaschinenbau "Karl Liebknecht" Magdeburg,Dd | Rippenrohr mit profil |
DE4207597A1 (de) | 1992-03-10 | 1993-09-23 | Zl Cryo Technik Gmbh Industrie | Waermeaustauschelement und waermetauschereinheit |
JPH0979357A (ja) * | 1995-09-19 | 1997-03-25 | Daihatsu Motor Co Ltd | 車両のフィン付冷却パイプ構造 |
DE20021348U1 (de) * | 2000-12-16 | 2001-05-10 | Pluggit International N.V., Curaçao, Niederländische Antillen | Kanalrohr |
US20100282456A1 (en) * | 2009-05-06 | 2010-11-11 | General Electric Company | Finned tube heat exchanger |
-
2018
- 2018-11-26 DE DE102018129788.2A patent/DE102018129788B3/de not_active Expired - Fee Related
-
2019
- 2019-11-14 WO PCT/EP2019/081270 patent/WO2020109013A1/de unknown
- 2019-11-14 EP EP19805232.6A patent/EP3850293B1/de active Active
Also Published As
Publication number | Publication date |
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DE102018129788B3 (de) | 2019-10-24 |
EP3850293B1 (de) | 2022-05-25 |
WO2020109013A1 (de) | 2020-06-04 |
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