EP0268831A1 - Lamelle - Google Patents

Lamelle Download PDF

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Publication number
EP0268831A1
EP0268831A1 EP87115457A EP87115457A EP0268831A1 EP 0268831 A1 EP0268831 A1 EP 0268831A1 EP 87115457 A EP87115457 A EP 87115457A EP 87115457 A EP87115457 A EP 87115457A EP 0268831 A1 EP0268831 A1 EP 0268831A1
Authority
EP
European Patent Office
Prior art keywords
lamella
bulges
fluid
heat exchanger
flow
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
Application number
EP87115457A
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German (de)
English (en)
Other versions
EP0268831B1 (fr
Inventor
Roland Dipl.-Ing. Haussmann
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.)
Thermal-Werke Warme- Kalte- Klimatechnik GmbH
Original Assignee
Thermal-Werke Warme- Kalte- Klimatechnik GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Thermal-Werke Warme- Kalte- Klimatechnik GmbH filed Critical Thermal-Werke Warme- Kalte- Klimatechnik GmbH
Priority to AT87115457T priority Critical patent/ATE52847T1/de
Publication of EP0268831A1 publication Critical patent/EP0268831A1/fr
Application granted granted Critical
Publication of EP0268831B1 publication Critical patent/EP0268831B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F28F1/32—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 having portions engaging further tubular elements

Definitions

  • the invention relates to a fin made of AI or an AI alloy for the common ribbing of several heat exchanger tubes of a tube fin heat exchanger in motor vehicles according to the preamble of claim 1.
  • Heat exchanger fins of this type are known from DE-OS 25 30 064. They are acted upon by outside air as the first heat exchange fluid, while a second heat exchange fluid is guided in the heat exchanger tubes, which are ribbed by the fins.
  • Fins for tube fin heat exchangers of motor vehicles are now generally made of Al or Al alloys, in very thin wall thicknesses between typically 0.08 and 0.15 mm.
  • a production of such lamellae from sheet iron is practically out of the question for reasons of fourfold - poorer thermal conductivity, corrosion and weight reasons.
  • Stainless steel sheet would be corrosion-resistant, but only accounts for about 10% of the thermal conductivity of an AI lamella.
  • Manufacture of such lamellae from Cu would meet the requirements with regard to corrosion resistance or even heat conduction, which is even better, but differs except in exceptional cases, e.g. with some engine coolers or solderable heating heat exchangers, - for reasons of weight and the Cu price in comparison with the AI price.
  • heat exchangers for motor vehicles in development as large series parts have been optimized not only according to performance data, but also according to weight, construction volume, use of materials and the like. result, which does not allow a comparison with heat exchangers from other applications with smaller quantities up to the individual production without further ado.
  • the highest possible heat transfer coefficient between the lamella on the one hand and the gaseous first fluid acting on the latter on the other hand is to be achieved with simple, permanent means.
  • This increase in the heat transfer value brings savings in the investment area and in operation, since with the same amount of heat to be transferred and the same operating temperatures, the heat exchanger front surface (exposed surface) and the structural depth can be reduced or the distance between the heat exchanger fins can be increased.
  • the heat exchanger lamella is used for tubular lamella heat exchangers in motor vehicles, the reduction in the construction volume and the associated reduction in the weight of the heat exchanger are of crucial importance. This applies both to the possible application on motor vehicle coolers or heating heat exchangers and to the preferred applications for condensers or evaporators in motor vehicle air conditioning systems.
  • the heat exchange between the two fluids takes place by means of heat radiation, heat conduction and convection, but in particular by means of convection, in which the heat is transferred by moving material particles.
  • the heat exchange by convection in particular depends largely on the type of flow of the gaseous first fluid around the tubes and the heat exchanger fins.
  • a further reduction in the heat exchange also results in the flow dead spaces that build up behind pipe areas in the flow direction of the first fluid, ie in their flow shadows. Due to a low-intensity stationary vortex formed by the flow behind the heat exchanger tubes, the local heat transfer numbers there are considerably smaller than in the areas touched by the main flow. Also, as the lamella thickness progressively decreases, the thermal resistances in the lamella have to be taken into account, which results in the requirement for a heat flow density in the lamella that is as uniform as possible with a constant pipe spacing, which in turn is achieved by adapting the local heat transfer coefficients. In order to meet these requirements, it is known to profile the lamella in various ways.
  • One of the simplest known profiles is a corrugated design of the lamella in the direction of flow of the first fluid, so that the wave crests and troughs run transversely to this direction of flow (cf. for example the generic DE-OS 25 30 064, but also for example the DE-OS 27 56 941).
  • This corrugation on the one hand slightly increases the flow path and thus the flow velocity between the fins, and on the other hand, due to the required deflection of the air in the corrugated fins, an at least partial rebuilding of the laminar boundary layer is achieved after each wave crest, thereby enlarging the boundary layer and thus degradation of the external heat transfer coefficient corresponding to the above equation can be at least partially avoided.
  • Corrugation of the lamella surface also means that there is no significant reduction in the dead space behind the pipes and no optimal distribution of the local heat transfer coefficients with respect to a uniform radial heat flow density.
  • Corrugation angles of approx. 45 ° lead to an enlargement of the boundary layer through which the heat has to be transported as a result of molecular conduction of the air, since the air is only used to a small extent flows parallel to the corrugation and a stationary vortex of low intensity forms in each trough.
  • the bleed edges are also limited to only a small proportion of the area of the lamella, while a large area of the lamella without profile-reducing profiles is designed as a smooth lamella.
  • a more uniform distribution of lamellar openings and guide bars is given in the known arrangement (DE-OS 25 18 226) of a heat exchanger lamella for the chemical industry, in particular the petroleum industry, in which a large number of guide bars of small width are provided between two exclusion points in the lamella which is to be forced to constantly rebuild the laminar boundary layer.
  • the air-side pressure loss was reduced and the required manufacturing tools were simplified while maintaining a high heat transfer coefficient by simplifying at least one opening and at least one edge of the opening between the adjacent connection points of the same row Extending in rows and adjacent to a connection point, a guide web for the gaseous fluid, which is extended from the lamella plane, is provided. Through the walkway. on the one hand the laminar boundary layer is broken down, on the other hand the air is guided so that the formation of a flow shadow behind the pipes is reduced.
  • the lamella stability is reduced, so that with a given lamella stability, the material thickness must be increased, since the use of harder lamella material due to the maximum achievable height of the sleeve-shaped connection points of up to 2.4 mm is not possible.
  • Even with a material thickness increased from 0.12 to 0.15 mm there are certain stability problems in handling during the production process in a lamella package in which the tubes have not yet been inserted into the sleeve-shaped connection points, so that relatively long production times are accepted have to. Also, the problem of contamination and the seizing of water when the fin falls below the dew point, analogous to the heat exchanger fin according to DE-OS 31 31 737, has not yet been completely solved.
  • the corrugation of the lamella is so short-wave that a tear hole with two flaps running parallel to each other occupies two flanks of the corrugation, bridging each of a wave crest. In the area of the tear hole there is no corrugation and its desired effect.
  • This design with the tear holes and the sharply curved lobes, which take up the entire distance between adjacent lamellae, is predestined to hold on to condensation water that forms when the temperature falls below the dew point and to trap dirt.
  • the lobes that occupy the entire lamella spacing are relatively large-area turbulence generators with their own slipstream effect for the gaseous first fluid, with the associated reduction in the heat transfer between the lamella and the gaseous first fluid.
  • solderable fins primarily made of copper
  • solderable fins are already known from US Pat. No. 1,575,864, which dates back to 1926, and in which protruding bulges protrude on one or both sides, in particular in the shape of a cone, from a flat fin, which are closed in the fin plane are.
  • Such bulging of flat slats has been considered again and again since the 1930s, also by the applicant, with the most varied of variants, but was also rejected just as often because the achievable surface enlargement and the turbulence increase for the required power density in comparison with the respective time otherwise known lamella constructions of the type discussed above are not sufficient.
  • this prior publication does not provide a model for arranging bulges of this type, if necessary, in such a way that the flow is directed into slipstream areas behind the pipes. This is not necessary because of the use of copper as lamella material in the known heat exchanger.
  • the invention has for its object to provide a fin for the common ribbing of several heat exchanger tubes of a tube fin heat exchanger in motor vehicles, which combines excellent heat transfer conditions with good drainage of condensed water when the temperature falls below the dew point and good stability of the fin and, if possible, only requires simple manufacturing tools and low maintenance.
  • the outstanding feature of the lamella according to the invention is that a further increase in the external heat transfer coefficient a a is achieved by the further local profiling impressed on the flanks of the basic corrugation of the lamella in the form of completely or almost completely closed bulges of a smaller height than the lamella distance. so that even those previously achieved only with slotted slats or with perforated slats (DE-PS 33 36 985), which were previously considered to be optimal heat transfer coefficients, can still be exceeded significantly, for example with approximately 8 to 20%. There is only a slight increase in the air-side (first fluid) pressure loss.
  • the turbulence-enhancing and boundary layer-reducing effect of the features fully benefits the lamella surface located downstream, without this being compensated again by local enlargements of the boundary layer.
  • the increase in surface area obtained through the characteristics also increases performance.
  • the bulges can be formed and distributed so that there is practically the same amount of heat flow density in concentric circles around the connection sleeves, so that this is distributed invariably with respect to the connection sleeves.
  • An embodiment of the heat exchanger lamella according to the invention is particularly recommended when it is used in the motor vehicle as an evaporator or air cooler, in which condensation water forms on the lamella due to the temperature falling below the dew point. Due to the practical elimination of all exhibitors, slits or openings in the lamella, the condensed water can flow off undisturbed, so that the water retention capacity is always lower. Due to the smaller amount of condensed water held between the heat exchanger fins by adhesion in the heat exchanger fin according to the invention, on the one hand the external heat transfer number 1 is further improved, since the heat resistance is reduced by the condensed water, and on the other hand the fin surface dries faster, which reduces the activity of odor-forming bacteria .
  • Another advantage of the lower water retention capacity of the heat exchanger lamella according to the invention is the better suitability for reheat operation (in vehicle air conditioning systems), since the amount of water evaporated and thus the fogging of the windshield after the compressor has been switched off is less.
  • the stability is greatly increased, in particular in comparison to slotted lamellae, so that the lamella thickness can be significantly reduced with the same strength.
  • the fin thickness can be significantly reduced without reducing the performance of the above-mentioned high-performance fins according to DE-PS 33 36 985. Since the heat exchanger fins are not manufactured in large numbers for the automotive industry. the material cost reduction as well as the weight reduction and the associated improvement of the driving characteristics as well as the reduction of the petrol consumption is of decisive advantage.
  • Another advantage in the large-scale production of the heat exchanger lamella is the elimination of the cutting punches, which are required to produce the openings in the lamella according to DE-PS 33 36 985 and require a high level of maintenance, while the tool inserts for producing the profile of the lamella according to the invention are almost maintenance-free are.
  • the average specialist will select the size, shape, number and distribution of the bulges in a targeted manner. So he will choose not too little bulges, but also not too many small bulges, since otherwise the air of the first fluid cannot follow the lamella. Bulges that are too large, on the other hand, would already create the danger of creating your own current dead spaces. They can also be used less for optimal division into current threads.
  • the wavelength of the corrugation is also related to the size of the bulges, since each bulge is only assigned to one flank of the corrugation and is therefore set back in its respective foot area with respect to the next wave crest.
  • the features according to claims 2 or 3 preferably extend only over part of the flank length of the corrugation, which in turn is optimally selected according to claims 4 and 16, respectively.
  • the arrangement of the knob-like bulges depending on the pipe distribution is also important for increasing the heat transfer coefficient. While within the scope of claim 8, for example at small distances between the connecting sleeves transversely to the air direction, two bulges arranged in alignment in the air direction Reaching a predetermined heat transfer coefficient with a low pressure loss - can already be sufficient (cf. also FIG. 1), the arrangement of the bulges can be offset from the air direction in the context of claim 9 with higher power requirements (cf. also FIG. 2).
  • the optimal geometry of the zigzag curl is defined in claim 4.
  • the number of wave crests results in an effective height of the corrugation, measured at right angles to the base area or main plane of the lamella.
  • the height of the bulges is measured as a protrusion perpendicular to the flap flank and is at least 15%, maximum 80%, but preferably 30 to 50%, of the fin spacing in the tube fin heat exchanger in the sense of claim 19.
  • Claims 17 and 18 relate to the already mentioned lamellar spacing via the connecting sleeves and underline the necessity that the entire lamellar surface should have a profile that is as uniform as possible in order to achieve a maximum heat transfer coefficient with a relatively low air-side pressure loss. According to claim 18, surfaces with an excessively large angle with respect to the fin base are to be avoided, since in the fin package of the tube fin heat exchanger the fin spacing is reduced by the factor cos 6 at these points and thus the water holding capacity increases as the fin spacing decreases.
  • bulges are given. Although currently tapered shapes are considered to be particularly useful, other shapes can also be permitted for the purpose of increasing turbulence and increasing the surface area according to claims 12 and 13, which shapes can be embossed without tearing the lamella. Axially symmetrical bulges are preferred; Elongated bulges, for example, are also possible, e.g. with oval cross section.
  • Claim 10 deals with a special arrangement of the bulges which, in order to obtain a constant heat flow density in the lamella, are arranged such that in the region of low flow velocities, i.e. large pipe distances, more bulges between two adjacent connection sleeves and in the area of high flow velocities, i.e. Small pipe distances between two adjacent connection sleeves, fewer or in the limit case no characteristics are available.
  • all of the bulges and all connection points protrude from the same side of the lamella.
  • the increased temperature gradient in the direction of the heat flow lines from the connection point to the center of the bridge-like strip then leads to a reduced tempera difference between the bridge-like strip and the gaseous first fluid flowing on the outside of the heat exchanger lamella, as a result of which the amount of heat transferred is reduced and the locally very high heat transfer coefficients cannot be converted accordingly into the transferred heat output.
  • fins 1 of a tube fin heat exchanger are shown in various embodiments, in which by shaping finned sheet with the preferred thickness of 0.07 to 0.5 mm, preferably 0.07 to 0.15 mm, from Al or an Al alloy thereof, the surface profiling described below is produced by stamping, drawing or embossing processes.
  • connecting sleeves 4 for receiving heat exchanger tubes 14 extend in each heat exchanger fin 1 (cf. FIGS. 8 and 9).
  • the connecting sleeves 4 are each designed to receive a heat exchanger tube 14 carrying the second fluid as a cylindrical, elliptical or differently shaped sleeve so that in the direction of the first gaseous fluid which acts on the heat exchanger lamella 1 itself, an outer diameter which is defined except for slight deviations is produced.
  • the connecting sleeves 4 are bent on their outer free edge, in the manner of an outer ring flange, to form a collar 13, in order to thereby fix the mutual spacing of the fins 1 in a fin package of a tube fin heat exchanger 22 (see FIGS. 8 and 9) .
  • the connecting sleeves 4 in turn protrude from an annular receiving trough 3 formed in the lamella 1, in which the corresponding collar 13 of a connecting sleeve 4 of an adjacent lamella 1 engages on the side facing away from the connecting sleeve.
  • the fins 1 are acted upon by ambient air as a gaseous first fluid which, via the fin 1 in the tube fin heat exchanger 22, enters into heat exchange with the second fluid carried in the heat exchanger tubes.
  • the flow direction 2 of the first fluid runs transversely to the flow direction of the second fluid following the axial direction of the heat exchanger tubes 14 or the inlet sleeve 4.
  • the flow direction 2 of the first fluid is indicated by directional arrows in the plan views of the heat exchanger fin 1 shown.
  • connection sleeves 4 are arranged in rows transverse to the flow direction 2 of the first fluid. Embodiments are possible in which successive rows of connecting sleeves 4 are set to a gap (FIGS. 1 to 4), as well as those in which adjacent connecting sleeves 4 successive rows are aligned in flow direction 2 (not shown in the drawing). Both embodiments of the slat 1 are possible.
  • the connection sleeves 4 are preferably designed identically. In each row, adjacent connection sleeves have 4 equal distances. The distances are generally the same in different rows. Likewise, the distance between two successive rows in the flow direction is also the same. In the embodiment according to FIG.
  • two conical bulges 6 are arranged on a zigzag-shaped corrugation between two adjacent connection sleeves 4 of the same row in such a way that the bulges 6 are symmetrical on the one hand between the two adjacent connection sleeves 4 of a row and on the other hand approximately in the middle between wave crest 5 and trough 11 are arranged.
  • each flank 20 of the corrugation is provided with bulges 6, which each occupy between 50 and 80% of the flank length measured in the flow direction 2.
  • FIG. 2 shows an advantageous modification of the aligned arrangement of the bulges 6 according to FIG. 1, so that they are arranged one behind the other in relation to the flow direction 2 of the first fluid according to FIG. 2.
  • the offset arrangement of the bulges 6 results in a higher pressure loss, but a further increase in the heat transfer coefficient can also be achieved in parallel.
  • FIG. 3 A further optimization of the basic idea of FIG. 2 is shown in FIG. 3, in which several bulges 6, in the special case of FIGS. 3 and 5, are arranged offset to the flow direction 2 between two connecting sleeves 4 of the same row of tubes.
  • three and two bulges 6 are alternately arranged on the flat lamella surface between the crest 5 and the trough 11 between two adjacent connecting sleeves 4 of a row of heat exchanger tubes 14 or connecting sleeves 4 in the flow direction 2 of the first fluid.
  • the distribution of the bulges 6 takes place symmetrically to the imaginary center line between adjacent connection sleeves 4, as in the case of FIG. 4 discussed below, with an equidistant distribution of the bulges 6 of a group of bulges 6 lying between two adjacent connection sleeves 4.
  • the height f of the bulges 6 is to be designed in all the embodiments of FIGS. 1 to 4 such that, depending on the permissible pressure loss, it is preferably 30 to 50% of the existing lamella spacing b.
  • the distance a between the centers of adjacent bulges 6 is expediently 1 to 3 times, preferably 1.3 to 2 times the diameter of the base area of the individual bulges 6.
  • FIG. 4 A further step in the direction of a in concentric circles around the connecting sleeve 4 uniform heat flow density or homogeneous external heat transfer coefficient distributed over the entire fin surface is shown in FIG. 4, in which the number of flanks 20 between two adjacent connecting sleeves 4 of a row of pipes has been increased from 2 to 3 compared to FIG. 3.
  • eight bulges 6 can be positioned between two adjacent connection sleeves 4 of a row of heat exchanger tubes 14 or connection sleeves 4 in an arrangement offset from the air direction 2, specifically in the flow direction 2 in the sequence 3 - 2 - 3.
  • a further increase in the number of wave crests 5 is conceivable for smaller lamella spacings b.
  • the limit to the increase in the number of waves and bulges is given by the air flow, which reacts in the event of a corrugation that is too fine and therefore an extremely high number of bulges associated with the formation of a greater thickness of the boundary layer 9 (see FIG. 6), since the Flow of the gaseous first fluid can no longer follow a very fine corrugation or bulge.
  • the tool cost is also increasing wall increased with increasing number of bulges, because the bulges 6 are embossed due to the required interchangeability of the tool profiles when worn with stamps that are embedded in a corrugated base plate, so that the tool costs increase with increasing number of stamps.
  • the length of the individual flanks 20 of the corrugation is expediently at least twice and at most five times the fin spacing b in the tubular fin heat exchanger.
  • a lamella 1 is shown in section. This figure shows the shape of all bulges 6 in one direction and the preferred relation of the heights f of the bulges 6 in relation to the lamella spacing b. There is also the effect of locally very large corrugation angles a, which lead to a local reduction of the lamella spacing from dimension b to g and thus to increased adhesive forces between the lamella 1 and condensation water droplets.
  • FIG. 6 on a lamella 1 (without features 6) designed according to the state of the art according to DE-OS 25 30 645, with exclusive corrugation by drawn flow lines, the increase in the boundary layer 9 that occurs when the corrugation angle 8 is too large is illustrated. Since the air cannot nearly follow the lamella 1, stationary vortices 10 of low intensity are formed in the troughs 11, which only have a slight effect on the depletion of the boundary layer and also adjust in temperature to the lamella 1, since they essentially are stationary and are not transported along with the turbulence bales in the main flow direction 2.
  • the resulting powers or pressure losses are plotted against the corrugation angle 8 in FIG. 7. It shows that from corrugation angles 6 of 20 ° no significant increase in performance is achieved and that there is only a steep increase in the air-side pressure losses at corrugation angles e of more than 20 °, since the resistance coefficient increases with an increased corrugation angle 0 due to the Redirection also increases the flow path and flow rate.
  • Fig. 8 it is shown how in a tube fin heat exchanger 22 (see FIG. 9) staggered heat exchanger tubes 14 are firmly connected to the connecting sleeves 4 of the individual fins 1 in a thermally conductive manner.
  • the attachment is carried out by the usual methods in the manufacture of tube fin heat exchangers, e.g. by expanding the heat exchanger tubes 2 and / or brazing.
  • the connecting sleeves 4 cause the spacing of adjacent plates 1 by a collar 13 at the free end of the respective connecting sleeve 4 engaging in an annular recess 3 on the rear of the foot zone of the next plate 1. This makes it possible that no additional bulges of the lamella have to take over spacer functions.
  • FIG. 9 show - schematically a whole tube fin heat exchanger 22, the fins of which are designed according to FIGS. 1, 2, 3 or 4 and are combined according to FIG. 8 into a fin package carried by heat exchanger tubes 14.
  • the individual heat exchanger tubes 14 are combined in terms of flow by means of reversing bends 24, optionally also using header boxes (not shown) or header tubes indicated in FIG. 9, in such a way that they partly cross-flow, partly cross-counter- and cross-countercurrent to the first fluid from a common inlet 26 can flow through a common outlet 28 of the second fluid.
  • the direction of flow of the second fluid is indicated by the arrows 30 at the inlet 26 and 31 at the outlet 28.
  • the flow direction 2 of the first fluid can be seen in the end view of the tube fin heat exchanger 22.
  • the tube fin heat exchanger 22 can be mounted by means of the fastening tabs 32.
  • the described features and properties of the new fins 1 also characterize the essential features, properties and in particular also quality features of the tube finned heat exchanger 22 having a packet of fins in the manner described.
EP87115457A 1986-10-22 1987-10-21 Lamelle Expired - Lifetime EP0268831B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87115457T ATE52847T1 (de) 1986-10-22 1987-10-21 Lamelle.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3635940 1986-10-22
DE19863635940 DE3635940A1 (de) 1986-10-22 1986-10-22 Lamelle

Publications (2)

Publication Number Publication Date
EP0268831A1 true EP0268831A1 (fr) 1988-06-01
EP0268831B1 EP0268831B1 (fr) 1990-05-16

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EP87115457A Expired - Lifetime EP0268831B1 (fr) 1986-10-22 1987-10-21 Lamelle

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EP (1) EP0268831B1 (fr)
AT (1) ATE52847T1 (fr)
DE (2) DE3635940A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0789216A3 (fr) * 1995-09-14 1998-04-01 Sanyo Electric Co. Ltd Echangeur de chaleur à ailettes ondulées et climatiseur équipé de celui-çi
EP1512931A1 (fr) * 2003-09-02 2005-03-09 Lg Electronics Inc. Echangeur de chaleur
EP1515107A1 (fr) 2003-09-15 2005-03-16 Lg Electronics Inc. Echangeur de chaleur
EP3231524A1 (fr) * 2016-03-28 2017-10-18 Howatherm Klimatechnik GmbH Procédé de fabrication d'un échangeur thermique à lamelles sur tubes et échangeur thermique et lamelles
WO2021098024A1 (fr) * 2019-11-21 2021-05-27 广州高澜节能技术股份有限公司 Ailette perfectionnée d'échange de chaleur pour refroidisseur d'air du type à pièce de manchon

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3918610A1 (de) * 1989-06-07 1990-12-13 Guentner Gmbh Hans Luftgekuehlter waermeaustauscher
DE102010023684A1 (de) 2010-06-14 2011-12-15 Howatherm-Klimatechnik Gmbh Lamellenrohrwärmeübertrager
DE102017120123A1 (de) 2017-09-01 2019-03-07 Miele & Cie. Kg Lamellenrohrwärmeübertrager

Citations (3)

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Publication number Priority date Publication date Assignee Title
US2046791A (en) * 1934-01-17 1936-07-07 Przyborowski Stanislaus Radiator
DE1501550A1 (de) * 1965-12-23 1969-09-11 Kuehlerbau Heinrich Schmitz & Querrippe fuer Waermeaustauscher
DE2530064A1 (de) * 1975-07-05 1977-01-27 Volkswagenwerk Ag Luftlamelle fuer einen leichtmetall- waermetauscher

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US1575864A (en) * 1922-10-19 1926-03-09 Mccord Radiator & Mfg Co Automobile radiator core
DE496733C (de) * 1928-10-27 1930-04-24 E H Hugo Junkers Dr Ing Rippenrohr-Waermeaustauschvorrichtung mit aus Blech von ueberall gleicher Dicke hergestellten Rippen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2046791A (en) * 1934-01-17 1936-07-07 Przyborowski Stanislaus Radiator
DE1501550A1 (de) * 1965-12-23 1969-09-11 Kuehlerbau Heinrich Schmitz & Querrippe fuer Waermeaustauscher
DE2530064A1 (de) * 1975-07-05 1977-01-27 Volkswagenwerk Ag Luftlamelle fuer einen leichtmetall- waermetauscher

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0789216A3 (fr) * 1995-09-14 1998-04-01 Sanyo Electric Co. Ltd Echangeur de chaleur à ailettes ondulées et climatiseur équipé de celui-çi
EP1512931A1 (fr) * 2003-09-02 2005-03-09 Lg Electronics Inc. Echangeur de chaleur
JP2005077083A (ja) * 2003-09-02 2005-03-24 Lg Electronics Inc 熱交換器
JP4607470B2 (ja) * 2003-09-02 2011-01-05 エルジー エレクトロニクス インコーポレイティド 熱交換器
EP1515107A1 (fr) 2003-09-15 2005-03-16 Lg Electronics Inc. Echangeur de chaleur
JP2005090939A (ja) * 2003-09-15 2005-04-07 Lg Electronics Inc 熱交換器
US7219716B2 (en) 2003-09-15 2007-05-22 Lg Electronics, Inc. Heat exchanger
EP3231524A1 (fr) * 2016-03-28 2017-10-18 Howatherm Klimatechnik GmbH Procédé de fabrication d'un échangeur thermique à lamelles sur tubes et échangeur thermique et lamelles
WO2021098024A1 (fr) * 2019-11-21 2021-05-27 广州高澜节能技术股份有限公司 Ailette perfectionnée d'échange de chaleur pour refroidisseur d'air du type à pièce de manchon

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Publication number Publication date
DE3635940A1 (de) 1988-05-05
EP0268831B1 (fr) 1990-05-16
DE3762772D1 (de) 1990-06-21
ATE52847T1 (de) 1990-06-15

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