EP2975350B1 - Échangeur thermique - Google Patents

Échangeur thermique Download PDF

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Publication number
EP2975350B1
EP2975350B1 EP15173792.1A EP15173792A EP2975350B1 EP 2975350 B1 EP2975350 B1 EP 2975350B1 EP 15173792 A EP15173792 A EP 15173792A EP 2975350 B1 EP2975350 B1 EP 2975350B1
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EP
European Patent Office
Prior art keywords
heat exchanger
surface structure
exchanger according
pipes
ribs
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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.)
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EP15173792.1A
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German (de)
English (en)
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EP2975350A1 (fr
Inventor
Thomas Gora
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.)
Kelvion Machine Cooling Systems GmbH
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Kelvion Machine Cooling Systems GmbH
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Priority to PL15173792T priority Critical patent/PL2975350T3/pl
Publication of EP2975350A1 publication Critical patent/EP2975350A1/fr
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Publication of EP2975350B1 publication Critical patent/EP2975350B1/fr
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    • 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
    • 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

Definitions

  • the invention relates to a heat exchanger with the features of claim 1.
  • Heat exchangers of the type in question have tubes which extend in an axial direction and are flowed through by a first fluid.
  • the tubes may be ribbed on the outside. Larger ribs can be interspersed by several tubes.
  • the ribs may be flat or contoured, in particular wavy or rippled. With corrugated or ribbed ribs it is possible to achieve better heat transfer, but with higher pressure losses compared to flat ribs. The pressure losses attributable to the changed flow conditions require more energy expenditure in forced-ventilation heat exchangers, since the pressure loss must be compensated for by correspondingly stronger fans.
  • ribs which have additional openings, so that the inflowing fluid can pass from one heat exchanger side of the rib to the other side of the rib.
  • turbulators at the additional openings can lead to the improvement of the heat transfer and, depending on the design, also reduce the pressure losses in comparison to the first two mentioned rib designs.
  • hygiene problems can occur in this rib design, since it is particularly in the area of the openings and adjacent to turbulators can come to the pollutions, which can be removed worse than with closed ribs.
  • the WO 2013/076990 A1 and WO 2014/167827 A1 show each rib arrangements for heat exchangers, which can be slipped over the tubes in a stacked arrangement.
  • One possibility is to form conical centering shoulders, which are part of an annular recess.
  • stacked fin arrangements on heat exchanger tubes It is provided a circumferential recess, which may be additionally interrupted to facilitate the outflow of medium.
  • a heat exchanger in which also a non-profiled ring is provided with a collar.
  • a second surface structure is provided with an annular circumferential, triangular in cross section recess. This depression is then followed by a zig-zag-shaped corrugated structure.
  • the object of the invention is to develop a heat exchanger to the effect that the heat transfer performance is increased at low pressure losses.
  • the heat exchanger according to the invention comprises tubes which extend in an axial direction.
  • the pipes are intended to be flown from the outside.
  • the tubes are externally in contact with ribs.
  • the ribs extend transversely to the axial direction of the tubes.
  • the ribs have openings for receiving the tubes.
  • the ribs have first and second areas. At least the second areas have a surface structure.
  • the term surface structure means in the present invention that the surface is not flat, that is profiled, in particular provided with embossments.
  • the first regions of the ribs can be free of a surface structure, that is to say they can be flat.
  • the first regions may also have a surface structure, that is, not be even.
  • the two surface structures differ in their structuring from each other.
  • first surface structures and second surface structures will be explained below, wherein the advantages of the invention over completely unprofiled ribs also arise when surface structures are arranged only in the second regions. An improvement is achieved by surface structures in the first and in the second areas.
  • the two surface structures are not flat in each case.
  • the first surface structure is a uniform repetition in the direction of flow of the tubes profiling.
  • the tubes are flowed transversely to the axial direction, that is radially.
  • the direction of flow is therefore perpendicular to the tubes.
  • a uniformly repeating profiling results in a wave-like expression.
  • a corrugation or a waveform to understand.
  • surface structures are to be recognized, like e.g. Zig-zag or sawtooth curves, ie profiles with sharp-edged transitions in the range of amplitudes.
  • Wave-like characteristics are not limited to strictly sinusoidal curves. It may also be combinations of wave-like and corrugated sections, but each repeat uniformly. The uniform repetition creates a wavefront which extends transversely to the direction of flow. The wavefront can be straight or curved. Significantly, it repeats uniformly at regular intervals.
  • the second surface structure deviates from the first surface structure and has at least one annular depression and, in addition, preferably at a radial distance to an annularly extending increase.
  • the at least one elevation and at least one depression surround the openings for receiving the tubes annularly.
  • the new rib design leads to improved heat transfer with only slightly higher pressure drops. This means that the size of the heat exchanger and thus the manufacturing costs can be reduced, with otherwise the same heat exchanger performance. Furthermore, the energy efficiency and / or the acoustic properties of the heat exchanger units can be improved, which is also due to the improved heat transfer and the only slightly higher pressure losses.
  • the design of the heat exchangers complies with current hygiene standards as the ribs do not have any slots, notches or openings.
  • the combination of two different surface structures contributes significantly to the improvement of the heat transfer.
  • the profiling leads to an increase in the flow velocity between adjacent ribs, since the flow is accelerated by the radial circumferential ridges and depressions in the region of the tubes. This leads to a remarkably improved heat transfer in a large part of the fin surface.
  • the special feature is that a stall is largely avoided, although the flow velocity is accelerated in the region of the tubes.
  • the surface structure of the ribs is preferably a combination of a corrugated or wave-shaped profile and an annular profile with radially encircling annular elevations and depressions.
  • This second surface structure is preferably sinusoidal in its radial propagation in cross section, so that this structure can be described as a wave propagating wavefront.
  • the first surface structure may have a sinusoidal but in particular a zigzag-shaped profiling.
  • a corrugated surface structure In the context of this application is also spoken of a corrugated surface structure.
  • the combination of a corrugated, in particular zig-zag profiling with the sinusoidal corrugated circumferential portions of the tubes results in a greatly improved heat transfer performance. Without the first surface structure, a large part of the flow would flow past the pipes at a greater distance.
  • the first surface structure mainly ensures that a larger part of the flow is brought closer to the tubes.
  • the second surface structure accelerates the flow radially to the tube and significantly increases the heat transfer area. At the same time, however, the heat transfer at the greater distance from the tubes is also improved by the first surface structure.
  • the second surface structure causes an increase in the heat transfer surface compared to a smooth in this area rib and thus improves the heat transfer performance.
  • the second surface structures each have exactly one annularly extending elevation and a single annular depression.
  • this second surface structure in each case has a plurality of annularly extending elevations and depressions. As the radial distance increases, the height of the ridges and valleys may decrease.
  • the wavelength of the second surface structure is tuned to the wavelength of the corrugated or wave-like first surface structure and is in an integer ratio +/- 10%. It is advantageous if the second surface structures have a radial outer diameter which corresponds to twice the wavelength of the corrugated first surface structure +/- 10%.
  • the recesses and elevations of the second surface structures are the same.
  • the center planes of the first surface structure and the second surface structures can be arranged at an axial distance from one another. That is to say, the second center plane, from which the depressions and elevations of the second surface structure are exposed, is arranged at an axial distance from the first center plane of the first surface structure.
  • the median plane of the first surface structure is the plane from which the corrugations or undulations on both sides of the medial plane are exposed.
  • the spacing of the center planes in this case preferably corresponds to the amplitudes of the elevations of the second surface structure +/- 10%.
  • the amplitudes of the first surface structure may correspond to the spacing of the center planes +/- 10%.
  • the amplitudes of the first surface structure are preferably the same size as the amplitudes of the second surface structure.
  • the height of the rib measured in the axial direction is as large as 3 amplitudes of the respective surface structures.
  • the tubes pass through the ribs at a distance which is twice the wavelength of the first surface structure. This distance is measured in the direction of flow radially to the tubes, wherein the axial directions of the tubes coincide with the troughs. That means in every second trough there is a pipe.
  • the tubes have a diameter which is within a range of 80 to 100% of the wavelength of the first surface structure. Therefore, the annular second surface structures have an inner diameter of 80 to 100% of a wavelength and an outer diameter of preferably 190 to 210%, in particular 200% of the wavelength of the first surface structure.
  • the second center plane coincides with the wave troughs of the first surface structure, so that no cracks occur in those regions which lie upstream and downstream of the tubes in the flow direction.
  • the flow may enter into the sinusoidal corrugated annular regions of the second surface structure in a manner accessible to a pipe through the corrugation trough of the corrugation, where the flow is passed and accelerated close to the pipe.
  • Each rib has two opposite sides which serve as heat exchange surfaces, with the sides, with the exception of the openings passing through the tubes, being free of further openings. Hygienic standards can be more easily adhered to because no soiling can stick to any openings. The pressure losses are accordingly low.
  • the rib design does not provide turbulence to improve heat transfer, but to increase the flow velocity between the ribs, and particularly near the tubes, without substantial flow separation.
  • the ribs have a predetermined distance from each other, which is determined by spacers or a collar on the ribs.
  • the collar increases the contact area between tube and rib and improves the heat transfer.
  • a mutual centering of adjacent ribs can take place via the collar.
  • an axially flared centering can connect radially outside of the unprofiled ring.
  • the collar Hold in this centering shoulder so that the openings in the ribs are aligned.
  • the collar may additionally be widened radially outwardly at one end. This creates a transitional area that serves as an insertion aid for a pipe.
  • the mutual centering in combination with an expansion on the collar simplifies the handling of a larger number of ribs during assembly.
  • FIG. 1 shows a rib 1 as part of a heat exchanger.
  • the heat exchanger comprises in addition to a plurality of mutually parallel ribs 1 tubes 2, which pass through openings 3 in the ribs 1.
  • the pipes 2 are circular in this embodiment, as are the openings 3.
  • the tubes 2, of which in FIG. 2 only one is shown by way of example, extend in an axial direction A.
  • the rib 1 is profiled, that is not flat, as in the sectional views in the FIGS. 2 and 3 can be seen.
  • the arrow P in the Figures 1 and 2 indicates the flow direction.
  • Several such ribs 1 are placed in a stacked arrangement parallel to each other and are in contact with the tubes 2, which are flowed through by a first heat exchanger medium.
  • the second flow medium flows around the tubes 2 on the outside.
  • it is preferably a cooler / heater, in which the tubes 2 are flowed through by a liquid or a refrigerant and in which outside of the tubes 2 cooling air is passed.
  • the rib 1 can be divided into two areas with regard to their surface structure.
  • a first region 5 has a first, zig-zag-shaped surface structure 6.
  • the zigzag-shaped surface structure 6 has a straight wavefront which propagates in the direction of the arrow P.
  • the zig-zag-shaped surface structure 6 is a uniformly repeating profiling and extends over the entire length of the flow path transversely to the flow direction.
  • first surface structure 6 second regions 7 are embedded with another surface structure 8.
  • the second regions 7 are configured annularly and surround the openings 3 for the tubes 2.
  • the annular second regions 7 have an annular peripheral elevation 10 and at a radial distance therefrom an annular depression 9 (FIG. FIG. 3 ).
  • the in FIG. 3 top side referred to as the top 4.
  • the terms indent 9 and elevation 10 are synonymous for reciprocal exhibitions in relation to a median plane. When viewed from the top, the elevation 10 of the opening 3 is radially closer than the recess 9.
  • the distance D of two successive openings 3 in the flow direction corresponds to twice the wavelength L of the zig-zag-shaped corrugated first surface structure 6.
  • the tubes 2 and the openings 3 are located in the region of a wave trough 11. That is to say, the longitudinal axes of the tubes 2 which are identical to the axial directions A are shown with the respective troughs 11, that is, the respective lowest points in the top 4 of the zigzag-shaped corrugations of the rib 1 together.
  • the openings 3 are arranged offset in two successive troughs 11 to each other transversely to the flow direction P by the pitch T / 2.
  • the tubes 2 have a diameter D1 which is almost equal in relation to the wavelength L. He is only slightly smaller.
  • the openings 3 are surrounded by a narrow, unprofiled ring 12, which is aligned transversely to the axial direction A of the tubes 2.
  • the tubes 2 with the ribs 1 in contact.
  • the ring 12 may have a collar pointing in the axial direction, which can serve as a spacer between adjacent ribs 1 and increases the contact area with the tube 2. This is followed by the second surface structure with the recesses 9 and elevations 10 connects.
  • the outer diameter D2 of the annular second surface structures 8 corresponds to twice the wavelength L, as shown in FIG. 1 can be seen.
  • the FIGS. 2 to 7 show that the second surface structure 8 is corrugated sinusoidally at a constant amplitude.
  • the annular second region 7 corresponds in its radial extent exactly the wavelength of a sinusoid plus the radial extent of the ring 12, so that a single annular extension 10 and an equally large annular recess 9 is formed.
  • the uniform corrugation of the first surface structure 6 is mutually deflected about a center plane M1, which can also be referred to as a neutral plane.
  • the sinusoidal profiling of the second surface structure 8 is mutually deflected about a second center plane M2, which can also be referred to as a neutral plane.
  • FIG. 2 shows that these two center planes M1, M2 are arranged at an axial distance A1 to each other.
  • the profiling of the first surface structure 6 does not project beyond the second center plane M2.
  • the elevations 10 of the second surface structure 8 do not project beyond the first center plane M1.
  • the two surface structures 6, 8 therefore overlap only by the height of a maximum amplitude.
  • the rib 1 has in In this embodiment, an extension in the axial direction of the tubes 2, which corresponds to three times the amplitudes of the first and second surface structures 6, 8.
  • the spacings of the center planes M1, M2 cause the outer edge regions of the second surface structures 8 to coincide in front of and behind the tubes 2 with a wave trough 11 in the flow direction. This means that in the region of each second wave trough 11, the thickness of the ribs 1 measured in the axial direction is limited to the sheet thickness.
  • the flow is transferred when flowing against a pipe 2 by a falling edge of the corrugated first surface structure 6 without obstacles in the second surface structure 8. There, the flow along the annular elevations 10 and depressions 9 is controlled and passed close to the tubes 2 and finally fed back to the first surface structure 6 when the diametrically opposite end of the second surface structure 8 is reached without a barrier.
  • the edge regions of the second surface surface structures 8 also coincide with the wave troughs 11 transversely to the flow direction.
  • transition flanks 14 are a support of the annular ridges 9 and recesses 10 with the aim of passing the flow close to the tubes 2.
  • the triangular transition flanks 14 are at most as large as twice the amplitude of the zigzag-shaped surface structure 6.
  • FIG. 4 shows a perspective view of a rib 1 in a slightly larger extension.
  • the flow direction is indicated by the arrow P.
  • the sinusoidal second surface structure 8 can be clearly seen, which merges into the zigzag-shaped first surface structure 6 in the flow direction P in front of and behind the respective openings 3 in the region of the wave troughs 11 without jump or offset.
  • the transition surfaces 14 between the first surface structure 6 and the second Surface structure 8 are relatively small and extend in particular in the circumferential direction of the circular second surface structure 8 and thus influence the flow so that it is urged toward the tubes.
  • FIG. 5 is a perspective view similar to the FIG. 3 ,
  • the arrow P again illustrates the flow direction. From this perspective, the profile differences between the surface structure 6 and the second surface structure 8 become even clearer. In particular, it can be seen that the sinusoidal surface structure 8 not only in the in the FIGS. 2 and 3 Section shown is located but also in the sectional plane transverse to FIG. 3 , The second surface structures 8 are rotationally symmetric with a circular wavefront.
  • FIGS. 6 and 7 show again perspective views of the ribs 1, once in the direction of the top 4 ( FIG. 6 ) and once in the direction of the bottom 15 ( FIG. 7 ).
  • the wave troughs 11 are exposed to the viewer.
  • the second surface structures 8 in the region of the wave troughs 11 merge into the first surface structure 6 without offset.
  • Cartesian coordinate systems whereby A in FIG. 2 means axial direction of the pipes, P means the direction of flow and Q the transverse direction in which the wave troughs 11 and peaks 13 of the first surface structure 6 extend.
  • FIGS. 8 and 9 show a further embodiment of a rib, wherein for substantially the same components, the reference numbers introduced to the previous figures are used.
  • the rib 1 differs from that of the FIGS. 1 to 7 in that the first regions 5 have no surface structure in the sense of a profiling or exhibition.
  • the first areas 5 are flat.
  • the second regions 7 are provided in the same way with the second surface structure 8, as in the above-described FIGS. 1 to 7 can be seen.
  • FIG. 9 shows the recesses 9 and elevations 10 of the second surface structure 8.
  • FIGS. 1 to 7 Referenced.
  • FIG. 10 shows a portion of a rib 1 in section, said rib 1 has an axially facing collar 16.
  • the collar 16 is formed on the unprofiled ring 12 which surrounds the opening 3 in the rib 1.
  • Radially on the outside, a centering shoulder 17 connects to the ring 12. He is trained circumferentially and issued in the picture plane down. He points away from the collar 16.
  • the centering shoulder 17 is followed by the second surface structure 8 with a ring-shaped elevation 10 and with a recess 9.
  • the first surface structure 6 is zig-zag-shaped, as in the preceding exemplary embodiments.
  • the collar 16 has at its free end a funnel-shaped widening 18.
  • the outer diameter of the widening 18 is adapted to the outer diameter of the ring 12, so that the widening 18 is arranged in a stacked arrangement of the ribs 1 within the centering shoulder 17.
  • the centering 17 serves as a stacking aid for identical ribs. 1

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  • 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)

Claims (18)

  1. Echangeur de chaleur comprenant des tubes (2)
    1.1. qui s'étendent dans un sens axial (A) et sont prévus afin d'être insufflés de l'extérieur transversalement au sens axial (A),
    1.2. et des nervures (1) se trouvant en contact côté extérieur avec les tubes (2) qui s'étendent transversalement au sens axial (A) des tubes (2),
    1.3. dans lequel les nervures (1) possèdent des ouvertures (3) pour la réception des tubes (2),
    1.4. dans lequel les ouvertures (3) sont entourées chacune par un anneau (12) non profilé des nervures (1) qui est contigu à l'ouverture respective (3) et qui est orienté transversalement au sens axial (A) des tubes (2),
    1.5. dans lequel les nervures (1) possèdent des première zones (5) et des secondes zones (7) qui divergent en ce qui concerne leur structure de surface (8), dans lequel les structures de surface (8) des secondes zones (7) ne sont pas planes,
    1.6. dans lequel les secondes structures de surface (8) présentent au moins une cavité (9) s'étendant en forme d'anneau, lesquelles entourent les ouvertures (3) pour la réception des tubes (2),
    caractérisé en ce que
    1.7. les secondes structures de surface (8) présentent au moins une élévation (10) s'étendant en forme d'anneau à distance radiale de la cavité (9) s'étendant en forme d'anneau.
  2. Echangeur de chaleur selon la revendication 1, caractérisé en ce que les secondes structures de surface (8) sont ondulées respectivement de manière sinusoïdale dans leur expansion radiale.
  3. Echangeur de chaleur selon la revendication 1 ou 2, caractérisé en ce que les secondes structures de surface (8) possèdent respectivement précisément une seule élévation (10) s'étendant en forme d'anneau et une seule cavité (9) s'étendant en forme d'anneau.
  4. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que les nervures (1) sont planes dans les premières zones (5).
  5. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3, caractérisé en ce que les nervures (1) possèdent dans les premières zones (5) une première structure de surface (6) non plane.
  6. Echangeur de chaleur selon la revendication 5, caractérisé en ce que la première structure de surface (6) est un profilage se répétant uniformément dans le sens d'insufflation des tubes (2).
  7. Echangeur de chaleur selon la revendication 6, caractérisé en ce que la première structure de surface (6) est un profilage sous la forme d'un cannelage ou de forme ondulée.
  8. Echangeur de chaleur selon la revendication 7, caractérisé en ce que les secondes structures de surface (8) possèdent un diamètre extérieur (D2) radial, qui correspond à la double longueur d'onde (L) de la première structure de surface (6) cannelée.
  9. Echangeur de chaleur selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les cavités (9) et élévations (10) des secondes structures de surface (8) sont de même taille.
  10. Echangeur de chaleur selon l'une quelconque des revendications 5 à 9, caractérisé en ce qu'un premier plan médian (M1) duquel les cavités et élévations (10) sont exposées, est agencé à distance axiale (A1) d'un second plan médian (M2) de la seconde structure de surface (8).
  11. Echangeur de chaleur selon la revendication 10, caractérisé en ce que les amplitudes des élévations (10) de la seconde structure de surface (8) correspondent à la distance (A1) des plans médians (M1, M2) +/- 10 %.
  12. Echangeur de chaleur selon la revendication 10 ou 11, caractérisé en ce que les amplitudes de la première structure de surface (6) cannelée correspondent à la distance (A1) des plans médians (M1, M2) +/- 10 %.
  13. Echangeur de chaleur selon l'une quelconque des revendications 5 à 12, caractérisé en ce que la première structure de surface (6) est en forme de zigzag.
  14. Echangeur de chaleur selon l'une quelconque des revendications 5 à 13, caractérisé en ce que les tubes (2) traversent les nervures (1) à une distance (A1) correspondant à la double longueur d'onde (L) de la première structure de surface (6) de sorte que les sens axiaux (A) des tubes (2) coïncident avec les crêtes d'onde (13).
  15. Echangeur de chaleur selon l'une quelconque des revendications 5 à 14, caractérisé en ce que les tubes (2) possèdent un diamètre (D1) qui se trouve dans une plage de 80 % à 100 % de la longueur d'onde (L) de la première structure de surface (6).
  16. Echangeur de chaleur selon l'une quelconque des revendications 1 à 15, caractérisé en ce que chaque nervure (1) possède deux côtés opposés (4, 15) qui servent de surfaces d'échangeur de chaleur, dans lequel les côtés (4, 15) sont exempts d'autres ouvertures à l'exception des ouvertures (3) traversées par les tubes (2).
  17. Echangeur de chaleur selon l'une quelconque des revendications 5 à 16, caractérisé en ce que des tubes (2), qui sont agencés dans un creux d'onde (11) commun de la première structure de surface (6), sont agencés à une distance de séparation (T) l'un de l'autre, dans lequel les tubes (2) dans un creux d'onde suivant (11) sont agencés en déport de la demi-distance de séparation (T) par rapport aux tubes (2) dans le premier creux d'onde (11).
  18. Echangeur de chaleur selon l'une quelconque des revendications 1 à 17, caractérisé en ce qu'une saillie de centrage (17) axialement exposée se raccorde radialement à l'extérieur à l'anneau non profilé (12).
EP15173792.1A 2014-06-25 2015-06-25 Échangeur thermique Active EP2975350B1 (fr)

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PL15173792T PL2975350T3 (pl) 2014-06-25 2015-06-25 Wymiennik ciepła

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Application Number Priority Date Filing Date Title
DE102014108890.5A DE102014108890A1 (de) 2014-06-25 2014-06-25 Wärmetauscher

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EP2975350A1 EP2975350A1 (fr) 2016-01-20
EP2975350B1 true EP2975350B1 (fr) 2019-04-03

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PL (1) PL2975350T3 (fr)
TR (1) TR201908760T4 (fr)

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WO2023053319A1 (fr) * 2021-09-30 2023-04-06 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération

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JP2661356B2 (ja) * 1990-10-22 1997-10-08 松下電器産業株式会社 フィン付き熱交換器
US5927393A (en) 1997-12-11 1999-07-27 Heatcraft Inc. Heat exchanger fin with enhanced corrugations
US6889759B2 (en) * 2003-06-25 2005-05-10 Evapco, Inc. Fin for heat exchanger coil assembly
CN203069029U (zh) * 2011-11-25 2013-07-17 松下电器产业株式会社 传热翅片、翅片管型热交换器及热泵装置
JP5974276B2 (ja) * 2012-04-23 2016-08-23 パナソニックＩｐマネジメント株式会社 フィンチューブ熱交換器
JPWO2014167827A1 (ja) * 2013-04-09 2017-02-16 パナソニックＩｐマネジメント株式会社 伝熱フィン、熱交換器、および、冷凍サイクル装置

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DE102014108890A1 (de) 2015-12-31
TR201908760T4 (tr) 2019-07-22
PL2975350T3 (pl) 2019-10-31
EP2975350A1 (fr) 2016-01-20

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