EP2593741B1 - Evaporative heat exchange apparatus with finned elliptical tube coil assembly - Google Patents

Evaporative heat exchange apparatus with finned elliptical tube coil assembly Download PDF

Info

Publication number
EP2593741B1
EP2593741B1 EP11736229.3A EP11736229A EP2593741B1 EP 2593741 B1 EP2593741 B1 EP 2593741B1 EP 11736229 A EP11736229 A EP 11736229A EP 2593741 B1 EP2593741 B1 EP 2593741B1
Authority
EP
European Patent Office
Prior art keywords
tubes
generally
fins
segments
inch
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP11736229.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2593741A2 (en
Inventor
Thomas William Bugler
Davey Joe Vadder
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.)
Evapco Inc
Original Assignee
Evapco Inc
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 Evapco Inc filed Critical Evapco Inc
Priority to PL11736229T priority Critical patent/PL2593741T3/pl
Publication of EP2593741A2 publication Critical patent/EP2593741A2/en
Application granted granted Critical
Publication of EP2593741B1 publication Critical patent/EP2593741B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
    • F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals

Definitions

  • the present invention relates to improvements in tubes in a coil assembly for use in an evaporative heat exchange apparatus in which the coil assembly is to be mounted in a duct or plenum of the apparatus in which external heat exchange fluids, typically a liquid, usually water, and a gas, usually air, flow externally through the coil assembly to cool an internal heat transfer fluid passing internally through the tubes of the coil assembly.
  • the improvements concern the use of tubes or segments of the tubes having a generally elliptical cross-section, in combination with tube orientation, arrangement and spacing, and fin spacing, height and thickness, all of which must be carefully balanced, to provide increased heat transfer coefficients with an unexpected relatively low air pressure drop that produces high air volume that together produces very high heat exchange capacity.
  • JP2002 257484 describes a spiral finned tube mainly employed as a heat transfer part for a refrigerator, a showcase or the like.
  • the tubes may be used in any type of evaporative heat exchange coil assembly made of an array of several, and preferably, many tubes that can have a variety of arrangements.
  • the tubes are preferably arranged in generally horizontal rows extending across the flow path of the air and water which flow externally through the coil assembly, whether the air and water are in counterflow, parallel flow or crossflow pathways.
  • the ends of the tubes may be connected to manifold or headers for appropriate distribution of the internal heat transfer fluid.
  • the internal heat transfer fluid may be a heating fluid, a cooling fluid or a processing fluid used in various types of industrial processes, where the temperature of the internal heat transfer fluid needs to be modified, typically but not exclusively by cooling, and often but not exclusively by condensing, as a result of the heat transfer through the walls of the tubes by the external heat exchange fluids.
  • serpentine tubes are often the preferred type of tubes used due to the ease of manufacture of effective coil assemblies from such tubes.
  • serpentine tubes are often the preferred type of tubes used due to the ease of manufacture of effective coil assemblies from such tubes.
  • other types of tubes of the present invention useful for the evaporative heat exchange apparatus of the present invention, the tubes and coil assemblies of the present invention will primarily be described, without limitation, with respect to the preferred serpentine tubes. The following background information is provided to better understand the relationship of the tube and coil assembly components using serpentine tubes.
  • Each serpentine tube comprises a plurality of two different types of portions, "segments” and “return bends.”
  • the segments are generally straight tube portions which are connected by the return bends, which are the curved portions, sometimes referred to as “bights," to give each tube its serpentine structure.
  • the tubes which may be generally straight in structure (referred to hereinafter as “straight tubes"), or the segments of each of the serpentine tubes, are generally elliptical in cross-section and the return bends can be any desired shape and are typically generally circular, generally elliptical, generally kidney-shaped or some other shape in cross-section.
  • the generally horizontal maximum dimension of the generally elliptical segments is usually equal to or smaller than the generally horizontal cross-sectional dimension of the return bends, especially if the return bends have a circular cross-section.
  • the return bends can have an elliptical cross-section, or a kidney-shaped cross-section, but it is usually easier to make the return bends with a circular cross-section.
  • the segments of horizontally adjacent serpentine tubes are spaced from each other by the larger horizontal cross-section of the return bends when the return bends are in contact with each other, or may be spaced by vertically-oriented spacers between the return bends, depending on the design characteristics of the evaporative heat exchange apparatus in which the coil assemblies are used.
  • the straight tubes or the segments of the serpentine tubes are preferably arranged in generally horizontal rows extending across the flow path of the air and water which flow externally through the coil assembly, whether the air and water are in counterflow, parallel flow or crossflow pathways.
  • Evaporative heat exchangers using coil assemblies using serpentine tubes having segments with generally elliptical cross-sections are also known, for example as disclosed in U.S. Patents 4,755,331 and 7,296,620 , the disclosures of which are hereby incorporated herein in their entireties, which are assigned to Evapco, Inc., the assignee of the present invention. These patents do not disclose or contemplate the use of finned tubes in the coil assembly in the evaporative heat exchange environment.
  • Finned tubes used in coil assemblies of dry (non-evaporative) heat exchangers are known and are used in view of the greater surface area provided by the fins to dissipate heat by conduction when exposed to air flowing externally through the coil assembly of the dry heat exchanger.
  • the fins in such dry heat exchangers do not materially adversely affect the flow of air through the coil assembly of the dry heat exchanger.
  • Finned coils are also used extensively in coil assemblies of products like home refrigerators to dissipate the heat to the ambient air.
  • coil assemblies for dry heat exchangers made using fins in the form of sheets or plates having holes though which segments having generally elliptical cross-sections pass are disclosed in Evapco, Inc.'s U.S. Patents 5,425,414 , 5,799,725 , 6,889,759 , and 7,475,719 .
  • such coil assemblies are not useful with evaporative heat exchangers, since the sheets or plates would adversely affect the mixing and turbulence of the air and water involved with evaporative heat exchange that must pass externally through the coil assembly.
  • the finned tube coil assembly of the present invention provides a number of significant advantages.
  • the combination of the shape of the tubes, the spacing of the tubes, the height of the fins, and the number of fins per inch have resulted in exceptional and unexpected increases in evaporative thermal performance.
  • the geometry of the tubes and their orientation and arrangement with a coil assembly play an essential part in the turbulent mixing of the air and water.
  • the generally elliptical cross-sectional shape of the segments provides the advantages of a large amount of surface area of the tubes in a coil assembly, effective flow and heat transfer of process fluid internally within the tubes and enhanced external air and water flow characteristics.
  • the surprising result of less resistance to the air and water passing externally through the coil assembly allows the use of higher air volume that provides additional thermal capacity compared to the prior art systems without adding any fan energy.
  • the finned tubes provide an enhanced surface area for conductive heat exchange with the tubes and aid in turbulent mixing of the air and water externally flowing through the coil assembly, enhancing convective heat exchange between the air and the water.
  • the finned tubes take up space that may impede the water and air flow and thereby would be expected to cause a very significant air side pressure drop, with the need for stronger motors for fans to move the air through the coil assembly in the heat exchanger.
  • the finned tubes with generally elliptical cross-sections having the characteristics of the present invention not only provide a careful balance of enhanced coil assembly surface area for conductive heat exchange with any fluid flowing within the interior of the tubes and mixing and turbulence of the air and water for the convective heat exchange but also provide a surprising reduction in the air side pressure drop through the coil assembly, while retaining a very large increase in external heat transfer coefficient.
  • the overall capacity of the coil assembly of the present invention and evaporative heat exchangers containing it are greatly improved at nominal, or in certain circumstances even reduced cost, compared to the increase in capacity.
  • the cost per cooling ton may be reduced by, for instance, replacing a coil assembly using more non-finned tubes with a coil assembly using fewer finned tubes of the present invention.
  • an evaporative heat exchanger of a given size using non-finned tubes of the prior art could be replaced with a smaller evaporative heat exchanger according to the present invention that achieves the same or better thermal performance.
  • using a coil assembly having the finned tubes of the present invention could significantly reduce required fan energy, and therefore overall power consumption, as compared to a non-finned coil assembly of the same size.
  • heat is transferred using indirect evaporative exchange, where there are three fluids: a gas, typically air (accordingly, such gas will usually be referred to herein, without limitation, as “air”), a process fluid flowing internally through a coil assembly of tubes, and an evaporative cooling liquid, typically water (accordingly, such external heat exchange or cooling liquid will usually be referred to herein, without limitation, as “water”), which is distributed over the exterior of the coil assembly through which the process fluid is flowing and which also contacts and mixes with the air or other gas flowing externally through the coil assembly.
  • a gas typically air
  • air a process fluid flowing internally through a coil assembly of tubes
  • an evaporative cooling liquid typically water (accordingly, such external heat exchange or cooling liquid will usually be referred to herein, without limitation, as “water”)
  • the process fluid first exchanges sensible heat with the evaporative liquid through indirect heat transfer between the tubes of the coil assembly, since it does not directly contact the evaporative liquid, and then the air stream and the evaporative liquid exchange heat and mass when they contact each other, resulting in more evaporative cooling.
  • direct evaporative heat exchange may be used together with the indirect evaporative heat exchange involving the finned tube coil assembly of the present invention, as explained in more detail hereinafter, to provide enhanced capacity.
  • direct evaporative heat exchange apparatus air or other gas and water or other cooling liquid may be passed through direct heat transfer media, called wet deck fill, where the water or other cooling liquid is then distributed as a thin film over the extended fill surface for maximum cooling efficiency. The air and water contact each other directly across the fill surface, whereupon a small portion of the distributed water is evaporated, resulting in direct evaporative cooling of the water, which is usually collected in a sump for recirculation over the wet deck fill and any coil assembly used in the apparatus for indirect heat exchange.
  • the present invention uses a finned tube coil assembly where the claimed combination of factors of tube shape, orientation, arrangement and spacing, and fin spacing, height and thickness, all of which must be carefully balanced, to provide increased heat transfer coefficients with an unexpected relatively low air pressure drop that produces high air volume.
  • the combination of increased heat transfer coefficients with high air volume produces very high heat exchange capacity.
  • the term "about” with respect to any numerical value means that the numerical value has some reasonable leeway and is not critical to the function or operation of the component being described or the system or subsystem with which the component is used, and will include values within plus or minus 5% of the stated value.
  • the term "generally" or derivatives thereof with respect to any element or parameter means that the element has the basic shape, or the parameter has the same basic direction, orientation or the like to the extent that the function of the element or parameter would not be materially adversely affected by somewhat of a change in the element or parameter.
  • the segments having a "generally elliptical cross-sectional shape” refers not only to a cross-section of a true mathematical ellipse, but also to oval cross-sections or somewhat squared corner cross-sections, or the like, but not a circular cross-section or a rectangular cross-section.
  • an element that may be described as "generally normal” to or “generally parallel to” another element can be oriented a few degrees more or less than exactly 90° with respect to "generally normal” and a few degrees more or less than exactly perfectly parallel or 0° with respect to "generally parallel,” where such variations do not materially adversely affect the function of the apparatus.
  • the term "substantially” with respect to any numerical value or description of any element or parameter means precisely the value or description of the element or parameter but within reasonable industrial manufacturing tolerances that would not adversely affect the function of the element or parameter or apparatus containing it, but such that variations due to such reasonable industrial manufacturing tolerances are less than variations described as being “about” or “generally.”
  • “fins having a height extending from the outer surface of the segments a distance of substantially 23.8% to substantially 36% of the nominal tube outside diameter” would not allow variations that adversely affect performance, such that the fins would be too short or too tall to allow the evaporative heat exchanger to have the desired enhanced performance.
  • the term "thickness" with respect to the thickness of the fins refers to the thickness of the fins prior to treatment after the fins are applied to the tubes to make the finned tubes, such as galvanizing the tubes or the coil assembly using the finned tubes, as such treatment would likely affect the nominal thickness of the fins, the nominal fin height and the nominal spacing of the fins.
  • all of the dimensions set forth herein are of the finned tubes prior to any later treatment of the finned tubes themselves or of any coil assembly containing them.
  • centimeter dimensions As used herein, where specific dimensions are presented in inches and parenthetically in centimeters (cm), the dimensions in inches controls, as the centimeter dimensions were calculated based on the inches dimensions by multiplying the inches dimensions by 2.54 cm per inch and rounding the centimeter dimensions to no more than three decimal places.
  • the present invention relates to an improvement in an evaporative heat exchanger comprising a plenum having a generally vertical longitudinal axis, a distributor for distributing an external heat exchange liquid into the plenum, an air mover for causing air to flow in a direction through the plenum in a direction generally countercurrent to, generally parallel to, or generally across the longitudinal axis of the plenum, and a coil assembly having a major plane and being mounted within the plenum such that the major plane is generally normal to the longitudinal axis of the plenum and such that the external heat exchange liquid flows externally through the coil assembly in a generally vertical flow direction, wherein the coil assembly comprises inlet and outlet manifolds and a plurality of tubes connecting the manifolds, the tubes extending in a direction generally horizontally and having a longitudinal axis and a generally elliptical cross-sectional shape having a major axis and a minor axis where the average of the major axis length and the minor axis length is a nominal tube
  • the improvement comprises the tubes having external fins formed on an outer surface of the tubes, wherein the fins have a spacing of substantially 1.5 to substantially 3.5 fins per inch (2.54 cm) along the longitudinal axis of the tubes, the fins having a height extending from the outer surface of the tubes a distance of substantially 23.8% to substantially 36% of the nominal tube outside diameter, the fins having a thickness of substantially 0.007 inch (0.018 cm) to substantially 0.020 inch (0.051 cm), the tubes having a center-to-center spacing generally horizontally and generally normal to the longitudinal axis of the tubes of substantially 100% to substantially 131% of the nominal tube outside diameter, and the horizontally adjacent tubes having a generally vertical center-to-center spacing of substantially 110% to substantially 300% of the nominal tube outside diameter.
  • the tubes are serpentine tubes having a plurality of segments and a plurality of return bends, the return bends being oriented in generally vertical planes, the segments of each tube connecting the return bends of each tube and extending between the return bends in a direction generally horizontally, the segments having a longitudinal axis and a generally elliptical cross-sectional shape having a major axis and a minor axis where the average of the major axis length and the minor axis length is a nominal tube outside diameter, the segments being arranged in the coil assembly such that the segments of adjacent tubes are generally vertically spaced from each other within planes generally parallel to the major plane, the segments of adjacent tubes in the planes generally parallel to the major plane being staggered and spaced with respect to each other generally vertically to form a plurality of staggered generally horizontal levels in which every other segment is aligned in the same generally horizontal level generally parallel to the major plane, and wherein the segments are spaced from each other generally horizontally and generally normal to the longitudinal axis of
  • the improvement comprises the segments having external fins formed on an outer surface of the segments, wherein the fins have a spacing of substantially 1.5 to substantially 3.5 fins per inch (2.54 cm) along the longitudinal axis of the segments, the fins having a height extending from the outer surface of the segments a distance of substantially 23.8% to substantially 36% of the nominal tube outside diameter, the fins having a thickness of substantially 0.007 inch (0.018 cm) to substantially 0.020 inch (0.051 cm)%, the segments having a center-to-center spacing generally horizontally and generally normal to the longitudinal axis of the segments of substantially 100% to substantially 131% of the nominal tube outside diameter, and the horizontally adjacent segments having a generally vertical center-to-center spacing of substantially 110% to substantially 300% of the nominal tube outside diameter.
  • a plurality of finned tubes such that at least some, more preferably the majority, and most preferably as mentioned above, all of the tubes in a coil assembly for an evaporative heat exchange apparatus are the finned tubes of the present invention.
  • the finned tubes are used in any desired arrangement of finned and non-finned tubes, but preferably and without limitation, the finned tubes may usually be arranged to be on the top portion of a coil assembly and the non-finned tubes may be on the bottom portion of the coil assembly.
  • the tubes 10 may be made of any heat-conductive metal, such as galvanized steel, stainless steel, copper, aluminum or the like.
  • Stainless steel and galvanized steel, where the zinc is applied to the steel to form galvanized steel after tubes are assembled into a coil assembly 24, are the presently preferred materials for the tubes 10 for most evaporative heat exchange applications.
  • the connecting end portions 16 of the return bends 14 match the shape and may be slightly smaller in cross-sectional area than the connecting end portions 18 of the segments 12, such that the connecting end portions 18 of the segments fit over the connecting end portions 16 of the return bend 14, and may be conveniently substantially sealed in a substantially liquid-tight and preferably substantially gas-tight manner, such as by welding the connecting end portions 16 and 18 together.
  • the connecting end portions 16 and 18 may have a generally elliptical or other cross-sectional shape.
  • the connecting end portions 16 and 18 have a generally circular cross-sectional shape, such that it is easier to orient and connect together the connecting end portions 16 and 18, and so that uniform return bends 14 can be used that preferably have a generally circular cross-sectional shape throughout their curved length from one connecting end portion 16 to the opposite connecting end portion 16.
  • the return bends may have a generally elliptical cross-sectional shape, where major axes of the ellipses of the body of the return bends 14 between the connector end portions 16 are oriented in a generally vertical direction, for most applications within an evaporative heat exchanger.
  • the return bends 14 may have a kidney-shaped cross-section throughout their length, with or without kidney-shaped connecting end portions 16 if the connecting end portions 18 of the segments 12 have matching kidney-shaped cross-sections. It is preferred to connect the return bends 14 to the segments 12 after the fins 20 have been applied to the segments, for ease of manufacture.
  • the inlet 30 is shown at the top and the outlet 34 is shown at the bottom of the coil assembly 24, the orientation of the inlet and outlet could be reversed, such that the inlet is at the bottom and the outlet is at the top, if desired.
  • the assembled coil assembly 24 may be moved and transported as a unitary structure such that it may be dipped, if desired, if its components are made of steel, in a zinc bath to galvanize the entire coil assembly.
  • Fig. 6B is a schematic side elevation drawing of another alternative embodiment of an exemplary coil assembly 24 made using the finned tubes 10 of the present invention, where the finned tubes 10 are generally straight tubes that extend across the major plane 25 (not shown).
  • an inlet 30 for the internal heat transfer or process fluid is connected to an inlet manifold or header 32.
  • the internal fluid flows from the inlet manifold or header 32 into a plurality of finned tubes 10 that are fluidly connected at one end to the inlet manifold or header 32 at an upper level and into a second, upper manifold or header 33A to which the opposite ends of the upper level finned tubes 10 are fluidly connected.
  • the internal fluid then flows from the second, upper manifold or header 33A through a lower level of finned tubes 10 fluidly connected at one end to the second, upper manifold or header 33A into a third, intermediate manifold or header 33B to which the opposite ends of the finned tubes 10 are fluidly connected. From the third, intermediate manifold or header 33B, the internal fluid flows into a still lower level of finned tubes 10 which are fluidly connected at one end to the third, intermediate manifold or header 33B to a fourth, lower manifold or header 33C to which the opposite ends of the finned tubes 10 are fluidly connected.
  • the internal fluid flows from the fourth, lower manifold or header 33C to which the one end of the lowest level of the finned tubes 10 are fluidly connected to an outlet manifold or header 36 to which the opposite ends of the finned tubes 10 are fluidly connected.
  • An outlet 34 for the internal heat transfer or process fluid is connected to the outlet manifold or header 36.
  • Fig. 6C is a schematic side elevation drawing of an alternative embodiment of an exemplary coil assembly 24 made using the finned tubes 10 of the present invention, where the finned tubes 10 are generally straight tubes that extend across the major plane 25 (not shown) and fluidly connect directly at respective opposite ends to an inlet manifold or header 32 and to an outlet manifold or header 36.
  • An inlet 30 for the internal heat transfer or process fluid is connected to the inlet manifold or header 32.
  • An outlet 34 for the internal heat transfer or process fluid is connected to the outlet manifold or header 36.
  • the flow of the internal fluid can be reversed, such that the described inlet 30 would be an outlet and the described outlet 34 would be the inlet.
  • the segments 12 of the finned tubes 10 shown in Figs. 6 and 6A and the generally straight finned tubes 10 as shown in Figs. 6B and 6C have external fins 20, which are preferably spiral fins, that contact the outer surface of the segments 12.
  • the fins may be serrated, may have undulations or corrugations or may be of any other desired well-known structure.
  • collars 22 may be integrally and unitarily formed with the fins 20, where the collars 22 provide a direct and secure contact with the surface of the tubes 10 or segments 12 over a greater surface area than if only the edges of the fins 20 were in contact with the outer surface of the tubes 10 or segments 12.
  • the fins 20 and collars 22 may be formed simultaneously on the tubes 10 or segments 12 using commercially available equipment in a manner known to those involved with producing finned tubes, and especially spiral finned tubes.
  • the fins 20, with or without collars 20 may be applied individually onto the outer surface of the tubes 10 or segments 12, and then secured, such as by welding, into place, but this is an expensive and labor intensive manner of applying the fins 20 to the tubes 10 or segments 12.
  • the fins 20 are applied spirally in a continuous manner to the tubes 10 or segments 12 by conventional equipment.
  • the fins 20 are formed from a band of metal of the same type as used in for the tubes 10, and the band is fed from a source of the band at a rate and in a manner to spirally wrapped around the tube 10 or segment 12 as the tube 10 or segment 12 is advanced longitudinally along and rotated around its longitudinal axis 13 through the spiral fin forming equipment.
  • the inner radius of the fins 20 buckles while the outer radius does not, which creates minor corrugations or indentations in the fins themselves. This buckling occurs in a regular, repeating process in a left-to-right pattern, to form undulations in and out of the plane of the material used to form the fins, not shown in Figs. 2 and 3 .
  • the band of metal of the same type as used in for the tubes 10 is fed from a source of the band at a rate and in a manner to be bent longitudinally to provide a flat portion that becomes the collars 22 and an upstanding portion that becomes the fins 20.
  • the bent metal band is spirally wrapped around the segments 12 as the segments 12 are advanced longitudinally along and rotated around their longitudinal axis 13 through the spiral fin forming equipment.
  • the fins 20 typically have undulations in and out of their plane, rather than straight as shown in Figs. 2 and 3 for the ease of illustration, while the collars 22 are flat against the surface of the segments 12, resulting from the metal deformation during the application of the strip of metal to the advancing and rotating segments.
  • Figs. 5A and 5B show respective first and second embodiments, partly in end elevation and partly in vertical cross-section, of a portion of four serpentine tubes 10A or 10B, for Figs. 5A and 5B , respectively, of a plurality of tubes 10 of a coil assembly 24, taken along lines 5--5 of the embodiment of Fig. 1 .
  • the second and fourth tubes are shown in a preferred orientation as being staggered in height, or vertically (as shown, lower), with respect to their next generally horizontally adjacent first and third tubes.
  • Figs. 5A and 5B show respective first and second embodiments, partly in end elevation and partly in vertical cross-section, of a portion of four serpentine tubes 10A or 10B, for Figs. 5A and 5B , respectively, of a plurality of tubes 10 of a coil assembly 24, taken along lines 5--5 of the embodiment of Fig. 1 .
  • the second and fourth tubes are shown in a preferred orientation as being staggered in height, or vertically (as shown, lower
  • FIG. 5A and 5B also illustrate alternative embodiments of orientations of the major axes of the generally elliptical segments 12A of serpentine tubes 10A in Fig. 5A and the generally elliptical segments 12B of serpentine tubes 10B in Fig. 5B .
  • the embodiments of Figs. 5A and 5B are similar to each other.
  • the cross-section of Fig. 1 was selected such that the fins are not shown or described for the sake of clarity, but the orientations of the major and minor axes of the generally elliptical segments should be understood as relating to the entire length of the finned segments 12 until they connect with or are unitarily formed with the return bends 14A and 14B.
  • each of the return bends 14A and 14B is shown as having a circular cross-sectional shape, as explained above, the return bends 14A and 14B may alternatively have a generally elliptical cross-sectional shape, a generally kidney-shaped cross-sectional shape, or other cross-sectional shape.
  • the orientation of the major axes of the generally elliptical finned segments 12A and 12B will be described in the preferred embodiment of the serpentine tubes 10 as shown in the embodiment illustrated in Figs. 6 and 6A , but in principle, the same orientation can be and, preferably, is provided for the generally straight and generally elliptical finned tubes 10 used in a coil assembly such as the coil assemblies shown in Figs. 6B and 6C .
  • the segments 12A or 12B of adjacent tubes are generally vertically spaced from each other within planes generally parallel to the major plane 25 of the coil assembly 24 at respective upper generally horizontal levels L1A and L1B and respective lower generally horizontal levels L2A and L2B.
  • the segments 12A or 12B of adjacent tubes 10A or 10B are in planes generally parallel to the major plane 25 and are staggered and spaced with respect to each other generally vertically to form a plurality of staggered generally horizontal levels in which every other segment is aligned in the same generally horizontal level generally parallel to the major plane 25.
  • each horizontal level L1B, the major axes of all of the segments 12B are oriented in the same angled direction and on the next adjacent lower level L2B, the major axes of all the segments are oriented in the same angled direction, but in an opposite angled orientation from the angled orientation of the major axes in level L1B.
  • the major axes are angled in opposite directions on adjacent horizontal levels, they are sometimes known as a "ric-rac" arrangement or orientation, and this term is used in the Table below to designate this type of arrangement or orientation. If desired, however, on each level L1B or L2B, the major axes of the segments within the same generally horizontal level may be angled in opposite directions.
  • the major axes of the finned segments 12A or 12B on a first generally horizontal level L1A or L1B, respectively may be 0° to about 25° degrees from the plane of the return bends and the angle of the major axes of the finned segments 12B or 12A, respectively, on the next adjacent generally horizontal level L2B or L2A, respectively, may be about 335° to 360° from the plane of the return bends.
  • Fig. 4 shows the oppositely angled major axes of the finned segments 12 as described with respect to Fig. 5B for a complete serpentine tube 10.
  • the return bends 14, 14A and 14B are shown as being generally circular in cross-section.
  • the outside diameter of the circular cross-section of the return bends substantially equals the nominal tube outside diameter that is an average of the lengths of the major and minor axes of the segments 12, 12A and 12B having a generally elliptical cross-section.
  • the outside diameter of the return bends and the nominal tube outside diameter are about and preferably substantially 1.05 inches (2.67 cm), where the wall thickness of the tubes forming the segments 12 and the return bends 14 is about 0.055 inch (0.14 cm).
  • the minor axis of the generally elliptical tube 10 or segments 12, 12A and 12B is about 0.5 to about 0.9 times, and preferably about 0.8 times the nominal tube outside diameter.
  • the generally elliptical straight tubes 10 and segments 12, 12A and 12B having a nominal tube outside diameter of 1.05 inches (2.67 cm), would have a minor axis length of about and preferably substantially 0.525 inch (1.334 cm) to about and preferably substantially 0.945 inch (2.4 cm), and preferably about and preferably substantially 0.84 inch (2.134 cm).
  • Tubes 10 with these dimensions have been found to have a good balance among an appropriate inner diameter or dimensions to allow the processing fluid in the form of any desired gas or liquid to easily flow within the tubes 10, proximity of such processing fluid to the tube wall for good heat transfer through the walls of the tubes with the elliptical cross-sectional shape that has a large effective surface area, and ability to provide an appropriate number of tubes 10 to be packed into a coil assembly 24.
  • the tubes are strong, durable and when in serpentine form, able to be readily worked, including connecting the segments 12 and return bends 14 and placement within a coil assembly 24.
  • the evaporative heat exchangers such as the evaporative heat exchanger 26, in which the finned tubes 10 of the present invention are placed, the dimensions and cross-sectional shape of the tubes 10 may be varied considerably.
  • the spacing and orientation of the tubes 10 having the generally elliptical cross-sectional shape or segments having the generally elliptical cross-sectional shape within a coil assembly 24 are important factors for the performance of the evaporative heat exchanger containing the coil assembly 24. If the spacing between segments 12 is too tight, air and water flow through and turbulent mixing within the coil assembly will be adversely affected and fans with greater horsepower will be needed and there will be an increased pressure drop. If the spacing between segments 12 is too great, then there will be less tubes per surface area of the major plane 25 of the coil assembly 24, reducing the heat transfer capacity, and there may be inadequate, as in insufficient for example, mixing of the air and water, adversely affecting the degree of evaporation, and thereby heat exchange. The orientation of the segments 12, particularly with respect to the angle of the major axes of the segments, also affects the heat exchange ability of an evaporative heat exchanger with which they are used.
  • the spacing of the fins 20 around the outer surface of the segments 12 is critical. If the fin spacing is too close (too many fins per inch, for example), the ability of the external heat exchange liquid and the air to effectively mix turbulently is adversely affected and the fins 20 may block the space externally of the coil assembly 24, such that greater air mover power is needed. Similar concerns involve the critical determination of the height of the fins (the distance from the proximal point where the base of the fins 20 contact the outer surface of the segments 12 and the distal tip of the fins). While higher fins have greater surface area which the evaporating water may coat, longer fins may block the air passage. Thicker fins 20 also have similar critical concerns.
  • Thicker fins are more durable and are better able to withstand the forces of water and air, as well as other material that may be entrained in either as they pass through a coil assembly, but thicker fins may also block the flow of water or air through the coil assembly and would be more expensive to manufacture. All of these factors adversely affect performance.
  • the advantages of a sufficient number of fins 20 for the evaporative water to coat would not be present and there may be an adverse effect on the desired mixing of the water and air responsible for efficient evaporation. Similar concerns are present when the fin height is too low, as there is not enough structure of the fins to be coated with the water, and there may be less mixing of the water and air. Thinner fins may not be sufficiently durable to withstand the hostile environment to which they are subject in evaporative heat exchangers and if the fins are too thin, they could be bent during operation as they are subject to the forces of both the water and air impacting them, adversely affecting flow of both the water and air. In addition, and more significantly, thinner fins transfer less heat.
  • the present invention was conceived and developed in view of the foregoing factors of tube shape, orientation, arrangement and spacing, and fin spacing, height and thickness, all of which must be carefully balanced, and which was a difficult task requiring considerable testing and experimentation. Based on such work, the appropriate parameters of tube shape, arrangement, orientation and spacing, as well as fin spacing, height and thickness were determined.
  • the orientation and spacing, within a coil assembly 24 and an evaporative heat exchanger, of the tubes 10 with their segments 12 and return bends 14 will be described primarily with reference to Figs. 5A and 5B .
  • the center-to-center spacing D H generally horizontally (which will be generally parallel to the major plane 25 in Fig. 6 ) and generally normal to the longitudinal axis 13 of the segments 12, 12A and 12B is substantially 100% to substantially 131%, preferably substantially 106% to substantially 118%, and more preferably substantially 112% of the nominal tube outside diameter.
  • the vertical straight tube or segment spacing D V generally is not as critical to the performance of an evaporative heat exchanger as the horizontal tube or segment spacing D H .
  • the segments 12, 12A and 12B have a generally vertical center-to-center spacing of substantially 110% to substantially 300% of the nominal tube outside diameter, preferably substantially 150% to substantially 205% of the nominal tube outside diameter, and more preferably, substantially 179% of the nominal tube outside diameter.
  • This generally vertical center-to center spacing is indicated by the distance D V between the upper generally horizontal levels L1A and L1B and the lower generally horizontal levels L2A and L2B, respectively.
  • the center-to-center spacing D H of the finned straight tubes 10 or segments 12, 12A and 12B of the serpentine finned tubes 10 would be substantially 1.05 inches (2.67 cm) to substantially 1.38 inches (3.51 cm), preferably substantially 1.11 inches (2.82 cm) to substantially 1.24 inches (3.15 cm), and more preferably substantially 1.175 inches (2.985 cm).
  • the finned tubes 10 or the finned segments 12, 12A and 12B would have a generally vertical center-to-center spacing D V of substantially 1.15 inches (2.92 cm) to substantially 3.15 inches (8.00 cm), preferably substantially 1.57 inches (3.99 cm) to substantially 2.15 inches (5.46 cm), and more preferably substantially 1.88 inches (4.78 cm).
  • the major axes of the finned tubes 10 or the finned segments 12, 12A are oriented substantially vertically, so that they are generally parallel to the plane of the return bends 14 as shown in Fig. 4 .
  • the major axes of the finned tubes 10 or the finned segments 12B may be greater than 0° to about 25°, and preferably about 20°, from the plane of the return bends 14 and the angle of the major axes of the finned tubes 10 or the finned segments 12B on the next vertically adjacent generally horizontal level, may be about 335° to less than 360°, and preferably about 340° from the plane of the return bends 14, such that the major axes of the finned tubes 10 or the finned segments 12 are oriented in opposite directions on vertically adjacent horizontal levels.
  • the parameters relating to the fins 20, namely fin spacing along the longitudinal axis 13 of the segments 12, the fin height from the outer surface of the segments 12 and the fin thickness are as follows according to the present invention.
  • the fins 20 are preferably spiral fins and have a spacing of substantially 1.5 to substantially 3.5 fins per inch (2.54 cm) along the longitudinal axis 13 of the segments 12, preferably substantially 2.75 to substantially 3.25 fins per inch (2.54 cm) and more preferably substantially 3 fins per inch (2.54 cm).
  • the center-to-center distance between the fins is therefore, respectively, substantially 0.667 inch (1.694 cm) to substantially 0.286 inch (0.726 cm), preferably substantially 0.364 inch (0.925 cm) to substantially 0.308 inch (0.782 cm), and more preferably substantially 0.333 inch (0.846 cm).
  • the fins 20 have a height of substantially 23.8% to substantially 36% of the nominal tube outside diameter, preferably substantially 28% to substantially 33% of the nominal tube outside diameter, and more preferably substantially 29.76% of the nominal tube outside diameter. These parameters may be applied as follows to the presently preferred embodiment, where the nominal tube outside diameter is substantially 1.05 inches (2.667 cm). In this embodiment, the fins 20 have a height of substantially 0.25 inch (0.635 cm) to substantially 0.375 inch (0.953 cm), preferably substantially 0.294 inch (0.747 cm) to substantially 0.347 inch (0.881 cm), and more preferably 0.3125 inch (0.794 cm).
  • the thickness of the fins increases by the thickness of the zinc coating applied during galvanization.
  • the fins after galvanization are thicker at a base proximal to the outer surface of the tube than at a tip of the fins distal from the outer surface of the tube. Because the fins are thicker after galvanizing, the spacing between the fins is reduced accordingly. Usually this is not of concern concerning the thermal performance or heat capacity of the evaporative heat exchangers and the rust or other corrosion inhibition of the galvanizing is important in providing the finned tubes and coil assemblies with greater longevity than if they were not galvanized.
  • the coil assembly 24 of any desired configuration is then installed into an evaporative heat exchanger apparatus, such as evaporative heat exchanger 26, as shown in Fig. 7 .
  • Evaporative heat exchangers have many varied configurations, and several are shown schematically in Figs. 7-11 .
  • Typical evaporative heat exchangers in which the coil assembly 24 of the present invention may be used are, for example without limitation, any of several available from Evapco, Inc., such as Models ATWB or ATC, which may include the components and operate as disclosed in Evapco, Inc.'s U.S. Patent 4,755,331 .
  • Evaporative heat exchange apparatus though they many variations, have the basic structure and operation described below, initially with reference to Fig. 7 .
  • the finned segments 12, with their longitudinal axes 13, of the tubes 10 are also in generally horizontal staggered planes parallel to the major plane 25 of the coil assemblies 24 and generally normal to the longitudinal axis 42 of the plenum 40. If generally straight finned tubes 10 are used as shown in Figs. 6B and 6C , then the finned tubes with their longitudinal axes also are in generally horizontal staggered planes parallel to the major plane 25 of the coil assemblies 24 and generally normal to the longitudinal axis 42 of the plenum 40.
  • air is drawn into the plenum 40, passes though the coil assemblies 24 and exits an air outlet 46 by the action of an air mover located in an air outlet housing 50.
  • the air mover in this embodiment is shown as a fan 48, in the form of a propeller fan, which is preferred for use as an induced draft fan to draw air from the ambient atmosphere.
  • a drain pipe with an appropriate valve and a fill pipe with an appropriate valve may be included for draining and filling or replenishing the sump 52.
  • Water in the sump 52 is circulated to a liquid distributor assembly 54, which when turned on distributes, via spray nozzles, orifices in a pipe or via other known devices and techniques, the water as the evaporative heat transfer liquid above the coil assemblies 24.
  • the distributor assembly 54 is connected to one end of a conduit 56 in fluid connection at the other end to the water in the sump.
  • the distributor assembly 54 is activated or turned on typically when a pump 58 is turned on to pump water from the sump 52 to the distributor assembly 54 through the conduit 56.
  • the evaporative heat exchanger 26 also preferably includes drift eliminators 60 above the liquid distributor assembly 54 and below the fan 48 and air outlet 46.
  • the drift eliminators very significantly reduce water droplets or mist entrained in the air exiting the outlet 46.
  • Many drift eliminators of various materials are available commercially.
  • the presently preferred drift eliminators are PVC drift eliminators available from Evapco, Inc. as disclosed in Evapco, Inc.'s U.S. Patent 6,315,804 , the disclosure of which is hereby incorporated by reference herein in its entirety.
  • any associated louvers or dampers 45 In operation, as air is drawn into the plenum 40 through the air inlets 44 and any associated louvers or dampers 45, it is also drawn through the coil assemblies 24. Water is distributed over the coil assemblies 24 by the liquid distributor 54. As the air travels upwardly through the coil assemblies 24 it is mixed with the water, with an appropriate degree of turbulence as provided by the orientation and arrangement of the finned segments 12 having the fins 20 with the characteristics, dimensions and parameters disclosed above. The water coats the outer surfaces of the tubes 10, including the segments 12 having the generally elliptical cross-sectional shape, as well as the fins 20. The air causes the water to evaporate, thereby cooling the water, such that the cooled water exchanges heat with the tubes 10 of the coil assembly and the process fluid contained internally within the tubes 10.
  • the coil assemblies 24 having the finned tubes 10 of the present invention may be used in a large variety and types of evaporative heat exchange apparatus.
  • Figs. 8-11 schematically illustrate a small sample of such various evaporative heat exchangers, with some typical components shown in Fig. 7 removed for the sake of clarity.
  • components that are shown and that are the same as those in Fig. 7 are not described again, but are identified by like numerals used in Fig. 7 , except that a letter designation common to the embodiments of each of Figs. 8-11 is used, where, for example, the coil assemblies 24A are used in the evaporative heat exchanger 26A of Fig.
  • the coil assembly 24B is used in the evaporative heat exchanger 26B of Fig. 9
  • the coil assembly 24C is used in the evaporative heat exchanger 26C of Fig. 10
  • the coil assembly 24D is used in the evaporative heat exchanger 26D of Fig. 11 .
  • Any new components not used in a previous Fig. are identified by a different numeral.
  • Fig. 8 is a schematic, vertical cross-section view of an embodiment of a forced draft, counterflow, evaporative heat exchanger 26A including an arrangement of two finned tube coil assemblies 24A of the present invention within the plenum 40A of the evaporative heat exchanger.
  • the forced draft evaporative heat exchanger 26A of Fig. 8 uses a centrifugal fan 62 type of air mover to force air, entering the plenum 40A within the housing 38A through a screen 47 covering the air inlet.
  • the air is then forced generally vertically upwardly and through the coil assemblies 24A, through which water is flowing generally vertically downwardly. Thereafter, the air moves through the drift eliminators 60A and out of the evaporative heat exchanger 26A through the air outlet 46A.
  • the centrifugal fan 62 is typically mounted within a lower portion at one side of the housing 38A adjacent an air inlet typically covered by a screen 47. The sump for the water is not shown in Fig. 8 , but would be present below the coil assemblies 24A such that the water in the sump is blocked from reaching the centrifugal fan 62.
  • Fig. 9 is a schematic, vertical cross-section view of an embodiment of an induced draft evaporative heat exchanger 26B including an arrangement of a finned tube coil assembly 24B of the present invention located directly below a direct contact heat transfer media section including wet deck fill 64, described below, within the plenum 40B of the evaporative heat exchanger.
  • air is drawn into the plenum 40B through an air inlet 44B and any associated louvers or dampers 45B, where the air inlet 44B is laterally adjacent to the coil assembly 24B.
  • the evaporative heat exchanger 26B of Fig. 9 differs in a first respect from the evaporative heat exchanger 26 of Fig.
  • the evaporative heat exchanger 26B of Fig. 9 differs in a second respect from the evaporative heat exchanger 26 of Fig. 7 in that the evaporative heat exchanger 26B of Fig. 9 includes a direct contact heat exchange section containing wet deck fill 64 below the liquid distributor 54B and above the coil assembly 24B, which provides direct, evaporative heat exchange when the air flow and the evaporative water or other cooling liquid come into direct contact with each other and are mixed with some desired degree of turbulence within the wet deck fill 64 resulting in additional evaporative cooling.
  • the turbulent mixing of the air and water in the wet deck fill 64 allows for greater heat transfer between the air and water, but the benefits of the increased turbulent mixing in the wet deck fill 64 should not be overcome by potential adverse effects on the energy requirements of a larger fan motor or fan size or air flow reduction. As noted above, there is a fine balance among these factors when deciding whether and what type of wet deck fill heat transfer media to use. That is why the use of the wet deck fill 64 is optional in evaporative heat exchangers using the coil assembly of the present invention.
  • the wet deck fill may be any standard fill media, such as plastic fill, typically PVC, as well as wood or ceramic fill media, or any other fill media known in the art.
  • the presently preferred fill media is Evapco, Inc.'s EVAPAK® PVC fill, disclosed in Evapco, Inc.'s U.S. Patent 5,124,087 , the disclosure of which is hereby incorporated by reference herein, in its entirety.
  • wet deck fill 64 When wet deck fill 64 is used, it may be located above the coil assembly 24B as shown in Figs. 9 , or below the coil assembly 24C as shown in Fig. 10 , since in either location, the additional heat transfer in the wet deck fill 64 will further evaporatively cool the water draining into the sump 52B or 52C.
  • louvers 65 are built into the inlet side of the wet deck fill 64, such that the air may be drawn through the louvers 65 into the wet deck fill in a crossflow manner as described above with respect to the crossflow arrangement concerning the coil assembly 24B.
  • the embodiment of the evaporative heat exchanger 26B of Fig. 9 operates as follows. Ambient air in the environment of the evaporative heat exchanger is drawn into the plenum 40B through the air inlets 44B and any associated louvers or dampers 45B, and in a crossflow manner externally through the coil assembly 24B, though which water, pre-cooled in the wet deck fill 64 of the direct contact heat exchange section, externally flows generally vertically downwardly. Ambient air is also drawn into the wet deck fill 64 in a crossflow manner with respect to the water flowing generally vertically downwardly through the louvers 65, where the water is evaporatively cooled before it contacts the coil assembly 24B below the wet deck fill 64. The air is then drawn from the wet deck fill 64 into the plenum 40B.
  • Water is distributed over the wet deck fill 64 by the liquid distributor 54B where it is initially cooled evaporatively by mixing with the air flowing through the wet deck fill 64 before draining into the coil assembly 24B where it is turbulently mixed with the air and thereafter is drained from the coil assembly 24B and collected in the sump 52B.
  • the water is recycled from the sump 52B into the liquid distributor 54B through the conduit 56B by the pump 58B.
  • the air, with any entrained water, in the plenum 40B is drawn upwardly through drift eliminators 60 (not shown in Fig. 9 ) by the fan 48B in the air outlet housing 50B, before the air is exhausted through the air outlet 46B.
  • Fig. 10 is a schematic, vertical cross-section view of another embodiment of an induced draft evaporative heat exchanger 26C including an arrangement of a finned tube coil assembly 24C of the present invention located directly above a direct contact heat transfer media section including wet deck fill 64C within the plenum 40C of the evaporative heat exchanger.
  • the embodiment of the evaporative heat exchanger 26C of Fig. 10 operates as follows. One portion of ambient air in the environment of the evaporative heat exchanger is drawn into the apparatus through an inlet 44C at the top of the apparatus aligned above the coil assembly 24C and flows downwardly externally through the coil assembly in a generally vertical direction concurrent with the flow of water distributed over the coil assembly by the liquid distributor 54C.
  • Water is distributed over the coil assembly 24C by the liquid distributor 54C where it is mixed with the concurrently flowing air, thereby being cooled evaporatively in the coil assembly, exchanging heat with the coil assembly 24C, before draining into and through the wet deck fill 64C.
  • the water is further turbulently mixed with the cross-flowing air where it is further evaporatively cooled, and thereafter is drained from the wet deck fill 64C and collected in the sump 52C.
  • the water is recycled from the sump 52C into the liquid distributor 54C through the conduit 56C by the pump 58C.
  • the air with any entrained water is drawn into the plenum 40C and then upwardly through drift eliminators 60 (not shown in Fig. 10 ) by the fan 48C in the air outlet housing 50C, before the air is exhausted through the air outlet 46C.
  • Fig. 11 is a schematic, vertical cross-section view of an embodiment of an induced draft, counterflow, evaporative heat exchanger 26D including an arrangement of a finned tube coil assembly 24D located in a spaced configuration below wet deck fill 64D within the plenum 40D in the housing 38D in the evaporative heat exchanger.
  • the performance of evaporative heat exchange apparatus is measured by the amount of heat transfer, typically but not exclusively during cooling.
  • the measurements are affected by several factors. First, the measurements are affected by the amount and temperature of the process fluid flowing internally though the tubes 10 of the apparatus coil assembl(ies) 24 and the water or other cooling liquid flowing externally through the coil assembly.
  • the flow rates are measured using flow meters and the temperature is measured using thermometers.
  • the rate and temperature of the air flowing through the system is also significant, as well as the force required to drive the air mover 48 that moves the air through the apparatus.
  • the air flow is typically measured by an anemometer in feet per minute through a tube, although other well-known air flow measuring devices could also be used, and is typically determined by the rating of the motor driving the fan of the air mover, usually expressed in horsepower (HP).
  • the process fluid in the form of water
  • the process fluid is pumped into the inlet 30 and flows internally through the coil assembly at a rate of approximately 0.75 gpm to approximately 16.5 gpm per tube present in the coil assemblies, and preferably approximately 10 gpm per tube.
  • the amount and rate of water that passes externally through the coil assembl(ies) 24 supplied through the water supply conduit 56 as distributed by the liquid distributor 54 is approximately 1.5 gpm/sq. ft. to approximately 7 gpm/sq. ft. of coil plan area determined with respect to the major plane 25, and is preferably approximately 3 gpm/sq. ft.
  • the power of the fan motors varies within a very broad range, such as approximately 0.06 HP to approximately 0.5 HP per square foot of plan area of the coil assemblies used in the evaporative heat exchangers, corresponding to the area of the major plane 25 coextensive with the length and width of the coil assembly.
  • the tested coil assemblies all had a plan area of 6 feet (1.83 m) long (corresponding to serpentine tubes having segments with return bends fitting within frames of this length with the appropriate spacing) by 4 feet (1.22 m) wide (corresponding to 37 adjacent tubes that were packed within frames of this width with the appropriate spacing) and had ten generally horizontal rows of segments 12 with generally elliptical cross-sectional shapes connected by return bends having a circular cross-sectional shape, where the major axes of segments were arranged in various orientations.
  • All tested coil assemblies used tubes with return bends having an outside diameter of substantially 1.05 inches (2.67 cm) and segments having a nominal tube outside diameter of substantially 1.05 inches (2.67 cm), with a substantially horizontal center-to-center spacing D H of 1.0625 inches (2.699 cm) (designated “Narrow” in the Table below) or 1.156 inches (2.936 cm) (designated “Wide” in the Table below) and a substantially vertical center-to-center spacing D V of about 1.875 inches (4.763 cm).
  • One tested coil assembly had no fins 20 on the segments (Test ID "A” in the Table below and the graph of Fig. 12 ) and represented a base line against which other finned coil assemblies were compared.
  • Other tested coil assemblies identified in the Table below and the graph of Fig.
  • the performance of the coil assemblies was tested over varying water flow rates internally through the coils of 60 gpm to 360 gpm, water flow rates externally through the coils of approximately 5.9 gpm per square foot, and air flow rates of 300 feet per minute (91.44 meters per minute) to 750 feet per minute (228.6 meters per minute), generated by a fan driven by a 3 HP motor (except as noted above regarding Test ID "C").
  • the coil assemblies tested had the parameters as set forth in the following Table: Test ID Major Axes Orientation D H Tube Spacing Fins Fin Spacing (Fins/Inch) Fin Height (Inch) A 20 ° & 340° Ric-rac Wide No - - B 0° Wide Yes 3 0.25 C 20° & 340° Ric-rac Wide Yes 1.5 0.3125 D 0° Narrow Yes 3 0.3125 E 20° & 340° Ric-rac Wide Yes 3 0.3125 F 0° Wide Yes 3 0.3125 G 20° & 340° Ric-rac Wide Yes 1.5 0.5 H 20° & 340° Ric-rac Wide Yes 3 0.5
  • Fig. 12 is a graph of results of testing of the coil assemblies identified in the Table in the evaporative heat exchanger under the same conditions set forth in the procedure described above, with respect to preferred internal process fluid (water) flow rates from 6 to 9.8 gpm per tube (where each tube is identified as a "circuit" in the x-axis legend on the graph.
  • the graph show curves based on the heat transferred as measured in thousands of BTU/hour (MBH) versus the water flow internally through the coil assembly in gallons/minute/tube (GPM).
  • MMH BTU/hour
  • GPM gallons/minute/tube
  • the baseline performance of Curve A relates to coil assembly A, with a 20° to 340° ric-rac major axes segment orientation and no fins.
  • Curves B to F above Curve A indicate that at the indicated internal water flow rate along the X-axis, such curves have a better thermal performance than the baseline performance, with increasingly better thermal performance from Curve B to Curve F.
  • the test results show that an orientation of the major axes of the generally elliptical finned segments in a generally vertical direction (0°) provides better thermal performance than a ric-rac orientation of the major axes for tubes having the same fin height and fin spacing. Nevertheless arranging the major segments in a ric-rac orientation still provides a very considerable increase in thermal performance of a coil assembly having all of the other parameters within the scope of the present invention.
  • fins having a height of 0.3125 inch (0.794 cm) provided the better thermal performance.
  • less spacing within the parameters of the present invention provide better thermal performance.
EP11736229.3A 2010-07-16 2011-07-08 Evaporative heat exchange apparatus with finned elliptical tube coil assembly Active EP2593741B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL11736229T PL2593741T3 (pl) 2010-07-16 2011-07-08 Urządzenie wyparne do wymiany ciepła z zespołem wężownicy o eliptycznych rurach żebrowych

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US12/838,003 US20120012292A1 (en) 2010-07-16 2010-07-16 Evaporative heat exchange apparatus with finned elliptical tube coil assembly
PCT/US2011/043351 WO2012009221A2 (en) 2010-07-16 2011-07-08 Evaporative heat exchange apparatus with finned elliptical tube coil assembly

Publications (2)

Publication Number Publication Date
EP2593741A2 EP2593741A2 (en) 2013-05-22
EP2593741B1 true EP2593741B1 (en) 2014-09-03

Family

ID=44629007

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11736229.3A Active EP2593741B1 (en) 2010-07-16 2011-07-08 Evaporative heat exchange apparatus with finned elliptical tube coil assembly

Country Status (11)

Country Link
US (3) US20120012292A1 (pt)
EP (1) EP2593741B1 (pt)
CN (1) CN103080687B (pt)
AU (1) AU2011279513B2 (pt)
BR (1) BR112013000863B1 (pt)
CA (1) CA2805373C (pt)
ES (1) ES2525165T3 (pt)
MX (1) MX2013000602A (pt)
PL (1) PL2593741T3 (pt)
RU (1) RU2529765C1 (pt)
WO (1) WO2012009221A2 (pt)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013170802A (ja) * 2012-02-22 2013-09-02 Hoshizaki Electric Co Ltd 熱交換器および該熱交換器を備えた製氷機
US20140262167A1 (en) * 2013-03-14 2014-09-18 Mao-Ho Kuo Coil assembly
JP5544580B1 (ja) * 2013-07-26 2014-07-09 株式会社 エコファクトリー 空気調和装置及び空気調和装置の運転方法
CN103776278A (zh) * 2013-12-24 2014-05-07 河南省法斯特散热器有限公司 超长双排圆铜管翅片整体式芯体
WO2015170431A1 (ja) * 2014-05-09 2015-11-12 株式会社エコファクトリー 空気調和装置
US10502501B1 (en) * 2015-04-01 2019-12-10 Hrl Laboratories, Llc Louvered elliptical tube micro-lattice heat exchangers
ES2894870T3 (es) * 2016-01-08 2022-02-16 Evapco Inc Mejora de la capacidad térmica del intercambiador de calor con aletas elípticas
AU2017206116B2 (en) * 2016-01-08 2022-04-07 Evapco, Inc. Improvement of thermal capacity of elliptically finned heat exchanger
CN109073331A (zh) * 2016-04-01 2018-12-21 艾威普科公司 用于空气蒸发式换热器的多腔管
BR112018069956B1 (pt) * 2016-04-01 2022-07-12 Evapco, Inc Trocador de calor evaporativo para arrefecer ou condensar um fluido de processo
CA2970687A1 (en) * 2016-06-14 2017-12-14 Carbon Engineering Limited Partnership Capturing carbon dioxide
CN109844437A (zh) * 2016-07-22 2019-06-04 艾威普科公司 超窄通道超低制冷剂充注量蒸发式冷凝器
US10895420B2 (en) * 2016-09-01 2021-01-19 Spx Cooling Technologies, Inc. Hybrid fluid cooler method and apparatus
US10462565B2 (en) * 2017-01-04 2019-10-29 Samsung Electronics Co., Ltd. Displacement limiter for loudspeaker mechanical protection
CN106839854A (zh) * 2017-01-26 2017-06-13 上海宝丰机械制造有限公司 换热管及包括其的蒸发式冷凝器
RU2646524C1 (ru) * 2017-04-11 2018-03-05 Ришат Сафуанович Шаймухаметов Котел водотрубный
RU184599U1 (ru) * 2017-04-11 2018-10-31 Ришат Сафуанович Шаймухаметов Водотрубный котел
EP3410054B1 (en) * 2017-05-30 2022-10-26 Ge Avio S.r.l. Additively manufactured heat exchanger
CN107976101B (zh) * 2017-12-22 2023-07-14 上海发电设备成套设计研究院有限责任公司 一种外翅片换热管的使用方法
RU183563U1 (ru) * 2018-04-16 2018-09-25 Федеральное государственное бюджетное образовательное учреждение высшего образования "Волгоградский государственный технический университет" (ВолгГТУ) Оросительный теплообменник
TWI672479B (zh) * 2018-10-11 2019-09-21 國立臺北科技大學 散熱盤管排列結構與具有散熱盤管排列結構的冷卻水塔
US20220256743A1 (en) * 2021-02-10 2022-08-11 Bae Systems Information And Electronic Systems Integration Inc. Simplified liquid cooled card cage with internal and external heat
CN113639488B (zh) * 2021-06-28 2022-10-18 江苏河海新能源股份有限公司 一种高效除尘空气源热泵及其使用方法

Family Cites Families (45)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1284578A (en) * 1918-04-10 1918-11-12 Hjalmar F Branzell Wrought-iron ribbed pipe.
US2342412A (en) * 1941-08-28 1944-02-22 Bell Telephone Labor Inc Electron discharge device
US2430210A (en) * 1945-04-17 1947-11-04 Griscom Russell Co Method and apparatus for making finned tubing
US2532239A (en) * 1948-07-23 1950-11-28 Merchant & Evans Company Finned tube winding machine
US3180405A (en) * 1959-03-11 1965-04-27 Itt Condensers
US3025685A (en) * 1960-02-03 1962-03-20 Arkla Ind Means for wetting surfaces
US3384165A (en) * 1966-02-03 1968-05-21 Du Pont Heat exchanger
US3645330A (en) * 1970-02-05 1972-02-29 Mcquay Inc Fin for a reversible heat exchanger
US4236299A (en) * 1973-03-17 1980-12-02 Balke-Durr Aktiengesellschaft Method and device for winding spiral fins onto oval tubing
NO141963L (pt) * 1975-03-19
SE415607B (sv) * 1975-11-04 1980-10-13 Stal Laval Apparat Ab Anordning for stagning av kamflensror i vermevexlare
US4440216A (en) * 1980-02-18 1984-04-03 Lockheed Missiles & Space Company, Inc. Finned heat exchanger tube
BE894754A (fr) * 1982-10-21 1983-02-14 Huetoetechnika Ipari Szoevetke Pre-refroidisseur de vapeur combine pour des condenseurs notamment pour des installations de refrigeration
FR2543282A1 (fr) * 1983-03-21 1984-09-28 Bertin & Cie Refrigerant ferme a ventilation forcee et a circuit etanche
US5033544A (en) * 1985-08-21 1991-07-23 Abbott Roy W Looped fin heat exchanger and method for making same
US4755331A (en) * 1986-12-02 1988-07-05 Evapco, Inc. Evaporative heat exchanger with elliptical tube coil assembly
JPH0624714Y2 (ja) * 1987-02-18 1994-06-29 信和産業株式会社 角形向流式冷却塔
US5092038A (en) * 1989-04-03 1992-03-03 G. P. Industries, Inc. Method of manufacturing spiral heat exchanger tubes with an external fin
US4949543A (en) * 1989-09-12 1990-08-21 Modine Manufacturing Company Tube and fin assembly for heat exchangers in power plants
US5124087A (en) 1990-10-04 1992-06-23 Evapco International, Inc. Gas and liquid contact body
US5067322A (en) * 1990-10-05 1991-11-26 General Electric Company Refrigerator with spine fin evaporator
US5292056A (en) * 1990-12-08 1994-03-08 Gea Luftkuhler Gmbh method of welding heat exchangers
US5168923A (en) * 1991-11-07 1992-12-08 Carrier Corporation Method of manufacturing a heat exchanger plate fin and fin so manufactured
US5318112A (en) * 1993-03-02 1994-06-07 Raditech Ltd. Finned-duct heat exchanger
US5425414A (en) * 1993-09-17 1995-06-20 Evapco International, Inc. Heat exchanger coil assembly
DE4420848A1 (de) * 1994-06-15 1995-12-21 Balcke Duerr Ag Verdunstungskühlturm
JP3300728B2 (ja) * 1994-11-14 2002-07-08 三菱重工業株式会社 スパイラルフィンチューブを用いた熱交換器
JP2001173977A (ja) * 1999-12-10 2001-06-29 Samsung Electronics Co Ltd 冷凍サイクル用熱交換器及びその製造方法
US6315804B1 (en) 2000-01-07 2001-11-13 Evapco International, Inc. Drift eliminator
JP4496657B2 (ja) * 2001-03-05 2010-07-07 パナソニック株式会社 スパイラルフィンチューブ
US6598862B2 (en) 2001-06-20 2003-07-29 Evapco International, Inc. Evaporative cooler
TW563805U (en) * 2002-11-18 2003-11-21 Air Tech Co Ltd Condenser with refrigerant coil made of copper tube having streamlined cross-section
KR20040082571A (ko) * 2003-03-19 2004-09-30 엘지전자 주식회사 핀-튜브 일체형 열교환기
US6789317B1 (en) * 2003-06-17 2004-09-14 Bechtel Bwxt Idaho, Llc Finned tube with vortex generators for a heat exchanger
US6889759B2 (en) 2003-06-25 2005-05-10 Evapco, Inc. Fin for heat exchanger coil assembly
US6766655B1 (en) * 2003-10-16 2004-07-27 Ho Hsin Wu Evaporative condenser without cooling fins
US6820685B1 (en) * 2004-02-26 2004-11-23 Baltimore Aircoil Company, Inc. Densified heat transfer tube bundle
RU48046U1 (ru) * 2004-03-26 2005-09-10 Даниленко Виктор Георгиевич Оребренная труба пучка теплообменных труб аппарата воздушного охлаждения газа
US7717166B2 (en) * 2004-05-21 2010-05-18 United Aluminum Corporation Fin stock for a heat exchanger and a heat exchanger
US7913512B2 (en) * 2006-04-18 2011-03-29 Wood Group Advanced Parts Manufacture, Ag Air-heated heat exchanger
US7296620B2 (en) * 2006-03-31 2007-11-20 Evapco, Inc. Heat exchanger apparatus incorporating elliptically-shaped serpentine tube bodies
US7549465B2 (en) * 2006-04-25 2009-06-23 Lennox International Inc. Heat exchangers based on non-circular tubes with tube-endplate interface for joining tubes of disparate cross-sections
CN201020957Y (zh) * 2006-10-08 2008-02-13 第一美卡事业股份有限公司 卡片改良结构
US7475719B2 (en) 2006-12-14 2009-01-13 Evapco, Inc. High-frequency, low-amplitude corrugated fin for a heat exchanger coil assembly
JP5023911B2 (ja) * 2007-09-19 2012-09-12 パナソニック株式会社 スパイラルフィンチューブ型熱交換器

Also Published As

Publication number Publication date
AU2011279513B2 (en) 2015-02-26
CN103080687A (zh) 2013-05-01
RU2529765C1 (ru) 2014-09-27
EP2593741A2 (en) 2013-05-22
US20180003443A1 (en) 2018-01-04
WO2012009221A2 (en) 2012-01-19
AU2011279513A1 (en) 2013-02-28
RU2013106852A (ru) 2014-08-27
PL2593741T3 (pl) 2015-03-31
MX2013000602A (es) 2013-06-03
CN103080687B (zh) 2016-04-20
BR112013000863B1 (pt) 2020-12-15
ES2525165T3 (es) 2014-12-18
CA2805373A1 (en) 2012-01-19
CA2805373C (en) 2015-11-24
US20200300548A1 (en) 2020-09-24
BR112013000863A2 (pt) 2016-05-17
US20120012292A1 (en) 2012-01-19
WO2012009221A3 (en) 2012-04-26

Similar Documents

Publication Publication Date Title
US20200300548A1 (en) Evaporative heat exchange apparatus with finned elliptical tube coil assembly
KR100690101B1 (ko) 열교환기용 코일 조립체 및 이를 이용한 열 교환기
US9243847B2 (en) Hybrid heat exchange apparatus
US8966924B2 (en) Pre-cooling chamber for a cooling tower
US8739855B2 (en) Microchannel heat exchanger
EP3056846B1 (en) Improved heat exchange apparatus
CN107796239B (zh) 混合式流体冷却方法和装置
US20130240177A1 (en) Nested heat exchanger
US6702004B2 (en) Heat exchange method and apparatus
US6883595B2 (en) Heat exchange method and apparatus
US7913512B2 (en) Air-heated heat exchanger

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130213

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

DAX Request for extension of the european patent (deleted)
INTG Intention to grant announced

Effective date: 20130701

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140102

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140207

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 685833

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140915

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602011009645

Country of ref document: DE

Effective date: 20141016

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2525165

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20141218

REG Reference to a national code

Ref country code: NL

Ref legal event code: T3

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 685833

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140903

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141203

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20141204

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

REG Reference to a national code

Ref country code: PL

Ref legal event code: T3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150105

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150103

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602011009645

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

26N No opposition filed

Effective date: 20150604

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150708

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150731

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150731

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150708

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20110708

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230530

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CZ

Payment date: 20230622

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: PL

Payment date: 20230627

Year of fee payment: 13

Ref country code: NL

Payment date: 20230726

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: TR

Payment date: 20230706

Year of fee payment: 13

Ref country code: IT

Payment date: 20230720

Year of fee payment: 13

Ref country code: GB

Payment date: 20230727

Year of fee payment: 13

Ref country code: ES

Payment date: 20230804

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20230725

Year of fee payment: 13

Ref country code: DE

Payment date: 20230727

Year of fee payment: 13

Ref country code: BE

Payment date: 20230727

Year of fee payment: 13