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EP3455575B1 - Ailette pour un bloc à ailettes pour échangeurs de chaleur et échangeur de chaleur - Google Patents

Ailette pour un bloc à ailettes pour échangeurs de chaleur et échangeur de chaleur Download PDF

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Publication number
EP3455575B1
EP3455575B1 EP17735621.9A EP17735621A EP3455575B1 EP 3455575 B1 EP3455575 B1 EP 3455575B1 EP 17735621 A EP17735621 A EP 17735621A EP 3455575 B1 EP3455575 B1 EP 3455575B1
Authority
EP
European Patent Office
Prior art keywords
baffles
section
partially surrounded
fluid
constant
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
EP17735621.9A
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German (de)
English (en)
Other versions
EP3455575A1 (fr
Inventor
Michelangelo SASSANELLI
Matteo LEONI
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.)
Stefani SpA
Original Assignee
Stefani SpA
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Publication date
Application filed by Stefani SpA filed Critical Stefani SpA
Publication of EP3455575A1 publication Critical patent/EP3455575A1/fr
Application granted granted Critical
Publication of EP3455575B1 publication Critical patent/EP3455575B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • 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
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/02—Streamline-shaped elements

Definitions

  • the present invention regards a fin for a finned pack for heat exchangers, a finned pack and a heat exchanger including the latter.
  • Heat exchangers are used in many applications for heating or cooling a first fluid by placing it in heat exchange communication with a second fluid. This is usually obtained by conveying a first fluid in tubes which cross passage zones of the second fluid.
  • fins comprise plate-like elements having a plurality of holes in which tubes for conveying a first fluid are inserted, while a second fluid is sent between the fins for the heat exchange with the first fluid.
  • the fins can have substantially smooth or corrugated geometry, i.e. in particular if it is desired to increase the surface area or the efficiency of the heat exchange.
  • GB 332 455 A discloses a fin for a finned pack for heat exchangers having the features in the preamble of claim 1.
  • One object of the present invention is to provide a new fin of a finned pack for heat exchangers as well as a new finned pack and a new heat exchanger obtainable starting from one such fin.
  • Another object of the present invention is to provide a new fin of a finned pack that is able to ensure a greater heat exchange efficiency.
  • Another object of the present invention is to provide a fin like the aforesaid claim 1.
  • a fin 1 is illustrated for a finned pack for heat exchangers, which comprises a plate 2 in which a plurality of through holes 3 is obtained for the positioning of tubes 4 intended to convey a first heat exchange fluid, e.g. a liquid.
  • a first heat exchange fluid e.g. a liquid.
  • the plate 2 has an edge 5 as well as two main faces 6, each intended to be licked or hit by a second heat exchange fluid, such as air, in a crossing direction A-A from an inlet portion 5a to an outlet portion 5b of the edge 5 of the plate 2.
  • a second heat exchange fluid such as air
  • the facing main faces 6 of two adjacent and successive fins 1 together delimit a respective area of passage or crossing of a second fluid, which hits respective sections of tubes 4 inserted in such fins.
  • the edge 5 actually constitutes a face of external connection between the two main faces 6 and the same can be provided with two main sides 5a, 5b, e.g. parallel, which are bridge connected by means of secondary or smaller sides 5c, 5d, also if desired parallel and orthogonal to the main sides.
  • the main sides 5a, 5b actually constitute, respectively, the inlet portion 5a and the outlet portion 5b.
  • the holes 3 are delimited by a respective inner delimiting wall 7 of the plate 2, which includes a first portion 7a facing towards the inlet portion 5a and a second portion 7b (equal to or greater than the portion 7a) facing towards the outlet portion 5b.
  • the delimiting wall 7 for the holes 3 can be substantially cylindrical.
  • the fin 1 then comprises one or more confinement units 8, 9 for the flow of the second fluid, each confinement unit being placed around a respective section of the second portion 7b of the delimiting wall 7 of a hole 3 of the plurality of holes so as to obtain or define a partially surrounded hole or better yet a respective partially surrounded hole 3.
  • a confinement unit 8, 9 is provided for each hole 3 of the fin 1 or in any case for most of the holes 3 of the fin itself.
  • At least one confinement unit comprises two first baffles 8, 9 or two through recesses for housing second baffles placed on opposite sides from each other with respect to a respective partially surrounded hole 3, and each enclosing and spaced by a respective section of the second portion 7b of the delimiting wall 7 of the partially surrounded hole 3, so as to confine on the plate 2, during use, a first flow zone FZ1 of the second fluid between each baffle 8, 9 or recess and a respective section of the second portion 7b of the delimiting wall 7.
  • first baffles The configuration that will be described with reference to the first baffles is also applied in substance to the second baffles and vice versa, if it is considered that, once a finned pack is assembled, such components (first or second baffles) are intended to carry out the same task and substantially in the same manner.
  • the first flow zone FZ1 comprises a mouth for introducing the second fluid delimited between the plate 2, the first baffles 8, 9 and a part of the delimiting wall 7 as well as a mouth for delivering the second fluid leading into an area downstream of the respective hole 3, i.e. an area after the hole 3 in the sense of the crossing direction A-A.
  • the first flow zone FZ1 or better yet the walls thereof are fluid-sealed so as to prevent leaks or outflows of liquid between the introduction mouth and the delivery mouth.
  • the introduction mouth it is preferably delimited between the plate 2, a first end 8a, 9a of the first baffles 8, 9 or recesses and a part of the second portion 7b of the delimiting wall 7.
  • each baffle 8, 9 or of the recesses has one of the following geometries or extensions:
  • Such distance is calculated on a plane orthogonal to the axis x-x of a partially surrounded hole 3 and along an axis that connects the center or central point of the partially surrounded hole 3 with the baffle 8, 9 or better yet with the intrados of the baffle 8, 9 or of the recesses, i.e. the section of the baffles 8, 9 or recesses directed towards or facing the respective partially surrounded hole 3.
  • the first flow zone FZ1 has a section, evaluated with reference to a plane orthogonal to the plate 2 or in any case to the main extension plane thereof, and passing through the center or a central point of the respective partially surrounded hole 3, that is:
  • the first flow zone FZ1 does not have stagnation areas, i.e. it does not have first areas with section, evaluated with reference to a plane orthogonal to the plate 2 and passing through the center or a central point of the respective partially surrounded hole 3, greater than areas downstream and upstream, with reference to the sense from the inlet portion 5a to the outlet portion 5b of the first areas. If for example, the section of the first flow zone FZ1 first increases, and then once again decreases, there would be a stagnation zone of the second fluid at the increase of the section, which would involve an alteration of the laminar flow of the second fluid.
  • the initial angle ⁇ 0 is between 45° and 135°, preferably between 80° and 100°.
  • the first angle is between 45° and 135°, preferably between the value of the initial angle ⁇ 0 and 100°.
  • the second angle is between 45° and 180°, preferably between the value of the second angle ⁇ 2 and 150°.
  • the second angle ⁇ 2 is between 45° and 180°, preferably between 45° and 150°.
  • the section is constant and then diverging, identifying, in a plane orthogonal to the axis of symmetry x-x of the partially surrounded hole 3, a third angle ⁇ 3 between a second axis S2 that extends from the center of the partially surrounded hole 3 to the point of a baffle or recess 8, 9 defining the termination or end of the constant section and a fourth axis S4 that extends from the center of the partially surrounded hole 3 to the point of such baffle or recess 8, 9 defining the termination of the diverging section, the third angle ⁇ 3 is between 45° and 180°, preferably between the value of the first angle ⁇ 1 and 165°.
  • the section is converging and then diverging or constant, then converging and finally diverging, identifying, in a plane orthogonal to the axis of symmetry x-x of the partially surrounded hole 3, a third angle ⁇ 3 between a third axis S3 that extends from the center of the partially surrounded hole 3 to the point of a baffle or recess 8, 9 defining the termination of the converging section and a fourth axis S4 that extends from the center of the partially surrounded hole 3 to the point of such baffle or recess 8, 9 defining the termination of the diverging section, the third angle ⁇ 3 is between 45° and 180°, preferably between the value of the second angle ⁇ 2 and 165°.
  • the first baffles 8, 9 or the recesses can also be extended beyond a respective hole, i.e. they have terminal sections closer to the outlet portion 5b relative to a respective hole and hence define a second flow zone FZ2, that actually constitutes a continuation of the first flow zone FZ1, and such second flow zone FZ2 is delimited between terminal sections of the first baffles 8, 9 or recesses.
  • the second flow zone FZ2 is not extended around the respective partially surrounded hole 3.
  • the second flow zone FZ2 has a feeding mouth corresponding to the delivery mouth of the first flow zone FZ1 as well as a mouth for discharging the second fluid towards successive holes or parts of the fin with reference to the crossing direction A-A.
  • the second flow zone FZ2 or better yet the walls thereof are fluid-sealed so as to prevent leaks or outflows of fluid between the delivery mouth and the discharge mouth.
  • the second flow zone FZ2 has a section that is divergent, evaluated with reference to a plane orthogonal to the plate and passing through the center of the hole 3 partially surrounded by the respective baffle 8, 9 or groove.
  • the extrados 8d, 9d of the baffles 8, 9 or recesses i.e. the section of the baffles or recesses directed away from the respective partially surrounded hole 3
  • this is substantially rectilinear or slightly curved and does not have stagnation zones for the second fluid.
  • the concavity/convexity of the extrados 8d, 9d depends on the velocity field that is established due to the presence of other tubes.
  • the extrados 8d, 9d is substantially tilted with respect to the crossing direction A-A by an angle between -45° and 45°, preferably between 0° and +20° or between -15° and 45°, with an initial end 8a, 9a proximal to the inlet portion 5a and distal from the outlet portion 5b and a final end 8b, 9b distal from the inlet portion 5a and proximal to the outlet portion 5b, the initial ends 8a, 9a of the extradoses 8d, 9d of the baffles or recesses 8, 9 of a partially surrounded hole 3 being at a distance from each other greater than the distance between the final ends 8b, 9b of the extradoses 8d, 9d of such baffles or recesses 8, 9.
  • the baffles 8, 9 or recesses have a configuration, with reference to the travel sense or crossing direction A-A of the second fluid, with a first section 8e with preferably constant width, a second section 8f with preferably increasing width and then a third section 8g with preferably decreasing width.
  • the second section 8f has initial width equal to the first section 8e and final width equal to 2-5 times the first section, preferably 3-4 times the first section 8e.
  • the holes 3 are each extended around a respective axis of symmetry x-x, with the axes of symmetry x-x of the holes 3 being substantially parallel to each other, while the first baffles 8, 9 or the housing recesses for second baffles of a confinement unit 8, 9 are substantially symmetric to each other with respect to a plane passing through the crossing direction A-A from an inlet portion 5a to an outlet portion 5b of the edge 5 and (passing) through the axis of symmetry x-x of the at least partially surrounded respective hole 3.
  • the delimiting wall 7 can have a collar section 7c projecting upward with respect to one of the main faces 6, while the first baffles 8, 9 of the partially surrounded hole 3 with collar section 7c are extended around at least one part of the collar section 7c distal from the inlet portion 5a and facing towards the outlet portion 5b, the first or second baffles having height or thickness equal to or greater than the collar section 7c.
  • the collar section 7c of the delimiting walls 7 also carries out, in addition to the function of heat transfer between fin and tube, also the function of spacer between two adjacent and successive fins 1 of a finned pack.
  • the first baffles 8, 9 or the recesses of one or more confinement units 8, 9 have a first end 8a, 9a proximal to the inlet portion 5a as well as a second end 8b, 9b distal from the inlet portion 5a of the plate 2.
  • the first proximal 8a, 9a of the first baffles 8, 9 or housing recesses are at a first distance D1 from each other, while the distal ends 8b, 9b of the first baffles 8, 9 or recesses of a confinement unit are at a second distance D2 from each other which is advantageously smaller than the first distance D1, such that the first baffles or recesses together delimit a first area that is substantially tapered moving away from the inlet portion 5a.
  • the distance between the first baffles 8 could initially decrease moving away from the inlet portion 5a and then, having reached a minimum value at an intermediate portion of the first baffles, where the distance D3 between the baffles 8, 9 or recesses is minimal, once again increase up to the second end 8b, 9b; according to such variant, the distance D2 between the first baffles at the respective second end 8b, 9b could also be greater than the distance D1.
  • the area between the proximal ends and the intermediate portions of the first baffles or of the housing recesses is substantially tapered in the sense moving away from the inlet portion 5a, while a second area would be provided between the intermediate portions and the second ends of the first baffles or of the housing recesses with an initial section with decreasing cross section and then a terminal section with cross section increasing moving away from the inlet portion 5a.
  • the distance between the baffles 8, 9 or recesses in the sense moving away from the inlet portion 5a can initially progressively decrease and then, once a minimum value at an intermediate portion of the baffles or recesses has been reached, progressively increase once again up to the second end 8b, 9b.
  • the (first and/or second) baffles can have a tubular body or solid block body, which at the intrados 8h, 9h, i.e. the section of the baffles 8, 9 or recesses directed towards or facing the respective partially surrounded hole 3, is substantially flat or slightly curved with trim, preferably, orthogonal or projecting upward with respect to the plate 2.
  • the (first and/or second) baffles are, preferably, fluid-sealed (if desired they are not perforated) so as to prevent the passage of the second fluid therethrough.
  • each baffle is preferably formed in a single piece.
  • the intrados 8h, 9h of the baffles 8, 9 or of the second baffles is substantially continuous, so as to ensure the passage from one section of the first flow zone FZ1 to another (from constant to converging, from converging to diverging or from constant to diverging) in a gradual and progressive manner, i.e. there are no sudden passages or steps from one section of such first flow zone to another or along the extension of each of the same.
  • the intrados 8h, 9h along the first flow zone FZ1 comprises a curved or substantially curved surface, better yet slightly curved with concavity directed towards the first flow zone FZ1 itself at the areas with constant section and/or converging section thereof, and a curved or substantially curved surface, better yet slightly curved with concavity directed away from the flow zone itself at possible areas with diverging section thereof.
  • the intrados 8h, 9h of the baffles 8, 9 or of the second baffles is made in a manner such that the passage from a terminal section of the first flow zone FZ1 to the second flow zone FZ2 occurs in a gradual and progressive manner, i.e. there are no sudden passages or steps between such zones. More particularly, the intrados 8h, 9h at the passage from the first FZ1 to the second FZ2 flow zone comprises a curved surface or better yet slightly curved surface with concavity directed towards the extrados 8d, 9d.
  • the intrados 8h, 9h is therefore not flat or rectilinear.
  • the first baffles comprise a first drawn or cut and bent portion 2a of the plate 2, i.e. the baffles 8, 9 are obtained by means of drawing of the plate 2 itself. If a collar section 7c is provided, then both the first baffles 8, 9 and the collar sections 7c are obtained by means of drawing a respective plate 2.
  • the at least one drawn portion 2a of the plate 2 can be tapered moving away from the main extension plane of the plate 2, such that such drawn portion has a tip or free end 2a1 of lower width with respect to the base or end thereof for constraining 2a2 to the plate.
  • said baffles have a substantially tubular structure so as to delimit at least one first opening or channel (11).
  • Each drawn portion 2a preferably has two separate and drawn sections 2a3, 2a4 defining the channel or opening 11 therebetween, e.g. substantially tapered, the ends of which together defining the tip 2a1 and the base 2a2 of the drawn portion 2a.
  • the separate sections 2a3, 2a4 preferably have thickness lower than the remaining part of the plate 2, since the drawing determines or can determine a "stretching" of the edges, so as to increase the exposed surface area thereof and reduce their thickness.
  • the plate 2 can have second drawn portions, each set to define a collar section 7c, which in this case could be tapered like the first drawn portions.
  • Such second drawn portions ensure a good transfer of the heat between fin and tubes.
  • the (first and/or second) baffles 8, 9 can comprise a tubular body or solid block body with trim substantially orthogonal to the plate 2, and such tubular body or solid block body can be formed apart or separately with respect to the plate 2 and connected, if desired via welding or fitting with the plate 2.
  • second baffles could be formed apart and inserted each in a respective recess for housing a confinement unit 8, 9, and such baffles could have a configuration and, during use, arrangement substantially corresponding to the baffles 8, 9.
  • the second baffles could be metal sections obtained via extrusion, molding or shaping and mechanically inserted in the fins of a finned pack or better yet in the plates thereof, for example with forced insertion or via interference or by means of use of welding materials or alloys that facilitate the adhesion and the transmission of the heat.
  • the second baffles entirely fill the respective recesses, such that after the insertion of the second baffles there are no remaining parts of the recesses still open or not filled.
  • the height or thickness of the (first and/or second) baffles 8, 9, or even the pitch of the fins or distance between two successive fins, could vary from about 0.1 mm to about 36 mm.
  • one or more holes 3 will be considered with substantially circular or even non-circular cross section, e.g. oval, elliptical, etcetera and the first portion 7a and the second portion 7b with cross section that is substantially semi-circular, semi-oval, semi-elliptical, etcetera.
  • each baffle 8, 9 or recess can be at a third distance D4 from the delimiting wall 7 and more particularly from a section of the second portion 7b of the delimiting wall 7 between about 0.05R and about 3R, where with R the radius of a tube 3 or of a partially surrounded hole is indicated.
  • a fin like that illustrated in figures 1 to 4 allows reducing the so-called “dead zone" downstream of the tubes, with reference to the direction A-A of the flow of the second fluid.
  • baffles 8, 9 or in any case the baffles insertable in the housing recesses in fact determine, as can be verified, a conveyance or confinement of the second fluid on the second portion 7b of the respective delimiting wall 7 and hence towards the respective tube 4, which ensures that each portion of the delimiting wall 7 and hence of the respective tube is hit by the second fluid.
  • a fin according to the present invention preferably comprises one, two or more rows of holes 3, offset or aligned with respect to each other with respect to the crossing direction A-A, such that each row of holes 3 is at a distance from the inlet portion 5a that is different with respect to the other rows of holes 3.
  • a baffle 8, 9 can have tubular configuration defining an opening or first opening 11 (see figures 5 and 6 ), if desired extended substantially parallel to the axis of symmetry x-x of the respective hole 3.
  • Such opening 11 is typically used for the passage through the respective baffle, i.e. in a direction substantially parallel to the axis x-x, of a third fluid F3 such to increase the exchange efficiency of the exchanger.
  • the opening 11 could also be fed with the first F1 or the second F2 fluid.
  • baffles 8, 9 described above could have an opening or channel 11, such to have a structure that is substantially tubular with through opening extended substantially parallel to the axis of symmetry x-x of the respective hole 3.
  • the first opening 11 of one or more baffles could have a section with any suitable shape, e.g. circular, elliptical, rectangular or polygonal.
  • baffles 11 two or more openings or micro-channels 11 could also be provided.
  • one or more baffles could also delimit two or more channels or openings for the conveyance of two different fluids or for sending a same fluid between one channel and the next.
  • an opening 11 as indicated above can be present in particular if the baffles comprise metal sections obtained - via extrusion, molding or shaping - apart with respect to the plates 2 and then mechanically inserted in the plates 2 themselves, or portions 2a obtained via drawing or shaping of the plate 2a.
  • first opening 11 is delimited at the second 8f and third section 8g or at the first 8e, second 8f and third 8g section.
  • the baffles 8, 9 comprise a tubular body with thickness that is substantially constant, such that the delimiting wall for the opening 11 has constant thickness.
  • a fin according to the present invention could have AxB between 10 mm x 10 mm and 200 mm x 200 mm.
  • each row of holes 3 comprises at least one hole aligned along the crossing direction A-A with a respective hole of the other rows of holes and/or at least one hole offset with respect to the holes 3 of the other rows of holes 3, still with reference to the crossing direction A-A.
  • a fin according to the present invention comprises two or more lines or rows of holes 3, i.e. groups of holes substantially at a same distance from the inlet portion 5a.
  • the holes of adjacent and successive rows can be offset or aligned with reference to the crossing direction A-A.
  • a fin according to the present invention there may or may not be holes for the positioning of heating elements, e.g. through holes with diameter equal to 9.5 mm.
  • the thickness of a fin according to the present invention can vary between 0.1 mm and 2 mm.
  • the distance D5 of the intrados 8h, 9h of a baffle 8, 9 or recess at the first end 8a, 9a of the baffles or recesses from the initial axis S0 parallel to the crossing direction A-A, and passing through the center or a central point of the partially surrounded hole 3, can thus be as indicated hereinbelow: R 1 + 0.1 mm sin ⁇ 0 ⁇ D 5 ⁇ PT / 2 wherein R1 is the radius of a partially surrounded hole 3.
  • D5 is greater than 1.2R1 and smaller than 2.2R1.
  • the distance D6 of the extrados 8d, 9d of a baffle 8, 9 or recess at the first end 8a, 9a of the baffles or recesses from the initial axis S0 parallel to the crossing direction A-A, and passing through the center or a central point of the partially surrounded hole 3, can thus be as indicated hereinbelow: R 1 + 0.1 mm sin ⁇ 0 ⁇ D 6 ⁇ PT / 2 wherein R1 is the radius of a partially surrounded hole 3.
  • D6 is greater than D5 and smaller than D5 + 2 mm.
  • D2/2 is greater than D3/2 and smaller than D6.
  • the length D8 of the extrados 8d, 9d of the baffles or recesses can be as indicated hereinbelow: R 1 ⁇ D 8 ⁇ PR
  • D8 is greater than 0.8PR and smaller than 1.2PR.
  • the first flow zone FZ1 has a section, evaluated with reference to a plane orthogonal to the plate 2 and passing through the center or a central point of the respective partially surrounded hole 3, constant and then converging, or constant, then converging and finally diverging, or always constant or always converging, then, having considered D9 to be the value of the distance of the partially surrounded hole 3 from a baffle 8, 9 or recess at the termination of the constant section and, if provided, the start of the converging section, and D10 to be the value of the distance of the partially surrounded hole from a baffle 8, 9 or recess at the termination of the converging section, D9 and D10 can be as indicated hereinbelow: 0.1 mm ⁇ D 9 ⁇ PT / 2 ⁇ R 1 0.1 mm ⁇ D 10 ⁇ D 9
  • D9 is greater than 0.9(D5/sin( ⁇ 0)-R1) and smaller than D5/sin( ⁇ 0)-R1, while D10 is greater than 0.6(D5/sin( ⁇ 0)-R1) and smaller than 0.9(D5/sin( ⁇ 0)-R1).
  • D3/2 is greater than 0.4(D5/sin( ⁇ 0)-R1) and smaller than D5/sin( ⁇ 0)-R1.
  • the pitch or distance between the fins can vary between 1.2 and 36 mm.
  • this is a zone with a section which varies between completely constant and completely diverging, with constant and divergent sections alternating with each other and dependent on the mutual position of the tubes 4 and on their shape.
  • the length of the zone FZ2 is extended from 0 up to a line distance of 0.2 mm, with typical range of 0 to 3/4 the line distance.
  • the region between two baffles of two rows of tubes defines a further channel that has a section which can be a combination of straight, converging and diverging sections so as to guide the flow (there could be a line offset with the tube that is in the middle).
  • Each section will have a length comprised between 0 and the overall length of the baffle.
  • a fin 1 according to the present invention can then have a smooth surface or so-called “w_vaffle”, “pyramid” or “turbulence” surface. Such fin can also have an edge so-called “cap-like” or “smooth”.
  • the fin 1 could be made of any suitable material, e.g. aluminum, aluminum alloys, copper, copper alloys, steel, stainless steel made of different alloys, such as AISI 304, AISI 316, etcetera.
  • the fin 1 could be finished with surface treatments, e.g. painting, cataphoresis or other treatments.
  • a finned pack 10 is illustrated according to the present invention for heat exchangers, which comprises a plurality of fins 1 according to the present invention, placed in succession one after the other or one alongside the other and substantially parallel to each other.
  • Each fin 1 also has its through holes 3 aligned with the through holes 3 of the other fins 1.
  • the finned pack 10 then comprises an opening 10a for introducing a second fluid between pairs of fins of the plurality of fins, and an outlet opening 10b for the second fluid between the pairs of fins.
  • the fins 1 have the inlet portions 5a thereof at the introduction opening 10a and the outlet portions 5b thereof at the outlet opening 10b.
  • a plurality of tubes 4 inserted in the aligned through holes of the plurality of fins 1, the tubes 4 having a first sector 4a directed towards the inlet opening 10a as well as a second sector 4b directed towards the outlet opening 10b, the fins 1 having the confinement unit(s) 8, 9 around a portion of a second sector of a respective tube 4.
  • the tip 2a1 of the drawn portions 2a of a plate of one of such fins 1 is fit in the base 2a2 or better yet in the opening defined by the base 2a2 of the drawn portions 2a of an adjacent and successive fin 2.
  • the facing main faces 6 of two adjacent and successive fins 1 together delimit a respective area of passage or crossing of a second fluid that hits respective sections of tubes 4 inserted in such fins, and such tubes 4 as well as the baffles are extended through the passage areas so as to be hit by the flow of the second fluid.
  • the finned pack 10 can then comprise an upper tile 10c, a lower tile 10d and in addition at one side, manifolds 10f for the tubes 4, and on the other side forks 10g for transmitting the first fluid between two tubes 4.
  • each fin has at least one confinement unit with two through recesses for positioning baffles and each through recess of each confinement unit is aligned with a respective recess of the other fins.
  • the finned pack 10 also comprises two baffles for each confinement unit, each inserted in a respective series of aligned through recesses of the fins 1, preferably of all the fins of the finned pack 10.
  • the baffles or bars could constitute a mechanical load-bearing element of the finned pack 10.
  • the finned pack 10 or better yet the respective heat exchanger could comprise means for feeding a third fluid or the first fluid into the opening 11 of one or more baffles 8, 9.
  • outlets could be provided, along with tubular connection elements between the end of a baffle and a respective end of another baffle.
  • a circuit can be provided for feeding a third fluid constituted by the baffles connected with each other in series and/or in parallel.
  • the baffles could be connected in series and/or in parallel with each other and with the tubes 4, such that baffles and tubes would be fed with the first fluid.
  • the opening 11 could be simply placed in communication with the outside without providing for feeding the first or a third fluid within the same.
  • the tubes 4 of a finned pack 10 could be made, for example, of copper and its alloys, stainless steel and its alloys, iron and its alloys, aluminum and its alloys or other suitable materials.
  • the tubes could also have an internal wall that is smooth, grooved, e.g. tilted grooved, helical grooved or grooved with cross spirals.
  • the tubes could then have a diameter between 4 and 90 mm, advantageously between 5 and 22 mm, preferably 5 mm, 6.35 mm, 7.2 mm, 7.9 mm, 9.5 mm, 12 mm, 14, 16 mm or 22 mm.
  • the thickness of the tubes instead preferably varies between 0.15 and 3 mm, and, still more preferably, is equal to 0.25 mm, 0.28 mm, 0.32 mm, 0.35 mm, 0.4 mm or 0.5 mm.
  • a finned pack according to the present invention can be integrated or installed in:
  • a fin and a finned pack according to the present invention allow conveying the second fluid around the entire surface of the holes and hence of the tubes of the fin, also in the zone of each tube that is directed towards the outlet portion.
  • the second fluid correctly and uniformly hits and affects the part of the tubes directed towards the inlet portion of the fins, but in the zone between the tubes of one row and the tubes of a successive row, the second fluid "detaches" from the external surface of the tubes, hence it does not affect the part of the tubes directed towards the outlet portion of the fins.
  • this involves a considerable reduction of the heat exchange efficiency since most of the external face of the tubes crossed by the first fluid is not in heat exchange contact with the second fluid.
  • the second fluid is instead actually guided and maintained close to the tubes even in the zone downstream thereof, so as to affect and place the second fluid in heat exchange with the entire external face of the tubes and the portion of the fin 2 downstream of the tube 3, considerably improving the obtainable heat exchange efficiency.
  • baffles have been proposed that are intended to be licked by a fluid current (e.g. air), which are provided with the same object of increasing the thermally active surface and, hence, reducing the overall thermal resistance of the fin.
  • a fluid current e.g. air
  • thermo-fluid-dynamic problem that has two aspects:
  • the base of the baffles in particular when the same are obtained by means of drawing of a plate, is in direct contact with a surface (the plate 2) at high temperature, T w , while the lateral skirt thereof is hit with a fluid current (second fluid) that is cooler, which maintains the surface of the skirt of the baffles at a temperature T m (x) lower than that of the hot body (main body of the plate 2) and variable as a function of the distance x from the body itself.
  • the energy that, in this manner, enters within the baffles is removed via convection through the lateral skirt and the terminal surface thereof.
  • the convective heat flow can be evaluated with the following expression:
  • FZ0 is the initial flow zone around a tube 4 before or upstream of the inlet portion 8a, 9a or of the first flow zone FZ1.
  • zone FZ0 With reference to the zone FZ0, the part relative to the problem of the separation of the limit layer will be discussed; such problem is manifested at about the maximum radius (diameter) of the cylinder or tube 4 hit by the flow.
  • a flow dead zone is determined that is characterized by a region of stationary recirculation, which is formed downstream of the tube itself, thus allowing the complete separation of the dynamic flow at the geometric region affected by the vortical-stationary recirculation.
  • thermo-fluid-dynamic flow baffles in passive or active mode, i.e. without or with opening 11
  • the geometric role performed by the thermo-fluid-dynamic flow baffles will instead be described as a new solution for reducing the stationary recirculation (dead zone) so as to increase the transfer of convective heat.
  • the increase of the heat convection essentially regards the study of the heat exchange between a solid surface and a fluid that is moving with respect thereto.
  • the outlet section of the baffles is designed so as to determine a realignment and directional linking of the exiting flow with the tube of the successive line, in such a manner exploiting the increase of pressure generated in the section with possible divergence.
  • the type of fluid motion has such an effect on the heat exchange that it is possible to obtain various convection types.
  • the presence of forced convection will be considered.
  • Equation (1') is known as Newton's Law and the proportionality constant h[W/(m 2 K)] is termed coefficient of convective heat exchange or, more simply, convective coefficient. It is considered that h, unlike the heat conductivity, is not a thermo-physical property of the fluid, but it should be considered as an "easy" operating definition, useful in evaluating the quantity of heat exchanged in a convective manner.
  • Nu represents the ratio between the convective heat flow and the conductive heat flow in the fluid.
  • Nu represents the ratio between the convective heat flow and the conductive heat flow in the fluid.
  • the forced convection used in the tube/baffles system subjected to technical/analytical description assumes the existence of a fluid in relative motion with respect to a solid surface.
  • the geometry of the latter it is possible to make a distinction within the forced convection. Indeed, it is possible to distinguish between:
  • T b is the so-called bulk temperature or average temperature.
  • the latter is also termed mixing cup temperature, since it is the temperature which would be obtained by placing the entire fluid in an adiabatic container and mixing so as to eliminate any thermal gradient. This is very important in the internal outflows since there is no analogous undisturbed temperature T ⁇ .
  • the bulk temperature in a given section of the duct is defined as in equation 5: T b ⁇ ⁇ A s ⁇ uc v TdA s m ⁇ c v
  • equation 5 If it is set that the fluid is incompressible, (in the case of air, the fluid is compressible, but we can use the assumption of incompressibility given the operating conditions involved) and the physical properties are known and constant, equation 5 becomes: T b ⁇ ⁇ A s uTdA s V ⁇
  • the wall temperature T p is constant and independent from x
  • the thickness of the thermal limit layer increases with the increase of x.
  • the temperature gradient along y progressively decreases in moving away from the leading edge of a plate or sheet. Therefore, the coefficient of convective heat exchange h, and hence the heat flow q ⁇ , decrease with the increase of x.
  • the presence of the border surfaces conditions both the formation and the shape of the speed and thermal limit layers, and in this motion type it is possible to identify two regions: that of the inlet, where the motion is not developed, and that where the motion is completely developed. It is necessary at this point to better specify what is intended by completely developed motion.
  • the particles closest to the wall delimiting such channel undergo, due to the viscosity of the fluid, a deceleration while the particles at the center of the channel, in order to maintain the flow rate constant, are accelerated.
  • two limit layers are formed which tend to be thickened along the direction of the motion and that, if the distance L between the plates defining the channel is not high with respect to the length of the channel, are joined together at a certain distance x v from the inlet edge.
  • a parabolic speed distribution is created, typical of the fully developed laminar profile of Couette motion, which no longer varies with the increase of the distance on the inlet edge.
  • the entering fluid is at the uniform temperature T while the walls can be considered at the uniform and constant temperature T p and subject to a constant heat flow q ⁇ .
  • thermal limit layer is formed, in proximity to both interfaces, which is identical to that of the isolated profile. Nevertheless, continuing in the sense of the motion, these two tend to be thickened until they are joined at a distance x t , from the inlet edge, which is termed thermal development length, and finally defined as that distance from the inlet for which the Nusselt number differs by 5% from the value corresponding to the developed thermal operating conditions.
  • xt In laminar operating conditions, the value of xt depends on the thermal conditions at the wall and can be evaluated with the empirical expression 12, in the case of assigned wall temperatures, and 13, in the case of imposed heat flow.
  • x t D h 0.033 Re D h Pr
  • x t D h 0.045 Re D h Pr
  • the fluid-dynamic limit layer is much thicker than the thermal limit layer.
  • the local convective coefficient is constant and independent.
  • the length of thermal development can also be defined as that distance from the inlet edge for which the Nusselt number differs by 5% from the value corresponding to the developed thermal operating conditions.
  • the increase of performances is obtained with a marginal increase of the expenses necessary for the creation of the baffles, which can be obtained by means of fitting of the surfaces directly drawn from the surface of the existing fin.
  • the increase of the exchange surface area is in any case ensured and the geometry of the duct (and hence the shape of the baffle) can be reproduced with high accuracy.
  • baffles behave as passive elements, since their temperature is determined by the situation of equilibrium that is created between the heat transferred from the fin and that exchanged with the fluid.
  • the baffles 8, 9 have the double function of increasing the exchange on the main tube 4 and increasing the total surface area of heat exchange of the fin.
  • the proposed system has various applications.
  • An application of type c) with fluid in the channels 11 different from that of the tubes 4 is obtained in the applications of cooling the second fluid by means of a first fluid moving within the tubes 4.
  • a first fluid moving within the tubes 4. in particular when the temperature of the second fluid falls below 0°C, there is the formation of frost or ice around the tube 4 and on the fins 2.
  • the system will function as a double-flow exchanger in which the transfer of heat between the two fluids (in the tube 4 and in the channels 11) occurs via pure conduction. Together with this conduction, however, we also have the convective part within the flow zones created by the baffles.
  • the calculation complication is given by the boundary conditions which depend on the conduction equation.
  • the thermal gradient that is established leads to having a complex temperature field, determined by the two wall temperatures, by their thermal connection and by the temperature of the fluid which passes inside the channels.
  • the fluid carries out two independent heat exchanges with the two surfaces (in realty, there is a further exchange with the fin, which we can consider similar to that of the passive case or that without the baffles).
  • the duct can be divided into two semi-ducts in which the (undisturbed) temperature end point is not reached at the center line, but at a distance from the walls proportional to the temperature difference between wall and fluid. The point will be situated closer to the colder wall than from the warmer wall.
  • the movement of the thermal well from the center line towards the colder wall uses a greater quantity of fluid for the heat exchange, thus increasing the machine output.
  • each tube of an existing geometry can be substituted with the tube+baffles assembly. From the structural standpoint, the system can be easily made by means of cutting and drawing the existing fin so as to create a continuous and load-bearing system of channels for the structure.

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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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Claims (23)

  1. Ailette pour un ensemble à ailettes (10) pour échangeurs de chaleur, comprenant une plaque (2) dans laquelle une pluralité de trous traversants (3) est obtenue pour le positionnement de tubes (4) destinés à transporter un premier fluide d'échange de chaleur, ladite plaque (2) comportant un bord (5) ainsi que deux faces principales (6), chacune étant destinée à être léchée par un deuxième fluide d'échange de chaleur dans une direction transversale (A-A) d'une partie d'entrée (5a) à une partie de sortie (5b) dudit bord (5) de ladite plaque (2), lesdits trous (3) étant délimités par une paroi de délimitation intérieure (7) respective de ladite plaque (2) comprenant une première partie (7a) orientée vers ladite partie d'entrée (5a) et une deuxième partie (7b) orientée vers ladite partie de sortie (5b), ladite ailette comprenant au moins une unité de confinement (8, 9) dudit deuxième fluide disposée autour d'un trou (3) de ladite pluralité de trous (3) de manière à obtenir au moins un trou (3) partiellement entouré, ladite au moins une unité de confinement comprenant deux déflecteurs (8, 9) ou deux évidements traversants pour contenir les déflecteurs (8, 9) disposés l'un opposé à l'autre par rapport à un trou (3) partiellement entouré respectif et chacun entourant et étant espacé d'une section respective de ladite deuxième partie (7b) de ladite paroi de délimitation (7) dudit trou (3) partiellement entouré, de manière à confiner, pendant l'utilisation, sur ladite plaque (2) une première zone d'écoulement (FZ1) dudit deuxième fluide entre chaque déflecteur (8, 9) ou évidement et une section respective de ladite deuxième partie (7b) de ladite paroi de délimitation (7),
    dans laquelle ladite première zone d'écoulement (FZ1) présente une section, évaluée en référence à un plan orthogonal à ladite plaque (2) et traversant le centre ou le point central du trou (3) partiellement entouré respectif, qui est
    constante sur toute son extension,
    constante puis divergente,
    convergente sur toute son extension,
    convergente puis divergente,
    constante puis convergente, ou
    constante, puis convergente et enfin divergente,
    et dans laquelle l'intrados (8h, 9h) desdits déflecteurs (8, 9) ou desdits évidements le long de ladite première zone d'écoulement (FZ1), c.à.d. la section desdits déflecteurs (8, 9) ou évidements orientée vers ou face au trou (3) partiellement entouré respectif, comprend une surface incurvée ou sensiblement incurvée avec la concavité orientée vers ladite première zone d'écoulement (FZ1) au niveau des zones avec une section constante et/ou convergente de ladite première zone d'écoulement (FZ1), et une surface incurvée ou sensiblement incurvée avec la concavité orientée loin de ladite première zone d'écoulement (FZ1) au niveau des zones optionnelles avec la section divergente de ladite première zone d'écoulement (FZ1), caractérisé en ce que lesdits déflecteurs (8, 9) ont une structure sensiblement tubulaire de manière à délimiter au moins une première ouverture ou un premier canal (11).
  2. Ailette selon la revendication 1, dans laquelle ladite première zone d'écoulement (FZ1) ne comporte pas de zones de stagnation, c.à.d. qu'elle ne comporte pas de premières zones avec une section, évaluée en référence à un plan orthogonal à ladite plaque (2) et traversant le centre du trou (3) partiellement entouré respectif, supérieure aux zones en aval et en amont desdites premières zones.
  3. Ailette selon l'une quelconque des revendications précédentes, dans laquelle en identifiant, dans un plan orthogonal à l'axe de symétrie x-x d'un trou (3) partiellement entouré, un angle initial (α0) entre un axe initial (S0) parallèle à ladite direction transversale (A-A) et traversant le centre ou un point central du trou (3) partiellement entouré et un premier axe (S1) qui s'étend depuis le centre ou le point central du trou (3) partiellement entouré jusqu'à la partie d'entrée (8a, 9a) d'un déflecteur ou évidement (8, 9), ledit angle initial (α0) étant entre 45° et 135°, de préférence entre 80° et 100°.
  4. Ailette selon la revendication 3, dans laquelle en identifiant, dans un plan orthogonal à l'axe de symétrie (x-x) d'un trou (3) partiellement entouré, un premier angle (α1) entre un premier axe (S1) qui s'étend depuis le centre ou un point central du trou (3) partiellement entouré jusqu'à la première extrémité (8a, 9a) d'un déflecteur ou évidement (8, 9) et un deuxième axe (S2) qui s'étend depuis le centre ou le point central du trou (3) partiellement entouré jusqu'au point de ce déflecteur ou évidement (8, 9) définissant la fin ou l'extrémité de ladite section constante, le premier angle est entre 45° et 135°.
  5. Ailette selon la revendication 4, dans laquelle ledit premier angle (α1) a une valeur entre la valeur de l'angle initial (α0) et 100°.
  6. Ailette selon l'une quelconque des revendications précédentes, dans laquelle si ladite section de ladite première zone d'écoulement (FZ1) est constante puis convergente ou constante, puis convergente et enfin divergente, en identifiant dans un plan orthogonal à l'axe de symétrie (x-x) du trou (3) partiellement entouré un deuxième angle (α2) entre un deuxième axe (S2) qui s'étend depuis le centre du trou (3) partiellement entouré jusqu'au point d'un déflecteur ou évidement (8, 9) définissant la fin ou l'extrémité de la section constante et un troisième axe (S3) qui s'étend depuis le centre du trou (3) partiellement entouré jusqu'au point de ce déflecteur ou évidement (8, 9) définissant la fin ou l'extrémité de la section convergente, ledit deuxième angle (α2) est entre 45° et 180°, alors que
    si la section de ladite première zone d'écoulement (FZ1) est convergente sur toute son extension ou convergente puis divergente, en identifiant dans le plan orthogonal un deuxième angle (α2) entre un deuxième axe (S2) qui s'étend depuis le centre du trou (3) partiellement entouré jusqu'au point d'un déflecteur ou évidement (8, 9) définissant la première extrémité (8a, 9a) d'un déflecteur ou évidement (8, 9) et un troisième axe (S3) qui s'étend depuis le centre du trou (3) partiellement entouré jusqu'au point de ce déflecteur ou évidement (8, 9) définissant la fin ou l'extrémité de la section convergente, le deuxième angle (α2) est entre 45° et 180°, de préférence entre 45° et 150°.
  7. Ailette selon la revendication 4 et 6 ou 5 et 6, dans laquelle ladite section est constante puis convergente ou constante, puis convergente et enfin divergente, et dans laquelle ledit deuxième angle (α2) a une valeur comprise entre la valeur dudit premier angle (α1) et 150°.
  8. Ailette selon l'une quelconque des revendications 4 à 7, dans laquelle si ladite section est constante puis divergente, en identifiant dans un plan orthogonal à l'axe de symétrie (x-x) du trou (3) partiellement entouré un troisième angle (α3) entre un deuxième axe (S2) qui s'étend depuis le centre du trou (3) partiellement entouré jusqu'au point d'un déflecteur ou évidement (8, 9) définissant la fin ou l'extrémité de la section constante et un quatrième axe (S4) qui s'étend depuis le centre du trou (3) partiellement entouré jusqu'au point de ce déflecteur ou évidement (8, 9) définissant l'extrémité de la section divergente, le troisième angle (α3) est entre 45° et 180°, alors que si la section est convergente puis divergente ou constante, puis convergente et enfin divergente, en identifiant dans un plan orthogonal à l'axe de symétrie (x-x) du trou (3) partiellement entouré un troisième angle (α3) entre un troisième axe (S3) qui s'étend depuis le centre du trou (3) partiellement entouré jusqu'au point d'un déflecteur ou évidement (8, 9) définissant l'extrémité de la section convergente et un quatrième axe (S4) qui s'étend depuis le centre du trou (3) partiellement entouré jusqu'au point de ce déflecteur ou évidement (8, 9) définissant l'extrémité de la section divergente, le troisième angle (α3) est entre 45° et 180°.
  9. Ailette selon la revendication 4 et 8 ou 5 et 8, dans laquelle ladite section est constante puis divergente, dans laquelle ledit troisième angle (α3) présente une valeur comprise entre la valeur dudit premier angle (α1) et 165°, ou
    selon la revendication 6 et 8 ou 7 et 8, dans laquelle ladite section est convergente puis divergente ou constante, puis convergente et enfin divergente, et dans laquelle ledit troisième angle (α3) présente une valeur comprise entre la valeur dudit deuxième angle (α2) et 165°.
  10. Ailette selon l'une quelconque des revendications précédentes, dans laquelle lesdits déflecteurs (8, 9) ou lesdits évidements de logement s'étendent au-delà d'un trou (3) partiellement entouré respectif, c.à.d. que lesdits déflecteurs (8, 9) ou lesdits évidements de logement présentent des sections d'extrémité plus proches de ladite partie de sortie (5b) par rapport à un trou (3) partiellement entouré respectif et définissant une deuxième zone d'écoulement (FZ2) constituant une continuité de ladite première zone d'écoulement (FZ1), ladite deuxième zone d'écoulement (FZ2) ne s'étendant pas autour dudit trou (3) partiellement entouré, ladite deuxième zone d'écoulement (FZ2) présentant un orifice d'alimentation correspondant à l'orifice de distribution de ladite première zone d'écoulement (FZ1) ainsi qu'un orifice d'évacuation pour ledit deuxième fluide vers des parties de ladite ailette successives dans le sens de ladite direction transversale (A-A), ladite deuxième zone d'écoulement (FZ1) présentant une section, évaluée en référence à un plan orthogonal à ladite plaque et traversant le centre du trou (3) partiellement entouré respectif, qui est divergente.
  11. Ailette selon l'une quelconque des revendications précédentes, dans laquelle les déflecteurs (8, 9) ou les évidements de logement d'une unité de confinement respective présentent une première extrémité (8a, 9a) proche de ladite partie d'entrée (5a), une deuxième extrémité (8b, 9b) distante de ladite partie d'entrée (5a) de ladite plaque (2) et dans laquelle la distance entre lesdits déflecteurs (8, 9) ou lesdits évidements dans la direction d'éloignement de la partie d'entrée (5a) diminue initialement progressivement puis, une fois qu'une valeur minimale a été atteinte au niveau d'une partie intermédiaire desdits déflecteurs ou évidements (8, 9), augmente progressivement de nouveau jusqu'à ladite deuxième extrémité (8b, 9b).
  12. Ailette selon l'une quelconque des revendications précédentes, dans laquelle l'extrados (8d, 9d) desdits déflecteurs (8, 9) ou desdits évidements, c.à.d. la section desdits déflecteurs ou desdits évidements orientée loin du trou (3) partiellement entouré respectif, est sensiblement rectiligne ou légèrement incurvé et ne présente pas de zones de dépression ou de stagnation pour ledit deuxième fluide.
  13. Ailette selon la revendication 12, dans laquelle ledit extrados est sensiblement incliné par rapport à ladite direction transversale (A-A) pour un angle entre -45° et 45°, avec une extrémité initiale (8a, 9a) proche de ladite partie d'entrée (5a) et distante de ladite partie de sortie (5b) et une extrémité finale (8b, 9b) distante de ladite partie d'entrée (5a) et proche de ladite partie de sortie (5b), les extrémités initiales (8a, 9a) des extrados (8d, 9d) des déflecteurs ou évidements d'un trou partiellement entouré étant situées à une les unes des autres supérieure à la distance entre les extrémités finales (8b, 9b) des extrados (8d, 9d) de ces déflecteurs ou évidements.
  14. Ailette selon la revendication 12 ou 13, dans laquelle chaque déflecteur (8, 9) ou évidement de ladite au moins une unité de confinement présente un intrados (8h, 9h) qui n'est pas parallèle à l'extrados (8d, 9d) respectif, c.à.d. la section des déflecteurs (8, 9) ou des évidements orientée loin du trou (3) partiellement entouré respectif.
  15. Ailette selon l'une quelconque des revendications précédentes, dans laquelle lesdits déflecteurs (8, 9) ou évidements ont une configuration, en référence au sens de déplacement dudit deuxième fluide sur ladite plaque (2), avec une première section (8e) de largeur constante, une deuxième section (8f) de largeur croissante puis une troisième section (8g) de largeur décroissante.
  16. Ailette selon l'une quelconque des revendications précédentes, dans laquelle ladite au moins une première ouverture ou ledit au moins un premier canal (11) s'étend sensiblement parallèlement à l'axe de symétrie (x-x) du trou (3) respectif et est défini(e) pour permettre le passage à travers le déflecteur respectif et dans une direction sensiblement parallèle audit axe de symétrie (x-x) d'un troisième fluide ou dudit premier fluide ou est défini(e) pour être en communication avec l'extérieur.
  17. Ailette selon la revendication 15, dans laquelle ladite première ouverture (11) est délimitée au niveau de ladite deuxième (8f) et de ladite troisième (8g) section ou au niveau de ladite première (8e), ladite deuxième (8f) et ladite troisième (8g) section.
  18. Ailette selon l'une quelconque des revendications précédentes, dans laquelle lesdits déflecteurs (8, 9) comprennent un corps tubulaire d'une épaisseur sensiblement constante.
  19. Ailette selon l'une quelconque des revendications précédentes, dans laquelle lesdits déflecteurs (8, 9) comprennent au moins une partie étirée (2a) de la plaque (2), c.à.d. que lesdits déflecteurs (8, 9) sont obtenus par étirage de ladite plaque (2).
  20. Ailette selon la revendication 19, dans laquelle ladite au moins une partie étirée (2a) de ladite plaque (2) est effilée en s'éloignant du plan d'extension principal de ladite plaque (2), de telle sorte que ladite au moins une partie étirée (2a) présente une extrémité ou un bout libre (2a1) moins large que sa base ou extrémité (2a2) pour le maintien sur la plaque (2).
  21. Ensemble à ailettes pour un échangeur de chaleur, comprenant :
    - une pluralité d'ailettes (1) selon l'une quelconque des revendications précédentes, disposées en succession l'une après l'autre et sensiblement parallèles l'une à l'autre, chaque ailette (1) comprenant des trous traversants (3) alignés avec les trous traversants (3) des autres ailettes (1) ;
    - une ouverture d'introduction (10a) pour introduire un deuxième fluide entre des paires d'ailettes (1) de ladite pluralité d'ailettes (1), lesdites ailettes (1) ayant leurs parties d'entrée (5a) au niveau de ladite ouverture d'introduction (10a) ;
    - une ouverture de sortie (10b) pour ledit deuxième fluide entre lesdites paires d'ailettes (1), lesdites ailettes (1) ayant leurs parties de sortie (5b) au niveau de ladite ouverture de sortie (10b) ;
    - une pluralité de tubes (4) insérés dans les trous traversants (3) alignés de ladite pluralité d'ailettes (1), lesdits tubes (4) comportant un premier secteur (4a) orienté vers ladite ouverture d'entrée (10a) ainsi qu'un deuxième secteur (4b) orienté vers ladite ouverture de sortie (10b) ; et
    lesdites ailettes (1) comprenant une unité de confinement (8, 9) autour d'une partie d'un deuxième secteur (4b) d'au moins l'un desdits tubes (4).
  22. Ensemble à ailettes selon la revendication 21 quand il est doté d'au moins deux ailettes adjacentes et successives selon la revendication 20, dans lequel ledit bout (2a1) des parties étirées (2a) d'une plaque (2) est inséré dans la base (2a2) ou mieux dans l'ouverture définie par la base (2a2) des parties étirées (2a) d'une ailette (2) adjacente et successive.
  23. Échangeur de chaleur avec un ensemble à ailettes comprenant au moins un ensemble à ailettes selon la revendication 21 ou 22.
EP17735621.9A 2016-05-13 2017-05-12 Ailette pour un bloc à ailettes pour échangeurs de chaleur et échangeur de chaleur Active EP3455575B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITUA2016A003433A ITUA20163433A1 (it) 2016-05-13 2016-05-13 Aletta per un pacco alettato per scambiatori di calore, nonché scambiatore di calore
PCT/IB2017/052794 WO2017195157A1 (fr) 2016-05-13 2017-05-12 Ailette pour un bloc à ailettes pour échangeurs de chaleur et échangeur de chaleur

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EP3455575A1 EP3455575A1 (fr) 2019-03-20
EP3455575B1 true EP3455575B1 (fr) 2021-03-10

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WO (1) WO2017195157A1 (fr)

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EP3443287B1 (fr) * 2016-04-14 2021-12-08 Linde GmbH Fluide caloporteur enroule
JP6897372B2 (ja) * 2017-07-03 2021-06-30 ダイキン工業株式会社 熱交換器
CN117199032B (zh) * 2023-10-07 2025-01-03 中科可控信息产业有限公司 一种微通道液冷冷板散热器
CN120467050A (zh) * 2024-02-09 2025-08-12 特灵空调系统(中国)有限公司 具有椭圆形套环基部和翼型件的翅片及相关的翅片管热交换器

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Publication number Priority date Publication date Assignee Title
GB332455A (en) * 1928-10-26 1930-07-24 Hugo Junkers Improvements in and relating to heat-exchanging apparatus
JPS5552228Y2 (fr) * 1975-04-28 1980-12-04
KR100225627B1 (ko) * 1996-12-30 1999-10-15 윤종용 공기조화기의 열교환기
JP2000009391A (ja) * 1998-06-19 2000-01-14 Kimura Kohki Co Ltd 空気調和機用熱交換コイル
JP4115390B2 (ja) * 2001-08-10 2008-07-09 よこはまティーエルオー株式会社 伝熱装置
DE102010038945A1 (de) * 2010-08-05 2012-02-09 Behr Gmbh & Co. Kg Plattenförmiger Wärmeübertrager für eine, mindestens ein Wärmeübertragerpaket aufweisende Kühleinrichtung
CN102135388A (zh) * 2011-03-25 2011-07-27 兰州交通大学 三角形曲面涡产生器式圆管管翅换热器
CN102297624A (zh) * 2011-07-14 2011-12-28 许昌怡家电器有限公司 一种强化换热翅片
CN203432432U (zh) * 2013-08-01 2014-02-12 宁波大学 一种翅片
CN204495146U (zh) * 2014-12-19 2015-07-22 北京龙源冷却技术有限公司 一种空冷散热器翅片

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EP3455575A1 (fr) 2019-03-20
ITUA20163433A1 (it) 2017-11-13
CN109477704A (zh) 2019-03-15
US20190145716A1 (en) 2019-05-16
WO2017195157A1 (fr) 2017-11-16

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