WO2006124014A1 - Ailettes de types multiples pour multi-echangeurs - Google Patents

Ailettes de types multiples pour multi-echangeurs Download PDF

Info

Publication number
WO2006124014A1
WO2006124014A1 PCT/US2005/016421 US2005016421W WO2006124014A1 WO 2006124014 A1 WO2006124014 A1 WO 2006124014A1 US 2005016421 W US2005016421 W US 2005016421W WO 2006124014 A1 WO2006124014 A1 WO 2006124014A1
Authority
WO
WIPO (PCT)
Prior art keywords
fin
separator
exchanger
heat exchanger
tubes
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.)
Ceased
Application number
PCT/US2005/016421
Other languages
English (en)
Other versions
WO2006124014A8 (fr
Inventor
Zaiqian Hu
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.)
Valeo Inc
Original Assignee
Valeo 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 Valeo Inc filed Critical Valeo Inc
Priority to EP05747445A priority Critical patent/EP1966558A1/fr
Priority to PCT/US2005/016421 priority patent/WO2006124014A1/fr
Priority to JP2008511090A priority patent/JP2008540998A/ja
Anticipated expiration legal-status Critical
Publication of WO2006124014A1 publication Critical patent/WO2006124014A1/fr
Publication of WO2006124014A8 publication Critical patent/WO2006124014A8/fr
Ceased legal-status Critical Current

Links

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
    • F28D1/00—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, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—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, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—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, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0443—Combination of units extending one beside or one above the other
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0084—Condensers
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0089—Oil coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/0287—Other particular headers or end plates having passages for different 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
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/16—Safety or protection arrangements; Arrangements for preventing malfunction for preventing leakage

Definitions

  • the invention relates to the field of multi-exchangers such as combo cooler heat exchangers, for automotive vehicles, having a bank of spaced fluid conduits or tubes capable of being traversed by different fluids and fins of varying structure.
  • engine oils transmission oil, power steering oil, etc
  • oil coolers are located either within the water tank of a radiator (called “water-cooled in-tank” oil cooler) or in front of condensers (air-cooled oil cooler).
  • water-cooled in-tank oil cooler water-cooled in-tank oil cooler
  • air-cooled oil cooler air-cooled oil cooler
  • the traditional oil cooler layout has several advantages: the in-tank oil cooler has good cold start in the winter, as oil is warmed by water inside radiator. Air-cooled oil coolers have flexibility of location. The disadvantages of a separate air-cooler are decreased by employing an air-cooled oil-cooler within a combo-cooler, which leads to lower cost, as well as huge packaging savings.
  • the use of fins in air-cooled type heat exchangers for automobiles is known. Fins reduce the temperature of various working fluids, including engine coolant, engine lubricating oil, air conditioning refrigerant, and automatic transmission fluid, among others.
  • the heat exchanger typically includes a plurality of spaced fluid conduits or tubes connected between an inlet and an outlet, and a plurality of heat exchanging fins interposed between adjacent tubes or conduits. Air is directed across the fins via a cooling fan or the motion of the automobile. As the air flows across the fins, heat in the fluid flowing in the tubes is conducted through the walls of the tubes into the fins and transferred or "exchanged" into the airflow.
  • fins or separators are used.
  • the fins or separators may touch or connect similar types of tubes, (i.e. the fins or separators may 'touch' or 'connect' condenser tubes to condenser tube, or oil tube to oil tubes), or different tubes (for example condenser to oil tubes, etc.).
  • Thermal efficiency is measured by dividing the amount of heat that is actually transferred by the heat exchanger in a given set of conditions (amount of airflow, temperature difference between the air and fluid, etc.) by the theoretical maximum possible heat transfer under those conditions. An increase in the rate of heat transfer, therefore, results in greater thermal efficiency. Heat transfer is also affected by the air pressure drop associated with the change in airflow direction caused by the fins. A greater air pressure drop results in less heat transfer.
  • Various types of fin designs have been disclosed in the prior art with the object of increasing the heat exchanger efficiency by making improvements in the fins and airflow pattern.
  • Multi-exchanger or combo-coolers have two or more heat exchanger parts comprising fluid conduits or tubes wherein different fluids can flow within the different tubes.
  • Combo coolers therefore, encounter manufacturing difficulties, and, therefore, there has been a need to find solutions to make production of said coolers more uniform, and therefore, increase efficiency of production.
  • the prior art has shown a fin preference towards using the same types of fins or separators in heat exchangers.
  • One objective of the present invention is to optimize the designs of heat exchangers, and, in particular, heat exchangers comprising different heat exchanger parts or elements, wherein the use of different type fins or separators or different parts of the heat exchanger, and, especially, on the multi-exchanger on combo cooler, is achieved to result in a superior overall thermal exchange function. More particularly, it is an object of the invention to provide a heat exchanger comprising at least one multi-exchanger or combo cooler, with fins or separators, with superior overall thermal exchange function while remaining competitive from a cost standpoint.
  • It a further object of the invention to provide for a design of heat exchanger comprising both oil cooler and condenser parts or elements, such as a combo cooler, which, with improved overall thermal exchange properties, and, which, when used in conjunction with other single heat exchangers , such as radiators, provide for both overall thermal exchange and cost benefits.
  • the present invention therefore, keeps the key advantage of combo-cooler technology (exchangers sharing the same pair of manifolds / brackets, as well as the same core assembling / brazing process) with the advantage of having fins or separators specifically chosen and integrated to optimize the separate exchanger parts as well as the overall function of the multi-exchanger.
  • the prevent invention relates to the heat exchangers, and, in particular, multi- exchangers or combo cooler heat exchangers, for automotive vehicles, having a bank of spaced fluid conduits or tubes linked to manifolds, the bank divided into two parts capable of having different fluids flow therethrough, and fins that differ in characteristics, such as height, pitch and/or structure, to increase heat exchanger efficiency.
  • heat exchangers such as condensers and oil coolers, may look similar. However, they differ fundamentally in their thermal properties. In particular, oil is much more viscous than refrigerant or gas.
  • the refrigerant-side thermal resistance is usually between about 25% to 35% of the total resistance of the condenser, and air-side thermal resistance is usually about between 65% to 75% of the total resistance.
  • the oil-side thermal resistance is usually between about 55% to 65%, and the air-side thermal resistance is usually between about 35% to 45%. This difference in values for coolant or refrigerant side thermal resistance versus air-side thermal resistances is significant.
  • the present invention provides an improved heat exchanger having a first end tank or manifold and a second end tank or manifold opposite the first end tank or manifold.
  • One or more first tubes are in fluid communication with the first and second end tanks or 'manifolds' and the one or more first tubes are adapted to have a first fluid flow therethrough.
  • One or more second tubes are also in fluid communication with the first and second end tanks or 'manifolds' and the one or more second tubes are adapted to have the second fluid flow therethrough.
  • the first and second tubes may be similar or identical to each other, it is preferable that they be different.
  • multi-exchanger or combo cooler heat exchangers there, preferably, is a plurality of tubes or a 'bank' of tubes divided into at least one first part wherein circulates the first fluid, such as oil in an oil cooler, and at least one second part wherein circulates the second fluid, such as a refrigerant in a condenser, and a plurality of heat exchanging fins 'integrated' or 'interposed' between adjacent tubes or conduits such that at least one first type of fin contacts a tube or tubes of the first part of the bank and at least one second type of fin contacts the tube or tubes of the second part of the bank, thereby optimizing the overall thermal exchange capacity of the multi-exchanger.
  • first fluid such as oil in an oil cooler
  • second fluid such as a refrigerant in a condenser
  • the North America market has long faced the same problem in reverse: the majority of vehicles in the market use automatic transmission technology, and the minority of vehicles use manual transmission technology.
  • the present invention finally provides a uniform solution under both such environments, particularly where multi-exchanger or combo-coolers are used, by providing for a more optimal fin, and multi-exchanger assembly arrangement, to provide higher overall heat exchanger efficiency.
  • FIG. 1 is a schematic elevational view of a combo cooler as may be found in the prior art
  • FIG. 2 is a schematic elevational view of a multi-exchanger in accordance with an aspect of the present invention
  • FIG. 3 is a schematic elevational view of a multi-exchanger in accordance with an aspect of the present invention.
  • FIG. 4 is a schematic elevational view of a multi-exchanger in accordance with an aspect of the present invention
  • FIG. 5 is a schematic elevational view of a multi-exchanger in accordance with an aspect of the present invention
  • FIG. 6 is a schematic elevational view of a multi-exchanger in accordance with an aspect of the present invention.
  • FIG. 7 is schematic view of fins employed in multi-exchangers in accordance with aspects of the present invention.
  • FIG.8 is a stylized perspective view of a multi-exchanger and assembly in accordance with an aspect of the present invention.
  • the prevent invention relates to the heat exchangers, and, in particular, multi- exchangers or combo cooler heat exchangers, for automotive vehicles, having a bank of spaced fluid conduits or tubes linked to manifolds, the bank divided into two parts capable of having, respectively, different fluids flowing therethrough and fins that differ in characteristics, such as average height, pitch and/or structure, preferably average height and pitch, to increase heat exchanger efficiency.
  • the present invention further provides for a heat exchanger assembly, and more preferably, a heat exchanger assembly comprising a multi-exchanger such as combo-cooler, with different sizes types of fins or separators, which optimizes both condenser performance, as well as oil-cooler performance.
  • a heat exchanger assembly comprising a multi-exchanger with fins of larger fin pitch for oil-cooler fins, the thermal performance of additional heat exchangers, such as, for example, single fluid heat exchanger such as radiators, back or down flow from the air stream, overall heat exchanger performance for the vehicle is improved.
  • one aspect of the present invention provides for a multi-exchanger or combo cooler heat exchanger having a first tube or tubes; a second tube or tubes; a first end tank or manifold; a second end tank or manifold opposite the first end tank or manifold; one or more first tubes in fluid communication with the first and second end tanks or 'manifolds' and adapted to have a first fluid flow therethrough; one or more second tubes in fluid communication with the first and second end tanks or 'manifolds' and adapted to have a second fluid flow theretnrougn; at least one first separator or fin interposed between adjacent first tubes; and at least one second separator or fin interposed between adjacent second tubes.
  • the first separator or fin has different characteristics from the second separator or fin, in particular, different average fin sizes or fin pitches from one another.
  • the air- side thermal resistance of the at least one first separator or fin, on a per separator or fin basis is less than the air-side thermal resistance of the at least one second separator or fin.
  • the air-wetted area of the at least one first separator or fin, on a per separator or fin basis is less than that of the at least second separator or fin. Particularly preferred is where air-side thermal resistance and air-wetted area as described above for the first separator or fin is less than the air-side thermal resistance and air-wetted area as described above for the second separator or fin.
  • an at least one third separator or fin is provided.
  • the at least one third separator or fin may be different or the same as the at least one first or second separator or fin.
  • the at least one third separator or fin contacts or touches (is 'interposed') between at least one first tube and at least one second tube, and the height of the at least one third separator or fin is greater than or equal to the height of the at least one first separator or fin.
  • the multi-exchanger or combo cooler heat exchanger has at least two different fluids flowing therethrough. More preferred embodiments have the first fluid comprising a high viscosity fluid or oil and the second fluid comprising a low viscosity fluid, refrigerant or coolant.
  • the multi-exchanger or combo cooler has hydraulic diameters of the first tubes (oil cooler) greater than the hydraulic diameter of the second tubes.
  • the at least one first separator or fin, on a per separator or fin basis has an air contact area less in area than the at least one second separator or fin, on a per separator or fin basis.
  • the height of the at least one second separator or fin is greater than the height of the at least first separator of fin, for example, in an oil-cooler.
  • the pitch of the at least one second separator or fin (for example, in a condenser) is less than the pitch of the at least one first separator or fin, for example, in an oil -cooler.
  • the height of the at least one second separator or fin is greater than that of the at least first separator of fin and the pitch of the at least one second separator or fin is less than the pitch of the at least one first separator or fin.
  • a plurality of tubes, adjacent to one another are provided, wherein the multi-exchanger or combo cooler heat exchanger comprises a first manifold and a second manifold; a plurality of adjacent tubes or a bank of tubes between the manifolds having at least one first part wherein circulates a first fluid; at least one second part of the plurality of adjacent tubes or bank of tubes between the manifolds wherein circulates a second fluid; a plurality of at least two types of heat exchanger fins interposed between adjacent tubes or conduits.
  • the least one first type of fin is interposed between at least two tubes of the first part of the bank and at least one second type of fin is interposed between at least two tubes of tne secon ⁇ pan o ⁇ tne DanK; and where within the heat exchanger the first fluid has no direct contact with the second fluid.
  • the air-side thermal resistance of the fins interposed on the first part of the bank, on a per fin basis is less than the air-side thermal resistance of the fins interposed on the second part of the bank.
  • the air-wetted area of the fins interposed on the first part of the bank, on a per fin basis is less than that of the second part of the bank, even more preferably, the air side thermal resistance of the fins is less in the first part of the bank than the second and the air-wetted area of the fins is less in the first part of the bank than the second.
  • the first part of the bank or first tubes of the multi-exchanger or combo cooler have air-wetted areas less than that of the second bank or second tubes, which allows, for example, the placement of more first tubes in the same packaging (smaller overall space requirements for the same overall performance).
  • wetted area can be defined as the fin depth (e.g. for a 16mm core heat exchanger approximately 16mm) multiplied by fin length. In such a case, the thermal resistance on the side of the first part of the bank or first tubes is high, and the additional tubes allow for an effectively increased overall heat exchange performance in that area.
  • the air-side thermal resistance of an area of exchange such as that defined by the first bank of tubes when less than the area of exchange such as that defined by the second bank of tubes, also exhibits the characteristic that, on a per fin basis, the air-wetted area (area of exchange) of the first bank of tubes will be less than that of the second bank of tubes.
  • a 'core' comprises the area of heat exchange of the multi-exchanger or combo cooler, and, at the end of the area of heat exchange, is found the manifolds or end tanks.
  • the core is defined as having 'parts' or areas of first and second tubes', wherein the depth of the core, when measured from front to back based on the normal orientation of the heat exchanger when in use, is between about 4mm to 40mm, and wherein the first separator or fin has different characteristics, such as fin height and pitch, from the second separator or fin.
  • the height of the second separator or fin is greater than that of the first separator or fin. More preferred is when the first separator or fin has a height of between about 3 to about 12 mm. Also preferred is when the second separator or fin has a height of between about 4 to about 13 mm. More preferred is when the height of the first separator or fin is between about 3 to about 12 mm. Also more preferred is when the height is the average height of the fins per a defined area. In more preferred aspects of the present invention, the absolute value of the average difference in the heights of the second separator or fin and the first separator or fin is greater than or equal to 0.5 mm.
  • the fin pitch, and, in particular, the average fin, pitch of the first separator(s)or fin(s) in the core differs from the fin pitch, and, in particular, the average fin pitch of the second separator(s) or fin(s). More preferably, the pitch of the first separator or fin is greater than that of the second separator or fin.
  • the average fin pitch of the first separator or fin is between about 1.0 to 3.0mm. In other more preferred aspects of the present invention, the average fin pitch of the second separator or fin is between about 0.5 to about 2.0 mm.
  • the absolute value of the average difference in the pitches of the second separator or fin and the first separator or fin is greater than or equal to 0.1 mm.
  • the multi-exchanger or combo cooler heat exchanger banks, manifolds and fins are formed into an assembly by brazing.
  • a heat exchanger assembly and, particularly and oil cooler and condenser part of such an assembly, the oil-cooler tube is physically positioned higher than the condenser tube, such an architecture causing higher air-side pressure drop across the oil cooler tube than the condenser tube because it blocks more of the air-passage.
  • an engine cooling system is that the performance of radiator, which is normally situated behind of back of the combo-cooler, is reduced by this higher air-side pressure drop.
  • the multi-exchanger or combo cooler of the present invention may form a heat exchanger assembly comprising a multi-exchanger or combo cooler described hereinabove and another heat exchanger. More preferably, the heat exchanger assembly comprises a multi-exchanger or combo cooler described hereinabove and a single fluid heat exchanger.
  • the heat exchanger assembly comprises a multi-exchanger and a single fluid heat exchanger positioned so that the multi-exchanger and single fluid heat exchanger provide for a thermal exchange affect between multi-exchanger and fluid heat exchanger.
  • the single fluid heat exchanger is a radiator
  • the radiator is positioned so that it is downstream or back of the multi-exchanger.
  • the single fluid heat exchanger is positioned so that it is downstream or back of the multi-exchanger, and the fluid passing through the single fluid heat exchanger flows parallel with one or both of the fluids of the multi-exchanger, either following the same flow direction (concurrent) or following the opposite flow direction of the multi-exchanger flow or flows (countercurrent) with the associated air-side pressure drop within acceptable levels.
  • a heat exchanger of the prior art is shown.
  • a multi- exchanger such as a combo-cooler, having a condenser and an oil-cooler, may have an oil cooler part and condenser part connected with the same pair of manifolds and tubes connected to one another with fins.
  • 1 comprises a core consisting of a multiplicity of tubes 12_extending parallel to each other and between which are arranged corrugated spacers 14 forming cooling fins.
  • the ends of the tubes VZ open out, at one end, into a common manifold 16a and, at the other end, into another common manifold 16b.
  • the core is divided into two parts, namely a part A forming an oil cooler and consisting of tubes 12a and a part B forming a condenser and consisting of tubes 12b.
  • the partition 15a divides the manifold 16a into a compartment 17a for the oil (here placed in the upper part) and a compartment 19a for the cooling fluid (here placed in the lower part).
  • the partition 15b divides the manifold 16b into a compartment 17b for the oil (here placed in the upper part) and a compartment 19b for the cooling fluid (here placed in the lower part).
  • a multi-exchanger 20 is shown with two types of tubes, condenser tubes 26 and/or other tubes 24
  • the condenser tubes 26 and oil-cooler tubes 24 are basically parallel in arrangement, and separated by fins 23, 25 .
  • the tubes are connected with a pair of manifolds 22 at the ends of the heat exchanger.
  • the oil-cooler fins 23 are of a lower height, than the condenser fins 25 , In addition, the oil-cooler fins 23 have a pitch Po that is greater than that of the condenser fins Pc.
  • a heat exchanger 30 is shown with two types of tubes, condenser tube 36 and tube 38
  • the condenser tubes 36 and oil-cooler tubes 38 are basically parallel in arrangement, and separated by fins 35, 39 .
  • the tubes are connected with a pair of manifolds 32 at the ends of the heat exchanger.
  • the oil-cooler fins 39 are of lower height (ho) than the condenser fins 35 (he) .
  • Figure 3 shows another aspect of the present invention.
  • the oil cooler fins are different from condenser fins in these embodiments, (i.e. different height and/or pitch), overall thermal exchange in optimized.
  • metals capable of being brazed with conventional techniques for use in automotive heat exchanger applications
  • metals such as copper or copper alloys and aluminum or aluminum alloys preferably may be used; more preferably, aluminum or aluminum alloys are used
  • the separator or fins are made of at least one metal or alloy capable of brazing, more preferably the fins are made of the same metals or alloys capable of being brazed, more preferably the condenser or lower viscosity fluid flow-through tube fins of the multi-exchanger comprise at least one aluminum or aluminum alloy, and the oil cooler or higher viscosity fluid flow-through tube fins comprise at least one aluminum or aluminum alloy.
  • the oil cooler part or area has fins with fin pitches greater than condenser fin
  • the present invention as shown in Figs 2 and 3, exemplifies that on a per-fin basis, more air-side surface to condenser fins is provided, because the air-side thermal resistance is high for the condenser and less air-side surface to oil-cooler fins is provided, due to the lower air-side thermal resistance for the oil cooler.
  • a heat exchanger has manifolds_42, weephole 48, fins 43, 45, tubes 44, 46, and inlets and outlets 4JL.
  • a fin(s) 49 is located between a condenser tube(s) 46 and an oil-cooler tube(s) 44
  • the fin may be a condenser fin or an oil cooler fin.
  • Preferred is a condenser fin.
  • a multi-exchanger 50 comprising manifolds 52, inlets and outlets_5_l, high viscosity fluid flow through tubes 54, low viscosity fluid flow through tubes 56, first fins 53, . and second fins 55, with manifolds weephole 59.
  • Baffles of a double baffle 57, 58, are provided.
  • fin(s) or separator(s) 60, 61 , 70, 71 of the type that may be used in the present invention are shown.
  • the fins shown here have, as essential features or 'characteristics', a height hiand pitch h2, more particularly, an average height and pitch, which may differ based on whether they are on the first or second bank or interposed between first and second tubes, of the multi- exchanger or condenser.
  • Fins with height h, 60 and pitch P, 70 are interposable between the first tubes.
  • the average height of the fins h2 is inferior to the average height of the fins h2 in the core.
  • a multi-exchanger assembly 91 comprising a multi cooler _80_and a single fluid exchanger (radiator) 89 is shown.
  • the multi exchanger 80 has tubes 84, 82, fins 83, 81 , manifolds 86, 87, inlets, outlets 90, and baffles 88.
  • a single fluid exchanger 89 Back, or downstream the multi-exchanger 80 is a single fluid exchanger 89, that is placed in close proximity to the multi exchanger so that a combined heat exchanger effect can take place, with inlet and outlet 90.
  • the size of the fin and its composition may differ based on the hydraulic diameter of the tubes.
  • the high viscosity fluid or oil-cooler part of the heat exchanger preferably has tubes with a hydraulic diameter greater than the hydraulic diameter ot the tubes ot the low viscosity fluid or condenser part. It is also preferred that the tubes of the heat exchangers of the present invention have a number of passageways, ports or channels therein.
  • the number of passageways or channels of the tubes of the oil-cooler part be fewer in number than the number of channels of the tubes of the condenser part.
  • the tubes of the oil-cooler part contain fewer 'partitions' than the tubes of the condenser part.
  • a mean for detecting 'leaks' or previously un-detected fluid mixture, between, for example, oil and refrigerant fluids in the manifold is provided.
  • a preferred means for detecting said 'leaks' or undesired 'mixtures' is by using a detecting hole or 'weephole' along with a baffle, or, preferably a double baffle inside the manifold to keep the different fluids separate.
  • the tubes of the bank are linked to two manifolds each of which includes a separating partition or baffle for isolating the first fluid circulating in the first part of the multi-exchanger or combo cooler, from the second fluid circulating in the second part of the multi-exchanger or combo cooler.
  • the baffle isolates the oil circulating in the oil-cooler part from the cooling fluid circulating in the condenser part.
  • manifolds comprising at least two baffles or one double baffle.
  • At least one tube of the bank is constructed so that fluid is restricted from flowing therein forming a so called “inactive tube” or “dead tube”.
  • the bank, fins and the manifolds are assembled by brazing.
  • the multi-exchanger or combo cooler heat exchanger of the present invention can be produced according to well-known technologies of brazing used for the construction, for example, of brazed heat exchangers.
  • the tubes of the bank are made with extrusion techniques or by extrusion.
  • the present invention may be used in a wide range of applications.
  • the present invention in preferred embodiments, may comprise not only oil cooler/condenser combination but may be applicable to all multi exchangers that comprise different fluids for maximum effect, for example, a condenser is an example of one type of cooler or exchanger, the radiator an another type of cooler or exchanger.
  • the air- side thermal resistance measured in percentage of each cooler or exchanger is different particularly in a combo-cooler or multi heat exchanger comprising two or more air-cooled exchanger elements, in which each exchanger has fins.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La présente invention concerne des échangeurs thermiques optimisés et en particulier des échangeurs thermiques et des ensembles comprenant des multi-échangeurs ou des refroidisseurs combinés comprenant différentes parties ou différents éléments d'échangeurs thermiques et des ailettes (43, 45, 49) ou des séparateurs de types et/ou de caractéristiques différents sur les différentes parties de tube (44, 46) des échangeurs thermiques. L’échangeur thermique en deux parties peut être traversé par différents fluides et les ailettes (43, 45, 49) ont des caractéristiques différentes, par exemple en matière de hauteur et de pas, pour augmenter l’efficacité d’ensemble de l’échangeur thermique.
PCT/US2005/016421 2004-05-21 2005-05-11 Ailettes de types multiples pour multi-echangeurs Ceased WO2006124014A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP05747445A EP1966558A1 (fr) 2004-05-21 2005-05-11 Ailettes de types multiples pour multi-echangeurs
PCT/US2005/016421 WO2006124014A1 (fr) 2004-05-21 2005-05-11 Ailettes de types multiples pour multi-echangeurs
JP2008511090A JP2008540998A (ja) 2005-05-11 2005-05-11 マルチ熱交換器のためのマルチタイプのフィン

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US10/851,392 2004-05-21
PCT/US2005/016421 WO2006124014A1 (fr) 2004-05-21 2005-05-11 Ailettes de types multiples pour multi-echangeurs

Publications (2)

Publication Number Publication Date
WO2006124014A1 true WO2006124014A1 (fr) 2006-11-23
WO2006124014A8 WO2006124014A8 (fr) 2008-09-04

Family

ID=37431515

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2005/016421 Ceased WO2006124014A1 (fr) 2004-05-21 2005-05-11 Ailettes de types multiples pour multi-echangeurs

Country Status (2)

Country Link
JP (1) JP2008540998A (fr)
WO (1) WO2006124014A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105571211A (zh) * 2016-02-11 2016-05-11 合肥长城制冷科技有限公司 一种新型超薄单孔翅片蒸发器

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101299019B1 (ko) * 2013-05-15 2013-08-23 (주)정인하이테크 냉동사이클장치
JP2015081705A (ja) * 2013-10-22 2015-04-27 株式会社デンソー 冷却システム

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2682160A1 (fr) * 1991-10-07 1993-04-09 Renault Vehicules Ind Systeme de refroidissement pour moteur a combustion interne comportant deux parties distinctes de radiateur.
DE19813069A1 (de) * 1998-03-25 1999-09-30 Behr Gmbh & Co Anordnung von Wärmeübertragern, insbesondere in einem Kraftfahrzeug
JP2001174190A (ja) * 1999-12-17 2001-06-29 Denso Corp 複式熱交換器
JP2003021432A (ja) * 2001-07-09 2003-01-24 Zexel Valeo Climate Control Corp コンデンサ
WO2003095918A2 (fr) * 2002-05-07 2003-11-20 Valeo, Inc. Echangeur thermique perfectionne
WO2003106910A1 (fr) * 2002-06-18 2003-12-24 Showa Denko K.K. Echangeur thermique de type unite
WO2004099695A1 (fr) * 2003-04-30 2004-11-18 Valeo Inc. Echangeur thermique
WO2005003669A2 (fr) * 2003-06-25 2005-01-13 Valeo Inc. Echangeur de chaleur

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2682160A1 (fr) * 1991-10-07 1993-04-09 Renault Vehicules Ind Systeme de refroidissement pour moteur a combustion interne comportant deux parties distinctes de radiateur.
DE19813069A1 (de) * 1998-03-25 1999-09-30 Behr Gmbh & Co Anordnung von Wärmeübertragern, insbesondere in einem Kraftfahrzeug
JP2001174190A (ja) * 1999-12-17 2001-06-29 Denso Corp 複式熱交換器
JP2003021432A (ja) * 2001-07-09 2003-01-24 Zexel Valeo Climate Control Corp コンデンサ
WO2003095918A2 (fr) * 2002-05-07 2003-11-20 Valeo, Inc. Echangeur thermique perfectionne
WO2003106910A1 (fr) * 2002-06-18 2003-12-24 Showa Denko K.K. Echangeur thermique de type unite
WO2004099695A1 (fr) * 2003-04-30 2004-11-18 Valeo Inc. Echangeur thermique
WO2005003669A2 (fr) * 2003-06-25 2005-01-13 Valeo Inc. Echangeur de chaleur

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 23 10 February 2001 (2001-02-10) *
PATENT ABSTRACTS OF JAPAN vol. 2003, no. 05 12 May 2003 (2003-05-12) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105571211A (zh) * 2016-02-11 2016-05-11 合肥长城制冷科技有限公司 一种新型超薄单孔翅片蒸发器

Also Published As

Publication number Publication date
JP2008540998A (ja) 2008-11-20
WO2006124014A8 (fr) 2008-09-04

Similar Documents

Publication Publication Date Title
US7506683B2 (en) Multi-type fins for multi-exchangers
US6904963B2 (en) Heat exchanger
US20060113068A1 (en) Multi fluid heat exchanger assembly
US7337832B2 (en) Heat exchanger
US5743328A (en) Duplex heat exchanger
US5036909A (en) Multiple serpentine tube heat exchanger
US4712612A (en) Horizontal stack type evaporator
US6213196B1 (en) Double heat exchanger for vehicle air conditioner
RU2470245C2 (ru) Теплообменник с теплообменными камерами, в которых используются соответствующие элементы для направления среды
EP1167910B1 (fr) Condenseur
US20030116308A1 (en) Heat exchanger
US20050061488A1 (en) Automotive heat exchanger
JPH0384395A (ja) 複式熱交換器
WO1991019949A1 (fr) Echangeur thermique circulaire a tubes et ailettes
EP1195567B1 (fr) Echangeur de chaleur comportant plusieurs portions d'échange de chaleur
JPS61202084A (ja) 熱交換器
WO2007129851A1 (fr) Échangeur de chaleur pour automobile et procédé de fabrication de celui-ci
US20050217839A1 (en) Integral primary and secondary heat exchanger
JP4625687B2 (ja) 熱交換器
US6672376B2 (en) Twisted-louver high performance heat exchanger fin
JP2004037073A (ja) 積層型熱交換器
US7036571B2 (en) Compound type heat exchanger
JP3627295B2 (ja) 熱交換器
WO2006124014A1 (fr) Ailettes de types multiples pour multi-echangeurs
US20070056718A1 (en) Heat exchanger and duplex type heat exchanger

Legal Events

Date Code Title Description
ENP Entry into the national phase

Ref document number: 2008511090

Country of ref document: JP

Kind code of ref document: A

121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 2005747445

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: DE

NENP Non-entry into the national phase

Ref country code: RU