US20090277611A1 - Air-cooled radiator assembly for oil-filled electrical quipment - Google Patents

Air-cooled radiator assembly for oil-filled electrical quipment Download PDF

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US20090277611A1
US20090277611A1 US12/386,561 US38656109A US2009277611A1 US 20090277611 A1 US20090277611 A1 US 20090277611A1 US 38656109 A US38656109 A US 38656109A US 2009277611 A1 US2009277611 A1 US 2009277611A1
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Prior art keywords
plate
radiator
duct
ducts
inches
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Abandoned
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US12/386,561
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English (en)
Inventor
Vasanth Vailoor
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TRANTECH RADIATOR PRODUCTS Inc
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Individual
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Priority to US12/386,561 priority Critical patent/US20090277611A1/en
Priority to PCT/US2009/002477 priority patent/WO2009131668A2/fr
Assigned to TRANTECH RADIATOR PRODUCTS, INC. reassignment TRANTECH RADIATOR PRODUCTS, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: VAILOOR, VASANTH
Publication of US20090277611A1 publication Critical patent/US20090277611A1/en
Assigned to FIDUS INVESTMENT CORPORATION reassignment FIDUS INVESTMENT CORPORATION SECURITY AGREEMENT Assignors: TRANTECH RADIATOR PRODUCTS, INC.
Assigned to ASSOCIATED BANK, NATIONAL ASSOCIATION, AS AGENT reassignment ASSOCIATED BANK, NATIONAL ASSOCIATION, AS AGENT SECURITY AGREEMENT Assignors: TRANTECH RADIATOR PRODUCTS, INC.
Assigned to MAIN STREET CAPITAL CORPORATION reassignment MAIN STREET CAPITAL CORPORATION SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TRANTECH RADIATOR ACQUIRECO LLC, TRANTECH RADIATOR HOLDINGS, INC., TRANTECII RADIATOR PRODUCTS, INC.
Abandoned legal-status Critical Current

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    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • 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
    • F28D1/053—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 the conduits being straight
    • F28D1/0535—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 the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05358—Assemblies of conduits connected side by side or with individual headers, e.g. section type radiators
    • 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
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations

Definitions

  • This invention is directed towards heat exchangers and, more specifically, radiator assemblies for use with fluid sealed electrical apparatuses.
  • Radiator assemblies for oil-filled electrical apparatuses have been widely used and are available in a number of different shapes and cooling configurations. Radiator assemblies are frequently needed for electrical equipment which use oil to transfer heat from electrical equipment. The oil is directed to an oil-filled radiator which is cooled by the passage of ambient air over the radiator surface.
  • radiators provide a recirculation loop to cool oil which is in contact with the electrical equipment. As the oil is heated by the electrical equipment, it expands due to the increase in temperature. The volume of oil likewise increases along with a reduction in the oil density. The hot, low-density oil will rise to the top of the electrical equipment and flows through a connecting passage into an upper region of a radiator. The hot oil transfers heat to the radiator which is subsequently transferred into the surrounding ambient air. As the oil cools, the oil flows by gravity to the bottom of the radiator undergoing additional cooling as the oil passes through the radiator. The oil is then directed back into the electrical apparatus.
  • radiator cooling products may expend resources acquiring a radiator that has excessive cooling capacity and in so doing expend more money than is required to bring about efficient cooling.
  • a radiator product may be acquired which under performs with respect to the electrical transformer.
  • auxiliary fans or oil pumps are utilized to increase air flow or oil flow across or through the radiator at considerable expense that could have been avoided by proper matching of the radiator to the cooling needs.
  • FIG. 1 is a perspective view of a radiator section attached to portions of an inlet and outlet header in accordance with one exemplary embodiment.
  • FIG. 2 is a cross-sectional view taken along line 2 - 2 of FIG. 1 .
  • FIG. 3 is a perspective view of a pair of radiator sections attached to portions of an inlet and outlet header in accordance with a prior design.
  • FIG. 4 is a cross-sectional view taken along line 4 - 4 of FIG. 3 .
  • ranges mentioned herein include all ranges located within the prescribed range. As such, all ranges mentioned herein include all sub-ranges included in the mentioned ranges. For instance, a range from 100-200 also includes ranges from 110-150, 170-190, and 153-162. Further, all limits mentioned herein include all other limits included in the mentioned limits. For instance, a limit of up to 7 also includes a limit of up to 5, up to 3, and up to 4.5.
  • radiators are known to be used for the cooling of transformer oil. Such radiators include the radiator assembly seen in U.S. Pat. No. 4,019,572 assigned to Westinghouse Electric Corporation and U.S. Pat. No. 3,153,447 assigned to Tranter Manufacturing, Inc., and which are incorporated herein by reference.
  • Q is the heat dissipated
  • U is the heat transfer co-efficient
  • A is the heat transfer surface area
  • ⁇ T is the effective temperature difference between the oil and the air.
  • the present design may be directed to improvements to a natural convection radiator which can bring about an improvement (increase) of the heat transfer co-efficient for the entire radiator performance.
  • a radiator section 10 of a passive radiator is provided for use with an electrical transformer oil bath.
  • the width 110 of a plate 20 of 21.25 inches is held constant as is the effective length 112 of 19.75 inches.
  • changing the width 110 of the plate 20 or changing the length 112 of the plate 20 can bring about changes in the heat transfer efficiency.
  • changes to the width 110 of the plate 20 can bring about improvements with respect to ambient air flow relative to the plate 20 but such changes are quickly diluted by diminishing returns in terms of efficiency versus increased commercial cost of materials.
  • increasing the length 112 or height of a radiator increases the contact interval between the oil and the ambient air and increases the residence time of the oil within the radiator.
  • changes to this particular geometry of the radiator can easily create changes in which the cost of bringing about the change far exceeds the incremental increase in overall thermal efficiency.
  • radiator dimensions are often set within a very narrow range.
  • radiator designs typically will use the largest length 112 available given the limitations of the electrical equipment design.
  • significant improvements in the amount of heat that can be dissipated can be achieved by altering features of the radiation design.
  • the design modification allows for increased efficiency of the radiator in a same sized space while using less material which contributes to manufacturing efficiency.
  • the inlet header 12 size and outlet header 14 sizes it has been found beneficial to increase the inlet header 12 size and outlet header 14 sizes to a diameter of 5 inches.
  • the diameter 16 of the inlet header 12 is 5 inches
  • the diameter 18 of the outlet header 14 is likewise 5 inches although the diameters 16 and 18 may be different in other exemplary embodiments.
  • the 5 inch header size allows for a reduced pressure drop for the resulting oil bath fluid flow.
  • the radiator having increased head size will have an improved heat transfer co-efficient as a result of the higher oil flow velocity.
  • couplings or connections from the oil bath may be similarly sized so as not to create an undesired diminishment of flow to or from the headers 12 and 14 .
  • the diameters 16 and 18 need not be identical in other exemplary embodiments but may be different from one another. Further, the diameters 16 and 18 need not be only five inches but can be variously sized in other arrangements. For example, the diameters 16 and 18 may each be from 3.5 to 5 inches, from 4 to 6 inches, or from 4.5 to 5.5 inches in accordance with various exemplary embodiments.
  • FIG. 2 illustrates a cross-sectional view of the plate 20 at a location located half-way between the center axes of the inlet header 12 and the outlet header 14 .
  • the plate 20 is formed by a first panel 26 and a second panel 28 that are attached to one another through welding. However, it is to be understood that the panels 26 and 28 may be attached to one another by use of various means in other embodiments. Further, the plate 20 need not include a pair of panels 26 and 28 but may include only one panel in other arrangements.
  • the first panel 26 may be the portion of the plate 20 above the lateral centerline 30
  • the second panel 28 may be the portion of the plate 20 below lateral centerline 30
  • the first panel 26 and second panel 28 define a plurality of ducts 32 , 34 , 36 , 38 , 40 , and 42 through which oil may flow.
  • the first duct 32 and the sixth duct 42 that are located on opposite ends of the plate 20 with respect to the longitudinal centerline 102 may be symmetrical to one another with respect to centerline 102 .
  • the first panel 26 defines a first duct first ridge 56 that has is convex and has a radius of 0.1377 inches.
  • the first panel 26 also defines a first duct second ridge 58 that is likewise convex and has a radius of 0.1377 inches.
  • a first duct first furrow 64 is located between the ridges 56 and 58 and is concave in shape with a radius of 0.0937 inches.
  • the second panel 28 defines a first duct third ridge 60 that is convex in shape and is located opposite from the first duct first ridge 56 with respect to the lateral centerline 30 of the plate 20 .
  • the first duct third ridge 60 may have a radius of 0.1378 inches. However, in another exemplary embodiment the first duct third ridge 60 has a radius that is 0.1377 inches.
  • the second panel 28 additionally defines a first duct third ridge 62 that is located opposite from the first duct second ridge 58 and is convex in shape.
  • the first duct third ridge 62 may have a radius of 0.1377 inches in accordance with one embodiment.
  • a first duct second furrow 66 is disposed between the ridges 60 and 62 and is concave in shape with a radius of 0.0937 inches.
  • the first duct second furrow 66 is located opposite from the first duct first furrow 64 with respect to the lateral centerline 30 .
  • the first duct 64 may have a first duct width 68 of 2.25 inches.
  • the sixth duct 42 can be arranged in a manner identical to the first duct 32 .
  • the sixth duct 42 is symmetrical with respect to the first duct 32 about the longitudinal centerline 102 .
  • the ridge of the sixth duct 42 formed by the first panel 26 that is farthest from the inlet header 12 along the lateral centerline 30 may be arranged in a manner identical to the first duct first ridge 56 .
  • the ridge of the sixth duct 42 formed by the first panel 26 closest to the inlet header 12 along the direction of the lateral centerline 30 can be arranged in a manner similar to the first duct second ridge 58 as previously discussed.
  • the furrow formed by the first panel 26 may be made in an identical manner to the first duct first furrow 64 as previously discussed. Additionally, the features of the sixth duct 42 formed by the second panel 28 may be identical and symmetrical to the features of the first duct 32 formed by the second panel 28 .
  • the plate 20 also features a second duct 34 defined by the first panel 26 and the second panel 28 .
  • the first panel 26 defines a second duct first ridge 70 that is convex with a radius of 0.2003 inches.
  • a second duct second ridge 72 is also defined by the first panel 26 and may be convex with a radius of 0.1378 inches.
  • a second duct first furrow 86 is defined between the ridges 70 and 72 and is concave in shape and may have a radius of 0.0938 inches.
  • Third and fourth second duct ridges 74 and 76 are likewise defined by the first panel 26 and are convex in shape.
  • the ridge 74 may have a radius of 0.1377 inches in one embodiment, and ridge 76 may have a radius of 0.2002 inches in one embodiment.
  • the first panel 28 defines a second duct second furrow 88 located between the ridges 72 and 74 , and the first panel 28 defines a second duct third furrow 90 that is located between the ridges 74 and 76 .
  • the furrows 88 and 90 may be concave in shape and can each have a radius of 0.0938 inches in accordance with one embodiment.
  • the second panel 28 defines additional portions of the second duct 34 such as a second duct fifth ridge 78 that is convex in shape and is located opposite from ridge 70 with respect to the lateral centerline 30 .
  • Ridge 78 may have a radius of 0.2003 inches in certain embodiments.
  • a second duct sixth ridge 80 is present and is convex in shape and located opposite to the ridge 72 with respect to the lateral centerline 30 .
  • Ridge 80 may have a radius of 0.1378 inches in accordance with certain embodiments.
  • a second duct fourth furrow 92 is located between the ridges 78 and 80 and is located opposite from the furrow 86 with respect to the lateral centerline 30 .
  • the furrow 92 may have a radius of 0.0938 and can be concave in shape in accordance with certain exemplary embodiments.
  • a second duct seventh ridge 82 and a second duct eighth ridge 84 may likewise be defined on the second panel 28 and can be located opposite from the ridge 74 and ridge 76 respectively.
  • the ridges 82 and 84 may have a radius of 0.1377 inches and a radius of 0.2002 inches respectively and may both be convex in shape.
  • a second duct fifth furrow 94 and a second duct sixth furrow 96 can be included and may be concave in shape with a radius of 0.0938 inches.
  • the second duct fifth furrow 94 is located opposite from the furrow 88 with respect to the lateral centerline 30
  • furrow 96 is located opposite from the furrow 90 with respect to the lateral centerline 30 .
  • the second duct 34 may have a width 98 of 3.19 inches in accordance with certain exemplary embodiments.
  • the second duct 34 thus features eight ridges 70 , 72 , 74 , 76 , 78 , 80 , 82 , and 84 that are convex in shape and six furrows 86 , 88 , 90 , 92 , 94 , and 96 that are concave in shape.
  • the ridges 70 , 72 , 74 , 76 , 78 , 80 , 82 , and 84 may be symmetrical about the lateral centerline 30 in certain embodiments.
  • furrows 86 , 88 , 90 , 92 , 94 , and 96 may be symmetrical to the opposite furrow 86 , 88 , 90 , 92 , 94 , or 96 about the lateral centerline 30 in various embodiments.
  • the fifth duct 40 is provided with four convex ridges on the first panel 26 and four convex ridges oppositely disposed on the second panel 28 . Concave furrows are also present on the first panel 26 that are located opposite from concave furrows on the second panel 28 .
  • the fifth duct 40 may be identically arranged with respect to the second duct 34 and symmetrical thereto with respect to the longitudinal centerline 102 . However, it is to be understood that other embodiments may exist in which the second and fifth ducts 34 and 40 are not symmetrical about longitudinal centerline 102 .
  • the third and fourth ducts 36 and 38 are located the closest to the longitudinal centerline 102 in the distance along the lateral centerline 30 than any of the other ducts.
  • the third and fourth ducts 36 and 38 may each have eight ridges and six furrows that are located opposite to one another about the lateral centerline 30 as discussed above concerning the second duct 34 .
  • the third and fourth ducts 36 and 38 may be symmetrical with respect to one another about the longitudinal centerline 102 .
  • the ridges and furrows of the third and fourth ducts 36 and 38 may have radii that are different from or the same as the radii of the ridges and furrows of the second duct 34 and/or the fifth duct 40 .
  • the third duct 36 may be constructed in a manner identically to that of the second duct 34
  • the fourth duct 38 may be constructed in a manner identical to the fifth duct 40
  • the second duct 34 and third duct 36 may be symmetrical to the fourth and fifth ducts 38 and 40 about the longitudinal centerline 102
  • the first duct 56 and the sixth duct 42 may be symmetrical about the longitudinal centerline 102 so that all of the ducts of the plate 20 are symmetrical to another one of the ducts about the longitudinal centerline 102 .
  • the ducts can be variously arranged in other exemplary embodiments so that all or none of the ducts of the plate 20 are symmetrical about the longitudinal centerline 102 . Further, it is to be understood that each individual duct 32 , 34 , 36 , 38 , 40 , and 42 may or may not be symmetrical about the lateral centerline 30 in accordance with various exemplary embodiments.
  • the height of the apexes of the various ridges to the lateral centerline 30 can be different or the same with respect to all of the ridges of the ducts 32 , 34 , 36 , 38 , 40 and 42 .
  • the height 100 of the ridge of the fourth duct 38 farthest from the longitudinal centerline 102 may be 0.23 inches as measured from the apex of the ridge to the lateral centerline 30 .
  • Any other one or ones of the ridges of ducts 32 , 34 , 36 , 38 , 40 and 42 may have a similar height 100 .
  • all of the furrows of the ducts 32 , 34 , 36 , 38 , 40 and 42 may have the same near point to the lateral center line 30 or may have varying near points to the lateral center line 30 in accordance with various exemplary embodiments.
  • the plate 20 includes a first section 44 that is located between the first duct 32 and the second duct 34 .
  • the first section 44 features engagement between the first panel 26 and the second panel 28 so that oil will not flow through the first section 44 .
  • a second section 46 , third section 48 , fourth section 50 , and fifth section 52 are provided between the ducts 34 , 36 , 38 , 40 , and 42 .
  • the various sections 46 , 48 , 50 and 52 are arranged so that the first panel 26 engages the second panel 28 to prevent oil from flowing therethrough.
  • the third section 54 is located at the longitudinal centerline 102 of the plate 20 and has a width 54 of 0.5 inches in accordance with one exemplary embodiment.
  • the various sections 44 , 46 , 48 , 50 and 52 may all have the same width or may have different widths from one another in accordance with different exemplary embodiments.
  • FIGS. 3 and 4 illustrate a radiator section 10 of a known design in which the diameters 16 and 18 are 3.5 inches.
  • Five ducts 32 , 34 , 36 , 38 , 40 , and 42 are present in which the first duct 32 and the sixth duct 42 each have a design with 6 ridges and 4 furrows.
  • Ducts 34 , 36 , 38 , and 40 each have 10 ridges and 8 furrows.
  • the radiator section 10 has a second plate 104 with a plate spacing 106 between the plate 20 and the second plate 104 .
  • the plate spacing 106 may be the distance between the lateral centerline 30 of plate 20 and the lateral centerline 108 of the second plate 104 . In the embodiment shown, the plate spacing 106 is 1.77 inches.
  • the radiator section 10 of the exemplary embodiment of FIGS. 1 and 2 may have a plurality of additional plates as is known in the art.
  • the plate 20 may have a plate spacing 106 of 2.25 inches so that the distance from the lateral centerline 30 of plate 20 to the lateral centerline of an adjacent plate is 2.25 inches.
  • Each one of the plates of the plurality of plates may have a plate spacing of 2.25 inches in accordance with one exemplary embodiment of the radiator.
  • the increase in plate spacing in the embodiment of FIGS. 1 and 2 provides for a better air flow between the plates and reduces interference between the inherent boundary layers that occur adjacent to the plates.
  • the plate spacing may be from 2 to 3 inches, from 2.1 to 2.8 inches, from 2.2 to 2.75 inches, or from 2.25 to 2.5 inches in accordance with various exemplary embodiments.
  • the plate spacing in the embodiment in FIGS. 1 and 2 is increased, it is also desirable to increase the heat transfer area by providing an enhanced ripple pattern to the plates 20 .
  • the enhanced ripple pattern was previously shown and described with respect to the ridges and furrows and other features of the ducts 32 , 34 , 36 , 38 , 40 , and 42 .
  • fewer plates 20 may be used within the same footprint of a previous radiator to bring about comparable performance even though fewer plates 20 are utilized.
  • the ripple pattern defines a ripple having a longer length in which the defining angles are sharper. The combination of length and angles provides an increase to the hydraulic diameter of the plate 20 which offers less resistance to oil flow. As the oil flow increases, the amount of heat transferred to the ambient air increases, enhancing the overall heat dissipation by the system.
  • the inlet and outlet headers 12 and 14 have a hydraulic diameter (Dh) of 5 inches in the exemplary embodiment of FIGS. 1 and 2 due to the fact that the diameters 16 and 18 may be 5 inches. This Dh is contrasted to a Dh of 3.5 inches of the inlet header 12 and the outlet header 14 of the embodiment in FIGS. 3 and 4 in which the diameters 16 and 18 are each 3.5 inches.
  • Increasing the diameters 16 and 18 causes the hydraulic diameter on the inlet and exit side to be increased to result in a reduction of the fluid friction factor and thus an increase in oil flow.
  • the actual values of area and perimeter are used to calculate the Dh as 0.529 inches in the FIGS. 1 and 2 embodiment as contrasted to a Dh of 0.457 inches in the FIGS. 3 and 4 embodiment.
  • the modifications to the plate 20 may result in a 15.9% increase in the hydraulic diameter over the previous design illustrated in FIGS. 3 and 4 .
  • the hydraulic diameter is increased while the perimeter is reduced in addition to a reduction in the fluid flow friction factor of the oil.
  • the ripple pattern disclosed in the exemplary embodiment of FIGS. 1 and 2 causes an increased hydraulic diameter to be associated with this portion of the radiator section 10 . By increasing the hydraulic diameter, the fluid flow friction is reduced to result in an increased oil flow rate.
  • the heat transfer coefficient (U) previously mentioned is calculated to be 10.1 W/° C./ft 2 in the radiator of FIGS. 3 and 4 , and the heat transfer coefficient U is calculated to be 12.4 W/° C./ft 2 in the embodiment of FIGS. 1 and 2 .
  • the increase of the diameters 16 and 18 may allow a larger slot or opening to be present between the headers 12 and 18 and the inlet neck 22 and outlet neck 24 .
  • the inlet neck 22 and outlet neck 24 may thus be larger in the embodiment in FIGS. 1 and 2 as compared to the embodiment of FIGS. 3 and 4 .
  • Increasing the cross-section of the necks 22 and 24 allows for an increase in oil flow that can improve the heat dissipation capacity of the radiator.
  • Table 1 illustrates a test that compared a regular radiator built in a manner similar to the FIGS. 3 and 4 embodiment to a prototype radiator build along the lines discussed with reference to the FIGS. 1 and 2 embodiment. The testing was conducted in a lab.
  • the test was conducted between a regular radiator and an enhanced prototype and results thereof are illustrated below in Table 2.
  • the regular radiator was a radiator bank with one radiator having 18 plates 20 and 4 radiators having 23 plates 20 each
  • the enhanced prototype radiator was a radiator bank having 1 radiator with 15 plates 20 and 4 radiators with 18 plates 20 each.
  • the heat transfer area was reduced about 21% in the enhanced prototype radiator, and the heat transfer coefficient was improved about 22%.
  • the difference between the top radiator oil temperature and the bottom radiator oil temperature showed an increase in oil flow of about 22%.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US12/386,561 2008-04-21 2009-04-20 Air-cooled radiator assembly for oil-filled electrical quipment Abandoned US20090277611A1 (en)

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US12/386,561 US20090277611A1 (en) 2008-04-21 2009-04-20 Air-cooled radiator assembly for oil-filled electrical quipment
PCT/US2009/002477 WO2009131668A2 (fr) 2008-04-21 2009-04-21 Ensemble radiateur refroidi à l’air pour un équipement électrique rempli d’huile

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US12498908P 2008-04-21 2008-04-21
US12/386,561 US20090277611A1 (en) 2008-04-21 2009-04-20 Air-cooled radiator assembly for oil-filled electrical quipment

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US20200166293A1 (en) * 2018-11-27 2020-05-28 Hamilton Sundstrand Corporation Weaved cross-flow heat exchanger and method of forming a heat exchanger
CN112768195A (zh) * 2020-12-24 2021-05-07 江苏腾奇电力设备科技有限公司 油道不等分的散热片以及片式散热器

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