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
  • 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
• • 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
  • F28D1/0316—Assemblies of conduits in parallel
• • 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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F1/00—Tubular elements; Assemblies of tubular elements
  • F28F1/02—Tubular elements of cross-section which is non-circular
  • F28F2001/027—Tubular elements of cross-section which is non-circular with dimples
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10S165/00—Heat exchange
  • Y10S165/454—Heat exchange having side-by-side conduits structure or conduit section
  • Y10S165/464—Conduits formed by joined pairs of matched plates
  • Y10S165/467—Conduits formed by joined pairs of matched plates with turbulence enhancing pattern embossed on joined plates
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T29/00—Metal working
  • Y10T29/49—Method of mechanical manufacture
  • Y10T29/4935—Heat exchanger or boiler making
  • Y10T29/49359—Cooling apparatus making, e.g., air conditioner, refrigerator
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T29/00—Metal working
  • Y10T29/49—Method of mechanical manufacture
  • Y10T29/49396—Condenser, evaporator or vaporizer making

Definitions

• the invention relates to a condenser for a motor vehicle and a method for producing it, this condenser having a particular application in uses where resistance to high internal pressures of a fluid is necessary.
• the heat exchangers still used such as condensers for motor vehicle air conditioning systems usually comprise a tube configured in the form of a continuous coil inside which fluids can flow in gaseous and / or liquid forms.
• a cooling means such as ambient air, passes over the tubes and fins allowing the heat exchange of the very hot fluid in the tube towards the cooling means.
• the continuous tubes are made from U-shaped elements to allow insertion through the fins and, after assembly, the elements are connected to each other by U-shaped brackets of so as to constitute a tube in the form of a continuous serpentine.
• the condensers comprise manifold boxes spaced apart and parallel to each other, said boxes being connected to each other by a multiplicity of parallel heat exchange tubes so as to allow the circulation of the ._
• the multiplicity of tubes are circular or rectangular in configuration and have fins of flat or corrugated shapes disposed through or between the tubes so as to increase the heat exchange efficiency of the heat exchange tubes.
• the device is formed, in known manner, by inserting the multiplicity of tubes into holes provided on the manifolds, placing corrugated fins between the tubes and welding or brazing the tubes to the manifolds and the fins to the tubes.
• the refrigerant gas flows through the heat exchange tubes and is cooled or substantially condensed into a liquid by the flow of cooling air sweeping the tubes.
• the direction of the cooling stream and the cooling air flow are generally perpendicular to each other.
• the longitudinal dimension of one of the edges of the tube perpendicular to the air flow is the leading edge in contact with the air flow and the width of this leading edge is generally considered to be the transverse dimension of the tube d 'heat exchanger.
• the transverse dimension of a tube is thus the average width of the tube.
• a round tube has a transverse dimension equal to its diameter and a rectangular tube has a transverse dimension equal to the width of its leading edge.
• cylindrical shaped heat exchange tubes can decrease the efficiencies required in many modern automotive applications.
• the width of the leading edge represents an obstruction to the air flows and it is generally desired to minimize this obstruction.
• the smallest round tubes used commercially have a diameter greater than 5.08mm (0.2 inches) creating a barrier causing the formation of transverse dimension of less than 5.08mm (0.2 inches).
• substantially rectangular heat exchange tubes In order to reduce the width of the leading edge, for example by reducing the transverse dimension, substantially rectangular heat exchange tubes have been proposed and have found a degree of acceptance in the industry thanks to the different rectangular configurations. variables.
• US-A-4 615 385 although particularly relating to a manifold construction, describes a heat exchange tube of rectangular shape with a plurality of tubes connected in parallel between the manifolds.
• the tube is described as being flat such that the smallest dimension of the rectangle includes a circular surface which is arranged in the device including the transverse dimension.
• US-A-4,688,311 describes a method for manufacturing a heat exchange tube of rectangular shape which can be effective in resisting the high internal pressures of the fluid of an automobile air conditioning system.
• a rectangular tube comprising the circular configuration of the transverse dimension of US-A-615 385 is internally connected with an insert in the form of a corrugated fin which is fixed with the interior of the tube along its longitudinal dimension.
• the internal fins serve as tension spacers to aid resistance to internal fluid pressures.
• Such tubes require the use of additive materials during their development and it is not easy to manufacture them because of the difficulties of inserting the fins inside the tube.
• One of the objects of the invention is to provide heat exchange structures having effective resistances to air flows in their transverse dimensions.
• Another object of the invention is to provide heat exchange structures having resistances to the internal pressures of the fluids.
• Another object of the invention is to provide an automotive condenser having resistance to the internal pressures of the fluids.
• the invention relates to a condenser for a motor vehicle comprising elongated generally rectangular and hollow heat exchange structures extending between manifolds.
• the hollow structures include opposite elongated plates connected along their longitudinal edges to define a passage extending in the longitudinal direction of the plate, said opposite plates being corrugated in a transverse structure so as to define generally parallel bumps and depressions and arranged obliquely to the longitudinal direction.
• the hollows of a first plate are arranged to cross the hollows of a second plate in such a way that the maximum distance between the crossing points of the intersecting hollows is not greater than 5.08mm (0.2 inches).
• the intersecting recesses are contiguous and the opposing bumps define intersecting passages, arranged obliquely, and extending longitudinally through the heat exchange structure.
• the automobile condensers according to the invention are manufactured by a method according to which the elongated plates corrugated in a cross section so as to have a plurality of bumps angularly arranged obliquely and extending longitudinally, said bumps being separated by hollows, being arranged in such a way that the apexes of the hollows of a first plate cross the apexes of the hollows of a second plate at a maximum distance between the crossing points which does not exceed 5.08mm (0.2 inches).
• Figure 1 is a perspective view of the automobile condenser obtained according to the present invention.
• Figure 2 is an enlarged partial sectional view along approximately line 2-2 of Figure 1.
• Figure 3 is a plan view of the heat exchange structure obtained according to the present invention.
• Figure 4 is an enlarged sectional view along line 4-4 of Figure 3.
• Igure 5 is a view similar to FIG. 4 but showing the parts in assembly condition, this view being taken on line 5-5 of FIG. 3.
• FIG. 1 An embodiment of an automobile condenser according to the invention is illustrated in FIG. 1. It is however understandable that the present invention can be used in a plurality of other condensers in which a heat exchange structure is provided between manifolds.
• a condenser for an automobile is illustrated and includes an intake manifold 11 and, disposed generally parallel thereto, being opposite, an exhaust manifold 12.
• the intake manifold 11 includes an intake 13 and the evacuation manifold 12 includes an outlet 14.
• a first hot fluid in gaseous form such as a refrigerant enters the intake manifold 11 through the intake 13 flows along the longitudinally extending passages of the plurality hollow heat exchange structures and inside the outlet manifold 12.
• the flow of gaseous fluid, along the exchange structures is directed by the hollows and bumps, arranged angularly, opposite elongated plates , in a discontinuous and undulating circuit in which the flow of fluid is passively separated and mixed by the circuits crossing intersecting hollows by increasing the contact of the flow of fluid with the elongated plates.
• the heat of the fluid is dissipated towards the opposite plates of the heat exchange structures and towards the corrugated fins in contact with them.
• a second flow of fluid such as ambient air, flows through the condenser in such a way that the second fluid flows along the cross section of the heat exchange structures and along the corrugated fins.
• the heat is dissipated from such structures and fins towards the second fluid sweeping them, when the heat of the second fluid is less important than the heat of the heat exchange structure and / or of the corrugated fins.
• the first gaseous fluid condenses into a liquid which flows along the remaining length of the heat exchange structures to the outlet manifold 12 and via outlet 14 for processing in other parts of the system.
• FIG 2 illustrates a sectional view of the condenser of Figure 1, in which the inlet and outlet manifolds 11 and 12 are provided with a plurality of elongated holes 18 substantially parallel and separate , configured to receive the open ends of the plurality of elongated hollow heat exchange structures and allow circulation of gaseous and / or liquid material therebetween.
• the exchange structures are sealed with the manifolds by suitable connecting means which provide sufficient structural integrity so as to withstand the pressures generated inside the system when the condenser is used.
• the solder joint 17 is illustrated as a preferred embodiment when the building materials are aluminum.
• the heat sink fins can preferably be connected to the heat exchange structures with a conductive material thermal, or can be linked to structures depending on the expected services of the system.
• planar fins can generally be provided with elongated rods generally shaped in relation to the cross section of the heat exchange structures and can be inserted around these structures.
• the corrugated dissipative fins or the flat fins comprise at least the same width as the heat exchange structures, said fins being in contact with the exchange structures as much as possible along the width of said exchange structures.
• the heat sink fins are fine and made from high level thermal conductive material.
• the fins 16 of the condenser 10 comprise a thin conductive material of approximately the same width as the heat exchange structures 15 and are intimately linked between the plurality of exchange structures to maintain their structural integrity in the condenser.
• Figures 3, 4 and 5 illustrate a preferred embodiment of the heat exchange structures according to the invention in which the bumps generally form rectangular passages in the central section of the body of the structure and passages having a generally circular surface are formed with contiguous longitudinal edges.
• a heat exchange structure 15 comprises an elongated corrugated upper plate 19 and an elongated corrugated lower plate 20 contiguous to the intersecting recesses 21 to form generally rectangular passages 22.
• the undulations in the plate 19 are oblique with respect to the undulations of the plate 20.
• passages 26 By joining the opposing plates by covering its outer longitudinal edge 24 with the inner longitudinal edge 25, there are formed passages 26 having a substantially circular surface.
• the edges 24 and 25 can be carried together and be united in a common plane parallel to the main plane of the plates and can even comprise an elongated flat surface.
• the longitudinal edges are brazed at the interface 28 and the intersecting recesses 21 are brazed at the intersecting point 19 to ensure the structural integrity of the hollow passages of the heat exchange structures.
• the hollows and bumps of the elongated plates can be suitably formed by stamping, embossing or the like by forming the hollows of desired shape in the elongated plates.
• the surface between the recesses includes adjacent bumps.
• bumps can be stamped or otherwise formed in the plates in order to be erected above. above the plate plane.
• the bumps and the hollows will present an oblique angle to the longitudinal direction of the elongated plate.
• the oblique angle will be of the order of 10 to 85 ° considering the longitudinal direction of the plate and preferably of the order of 20 to 70A
• the first and second opposite elongated plates, having recesses angularly arranged, are assembled in such a way that the recesses of the first plate cross the opposite recesses of the second plate. It is not essential for the hollows or bumps of the first plate to be in the same oblique angle in the longitudinal direction as those of the second plate, although this is generally preferred.
• angles of the intersection of the hollows which is an angle formed by the hollows crossing and opening in the longitudinal direction of the assembled plates, can generally be of the order of 20 to 170A
• An angle will approach 0 ° when the oblique angle of the hollows of the opposed elongate plates will approach the longitudinal direction and will approach 180 ° when the oblique angles will approach a perpendicular to the longitudinal direction.
• the hollows in the opposite plates are preferably formed with a small radius of apex inside their apices.
• the inner apex radius is preferably no greater than 1.5 times the thickness of the material from which the plate is made and most preferably less than the thickness of the material.
• the width of a hump includes the dimension of the plate between the vertices of adjacent hollows and of such dimension is variable depending on the internal pressure considered inside the exchange structure and the extent of the junction of the hollow intersecting opposite plates.
• the width of the bumps on a plate with a The defined number of contiguous intersecting depressions in an internal high pressure system will typically be smaller than that in an internal low pressure system.
• the width of the bumps is preferably greater than two and a half times the thickness of the material from which the plate is produced and less than seven times this thickness.
• the thickness of the material of the opposite plates is from 0.30 mm to 0.76 mm (0.012 to 0.030 inches) and preferably from 0.30 to 0, 71 mm (0.012 to 0.028 inches).
• the internal radius of the recesses is preferably of the order of 1.5 times the thickness of the material of the thickness of the plate or less and the width of the bumps is preferably of 2.5 to 7 times the thickness of the material of the plaque.
• the heat exchange structures having the configuration of the invention and dimensioned according to the preferred data can thus preferably be produced having a transverse dimension of the order of 3.17 mm (0.125 inches) or less.
• the condensers of the invention may be constructed from a suitable material which will withstand the effects of corrosion and internal pressures of system fluid.
• Typical materials include malleable materials such as aluminum and copper and in particular alloys.
• each of the components of a condenser is formed from the same material when joined together.
• the plates used to make the heat exchange structures will be formed from the same material.
• manifolds and heat exchange structures will also be formed from the same metal or a metal alloy when brazed or welded together. It is understandable that, although the illustrated invention includes a condenser for an automobile, the invention is applicable to multiple uses of heat exchangers.

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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)
• Air-Conditioning For Vehicles (AREA)

Applications Claiming Priority (2)

Publications (2)

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Family Applications (1)

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• 1989
  • 1989-10-04 US US07/417,049 patent/US4932469A/en not_active Expired - Fee Related
• 1990
  • 1990-10-03 JP JP2513924A patent/JPH04505362A/ja active Pending
  • 1990-10-03 CA CA002037901A patent/CA2037901A1/fr not_active Abandoned
  • 1990-10-03 EP EP90914931A patent/EP0447528B1/de not_active Expired - Lifetime
  • 1990-10-03 DE DE90914931T patent/DE69004793T2/de not_active Expired - Fee Related
  • 1990-10-03 BR BR909006944A patent/BR9006944A/pt not_active IP Right Cessation
  • 1990-10-03 WO PCT/FR1990/000702 patent/WO1991005211A1/fr not_active Ceased

Non-Patent Citations (1)

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