Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F1/00—Tubular elements; Assemblies of tubular elements
  • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
  • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
  • F28F1/126—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
  • F28F1/128—Fins with openings, e.g. louvered 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
  • 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
  • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
  • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
• • 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
  • Y10S165/471—Plural parallel conduits joined by manifold
  • Y10S165/486—Corrugated fins disposed between adjacent conduits
  • Y10S165/487—Louvered

Definitions

• the invention relates to a heat exchanger, in particular for power
• Such a heat exchanger is for example from DE 198 13 989 A1
• This heat exchanger can, for example, be a condenser
• Air conditioning system for motor vehicles is a simple air conditioning system for motor vehicles. Alternatively, the following Air conditioning system for motor vehicles. Alternatively, the following Air conditioning system for motor vehicles. Alternatively, the following Air conditioning system for motor vehicles. Alternatively, the following Air conditioning system for motor vehicles. Alternatively, the following Air conditioning system for motor vehicles. Alternatively, the following Air conditioning system for motor vehicles. Alternatively, the following Air conditioning system for motor vehicles. Alternatively, the following Air conditioning system for motor vehicles. Alternatively, the
• Heat exchanger can be designed, for example, as a coolant cooler
• the heat exchanger has a number arranged side by side
• Cross section is substantially rectangular. It flows in these flat tubes
• a first fluid for example a coolant in the case of a coolant cooler or a gaseous refrigerant to be condensed in the case of a condenser
• the flat tubes are connected to manifolds or manifolds and the flow of a second fluid, e.g. Ambient air exposed to cause heat transfer between the fluids.
• a second fluid e.g. Ambient air exposed to cause heat transfer between the fluids.
• Flat tubes have flow paths for the second fluid.
• the flow velocity of the second fluid is to be reduced in a targeted manner.
• this increases the residence time of the second fluid when it flows through the heat exchanger, i.e. the time in which the second fluid absorbs heat from the first fluid
• Flow rate of the second fluid limits the amount of heat that can be transferred between the first and the second fluid, ie the heat exchanger output.
• Another heat exchanger with cooling fins is from, for example
• the invention has for its object to provide a heat exchanger with flat tubes, in particular for motor vehicles, with cooling fins
• a first fluid to flow through flat tubes the outside with a second fluid can be acted upon and are arranged essentially parallel to one another in a direction transverse to the flow direction of the second fluid such that flow paths are formed for the second fluid in which
• Cooling fins are arranged, each extending between adjacent flat tubes.
• the cooling fins are designed as corrugated fins,
• Mass flow of the second fluid through gills which are arranged in the region of the downstream side of a rib for the second fluid, as
• a temperature boundary layer which may form on a pipe wall, is influenced, so that heat transfer may occur
• a streamlined configuration of the corrugated fins is preferably achieved in that their surfaces are essentially parallel to the flow
• the lateral offset means that they are arranged one behind the other
• Corrugated fins ensure that only a small proportion of the second fluid is unused, i.e. without significant heat transfer, between the
• ribs are preferably directly adjacent, i.e. without distance in
• a spaced arrangement of the in this case narrower corrugated ribs may be provided.
• the corrugated ribs have gills for guiding the second fluid.
• a so-called start-up flow which forms on the gills and has a high temperature gradient in an area of the corrugated fin, improves
• All gills of a fin section enclosed between two flat tubes are preferably opposite a corrugated fin in the same direction the flow direction of the second fluid is inclined.
• Inclination of the gills within a rib section has the advantage that, if necessary, the flow can thus be directed in a targeted manner to a downstream rib section.
• the gills staggered rib sections are preferably inclined in opposite directions, so that the heat exchanger
• the gills of two adjacent gill fields can also be
• the gills one of the two gills adjacent to each other
• rib geometry according to the invention can be used in particular in motor vehicle heat exchangers such as coolant coolers, radiators, condensers and evaporators.
• a plurality of corrugated ribs arranged one behind the other are preferably made from a common band
• corrugated fins including the gills are particularly through
• Rolls can be made from a metal strip. Is technically advantageous
• ribs for example three or five corrugated ribs.
• the gill depth LP is in the range from 0.7 to 3 mm with a gill angle of 20 to 30 degrees
• the rib height for such a system is advantageously in the range from 4 to 12 mm.
• the rib density for this system is advantageously in the range from 40 to 85 Ri / dm, which means a rib spacing or
• Fig. 1a, 1 b a heat exchanger with two staggered one behind the other
• corrugated fins as cooling fins between two adjacent flat tubes
• FIG. 5c a Wellr ppe from a tape m 12 rows in cross section
• Fig. 5d a Wellr ppe from a tape m 13 rows in cross section
• Fig. 5g a Wellr ppe from a tape m 1 5 rows in cross section
• Fig. 5h a Wellr ppe from a tape m 1 5 rows in cross section
• Fig. 5i a Wellri ppe from a tape m 13 rows in cross section
• Fig. 5j a Wellri ppe from a tape m 13 rows in cross section 6 shows a snapshot of a simulated air flow through
• Fig. 8 shows the proportion of one through a lamella opening
• Fig. 9 plots the portion of a through a slat opening
• the flat tubes 2 are equipped with flow guiding elements 2a and connected to manifolds or manifolds (not shown).
• FL1 is, for example, a cooling liquid or a refrigerant that condenses in the heat exchanger 1.
• Two (Fig. 1a, 1b) and three (Fig. 2a, 2b) corrugated beads 3 are arranged as cooling fins between two adjacent flat tubes 2. Embodiments with a higher number of corrugated fins 3 are also
• the corrugated fins 3 are meandering from a sheet metal
• Rib section 4b alternates.
• the rib sections 4a abutting the flat tubes 2 are connected to the flat tubes 2 in a heat-conducting manner,
• Rib sections 4b are perpendicular to the flat tubes 2 and form
• the second fluid FL2 flows essentially parallel to the surface 5 of the corrugated fins 3, i.e.
• the second fluid FL2 can thereby flow through the heat exchanger 1 at high speed and correspondingly high mass throughput.
• gills 7 are formed, which extend transversely to the flow direction S2 of the second fluid FL2 and transversely to the flow direction S1 of the first
• Two corrugated fins 3 arranged one behind the other between two flat tubes 2 are half a width b between adjacent fin sections 4b
• Extend heat exchanger 1 are produced by rolling from a strip 8. During rolling, the strip 8 is cut in the region of the respective offset between the two (FIGS. 1a, 1b, FIG. 3) or three (FIGS. 2a, 2b, FIG. 4) corrugated ribs 3 and the gills 7 in the corrugated ribs 3 cut.
• offset or higher-order offset (FIGS. 5e, 5f, 5g) of the corrugated fins 3 can alternatively be produced by arranging separate corrugated fins 3 of the same type with an offset between 0.1 mm and b / 2, where b is the distance between two adjacent flat tubes 2.
• the finned sections 4a of the corrugated fins 3 resting on the flat tubes 2 have no gills. A laminar flow of the fluid FL2 is therefore formed in this area rather than in the one provided with gills 7
• Laminar flow can form with increasing barrel length
• Fig. 5 shows corrugated ribs 10a, b ... j, each with several gill panels in Quer ⁇
• cooling fins have at least two so-called gill panels 11, 12 and 13, 14, respectively, which have a web of different design
• Slats can be offset from one another in several levels.
• the number of corrugated fins, which are arranged one behind the other in the direction of flow of the second fluid, can be selected depending on the depth of the heat exchanger and / or the depth of the corrugated fins
• 2, 3 or more rows are used, with a construction depth of up to 24 mm, for example 2, 3, 4 or more rows can be used for
• mm can use, for example, 2, 3, 4, 5, 6, 7 or more rows 2, 3, 4, 5, 6, 7, 8 or more rows can be used for a construction depth of up to 48 mm, for a construction depth of up to 54 mm
• 2, 3, 4, 5, 6, 7, 8, 9 or more rows can be used.With a construction depth of up to 60 mm, for example 2, 3, 4, 5, 6, 7, 8, 9, 10
• rows are used, with a construction depth of up to 66 mm, for example 2, 3, 4, 5, 6, 7, 8, 9, 10, 11 or more rows can be used.
• 5c shows an exemplary embodiment for two rows 15 and 16 in a transverse
• 5d shows an exemplary embodiment for 3 rows 17, 18 and 19 in a cross-sectional view.
• FIG. 5e An exemplary embodiment for 4 rows 20, 21, 22 and 23 is shown in FIG. 5e in one
• 5f shows an exemplary embodiment for 5 rows 24, 25, 26, 27 and 28 in a cross-sectional view.
• FIG. 5g An exemplary embodiment for 5 rows 29, 30, 31, 32 and 33 is shown in FIG. 5g in
• 5h shows an exemplary embodiment for 5 rows 34, 35, 36, 37 and 38
• More than two mutually offset rows can preferably be distributed over a total of two mutually offset levels, as in the embodiments in FIGS. 5d, 5e and 5g. You can also choose three
• Levels can be the same or different.
• the corrugated fin 10i or 10j has no gill in the area 41 or 44. This configuration also has an influence on the temperature boundary layer on the tube walls and / or an improved flow through the fins.
• the number of gills per row is, for example, between 2 and 30 gills depending on the number of rows and the depth of the heat exchanger.
• the number of gills per gill field is preferably from an engineering point of view with an odd number of rows,
• the number of gills per gill field can be identical, although this is not necessary.
• a corrugated fin is used as the basis in one
• Row i.e. without offset, consisting of a row with two gills
• V L runs of 3 m / s in a heat exchanger 71 with corrugated fins 72, 73 under the above described conditions in the region of an offset location 74
• the air particles undergo a flow deflection after flowing through the offset opening 75, the air particles passing through the offset opening
• Flap opening 82, 83 of the adjacent gill panel 79 flow.
• the air particles that flow through the last lamella opening 81 before the offset flow after they also have a flow deflection have experienced, mainly through the third lamella opening 84 of the
• Fig. 8 and Fig. 9 show a graph of the ratio of
• the percentage air mass flow is in the two corrugated fin configurations with two or three rows (one or two
• connection to the web area drops to below 8% with a minimum of about 4%. If the air mass flow at the corrugated fin consists of a
• the level at the slat opening in front of the web area decreases from about 12% to about 10%, so with the corrugated fin consisting of two levels / rows the mass flow through the last slat opening in front of the offset point increases from about 12 to about 13%.

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• 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)
• Separation By Low-Temperature Treatments (AREA)
• Power Steering Mechanism (AREA)
• Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
• Air-Conditioning For Vehicles (AREA)

Applications Claiming Priority (5)

Publications (2)

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• 2003
  • 2003-02-24 CN CNB03805504XA patent/CN100354592C/zh not_active Expired - Fee Related
  • 2003-02-24 WO PCT/EP2003/001852 patent/WO2003076860A1/fr not_active Ceased
  • 2003-02-24 AT AT03720308T patent/ATE380324T1/de not_active IP Right Cessation
  • 2003-02-24 AU AU2003223946A patent/AU2003223946A1/en not_active Abandoned
  • 2003-02-24 EP EP03720308A patent/EP1488184B1/fr not_active Expired - Lifetime
  • 2003-02-24 US US10/506,973 patent/US7147047B2/en not_active Expired - Lifetime
  • 2003-02-24 JP JP2003575040A patent/JP2005520113A/ja active Pending
  • 2003-02-24 DE DE50308729T patent/DE50308729D1/de not_active Expired - Lifetime

Non-Patent Citations (1)

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