EP1460363B1 - Evaporateur - Google Patents

Evaporateur Download PDF

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Publication number
EP1460363B1
EP1460363B1 EP20040005357 EP04005357A EP1460363B1 EP 1460363 B1 EP1460363 B1 EP 1460363B1 EP 20040005357 EP20040005357 EP 20040005357 EP 04005357 A EP04005357 A EP 04005357A EP 1460363 B1 EP1460363 B1 EP 1460363B1
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EP
European Patent Office
Prior art keywords
evaporator
flow
leeward
windward
deflection
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.)
Expired - Fee Related
Application number
EP20040005357
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German (de)
English (en)
Other versions
EP1460363A3 (fr
EP1460363A2 (fr
Inventor
Gottfried Dipl.-Ing. Dürr
Wolfgang Seewald
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.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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Publication date
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Publication of EP1460363A2 publication Critical patent/EP1460363A2/fr
Publication of EP1460363A3 publication Critical patent/EP1460363A3/fr
Application granted granted Critical
Publication of EP1460363B1 publication Critical patent/EP1460363B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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
    • F28D1/03—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
    • F28D1/03—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
    • F28D1/035—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 with U-flow or serpentine-flow inside the conduits
    • 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
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • 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
    • F28D2021/0085—Evaporators

Definitions

  • the invention relates to an evaporator, in particular for a motor vehicle.
  • Heat exchangers such as evaporators, in particular for air conditioning systems of motor vehicles are known in various constructions, for. B. as evaporator as a round tube evaporator, as a disk evaporator or as a flat tube evaporator.
  • the round tubes, discs or flat tubes form flow channels for a refrigerant, eg. B. R 134a, which is evaporated in the flow through the evaporator.
  • a refrigerant eg. B. R 134a
  • heat exchange surfaces are arranged in the form of, for example, corrugated fins, which are overflowed by air. The air supplies the refrigerant with the heat required for evaporation.
  • an expansion valve In an automotive air conditioning system is located on the refrigerant side in front of the evaporator, an expansion valve, which reduces the refrigerant pressure to the evaporation pressure.
  • the expansion valve is connected via a pressure and a suction line to the evaporator.
  • connection element is arranged laterally and a connection element in the middle region.
  • This flat-tube evaporator has two rows of flat tubes that communicate with manifolds divided into longitudinal chambers. Suction and pressure line are laterally, ie connected to the narrow sides of the headers.
  • the flat-tube evaporator is flowed through in 6 floods, ie it has two deflections in width on both the leeward and the windward side (the side facing the airflow) and additionally a deflection in the depth, ie from leeward to windward. This results in a uniform temperature distribution on the air outlet side.
  • this flat-tube evaporator has the already mentioned disadvantages of a lateral connection.
  • a problem with such evaporators is the uniform temperature distribution on the air outlet side - this is particularly due to overheating of the refrigerant vapor at the end of the flow path through the evaporator.
  • the refrigerant retains the evaporation temperature from entry to the evaporator over most of the flow path, ie, an approximately constant temperature.
  • the refrigerant must exiting the evaporator have a predetermined overheating, which is controlled by the expansion valve. However, this overheating can already occur in the penultimate round (the penultimate passage).
  • Such overheating ie, a temperature of the refrigerant lying above the evaporation temperature has an unfavorable effect on a uniform temperature distribution, in particular in the case of smaller evaporators which have only a 4-flow throughflow or block interconnection.
  • the overheating zone would "strike through" the air outlet area and influence the temperature distribution particularly unfavorably.
  • the inlet opening for the evaporator is laterally, d. H. arranged on the narrow side and the outlet opening on the longitudinal side of the evaporator.
  • d. H. arranged on the narrow side and the outlet opening on the longitudinal side of the evaporator.
  • advantageous Verschaltungsde, d. H. Both a 6-flow flow for larger and a 4-flow flow for smaller evaporators. Even with a 4-flow flow, overheating will not adversely affect the temperature distribution on the air outlet side, because the last two passages of the refrigerant flow on the air inlet side (windward side) are arranged and thus there is no risk that the overheating on the lee side " breaks down ".
  • the inventive connection of suction and pressure line on the longitudinal and narrow side of the evaporator is on flat-tube evaporator applicable.
  • the solution according to the invention has a double-tube flat-tube evaporator, the collecting tanks with longitudinal chambers.
  • the inlet opening in the front side of the leeward longitudinal chamber and the outlet opening on the longitudinal side of the windward longitudinal chamber is arranged and connected to the pressure or suction line.
  • not only a 6-flow, but also a 4-flow flow through the evaporator is possible, which is advantageous in particular for small evaporators.
  • Six or four-flow means that the evaporator is flowed through in six or four passages (group of flow channels with the same flow direction), with deflections in the width or in the depth between the individual passages.
  • Double row means that the evaporator is flowed through on the leeward side on the one hand and on the windward side on the other hand, whereby two rows can also be formed by a continuous flat tube.
  • the evaporator is first flowed through on the leeward side, ie in three or two passages and then on the windward or air inlet side, from where the extraction of the refrigerant vapor takes place.
  • an expansion valve is disposed in front of the evaporator and connected via a pressure and a suction line to the inlet or outlet port.
  • the suction tube is advantageously largely straight, d. H. without strong bends and short, causing only minimal pressure losses. This benefits the refrigeration capacity of the evaporator.
  • Fig. 1 shows a flat-tube evaporator 1 in perspective view with two refrigerant connection pipes 2, 3, which lead from the evaporator 1 to an expansion valve 4, which is shown only schematically and in broken lines.
  • the evaporator 1 is constructed from an evaporator block 5 of tubes and fins and two collecting boxes 6, 7 placed on this block. Both manifolds 6, 7 each have two longitudinal chambers 6a, 6b and 7a, 7b.
  • the evaporator block 5 consists of a plurality of flow channels, such as flat tubes, 8, between which ribs, not shown, such as corrugated fins are arranged, which are overflowed by air in the direction of flow shown by arrows L.
  • the evaporator block 5 is laterally closed by side parts 9, which form the one side, such as the narrow sides.
  • the other sides, for example the long side is designated 10 and corresponds to the air inlet side.
  • the parts of the evaporator block 5 and the manifolds 6, 7 are preferably made of aluminum or aluminum alloys and are preferably soldered together, the ends of the flat tubes 8 are sealed or sealed in openings in the manifolds 6, 7 are added.
  • the evaporator 1 is a refrigerant, for. B. R 134 a flows through, which is the rear, d. H. Lee side longitudinal chamber 6a through the pressure line 2 is supplied. Also, the refrigerant can be supplied to the windward side of the heat exchanger. Previously, the refrigerant in the expansion valve 4 is reduced to the evaporator pressure, i. H. the refrigerant enters the longitudinal chamber 6a as refrigerant wet steam. After flowing through the evaporator - which is explained in more detail below - the refrigerant is sucked through the suction line 3. The expansion valve 4 is thus located in the air flow direction L in front of the evaporator 1 and the evaporator block 5.
  • the suction tube 3 is short and relatively straight, d. H. formed without strong bends, so that 3 minimal pressure losses occur in this intake manifold.
  • the evaporator-side end of the suction tube 3 is soldered into an outlet opening 3a of the front longitudinal chamber 6b.
  • the input-side pressure tube 2 is soldered with its evaporator-side end in an inlet opening in the end face of the longitudinal chamber 6a and leads over two to three pipe bends to the expansion valve 4.
  • the connection of the suction tube 3 on the longitudinal side of the longitudinal chamber 6b is referred to as a so-called longitudinal connection and the Connection of the pressure tube 2 at the narrow or end side of the longitudinal chamber 6a is referred to as a lateral connection.
  • FIG. 2 shows the refrigerant-side and air-side flow of the flat tube evaporator 1 according to Fig. 1 ,
  • This representation of the evaporator 1 reveals a first row 11 of tube openings in the rear longitudinal chamber 6a and a second row 12 of tube openings in the front longitudinal chamber 6b.
  • Corresponding tube openings are provided in the two lower longitudinal chambers 7a, 7b.
  • In these openings 11, 12 open the flat tubes 8, which are formed either as two rows of flat tubes 8 or as a series of continuous flat tubes with two flow directions.
  • the flat tubes 8 are formed as multi-chamber tubes with a plurality of parallel flow channels.
  • the flat tube evaporator 1 is the refrigerant according to the illustrated Arrows from A to D 6 flows through, ie in the back row 11 there are three passages A, B, C, each with two deflections between A and B and B and C in the width and three passages of D over E to F in the front row 12, wherein the passage C is connected via a deflection in the depth C / D against the flow direction L of the air with the passage D.
  • the deflections in the width are effected by two transversely arranged partitions 13, 14 in the rear longitudinal chamber 6a and in the front longitudinal chamber 6b and further partitions 15, 16 in the lower longitudinal chambers 7a, 7b.
  • the entry of the refrigerant takes place - as before for Fig.
  • This refrigerant guide also called block interconnection, leads to a uniform temperature distribution on the air outlet side 17. Since the entry of the refrigerant takes place in the leeward row of pipes 11, the refrigerant is in the passages A, B, C still in the wet steam region, d. H. the refrigerant has in the leeward pipe row 11 throughout an approximately constant temperature, namely the evaporation temperature. Only in the last passages E or F in the windward tube row 12 occurs overheating of the refrigerant and thus an increase in temperature. This increase in the temperature of the refrigerant causes an asymmetry in the temperature distribution, but this is approximately compensated insofar as it occurs on the air inlet side 10 and does not strike the air outlet side 17.
  • Fig. 3 shows a further embodiment of the invention, namely a flat-tube evaporator 18 with a lateral refrigerant inlet 19 and a longitudinal port 20 for the outlet or the suction of the refrigerant.
  • the lateral inlet is arranged on a leeward side or on a leeward collecting box of the evaporator
  • the outlet is arranged on the windward side of the evaporator or on a windward collecting box.
  • the collection box areas 21a 'and 21b' are arranged with the terminals 19, 20 adjacent to one side of the evaporator.
  • This evaporator 18 is in principle the same as the evaporator 1 described above, but it is smaller in the longitudinal extent and is flowed through (only) 4-flow, d. H. in four passages I, II, III, IV, wherein after the passage II a deflection takes place in the depth II / III against the air flow direction L.
  • the evaporator 18 has an upper header 21 with two longitudinal chambers 21 a, 21 b and two transverse partitions 22, 23. These separate the collection chambers into four regions 21a ', 21a ", 21b' and 21b".
  • the partition walls 22 and 23 are arranged in the chambers 21a and 21b at the same height, in the width of the evaporator perpendicular to the air flow direction. Due to the central arrangement of the partitions it follows that the floods I to IV are the same size. However, it may also be expedient that the dividing walls are not arranged at the same height and / or not centrally and thus the floods are different, i. have different numbers of flat tubes or flow paths.
  • a lower collecting box 24 has two longitudinal chambers 24a, 24b - without transversely arranged dividing walls. Due to this design of the headers 21, 24 with partitions 22, 23 and lateral connection 19 and longitudinal connection 20 results in the illustrated 4-flow flow.
  • the refrigerant is in the passages I, II on the leeward side of the evaporator 18 as wet steam with (constant) evaporation temperature, so that there is a uniform temperature distribution on the air outlet side.
  • the refrigerant should be present at the outlet 20 as superheated steam at a predetermined superheat temperature; Therefore, in the last passage IV refrigerant with overheating temperature flows, possibly already in the penultimate passage III - but both are on the air inlet side. A breakthrough of overheating on the Air outlet side is not to get. This results in a uniform temperature distribution on the air outlet side - even for a small, four-flow evaporator.
  • Fig. 4 shows a further embodiment of the invention, namely a flat tube evaporator 118 with a lateral refrigerant inlet 119 and a longitudinal port 120 for the exit or the suction of the refrigerant.
  • This evaporator 118 is in principle the same as the evaporator 1 described above, but it is greater in the longitudinal extent and flows through 5-flow, ie in five passages I, II, III, IV, V, wherein after the passage III a deflection in the depth III / IV against the air flow direction L takes place. However, the deflection in depth can also take place in the air flow direction. This also applies generally to the other embodiments.
  • the evaporator 118 has an upper header box 121 with two longitudinal chambers 121a, 121b and two transverse partitions 122, 123.
  • a lower header 124 has two longitudinal chambers 124a, 124b with a transverse partition 150.
  • the partition walls 122, 150 on the leeward side are staggered with respect to the longitudinal extent of the evaporator to ensure the three-flow formation.
  • the partition wall 123 is arranged centrally of the evaporator. As a result, two equally distributed floods are generated on the windward side.
  • the refrigerant should be present at the outlet 120 as superheated steam at a predetermined superheat temperature; therefore flows in the last passage V Overheating temperature refrigerant, possibly already in last but one passage IV - both are on the air intake side. This results in a uniform temperature distribution on the air outlet side, even for a 5-flow evaporator.
  • the evaporator is divided into different areas on the lee side and the windward side, as in different floods. These areas are not the same size on the lee side and the windward side as shown.
  • the block interconnection is progressive, that is, the first row of tubes into which the refrigerant flows or is injected is divided into three areas (I, II, III), while the second row of tubes from which the refrigerant is sucked, divided into only two areas or floods (IV, V).
  • the block interconnection in a five-pass evaporator, may also be degressive, that is, the first row of tubes into which the refrigerant flows or is injected divides into two zones (I, II), while the second Pipe row from which the refrigerant is sucked, divided into three areas or floods (III, IV, V).
  • the inlet for the refrigerant is arranged on a lower longitudinal chamber and the outlet on an upper connection.
  • the connections are arranged on the same side of the evaporator, viewed in the longitudinal direction.
  • the ports may also be arranged on opposite sides of the evaporator in the longitudinal direction.
  • Fig. 5 shows a further embodiment of the invention, namely a flat tube evaporator 218 with a side refrigerant inlet 219 and a longitudinal port 220 for the outlet or the suction of the refrigerant.
  • This evaporator 218 is basically the same as that described above Evaporator 118 is constructed and flows through 5-flow, ie in five passages I, II, III, IV, V, wherein after the passage II, a deflection in the depth II / III against the air flow direction L takes place. However, the deflection in depth can also take place in the air flow direction. This also applies generally to the other embodiments.
  • the evaporator 218 has an upper header 221 with two longitudinal chambers 221a, 221b and a transverse partition 222.
  • a lower collection box 224 has two longitudinal chambers 224a, 224b with two transverse partitions 150, 151. Due to this design of the collection boxes 221, 224 with dividing walls 222, 251, 250 and lateral connection 219 and longitudinal connection 220 results in the illustrated 5-flow flow ,
  • the partitions 222, 251 on the windward side are arranged offset with respect to the longitudinal extent of the evaporator to ensure the dreiflutige training.
  • the dividing wall 250 is arranged in the middle of the evaporator. As a result, two equally distributed floods are generated on the leeward side.
  • the refrigerant in the passages and II on the leeward side of the evaporator 218 as wet steam with (constant) evaporation temperature, so that could result in a uniform temperature distribution on the air outlet side.
  • the refrigerant should be present at the outlet 220 as superheated steam at a predetermined superheat temperature; Therefore, in the last passage V refrigerant with superheat temperature flows, possibly already in the penultimate passage IV - but both are on the air inlet side. This results in a uniform temperature distribution on the air outlet side, even for a 5-flow evaporator.
  • the evaporator is divided into different areas on the lee side and the windward side, as in different floods. These areas are not the same size on the lee side and the windward side as shown. This results in that the block interconnection is degressive, that is, that the first row of tubes, in which the refrigerant flows or is injected, in two areas or floods divides (I, II), while the second row of tubes from which the refrigerant is sucked, divided into three areas or floods (III, IV, V).
  • the inlet for the refrigerant is arranged at the leeward side on a lower longitudinal chamber and the outlet at the upper connection is windward.
  • the connections are arranged on the same side of the evaporator, viewed in the longitudinal direction.
  • the ports may also be arranged on opposite sides of the evaporator in the longitudinal direction.
  • Fig. 6 shows a further embodiment of the invention, namely a flat tube evaporator 318 with a side refrigerant inlet 319 and a longitudinal port 320 for the outlet or the suction of the refrigerant.
  • This evaporator 318 is constructed in principle the same as the evaporator 118 described above and is flowed through 5-flow, ie in five passages I, II, III, IV, V, wherein after the passage I a deflection in the depth I / II in the air flow direction L takes place and after the passage III a deflection takes place in the depth III / IV counter to the direction of air flow.
  • the evaporator 318 has an upper header 321 with two longitudinal chambers 321a, 321b and three transverse partitions 360,361,362.
  • a lower collection box 324 has two longitudinal chambers 324a, 324b with a transverse partition 350. Due to this design of the collection boxes 321, 324 with partitions 350, 360,361,362 and side connection 319 and longitudinal connection 320 results in the illustrated 5-flow flow.
  • the refrigerant in the passages II and III on the leeward side of the evaporator 218 can be present as wet steam with (constant) evaporation temperature, so that a uniform temperature distribution could result on the air outlet side.
  • the refrigerant should be present at the outlet 320 as superheated steam at a predetermined superheat temperature; Therefore, in the last passage V refrigerant with superheat temperature flows, possibly already in the penultimate passage IV - both are, however on the air inlet side. This results in a uniform temperature distribution on the air outlet side, even for a 5-flow evaporator.
  • the arrangement of the partitions 361 and 362 allows an exit 320 in the middle flood of the evaporator on the windward side. However, this requires the two deflections at depth (A-> B, C-> D).
  • Fig. 7 shows a further embodiment of the invention, namely a flat tube evaporator 418 with a side refrigerant inlet 419 and a longitudinal port 420 for the outlet or the suction of the refrigerant.
  • This evaporator 418 is basically the same as the evaporator 1 described above, but it is greater in the longitudinal extent and flows through 7-flow, ie in seven passages I, II, III, IV, V, VI, VII, wherein after passage IV a deflection in the depth IVN against the air flow direction L takes place. However, the deflection in depth can also take place in the air flow direction. This also applies generally to the other embodiments.
  • the evaporator 418 has an upper header 421 with two longitudinal chambers 421a, 421b and two transverse partitions 422, 423.
  • a lower collection box 424 has two longitudinal chambers 424a, 424b with three transverse partitions 450, 451, 452. Due to this design of the collection boxes 421, 424 with partitions 422, 423, 450, 451, 452 and side port 419 and longitudinal port 420 results the illustrated 7-flow flow.
  • the refrigerant in the passages I, II, III and IV on the leeward side of the evaporator 418 as wet steam with (constant) evaporation temperature, so that could result in a uniform temperature distribution on the air outlet side.
  • the refrigerant should be present at the outlet 420 as superheated steam at a predetermined superheat temperature; Therefore, in the last passage VII refrigerant with superheat temperature flows, possibly already in the penultimate passage VI - but both are on the air inlet side. This results in a uniform temperature distribution on the air outlet side, even for a 7-flute evaporator.
  • evaporators with three or more than seven floods can be created.
  • the injection can be made over the entire leeward or windward side, in which case there is a double-flow connection on the windward or leeward side.
  • an interconnection similar to a six-flow interconnection can be realized, in which case four floods are realized per windward and leeward side.
  • Heat exchangers shown are preferably evaporators for use in air conditioning systems of a motor vehicle. These evaporators can be used in an air conditioner that provide the entire vehicle (front air conditioning) or as an evaporator for a rear air conditioning, see for example FIG. 8 ,
  • a preferred embodiment is designed such that the dimensions of the tube / fin block between the header boxes has nearly square dimensions, such as about 130 mm * about 120 mm.
  • An almost square is understood to mean a geometry which has a ratio of the side lengths of 0.7 to 1.3, preferably of 0.8 to 1.2 and particularly preferably of 0.9 to 1.1.
  • an even or odd number of tubes or flow channels is provided. It may also be expedient if, for example, the number of tubes per flood is equal or unequal. For example, it can be useful in a 5- or 6-flute evaporator with a total of 11 tubes on the leeward or windward side when two floods on the windward and / or leeward side comprise 4 tubes and one tide comprises 3 tubes, see FIG. 8 , There are two floods A, B equipped with four pipes and a flood with three pipes. Preferably, the flood is with more or less pipes, here with three pipes between or next to the floods with the same number of tubes, here with four pipes.

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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)

Claims (10)

  1. Évaporateur, en particulier pour un véhicule automobile, comprenant un bloc évaporateur prouvant être traversé par un fluide frigorigène à flux multiplets et circulant sur au moins deux rangées dans des conduits d'écoulement, ledit bloc évaporateur comprenant des ailettes disposées à l'extérieur des conduits d'écoulement et prouvant être balayées par de l'air, et comprenant au moins un bac collecteur qui communiqué avec les conduits d'écoulement et présente des grands côtés et des petits côtés ainsi que des ouvertures pour l'entrée et la sortie du fluide frigorigène, où une ouverture pour l'entrée du fluide frigorigène est disposée sur le petit côté, l'autre ouverture, de préférence l'ouverture pour la sortie du fluide frigorigène, étant disposée sur le grand côté, où les conduits d'écoulement sont configurés comme des tubes plats d'un évaporateur à tubes plats, et le bac collecteur (6) présente deux chambres longitudinales (6a, 6b) qui communiquant avec les tubes plats (8), et l'ouverture d'entrée (2a) est disposée sur le côté de sortie d'air de la chambre longitudinale (6a), l'ouverture de sortie (3a) étant disposée sur le côté d'entrée d'air de la chambre longitudinale (6b).
  2. Évaporateur selon la revendication 1, caractérisé par une rangée de tubes plats qui peuvent être traversés à chaque fois par 2 flux, en comportant un retour de flux se produisant en profondeur.
  3. Evaporateur selon l'une des revendications 1 ou 2, caractérisé en ce que les ailettes sont configurées comme des ailettes ondulées.
  4. Evaporateur selon l'une quelconque des revendications 1 à 3, caractérisé par un écoulement se faisant en 6 flux (A, B, C, D, E, F), comportant à chaque fois deux retours de flux se produisant en largeur sur le côté de sortie d'air et sur le côté d'entrée d'air, ainsi qu'un retour de flux se produisant en profondeur, depuis le côté de sortie d'air jusqu'au côté d'entrée d'air.
  5. Evaporateur selon l'une quelconque des revendications 1 à 3, caractérisé par un écoulement se faisant en 4 flux (I, II, III, IV), comportant à chaque fois un retour de flux se produisant en largeur sur le côté de sortie d'air et sur le côté d'entré d'air, et un retour de flux se produisant en profondeur, depuis le côté de sortie d'air jusqu'au côté d'entrée d'air.
  6. Evaporateur selon l'une quelconque des revendications 1 à 3, caractérisé par un écoulement se faisant en 5 flux (I, II, III, IV, V), comportant à chaque fois au moins un retour de flux se produisant en largeur sur le côté de sortie d'air et sur le côté d'entrée d'air, et au moins un retour de flux se produisant en profondeur, depuis le côté de sortie d'air jusqu'au côté d'entrée d'air.
  7. Evaporateur selon l'une quelconque des revendications 1 à 3, caractérisé par un écoulement se faisant en 3 flux (I, II, III), comportant à chaque fois au moins un retour de flux se produisant en largeur sur le côté de sortie d'air ou sur le côté d'entrée d'air, et au moins un retour de flux se produisant en profondeur, depuis le côté de sortie d'air jusqu'au côté d'entrée d'air.
  8. Evaporateur selon l'une quelconque des revendications 1 à 3, caractérisé par un écoulement se faisant en 7 flux, ou plus, comportant à chaque fois au moins un retour de flux se produisant, en largeur sur le côté de sortie d'air et sur le côté d'entrée d'air, et au moins un retour de flux se produisant en profondeur, depuis le côté de sortie d'air jusqu'au côté d'entrée d'air.
  9. Evaporateur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un détendeur (4) est disposé en amont de l'évaporateur (1), dans la direction (L) d'écoulement de l'air, détendeur qui est raccordé à l'ouverture d'entrée (2a) par une conduite de refoulement (2), et à l'ouverture de sortie (3a) par une conduite d'aspiration (3).
  10. Evaporateur selon la revendication 9, caractérisé en ce que la conduite d'aspiration est configurée en étant sensiblement droite.
EP20040005357 2003-03-21 2004-03-05 Evaporateur Expired - Fee Related EP1460363B1 (fr)

Applications Claiming Priority (2)

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DE2003112780 DE10312780A1 (de) 2003-03-21 2003-03-21 Wärmetauscher
DE10312780 2003-03-21

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EP1460363A2 EP1460363A2 (fr) 2004-09-22
EP1460363A3 EP1460363A3 (fr) 2007-08-01
EP1460363B1 true EP1460363B1 (fr) 2012-05-09

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DE102004056790A1 (de) 2004-10-04 2006-04-06 Behr Gmbh & Co. Kg Wärmetauscher
DE102005059917A1 (de) * 2005-04-15 2006-11-02 Behr Gmbh & Co. Kg Verdampfer
DE102006055837A1 (de) * 2006-11-10 2008-05-15 Visteon Global Technologies Inc., Van Buren Wärmeübertrager, insbesondere als Verdampfer von Fahrzeugklimaanlagen
DE102007013125A1 (de) * 2007-03-15 2008-09-18 Behr Gmbh & Co. Kg Wärmeübertrager
DE102008055624A1 (de) * 2007-12-10 2009-06-18 Behr Gmbh & Co. Kg Wärmeträger, insbesondere Heizkörper für Kraftfahrzeuge
DE102008035400A1 (de) * 2008-07-29 2010-02-04 Behr Gmbh & Co. Kg Vorrichtung zur Kühlung einer Wärmequelle eines Kraftfahrzeugs
EP2149771B8 (fr) 2008-07-29 2017-03-15 MAHLE Behr GmbH & Co. KG Dispositif destiné au refroidissement d'une source de chaleur d'un véhicule automobile
DE102010031397A1 (de) * 2010-07-15 2012-03-29 Behr Gmbh & Co. Kg Verdampfervorrichtung
DE102010042504A1 (de) * 2010-10-15 2012-04-19 Behr Gmbh & Co. Kg Wärmetauscher
DE102011053894A1 (de) 2010-11-23 2012-05-24 Visteon Global Technologies, Inc. Kälteanlage mit Kältemittelverdampferanordnung und Verfahren zur parallelen Luft- und Batteriekontaktkühlung
DE102015210184A1 (de) 2015-06-02 2016-12-22 Volkswagen Aktiengesellschaft Kraftfahrzeug mit einem Klimagerät
DE102016201027A1 (de) 2016-01-25 2017-07-27 Volkswagen Aktiengesellschaft Verdampferanordnung, Klimatisierungseinrichtung und Betriebsverfahren dafür
DE102016219205B4 (de) 2016-10-04 2023-02-02 Volkswagen Aktiengesellschaft Mehrpassiger Luft/Kältemittel-Wärmeübertrager, Klimatisierungsvorrichtung für ein Kraftfahrzeug und Kraftfahrzeug
FR3062198B1 (fr) * 2017-01-23 2020-05-01 Valeo Systemes Thermiques Circuit de circulation d'un fluide refrigerant pour un evaporateur a deux nappes
CN108344210B (zh) * 2018-03-14 2023-10-24 深圳市丰瑞德机电技术有限公司 提高换热效率的平行流换热系统
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DE102021208038A1 (de) 2021-07-26 2023-01-26 Mahle International Gmbh Verdampfer

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EP1460363A3 (fr) 2007-08-01
EP1460363A2 (fr) 2004-09-22

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