EP1798505A2 - Echangeur de chaleur, en particulier évaporateur - Google Patents

Echangeur de chaleur, en particulier évaporateur Download PDF

Info

Publication number
EP1798505A2
EP1798505A2 EP20060025336 EP06025336A EP1798505A2 EP 1798505 A2 EP1798505 A2 EP 1798505A2 EP 20060025336 EP20060025336 EP 20060025336 EP 06025336 A EP06025336 A EP 06025336A EP 1798505 A2 EP1798505 A2 EP 1798505A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
tube
exchanger according
passage openings
inner diameter
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.)
Withdrawn
Application number
EP20060025336
Other languages
German (de)
English (en)
Inventor
Gottfried Dipl.-Ing. Dürr
Michael Dipl.-Ing. Kranich
Karl-Heinz Dipl.-Ing. Staffa
Christoph Dipl.-Ing. Walter
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1798505A2 publication Critical patent/EP1798505A2/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-section
    • 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
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates

Definitions

  • the invention relates to a heat exchanger, in particular an evaporator, as used in particular for the air conditioning of a motor vehicle, according to the preamble of claim 1.
  • an evaporator in which the collecting containers are provided with plates with throttle openings for reducing the refrigerant passage cross-section between the individual distribution tank sections.
  • the throttle openings are provided here exclusively in the lower reservoir and serve to equalize the refrigerant distribution to the individual multi-channel flat tubes of the evaporator.
  • Such an evaporator still leaves something to be desired.
  • turbulence generators in the form of slots can be provided in the distributor tube, the ridges projecting inward in the direction of the center of the collecting container being bent outward until they bear against the inner wall of the collecting container.
  • Each of the slots is formed here by means of a cutting tool with a tapered blade, wherein the width of the slots varies.
  • n is the number of the passage opening in the fluid supply direction, a, b, c and d constants, wherein ⁇ is at most 0.2, preferably 0.1 and more preferably 0.05. In the case of non-circular cross-sections, the hydraulically equivalent diameter will replace the diameter.
  • the constants a, b and c are preferably in the following ranges: a in a range of +3.2 to +3.6, especially +3.4286 ⁇ 5%, b in a range of -0.5 to -0 , 2, in particular -0.3536 ⁇ 5%, and c in a range of 0 to +0.1, in particular +0.0179 ⁇ 5%.
  • Particularly preferred value for a is +3.4286, for b -0.3536 and for c + 0.0179.
  • three to twelve, in particular five to ten and in particular preferably six to eight through openings are preferably provided on an infeed pipe.
  • the indicated values make it possible, especially with exactly seven passage openings, to achieve an optimal distribution of the refrigerant serving as the medium and thereby lead to a uniform temperature distribution.
  • such a configuration can be provided both in an injection pipe and in an overflow pipe.
  • it is important to ensure a uniform distribution of the mass flow since in the region of the overflow pipe, the proportion of gaseous phase is greater than at the injection pipe, so that the risk of uneven temperature distribution is significantly greater in the subsequent heat exchanger area.
  • the difference between the maximum and the minimum diameter of the passage openings divided by the maximum diameter of the passage openings is at least 0.3, preferably at least 0.4.
  • the free flow cross section in the injection tube and / or overflow tube is preferably substantially constant, which is understood below to mean changes of less than ⁇ 5%. However, too Measures are taken to at least partially change the cross-section, in particular to reduce, so that the flow rate of the medium is increased, whereby a better mixing of the liquid and gaseous phase takes place.
  • a sleeve for reducing the free flow cross section is preferably provided.
  • the sleeve is in this case preferably formed slotted at least in regions, wherein the sleeve is preferably applied over a maximum of three quarters, in particular over half, of the inner circumference of the injection tube.
  • the slot in the sleeve can narrow to influence the flow velocity of the medium in the flow direction of the medium, so that the free flow cross-section of the injection pipe or overflow pipe is reduced.
  • the injection tube and / or the suction tube and / or an overflow tube, which is arranged between two rows of tubes, preferably has a substantially D-shaped cross-section.
  • the distances of the passage openings to the upper region of the tube, in which usually accumulates the gaseous phase low, so that even with relatively simple measures an increased suction of the gaseous phase can be realized.
  • the inner diameter of the injection tube at least in a region in which passage openings are provided, between 2.0 and 3.0 mm, in particular between 2.2 and 2.6 mm, wherein in the case of non-circular cross-sections of the hydraulically equivalent inner diameter in place of the inner diameter occurs.
  • the inner diameter of the suction tube is preferably between 4.0 and 6.6 mm, in particular between 4.5 and 6.0 mm, wherein in the case of non-circular cross sections of the hydraulically equivalent inner diameter occurs in place of the inner diameter.
  • the inner diameter of the injection pipe is preferably 2.0 to 3.0 mm, in particular between 2.2 and 2.6 mm, the inner diameter of an overflow pipe 2.0 to 4.5 mm, in particular between 3.0 and 4.0 mm, and the inner diameter of the suction pipe between 4.0 and 6.6 mm, in particular between 4.5 and 6.0 mm, wherein in the case of non-circular cross-sections of the hydraulically equivalent inner diameter occurs in place of the inner diameter.
  • the free flow cross sections are designed accordingly.
  • the heat exchanger is preferably an evaporator, particularly preferably a plate-type or serpentine-type evaporator.
  • the injection pipe or the overflow pipe is attached to the upper side of the heat exchanger. In principle, however, another attachment is possible.
  • An evaporator 1 which is flowed through during operation of a refrigerant, in this case of R744, has a plurality of juxtaposed, U-shaped bent flat tubes 2 with interposed corrugated fins 3. Further, an injection pipe 4, through which cold refrigerant enters the evaporator 1, an injection plate 5, which is disposed between the injection pipe 4 and the flat tubes 2 and in conjunction with a distributor plate 6 and a bottom plate 7 forms a collecting box arranged above, and a Exit or suction pipe (not shown) provided by which the heated refrigerant is discharged from the evaporator 1.
  • the injection plate 5 is formed such that it has a plurality of passages produced by punching 8, which correspond to holes 9 in the injection tube 4, wherein the passages 8 extend into the holes 9 in the injection tube 4, in which they are relatively flush with the present Inner circumferential surface of the same end.
  • seven passages 8 for the introduction of refrigerant and correspondingly seven holes 9 are provided in the injection pipe 4, which passages 9 'to the flat tubes 2 form.
  • Corresponding passages 8 'and bores are provided for the outlet of the refrigerant in a suction pipe (not shown) after it has passed through the evaporator 1.
  • Figures 3 and 4 show sections through the passages 8 ', these correspond but - except for the diameter of the passages - the passages 8 for the refrigerant inlet.
  • the suction pipe has, as a result of the evaporation of refrigerant, a larger volume flow must be passed through, a larger inner diameter than the injection pipe 4.
  • the passages 8, which form the passage openings 9 ' have an (inner) diameter d which is dependent on the position in the injection pipe 4, the cross-section free of the refrigerant at all injection openings decreasing over the length of the injection pipe 4.
  • a is +3.4286, b is -0.3536 and c is +0.0179 and n corresponds to the number of the passage opening in the flow direction, so that for the first diameter 3.1 mm, the second diameter 2.8 mm, the third diameter is 2.5 mm, the fourth diameter is 2.3 mm, the fifth diameter is 2.1 mm, the sixth diameter is 2.0 mm and the seventh diameter is 1.8 mm.
  • the ratio of the difference between the largest and smallest diameter to the largest diameter is 0.42.
  • the outer diameter of the injection tube is in this case 10 mm, the wall thickness 2 mm, so that there is an inner diameter D h of 6 mm.
  • the diameter of the bores and passages 8 'for the refrigerant outlet is constant, as well as the inner diameter of the suction pipe.
  • the spacing of the bore centers of the first and second bores, the third and fourth bores, the fifth and sixth bores is constant, as is the distance between the second and third bores, the fourth and fifth hole and the sixth and seventh hole.
  • the refrigerant flow is predetermined by the distributor plate 6.
  • This has a structure with approximately 1-shaped and H-shaped openings, which in some areas, ie omitting the stacked H-shaped openings in shortening and changing the design of one of the two end portions, the.
  • Structure of the distributor plate 6, which is shown in Fig. 6, corresponds.
  • an I-shaped opening in the region of the passage openings 9 and in extension thereof is also provided correspondingly in the region of the passage openings for the refrigerant outlet.
  • the I-shaped openings in the middle region on a circular extension In order to improve the inflow and outflow of the refrigerant, the I-shaped openings in the middle region on a circular extension.
  • the introduced refrigerant is relatively evenly distributed to the front, ie the air inlet side arranged half of the flow channels of the flat tubes, flows down, is deflected by the arc of the U-shaped flat tube, flows back up, where it again in the region of the distributor plate. 6 arrives.
  • the H-shaped opening has approximately twice the height of the I-shaped opening, wherein the central region has a transition from one flat tube to the next.
  • the H-shaped opening has an approximately twice as high height as the I-shaped openings Flat tube, which is flowed through in mirror image to the central longitudinal axis of the H-shaped opening (which runs in the air flow direction), allows.
  • the refrigerant is deflected backwards and flows from top to bottom in the other part of the flat tube channels, which are flowed through opposite to the front channels, so that the refrigerant exits at the rear I-shaped opening and the evaporator again leaves via the corresponding passage to the suction pipe.
  • a sleeve 20 is additionally provided in the otherwise corresponding to the first embodiment, the evaporator 1 in the injection tube 4, which is formed by a longitudinally wide slotted wide tube.
  • the slot in this case occupies about half of the corresponding hollow cylinder, so that the sleeve 20, as shown in Fig. 5, only in the holes 9 opposite region of the injection tube 4 is arranged and reduces the free flow area, whereby the flow rate of the refrigerant is increased ,
  • the upper region, in which the gaseous phase preferably accumulates is brought closer to the entry into the passage openings 9 '.
  • the sleeve 20 extends substantially over the entire straight length of the injection tube 4, that is, it begins before the first hole 9.
  • the distributor plate 6 and the injection plate 5 of an evaporator which has ten passage openings.
  • a double deflection into the width of the evaporator both on the front and on the back
  • a simple deflection in the depth of the evaporator The dimensions of the individual passage openings correspond essentially to the aforementioned formula.
  • evaporators in which the design of the injection tube and the passage openings can be made according to the embodiments described above, are described in their general structure with reference to the figures 8 et seq.
  • the evaporators of Figures 8 to 13 are in view of their general configuration in the DE 102 60 107 A1 discloses the entire disclosure content with respect to the general design of the evaporator is explicitly included.
  • the evaporator 70 shown in Figures 8 to 10 has a plurality of U-shaped bent flat tubes 71a, 71b, 71c, etc. on. Each flat tube has two legs 72 and 73. The free ends of the legs 72 and 73 are secured in a bottom plate 74 (see Figures 9 and 10).
  • a distributor plate 75 Arranged above the base plate 74 is a distributor plate 75, which alternately has two slit-shaped openings 76, 77 lying one behind the other in the depth direction, leaving a web 78 and a deflecting channel 79 extending in the depth direction.
  • An injection plate 80 disposed adjacent to the distributor plate 75 is omitted in the illustration of FIG. 8.
  • the flow of the refrigerant is carried out according to the arrows, ie the refrigerant enters at E in the front flow section of the flat tube 71 a, first flows downwards, is then deflected down, flows then up and enters the deflection channel 79, where it is deflected according to the arrow U in the depth, then flows on the back down, is deflected there and then flows back up to pass through the aperture A through the opening 77 ,
  • the supply and discharge of the refrigerant can be seen from Fig. 9, in which the injection plate 80 and the injection tube 81 and the suction tube 82 are shown.
  • the distributor plate 75 has two openings 76c and 77c, which are separated from each other by the web 78c.
  • a refrigerant inlet opening 83 is provided, which is arranged with an aligned refrigerant opening 84 in the injection tube 81.
  • the refrigerant inlet breakthrough 83, as well as the Kätsesch takebruch 84 are formed by flangeless holes, but also a configuration according to the embodiment of Fig. 1 may be provided, i. the distributor plate 75 has protruding edges which project into the injection tube 81 and terminate flush with the refrigerant passage 84. According to a further variant, the edges can also protrude into the interior of the injection tube 81, so that an intensified mixing of the liquid and gaseous phase of the refrigerant takes place.
  • the free flow cross sections correspond to the o.g. Formula.
  • a refrigerant discharge opening 85 in the injection plate 80 and an aligned refrigerant opening 86 are arranged in the suction pipe 82.
  • the apertures 85, 86 formed as bores in the present case can be formed as shown in FIG.
  • the injection tube 81 and the suction tube 82 are sealingly and pressure-resistant soldered to the injection plate 80, as well as the other parts 75, 74 and 71c.
  • Fig. 10 shows a section through the deflection channel 79d.
  • the refrigerant coming from below flows upward into the deflection passage 79d, in which it is deflected to the right (depth direction) and enters the rear portion of the flat tube 71d in which it flows from top to bottom. It is thus provided in each case a simple deflection in the width and in the depth.
  • a plurality of passage openings from the injection tube 81 into the collecting box and from the collecting box to the suction tube 82 are required, in the present case one per U-shaped bent flat tube 71.
  • the free passage openings are formed starting from the injection pipe according to the formula mentioned in the first embodiment including the above values for a, b and c.
  • Fig. 11 shows an embodiment of an evaporator 90 having a plurality of U-shaped bent flat tubes 91a, 91b, 91c, etc., which allows a double deflection in width and a simple deflection in depth.
  • the distributor plate 93 is formed such that for the deflection in the width two openings 96 and 98 are interconnected via a transverse channel 101, wherein the apertures 96, 98 and the transverse channel form an H-shaped opening in the distributor plate 93.
  • a long deflection channel 102 is provided, which corresponds to the deflection channel 79 of the previously described evaporator.
  • the refrigerant flow is shown in Fig.
  • the refrigerant at A enters the front part of the left leg of the flat tube 91a, flows downward, becomes wide deflected, flows back up and exits the flat tube 91a, in an opening of the distributor plate 93, flows along the arrow B through the transverse channel 101 and enters the adjacent flat tube 91 b, which flows through it. From there it passes into the deflection channel 102 and, following the arrow C, is directed into the rear part of the flat tube 91 b, which it flows through counter to the throughflow direction of the front part.
  • the refrigerant passes to the first flat tube 91a, which also flows through it opposite to the flow direction of the front part, and exits at D again, from where it enters the suction tube (not shown).
  • the design of injection and suction pipe corresponds to that of the previously described evaporator, ie the diameter of the passage openings of the leads are formed according to the above formula.
  • Fig. 12 shows a variant of the evaporator of Fig. 11, wherein the individual units are arranged in mirror image to each other. As indicated in the region of the leftmost, adjacent deflection channels, an H-shape of the opening in the distributor plate is also possible in this area, so that a Käftesch s between adjacent units in the region of the deflection in depth is possible.
  • FIG. 13 shows a variant of the evaporator of FIG. 12, wherein the subdivisions differ in depth.
  • the design of the injection tube including the dimensions of passage openings in turn corresponds to that of FIG. 1.
  • the opening in the distributor plate is in this case preferably H-shaped with a widened web for the refrigerant inlet or outlet formed.
  • FIGS. 14 to 26 show a further heat exchanger and a variant for this purpose, in which the design of the injection tube and the passage openings can be made in accordance with the exemplary embodiments described above.
  • the heat exchanger illustrated in FIGS. 14 to 24 is an evaporator for a motor vehicle air conditioning system and has a tubular supply line 1001 and a tubular discharge line 1002.
  • the two lines 1001 and 1002 are arranged parallel to one another in a longitudinal direction of the evaporator above a collecting box 1003 extending over the entire length of the evaporator. Beyond the collecting tank 1003 supply and discharge are continued to a common flange plate 1004, via which they are connected to the other air conditioning system of the vehicle (not shown).
  • the lines 1001 and 1002 In the area of continuations 1001a, 1002a between collection box 1003 and flange plate 1004, the lines 1001 and 1002 have a number of kinks and bends, whereby they are adapted to the individual geometry of the installation space in the vehicle.
  • an overflow pipe 1005 is furthermore arranged above the collecting tank 1003 at the latter and extends over the entire width of the evaporator.
  • the overflow tube 1005 is than at its two ends each closed Pipe section formed. The diameter of the passage openings is formed according to the formula mentioned in the first embodiment.
  • the collecting tank 1003 On the underside of the collecting tank 1003 is a plurality of U-shaped bent flat tubes 1006, here twenty, arranged, the leg heights of the U-shaped flat tubes 1006 plus the collection box height and the injection tube, overflow or Saugrohrau joint of the overall height of the evaporator.
  • Each of the flat tubes 1006 has a plurality of chambers or channels 1006a (see cross section through one of the flat tube legs of FIG. 16).
  • only half of the chambers 1006a of each of the flat tubes 1006 forms a flow path together or is arranged hydraulically in parallel. In the direction of the air flow, that is to say perpendicular to the plane of the drawing according to FIG. 14, two flow paths in each flat tube 1006 are thus located one behind the other in depth.
  • the flat tubes 1006 are each inserted with their ends in apertures 1007a of a bottom plate 1007 (see FIG. 15) and soldered thereto.
  • a central, longitudinally extending web 1007b of the bottom plate 1007 separates the two groups of chambers 1006a of the flat tubes 1006 from each other.
  • a distributor plate 1008 (see FIG. 12) is placed flat on the lower base plate 1007 and soldered to the same over the entire surface but at least along closed edge lines.
  • the distributor plate 1008 has a number of slot-like openings 1008 a, which are partially aligned with the openings 1007 a of the bottom plate 1007 and thus with the end faces of the flat tubes 1006. Not aligned portions of the apertures, eg H-shaped apertures 1008b of the manifold plate 1008, are intended to interconnect various flow paths.
  • the H-shaped openings shown here each connect two adjacent flat tubes 1006 or four flow paths with each other.
  • injection plate 1009 of the header 1003 is soldered flush to the distributor plate 1008.
  • the injection plate 1009 has a number of circular passages 1009a made by punching each on the same side. The punching creates on the side facing away from the distributor plate in each case a protruding collar 1009b (see side view of the distributor plate in Fig. 13), by means of which the supply line 1001, i. the injection tube, the drain 1002, i. the suction tube, and the overflow 1005 are particularly easy to attach.
  • the tubular lines 1001, 1002 and 1005 are each provided with bores which correspond to the above-described passages 1009a of the injection plate 1009. In the course of assembly of the evaporator, the lines are thus attached to the collar 1009b and soldered cold-resistant, whereby at the same time a mechanically secure connection between the collection box and pipes is made.
  • the distances of the farthest holes result in an effective length of the respective lines 1001, 1002 and 1005.
  • An effective in terms of heat exchange evaporator length is meaningful defined as the largest distance between two flow paths in the width direction of the evaporator. It follows that in the present embodiment, the effective length of the feed line 1001 is less than 40% of the effective evaporator width.
  • the evaporator works as follows:
  • a high-pressure liquid consisting of liquid and gaseous phase refrigerant is supplied to the evaporator (in the present case carbon dioxide, ie R744).
  • the refrigerant enters through the passages 1009a or holes of the feed line 1001 into a first group of eight flow paths. There is a transfer to the eight corresponding, opposite flow paths in the H-shaped apertures, each with a first and a subsequent continuous flow path to the same flat tube belong (“transfer to the depth") After passing sixteen of the total of 40 flow paths of the evaporator enters the refrigerant through slightly larger holes in the overflow pipe 1005 a. These sixteen first flow paths, which correspond to the first eight flat tubes from the right according to FIG. 14, are thus grouped into a first section.
  • the overflow pipe 1005 has the function of an intermediate collector, so that the refrigerant of the various flow paths is remixed at the same time it flows to the left as shown in FIG. 14, wherein the flow rate is already significantly increased compared to the supply line 1001.
  • the remaining twelve flat tubes form a second group or a second section of a total of twenty-four flow paths 1006.
  • the inlet from the overflow pipe 1005 into the first twelve flow paths of the second section and then into the second twelve flow paths of the second section by means of the H-shaped openings of the distributor plate.
  • the higher number of flow paths of the second section is accommodated in the overflow tube 1005 in that the diameter of the passages 1009a of the second section is smaller than the diameter of the eight passages of the first section.
  • substantially vaporized and expanded refrigerant from a particularly large twelve passages enters the discharge line 1002, in order to be supplied from there to the further refrigeration cycle.
  • the flat tubes 1006 are surrounded by air, which is subsequently used for air conditioning of a vehicle interior.
  • FIGS. 25 and 26 differs from the previous exemplary embodiment only in the design of the passages 1009a 'and their corresponding bores in the lines 1001, 1002 and 1005, as well as in the shape of the distributor plate 1008'.
  • some of the openings 1009a ' are each formed so that two flow paths 1006a are directly charged with refrigerant by a single bore.
  • two flow paths per section of the evaporator are flowed through, for which H-shaped openings 1008a 'are also responsible for the transition between the flow paths.
  • the passage openings in the lines 1001 and 1005 are formed according to the formula mentioned in the first embodiment, so that a very uniform temperature distribution over the entire evaporator width is possible.

Landscapes

  • 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)
EP20060025336 2005-12-13 2006-12-07 Echangeur de chaleur, en particulier évaporateur Withdrawn EP1798505A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005059920.6A DE102005059920B4 (de) 2005-12-13 2005-12-13 Wärmetauscher, insbesondere Verdampfer

Publications (1)

Publication Number Publication Date
EP1798505A2 true EP1798505A2 (fr) 2007-06-20

Family

ID=37847129

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060025336 Withdrawn EP1798505A2 (fr) 2005-12-13 2006-12-07 Echangeur de chaleur, en particulier évaporateur

Country Status (2)

Country Link
EP (1) EP1798505A2 (fr)
DE (1) DE102005059920B4 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108551762A (zh) * 2016-01-21 2018-09-18 三星电子株式会社 空调器
EP3341669A4 (fr) * 2016-01-21 2018-10-31 Samsung Electronics Co., Ltd. Climatiseur
US20210356144A1 (en) * 2020-05-14 2021-11-18 Samsung Electronics Co., Ltd. Distributor and air conditioner including the same

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006035951B4 (de) * 2006-07-31 2019-09-05 Mahle International Gmbh Wärmetauscher in Plattenbauweise, insbesondere Verdampfer und Vorrichtung zur Montage eines Sammlers in Plattenbauweise
JP5796563B2 (ja) * 2011-11-29 2015-10-21 株式会社デンソー 熱交換器
WO2020066462A1 (fr) * 2018-09-28 2020-04-02 ダイキン工業株式会社 Échangeur de chaleur

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1958840B2 (de) * 1969-11-24 1972-07-13 GEA Luftkühlergesellschaft Happel GmbH & Co KG, 4630 Bochum Waermetauschelement zum aufheizen oder kuehlen von gasen, insbesondere luft, fuer klima- und trocknungsanlagen
JP2767963B2 (ja) * 1990-03-08 1998-06-25 三菱電機株式会社 気液二相流体の分配器
DE9403848U1 (de) * 1994-03-08 1994-05-11 Behr Gmbh & Co, 70469 Stuttgart Wärmetauscher für ein Kraftfahrzeug
DE60010377T2 (de) 1999-07-02 2004-09-16 Denso Corp., Kariya Kältemittelverdampfer mit Kältemittelverteilung
EP2026028B1 (fr) 2001-12-21 2018-07-18 MAHLE Behr GmbH & Co. KG Échangeur de chaleur, en particulier pour véhicule automobile
US6814136B2 (en) 2002-08-06 2004-11-09 Visteon Global Technologies, Inc. Perforated tube flow distributor
JP4679827B2 (ja) * 2003-06-23 2011-05-11 株式会社デンソー 熱交換器
JP2005030741A (ja) * 2003-07-11 2005-02-03 Denso Corp 熱交換器
FR2865028B1 (fr) * 2004-01-12 2006-12-29 Ziepack Echangeur thermique et module d'echange s'y rapportant

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108551762A (zh) * 2016-01-21 2018-09-18 三星电子株式会社 空调器
EP3341669A4 (fr) * 2016-01-21 2018-10-31 Samsung Electronics Co., Ltd. Climatiseur
US10907903B2 (en) 2016-01-21 2021-02-02 Samsung Electronics Co., Ltd. Air conditioner with flow direction changing mechanism
US20210356144A1 (en) * 2020-05-14 2021-11-18 Samsung Electronics Co., Ltd. Distributor and air conditioner including the same

Also Published As

Publication number Publication date
DE102005059920B4 (de) 2019-07-04
DE102005059920A1 (de) 2007-06-14

Similar Documents

Publication Publication Date Title
EP1459027B1 (fr) Echangeur thermique notamment destine a un vehicule
EP1798506B1 (fr) Evaporateur
DE69219107T2 (de) Verdampfer
EP2150757B1 (fr) Échangeur de chaleur
DE69428219T2 (de) Plattenwärmetauscher
DE602006000470T2 (de) Luftgekühlter Ölkühler
DE69911131T2 (de) Wärmetauscher
EP2232183B1 (fr) Échangeur de chaleur, en particulier radiateur pour des véhicules automobiles
EP2135025B1 (fr) Échangeur de chaleur pour la vaporisation d'une partie liquide d'un milieu, pourvu d'une dérivation pour une partie à l'état de vapeur du milieu
DE10314782A1 (de) Wärmetauscher für den Wärmeaustausch zwischen einem inneren und einem äußeren Fluid und Verfahren zur Herstellung desselben
WO2005038375A1 (fr) Echangeur de chaleur, en particulier pour vehicules automobiles
DE102005059920B4 (de) Wärmetauscher, insbesondere Verdampfer
DE69500676T2 (de) Wärmetauscher
DE102004002252B4 (de) Wärmeübertrager für Fahrzeuge
EP1411310B1 (fr) Echangeur de chaleur à structure en serpentin
DE19719259A1 (de) Flachrohrwärmetauscher für Kraftfahrzeuge mit an Krägen eines Rohrbodens gehaltenen Flachrohren
EP1643202B1 (fr) Echangeur de chaleur
EP1798507A2 (fr) Echangeur de chaleur, en particulier évaporateur
EP1717530B1 (fr) Echangeur de chaleur, en particulier évaporateur arrière pour véhicule automobile
WO2006094583A1 (fr) Echangeur thermique, en particulier evaporateur d'une installation de climatisation pour vehicules
DE102006004983A1 (de) Wärmetauscher, insbesondere Verdampfer einer Kraftfahrzeug-Klimaanlage
EP1816426B1 (fr) Dispositif de transfert de chaleur, en particulier d'un évaporateur arrière dans un véhicule automobile
DE69319108T2 (de) Kältemittelverdampfer
DE102006059289A1 (de) Wärmetauscher, insbesondere Verdampfer
DE102009017813A1 (de) Wärmeübertrager

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20110701