EP1382926B1 - Evaporateur pour système de climatisation de véhicules automobiles - Google Patents

Evaporateur pour système de climatisation de véhicules automobiles Download PDF

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Publication number
EP1382926B1
EP1382926B1 EP03015967.7A EP03015967A EP1382926B1 EP 1382926 B1 EP1382926 B1 EP 1382926B1 EP 03015967 A EP03015967 A EP 03015967A EP 1382926 B1 EP1382926 B1 EP 1382926B1
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Prior art keywords
evaporator
refrigerant
collecting
evaporator according
collecting box
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 - Lifetime
Application number
EP03015967.7A
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German (de)
English (en)
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EP1382926A1 (fr
Inventor
Gottfried DÜRR
Wolfgang Seewald
Matthias Jung
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
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Mahle Behr GmbH and Co KG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—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
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • 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
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions

Definitions

  • the invention relates to an evaporator of an air conditioner for a motor vehicle according to claim 1.
  • the usual today evaporator such as disc evaporator and flat tube evaporator are installed vertically in the air conditioner or the vehicle, ie with vertical tubes.
  • Common flat tube evaporator, z. B. known by the DE-A 198 26 881 the applicant, are formed in two rows, ie with two rows of flat tubes, which are successively or successively flowed around by air.
  • the ends of the headers open into headers, which are each divided into two chambers which receive the ends of the flat tubes.
  • the refrigerant is deflected once in the depth, that is opposite to the direction of air flow in double-flow.
  • Such flat tube evaporators have a height H, measured in the longitudinal direction of the tubes, and a width B, measured transversely to the tube longitudinal direction.
  • the product of height H and width B gives the face of the evaporator.
  • the refrigerant can - in addition to the deflection in the depth - be deflected in width.
  • This evaporator design is known to have a height to width ratio of about 0.5 to 2.0, that is, for the lowest evaporators of this type, the height is about half the width.
  • the invention provides a horizontal evaporator, in which the flow channels are arranged approximately horizontally in the installation position and the lateral collecting chambers are arranged approximately vertically or flowed through.
  • Vertical does not mean strictly vertical, since the evaporators in air conditioners are sometimes arranged slightly inclined. Such an arrangement should also be encompassed by the term approximately vertically.
  • a ratio of height to width in the range of 1: 3 to 1: 6 or a ratio of width to height in the range of about 3 to 6 and more, that is advantageously up to 7, 8, 9m or 10 or more can be realized without the performance of the evaporator decreases.
  • Opposite the Construction with vertical flow channels even results in a performance gain.
  • the advantage of a smaller number of parts over the known construction with vertical flow channels since the inventive evaporator longer, but has fewer tubes or flow channels. This reduces the manufacturing costs.
  • the evaporator is designed as a disk or flat tube evaporator, wherein the flat tube evaporator proves to be particularly advantageous. It can in principle be built with almost the same or similar components as the aforementioned prior art of the applicant - but in a horizontal design with correspondingly low height and large width. By arranging partition walls in the collecting tanks, a double or multiple flooding with deflection of the refrigerant in the depth and the height can be made possible, which causes a favorable temperature distribution for the exiting air from the evaporator.
  • the injection of the refrigerant takes place in the underlying tubes or in the underlying of the collection chamber.
  • the refrigerant is then aspirated in the upper region in the vaporous or superheated state. This makes it possible to operate the evaporator according to the invention also with a conventional expansion valve.
  • the inlet and outlet openings can both be arranged at the bottom of a collection box, then the overflow openings for the deflection of the refrigerant in the depth in the upper region of the vertical partition. This prevents liquid refrigerant from being sucked out.
  • the inlet and outlet openings can both be arranged at the top of a collecting box, then the overflow openings for the deflection of the refrigerant in the depth in the lower region of the vertical partition. This ensures that only vaporous refrigerant is sucked out.
  • spray water grids for collecting the sprayed condensed water can be arranged on the air outlet end region of the evaporator.
  • At least one or more recesses are provided, such as a plurality of elongated recesses. It may be expedient if the recesses are arranged in the side part substantially on the down or on the outflow side. In another embodiment, it may also be expedient if the recess / the recesses lie on the inflow side or at least partially over both regions, that is to say outflow side or inlet or inflow side.
  • Fig. 1, 1st A and 1 b show a double-row, double-flow flowed through flat-tube evaporator 1 in a horizontal installation position, that is with lying flat tubes, in a view from below.
  • the air flow direction is indicated by the arrow L.
  • Fig. 1a shows the evaporator 1 with respect to its end face, which is defined by the height H and the width B.
  • the front side of the evaporator 1 shows a total of ten flat tubes 2, between which corrugated fins 3 are arranged.
  • the flat tubes 2 open on both sides in collecting tanks 4, 5, which are each divided by a longitudinal partition wall 6 into two chambers 7, 8 (the subdivision of the chamber 5 is in Fig. 1 and 1 a not recognizable).
  • the first flat tube row 9 opens into the chamber 7 and the opposite (concealed), while the second flat tube row 10 (hidden), represented by arrows 10, in the chamber 8 and the opposite chamber (hidden) opens.
  • the lying in the installation position side panel 12 has three elongated recesses 13, which partially share the view of the first row of flat tubes 9. These recesses 13 are provided for the drainage of condensate, which forms in humid air on the evaporator surface.
  • the evaporator 1 has two refrigerant connections, namely a refrigerant inlet 14 and a refrigerant outlet 15, which are connected via a refrigerant supply line 16 and a refrigerant discharge line 17 to an expansion valve 18 ( Fig. 1b ).
  • the injection of the refrigerant is thus at the bottom of the evaporator 1, and first in the air flow direction (arrow L) lying behind pipe row 10 is flowed through by refrigerant.
  • the refrigerant then passes into the rear chamber 8 of the collecting tank 4.
  • In the Partition 6 are arranged through openings 19, through which the refrigerant in the upstream in the direction of air flow chamber 7 (deflection in depth). From there it enters the front row of flat tubes 9 and then into the collecting box 5, the rear chamber 5a and front chamber 5b in Fig. 1b are recognizable.
  • the refrigerant is sucked in the upper region of the chamber 5b via the connecting piece 15.
  • the flat tube evaporator 1 is - as already mentioned - lying, so as shown in the drawing, installed in the air conditioning of the motor vehicle and the air to be cooled in the direction of the arrow L flows. In this respect results for the flow between refrigerant and air, a cross counterflow.
  • the flat tube evaporator has in the illustrated embodiment, a width B of 500 mm, which width includes the two headers 4, 5 with.
  • the height H of the evaporator is 120 mm. This results in a ratio of width B to height H of 4.16.
  • the Figure 1c shows an evaporator in a view from below, in which the same reference numerals are used in the same components, as in FIG. 1 a.
  • the openings 13 'for condensate drain on the other side in comparison to the embodiment of FIG. 1a are arranged.
  • the outlet 13 for the condensate arranged on the air inflow side in the side part is the outlet 13 for the condensate arranged on the air inflow side in the side part, whereas in the embodiment of the Figure 1c the drain 13 'is arranged on the outflow side or outflow side in the side part.
  • the drain for condensate condensing on the surface of the evaporator may also be on both the upstream and downstream sides of the side member.
  • the recesses are formed by elongated cutouts, but they can also be designed as round cutouts or other cutouts.
  • Fig. 2 shows a modified embodiment of a flat tube evaporator tube 20 in a schematic representation, ie tubes and ribs are not shown, but essentially replaced by flow arrows.
  • the flat tube evaporator 20 has - similar to the embodiment according to Fig. 1 - A horizontal flat tube bundle 21, which has a front tube bundle half 21 a and a rear tube bundle half 21 b. However, the air flowing through the flat tube evaporator 20 in the direction of the arrow L, but first meets the rear flat tube bundle half 21 b.
  • On both sides of the flat tube bundle 21 collector boxes 22, 23 are arranged, in which open the flat tubes, not shown, of the bundle 21.
  • the left in the drawing collection box 22 is divided by a continuous, vertically arranged partition wall 24 in a front chamber 22a and in a rear chamber 22b, wherein the front chamber 22a has an inlet opening 25 and the rear chamber 22b has an outlet opening 26 for the refrigerant , Inlet and outlet openings 25, 26 are thus both on the lower side of the flat tube evaporator 20, which is in the position as shown in the drawing, installed in the vehicle.
  • the right in the drawing collection box 23 has a vertically arranged partition wall 27, which divides the collection box 23 into a front chamber 23 a and 23 b in a rear chamber.
  • the partition wall 27 has in its upper region, preferably in its upper half, three overflow openings 28 which connect the two adjacent chambers 23a, 23b to one another (fewer or more openings are also possible).
  • the flat tube evaporator 20 is traversed by double-flow of refrigerant, in the following manner: the refrigerant enters the direction of the arrow E via the opening 25 in the front chamber 22 a and then flows through the front tube bundle 21 a, the arrows V, in the Chamber 23a on the right side of the evaporator 20.
  • the refrigerant enters the chamber 23a in a liquid state and partially becomes en route to the chamber 23a evaporates, that is, a portion of the inflowing into the chamber 23 a refrigerant is still liquid. Therefore, the overflow openings 28 are arranged in the upper portion of the partition wall 27, so that an overflow of liquid refrigerant from the front chamber 23 a into the rear chamber 23 b is prevented.
  • refrigerant predominantly passes through the overflow openings 28 into the chamber 23b in the vapor state - here, in the direction of the arrow U, the deflection of the refrigerant takes place "in the depth", ie counter to the air flow direction L.
  • the refrigerant then enters the chamber 23b the rear tube bundle 21 b and flows through this in the direction of arrow R until it enters the outlet chamber 22b. From there, the refrigerant exits in the vapor state through the outlet opening 26 in the lower region of the chamber 22 b from the flat tube evaporator 20.
  • FIG. 2 A further, not shown embodiment of the flat tube evaporator is possible, with the top inlet E and outlet A (corresponding Fig. 2 ).
  • the evaporator 20 according to Fig. 2 would be rotated about its longitudinal axis by 180 °, so that the inlet opening 25 and the outlet opening 26 would be at the top and the overflow openings 28 would come to lie in the lower half of the partition wall 27.
  • the liquid refrigerant would then remain substantially at the bottom of the evaporator, so that only vaporous refrigerant would be sucked.
  • Fig. 3 shows a performance comparison between conventional evaporator design with vertical tubes and inventive design with horizontal tubes.
  • the performance of the evaporator is applied over the installed face including the collector - based on the FIGS. 1a and 2a
  • the end face corresponds to the product B x H.
  • the solid curve K clearly below the curve E, refers to evaporators of conventional construction, ie with vertical tubes, horizontally extending headers within a ratio of B to H of 2.9 to 5.4.
  • the reduced power compared to the construction according to the invention results from a multiplicity of refrigerant deflections and the resulting refrigerant-side pressure drop.
  • Fig. 4 shows another diagram in which the specific usable space, ie the ratio of usable space to installation space is plotted over the free end face (this is the product B 'x H, where B' is the width reduced by the height of the collecting boxes)
  • the upper dashed curve E corresponds to the construction according to the invention
  • the underlying horizontally extending curve K corresponds to the conventional construction with vertical tubes.
  • Fig. 5 shows another diagram in which the air-side pressure drop across the evaporator is plotted over the total end face including the surface of the collector.
  • the dashed line E again the inventive and the solid line K denotes the conventional Construction.
  • the pressure drop for the invention is therefore much cheaper. This advantage in favor of the invention results in turn due to the lower proportions of the collecting boxes on the entire end face in the invention.

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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 (9)

  1. Evaporateur pour des systèmes de climatisation de véhicules automobiles, se composant de conduits d'écoulement s'étendant parallèlement et guidant un fluide frigorigène, se composant d'ailettes sollicitées par de l'air et disposées entre les conduits d'écoulement, se composant également au moins d'une chambre collectrice comportant des ouvertures d'entrée et / ou de sortie de fluide frigorigène, où l'évaporateur présente un bloc ayant une hauteur H mesurée dans le sens vertical et une largeur B mesurée dans le sens horizontal, bloc dont le produit H x B donne la surface frontale de l'évaporateur, où les conduits d'écoulement se trouvant en position de montage, c'est-à-dire pratiquement de manière horizontale, et la chambre ou les chambres collectrice(s) se trouvant dans le sens vertical, sont disposés en pouvant être traversés, caractérisé en ce que le rapport V de la largeur B, sur la hauteur H, présente la plage suivants : 2 , 5 ≤ V ≤ 6 , préférence 3 , 5 ≤ V ≤ 5 ,
    Figure imgb0003
     où les conduits d'écoulement sont conçus comme des tubes plats (2), les chambres collectrices étant conçues comme des bacs collecteurs (4, 5 ; 22, 23) dans lesquels débouchent les tubes plats (2), ledit évaporateur comprenant deux rangées (9, 10) de tubes plats (2) et comprenant des bacs collecteurs (4, 5) disposés des deux côtés des extrémités des tubes plats, bacs collecteurs qui sont subdivisés à chaque fois en deux chambres (7, 8 ; 5a, 5b) pour chaque rangée de tubes plats (9, 10), où des parties latérales (11, 12) sont disposées des deux côtés des rangées de tubes plats (9, 10), où la partie latérale (12) se trouvant en bas présente des évidements (13) pour l'évacuation de condensat.
  2. Evaporateur selon la revendication 1, caractérisé en ce que l'ouverture d'entrée de fluide frigorigène (14) est disposée dans la zone inférieure d'une chambre (5a) d'un bac collecteur (5).
  3. Evaporateur selon la revendication 1 ou 2, caractérisé en ce que l'ouverture de sortie de fluide frigorigène (15) est disposée dans la zone supérieure d'une chambre (5b) d'un bac collecteur (5).
  4. Evaporateur selon la revendication 2 ou 3, caractérisé en ce que des ouvertures d'entrée et de sortie de fluide frigorigène (14, 15) sont disposées sur le même bac collecteur (5).
  5. Evaporateur selon l'une quelconque des revendications 1 à 4, caractérisé par un double flux traversant (V, R) avec un retour de flux U du fluide frigorigène, retour de flux qui se produit en profondeur, c'est-à-dire dans le sens opposé à la direction d'écoulement d'air L.
  6. Evaporateur selon la revendication 4 ou 5, caractérisé en ce que des ouvertures d'entrée et de sortie de fluide frigorigène (25, 26) sont disposées dans la zone inférieure d'un bac collecteur (22), et en ce que l'autre bac collecteur (23) présente une paroi de séparation (27) verticale comportant des ouvertures de trop-plein (28) qui sont disposées dans la zone supérieure.
  7. Evaporateur selon la revendication 4 ou 5, caractérisé en ce que les ouvertures d'entrée et de sortie de fluide frigorigène sont disposées dans la zone supérieure d'un bac collecteur, et en ce que l'autre bac collecteur présente une paroi de séparation verticale comportant des ouvertures de trop-plein qui sont disposées dans la zone inférieure.
  8. Evaporateur selon l'une quelconque des revendications précédentes, caractérisé en ce que des évidements prévus pour l'évacuation de condensat sont disposés de préférence dans la partie latérale, sur le côté de flux d'air sortant.
  9. Evaporateur selon l'une quelconque des revendications précédentes, caractérisé en ce que des évidements prévus pour l'évacuation de condensat sont disposés de préférence dans la partie latérale, sur le côté de flux d'air entrant.
EP03015967.7A 2002-07-15 2003-07-14 Evaporateur pour système de climatisation de véhicules automobiles Expired - Lifetime EP1382926B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2002131918 DE10231918A1 (de) 2002-07-15 2002-07-15 Verdampfer für Kfz-Klimaanlagen
DE10231918 2002-07-15

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EP1382926A1 EP1382926A1 (fr) 2004-01-21
EP1382926B1 true EP1382926B1 (fr) 2017-05-10

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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4679410A (en) * 1986-10-30 1987-07-14 General Motors Corporation Integral evaporator and accumulator for air conditioning system

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4220823C2 (de) * 1992-06-25 1996-08-29 Thermal Waerme Kaelte Klima Heizungswärmetauscher für Personenkraftwagen mit mindestens zwei Teilwärmetauschern
JPH116693A (ja) * 1997-04-23 1999-01-12 Denso Corp 車両空調用熱交換器
DE19826881B4 (de) * 1998-06-17 2008-01-03 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Verdampfer
AU2002351617A1 (en) * 2001-12-27 2003-07-15 Dana Canada Corporation Heat exchanger with internal slotted manifold

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4679410A (en) * 1986-10-30 1987-07-14 General Motors Corporation Integral evaporator and accumulator for air conditioning system

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DE10231918A1 (de) 2004-01-29
EP1382926A1 (fr) 2004-01-21

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