EP1712868B1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
EP1712868B1
EP1712868B1 EP06005287.5A EP06005287A EP1712868B1 EP 1712868 B1 EP1712868 B1 EP 1712868B1 EP 06005287 A EP06005287 A EP 06005287A EP 1712868 B1 EP1712868 B1 EP 1712868B1
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EP
European Patent Office
Prior art keywords
heat exchanger
aperture
exchanger according
refrigerant
blocks
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Application number
EP06005287.5A
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German (de)
French (fr)
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EP1712868A3 (en
EP1712868A2 (en
Inventor
Gottfried Dipl.-Ing. Dürr
Boris Dr.-Ing. Kerler
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Mahle Behr GmbH and Co KG
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Mahle Behr GmbH and Co KG
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Publication of EP1712868A2 publication Critical patent/EP1712868A2/en
Publication of EP1712868A3 publication Critical patent/EP1712868A3/en
Application granted granted Critical
Publication of EP1712868B1 publication Critical patent/EP1712868B1/en
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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
    • F28D1/04—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
    • F28F9/0202—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
    • 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
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • 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, according to the preamble of claim 1.
  • a refrigerant evaporator with refrigerant distribution which has four blocks. Between the individual blocks in each case a plurality of flat tubes and arranged therebetween corrugated fins are provided, which are flowed around by the outer fluid.
  • the refrigerant evaporator is configured such that the first and second blocks are adjacent to each other in the width direction, perpendicular to a flow direction of an outer fluid, and the third and fourth blocks are arranged adjacent to each other in the width direction, the first block on an immediately downstream side of the fourth block is arranged in the flow direction of the outer fluid, while the second block is arranged on a direct downstream side of the third block in the flow direction of the outer fluid.
  • throttles for reducing the refrigerant passage cross section are provided, that is, in all the blocks flowed through from the bottom up.
  • the throttle holes that liquid refrigerant accumulates in front of the throttles, entrained with gaseous refrigerant due to the high refrigerant flow rate, and mixed with the same, resulting in a more uniform distribution of liquid and gaseous refrigerant.
  • the throttling holes also put some effort into the production of the evaporator
  • the throttle holes cause a narrowing of the flow cross-section, which can result in an increased pressure drop in the evaporator and thus a deterioration of performance and efficiency of the air conditioner.
  • undesirable noise may occur at such throttle holes.
  • a heat exchanger in particular for a motor vehicle, with a plurality of blocks, wherein in each block a plurality of tubes between two collecting sections are arranged, one of which is above and the other below, and at least one aperture is provided, wherein the diaphragm (s) is (are) arranged exclusively in or between blocks located in the flow path of the medium flowing through the heat exchanger.
  • the orifice (s) is (are) located exclusively in or on the passage to the last bottom flowed through block or on the passage to the penultimate block.
  • the orifice (s) can hereby ensure that flows through all the tubes of the last block, a balanced ratio of liquid and gaseous refrigerant from bottom to top.
  • the diaphragm is arranged directly on the transition, particularly preferably on Transfer from penultimate to last collection section and possibly also at the transfer from the third last to the penultimate collection section.
  • the provision of the orifices in the rear region of the heat exchanger results in a significant improvement in the distribution of refrigerant in the last and possibly second-to-last block, as opposed to an arrangement of two diaphragms each of a partition, ie the transition from the third last block to the penultimate block and the transition from the penultimate block to the last block of the heat exchanger, installation in the wrong collection box can be avoided, ie the process reliability is increased.
  • the heat exchanger preferably has six blocks. These are arranged in two rows and are preferably flowed through in countercurrent operation. In this case, the individual blocks are flowed through in such a way that the respective adjacent blocks in the opposite direction, i. from top to bottom or from bottom to top, to be flowed through.
  • the refrigerant supply and removal is preferably arranged on a narrow side of the evaporator, particularly preferably on the top, but also a longitudinal refrigerant feed and removal is possible.
  • the narrow-side inlet and outlet allows the provision of the openings in a substantially flat plate.
  • a more uniform flow formation of the injected refrigerant takes place. Also space advantages can result.
  • the aperture can be polygonal, in particular rectangular, rounded polygonal, circular, elliptical or oval. Particularly preferably, it may have a substantially rectangular shape with a rounded and slightly oblique narrow side.
  • the aperture is preferably arranged substantially centrally, however, for an increased refrigerant passage, for example, a downwardly offset or for a reduced refrigerant passage, for example, an upwardly offset arrangement of the aperture can be provided. Also can be optimized by such a staggered arrangement, the mixing quality of the two phases.
  • the aperture preferably occupies an area of at most 95%, particularly preferably at most 50% and at least 1%, in particular preferably at least 5%, of the free mean flow cross-section in the corresponding collection section.
  • This opening ratio leads to a good atomization of the liquid refrigerant collecting in front of the orifice, so that the refrigerant distribution and thus also the temperature distribution are optimized.
  • values of 2%, 3%, 4%, 5%, 6%, 7%, 8%, 9%, 10%, 11%, 12%, 13%, 14%, 15%, 16% are also conceivable. , 17, 18, 19, 20, 25, 30, 35, 40, 45, 55, 60, 65, 70, 75, 80, 85, 90 % and / or 95% as the start or end value of the interval.
  • the distance between the diaphragms remains the same or even decreases.
  • the apertures in the case of a plurality of successively arranged apertures are preferably larger in the flow direction of the refrigerant, so that the refrigerant distribution is optimized for the tubes. However, they can also become smaller or stay the same.
  • a heat exchanger 1 in this case an evaporator of a motor vehicle, which is connected via an injection pipe 2 and a suction pipe 3 with an expansion element 4, according to the present embodiment from (fluidically seen) six blocks B1-B6, where he two rows, each with three blocks B1-B3 and B4-B6 is formed side by side, and has partition walls for refrigerant guide divided collection boxes 5 (hereinafter referred to as collection sections, a common name is also collector section or collector box), a plurality of arranged between the manifolds 5 flat tubes 6 and between the flat tubes 6 arranged corrugated fins (not shown) on. In each case, two collecting sections and the flat tubes 6 extending therebetween together with corrugated finned plates form a block.
  • the collecting box 5 has laterally each an opening for the injection tube 2 and the suction tube 3 and is in principle of conventional design, ie consisting of a box bottom with two rows of slot-like openings into which the ends of the flat tubes 6 are inserted, an approximately U shaped box part, the said partitions for guiding the flow of refrigerant, side plates for the lateral termination, wherein in one of the two side plates, the openings for the injection pipe 2 and the suction pipe 3 are provided.
  • the present, arranged here below collection box 5 in addition to a diaphragm 7, whose function is explained in more detail later.
  • Block B1 comprises sixteen
  • block B2 is eleven
  • block B3 is sixteen
  • block B4 is sixteen
  • block B5 is eleven
  • block B6 is again sixteen flat tubes 6, whereby the middle blocks B2 and B5 are made somewhat narrower than the outer blocks B1, B3, B4 and B6 ,
  • the injection pipe 2 and the suction pipe 3 are mounted on one of the two side plates of the upper header 5, ie at the upper collecting section of the first block B1 or at the upper collecting section of the last block B6, wherein the heat exchanger 1 is flowed through in countercurrent operation.
  • the flow direction of the refrigerant, in this case R134a, in the evaporator and the air to be cooled on the outside is in the FIGS. 1 and 4 or 2, 3 and 4 illustrated by arrows.
  • the refrigerant is injected into the evaporator 1 in a two-phase state. It leaves the evaporator - depending on the load and control method - if necessary also in superheated, gaseous state.
  • the orifice 7 is arranged between the eleventh last and the twelfth last flat tube 6, ie at the present sixteen flat tubes 6 approximately at the end of the front third of the lower collecting section of the last bottom flowed through block B6.
  • the panel 7 is - in accordance with the attachment of the partitions - in the lower header box 5 present centrally located between two adjacent openings for flat tubes 6 and soldered to the collection box 5.
  • the aperture 8 is arranged substantially centrally between the ends of the inserted flat tubes 6 and the lower wall of the collecting box 5 and has a square shape, wherein the surface of the aperture 8 occupies about 10% of the area of the collecting portion.
  • the orifice 7 With regard to the effectiveness of the orifice 7 are the shape of the evaporator, the hydraulic diameter of the aperture 8, the number of diaphragms and their position in the last lower collection section, which is not directly connected to the suction tube 3, relevant, which is why for an optimization of Temperature distribution these parameters must be considered.
  • the aperture has a circular shape.
  • the shape of the aperture are in particular rectangular (see. Fig. 7b ) or oval / elliptical Shapes possible, wherein the edges of the rectangles may also be rounded (cf. Fig. 7c ).
  • the aperture is arranged in the illustrated variants each approximately centrally between the ends of the flat tubes or the ends of the same receiving passages and the upper portion of the aperture receiving part of the header.
  • a diaphragm 7 may be arranged in a depression which is provided in the part of the collecting tank 5 facing away from the flat tubes.
  • the aperture 7, as in the embodiment described above, is arranged between two adjacent passages. This corresponds to a common installation method used for partitions.
  • the aperture is in Fig. 8 not shown.
  • the injection pipe and / or the suction pipe need not necessarily be connected on the narrow side, but also a longitudinal attachment is possible. It may well happen in a different flow through the heat exchanger, that the last of the refrigerant flowed through from below block, in which the diaphragm is arranged, is not arranged laterally, but for example in the middle.
  • FIGS. 9 and 10 a variant of the heat exchanger not according to the invention is shown, wherein - according to the first embodiment - the heat exchanger in turn has six blocks B1 to B6, which are flowed through in cross-countercurrent operation.
  • the heat exchanger in turn has six blocks B1 to B6, which are flowed through in cross-countercurrent operation.
  • a single aperture 7 (in Fig. 10 exaggerated shown), ie the aperture 7 is arranged in the lower header directly in the same height of the partition in the upper header.
  • the panel 7 may thus correspond in its outer contour of a partition.
  • the diaphragm 7 has an aperture 8, in this case as in FIG Fig. 13 represented in the form of a rectangle with a rounded and slightly beveled narrow side.
  • the aperture size here is about 50% of the total area of the diaphragm in the corresponding area of the collecting tank.
  • a second aperture 7 between the fourth block B4 and the fifth block B5 is arranged, due to the flow path so in the upper header (see Fig. 12 ).
  • the two apertures 7 in the present case have corresponding apertures 8, but also different configurations and arrangements of apertures are possible.

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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)

Description

Die Erfindung betrifft einen Verdampfer, insbesondere für ein Kraftfahrzeug, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to an evaporator, in particular for a motor vehicle, according to the preamble of claim 1.

Aus der EP 1 065 453 B1 ist ein Kältemittelverdampfer mit Kältemittelverteilung bekannt, der vier Blöcke aufweist. Zwischen den einzelnen Blöcken ist jeweils eine Mehrzahl von Flachrohren und von dazwischen angeordneten Wellrippen vorgesehen, die vom äußeren Fluid umströmt werden. Der Kältemittelverdampfer ist derart aufgebaut, dass der erste und der zweite Block benachbart zueinander in Breitenrichtung, senkrecht zu einer Strömungsrichtung eines äußeren Fluid angeordnet sind, und der dritte und vierte Block benachbart zueinander in Breitenrichtung angeordnet sind, wobei der erste Block auf einer unmittelbaren stromabwärtigen Seite des vierten Blocks in Strömungsrichtung des äußeren Fluids angeordnet ist, während der zweite Block auf einer direkten stromabwärtigen Seite des dritten Bocks in Strömungsrichtung des äußeren Fluids angeordnet ist. Dabei sind in einem Verteilungstankabschnitt des zweiten Blocks und einem Verteilungstankabschnitt des vierten Blocks, die jeweils unten angeordnet sind, Drosseln zum Verkleinern des Kältemitteldurchlassquerschnitts vorgesehen, d.h. in allen von unten nach oben durchströmten Blöcken. Dabei bewirken die Drossellöcher, dass sich vor den Drosseln flüssiges Kältemittel sammelt, in Folge der hohen Kältemittelströmungsgeschwindigkeit mit gasförmigem Kältemittel mitgerissen und mit dem selben vermischt wird, weshalb eine gleichmäßigere Verteilung von flüssigem und gasförmigem Kältemittel erfolgt Darüber hinaus stellen jedoch die Drossellöcher auch einen gewissen Aufwand bei der Herstellung des Verdampfers dar. Außerdem bewirken die Drossellöcher eine Verengung des Strömungsquerschnitts, was einen erhöhten Druckabfall im Verdampfer und somit eine Verschlechterung von Leistung und Wirkungsgrad der Klimaanlage zur Folge haben kann. Auch können an derartigen Drossellöchern unerwünschte Geräusche entstehen.From the EP 1 065 453 B1 is known a refrigerant evaporator with refrigerant distribution, which has four blocks. Between the individual blocks in each case a plurality of flat tubes and arranged therebetween corrugated fins are provided, which are flowed around by the outer fluid. The refrigerant evaporator is configured such that the first and second blocks are adjacent to each other in the width direction, perpendicular to a flow direction of an outer fluid, and the third and fourth blocks are arranged adjacent to each other in the width direction, the first block on an immediately downstream side of the fourth block is arranged in the flow direction of the outer fluid, while the second block is arranged on a direct downstream side of the third block in the flow direction of the outer fluid. In this case, in a distribution tank portion of the second block and a distribution tank portion of the fourth block, which are arranged at the bottom, throttles for reducing the refrigerant passage cross section are provided, that is, in all the blocks flowed through from the bottom up. The throttle holes, that liquid refrigerant accumulates in front of the throttles, entrained with gaseous refrigerant due to the high refrigerant flow rate, and mixed with the same, resulting in a more uniform distribution of liquid and gaseous refrigerant. In addition, however, the throttling holes also put some effort into the production of the evaporator In addition, the throttle holes cause a narrowing of the flow cross-section, which can result in an increased pressure drop in the evaporator and thus a deterioration of performance and efficiency of the air conditioner. Also, undesirable noise may occur at such throttle holes.

Es ist daher Aufgabe der Erfindung, einen verbesserten Wärmeübertrager zur Verfügung zu stellen, der die bei Wärmeübertragern nach dem Stand der Technik immanenten Nachteile zumindest zum Teil beseitigt oder wenigstens mindert. Insbesondere ist es die Aufgabe der Erfindung auch bei zweiphasig vorliegendem Kältemittel möglichst kostengünstig eine möglichst gleichmäßige Temperaturverteilung sicherstellen zu können, möglichst ohne Leistung und/oder Wirkungsgrad der Klimaanlage zu verringern.It is therefore the object of the invention to provide an improved heat exchanger which at least partially eliminates or at least reduces the disadvantages inherent in heat exchangers according to the prior art. In particular, it is the object of the invention to be able to ensure as even as possible a temperature distribution which is as even as possible in the case of a two-phase refrigerant, if possible without reducing the power and / or efficiency of the air conditioning system.

Diese Aufgabe wird gelöst durch einen Wärmeübertrager mit den Merkmalen des Anspruchs 1. Vorteilhafte Ausgestaltungen sind Gegenstand der Unteransprüche.This object is achieved by a heat exchanger with the features of claim 1. Advantageous embodiments are the subject of the dependent claims.

Erfindungsgemäß ist ein Wärmeübertrager vorgesehen, insbesondere für ein Kraftfahrzeug, mit mehreren Blöcken, wobei in den einzelnen Blöcken jeweils eine Mehrzahl von Rohren zwischen zwei Sammelabschnitten angeordnet sind, von denen einer oben und der andere unten angeordnet ist, und mindestens eine Blende vorgesehen ist, wobei die Blende(n) ausschließlich in oder zwischen, in Strömungsweg des den Wärmeübertrager durchströmenden Mediums gesehen, hinten liegenden Blöcken angeordnet ist (sind). Die Blende(n) ist (sind) ausschließlich im oder am Übertritt zum letzten von unten her durchströmten Block oder am Übertritt zum vorletzten Block angeordnet. Die Blende(n) können hierbei sicherstellen, dass durch sämtliche Rohre des letzten Blocks, ein jeweils ausgewogenes Verhältnis aus flüssigem und gasförmigem Kältemittel von unten nach oben strömt. Dadurch kann eine besonders gleichmäßige Temperaturverteilung sichergestellt werden. Das Gegenteil, also eine Entmischung und bevorzugte Durchströmung einzelner Rohre mit flüssigem bzw. gasförmigem Kältemittel tritt vor allen Dingen am Ende des Strömungswegs des Kältemittels in einem Verdampfer ohne Blende auf, da hier das Kältemittel aufgrund seiner Verdampfung in aller Regel bereits einen bedeutenden Anteil an gasförmiger Phase aufweist. Ferner stellt die Blende/stellen die Blenden eine gute Mischung der beiden Phasen sicher, was ebenfalls die Temperaturverteilung positiv beeinflusst. Hierbei ist - im Gegensatz zur EP 1 065 453 B1 - die Anordnung einer (oder zweier) Blenden in einen oder mehreren hinten liegenden Blöcken bzw. im letzten von unten durchströmten Block ausreichend, wodurch die Herstellungskosten etwas gesenkt werden können, der Strömungswiderstand des Verdampfers gesenkt werden kann und auch evtl. entstehende Geräusche verringert werden können.According to the invention, a heat exchanger is provided, in particular for a motor vehicle, with a plurality of blocks, wherein in each block a plurality of tubes between two collecting sections are arranged, one of which is above and the other below, and at least one aperture is provided, wherein the diaphragm (s) is (are) arranged exclusively in or between blocks located in the flow path of the medium flowing through the heat exchanger. The orifice (s) is (are) located exclusively in or on the passage to the last bottom flowed through block or on the passage to the penultimate block. The orifice (s) can hereby ensure that flows through all the tubes of the last block, a balanced ratio of liquid and gaseous refrigerant from bottom to top. As a result, a particularly uniform temperature distribution can be ensured. The opposite, so a segregation and preferred flow through individual tubes with liquid or gaseous refrigerant occurs above all at the end of the flow path of the refrigerant in an evaporator without aperture, since the refrigerant usually due to its evaporation already a significant proportion of gaseous Phase has. Furthermore, the iris diaphragm ensures a good mixture of the two phases, which also positively influences the temperature distribution. Here is - in contrast to EP 1 065 453 B1 - The arrangement of one (or two) aperture in one or more blocks behind or in the last flowed through bottom block sufficiently, whereby the production costs can be reduced slightly, the flow resistance of the evaporator can be lowered and any resulting noise can be reduced ,

Auch wenn zwei Blenden vorgesehen werden können, ist bevorzugt genau eine Blende vorgesehen. Diese Blende bzw. zumindest eine Blende ist am Ende des ersten Drittels des unteren Sammelabschnitts des letzten von unten her durchströmten Blocks angeordnet. Die Blende kann in Ausführungsbeispielen nicht Teil der vorliegenden Anmeldung auch an anderen Stellen vorgesehen sein, insbesondere mittig im Sammelabschnitt. In Ausführungsbeispielen nicht Teil der vorliegenden Erfindung ist die Blende direkt am Übertritt angeordnet, insbesondere bevorzugt am Übertritt vom vorletzten zum letzten Sammelabschnitt und gegebenenfalls auch am Übertritt vom drittletzten zum vorletzten Sammelabschnitt. Durch das Vorsehen der Blenden im hinteren Bereich des Wärmetauschers ergibt sich eine deutliche Verbesserung der Kältemittelverteilung im letzten und ggf. vorletzten Block, Durch eine Anordnung von zwei Blenden gegenüber von je einer Trennwand, also am Übertritt vom drittletzten Block zum vorletzten Block und am Übertritt vom vorletzten Block zum letzten Block des Wärmeübertragers, kann ein Einbau im falschen Sammelkasten vermieden werden, d.h. die Prozesssicherheit wird erhöht.Even if two diaphragms can be provided, exactly one diaphragm is preferably provided. This aperture or at least one aperture is arranged at the end of the first third of the lower collecting portion of the last bottom-flow block. The panel can not be provided in other places in embodiments, not part of the present application, in particular centrally in the collection section. In embodiments not part of the present invention, the diaphragm is arranged directly on the transition, particularly preferably on Transfer from penultimate to last collection section and possibly also at the transfer from the third last to the penultimate collection section. The provision of the orifices in the rear region of the heat exchanger results in a significant improvement in the distribution of refrigerant in the last and possibly second-to-last block, as opposed to an arrangement of two diaphragms each of a partition, ie the transition from the third last block to the penultimate block and the transition from the penultimate block to the last block of the heat exchanger, installation in the wrong collection box can be avoided, ie the process reliability is increased.

Der Wärmeübertrager weist bevorzugt sechs Blöcke auf. Diese sind zweireihig angeordnet und werden bevorzugt im Gegenstrombetrieb durchströmt. Dabei werden die einzelnen Blöcke derart durchströmt, dass die jeweils benachbarten Blöcke in entgegengesetzter Richtung, d.h. von oben nach unten bzw. von unten nach oben, durchströmt werden.The heat exchanger preferably has six blocks. These are arranged in two rows and are preferably flowed through in countercurrent operation. In this case, the individual blocks are flowed through in such a way that the respective adjacent blocks in the opposite direction, i. from top to bottom or from bottom to top, to be flowed through.

Die Kältemittelzu- und -abführung ist vorzugsweise an einer Schmalseite des Verdampfers, insbesondere bevorzugt oben, angeordnet, wobei jedoch auch eine längsseitige Kältemittelzu- und -abführung möglich ist. Die schmalseitige Zu- und Abführung ermöglicht das Vorsehen der Öffnungen in einer im Wesentlichen ebenen Platte. Zudem erfolgt eine gleichmäßigere Strömungsausbildung des eingespritzten Kältemittels. Auch können sich Bauraumvorteile ergeben.The refrigerant supply and removal is preferably arranged on a narrow side of the evaporator, particularly preferably on the top, but also a longitudinal refrigerant feed and removal is possible. The narrow-side inlet and outlet allows the provision of the openings in a substantially flat plate. In addition, a more uniform flow formation of the injected refrigerant takes place. Also space advantages can result.

Die Blendenöffnung kann mehreckig, insbesondere rechteckig, abgerundet mehreckig, kreisförmig, elliptisch oder oval ausgebildet sein. Insbesondere bevorzugt kann sie eine im Wesentlichen rechteckförmige Gestalt mit einer abgerundet und leicht schräg verlaufenden Schmalseite aufweisen.The aperture can be polygonal, in particular rectangular, rounded polygonal, circular, elliptical or oval. Particularly preferably, it may have a substantially rectangular shape with a rounded and slightly oblique narrow side.

Die Blendenöffnung ist bevorzugt im Wesentlichen mittig angeordnet, jedoch kann für eine erhöhte Kältemitteldurchleitung beispielsweise auch eine nach unten versetzte oder für eine verringerte Kältemitteldurchleitung eine beispielsweise nach oben versetzte Anordnung der Blendenöffnung vorgesehen sein. Auch kann durch eine derart versetzte Anordnung die Vermischungsgüte der beiden Phasen optimiert werden.The aperture is preferably arranged substantially centrally, however, for an increased refrigerant passage, for example, a downwardly offset or for a reduced refrigerant passage, for example, an upwardly offset arrangement of the aperture can be provided. Also can be optimized by such a staggered arrangement, the mixing quality of the two phases.

Die Blendenöffnung nimmt vorzugsweise eine Fläche von maximal 95%, insbesondere bevorzugt maximal 50% und minimal 1%, insbesondere bevorzugt minimal 5%, des freien mittleren Strömungsquerschnitts im entsprechenden Sammelabschnitt ein. Dieses Öffnungsverhältnis führt zu einer guten Vernebelung des sich vor der Blende sammelnden flüssigen Kältemittels, so dass die Kältemittelverteilung und somit auch die Temperaturverteilung optimiert wird. Denkbar sind aber auch Werte von 2%, 3%, 4%, 5%, 6%, 7%, 8%, 9%, 10%, 11%, 12%, 13%, 14%, 15%, 16%, 17%, 18%, 19%, 20%, 25%, 30%, 35%, 40%, 45%, 55%, 60%, 65%, 70%, 75%, 80%, 85%, 90% und/oder 95% als Anfangs- bzw. Endwert des Intervalls.The aperture preferably occupies an area of at most 95%, particularly preferably at most 50% and at least 1%, in particular preferably at least 5%, of the free mean flow cross-section in the corresponding collection section. This opening ratio leads to a good atomization of the liquid refrigerant collecting in front of the orifice, so that the refrigerant distribution and thus also the temperature distribution are optimized. However, values of 2%, 3%, 4%, 5%, 6%, 7%, 8%, 9%, 10%, 11%, 12%, 13%, 14%, 15%, 16% are also conceivable. , 17, 18, 19, 20, 25, 30, 35, 40, 45, 55, 60, 65, 70, 75, 80, 85, 90 % and / or 95% as the start or end value of the interval.

Im entsprechenden Sammelabschnitt können auch zwei Blenden vorgesehen sein. Dabei nimmt vorzugsweise der Abstand der Blenden voneinander und deren Abstand von den Enden des Sammelabschnitts in Strömungsrichtung des Kältemittels zu, was die Kältemittelverteilung vorteilhaft beeinflusst. Denkbar ist es jedoch auch, dass der Abstand der Blenden voneinander gleich bleibt, oder auch abnimmt.In the corresponding collection section and two panels can be provided. In this case, preferably increases the distance of the diaphragm from each other and their distance from the ends of the collecting section in the flow direction of the refrigerant, which advantageously influences the refrigerant distribution. However, it is also conceivable that the distance between the diaphragms remains the same or even decreases.

Die Blendenöffnungen im Falle mehrerer nacheinander angeordneter Blenden werden vorzugsweise in Strömungsrichtung des Kältemittels größer, so dass die Kältemittelverteilung auf die Rohre optimiert wird. Sie können jedoch auch kleiner werden oder gleich bleiben.The apertures in the case of a plurality of successively arranged apertures are preferably larger in the flow direction of the refrigerant, so that the refrigerant distribution is optimized for the tubes. However, they can also become smaller or stay the same.

Im Folgenden wird die Erfindung anhand eines Ausführungsbeispiels mit mehreren Varianten unter Bezugnahme auf die Zeichnung im Einzelnen erläutert. In der Zeichnung zeigen:

Fig. 1
eine Ansicht eines Verdampfers gemäß dem Ausführungsbeispiel,
Fig. 2
eine schematische Draufsicht auf den Verdampfer von Fig. 1 mit angedeutetem Strömungsverlauf,
Fig. 3
eine Seitenansicht des Verdampfers von Fig. 1,
Fig. 4
eine schematisch dargestellte Schnittansicht der Ebene VI-VI in Fig. 3,
Fig. 5
einen Bereich eines Schnitts entlang in der Ebene V-V von Fig. 4,
Fig. 6
eine Ansicht der Blende im eingebauten Zustand,
Fig. 7a-c
verschiedene Blenden mit unterschiedlichen Blendenöffnungen,
Fig. 8
eine Variante des Einbaus einer Blende mit Darstellung eines Abschnitts des Sammelkastens ohne Flachrohre, und
Fig. 9
eine Seitenansicht eines Verdampfers eines nicht erfindungsgemäßen Verdampfers gemäß einer Variante mit einer Blende,
Fig. 10
eine Ansicht des Verdampfers von Fig. 9 in Luftanströmrichtung mit schematisch dargestellten Trennwänden und Blende,
Fig. 11
eine Seitenansicht eines nicht erfindugsgemäßen Verdampfers gemäß einer weiteren Variante mit zwei Blenden,
Fig. 12
eine Ansicht des Verdampfers von Fig. 11 in Luftanströmrichtung mit schematisch dargestellten Trennwänden und Blenden,
Fig. 13
einen Schnitt durch den unteren Sammelkasten im Bereich einer Blende, und
Fig. 14
einen herkömmlichen Verdampfer ohne Blende mit schematisch angedeuteter Kältemittelverteilung.
In the following the invention will be explained with reference to an embodiment with several variants with reference to the drawings in detail. In the drawing show:
Fig. 1
a view of an evaporator according to the embodiment,
Fig. 2
a schematic plan view of the evaporator of Fig. 1 with indicated flow,
Fig. 3
a side view of the evaporator of Fig. 1 .
Fig. 4
a schematically illustrated sectional view of the plane VI-VI in Fig. 3 .
Fig. 5
a portion of a section along in the plane VV of Fig. 4 .
Fig. 6
a view of the panel in the installed state,
Fig. 7a-c
different apertures with different apertures,
Fig. 8
a variant of the installation of a panel showing a portion of the header box without flat tubes, and
Fig. 9
3 is a side view of an evaporator of a non-inventive evaporator according to a variant with a diaphragm,
Fig. 10
a view of the vaporizer of Fig. 9 in Luftanströmrichtung with schematically shown partitions and aperture,
Fig. 11
3 is a side view of a non-inventive evaporator according to another variant with two panels,
Fig. 12
a view of the vaporizer of Fig. 11 in Luftanströmrichtung with schematically shown partitions and diaphragms,
Fig. 13
a section through the lower collection box in the region of a panel, and
Fig. 14
a conventional evaporator without orifice with schematically indicated refrigerant distribution.

Ein Wärmeübertrager 1, vorliegend ein Verdampfer eines Kraftfahrzeugs, der über ein Einspritzrohr 2 und ein Saugrohr 3 mit einem Expansionsorgan 4 verbunden ist, besteht gemäß dem vorliegenden Ausführungsbeispiel aus (strömungstechnisch gesehen) sechs Blöcken B1-B6, wobei er zweireihig, mit je drei Blöcke B1-B3 und B4-B6 nebeneinander ausgebildet ist, und weist mittels Trennwänden zur Kältemittelführung unterteilte Sammelkästen 5 (im Folgenden als Sammelabschnitte bezeichnet; eine übliche Bezeichnung ist auch Sammlerabschnitt bzw. Sammlerkasten), eine Mehrzahl von zwischen den Sammelkästen 5 angeordneten Flachrohren 6 und zwischen den Flachrohren 6 angeordnete Wellrippenbleche (nicht dargestellt) auf. Hierbei bilden jeweils zwei Sammelabschnitte und die dazwischen verlaufenden Flachrohre 6 samt Wellrippenblechen einen Block.A heat exchanger 1, in this case an evaporator of a motor vehicle, which is connected via an injection pipe 2 and a suction pipe 3 with an expansion element 4, according to the present embodiment from (fluidically seen) six blocks B1-B6, where he two rows, each with three blocks B1-B3 and B4-B6 is formed side by side, and has partition walls for refrigerant guide divided collection boxes 5 (hereinafter referred to as collection sections, a common name is also collector section or collector box), a plurality of arranged between the manifolds 5 flat tubes 6 and between the flat tubes 6 arranged corrugated fins (not shown) on. In each case, two collecting sections and the flat tubes 6 extending therebetween together with corrugated finned plates form a block.

Der Sammelkasten 5 weist seitlich je eine Öffnung für das Einspritzrohr 2 und das Saugrohr 3 auf und ist im Prinzip von herkömmlicher Bauart, also bestehend aus einem Kastenboden mit zwei Reihen langlochartiger Öffnungen, in welche die Enden der Flachrohre 6 eingeführt sind, einem etwa U-förmigen Kastenteil, den besagten Trennwänden zur Führung des Kältemittelstroms, Seitenplatten für den seitlichen Abschluss, wobei in einer der beiden Seitenplatten die Öffnungen für das Einspritzrohr 2 und das Saugrohr 3 vorgesehen sind. Im Gegensatz zu den üblichen Sammelkästen 5 weist der vorliegende, hier unten angeordnete Sammelkasten 5 zusätzlich eine Blende 7 auf, deren Funktion an späterer Stelle näher erläutert ist.The collecting box 5 has laterally each an opening for the injection tube 2 and the suction tube 3 and is in principle of conventional design, ie consisting of a box bottom with two rows of slot-like openings into which the ends of the flat tubes 6 are inserted, an approximately U shaped box part, the said partitions for guiding the flow of refrigerant, side plates for the lateral termination, wherein in one of the two side plates, the openings for the injection pipe 2 and the suction pipe 3 are provided. In contrast to the usual collection boxes 5, the present, arranged here below collection box 5 in addition to a diaphragm 7, whose function is explained in more detail later.

Die Rohrverschaltung ist vorliegend 16-11-16/16-11-16, d.h. Block B1 umfasst sechzehn, Block B2 elf, Block B3 sechzehn, Block B4 sechzehn, Block B5 elf und Block B6 wiederum sechzehn Flachrohre 6, wodurch die mittleren Blöcke B2 und B5 etwas schmäler ausgebildet sind als die äußeren Blöcke B1, B3, B4 und B6.The piping is present 16-11-16 / 16-11-16, i. Block B1 comprises sixteen, block B2 is eleven, block B3 is sixteen, block B4 is sixteen, block B5 is eleven and block B6 is again sixteen flat tubes 6, whereby the middle blocks B2 and B5 are made somewhat narrower than the outer blocks B1, B3, B4 and B6 ,

Das Einspritzrohr 2 und das Saugrohr 3 sind schmalseitig an einer der beiden Seitenplatten des oberen Sammelkastens 5 angebracht, also am oberen Sammelabschnitt des ersten Blocks B1 bzw. am oberen Sammelabschnitt des letzten Blocks B6, wobei der Wärmeübertrager 1 im Gegenstrombetrieb durchströmt wird. Die Strömungsrichtung des Kältemittels, vorliegend R134a, im Verdampfer sowie der zu kühlenden Luft auf der Außenseite ist in den Figuren 1 und 4 bzw. 2, 3 und 4 durch Pfeile verdeutlicht. Hierbei wird das Kältemittel in einem zweiphasigen Zustand in den Verdampfer 1 eingespritzt. Es verlässt den Verdampfer - je nach Belastung und Regelungsverfahren - gegebenenfalls auch in überhitztem, gasförmigem Zustand.The injection pipe 2 and the suction pipe 3 are mounted on one of the two side plates of the upper header 5, ie at the upper collecting section of the first block B1 or at the upper collecting section of the last block B6, wherein the heat exchanger 1 is flowed through in countercurrent operation. The flow direction of the refrigerant, in this case R134a, in the evaporator and the air to be cooled on the outside is in the FIGS. 1 and 4 or 2, 3 and 4 illustrated by arrows. In this case, the refrigerant is injected into the evaporator 1 in a two-phase state. It leaves the evaporator - depending on the load and control method - if necessary also in superheated, gaseous state.

Um eine möglichst gleichmäßige Temperaturverteilung zu gewährleisten, ist sicherzustellen, dass in allen parallelgeschalteten Flachrohren 6 - sofern in dem entsprechenden Block überhaupt noch vorhanden - ein gewisser Anteil an flüssigem Kältemittel vorhanden ist Dies ist in den zuerst durchströmten Blöcken B1 bis B5 relativ unproblematisch. Im letzten Block B6 wird jedoch das noch verbleibende flüssige Kältemittel durch die Saugwirkung des Saugrohrs 3 besonders stark angezogen und darüber hinaus liegt hier bereits ein recht hoher Anteil an gasförmiger Phase im Kältemittel vor, so dass es bei herkömmlichen Verdampfern zu einer ungleichmäßigen Temperaturverteilung in diesem Block kommt. Um dies zu verhindern, ist gemäß der vorliegenden Erfindung die Blende 7 im letzten im Strömungsweg des Kältemittels liegenden, unteren Sammelabschnitt, der nicht mit dem Saugrohr 3 direkt verbunden ist, d.h. bei der vorliegenden oben angeordneten, seitlichen Anbringung des Einspritzrohres 2 und des Saugrohres 3 beim letzten Block B6, vorgesehen, welche zum Einen das flüssige Kältemittel anstaut und zum Anderen - auf Grund der erhöhten Strömungsgeschwindigkeit durch die vorliegend quadratische Blendenöffnung 8 - das angestaute Kältemittel mitreißt, wobei es vernebelt wird.In order to ensure the most uniform possible temperature distribution, it must be ensured that a certain proportion of liquid refrigerant is present in all parallel-connected flat tubes 6, provided that they still exist in the corresponding block. This is relatively unproblematic in blocks B1 through B5, which are flowed through first. In the last block B6, however, the still remaining liquid refrigerant is particularly strongly attracted by the suction effect of the suction pipe 3 and, moreover, there is already a fairly high proportion of gaseous phase in the refrigerant, so that in conventional evaporators an uneven temperature distribution in this block comes. To prevent this, according to the present invention, the orifice 7 in the last in the flow path of the refrigerant lying, lower collecting portion which is not directly connected to the suction pipe 3, that is provided in the present above arranged, lateral attachment of the injection tube 2 and the suction tube 3 in the last block B6, which accumulates on the one hand the liquid refrigerant and on the other - on Reason the increased flow velocity through the present square aperture 8 - the entrained refrigerant entrains, being nebulized.

Die Blende 7 ist zwischen dem elftletzten und dem zwölftletzten Flachrohr 6 angeordnet, also bei den vorliegend sechzehn Flachrohren 6 etwa am Ende des vorderen Drittels des unteren Sammelabschnitts des letzten von unten her durchströmten Blocks B6.The orifice 7 is arranged between the eleventh last and the twelfth last flat tube 6, ie at the present sixteen flat tubes 6 approximately at the end of the front third of the lower collecting section of the last bottom flowed through block B6.

Die Blende 7 ist - entsprechend der Anbringung der Trennwände - im unteren Sammelkasten 5 vorliegend mittig zwischen zwei benachbarten Öffnungen für Flachrohre 6 angeordnet und mit dem Sammelkasten 5 verlötet. Die Blendenöffnung 8 ist im Wesentlichen mittig zwischen den Enden der eingeführten Flachrohre 6 und der unteren Wand des Sammelkastens 5 angeordnet und weist eine quadratische Gestalt auf, wobei die Fläche der Blendenöffnung 8 ca. 10% der Fläche des Sammelabschnitts einnimmt.The panel 7 is - in accordance with the attachment of the partitions - in the lower header box 5 present centrally located between two adjacent openings for flat tubes 6 and soldered to the collection box 5. The aperture 8 is arranged substantially centrally between the ends of the inserted flat tubes 6 and the lower wall of the collecting box 5 and has a square shape, wherein the surface of the aperture 8 occupies about 10% of the area of the collecting portion.

In Hinblick auf die Wirksamkeit der Blende 7 sind die Form des Verdampfers, der hydraulische Durchmesser der Blendenöffnung 8, die Anzahl der Blenden und deren Position im letzten unteren Sammelabschnitt, der nicht direkt mit dem Saugrohr 3 verbunden ist, relevant, weshalb für eine Optimierung der Temperaturverteilung diese Parameter berücksichtigt werden müssen.With regard to the effectiveness of the orifice 7 are the shape of the evaporator, the hydraulic diameter of the aperture 8, the number of diaphragms and their position in the last lower collection section, which is not directly connected to the suction tube 3, relevant, which is why for an optimization of Temperature distribution these parameters must be considered.

Gemäß einer in Fig. 7a dargestellten Variante der Blende weist die Blendenöffnung eine kreisförmige Gestalt auf. Als weitere Varianten der Gestalt der Blendenöffnung sind insbesondere rechteckförmige (vgl. Fig. 7b) oder ovale/elliptische Formen möglich, wobei die Kanten der Rechtecke auch abgerundet ausgebildet sein können (vgl. Fig. 7c).According to a in Fig. 7a illustrated variant of the aperture, the aperture has a circular shape. As further variants of the shape of the aperture are in particular rectangular (see. Fig. 7b ) or oval / elliptical Shapes possible, wherein the edges of the rectangles may also be rounded (cf. Fig. 7c ).

Die Blendenöffnung ist in den dargestellten Varianten jeweils etwa mittig zwischen den Enden der Flachrohre bzw. den Enden von dieselben aufnehmenden Durchzügen und dem den oberen Bereich der Blende aufnehmenden Teil des Sammelkastens angeordnet.The aperture is arranged in the illustrated variants each approximately centrally between the ends of the flat tubes or the ends of the same receiving passages and the upper portion of the aperture receiving part of the header.

Gemäß der Darstellung von Fig. 8 kann eine Blende 7, beispielsweise um die Montage und das Verlöten zu vereinfachen, in einer Vertiefung angeordnet sein, die im von den Flachrohren abgewandten Teil des Sammelkastens 5 vorgesehen ist. Auf der anderen Seite ist die Blende 7, wie beim zuvor beschriebenen Ausführungsbeispiel zwischen zwei benachbarten Durchzügen angeordnet. Dies entspricht einer häufig für Trennwände verwendeten Einbauweise. Die Blendenöffnung ist in Fig. 8 nicht dargestellt.As shown by Fig. 8 For example, in order to simplify assembly and soldering, a diaphragm 7 may be arranged in a depression which is provided in the part of the collecting tank 5 facing away from the flat tubes. On the other side, the aperture 7, as in the embodiment described above, is arranged between two adjacent passages. This corresponds to a common installation method used for partitions. The aperture is in Fig. 8 not shown.

Das Einspritzrohr und/oder das Saugrohr müssen nicht notwendigerweise auf der Schmalseite angeschlossen sein, vielmehr ist auch eine längsseitige Anbringung möglich. Dabei kann es bei einer andersartigen Durchströmung des Wärmeübertragers durchaus vorkommen, dass der letzte vom Kältemittel von unten her durchströmte Block, in welchem die Blende angeordnet ist, nicht seitlich angeordnet ist, sondern beispielsweise in der Mitte liegt.The injection pipe and / or the suction pipe need not necessarily be connected on the narrow side, but also a longitudinal attachment is possible. It may well happen in a different flow through the heat exchanger, that the last of the refrigerant flowed through from below block, in which the diaphragm is arranged, is not arranged laterally, but for example in the middle.

In den Figuren 9 und 10 ist eine nicht erfindungsgemäße Variante des Wärmeübertragers dargestellt, wobei - entsprechend dem ersten Ausführungsbeispiel - der Wärmeübertrager wiederum sechs Blöcke B1 bis B6 aufweist, die im Kreuzgegenstrombetrieb durchströmt werden. Hierbei ist zwischen dem fünften Block B5 und dem sechsten Block B6 eine einzige Blende 7 (in Fig. 10 übertrieben dargestellt) angeordnet, d.h. die Blende 7 ist im unteren Sammelkasten direkt in gleicher Höhe der Trennwand im oberen Sammelkasten angeordnet. Die Blende 7 kann somit in ihrer Außenkontur einer Trennwand entsprechen.In the FIGS. 9 and 10 a variant of the heat exchanger not according to the invention is shown, wherein - according to the first embodiment - the heat exchanger in turn has six blocks B1 to B6, which are flowed through in cross-countercurrent operation. Here, between the fifth block B5 and the sixth block B6 a single aperture 7 (in Fig. 10 exaggerated shown), ie the aperture 7 is arranged in the lower header directly in the same height of the partition in the upper header. The panel 7 may thus correspond in its outer contour of a partition.

Entsprechendes gilt auch für den Sammelkasten in dem Bereich, in welchem die Blende 7 angeordnet ist. Im Unterschied zu einer Trennwand weist die Blende 7 jedoch eine Blendenöffnung 8 auf, vorliegend, wie in Fig. 13 dargestellt, in Form eines Rechtecks mit einer abgerundeten und leicht abgeschrägten Schmalseite. Die Blendenöffnungsgröße beträgt vorliegend ca. 50% der Gesamtfläche der Blende im entsprechenden Bereich des Sammelkastens.The same applies to the collection box in the area in which the panel 7 is arranged. In contrast to a partition wall, however, the diaphragm 7 has an aperture 8, in this case as in FIG Fig. 13 represented in the form of a rectangle with a rounded and slightly beveled narrow side. The aperture size here is about 50% of the total area of the diaphragm in the corresponding area of the collecting tank.

Gemäß einer weiteren, in den Figuren 11 und 12 dargestellten nicht erfindungsgemäßen Variante des Wärmeübertragers, welche soweit nachfolgend nicht ausdrücklich erwähnt der zuvor beschriebenen Variante entspricht, ist eine zweite Blende 7 zwischen dem vierten Block B4 und dem fünften Block B5 angeordnet, auf Grund des Strömungsweges also im oberen Sammelkasten (siehe Fig. 12). Die beiden Blenden 7 weisen vorliegend einander entsprechende Blendenöffnungen 8 auf, jedoch sind auch unterschiedliche Ausgestaltungen und Anordnungen der Blendenöffnungen möglich.According to another, in the FIGS. 11 and 12 illustrated variant of the heat exchanger, which does not explicitly mentioned below corresponds to the previously described variant, a second aperture 7 between the fourth block B4 and the fifth block B5 is arranged, due to the flow path so in the upper header (see Fig. 12 ). The two apertures 7 in the present case have corresponding apertures 8, but also different configurations and arrangements of apertures are possible.

Claims (13)

  1. A heat exchanger, in particular for a motor vehicle, with several blocks (B1-B6), wherein a respective plurality of tubes is arranged in the individual blocks (B1-B6) between two collection sections, one of which is arranged at the top and the other one at the bottom, wherein the heat exchanger, as seen in the air flow direction, is formed in two rows and wherein at least one aperture is provided in at least one collection section, characterised in that the aperture(s) (7) is (are) exclusively arranged in or between trailing blocks (B4, B5, B6), as seen in the flow direction of the medium flowing through the heat exchanger, wherein the aperture(s) is (are) exclusively arranged in or at the transition to the last block (B6) flowed through from below or at the transition to the second last block (B5) and that exactly one or two apertures (7) are provided, wherein the aperture (7)/at least one aperture (7) is arranged at the end of the first third of the lower collection section of the last block (B6) flowed through from below, wherein the aperture(s) (7) is (are) formed by a sheet which is inserted into a recess in the collection section and soldered thereto.
  2. The heat exchanger according to claim 1, characterised in that the heat exchanger (1) has six blocks (B1-B6).
  3. The heat exchanger according to one of the preceding claims, characterised in that the tubes are flat tubes (6).
  4. The heat exchanger according to one of the preceding claims, characterised in that corrugated rib sheets are arranged between the tubes.
  5. The heat exchanger according to one of the preceding claims, characterised in that the refrigerant inlet and outlet is arranged at a narrow side of the heat exchanger (1).
  6. The heat exchanger according to one of the preceding claims, characterised in that the aperture opening (8) is polygonal, rounded polygonal, circular, elliptical or oval.
  7. The heat exchanger according to one of the preceding claims, characterised in that the aperture opening (8) occupies a surface of 95% maximum, in particular 50% maximum, of the free middle flow cross-section in the corresponding collection section.
  8. The heat exchanger according to one of the preceding claims, characterised in that the aperture opening (8) occupies a surface of 1% minimum, in particular 5% minimum, of the free middle flow cross-section in the corresponding collection section.
  9. The heat exchanger according to one of the preceding claims, characterised in that two apertures are provided.
  10. The heat exchanger according to claim 9, characterised in that the distance of the apertures to the ends of the collection section increases in the flow direction of the refrigerant.
  11. The heat exchanger according to claim 9 or 10, characterised in that the aperture openings become bigger in the flow direction of the refrigerant.
  12. The heat exchanger according to one of the preceding claims, characterised in that R134a is provided as refrigerant.
  13. The heat exchanger according to one of the preceding claims, characterised in that exactly one aperture (7) is arranged at a transition from the second last block (B5) to the last block (B6).
EP06005287.5A 2005-04-15 2006-03-15 Heat exchanger Active EP1712868B1 (en)

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DE102005059917A DE102005059917A1 (en) 2005-04-15 2005-12-13 Evaporator

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DE69601547T2 (en) * 1995-12-14 1999-09-02 Sanden Corp Heat exchangers with end chambers provided with partitions and method for the production thereof

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EP1712868A3 (en) 2011-11-02
EP1712868A2 (en) 2006-10-18
DE102005059917A1 (en) 2006-11-02

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