WO2012022807A1 - Module de condenseur à réfrigérant - Google Patents

Module de condenseur à réfrigérant Download PDF

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Publication number
WO2012022807A1
WO2012022807A1 PCT/EP2011/064322 EP2011064322W WO2012022807A1 WO 2012022807 A1 WO2012022807 A1 WO 2012022807A1 EP 2011064322 W EP2011064322 W EP 2011064322W WO 2012022807 A1 WO2012022807 A1 WO 2012022807A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
cooling tubes
region
subcooling
parallel section
Prior art date
Application number
PCT/EP2011/064322
Other languages
German (de)
English (en)
Inventor
Guillaume David
Uwe FÖRSTER
Matthias Jung
Andreas Kemle
Christoph Walter
Herbert Hofmann
Original Assignee
Behr Gmbh & 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 & Co. Kg filed Critical Behr Gmbh & Co. Kg
Priority to EP11745804.2A priority Critical patent/EP2606291B1/fr
Publication of WO2012022807A1 publication Critical patent/WO2012022807A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters
    • 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
    • F28D2021/0084—Condensers

Definitions

  • the present invention relates to a refrigerant condenser assembly according to the preambles of claims 1 and 8, a method for operating a refrigeration circuit of an automotive air conditioning system according to the preamble of claim 9 and an automotive air conditioning system according to the preamble of claim 11.
  • refrigerant condenser assemblies for an automotive air conditioning system
  • vapor refrigerant is converted to a liquid state and then the refrigerant is further "subcooled.”
  • the refrigerant condenser assembly forms part of a refrigeration circuit of an automotive air conditioning system including an evaporator, an expansion device, and a compressor.
  • DE 10 2007 018 722 A1 shows a condenser for the air conditioning system of a motor vehicle, which has two manifolds and a container arranged next to the one manifold for receiving the desiccant of the refrigerant of the air conditioner.
  • the refrigeration cycle of an automotive air conditioning system is reduced by up to 10%.
  • the performance of a refrigeration cycle in an automotive air conditioning system can be increased, among other things, that the already liquefied refrigerant is cooled more strongly at a subcooling region of the refrigerant condenser assembly.
  • the refrigerant in gaseous form enters the refrigerant condenser assembly at an inlet port and is cooled to a saturation temperature at an overheat region. Subsequently, the refrigerant flows into a condensation region and in this the gaseous refrigerant is further cooled and liquefied. Subsequently, the liquid refrigerant flows into a subcooling region and is cooled below the boiling point, for example to a temperature of 6 or 7 K below the boiling temperature of the refrigerant. By a greater cooling of the refrigerant in the subcooling region below the boiling point of the refrigerant, a higher power of the refrigerant circuit can be achieved.
  • the refrigerant capacitor assembly within the motor vehicle a predetermined space, for example given by a certain depth, height and width available, so that although a greater cooling of the refrigerant at the subcooling by a larger surface at the subcooling and a larger associated Although space of the refrigerant condenser assembly is possible, but in general due to the predetermined dimensions of the space for the Kältemitteikondensatorbautik no larger space is available.
  • the refrigerant R1234yf is sought to increase the subcooling, for example, 15 K.
  • more cooling tubes or proportionally more area required by the capacitor has the consequence that less space is available for the condensation area, the cooling takes place at a higher saturation temperature and the associated saturation pressure increases. This causes a negative effect on the refrigeration capacity in the refrigeration cycle, which reduces or even negates the intended advantage.
  • the object of the present invention is to provide a refrigerant condenser assembly, a method for operating a refrigeration circuit of an automotive air conditioning system, and an automotive air conditioning system in which the refrigerant in a subcooling region of the refrigerant condenser assembly is strongly cooled without the condensing pressure substantially in the refrigerant condenser assembly increases.
  • the flow cross-sectional area is the cross-sectional area of the cooling tubes for passing the refrigerant.
  • the cooling tubes of the subcooling region thus have a smaller flow cross sectional area than the cooling tubes of the overheating region and / or the condensation region.
  • a smaller flow cross-sectional area can be achieved, for example, by cooling tubes with a smaller cross-sectional area or by cooling tubes with the same cross-sectional area, whereby turbulence inserts in the cooling tubes of the subcooling region reduce the flow cross-sectional area.
  • the refrigerant can be cooled more advantageously at the subcooling, for example, to a temperature of 14 K below the boiling temperature of the refrigerant, without thereby increasing the dimensions of the Käitestoffkondensatorbaueria and thus the Kältestoffkondensatorbaueria finds place in a given space of a motor vehicle.
  • the performance of a refrigeration circuit of an automotive air conditioning system can be improved and thereby the power reduction when using the new refrigerant R1234yf be at least partially compensated.
  • At least two cooling tubes act as the first subcooler parallel to the refrigerant flowing into the first subcooler, the first subcool intermembrane discharges into at least two cooling tubes as the second subcooler and preferably flows into the subcooling region second subcooling parallel section into a second subcooling intermediate flow channel and the second subcooling intermediate flow channel opens into at least two cooling tubes as the third subcooling parallel section.
  • Oer subcooling of the refrigerant condenser assembly is thus divided into a total of two or three Unterkühlparailelab bainitese each connected by the Unterkühl thoroughlyströmungskanal.
  • the refrigerant at the subcooling region can be cooled even further below the boiling point of the refrigerant.
  • the subcooling region of the refrigerant condenser assembly is thus subdivided into a first and a second subcooler parallel section, and in the subcooler parallel sections, at least two cooling tubes are in each case hydraulically or fluidly guided in parallel with the refrigerant.
  • the refrigerant exiting from the first subcooler parallel section is introduced into and mixed in a first subcooling intermediate flow channel, and the refrigerant is introduced into the second subcooler parallel section from the first subcooling intermediate flow channel.
  • the refrigerant is conducted in parallel in the subcooling region, for example, by four, seven or nine cooling tubes.
  • the first and second subcooler parallel section for example, two, three or five cooling tubes.
  • the refrigerant at the first and second subcooler parallel sections is subject to a a smaller cross-sectional area of flow is available in the prior art refrigerant condenser assembly, thereby increasing the flow rate of the refrigerant at the subcooling region and thereby improving or increasing the heat transfer from the refrigerant to the air flowing around the refrigerant condenser assembly.
  • one subcooler parallel section or the subcooling region between two or eight cooling tubes acted upon in parallel and / or the surface of the cooling tubes and preferably the headers of the subcooling region is less than 50%, 40%, 35%, 30%, 25% or 15% of the surface of the heat exchanger of the refrigerant condenser assembly and in particular the heat exchanger consists of the cooling tubes and preferably the headers,
  • At least two cooling tubes are acted as fluid-conducting parallel first parallel section, the refrigerant flowing out of the first parallel section opens into a first intermediate flow channel and the first intermediate flow channel opens into at least two cooling tubes as the second parallel section.
  • the flow direction of the refrigerant before the first subcooler parallel section ie before the subcooling region of the refrigerant condenser group, ie thus at the overheating region and / or at the condensation region of the refrigerant condenser assembly is thus arranged a first and a second parallel section.
  • the overheating region and / or the condensation region are subdivided into the first and second subcooler parallel sections between which the refrigerant is conducted through the first intermediate flow channel.
  • the refrigerant flowing out of the second parallel section opens into a second intermediate flow channel and the second intermediate flow channel opens into at least two cooling tubes as the third parallel section.
  • the refrigerant condenser assembly is thus subdivided into a total of three parallel sections with at least two, preferably at least four or six or eight, cooling tubes, which are each fluidically connected to one another through the intermediate flow channel.
  • a parallel section preferably has a larger number of cooling tubes than a subcooling parallel section and preferably the number of cooling tubes of a paralleling section is two, three, five or seven cooling tubes greater than the number of cooling tubes of a subcooling section.
  • the second parallel section preferably opens into a second intermediate flow channel and the second intermediate flow channel opens into the collecting container or the third parallel section opens into a third intermediate flow channel and the third intermediate flow channel opens into the collecting container.
  • the sum of the flow cross-sectional areas of all the cooling tubes of a subcooler parallel section is smaller than the product of 1, 0 or 0.9 or 0.7 or 0.5 or 0.3 or 0.1 and the sum of the flow cross-sectional areas of all the cooling tubes of a parallel section.
  • Tes and / or the cooling tubes are formed as flat tubes and corrugated fins are arranged between the flat tubes.
  • the filling amount of refrigerant can be reduced.
  • the cost can be reduced.
  • the width of the cooling tubes, in particular of all cooling tubes, a subcooler parallel section or the subcooling region is smaller than the product of 1, 0 or 0.9 or 0.7 or 0.5 or 0.3 or 0.1 and the width of Cooling tubes, in particular all cooling tubes, a parallel section.
  • the heat transfer in the subcooling region can also be controlled by the individual corrugated fins which are arranged between the vertical cooling tubes.
  • the corrugated fins have a different geometry in the subcooling region than the corrugated fins in the overheating region and / or condensation region.
  • the white ribs in the subcooling region are preferably designed such that the air-side heat transfer increases or improves in this region.
  • the Weil ribs in the subcooling could be made the same height as in the overheating area and / or condensation area, but by an increased corrugated fin density or gill fields have a different geometry, which improves the heat transfer in this area.
  • the corrugated fins in the subcooling region could be designed with a lower height than in the overheating region and / or condensation region.
  • narrower cooling tubes could be used in the subcooling to increase the flow rate and thus the heat transfer.
  • the corrugated fins could be designed in the subcooling with a higher height than in the overheating area and / or condensation area. In this case, the air-side heat transfer would be deteriorated. However, since fewer cooling tubes are arranged in parallel on the refrigerant side, the heat transfer on the refrigerant side would increase.
  • Method according to the invention for operating a refrigeration circuit of an automotive air conditioning system comprising the steps of: passing refrigerant through lines of a refrigerant circuit, compressing the gaseous refrigerant in a compressor so that the pressure of the gaseous refrigerant is increased, cooling and condensing the gaseous refrigerant in a refrigerant condenser assembly that passes through Cooling tubes is passed by the gaseous refrigerant is cooled in an overheating region to a saturation temperature, then in a condensation region, the gaseous refrigerant is cooled to a boiling temperature and liquefied and cooled in a subcooling the liquid refrigerant below the boiling temperature, expanding the liquid refrigerant to a Expansion organ, so that the pressure of the liquid refrigerant is reduced, heating and evaporating the refrigerant in an evaporator, conducting the gaseous refrigerant exiting the evaporator to the compressor, wherein in the subcooling region, the refrig
  • the refrigerant in the subcooling region, is passed in parallel through at least two cooling tubes of a first subcooler parallel section, the refrigerant flowing out of the first subcooler section is directed into a first subcooling intermediate channel, and the refrigerant passed through the first subcooling intermediate channel is then passed in parallel through at least two cooling tubes of a second subcooler parallel section or the volume flow of the refrigerant in the cooling tubes of the subcooling region is greater than the volume flow of the refrigerant in the cooling tubes of the overheating region and / or the condensation region by 1.0 or 1, 2 or 1, 5 or 2 times or the refrigerant in the subcooling section is cooled by more than 7, 10, 12 or 14 K and is preferably cooled by less than 30 K or 20 K.
  • Automobile air conditioning system comprising a refrigerant condenser assembly, an evaporator, a compressor, preferably a blower, preferably a housing for receiving the blower and the evaporator, the refrigerant condenser assembly being a refrigerant as described in this patent application.
  • capacitor assembly is formed and / or from the motor vehicle air conditioning system described in this patent application process is executable.
  • the refrigerant is R1234yf or R134a.
  • the refrigerant condenser assembly has a closure device formed on the collecting container for closing a closure opening of the collecting container.
  • a dryer and / or a filter are arranged in the collecting container and / or in the closure device.
  • FIG. 1 is a perspective view of a refrigerant condenser assembly
  • Fig. 2 is a partial perspective view of the refrigerant condenser assembly of FIG. 1 and
  • FIG. 3 shows a flow diagram of the refrigerant in the refrigerant condenser assembly according to FIG. 1.
  • a refrigerant condenser assembly 1 is shown in a perspective view.
  • the refrigerant condenser assembly 1 is part of an automotive air conditioning system with an evaporator and a compressor (not shown).
  • By horizontally arranged cooling tubes 2 as flat tubes 3 flows to be condensed and cooled refrigerant ( Figures 1 and 2).
  • the cooling tubes 2 open at their respective ends in a vertical manifold 5, that is, there are two manifolds 5 respectively at the ends of the cooling tubes 2.
  • the manifold 5 has for this purpose cooling tube openings through which the ends of the cooling tubes 2 protrude into the manifold 5.
  • baffles (not shown) are formed with which a certain flow path of the refrigerant can be achieved through the cooling tubes 2, so that the refrigerant flows through the cooling tubes 2 according to the flow diagram in Fig. 3 through the cooling tubes 2.
  • the cooling tubes 2 meandering corrugated fins 4 are arranged, which are in thermal communication with the cooling tubes 2 by means of heat conduction. This increases the area available for cooling the refrigerant.
  • the cooling tubes 2, the corrugated fins 4 and the two manifolds 4 consist in Ali Wunschen of Metali, in particular aluminum, and are materially connected as a solder joint.
  • a fastening device 8 is arranged, with which the refrigerant condenser assembly can be attached to a motor vehicle, in particular to a car body of a motor vehicle.
  • a collecting container 6 is arranged (Fig. 1, 2).
  • the collecting container 6 is by means of two overflow openings (not shown) in fluid communication with the collecting pipe 5 and thus also indirectly in fluid communication with the cooling tubes 2.
  • a dryer and a filter (not shown) is arranged in the collecting container 6.
  • the dryer is hygroscopic and can absorb water or moisture from the refrigerant.
  • the collecting container 6 is mechanically connected to the collecting tube 5 at the lower and upper ends with a concave support region. At the lower end of the collecting container 6 is closed by a VerInstitutelnraum 7 fluid-tight.
  • the removable Closing device 7 allows replacement of the dryer and the filter in the collecting container. 6
  • the refrigerant condenser assembly 1 has an inlet port 9 for introducing the refrigerant R1234yf into the refrigerant condenser assembly 1, and an outlet port 10 for discharging the refrigerant from the refrigerant condenser assembly 1 (FIGS. 1 and 3).
  • the ends of the cooling tubes 2 terminate in the manifolds 5.
  • baffles or flow guide plates, not shown, are arranged by means of which a certain predetermined flow diagram of the refrigerant can be achieved, d. H. with which flow path the refrigerant flows through the plurality of superimposed cooling tubes 2 of the refrigerant condensor assembly 1.
  • a first intermediate flow passage 20, a second intermediate flow passage 22, a third intermediate flow passage 24 as well as a first subcooling passage 15, which are shown in FIG. 3, are thus formed within the collecting tubes 5 by the flow guide plates (not shown).
  • the refrigerant condenser assembly 1 constitutes a heat exchanger for transferring heat from the refrigerant to air surrounding and circulating around the refrigerant condenser assembly 1.
  • the heat exchanger is essentially formed by the cooling tubes 2 and the two manifolds 5.
  • the heat exchanger as part of the Kältemiltelkondensatorbaueria 1 in this case has an inlet opening ⁇ , through which gaseous refrigerant from a compressor not shown ter to the refrigerant condenser assembly 1 is passed.
  • the gaseous refrigerant is at an overheating area 11 on a saturation cooled temperature, ie at the saturation temperature occurs according to the existing pressure, a condensation of the refrigerant.
  • a condensation region 12 connects, in which the refrigerant is condensed and thus liquefied.
  • the refrigerant liquefied in the condensation region 12 is supplied as a liquid to the subcooling region 13 and cooled in the subcooling region 13 below the boiling temperature of the refrigerant.
  • the specified in Fig. 3 clear separation in the overheating region 11, condensation region 12 and subcooling 13 may slightly differ during operation of a motor vehicle air conditioning, so that, for example, in a modification of the representation in Fig. 3, the overheating region 11 is slightly larger and thereby the condensation region 12 smaller is, so that, for example, a second parallel section 21 also partially forms the overheating region 11.
  • the overheating region and the condensation region may be arranged in exactly one partial section.
  • the overheating region 1 is formed by the first parallel section 19.
  • the first parallel section 19 has eleven cooling tubes, which are connected in parallel or flow through in a fluid-conducting or hydraulic manner. After flowing out of the refrigerant from the eleven cooling tubes 2 of the first parallel section 9, the refrigerant is introduced into the first intermediate flow passage 20 and introduced from the first intermediate flow passage 20 into the second separating section 21.
  • the second parallel section 21 has eight cooling tubes 2 through which the refrigerant flows simultaneously in parallel. The refrigerant flowing out of the second parallel section 21 is introduced into the second intermediate flow passage 22 and introduced therefrom into the third parallel section 23 with likewise eight cooling tubes 2.
  • the refrigerant flowing out of the third parallel section 23 is introduced into the third intermediate flow passage 24, and is then supplied to the subcooling section 13 of the refrigerant condenser assembly 1.
  • the subcooling region 13 comprises a first subcooler parallel section 14 and a second subcooler parallel section 16.
  • the two subcarrier sections 14, 16 each have six cooling tubes 2.
  • the first sub-cooling parallel section 14 is connected to the second sub-cooling parallel section 16 through the first sub-cooling intermediate flow passage 15.
  • the parallel sections 19, 21 and 23 and the subcooler parallel sections 14, 16 are fluidly connected in series and the cooling tubes 2 at the parallel sections 19, 21 and 23 and at the subcool parallel sections 14, 16 and 18 are hydraulic or connected in parallel fluid-conducting.
  • the entire refrigerant passed through the refrigerant condensing unit 1 thus flows through the parallel sections 19, 21 and 23 and the subcooling parallel sections 14, 16.
  • the subcooling sections 14, 16 have a smaller number of cooling tubes 2 than the parallel sections 19, 21 and 23 the flow cross-sectional area of the cooling tubes 2 of the subcooler parallel sections 14, 16 smaller than the flow cross-sectional area of the cooling tubes 2 of the parallel sections 19, 21 and 23, because the width of the cooling tubes 2 as flat tubes 3 at the parallel sections 19, 21, 23 1, 8 mm and the width of Cooling tubes 2 at the subcooler parallel sections 14, 16 is 1.3 mm.
  • the distance between see the cooling tubes 2 in the subcool parallel sections 14, 16 with 6 mm smaller than the distance between the distance between the cooling tubes of the parallel sections 19, 21, 23 with 8 mm, so that the height of Welirippen 4 at the parallel sections 9, 21, 23 with 8 mm greffyer than the height of Welirippen 4 at the subcooler parallel sections 14, 16 with 6 mm.
  • the width of the cooling tubes 2 in this case represents the expansion in a cross section of the cooling tubes 2 and the length of the cooling tubes 2 in the cross section corresponds to the depth of the refrigerant condenser assembly 1 to the cooling tubes 2, ie the expansion in the flow direction of the air passing through between the cooling tubes 2 the refrigerant condenser assembly 1 flows.
  • the refrigerant at the subcooler parallel sections 14, 16 has a substantially smaller flow cross-sectional area than at the parallel sections 19, 21 and 23 because the cooling tubes 2 have different flow cross-sectional areas and furthermore the number of cooling tubes 2 is preferably smaller at the subcooler parallel sections 14, 16 than at the parallel sections 19, 21, and 23.
  • the flow velocity is adjusted according to the density change.
  • the heat transfer from the refrigerant to the air in the subcooling region 13 can be increased, thereby transferring more heat from the refrigerant to the air flowing around the refrigerant condenser assembly 1
  • the refrigerant in the subcooling 13 are cooled more below the boiling temperature of the refrigerant, for example, be cooled by 14 K below the boiling temperature of the refrigerant. This can be increased advantageously the COP of a refrigerant circuit.
  • the pressure drop in the refrigerant condenser assembly 1 is not increased or only very slightly, so that the high pressure at the inlet opening 9 is only slightly increased. increases and thus the increase in performance of the refrigerant circuit due to the greater cooling at the subcooling region 13 is substantially greater than the power reduction due to the possible increase of the high pressure at the Einiassö réelle 9.
  • the subcooling region 13 also has a third subcooling parallel section in addition to the first and second subcooling sections 14, 16.
  • the overheating and condensation region 11, 12 may have only one or two parallel sections 19, 21.
  • the volume flow at the subcooling region 13 is greatly increased, so that greater undercooling or cooling of the refrigerant at the subcooling region 13 can be achieved without the refrigerant condenser assembly 1 requires more space or surface, because due to the larger volume flow, the heat transfer from the refrigerant to the air per surface unit of the refrigerant condenser assembly 1, in particular on the cooling tubes 2, the corrugated fins 4 or the manifolds 5 as a heat exchanger of the refrigerant condenser assembly 1, is increased.
  • the COP of a refrigeration circuit with the refrigerant condenser assembly 1 can be increased without requiring additional space for the refrigerant condenser assembly 1.
  • the reduction in COP due to the use of the refrigerant R1234yf can be at least partially compensated.

Abstract

L'invention concerne un module de condenseur à réfrigérant pour une installation de climatisation d'un véhicule automobile, qui comprend des tubes de refroidissement (2) pour conduire un réfrigérant, deux tubes collecteurs pour relier fluidiquement les tubes de refroidissement (2), de préférence un récipient collecteur avec au moins une ouverture de trop-plein au moyen de laquelle le récipient collecteur est en liaison fluidique avec les tubes de refroidissement (2) et/ou le tube collecteur. Les tubes de refroidissement (2) présentent une zone de surchauffe (11) pour refroidir le réfrigérant sous forme de vapeur, une zone de condensation (12) pour condenser le réfrigérant sous forme d'au moins une section parallèle (19, 21, 23), et une zone de sous-refroidissement (13) en tant que section parallèle de sous-refroidissement pour refroidir le réfrigérant liquide. Selon l'invention, le réfrigérant doit être fortement refroidi dans la zone de sous-refroidissement (13) du module de condenseur à réfrigérant sans que le module de condenseur à réfrigérant ne nécessite un espace de construction accru au niveau de la zone de sous-refroidissement (13). Cet objet est réalisé par le fait que les surfaces de section transversale d'écoulement des tubes de refroidissement (2) de la zone de sous-refroidissement (13) sont plus petites que le produit de 1,0 ou de 0,9 ou de 0,7 ou de 0,5 par les surfaces de section transversale d'écoulement des tubes de refroidissement (2) de la zone de surchauffe (11) et/ou de la zone de condensation (12).
PCT/EP2011/064322 2010-08-19 2011-08-19 Module de condenseur à réfrigérant WO2012022807A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP11745804.2A EP2606291B1 (fr) 2010-08-19 2011-08-19 Module de condenseur à réfrigérant

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010039518A DE102010039518A1 (de) 2010-08-19 2010-08-19 Kältemittelkondensatorbaugruppe
DE102010039518.8 2010-08-19

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Publication Number Publication Date
WO2012022807A1 true WO2012022807A1 (fr) 2012-02-23

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DE (1) DE102010039518A1 (fr)
WO (1) WO2012022807A1 (fr)

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DE102013204294A1 (de) * 2013-03-12 2014-10-02 Behr Gmbh & Co. Kg Kondensatorbaugruppe für Kältemittel
CN103438621B (zh) * 2013-08-28 2015-11-18 广东志高空调有限公司 一种可变流路空调冷凝器

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US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
JPH11211277A (ja) * 1998-01-22 1999-08-06 Showa Alum Corp サブクールシステムコンデンサ
JP2003021432A (ja) * 2001-07-09 2003-01-24 Zexel Valeo Climate Control Corp コンデンサ
EP1531309A2 (fr) * 2003-11-13 2005-05-18 Calsonic Kansei UK Limited Condenseur
EP1577629A1 (fr) * 2004-03-18 2005-09-21 Behr Lorraine S.A.R.L. Bouchon de fermeture, distributeur et échangeur de chaleur
DE102007018722A1 (de) 2007-03-23 2008-09-25 Modine Manufacturing Co., Racine Kondensator
FR2915793A1 (fr) * 2007-05-03 2008-11-07 Valeo Systemes Thermiques Echangeur de chaleur ameliore pour circuit de climatisation de vehicule automobile

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EP2606291A1 (fr) 2013-06-26
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