EP2606292A1

EP2606292A1 - Coolant condenser assembly

Info

Publication number: EP2606292A1
Application number: EP11749398.1A
Authority: EP
Inventors: Guillaume David; Uwe FÖRSTER; Matthias Jung; Andreas Kemle; Christoph Walter; Herbert Hofmann
Original assignee: Behr GmbH and Co KG
Current assignee: Mahle Behr GmbH and Co KG
Priority date: 2010-08-19
Filing date: 2011-08-19
Publication date: 2013-06-26
Anticipated expiration: 2031-08-19
Also published as: US20130219932A1; WO2012022806A1; US9970694B2; CN203286816U; EP2606292B1; DE102010039511A1

Abstract

The invention relates to a coolant condenser assembly for an air conditioning system for a motor vehicle, comprising an inlet opening (9) for the introduction of a coolant, an outlet opening (10) for the discharge of a coolant, and cooling pipes (2) for the passage of a coolant, two collective pipes for fluidic connection of the cooling pipes (2), and a collecting vessel having at least one overflow opening by means of which the collecting vessel is fluidically connected to the cooling pipes (2) and/or the collective pipe, the collecting vessel being disposed on a first longitudinal side of the coolant condenser assembly, and the cooling pipes (2) having a superheating region (11) for cooling the vaporous coolant, a condensation region (12) for condensing the coolant, and a supercooling region (13) for cooling the liquid coolant. The problem addressed by the invention is that the coolant in the supercooling region (13) of the coolant condenser assembly should be cooled intensely without the condensation pressure increasing substantially in the coolant condenser assembly. This problem is solved in that, in the supercooling region (13), at least two cooling pipes (2), as the first supercooling parallel section (14), are acted upon in parallel by the coolant in a fluid-conducting manner, the coolant which flows out of the first supercooling parallel section (14) flows into a first supercooling intermediate flow duct (15), and the first supercooling intermediate flow duct (15) opens into at least two cooling pipes (2) as the second supercooling parallel section (16), and the second supercooling parallel section (16) opens into a second supercooling intermediate flow duct (17) and the second supercooling intermediate flow duct (17) opens into at least two cooling pipes (2) as the third supercooling parallel section (18), such that the outlet opening (10) is disposed on a second longitudinal side of the coolant condenser assembly.

Description

Kältemittelkondensatorb ugru pe

The present invention relates to a Kaltemittelkondensaiorhaugruppe according to the preamble of Änspruehes 1, a method for operating a refrigeration circuit of a Kraftfahrzeugklimaaniage according to the preamble of claims 9 and a Kraftfahrzeugklimaaniage. According to the preamble of claim 11.

In elemenitteikondensatorbaugruppen for a Kraftfahrzeugklimaaniage vapor refrigerant is transferred to a liquid state of matter and then the liquid refrigerant further in a subcooling "onterkühlf. The refrigerant condenser assembly forms a Tel! egg nes refrigerant circuit of a Kraftfahrzeugklimaaniage with 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 header pipes and a container arranged next to the one collecting pipe for receiving the drying agent of the coolant. When using the new refrigerant 1234yf compared to the previous refrigerant R134a, there is a reduction in performance of the refrigeration circuit of an automotive air conditioning system in the range of up to 10% due to changes in the Stöffeigeiisehaften the new refrigerant R1234yf. The performance of a refrigeration circuit in a motor vehicle air conditioning system can be increased, inter alia, by cooling the already liquefied refrigerant more strongly at a subcooling region of the refrigerant intermediate condenser subassembly. in a Kälterniitelkond ^{'ensaforbaugruppe} the refrigerant occurs in the form of gas at an inlet opening in the Kaitemittelkondensatorbaugruppe and is cooled to a Üfoerhitzungsb.ereich to a saturation temperature Subsequently, the refrigerant flows in a condensation region, and in this is further cooled, the gaseous refrigerant to a boiling temperature and liquefied thereby , Subsequently, the liquid refrigerant flows into a Unterkühiungsbereieh and is cooled below the boiling temperature, 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 below the boiling temperature of the refrigerant, a higher power of the refrigerant circuit can be achieved, but generally 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 Unterkühiungsbereieh by a larger surface at the subcooling and an associated larger space of Kieiiemittelköndensatorbaugruppe is possible, but generally due to the predetermined dimensions of the space for the refrigerant condenser assembly no larger space is available. To increase the performance of the refrigerant circuit or to compensate for the under-performance of the refrigerant, in particular the refrigerant R1234yf is sought to increase the UnterKühlüng, for example, 15 K. For this purpose, more cooling tubes or proportionately more surface area required by the capacitor. This has the consequence that less space is available for the condensate 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 oldest circulation system, which reduces or even nullifies the desired benefit.

For this purpose, US Pat. No. 8,470,704 62 proposes a subcooling region which is subdivided into a first and a second subcooler parallel section. The disadvantage of this arrangement is that the outlet opening and the collecting container are arranged on the same side of the refrigerant condenser assembly. In many installation situations, it is desirable that the exhaust port and sump are located on different longitudinal sides of the coolant condenser assembly.

Therefore, the object of the present invention is to provide a refrigerant condensate subassembly, a method of operating a refrigeration cycle, an automotive cruising airbag, and an automotive air conditioning system in which the refrigerant in a sub-cooling section of the refrigerant condenser assembly is strongly cooled without the condensing pressure substantially in the refrigerant condensing device This object is achieved with a refrigerant condenser assembly for a motor vehicle air conditioning system, comprising an inlet opening for the introduction of a refrigerant condenser assembly for an automotive air conditioning system. a refrigerant, an outlet port for discharging a refrigerant, cooling pipes for passing a refrigerant, two header pipes for connecting the cooling pipes, a header having at least one bleed port by means of which the header is in fluid communication with the cooling pipes and / or a header; In the subcooling region, at least two cooling pipes are parallel to the first subcooling section parallel to the refrigerant acted upon, which emanates from the first supercooling section refrigerant flowing into a first Unterkühizwischenströmungskanal and the first bottom The second subcooler section opens into a second subcooling intermediate channel and the second subcooling intermediate channel opens into at least two cooling tubes as the third subcooler section so that the outlet port is located on a second longitudinal side of the capacitor condenser assembly

The subcooling area of the refrigerating condenser assembly is thus divided into a total of three subcooling feeder sections, each connected by a subcooling intermediate flow channel. Thereby, the refrigerant can be cooled at the Unterkühiungsbereieh even further below the boiling temperature of the refrigerant.

Further, through the three subcooling sections, the outlet port and the header tank are arranged on opposite longitudinal sides of the refrigerant refrigerant condensing unit. Thus, preferably a collection container with a larger collection volume may be available In addition, as in the prior art, inlet inlet and outlet opening are furthermore preferably arranged on the same longitudinal side of the medium condensate cake.

The Unterkühlüngsbereich the Käitemittelkondensatarb ug ^'roup is thus divided into first and second and third Unterkühlparalleiabschnitt and the Unterkühjparalielabschnitten at least two cooling tubes are hydraulically or fiuidleitend parallel acted upon by the cold middle !. In this case, the refrigerant, which exits from the first Onterkühlparallelabsohnitt is introduced into a first Unterkühizwischenströmungskanal and mixed in this and from the first UnterkühizwisGhenströmungskanal is the Kältemitie! Subsequently, the refrigerant, which emerges from the second cross-cooling section in a second Unterkühlzvvischenströsi ungskana! introduced and mixed in this and from the second Unterkuhlzwischensirö- mungskanal the refrigerant is introduced into the third UnterkühlparaSlelabschnitt. Subsequently, the refrigerant is discharged through the discharge port from the refrigerant condenser assembly. Thus, advantageously, the refrigerant can be cooled more strongly at the subcooling range, for example to a temperature of 14 K below the boiling temperature of the refrigerant, without the dimensions of the refrigerant condenser assembly being increased and thus the refrigeration condenser battery group finding room in a predefined space of a motor vehicle. Thus, the performance of a refrigeration circuit of a Kraftfahrzeugklimaaniage can be improved and thereby the reduction in performance when using the new refrigerant R1234 f are at least partially offset.

An increased pressure drop in the subcooling region, which is generated by the three subcooler sections, is not detrimental to the performance of the cold medium condenser subassembly reduce performance. This is due to the fact that the pressure drop takes place after the wet steam area, while the high pressure of the system is oriented at the saturation temperature before the Unierkühlungshereieh or after the condensation area,

The three subcooling parallel sections are thus arranged in a geodetically higher height than the second subcooling paraliel section, while the second subcooling parallel section is arranged geodetically higher than the first uncharacterizing section , Alternatively, of course, the three Unterkühlparallelahschnitte are also flowed through from top to bottom, in a further embodiment each Unterkühiparallefabschratt two, three or four parallel cooled cooling tubes and / or the surface of the cooling tubes and preferably the Sanlmelrohre the Unterkühiungsberei- ches is less than 50 %, 40%, 35%, 30%, 25% or 15% of the surface area of the heat exchanger of the Käfitemittelkondensatorhaugruppe and in particular the heat exchanger consists of the cooling tubes and preferably the headers,

I a complementary Äusführungsform are in the flow direction of the refrigerant before the first U ^{'nterkühlparailelabschnitt} least two Kühiroh- re acted upon fluid lettend parallel, the eiabschnitt from the first Parai! Refrigerant flowing opens into a first Zwisehenströmungskana first Parallelabschniit! and the first intermediate flow channel opens into at least two cooling tubes as the second parallel section in flow direction of the refrigerant upstream of the first subcooled parallel section, d, h, upstream of the subcooling region of the cold lifting capacitor group _t, ie, at the overheating area and / or at the condensation area This means that a first and a second parallel element are arranged. Thus, the overheating area and / or the condensing area are divided into the first and second paraliel sections between which the refrigerant passes through the first intermediate flow passage. is directed.

In a supplementary embodiment, in the flow direction of the refrigerant upstream of the first sub-cooling passage, the refrigerant flowing out of the second boundary opens into a second intermediate flow channel and the second intermediate flow channel discharges into at least two cooling tubes as the third parallel section upstream of the subcooling radiator, i. h, so that at the overheating region and / or the condensation region of Käitemittelkondensatorbaugruppe, thus the refrigerant condenser assembly is divided into a total of three parallel sections with at least two, preferably at least four or six or eight, cooling tubes, which are each connected fluidieitend by the intermediate flow channel. Preferably, this case has a Paralielabschnitt a greater number of cooling tubes than a UnterkühSparaileiabschnitt and preferably the number of cooling tubes of a parallel section of two, three, five or seven cooling tubes is greater than the number of cooling tubes of a Unterkü ^'h - paralle portion!.

Preferably, the second parallel section opens into a second intermediate flow channel and the second intermediate flow channel opens into the Samnielbehälteröder the third Paralielabschnitt opens into a third Zwischenströmungskanai and the third Zwischenströmungskanai flows into the collecting container. The Oberhitzungs- and / or Kondensationsbe- has rich Käitemittelkondensatorbaugruppe of the first and second parallel portion, thus the ausgeieäiete from the second ParailelabschniU refrigerant is introduced into the storage tank and then into the first sub ^{»kühiparallelabschnitf} or superheat and / or condensation tionfoereich has three Paralleiabschnitte, the discharged from the third Parall ielabschnitt refrigerant is introduced into the sump and then into the first Unterkübiparalleiabschnitt. This also applies analogously, provided that the overheating and / or condensation zone i is subdivided into more than three paralelafort branches, for example four or five parcel segments.

Alternatively, exactly one Parailelabschntti be provided so that it opens exactly a Parailelabschn tt in the sump.

Intensive measurements have shown that the following ratio of the number of tubes is preferable:

Overheat range: 15 cooling pipes

Condensation region; 12 cooling tubes {wherein the condensation area is subdivided into a first sectional area with 7 cooling zones and a second sectional area with 5 cooling tubes)

Subcooling area: 9 cooling tubes (where the subcooling area is subdivided into a first, second and drift cooling parallel section with 3 cooling tubes each).

In one variant, the sum of the Strörnüngsquerschnlttsflächen the cooling tubes of a subcooled parallel section is smaller than the product of 1.0 or 0.9 or 0 _t 7 or 0.5 or 0.3 or 0.1 and the sum of SirömürigsquersGhnittsf surfaces of the cooling tubes of a Parallelabschnii it and / or the cooling tubes are formed as flat tubes and between the flat tubes Weil ribs are arranged. The flow cross-sectional area st the Querschnifisfläche the cooling tubes for passing the refrigerant, Inventive method for operating a refrigeration circuit of a Kraftkrankenkllrnaanlage with the steps: passing refrigerant through Leiiuri gene of a Äitemittelkreislaufes, compressing the gaseous refrigerant in a compressor, so that the pressure of the gaseous refrigerant is increased, cooling, condensing and supercooling the gaseous refrigerant in a refrigerant condenser assembly, which is passed through cooling tubes by the gaseous refrigerant in an overheating range to a saturation temperature is cooled, then cooled in a condensation region, the gaseous refrigerant to a boiling temperature and is liquefied and cooled in a subcooling the liquid refrigerant below the boiling temperature, expanding the liquid refrigerant to an expansion device, so that the pressure of the liquid refrigerant is reduced , Heating and Evaporation of the Refrigerant In an evaporator, passing the gaseous refrigerant leaving the evaporator to the compressor, wherein in the subcooling region of the condenser d as refrigerant is directed parallel through at least two cooling tubes of a first Unterkühlparailelabschnittes, the effluent from the first UnterkühlparalSelabschniit refrigerant is directed into a first Unterküh ^{'lzwischenströmungskanal} and ischensfrömungskana by the first Unterkühlz! then led parallel refrigerant through at least two cooling pipes of a second Unterkühlparailelabschnittes parallel! and the second subcooler section i opens a second subcooling intermediate flow channel and the second subcooling flow channel opens into at least two cooling tubes as the third subcooling section and / or in the subcooling section the refrigerant is passed through cooling tubes with a smaller flow cross sectional area than the refrigerant passing through the cooling tubes the overheating region and / or the condensation region is conducted, so that the refrigerant passed through the cooling tubes in the subcooling region has a larger volume flow than the refrigerant conducted through the cooling tubes in the overheating region and / or the kingdom seasonal cycle. The volumetric flow of the refrigerant in the cooling tubes of the subcooling region is expediently greater than the volumetric flow of the refrigerant in the cooling tubes of the superheating zone and / or the condensation chamber and / or 1, 0 or 1.2 or 1, 5 or 2 times. or the refrigerant in the sub-cow region is cooled by more than 7, 10, 12 or 14K and is preferably cooled by less than 30K or 20K due to the greater volume flow of the refrigerant into the cooler tube of the subcooler as compared to just one subcooling tube hlparailejäbschnitt a Unlerkü ^'and the associated larger Strömüngsgeschwindigkeit the refrigerant in the supercooling region can thereby be achieved, Kraftfahrzeugkismaanlage invention comprising a Kältemitteikondensatorbaugruppe better heat transfer from the refrigerant to the air, which flows around the refrigerant condenser assembly, an evaporator, a compressor, preferably a fan, preferably a housing for accommodating the fan and the evaporator, wherein the refrigerant condenser assembly is designed as a described in this Schutzrechtsanmeidiing refrigerant condenser assembly and / or executable by the power plant air conditioning system described in this patent application process,

In an additional embodiment, the refrigerant is! R1234yf or R1S4a,

In one variant, the refrigerant Koridensatorbaugruppe a formed on the collecting Versehlusseinriohtung for closing a Ve closure opening of the collecting container. Preferably, a dryer and / or a filter are arranged in the collecting container.

In the following, an embodiment of the invention will be described below with reference to the accompanying drawings. It shows;

1 is a perspective view of a Kältemittelkondensatörba group,

FIG. 2 shows a perspective partial view of the oldest component capacitor assembly according to FIG. 1 and FIG

3 shows a flow switching diagram of the refrigerant in the refrigerant-capacitor assembly according to FIG. 1.

In Figures 1 and 2, a äiiemittelkondensatorbaugruppe 1 is shown in a perspective view. The refrigerant condenser assembly 1 is part of a Kraftfahrzeugkiimaaniage 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 (Fig. 1 and 2). The cooling tubes 2 open a their respective ends in a vertical manifold 5, d. h, there are two manifolds 5 respectively at the ends of the cooling pipe 2. In Flg. 2 If only one manifold 5 is shown. The manifold 5 has for this Kühirohroffnungen through which the ends of the cooling pipes 2 protrude into the manifold 5. Within the collecting pipes 5 baffles (not shown) are formed with which a certain flow path of the refrigerant can be achieved by the cooling pipe 2, so that the refrigerant flows through the cooling pipe 2 according to the flow diagram in Fig. 3 through the cooling tubes 2. Meander-shaped corrugated fins 4, which are in thermal communication with the cooling tubes 2 by means of heat dissipation, are arranged between the tubular tubes 2. This increases the area available for cooling the refrigerant. The cooling tubes .2, the Weurippen 4 and the two manifolds 4 are generally made of metal, in particular aluminum, and are materialschiüssig connected to each other as a solder joint. In four corners of the elite Mitteikond-senatorbaugruppe 1, a fastening device 8 is arranged with which the refrigerant condenser assembly to a Motor vehicle, in particular on a Ka rosserie a motor vehicle, can be attached.

At the collecting pipe 4, also vertically aligned, a collecting container 8 is arranged on a first longitudinal side (Fig _. , 1, 2). The collecting container 8 is in the middle of two overflow openings (not shown) in avoidance with the collecting pipe 5 and thus also indirectly in flight connection with the cooling pipes 2. A dryer and a filter (not shown) are arranged in the collecting container 6. The dryer is hygroscopic and can absorb water or moisture from the refrigerant. Oer Sammeibe- container 6 is mechanically connected at the lower and upper end to the manifold 5 with a concave on Sagebereich. At the lower end of the collecting container 8 is closed by a closure device 7 fluid-tight. The removable Verschijseinrjchtung 7 allows replacement of the dryer and the filter in the sump 6th

The refrigerant condensing unit 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 center-of-refrigerant condenser 1 (FIGS. 1 and 3). The ends of the cooling tubes 2 terminate in the Sammelrqhren 5. In the manifolds 5 baffles or flow guide plates, not shown, arranged by means of which a certain predetermined Ströo ungsschaltfaiid the refrigerant Erzjeit, d, h, with which flow path, the refrigerant flows through the plurality of superposed ühfrohre 2 of Käteemitteikondensatorbaugruppe 1. The Sirö- müngsschallbild shown in Fig. 3 serves only to illustrate the flow path of the refrigerant through the cooling tubes 2 and represents non-geometric orientation of the cooling tubes 2 to each other in the Kieitemiüelkondensatorbaugruppe 1. A first Zwisehenströmungskanal 20, a second intermediate flow channel 22, a between the third flow channel 24 and a first U ^'n terkühizwischenströmungskanal 15 and a second Unterkühlzwiscbenströ- flow duct 17, which are shown in Fig. 3, are thus formed within the Sammefrohre 5 of the flow baffles not shown.

The refrigerant condenser assembly 1 is a heat exchanger for transferring heat from the refrigerant to air surrounding and flowing around the refrigerant condensate booster 1. The heat exchanger is substantially the Küh ^'irohren 2 and the two header pipes 5 are formed. The heat exchanger as part of the refrigerant condenser assembly 1 in this case has an outlet opening 9, through which gaseous refrigerant is passed from a compressor, not shown, to the refrigerant condenser assembly 1. The gaseous refrigerant is cooled at a Überhitzungsbereieh 11 to a saturation temperature, d. h, at the saturation temperature occurs in accordance with the existing pressure, a condensation of the refrigerant. In the flow direction of the refrigerant after the overheating region 11, a condensation region 12 follows, 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 below the boiling temperature of the refrigerant in the cooling region 13. The clear separation given in FIG. 3 in the overheating region 11, the condensation region 12 and the subcooling region 13 can be slightly different during operation of an automotive air conditioning system. so that, for example, in a modification of the representation in Flg. 3, the overheating region 11 is slightly larger, and as a result the condensation region 12 becomes smaller, so that, for example, a second parallel drain 21 also partially forms the overheating region 1. This applies in an analogous manner for the separation .Between the condensation region 12 and the Unterkühiungsbereieh 13, which can slide either into a first U ^'nterkühl- paralielabschnitt 14 can move back in the direction of flow of the refrigerant, or in a third parallel portion 23 opposite to the flow direction of the refrigerant ,

The overheating region 11 is formed by the first parallel section 19. In this case, the first parallel section 19 has eleven cooling tubes, which are connected in parallel or through which the fluid flows in parallel to the fluid or hydraulically. After the outflow of the refrigerant from the eleven cooling tubes 2 of the first parallel section 19, the refrigerant is introduced into the first intermediate flow passage 20 and introduced from the first intermediate flow passage 20 into the second parallel 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 effluent from the third parallel section 23 refrigerant is introduced into the third intermediate flow channel 24 and then after it has passed through the sump 6, the Unterkühiungsbereieh 13 of the Käl emittelkondensatorbaugruppe 1 is supplied. The Unterkühiungsbereieh 13 includes a first Unterkühiparallelabschnitt 14, a second Unterkühlparaiielabschnltt 16 and a third UnterkUh1 _. Paralle.iab- section 18. The three Unterkü ^' hlparallejabschnitte 14, 16 and 18 each have three cooling tubes 2. The first subcooling parallel section 14 is connected to the second subcooling parallel section 18 by the first subcooling section 18. scbenströmungskanal 15 and connected in ^'a manner analogous to the second sub-cooling section 16 in parallel with the third supercooling parallel portion 18 through the second sub-cooling the intermediate flow channel 17 is connected. Thus, in the Käitemittelkondensatofbaugruppe 1, the parallel sections 19, 21 and 23 and the Unterkühiparailelabschnltte 14, 16 and 18 are conductively connected in series and the Kühirohre 2 at the parallel sections 19, 21 and 23 and the Unierkühlparallelabschnstten 14, 16 and 18 are hydraulically connected in parallel. The entire refrigerant passed through the oldest-end condenser module 1 thus flows through the respective Paralielabschnitte 19, 21 and 23 and the URterkühlparallelabschnstte 14, 16 and 18. In this case, the Unterkühlparalieiabschnitte 14, 18 and 18 a significantly smaller number of cooling tubes 2 than the Paralielabschnitte 19th 21 and 23. Due to the fluid-conducting or hydraulic circuit of the oldest-capacitor assembly 1 is thus the refrigerant at the subcooler sections 14, 18 and 18, a much smaller Strömungsquerschnlttsflöch® available than at the parallel sections 19, 21 and 23, because the cooling pipe have the same flow cross-sectional area. As a result, a greater flow velocity of the refrigerant or a larger volume flow of the refrigerant occurs at the subcooler sections 14, 16 and 18 than at a subcooling region with just one subcooler parallel section. Due to this greater flow velocity or the greater volume flow of the refrigerant to the subcooling region 13, the heat transfer can take place from the refrigerant to the air in the subcooling region 13, thereby transferring more heat from the refrigerant to the air flowing around the cheese condenser assembly 1, thus cooling the refrigerant in the subcooling region 13 more than the boiling temperature of the refrigerant, for example 14 K below the boiling temperature of the refrigerant to be cooled. In this way, advantageously, the CGP of a shopping district can be increased. the. Due to the sufficiently dimensioned

Flow cross-sectional area at the supercooling 13, the Druckafo- faii in the Kältemittei condenser assembly 1 is not or only slightly increased, so that the high pressure a of the inlet opening 9 only slightly increases and thus the increase in efficiency of the Käitekreises due to the greater cooling at the Unterkühlungsbereieh 13 substantially larger is, as the power reduction due to the eventual increase of the high pressure at the inlet opening 9 is. After flowing through the Unterkuh- iungsbereiches 13, the refrigerant is discharged through the outlet opening 10 from de Kältemiltel-capacitor assembly. By forming three sub-cooling sections, the escape opening is arranged on a second longitudinal side of the cold-end capacitor assembly. Thus Ausiassöffnung and reservoir 6 are arranged on different longitudinal sides of Kälternitteikondensatorbaugruppe. In a further embodiment (not shown), the supercooling section 13 has only the first and second un-cooling parabolic sections 14, 16 and not the third sub-cooling parabolic section 18. In an additional embodiment, not shown, the supercooling section 13 may also be divided into a total of four or five subcooling sections. However, the subcooling region 13 preferably has an odd number of subcooling parallel sections, so that the collecting container 6 and the outlet opening 10 are arranged on different sides of the refrigerant condenser assembly. Overall, significant advantages are associated with the inventive capacitor capacitor assembly 1. The flow velocity or the volume flow at the subcooling region 13 is greatly increased on account of the predetermined flow switching principle, so that a greater degree of subcooling or cooling of the coolant at the subcooling region 13 can be achieved without the elemenemitteikondensatorbaugrup e 1 requires more space or surface, because due to the greater flow rate, the heat transfer from the refrigerant per surface unit de Kältemitteikondensatorbaugruppe i, 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 , As a result, with an unchanged installation space for the refrigerated eScap capacitor assembly 1, the COP of a kite crate with the additive capacitor subassembly 1 can be increased without requiring additional space for the refrigerant condenser assembly 1. Thus, the reduction in COP due to the use of the refrigerant R1234yf can be at least partially compensated.

ex gszeie enii you

1 refrigeration capacitor assembly

2 cooling tube

3 Fiac ro r

4 ^' corrugated fin

5 manifold

8 collection containers

7 Versehlusseinrichtung the collecting container

8 Fastening n o

9 inlet opening

10 outlet opening

11 superheat overshoot

12 ondensationsbereäch

13 UntetliühüngsbereiGh

14 First subcommittee waiver

15 First Unterkühizvvlschenströmungskana!

18 Second sub-refrigeration paralysis section

17 Second subcooler intermediate flow cans

18 Drifter Unterkühlparalleiabschntt

19 First Paralielabsehnift

20 First intermediate flow canana!

21 Second parallel section

22 Second intermediate flow channel

23 Third parallel section

24 Third Intermediate Flow Channel

Claims

i e i a n s p r e e s

Refrigerant capacitor assembly (1) for a Krafffahrzeugk! Irnaan! A- ge, comprising

- An inlet opening (9) for dividing a refrigerant

- An Äusiassöffung (10) for distributing a refrigerant

Cooling tubes (2) for passing a refrigerant,

two collecting pipes (5) for fluidizing the cooling pipes (2),

a collecting container (6) with at least one Öberströmöffnung by means of the collecting container (8) in fluid communication with the cooling tubes (2) and / or Sammelroh (5), wherein the collecting container is arranged on a first longitudinal side of Käitemittelkondensatofbaugruppe

- The cooling tubes (2) an overheating region (11) for cooling the vapor refrigerant, a condensation region (12) for condensing the refrigerant and a UnterkühJungsbe- rich (13) for cooling the liquid refrigerant, wherein in Unterkühiungsbereich (13) at least two KüHirohre (2) as the first Unterkühiparallelabschnitt (14) ffuidleiiend are acted upon in parallel with the refrigerant, the effluent from the first UnterkühSparalielabsGhnitt (14) refrigerant! opens into a first subcool intermediate flow channel (15) and the first subcooling flow channel (15) opens into at least two cooling tubes (2) as a second subcooling parallel section (16), characterized in that in the subcooling area {13}, the second subcool trap section (16) opens into a second subcooling intermediate channel (17) and the second subcooler intermediate channel (17) discharges into at least two cooling tubes (2) as the third subcooling section (18) so that the outlet port (18) TO) is arranged on a second longitudinal side de refrigerant capacitor assembly.

Kältenköndensatorbaugruppe according to claim. 1, characterized in that each UnterkühiparaiielabschniÜ (14, 16, 18) has two, three or four parallel acted cooling tube (2) and / or the surface of the cooling tubes (2) and preferably the manifolds (5) of the subcooling region (13) less than 50%, 40%, 35%, 30%, 25% or 15% of the surface area of the heat exchanger of the refrigerant condenser assembly (1) and in particular the heat exchanger of the cooling tubes (2) and preferably the Sam.rne1roh.ren (5) consists.

Refrigerant capacitor assembly according to one or more of the preceding claims, characterized in that in the flow direction of the refrigerant upstream of the first supercooling line section (14) at least two cooling tubes (2) are acted upon in fluid-parallel fashion as the first parallel section (1),

Käitemittelkondensatortaaugfuppe according to claim 1 or 2, characterized in that in the flow direction of the refrigerant upstream of the first .Unterkühlparallelabschnitt (14) at least ZW I cooling tubes (2) as a first Parailelabschnitt († 9) are fluidieitend applied in parallel, which from the first Parailelabschnitt (19) outflowing refrigerant flows into a first intermediate flow channel (20) and the first Intermediate flow channel (20) opens into at least two cooling tubes (2) as a second paralysis section (21).

Refrigerant condenser assembly according to claim 4, characterized in that in the flow direction of the refrigerant before the first subcooler parallel section (14) from the second parallel section (21) effluent refrigerant in a second intermediate flow channel (22) opens and the second Zwischensirömungskanal (22) in at least two cooling tubes ( 2) as the third ParaHelahschniit (23) opens,

Kältemitteiköndensatorbaugruppe according to claim 4 or 5, characterized in that the second Paraileiabschnitt (21) opens into a second intermediate flow channel (22) and the second intermediate Strömungskana! (22) into the collecting container ( ^β ) (14) opens or the third parallel section (23) opens into a third Zwischenströmungskanai (24) and the third intermediate flow channel (24) in the collecting container (6) (14) opens

Refrigerant condenser assembly according to one or more of claims 3 to 8, characterized in that the sum de flow cross-sectional areas of the cooling tubes (2) of a Unterkühiparal ^■ lelabschnittes (14, 16, 18) is smaller than the product of 1.0 or 0.9 or 0th , 7 or 0.5 or 0.3 or 0.1 and the sum of the flow cross-sectional areas of the cooling tube (2) of a parallel section (19, 21, 23) and / or the Köhlröhre (2) are designed as flat tubes (3) and between the flat tubes Weil ribs (4) are arranged.

Refrigerant capacitor assembly according to one or more of the preceding claims, characterized in that the third Subcooler section (18) is arranged geodätisch higher than the second supercooling Paralielabschnitt (16) and the second Unterkühlparaätelabschnitt geodetically higher than the first Unierkühlparaitelabschnitt (4).

Method for operating a kite circuit of a motor vehicle ski system comprising the steps:

Conducting 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 (1) which is passed through cooling tubes (2) by cooling the gaseous refrigerant to a saturation temperature in an overheating zone (11), then gaseous in a condensation zone (12) Refrigerant is cooled to a boiling temperature and liquefied and in a ünterkühlungsbereieh (13) the liquid refrigerant is cooled below the boiling temperature,

Expanding the liquid refrigerant on an expansion device _s such that the pressure of the liquid refrigerant is reduced,

- Heating and evaporating the refrigerant in an evaporator _. .

Passing the gaseous refrigerant exiting the evaporator to the compressor, characterized in that in the supercooling region (13) the refrigerant is conveyed through at least two cooling tubes (2) of a first supercooled parallel section (14). directed refrigerant is discharged from the first Unterkülparalleiabschnstt (14) refrigerant in a first Uncomming flow channel (5) and passed through the first Unterkuhiz i¬ strömströmyngskanai (15) refrigerant then through at least two cooling tubes (2) of a second subcooling section (16) is tested in parallel, and the second subcooling section (16) is placed in a second subcooling circuit

(17) opens and the second Unierkühizwischenströmungskanal (17) in at least two cooling tubes (2) as a third Unterkühlparaltelabschnitt

(18) and / or in the Unterkühiungsbereich (13), the refrigerant is passed through cooling tubes (2) with a smaller flow cross-sectional area than the refrigerant which is passed through the cooling tubes (2) of the Öberbifzungsbereiches and / or the condensation region (2), so in that the refrigerant conducted through the cooling tubes (2) in the subcooling region (13) has a larger volumetric flow than the refrigerant conducted through the cooling tubes (2) in the top heating region (11) and / or the condenser (12).

A method according to claim Q, characterized in that the volumetric flow of the refrigerant in the cooling tubes (2) of the subcooling region (13) is greater than the volumetric flow of the refrigerant by 1, 0 or 1, 2 or 1, 5 or 2 times in the cooling pipes (2) of the overheating furnace (11) and / or the condensation zone (12) and / or because refrigerant in the subcooling furnace (13) is cooled by more than 7, 10, 12 or 14 K, and preferably less than 30 K or 20 K is cooled.

Power Equipment, Equipment and Services

A center of gravity condenser assembly (1), - an evaporator,

a compressor,

preferably a fan,

Preferably, a housing for accommodating the blower and the evaporator, characterized in that the refrigeration lite condenser assembly (1) according to one or more of claims 1 to 8 is formed and / or of the motor vehicle air conditioner a method according to claim 9 or 10 executable .