DE19849528A1 - Condensing internal coolant of motor vehicle air conditioning system involves condensing and subcooling partially condensed internal coolant in parallel paths with similar liquid/gas ratios - Google Patents

Abstract

Internal coolant path is divided into two or more parallel paths (16,18) in region into which external coolant, i.e. ambient air, flows. Internal coolant is partially condensed in this region, further condensed in first parallel path, which is higher than the second, subcooled in second parallel path and then recombined with coolant from first path, from which the gas phase has been removed. After partial condensation the internal coolant is fed to the parallel paths with an identical or at least similar ratio of liquid to gas phases. The flow rate in the second path is significantly reduced by a large pressure drop. An Independent claim is also included for a liquefier for condensing the internal coolant of a motor vehicle air conditioning system.

Description

The invention relates to liquefaction a refrigerant of a motor vehicle air conditioning and be applies a method according to the preamble of claim 1 and a condenser according to the preamble of claim 6. The condenser is particularly, but not out finally, destined to carry out the procedure. The Merk Male of the preambles of claims 1 and 6 are from Pa tent Abstracts of Japan with the publication number 03122472 A (publication date May 24, 1991).

In the known method and in the known The condenser takes place in an upper height range of the Ver partial condensation. A vertical one Distribution / collecting pipe also exercises the function of a he gas separator. From this the branches out Internal refrigerant flow path on two parallel paths. The first parallel path is the separated one Gas phase containing the upper space of the gas separator from ge feeds and carries its from saturated liquid and gas phase existing refrigerant mixture on the output side separates arranged second gas separator. This come nicated with a second way in which the refrigerant is made taken from the liquid supply of the first gas separator and is hypothermic. The supercooled liquid and the out Liquid removed from the second gas separator is there after united and taken together from the condenser.  With this known condenser, however, the liquid is level in the first gas separator depending on un different and / or changing filling quantities of the inside Ren refrigerant and / or changing operating conditions of the Motor vehicle changeable. An unwanted exposure of the first parallel path with which only existed as a liquid The liquid phase of the first gas separator can therefore only with a very wide cross section of the first gas separator and associated with very high fill quantities and high space requirements may be avoided, which meets the requirements of a minimali Sizing the installation requirements in the motor vehicle, the ecological Desired minor use of environmentally harmful interior Refrigerant as well as the generally sought after as low as possible contradicts the use of material. Also on the output side the well-known condenser has a variety of elements and Line connections that should be avoided if possible and create an additional risk of leakage.

The invention is based on the object different and / or changing filling quantities of the in refrigerant and / or changing operating conditions of the Motor vehicle a secure condenser and hypothermic radio tion even with a small amount of internal refrigerant Chen and a compact design of the condenser enable.

This task is accomplished by the procedure according to An saying 1 and the condenser according to claim 6 solved.

In contrast to the well-known liquefier According to the invention, the first and the second parallel path or the first or the second heat exchange tube practical with the same mixture of liquid and gaseous phases of the internal refrigerant, such as this from the flow exits moderately (in each case) last third heat exchange tubes. Any relative mixture changes are only relative small and come from differences in inertia, for example  or if the entry into the first and the second flow path takes place at different heights. A device for separating liquid and gas phases in the Entry area in the first and in the second parallel Flow path is not provided. Instead, the Hypothermia and thus also the automatic resorp tion when any gas phase is still present made that the inner Käl on the second flow path the cooling effect of the external coolant is set as on the first flow path. Claims 2 to 4 result in the slowdown required for this Internal refrigerant flow on the second flow away various preferred procedural options and claims 7 to 9 different device preferred options. One recognizes that alternatively one Throttling the flow of refrigerant on the second Flow path and / or a different pressure head at the Entrances of the first and the second flow path vorese hen, the input side different pressure altitude while changing the speed of the internal refrigerant due to the Bernoulli effect, i.e. a nozzle characteristic tik, can be generated.

From the Patent Abstracts of Japan with the Veröf Publication number 10009713 A (publication date 16.01.1998) it is known per se, two parallel We ge, both of which are intended for hypothermia, again to dine separately, one at a time the partial condensation and the other time only from the liquid phase of an intermediate after partial condensation Gas separator. So here, too, the one parallel path is out fed liquid phase fed. Besides, it is not safe asked that the other parallel path is not despite the Vereini with the first-mentioned parallel path still gas phase from the Condenser carried. This only recently became known  Construction therefore insists on the state of the art based on the preambles of claims 1 and 6 the prejudice, a hypothermia way from a liquid Phase of the partially condensed coolant.

The procedure according to the invention and the inventions Condensers according to the invention are based just like the one mentioned State of the art on the principle of the flow path Partial condensation of the internal refrigerant in two ways different influence on the internal refrigerant split up.

There is also the more conventional Ver drive along with associated condensers, the internal refrigerant tel after partial condensation without splitting into different parallel influences that influence the refrigerant to continue directly into a hypothermic state, where but also here the sub-cooling zone of the liquid phase previously carried out partial condensation is fed. The usual Liche procedure consists in the supercooled Zone upstream of a gas separator, like this already in the generic prior art regarding the two th flow path is the case (see in particular DE-42 38 853 A1 and the Patent Abstracts of Japan J07180930 A2, ver published July 18, 1995, and J09166371 A2 24.06.1997).

According to the particularly preferred method according to An saying 5 and the also preferred further development of the Ver liquid precondensation takes place according to claim 10 Lich below further influencing the internal cold by means of the two parallel paths mentioned. An arrangement Pre-condensation pipes in the lower area of a ver liquefier is known per se (cf. e.g. those already mentioned Patent Abstracts of Japan with file number J07166371 A2 and J 0387572 A2).

In further development of this idea after the Erfin  This construction method is used in order to be on the output side of the condenser has the highest possible fill level range nes gas separator on the output side and there Än changes depending on different and / or themselves changing filling quantities of the internal refrigerant and / or wech alternating operating conditions of the motor vehicle without interference to compensate for the operation of the condenser nen. Due to the great height available, you can go there with a small diameter of this gas on the outlet side Scheiders get along, which, as mentioned, with the input side gene gas separator according to the generic publication Patent Abstracts of Japan with the publication number 03122472 A2 is not possible. The small cross section of the in the invention provided on the output side gas separation ders is also possible in particular that about him at most half of the internal refrigerant mass flow is conducted, preferably a smaller proportion.

Claims 11 to 13 relate to structural features units of the latter construction.

Claim 14 with the training according to claim 15 offers an alternative solution for the case that as with the subject of the Patent Abstracts of Japan with the publication number 03122472 A2, from which the Oberbe handles of claims 1 and 6, the precondensation above the splitting of the success after the precondensation inner refrigerant in two parallel paths is made. With this known condenser, as mentioned earlier, on the output side of the condenser separate gas separator provided. The invention according to the Claims 14 and 15 integrated this gas separator into one middle section of a distribution / collecting pipe without the need Maneuverability, the distribution / collecting pipe in the horizontal direction to divide into several chambers. A division of a ver Part / collecting pipe in several superimposed chambers  is known per se (see e.g. the three-chamber subdivision of Patent Abstracts of Japan J09166371 A2, but in which none of the chambers is further developed as a gas separator.

The invention is based on schemati shear drawings at closer exemplary embodiments even closer explained. Show it:

Figure 1 is a vertical cross section through a he ste embodiment of a condenser.

Fig. 2 in an enlarged view a horizontal len section through the part shown in Figure 1 on the right / collecting pipe with structurally integrated collecting container;

Fig. 3 is an enlarged partial view of Fig. 1;

FIG. 3a shows a thermodynamic state diagram related to FIG. 3;

Figure 4 is a partial vertical cross section of a two-th embodiment of a condenser.

FIG. 4a shows a related thermodynamic state diagram of FIG. 4;

Fig. 5 is a partial vertical section of a third embodiment of a condenser and

FIG. 5a is a 5-related thermodynamic state diagram of FIG..

The following is common to all three exemplary embodiments:
It is a network of horizontally oriented and parallel stacked heat exchange tubes 2 see easily. These can be of any conventional shape and type of material. Preference is given to flat tubes made of aluminum or an aluminum alloy, which are combined to form a rigid register by zigzag fins 4 soldered in between with braze. Since the condenser is intended for a motor vehicle air conditioning device, this register is acted upon from the outside perpendicular to the plane of the drawing in FIGS. 1 and 3 to 5 by ambient air of the motor vehicle, which serves here as an external coolant. As an internal refrigerant of the heat exchange tubes 2, any suitable refrigerant may be used, such as R134a or according to future design CO _2.

The input-side and output-side supply of the heat exchange tubes 2 by the internal coolant takes place via two vertically running distribution / collecting tubes 6 and 8 , the circuit assignment of which to the individual heat exchange tubes 2 is different in the three exemplary embodiments.

The internal refrigerant enters the one part / collecting pipe via an inlet connection 10 and via an outlet connection 12 , which, depending on the circuitry, can be arranged on the same distribution / collecting pipe in a manner not shown, in the illustrations in FIG . 1, 3 and 4, collection tube or a structurally united with the sem member is disposed at the other dispensing /.

After all, all the condensers in it agree a that in their type of cooling function three types of A distinction must be made between heat exchange tubes, of which three differ correspond to the ways of the internal refrigerant, which, like him thinks interconnected via the distribution / collecting pipes are.

In general, the internal refrigerant coming from the inlet connection 10 , which is at least substantially gaseous, usually even in an overheated state, is supplied to at least one “third” heat exchange tube. On the corresponding third flow path, the inner refrigerant is first partially condensed in the area of influence of the outer cooling air from the gas phase into the liquid phase, so that when this third flow path emerges, a mixture of liquid and gaseous phase is still present. This is shown in the state diagrams of FIGS . 3a, 4a and 5a in each case by the state A, which is indicated together with other states in the diagrams mentioned, in which the pressure p of the internal refrigerant is logarithmically carried over the enthalpy h. In this diagram, the left-hand limit curve of the two-phase area of the states for saturated liquid is also drawn in, so that in the state diagram shown in full, all the states on the right in the drawing plane still contain gas phase, and all the states on the left correspond to the pure liquid state.

At the exit of this third flow path, the continuation of the flow path of the internal refrigerant is divided into two parallel paths, namely the first and the second parallel path corresponding to the at least one "first" heat exchange tube 16 and the at least one "second" heat exchange tube 18 .

On the first parallel path corresponding to the respective heat exchange tube 16 , the mixture of liquid and gaseous phase of the inner refrigerant coming from the third flow path is further condensed into the saturated state without intermediate treatment, with further cooling by the external coolant of the ambient air, with some gas phase still remaining can. This is then separated from the internal refrigerant.

On the second parallel path corresponding to the respective second heat exchange tube 18 , the mixture of liquid and gas phase of the third flow path is accordingly taken directly from the respective third heat exchange tube 14 without intermediate treatment, but then longer than on the first flow path the cooling influence of the external coolant exposed to the ambient air and therefore uncooled. In this supercooled state, the absorbed gas phase is absorbed without the need for a separate separation, so that no gas phase is contained in the inner refrigerant at the outlet of the second flow path. If there are still inclusions of gas phase on this second flow path under special circumstances, they condense again in the internal refrigerant without the need for further measures, at the latest under the vibrations of the motor vehicle operation.

The liquid phase of the internal refrigerant emerging from the first flow path, which is pure by gas separation, is then combined with the supercooled internal refrigerant emerging from the second flow path and jointly supplied to the outlet connection 12 in the liquid phase.

Constructively takes place in all three Ausführungsbei also play the supply of the respective third heat exchange tube 14 with the internal refrigerant from the inlet connection 10 provided with a distribution / collecting tube 6 in a known manner. From an inlet chamber 20 in the United part / collecting tube 6 , a plurality of - in the case of flat aluminum tubes typically 6-8 - third heat exchange tubes are fed in parallel. The outlet ends of these heat exchange tubes open into a collection and distribution clamp 22 in the United part / collection tube 8 , from where a smaller number of third heat exchange tubes 14 are returned in the backflow to the distribution / collection tube 6 . In this a further collection and distribution chamber 24 is provided, from which in turn in each case decreasing number of the third heat exchange tubes this via a distribution and collection chamber 26 in the distribution / collection tube 8 in a last distribution and collection chamber 28 in the distribution / Collecting pipe 6 can be returned. On the latter return line, in the case of flat aluminum tubes, the number of heat exchange tubes 14 loaded in parallel is typically reduced to 2 to 4, where only three heat exchange tubes 14 are shown in the exemplary embodiments.

The said distribution and collection chambers 22 to 28 are each in the distribution / collection tube 6 or Ver part / collection tube 8 by a simple transverse wall 30 of the flow completely divided.

From the first flow path in each case, the refrigerant occurs in each case in a gas separator 32 , which, however, is implemented differently in the individual exemplary embodiments.

The special features of the three exemplary embodiments are as follows:
In the first embodiment of FIGS . 1 to 3a, the first flow path is limited to a single first heat exchange tube 16 without restricting generality. From this, the internal refrigerant, which is usually still with some gas phase corresponding to the state point B in the diagram of FIG. 3a and which lies exactly on the dashed saturation line, enters the gas separator 32 , which will be explained in more detail below.

The inner refrigerant coming from the last three third heat exchange tubes 14 of the already mentioned state of A in the state diagram is not only the entrance of the first heat exchange tube 16 , but without further modification and in particular without intermediate gas separation in parallel without restriction of the generality in triplicate numbers mutually loaded second heat exchange tubes 18 supplied. These all open in a collecting chamber 34 in the distribution / collecting tube 8 , which is subsequently provided in the flow direction with a single three second heat exchange tubes 18 common throttle device 36 , which here as a throttling passage in the outer wall 38 of the distribution / collecting tube is trained. Due to the throttling effect of this throttle device 36 , the passage of the inner refrigerant takes place in the two heat exchange tubes 18 much more slowly than through the first heat exchange tube 16 , so that on this second heat exchange path a subcooling realized in the collecting chamber 34 according to the state point C of the diagram in FIG . 3a is realized. By means of the throttle device is lowered in the inner refrigerant having equivalent enthalpy after the throttle device has a complicated nied pressure, which corresponds to the state diagram of Fig. 3a shows the state point D.

Before further discussion of the changes in state, the concrete structural design of this first exemplary embodiment should be considered further:
As can be seen particularly clearly from the horizontal cross section of FIG. 2, parallel to the United part / collecting pipe 8 on its outer wall facing away from the pipe register 38, an additional camera is provided in structurally integrated form. It extends below egg ner collection chamber 40 , in which the first heat exchange tube 16 opens, in separation from this collection chamber 40 a vertically along the distribution / collection tube 8 extending tube-like chamber 42 , the part on the outer wall 38 of the United / collection -Tube 8 opposite side has its own outer wall 44 , which is common to a tubular header 46 larger horizontal cross-section. This collecting container, which can have a circular shape according to FIG. 2, but does not have to have it, communicates freely above with the collecting chamber 40 of the first heat exchange tube 16 . The tubular chamber 42 in turn communicates with the outlet of the throttle device 36 , which is downstream of the second flow path. The collecting container 46 in turn has the function mentioned earlier as a gas separator, so that in it depending on the operating conditions and the fill condition of the internal refrigerant, a differently high degree of horizontal phase separation surface 48 was arranged between the liquid phase lying below and the gas phase above is. The generally completely filled with supercooled internal refrigerant interior of the tubular chamber 42 communicates below through a connection opening 50 with the lower portion of the gas separator 32 , which is always filled with the liquid phase, where the internal refrigerant of the first and the second path is combined and is forwarded from the outlet port 12 in the flow direction.

Structurally, at least the various heat exchanger tubes 2 receiving the tube sheet 52 of both the distribution / collecting tube 8 and the distribution / collecting tube 6 are formed from solder-coated sheet metal and supplemented with a collector cover 54 to the collector. Especially in the case of the United part / collecting tube 8 , this collector cover 54 is part of an extrusion molding, which in one piece as well as the tubular chamber 42 and the tubular Sam container 46 forms and in turn expediently consists of aluminum or an aluminum alloy. The connection to the collector bottom can expediently be realized by soldering the inside of the sheet of the collector bottom coated on both sides with solder.

In the region of the lower region of the collecting container 46 normally occupied by the liquid phase, a drying cartridge 58 is still inserted in a closable access opening 56 at the bottom of the collecting container 46 . In a manner not shown, devices for level control and for measuring pressure and temperature can also be installed in the collecting container 46 , for example using appropriate sensors with a corresponding diagnostic display.

The tubular chamber 42 following the throttle device 36 is practically completely filled with supercooled refrigerant during operation of the condenser, so that at the lower end of the tubular chamber there is the static pressure of the entire liquid column, which extends almost over the entire height of the condenser ( with the exception of the height of the collection chamber 40 ). In the tubular collecting container 46 , on the other hand, the height of the liquid column under the phase separation surface 48 is always smaller and moreover varies depending on the fill level and the operating conditions of the vehicle.

So since in the tube-like chamber 42 at most at the top end above the throttle device 36 there may still be a small amount of gas phase, there is always a height difference between the liquid level at the top end of the tube-shaped chamber 42 and the phase separation surface 48 in the collecting container 46 . This height difference corresponds to the pressure difference between the state points C and D in the state diagram of FIG. 3a. In this diagram, the state point E then corresponds to the renewed pressure increase within the tubular chamber 42 corresponding to the pressure increase through the liquid column between the liquid level located at the top in the tubular chamber 42 and the phase separation surface 48 in the collecting container 46 . When the refrigerant flows of the first and second paths are combined, a slight pressure increase takes place in both ways on the one hand in accordance with the state point F in the diagram of FIG. 3 a due to the liquid column between the phase separating surface 48 and the connection 12 .

In the sense of the invention, it is desirable that only a relatively small mass flow part of the refrigerant flows in relation to the mass flow part on the second path, at most 50% of the mass flow part, preferably less, on the first flow path. As a result, the gas separator 32 can be dimensioned small without sacrificing its gas separation quality, here in particular with a relatively small horizontal cross-section. The result is that in the state diagram of FIG. 3a, the value of the enthalpy h lies at most in the middle between points E and B, with the very small portion of the mass flow aimed at, very clearly towards the left on the first path moved to point E.

The second embodiment according to FIG. 4a is identical to that of FIGS . 1 to 3a with the following exception.

Instead of the throttle device 36 , which can be dispensed with completely, but could possibly still be present proportionally in combination, the mass flow from the second flow path is throttled by significantly increasing the length of the second flow path in relation to the length of the first flow path, here by three times. Throttling takes place due to internal friction in the heat exchange tubes 18 .

The collection chamber 34 shrinks here in relation to the arrangement of FIG. 3 to a small collection chamber 34 a, which is arranged behind the flow last 18 c of the second flow path. The two heat exchange tubes 18 a and 18 b are arranged upstream and downstream of this heat exchange tube 18 c. In this case, only the lowermost heat exchange tube 18 a is fed directly from the partial and collecting chamber 28 . In a compared to Fig. 3 additional deflection chamber 60 takes place in countercurrent, the supply of the heat exchange tube 18 b and in a volume of the distribution and collection chamber 28 nested further deflection chamber 62 is then fed to the above-mentioned heat exchange tube 18 c. The connection opening 36 a of the collecting chamber 34 a no longer has a throttling function here if, as said, it can also be partially preserved.

The state diagram of FIG. 4a is modified in particular in comparison to the state diagram of FIG. 3a that in the three times the refrigerant passes through the heat exchange tubes 18 a, 18 b and 18 c, a pressure drop corresponding to the state points C1, C2 and T he follows.

Finally, with reference to FIG. 5, two further modifications are illustrated, which can also be used for changing the first and second exemplary embodiments described, respectively.

While, according to the first embodiment, the mass flow is throttled on the second flow path at its end via the throttle device 36 and in the second embodiment by increased internal friction in relation to the first flow path over the entire distance of the second flow path, the left takes place In Fig. 5 design of the distribution / collecting pipe 6 a throttling of the mass flow before the refrigerant from the third flow path into the second flow path via a throttle device 36 b in a transverse wall 64 between a supply chamber 66 to the second flow path and the general flow (last) distribution and collection chamber 28 . Such a measure of reducing the mass flow rate on the second flow path in relation to the mass flow speed on the first flow path can optionally be combined with the previously described throttling option along the second flow path or in the flow direction behind this.

The second variant lies in the type of gas separator 32 behind the first flow path or the first heat exchange tube 16 .

An essential peculiarity of the first and second exemplary embodiments was that the third flow path is arranged in each case in an area below the second and the first flow path arranged above this second flow path. In contrast, in the third embodiment according to FIG. 5, the third flow path of the heat exchange tubes 14 is arranged above the first flow path of one heat exchange tube 16 and the second flow path arranged below it with the two heat exchange tubes 18 . This results in other ways of gas separation, without a necessary attachment of the tubular chamber 42 and the tubular collecting container age 46 to the distribution / collecting pipe 8th Rather, this distribution / collecting tube 8 , like the distribution / collecting tube 6, can be designed without an additional transverse subdivision in the horizontal direction or horizontal arrangement of chambers as in the first and second exemplary embodiments. It should be noted that instead of the first and second exemplary embodiments with attached chambers, a horizontal subdivision of the distributing / collecting tube 8 can also be provided in the manner of the deflection chamber 62 in FIG. 4 in the distributing / collecting tube 6 of the second exemplary embodiment.

In the third embodiment of FIG. 5 mün det the first heat exchange tube 16 in the distribution / collecting pipe 8 in a collecting chamber 40 c, which also fulfills the function of egg nes gas separator 32 here . For this purpose, the collection chamber 40 c is completely separated in terms of flow at its top by a partition wall 30 c with respect to the collection and distribution chamber 26 adjoining above. Furthermore, a further partition 68 is provided on the underside of the collecting chamber 40 c, which is however perforated with a plurality of openings 70 .

The two partitions 30 c and 68 each have a vertically bent outward course so that the collecting chamber 40 c receives a volume that is increased both vertically and vertically below. In this case, the additional volume obtained below the bent-up area of the partition wall 30 c can serve as a preliminary separation space for the gas phase of the gas separation space 32 , while the partition wall 68 not only increases the volume for accommodating the liquid phase of the gas separator 32 , but also through openings for it refrigerant emerging on the first parallel path to the supercooled refrigerant emerging on the second parallel path via the heat exchange tubes 18 for the mixture of the emerging refrigerant from both the first and the second parallel path. Accordingly, the collecting chamber 72 at the outlet of the heat immersion tubes 18 of the second parallel path is at the same time a union chamber with the phase emerging from the gas separator 32 and also a common outlet chamber which communicates with the outlet connection 12 .

In the state diagram of FIG. 5a to go, as in the embodiments 1 and 2, by a teilkondensier th state from a lying still on the right of the position shown in Fig. 5a gestri smiles phase separation line rich in partially condensed Be. In the first heat exchange tubes 16 , the refrigerant is then fed to a saturated state C on the phase separation line. The pressure drop through the openings 70 in the partition 68 is represented by the pressure reduction from the state point C to C '.

In the second flow path, the refrigerant is first reduced in pressure from the saturated state A via the throttle opening 36 b to the state B and then transferred to the supercooled state D in the second heat exchange tubes 18 .

In the outlet plenum 72 , the supercooled state D and the saturated state C 'are then mixed in accordance with the mass flows to the state E, which leaves the condenser via the outlet connection 12 .

Claims (15)

1. A method of condensing into a saturated state and subsequent supercooling of the internal refrigerant of a motor vehicle air conditioning system, in which the ambient air of the motor vehicle serves as the external coolant, by splitting the path of the internal refrigerant in the area of influence of the external coolant into at least two parallel paths which are then brought together again ,
the inner refrigerant is partially condensed in the flow direction upstream of the two parallel paths in the area of influence of the outer coolant from the gas phase into the liquid phase,
the inner refrigerant is then further condensed to the saturated state on the first parallel path and remaining gas phase of the inner refrigerant is separated, while on the second parallel path the inner refrigerant is supercooled and in the supercooled state with the saturated inner refrigerant of the first which has been freed from the gas phase Parallel paths is united, and
wherein in particular the first parallel path is arranged at a higher level than the second parallel path , characterized in that
that after the partial condensation of the first and the second parallel path, the internal refrigerant in the same or at least similar, e.g. B. is slightly modified by inertia separation, the ratio of liquid to gaseous phase supplied, and
that afterwards on the second parallel path the refrigerant medium speed of the internal refrigerant is reduced in relation to the refrigerant speed on the first parallel path by a greater pressure loss and this pressure loss on the second parallel path is dimensioned such that the difference in static pressure at the outlet of the first flow path minus the static pressure at the outlet of the second flow path is greater than or equal to the pressure of the liquid column of the inner refrigerant between the gas / liquid separating surface of the inner refrigerant in the flow direction behind the outlet of the first parallel path and a level above the outlet of the second parallel path. 2. The method according to claim 1, characterized in that that in the second parallel path the higher pressure loss through Throttling the flow rate at the end of the second Parallel path and / or during the second parallel path is provided. 3. The method according to claim 1 or 2, characterized records that in the second parallel path the higher pressure loss by lowering the inlet pressure on the second parallel path in the Relationship to the inlet pressure on the first parallel path is posed. 4. The method according to claim 3, characterized in that the relatively different inlet pressures at the first and on the second parallel path using the Bernoulli Effect. 5. The method according to any one of claims 1 to 4, characterized characterized in that the partial condensation below the two Parallel paths are made and the height difference between a lower level of the partial condensate area  rens, with several entry openings of the deepest entry opening, the internal refrigerant in the way of the partial condensate sierens to just below the level of the first parallel way to compensate for fluctuations in gas / liquid Parting surface in the direction of flow behind the first parallel away depending on different and / or changes changing filling quantities of the internal refrigerant and / or alternating operating states of the motor vehicle is used. 6. Condenser of the internal refrigerant of a motor vehicle air-conditioning device with a network of horizontally oriented and parallel one above the other heat exchange tubes that can be acted upon by the ambient air of the vehicle as an external coolant and the flow on both sides vertically oriented distribution / manifold with each other for guidance an internal refrigerant are connected,
The interconnection at different heights on the one hand has at least one third heat exchange tube that can initially be flowed through and used for partial condensation, in particular a plurality of third heat exchange tubes, and on the other hand has a parallel connection that can be flowed through afterwards, at least one first and at least one second heat exchange tube, in which the respective one is related on the second heat exchanger tube (s) arranged at a higher level, the first heat exchange tube for further condensation in a partially saturated state and the respective second heat exchange tube can be used for subcooling, and
wherein in the flow direction behind the respective flow (respectively) last first heat exchange tube, a device for separating the remaining gas phase is arranged, in particular for carrying out the method according to one of claims 1 to 5, characterized in that
a distributing / collecting pipe distributing the partially condensed refrigerant emerging from the flow of the last third heat exchange pipe essentially in compliance with the gas / liquid ratio to the first and second heat exchange pipes,
the device for separating remaining Gaspha se of the refrigerant emerging from the respective last flow heat exchange tube with a United part / manifold is structurally summarized and
a device for generating a lower flow rate of the refrigerant in the respective second heat exchange tube is provided in relation to the respective first heat exchange tube. 7. A condenser according to claim 6, characterized net that the device for generating a lower current speed a throttle device at the Ausmün extension of the respective second heat exchange tube in a Ver part / collecting pipe and / or a throttle device in one Outlet opening of a collection chamber in a distribution / collection Pipe in the mouth area of the respective second heat has exchange tube. 8. A condenser according to claim 6 or 7, characterized ge indicates that the device for generating a small ren flow rate a the respective second heat flow tube upstream throttle device is, preferably at the entrance opening of the respective two th heat exchange tube or at an inlet opening of a upstream antechamber in a distribution / collecting pipe. 9. Condenser according to one of claims 6 to 8, there characterized in that the means for generating a lower flow rate due to different Design of the respective second heat exchange tube in the Ver equal to the respective first heat exchange tube in view on inner pipe diameter, length of flow path, pipe shape, internals and / or characteristics of the inner surface che is. 10. Condenser according to one of claims 6 to 9, characterized in that
the third heat exchange tubes are arranged at a height below the second heat exchange tubes, in the distribution / collecting tube, to which the respective second heat exchange tube is connected, a further channel for the supercooled refrigerant flowing from top to bottom is formed, and
in structural association with the same United part / collecting pipe a container connected to the respective first heat exchange pipe and provided as a gas separator is formed, which extends over the height of the condenser and at its lower end in the height region of the outlet of the refrigerant from the condenser communicates with the duct for the supercooled refrigerant. 11. A condenser according to claim 10, characterized net that the collecting container and that structurally combined with it Distribution / collecting pipe formed by separate components which form the further channel between them. 12. A condenser according to claim 11, characterized net that the separate components made of aluminum or one Aluminum alloy, the distribution / collecting pipe is made of Braze coated sheet metal is formed and the collection container together with the continuation channel an integral extrusi profile is. 13. A condenser according to one of claims 10 to 12, characterized in that the collecting container with a Dryer insert is provided. 14. A condenser according to one of claims 6 to 9, at which the third heat exchange tubes in a height range above half of the first heat exchange tubes are arranged, thereby ge indicates that inside the same distribution / collection Rohres three superimposed chambers each by one Partition wall are divided, of which the top chamber with the third heat exchange tube (s) communicated and through the upper partition from the middle chamber in terms of flow is separated, the middle chamber with the respective first  Heat exchange tube and at the same time as an exit chamber from the Condenser serving lower chamber with the respective two th heat exchange tube communicates, with the lower partition with formation of the facility for separating remaining Gas phase of the com from the respective first heat exchange tube refrigerant with at least one through opening for liquid refrigerant from the respective first pipe the middle chamber is provided in the lower chamber. 15. A condenser according to claim 14, characterized net that at least one partition, preferably both, under Extension of the middle chamber a vertically bent Has course.