EP2909563B1 - Condenser - Google Patents

Description

Technical area

The invention relates to a condenser in a stacked disk design, with a first flow channel for a refrigerant and with a second flow channel for a coolant, wherein a plurality of disc elements are provided, which form stacked mutually adjacent channels between the disc elements, in particular according to the preamble of claim 1. The US2009 / 0071189 discloses such a capacitor.

State of the art

Condensers are used in refrigerant circuits of motor vehicle air-conditioning systems to cool the refrigerant to the condensation temperature and then to condense the refrigerant. Regularly, capacitors have a collector in which a volume of refrigerant is kept in order to compensate for volume fluctuations in the refrigerant circuit and to achieve a stable supercooling of the refrigerant.

Often, additional means for drying and / or filtering the refrigerant are provided in the collector. The collector is usually arranged on the capacitor. It is flowed through by the refrigerant, which has already flowed through part of the condenser. After flowing through the collector, the refrigerant becomes returned to the condenser and subcooled in a subcooling below the condensation temperature.

In the case of conventional rib-tube-type condensers, the refrigerant for this purpose is led out of the condenser from one of the manifolds arranged at the side of a tube-rib block and introduced into the collector.

For capacitors constructed in a stacked disc design, ways in the art are known to attach the collector to the capacitor as an additional layer of disk elements.

In addition, it is known to lead the refrigerant via a special distribution plate from the built-up in stacked disk condenser and supply an external collector and return the refrigerant after the collector back into the condenser. This is for example in the unpublished application of the Applicant DE 10 2010 026 507 disclosed.

Furthermore, the disclosure US 2009/0071189 A1 a stacked disc capacitor in which a first stack of disc elements represents a first cooling and condensing region and a second stack of disc elements constitutes a subcooling region. The first stack is separated from the second stack by a housing containing a collector and dryer.

A disadvantage of the devices of the prior art is that the integration of capacitors in stacked disc design, collectors and subcoolers has been solved quite expensive. In addition to a complex structure, the capacitors from the prior art are characterized by an increased production cost. This results in the use of the capacitors additional costs that make their use unattractive.

Presentation of the invention, object, solution, advantages

Therefore, it is the object of the present invention to provide a condenser suitable for condenser, storage and further subcooling refrigerant, the condenser being characterized by a simple structure and compact design and inexpensive to manufacture.

The object of the present invention is achieved by a capacitor in stacking disk construction with the features of claim 1.

The construction of a condenser in Stapeischeibenbauweise is particularly simple and inexpensive to implement. As a rule, a multiplicity of identical disk elements can be used for the construction. Only the outer boundary plates of the disk stack or disk elements in the interior of the disk stack, which cause additional functionalities, such as the blocking or deflection of a flow channel, have a different design. The division of the flow channel, which leads the refrigerant into a first region which serves for the desuperheating and the condensation of the refrigerant in its vapor phase and a second region which serves for the subcooling of the condensed refrigerant, results in that the end of the condenser is always complete Undercooled refrigerant is present.

In order to keep the volume of refrigerant in the refrigerant circuit constant and the refrigerant in addition to drying and / or to filter, it is additionally advantageous to integrate a collector in the refrigerant circuit. This is advantageously integrated in the flow channel of the refrigerant, at a point after the complete condensation of the refrigerant and before the collection, drying and / or filtering of the refrigerant.

It is particularly advantageous if the first connection element is designed as a channel and the channel leads from the first region through the second region to the fluid inlet of the collector, wherein the channel is only in fluid communication with the first region of the first flow channel.

It is also advantageous if the second connection element is designed as a channel and the channel leads from the fluid outlet of the collector through the first region into the second region.

By using a tube to connect a header to the first flow channel, the condenser may be formed outside the condenser by a stack of discs consisting predominantly of identical disc elements, despite the arrangement of the header.

The tube is guided through a series of adjacent disc elements. In this case, the tube is preferably guided through the openings of the disc elements. The tube is thereby inserted so deeply into the disc stack until it opens into one of the channels, which is assigned to the desired flow channel. In the present case a channel of the first flow channel.

It is also preferable if the first connection element is designed as a tube and the tube leads from the first region through the second region to the fluid inlet of the collector, wherein the tube is only in fluid communication with the first region of the first flow channel.

In order to integrate the collector at the most favorable for the entire work process of the capacitor body, it is particularly advantageous if the collector is connected directly to the Enthitzungs- and condensation area. This first region of the condenser, viewed in the flow direction of the refrigerant, is located in front of the second region in which the subcooling takes place.

In order to guide the entire refrigerant from this first region of the first flow channel into the collector, the tube is dimensioned so that it passes through all the disk elements of the second region and opens into a channel of the first region. In this way, the refrigerant is passed over the second area directly into the collector.

In a further preferred embodiment it can be provided that the channels forming the first flow channel can be flowed through by the refrigerant in series and / or in parallel.

By a serial and / or parallel flow advantages, especially with regard to the heat transfer to be realized, can be achieved. Areas can be created in which the refrigerant flows through the first flow channel in cocurrent or in countercurrent to the coolant.

In addition, it may be advantageous if the channels forming the second flow channel can be flowed through by the coolant in series and / or in parallel.

Likewise, as with the first flow channel, advantages can be achieved in the heat transfer to be achieved. In particular, by a targeted influencing of the flow direction of the first and the second flow channel, a continuous flow in countercurrent of the refrigerant and the coolant can be achieved.

In addition, an advantageous design of the fluid inlets and fluid outlets of the condenser can be achieved by influencing the flow-through principle.

According to a particularly favorable development of the invention, it can be provided that a fluid inlet or fluid outlet of the second flow channel has a second tube which is in fluid communication with another channel of the second flow channel.

By connecting the second flow channel with a tube as a function of the fluid inlet or fluid outlet, it can be achieved that both the fluid inlet and the fluid outlet can be arranged at a common end region of the disk stack.

It is also advantageous if the other channel is one of the last channels of the second flow channel, which lies substantially opposite the insertion side of the tube in the disc stack.

In this way it is achieved that the refrigerant or the coolant flows through the entire condenser or the flow path provided therein, before it flows back through the pipe again through the entire condenser and at the same end portion of the disk stack where it has flowed into the disk stack also emanates again.

Furthermore, it is preferable if the second flow channel can be flowed through in series and a fluid inlet and a fluid outlet of the second flow channel are each arranged at the same end region of the disk stack.

By arranging the fluid inlet and the fluid outlet at the same end region of the disk stack, the condenser can be designed to be particularly compact.

In a particularly favorable embodiment of the invention, it is also provided that the second region of the first flow channel with a third flow channel forms an internal heat exchanger in stacked disk design, wherein the first and the third flow channel can be flowed through by a refrigerant.

The subcooling section of the second region is replaced in this embodiment by an internal heat exchanger. The subcooling of the refrigerant does not take place here by a heat transfer between the refrigerant and the coolant.

By means of an internal heat exchanger, the cooling of the refrigerant in the condenser can be amplified once again, which leads to an overall higher performance of the condenser. In this case, refrigerant flows in an internal heat exchanger, generally in countercurrent to one another, in two different flow channels.

The refrigerant, which thereby flows in the two flow channels, is supplied to the inner heat exchanger from different sections of the refrigerant circuit, whereby the largest possible temperature difference between the two flow channels is achieved.

Furthermore, it is expedient if the first flow channel has a third region which follows the second region and the subcooling of the refrigerant serves, wherein the third region has a third flow channel for a fluid, wherein the first and the third flow channel at least in sections as a heat exchanger, preferably as an internal heat exchanger in stacked disk design, can be ausgestaltbar.

The arrangement of an internal heat exchanger after the second area, in which the supercooling takes place, further lowers the temperature of the refrigerant. There is a greater undercooling of the refrigerant, as by the pure use of a subcooling or an internal heat exchanger.

In this case, the condenser is constructed so that the heat transfer between the refrigerant and the refrigerant takes place in the first area in which the refrigerant is deprived and condensed. In the second area, in which the refrigerant is subcooled after the flow through the collector, the heat transfer also takes place between the refrigerant and the coolant. In the third region, the heat transfer then takes place between the refrigerant in a first temperature range and the refrigerant in a second temperature range.

The second flow channel of the coolant is guided through the condenser so that only the first region and the second region are flowed through and the coolant is subsequently led out of the condenser.

The third region of the disk stack has a fluid inlet and a fluid outlet, via which the third flow channel can be flown with the refrigerant.

According to a further preferred embodiment, it can be provided that the third flow channel can be supplied with a coolant independently of the first flow channel or with a coolant independently of the second flow channel.

The independent supply of the third flow channel with either a coolant or a refrigerant is particularly advantageous, since so a higher temperature difference between the third flow channel and the first flow channel can be achieved. In particular, if the third flow channel, an additionally cooled fluid is supplied.

Furthermore, it is preferable if the collector is in fluid communication with only the first portion of the first flow passage via a pipe leading through a portion of the disk stack forming the fluid inlet into the accumulator and the fluid outlet of the accumulator is formed via another pipe which passes through a portion of the disk stack and is in fluid communication only with the second portion of the first flow channel.

Through this connection of the collector to the first and the second region of the first flow channel by means of pipes, the collector can be placed outside the disk stack and at the same time the simple construction of the disk stack can be achieved by using many identical disk elements.

The tubes are guided by the disc elements of the portions of the disc stack, with which they are not supposed to be in fluid communication, and then open into the channels of the disc stack, with which they are in fluid communication. Thus, the collector can be effectively supplied to the refrigerant from the region of the first flow channel, in which the refrigerant is already completely condensed.

It can also be the refrigerant, after flowing through the collector, the area of the first flow channel again supplied, which adjoins the first region. The tubes are dimensioned so that the refrigerant is discharged from one of the channels of the first flow channel into the collector and then in the subsequent channel of the first flow channel again is initiated. The two channels of the first flow channel are only in fluid communication with each other via the collector.

The openings of the disc element of the channel, from which the refrigerant is diverted, are so closed that no liquid can take place directly into the subsequent channel.

A further preferred embodiment of the invention provides that the fluid inlet and / or the fluid outlet of the internal heat exchanger are formed by a tube.

The connection of the inner heat exchanger via one or two tubes is advantageous because in this way the simple structure of the disk stack stack of the capacitor can be maintained. The refrigerant, which flows through the third flow channel of the inner heat exchanger, can be selectively guided through a pipe into a channel of the third flow channel and also be selectively led out of a channel of the third flow channel.

Further, it is preferable that the discs have apertures with or without passage to create or seal fluid communication between adjacent channels.

If directly adjacent disc elements have mutually opposite openings with passages, the fluid flows directly into the next but one channel of the disk stack. This ensures that a change between channels that belong to the first flow channel and channels that belong to the second flow channel is achieved in the disk stack. In this case, a uniform distribution can be generated so that a channel of the first flow channel always follows a channel of the second flow channel. Even deviating distributions can be generated with this method.

Moreover, it is advantageous if the tubes are guided through openings in the disc elements and with at least a portion of the disc elements, in particular with the passages, are soldered.

By inserting the tubes into the openings and soldering the tubes with the disc elements and in particular with the passages, a compact unit is achieved, which is characterized by a high strength. Advantageously, the tubes can be soldered to the disc stack in a single operation here.

This is particularly advantageous, in particular with regard to an optimized production process.

In addition, it is preferable if the first connection element is a tube and the second connection element is a flange or vice versa.

By means of an embodiment of the first and second connecting element as described above, an advantageous connection of the collector to the capacitor can be achieved. In particular, a very stable connection can be achieved by means of a flange, while the tube can be used to selectively supply the fluid into the condenser.

According to a further alternative embodiment, it can be provided that the collector is designed for filtering and / or drying the refrigerant.

In addition to the task of stocking, the collector advantageously also implements the function of drying the refrigerant via suitable means for drying and further filtering the refrigerant. In this way, the refrigerant can be easily withdrawn excess moisture and continue to be freed of impurities. The integration of these functions in a single component is particularly advantageous in terms of the variety of parts and the space utilization. It is particularly advantageous if the first section in the second channel has a plurality of flow paths through which the flow direction is alternately reversed.

It is also advantageous if the second section in the second channel has a plurality of flow paths through which the flow direction is alternately reversed in succession.

Advantageous developments of the present invention are described in the subclaims and in the following description of the figures.

Brief description of the drawings

Fig.1

eine schematische Ansicht eines Kondensators, welcher einen Bereich zur Enthitzung des Kältemittels aufweist und einen Bereich zur Unterkühlung des Kältemittels, wobei ein Sammler unterhalb des Kondensators angeordnet ist,

Fig. 2

eine schematische Ansicht eines Kondensators, gemäß Figur 1, mit der Darstellung zweier Strömungskanäle, wobei das Kältemittel den Kondensator seriell durchströmt und das Kühlmittel den Kondensator parallel durchströmt,

Fig. 3

eine schematische Ansicht eines Kondensators, gemäß der Figuren 1 und 2, mit der Darstellung zweier Strömungskanäle, wobei das Kältemittel den Kondensator seriell durchströmt und das Kühlmittel den Kondensator seriell durchströmt,

Fig. 4

eine schematische Ansicht eines Kondensators, gemäß der Figuren 1 bis 3, mit der Darstellung zweier Strömungskanäle, wobei das Kältemittel den Kondensator seriell durchströmt und das Kühlmittel den Kondensator sowohl seriell, als auch parallel durchströmt,

Fig. 5

eine schematische Ansicht eines Kondensators, gemäß der Figuren 1 bis 4, mit der Darstellung zweier Strömungskanäle, wobei das Kältemittel den Kondensator seriell durchströmt und das Kühlmittel den Kondensator seriell durchströmt, wobei das Kühlmittel mittels eines Rohres durch den Kondensator geleitet wird,

Fig. 6

eine schematische Ansicht eines Kondensators, gemäß der Figuren 1 und 2, wobei der Bereich zur Unterkühlung des Kältemittels durch einen inneren Wärmeübertrager gebildet ist, mit der Darstellung zweier Strömungskanäle, wobei das Kältemittel den Kondensator seriell durchströmt und das Kühlmittel den Kondensator parallel durchströmt,

Fig. 7

eine schematische Ansicht eines Kondensators, wobei auf den Enthitzungsbereich ein Unterkühlungsbereich folgt, an welchen ein innerer Wärmeübertrager angeschlossen ist,

Fig. 8

eine Schnittansicht einer Verbindungsstelle, an welcher ein Rohr in einen der Kanäle innerhalb des Kondensators mündet, und

Fig. 9

eine Schnittansicht einer Verbindungsstelle, an welcher zwei Rohre in zueinander benachbarte Kanäle des Kondensators münden.

In the following the invention will be explained in detail by means of embodiments with reference to the drawings. In the drawings show:

Fig.1

a schematic view of a condenser, which has a region for desuperheating of the refrigerant and a region for subcooling of the refrigerant, wherein a collector is arranged below the capacitor,

Fig. 2

a schematic view of a capacitor, according to FIG. 1 with the representation of two flow channels, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser in parallel,

Fig. 3

a schematic view of a capacitor, according to the Figures 1 and 2 with the representation of two flow channels, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser in series,

Fig. 4

a schematic view of a capacitor, according to the FIGS. 1 to 3 with the representation of two flow channels, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser both serially and in parallel,

Fig. 5

a schematic view of a capacitor, according to the FIGS. 1 to 4 with the representation of two flow channels, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser in series, wherein the coolant is passed through the condenser by means of a tube,

Fig. 6

a schematic view of a capacitor, according to the Figures 1 and 2 , wherein the area for subcooling the refrigerant is formed by an internal heat exchanger, with the representation of two flow channels, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser in parallel,

Fig. 7

1 is a schematic view of a condenser, wherein the superconducting area is followed by a subcooling area, to which an internal heat exchanger is connected,

Fig. 8

a sectional view of a junction at which a tube opens into one of the channels within the capacitor, and

Fig. 9

a sectional view of a junction at which two tubes open into adjacent channels of the capacitor.

Preferred embodiment of the invention

In the following FIGS. 1 to 7 different embodiments of a capacitor 1, 60, 70 are shown in stacked disc design. These are capacitors 1, 60, 70 for use in an air conditioning system for motor vehicles. All shown capacitors 1, 60, 70 are formed from a multiplicity of disc elements stacked on top of one another to form a slice stack 11, 68, 87.

The essential advantage of the construction as a condenser 1, 60, 70 in stacked disk design is that the disk elements are largely identical and only the outer terminal plates and individual, built in the stack deflection or blocking plates, which deflect or block the inner flow channels of the differ fundamentally identical shape of the disc elements. This allows a low-cost and easy production.

In the FIGS. 1 to 7 the capacitors 1, 60, 70 are indicated only by a schematic diagram. The individual portions of the capacitors 1, 60, 70, such as the Enthitzungsbereich 3, 80 or the subcooling 4, 81 and the region of an internal heat exchanger 61, 82 are shown in the figures only as cuboidal elements.

Each of these cuboid elements actually consists of a plurality of disc elements. These disk elements are stacked on top of one another and, by means of a special arrangement of openings which may have passages, form a multiplicity of individual channels which, due to the design of the individual disk elements, are combined to form flow channels which carry either a coolant or a refrigerant.

The flow channels of the coolant and the flow channels of the refrigerant are always adjacent to each other. In simple embodiments, it may be that channels for the refrigerant and channels for the coolant in one equally distributed alternating order are arranged. Likewise, it is conceivable to choose a deviating from the uniform distribution distribution of refrigerant to coolant channels. It is conceivable to realize the alternating rhythm between coolant and coolant channels by a ratio of 1: 1.

The flow channels of the coolant and the refrigerant are in the FIGS. 1 to 7 also indicated only schematically. Each of the cuboidal elements is traversed in the figures only once by a refrigerant or coolant flow channel. This illustration is intended to illustrate only the flow principle of the individual capacitors 1, 60, 70 and has no delimiting effect.

The flow channels of the refrigerant 25, 64, 73, 79 are each represented by a dotted line. The flow channels of the coolant 26, 42, 52, 67, 76 are each represented by a solid solid line.

The in the FIGS. 1 to 7 shown flow directions of the refrigerant and the coolant are each only one example and can in reality just as in opposite directions to those in the FIGS. 1 to 7 be executed directions shown.

The FIG. 1 shows a condenser 1, which consists of a Enthitzungsbereich 3 and a subcooling 4. The Enthitzungsbereich 3 is used for desuperheating a refrigerant and the condensation of the refrigerant from its vapor phase into a liquid phase. For the purpose of desuperheating the refrigerant is brought into a thermal exchange with a coolant, which also flows through the Enthitzungsbereich 3. Down to the Enthitzungsbereich 3 a subcooling 4 is connected. In this subcooling region 4, the completely liquid refrigerant is further cooled by a further thermal exchange with a coolant.

Below the condenser 1, a collector 2 is arranged, which is flowed through by the refrigerant. The task of the collector 2 is to store, filter and dry the refrigerant. By introducing a collector 2 in the refrigerant circuit can be provided for an always constant amount of refrigerant in the refrigerant circuit, since the collector 2 is a compensation reservoir, whereby refrigerant volume fluctuations in the refrigerant circuit can be compensated.

The collector 2 has at its fluid inlet 12 a tube 5, which is guided through the sub-cooling region 4 and is in the decompression region 3 in fluid communication with the flow channel of the refrigerant. The fluid outlet 6 of the collector 2 is in turn in fluid communication with the flow channel of the refrigerant in the subcooling region 4. In this way, it is ensured that the refrigerant is completely conducted from the Enthitzungsbereich 3 in the collector 2.

After flowing through the collector 2, the refrigerant is completely returned to the subcooling 4. The collector 2 thus represents the passage of fluid from the desuperheating area 3 into the subcooling area 4, in particular for the refrigerant.

At the upper end portion of the disk stack 11 of the capacitor 1 openings 8, 9, 10 are arranged. These can represent fluid inlets as well as fluid outlets, depending on the design of the inner flow channels. Also shown at the lower end of the disk stack 11 is an opening 7, which may also be a fluid inlet or a fluid outlet, depending on the design of the inner flow channels.

The FIG. 2 also shows a capacitor 1, which corresponds to the in FIG. 1 shown capacitor 1 corresponds substantially. In addition to the FIG. 1 are now in FIG. 2 Flow channels 25, 26 shown for a coolant and a refrigerant. The refrigerant flows through a arranged at the upper end portion of the disk stack 11 fluid inlet 21 in the Enthitzungsbereich 3 of the condenser 1. There it flows through the channels formed by the disc elements, which are associated with the flow channel 25 of the refrigerant.

Among other things, it flows through openings 24, which are arranged between the individual disc elements. After flowing through the de-icing area 3, the refrigerant flows into the collector 2 via the pipe 5. There it flows through the collector 2 for the purpose of storage, filtration and drying and then flows through the fluid outlet 6 of the collector 2 into the subcooling region 4 of the condenser 1. After flowing through the subcooling region 4, the refrigerant flows out of the subcooling region 4 through the fluid outlet 23 ,

The coolant flows through the fluid inlet 20 at the upper end portion of the condenser 1 into the dewarning area 3. In contrast to the refrigerant, which flows through the individual channels in series, the coolant flows through the individual channels of the Enthitzungsbereichs 3 and the subcooling 4 in parallel. For this purpose, the coolant through upper openings 24, which lie in an approximately rectilinear imaginary extension to the fluid inlet 20 of the coolant, from top to bottom through the disk stack 11 and then spreads across the width of the capacitor 1. After the coolant over the entire width of the Condenser 1, it then flows through a plurality of openings 24 in the disc elements from bottom to top through the fluid outlet 22 of the coolant from the condenser 1.

By the execution of the flow channel 26 of the coolant in parallel flow and the flow channel 25 of the refrigerant in serial flow arise in the condenser 1 areas in which the refrigerant to the coolant flows in countercurrent, but also areas where the refrigerant with the refrigerant in the DC flows.

The FIG. 3 shows a similar structure as it already in the Figures 1 and 2 was presented. The flow channel 25 of the refrigerant is analogous to FIG. 2 through the condenser 1 of FIG. 3 arranged. Deviating from FIG. 2 the coolant flows in FIG. 3 now no longer in a parallel arrangement through the channels of the condenser 1, but flows through the condenser 1 as well as the refrigerant in series.

For this purpose, the coolant flows through the fluid inlet 30 at the lower region of the condenser 1 into the subcooling region 4. There it is distributed over the width of the capacitor 1 and flows through an inner opening 24 upwards into the Enthitzungsbereich 3. There it also spreads over the entire width of the capacitor 1 and flows upward through a further inner opening 24 in the upper Area of the Enthitzungsbereichs 3 and finally flows after a redistribution across the width of the capacitor 1 through the fluid outlet 31 from the condenser 1 from. The flow channel 32 of the coolant extends in the FIG. 3 , So as well as the flow channel 25 of the refrigerant in series through the individual channels in the interior of the condenser 1. By in FIG. 3 As shown, the refrigerant flow over the entire condenser 1 is in countercurrent to the coolant.

The FIG. 4 again shows a capacitor 1 analogous to FIGS. 1 to 3 , The refrigerant flow channel 25 is analogous to Figures 2 and 3 executed. Deviating from the Figures 2 and 3 Now, the flow channel 42 of the coolant is disposed within the capacitor 1, that there are both areas in which the capacitor is flowed through in parallel, as well as areas in which it is passed through in series.

For this purpose, the coolant flows through the fluid inlet 40 into the subcooling region 4 of the condenser 1. There it is distributed both over the width of the condenser 1 as well as upwardly through an inner opening 24 in the Enthitzungsbereich 3. In the desuperheating 3, the coolant is also distributed over the entire width of the condenser 1. The coolant flow in the subcooling 4 also flows over an inner opening 24 upwards into the Enthitzungsbereich 3, where the coolant flow from the sub-cooling region 4 and the Enthitzungsbereich 3 reunites. Together, the coolant flows there via a further inner opening 24 in the upper region of the Enthitzungsbereichs 3 and there again distributed over the entire width of the capacitor 1 and finally flows out of the condenser 1 via the fluid outlet 41 of the coolant.

In this way, the condenser 1 is partially flowed through in parallel and partially in series by the coolant. This results in areas in which the coolant flows with the refrigerant in countercurrent, as well as areas in which the coolant flows with the refrigerant in the DC flow.

The FIG. 5 also shows a capacitor 1 analogous to the embodiments of FIGS. 1 to 4 , The flow channel 25 of the refrigerant is again unchanged from the FIGS. 2 to 4 executed. Notwithstanding the preceding figures, the coolant is now purely serially passed through the condenser 1 and is on the condenser by a, arranged at one of its end portions, fluid inlet 50 and fluid outlet 51 and removed.

However, the coolant is not distributed over the width of the condenser 1 as in the preceding figures, but is guided through a pipe 53, which is connected to the fluid inlet 50, through openings 54 in the disk elements down into the subcooling region 4 of the condenser 1 , Only in the subcooling region 4 does the coolant leave the tube 53 and spread over the width of the condenser 1.

On the opposite side of the condenser 1, the coolant flows again through an inner opening 24 in the Enthitzungsbereich 3, where it is distributed over the width of the capacitor 1 again. It then flows through a further opening 24 in the upper region of the Enthitzungsstrecke and is also distributed there across the width of the capacitor 1, before it flows out of the condenser 1 via the fluid outlet 51 of the coolant.

The coolant thus flows completely serially through the regions of the condenser 1. The coolant flowing in the flow channel 52 thus flows countercurrently to the refrigerant in the flow channel 25 at all times.

The FIG. 6 shows a capacitor 60, which unlike the capacitors 1 of FIGS. 1 to 5 now has a Enthitzungsbereich 3 in the upper part and arranged underneath an internal heat exchanger 61, which in place of the subcooling 4 of the FIGS. 2 to 5 occurs. The flow channel 25 of the refrigerant is analogous to FIGS. 2 to 5 passed through the capacitor 60.

The coolant flows into the condenser 60 through a fluid inlet 65 at the top of the disk stack 68 of the condenser 60. There, it is distributed through an inner opening 24 in depth via the Enthitzungsbereich 3 and then distributed there across the width of the capacitor 60 before it flows out through openings 24 and the fluid outlet 66 back out of the condenser 60.

In the FIG. 6 is the Enthitzungsbereich 3 flows through the coolant in parallel. The desuperheating region 3 is further serially flowed through by the refrigerant through the flow channel 25 of the refrigerant, thereby adjusting portions of the direct current and portions of the counterflow between the refrigerant and the coolant.

The region 61, which represents the inner heat exchanger, is not flowed through by the coolant. Instead, the inner heat exchanger 61 on a third flow channel 64, which is also traversed by the refrigerant. For this purpose, the refrigerant flows through a fluid inlet 62 into the inner heat exchanger 61 and is distributed over the width of the condenser 60 before it flows out of the condenser 60 via the fluid outlet 63. In the inner heat exchanger 61, the refrigerant in the flow channel 64 and the refrigerant in the flow channel 25 are in countercurrent to each other. In this way, a higher heat transfer between the two flow channels 64, 25 can be achieved.

The refrigerant, which flows through the flow channel 64 of the inner heat exchanger 61, comes as the refrigerant in the flow channel 25 from the same refrigerant circuit. The refrigerant in the flow channel 64 differs from the refrigerant in the flow channel 25 substantially by its temperature. Since it is intended that refrigerant in the flow channel 25 within the inner Heat exchanger 61 continue to cool, the refrigerant in the flow channel 64 has a lower temperature, whereby the refrigerant in the flow channel 25 further heat can be withdrawn.

In the FIG. 6 embodiment shown represents an alternative to that in the FIGS. 1 to 5 Instead of subcooling by a thermal transition between a coolant and the refrigerant, here a thermal transition between the refrigerant of a first temperature level and the refrigerant of a second temperature level is generated.

The FIG. 7 now shows a capacitor 70, which consists of a disk stack 87. In this case, the capacitor 70 is a combination of the embodiments of FIGS. 1 to 6 , At the upper Enthitzungsbereich 80 is followed at the bottom of a subcooling 81. An internal heat exchanger 82 is connected to the subcooling region 81 at the bottom.

The upper portion of the condenser 70, which consists of the Enthitzungsbereich 80 and the subcooling 81, is a coolant according to the flow, which is already in FIG. 2 for the coolant is shown, flows through. For this purpose, a coolant flows through the fluid inlet 74 into the Enthitzungsbereich 80 and there is distributed through inner openings along the depth of the condenser 70 into the sub-cooling region 81. It then flows through the capacitor 70 in its width uniformly, before it at the opposite end by internal openings flows upward and out of the condenser 70 via the fluid outlet 75. The coolant flows through the condenser 70 in its flow channel 76 completely parallel.

The refrigerant flows through a fluid inlet 71 into the Enthitzungsbereich 80 and flows through the Enthitzungsbereich 80 serially. The refrigerant then flows from the Enthitzungsbereich 80 via a pipe 84 which passes through the subcooling 81 and the inner heat exchanger 82, directly into the collector 2. From the collector second The refrigerant flows via the pipe 83 back into the subcooling region 81 and is distributed over the width of the capacitor 70 thereafter. It then flows through an inner opening from the subcooling 81 into the underlying inner heat exchanger 82 and also flows through the individual channels of the internal heat exchanger 82 serially before it flows out of the inner heat exchanger 82 via the fluid outlet 72 from the condenser 70.

The inner heat exchanger 82 is also traversed by a refrigerant. For this purpose, a refrigerant flows via a fluid inlet 77, which may be formed as a tube 85, into the internal heat exchanger 82. There it is distributed over the width of the inner heat exchanger 82 and flows through an inner opening in the upper region of the inner heat exchanger 82. There it also spreads again across the width of the capacitor 70 and finally flows through a tube 86 which passes through the lower Area of the internal heat exchanger 82 leads out of the condenser 70. The tube 86 thus also forms the fluid outlet 78 of the flow channel 79 of the refrigerant.

The in the FIGS. 1 to 7 shown positions of the fluid inlets or fluid outlets are each exemplary. Deviating orientations, for example laterally on the condenser, are just as conceivable as the arrangement of a fluid inlet or outlet in a middle region of the condensers. Rather, the FIGS. 1 to 7 Embodiments show that it is possible to lead a refrigerant flow and a coolant flow both in the DC principle as well as in the countercurrent principle by the individual regions of the capacitors 1, 60, 70. This results in different advantages for the arrangement of the fluid inlets or fluid outlets. Depending on the intended application of the capacitors 1, 60, 70, a corresponding internal design of the disk stack 11, 68, 87 of the capacitors 1, 60, 70 make.

Furthermore, the capacitors 1, 60, 70 can be selectively produced from a combination of desuperheating area 3, 80, subcooling area 4, 81 and internal heat exchanger 61, 82. Optimal configurations can be created depending on the application all follow a simple structure of individual disc elements and thus are very flexible in their construction.

The in the FIGS. 1 to 7 shown pipes are also inexpensive to manufacture and are introduced in the simplest case in the disk stack 11, 68, 87, thereby leading through inner openings of the disk elements. Advantageously, this is done in an early part of the production process, so that the disc elements can be soldered to the individual tubes in one operation. In this case, the tubes are in particular soldered to the openings which have passages.

The FIG. 8 shows a section through a connecting element, with which, for example, the collector 2 to the respective lower portion of the capacitors 1, 60 in the FIGS. 1 to 6 can be connected. For this purpose, the connection element has a tube 90, which forms a flow channel 96 between a fluid inlet 93 and a fluid outlet 94. This tube 90 corresponds in the FIGS. 1 to 6 the pipe 5, which connects the collector 2 with the lower part of the Enthitzungsbereichs 3. At the same time, the collector 2 is in fluid communication via the flow channel 97, which is formed between the fluid inlet 91 and the fluid outlet 92, with the subcooling region 4 or the internal heat exchanger 61.

Main task of in FIG. 8 connecting element shown is that refrigerant from different channels within the capacitors 1, 60 derive from the Enthitzungsbereich 3 and then the sub-cooling region 4 or the inner heat exchanger 61, which is arranged below the Enthitzungsbereichs 3, re-supply.

As already described, the tube 90 engages through at least one of the disk elements of the capacitors 1, 60. The capacitor is in FIG. 8 designated by the reference numeral 95. It can be seen in particular that the flow channel 97 extends completely around the tube 90 around.

The FIG. 9 shows a further alternative connection element, which in particular in an arrangement according to the FIG. 7 can be used. In this case, a first tube 100 is arranged parallel to a second tube 101. The tube 100 forms a flow channel 106 which extends between a fluid inlet 102 and a fluid outlet 103. The tube 101 also forms a flow channel 107, which runs between a fluid inlet 104 and a fluid outlet 105. The capacitor is in FIG. 9 indicated by the reference numeral 108.

Main task of the connection element of FIG. 9 it is to discharge a fluid from a region of the condenser 1, 60, 70, 108 and supply it to the collector 2. This is done via the longer tube 101. The return of the fluid from the collector 2 into the condenser 1, 60, 70, 108 is done via the shorter tube 100. By the length of the tubes 100, 101 and thus resulting different heights of the fluid outlets 103rd , 105 it is possible to divert the fluid at different heights relative to the condenser 1, 60, 70, 108 from the condenser 1, 60, 70, 108 and feed it again.

The in the FIGS. 8 and 9 shown fluid inlets and fluid outlets can also be arranged reversed depending on the flow direction.

Claims (17)

1. A condenser (1, 60, 70) of stacked plate design, having a first flow channel (25, 64, 73, 79) for a refrigerant and having a second flow channel (26, 31, 42, 52, 67) for a coolant, wherein a plurality of plate elements is provided, which form channels adjacent to each other between the plate elements when stacked on top of each other, wherein a first subset of the channels is associated with the first flow channel (25, 64, 73, 79) and a second subset of the channels is associated with the second flow channel (26, 31, 42, 52, 67), wherein the first flow channel (25, 64, 73, 79) has a first region (3, 80) for desuperheating and condensing the vaporous refrigerant and a second region (4, 81, 62) for subcooling the condensed refrigerant, having a receiver (2) for storing a refrigerant, wherein a refrigerant transfer from the first region (3, 80) to the second region (4, 81, 62) leads through the receiver (2), wherein the receiver (2) is in fluid communication with the first region (3, 80) by means of a first connection element which forms the fluid inlet (12) of the receiver (2), wherein a second connection element is in fluid communication with the second region (4, 81, 62) as a fluid outlet (6) of the receiver (2), characterised in that the first connection element or the second connection element is a tube (5) which passes through a number of plate elements by means of openings in plate elements.
2. The condenser (1, 60, 70) as claimed in claim 1, characterised in that the first connection element (5) is designed as a tube and the tube leads from the first region (3, 80) through the second region (4, 81, 61) to the fluid inlet (12) of the receiver (2), wherein the tube is in fluid communication only with the first region (3, 80) of the first flow channel (25, 64, 73, 79).
3. The condenser (1, 60, 70) as claimed in claim 1 or 2, characterised in that the second connection element (6) is designed as a tube and the tube leads from the fluid outlet of the receiver through the first region into the second region.
4. The condenser (1, 60, 70) as claimed in one of the preceding claims, characterised in that a fluid inlet (50) or fluid outlet of the second flow channel (26, 31, 42, 52, 67) has a second tube (53) which is in fluid communication with another channel of the second flow channel (26, 31, 42, 52, 67).
5. The condenser (1, 60, 70) as claimed in claim 4, characterised in that the other channel is one of the last channels of the second flow channel (26, 31, 42, 52, 67) which lies substantially opposite the insertion side of the tube (53) in the plate stack.
6. The condenser (1, 60, 70) as claimed in one of the preceding claims, characterised in that the second flow channel (52) allows flow in series and a fluid inlet (50) and a fluid outlet (51) of the second flow channel (52) are each arranged in the same end region of the plate stack.
7. The condenser (1, 60, 70) as claimed in one of the preceding claims, characterised in that the second region of the first flow channel (25) forms an internal heat exchanger (61) of stacked plate design with a third flow channel (64), wherein a refrigerant can flow through the first (25) and the third flow channel (64).
8. The condenser (1, 60, 70) as claimed in one of the preceding claims, characterised in that the first flow channel (73) has a third region (82) which follows the second region (4, 81) and is used to subcool the refrigerant, wherein the third region (82) has a third flow channel (79) for a fluid, wherein the first and the third flow channel can be configured at least partially as heat exchangers, preferably as internal heat exchangers (82) of stacked plate design.
9. The condenser (1, 60, 70) as claimed in claim 8, characterised in that the third flow channel (79) can be supplied with a refrigerant independently of the first flow channel or with a coolant independently of the second flow channel.
10. The condenser (1, 60, 70) as claimed in claim 7 to 9, characterised in that the receiver (2) is in fluid communication only with the first region (80) of the first flow channel (73) via a tube (84) which leads through part of the plate stack (87) and forms the fluid inlet into the receiver (2) and the fluid outlet of the receiver (2) is formed by another tube (83) which leads through part of the plate stack (87) and is in fluid communication only with the second region (81) of the first flow channel (73).
11. The condenser (1, 60, 70) as claimed in claim 7 to 10, characterised in that the fluid inlet (77) and/or the fluid outlet (78) of the internal heat exchanger (82) is formed by a tube (85, 86).
12. The condenser (1, 60, 70) as claimed in one of the preceding claims, characterised in that the plates have openings (24) with or without a rim in order to produce or seal off a fluid connection between adjacent channels.
13. The condenser (1, 60, 70) as claimed in one of the preceding claims, characterised in that the tubes (5, 50, 83, 84, 86, 87) are passed through openings (24) in the plate elements and are brazed to at least a subset of the plate elements, in particular to the rims.
14. The condenser (1, 60, 70) as claimed in one of the preceding claims, characterised in that the first connection element is a tube and the second connection element is a flange or vice versa.
15. The condenser (1, 60, 70) as claimed in one of the preceding claims, characterised in that the receiver (2) is designed to filter and/or dry the refrigerant.
16. The condenser (1, 60, 70) as claimed in at least one of the preceding claims, characterised in that the first section in the second channel has a plurality of flow paths through which the fluid flows in succession and in which the flow direction is in each case alternately reversed.
17. The condenser (1, 60, 70) as claimed in at least one of the preceding claims, characterised in that the second section in the second channel has a plurality of flow paths through which the fluid flows in succession and in which the flow direction is in each case alternately reversed.

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