EP2997318B1 - 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 according to claim 1.

State of the art

Condensers are used in refrigeration circuits of automotive air conditioning systems to cool and condense the refrigerant to the condensation temperature. Capacitors can have a collector which holds a volume of refrigerant. Volume fluctuations in the refrigerant circuit can be compensated for via this volume of 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 is 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 the tube-rib block and introduced into the collector.
In the case of capacitors in a stacking disk design, provision may be made for the collector to be attached to the disk stack as an additional layer in the form of disk elements.
In addition, in the prior art, solutions are known in which the refrigerant is led out of the stacked-disc condenser via a special distributor plate and fed to an external collector. After flowing through the collector, the refrigerant is returned to the condenser. US 2009/071189 A1 discloses a capacitor according to the preamble of claim 1. A disadvantage of the solutions of the prior art is in particular that an integration of capacitors, collectors and subcoolers is associated with great effort. The known from the prior art capacitors are characterized by a complex structure and increased manufacturing costs. This results in additional costs that make the use of such capacitors 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 invention relates to a capacitor in a stacked disk design, comprising a first flow channel for a refrigerant and a second flow channel for a coolant, wherein a plurality of disc elements is provided, which form stacked adjacent channels between the disc elements, wherein a first number of channels the a first number of channels is associated with the second flow channel, wherein the first flow channel has a first area for desuperheating and condensation of the vapor refrigerant and a second area for subcooling the condensed refrigerant, with a collector for storing a refrigerant, wherein a refrigerant transfer from the first region leads into the second region through the collector, wherein the collector via a first connection element, which forms a first fluid port of the collector, with the first Bere I am in fluid communication, wherein the collector is in fluid communication with the second region via a second connection element, which forms a second fluid connection of the collector, wherein the first connection element and / or the second connection element are formed by a tube which passes through openings in the Disc elements engages by a number of disc elements.
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 have 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, always leads to the end of the condenser completely 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 advantageous to integrate a collector in the refrigerant circuit. This is advantageously integrated at a point in the flow channel of the refrigerant, to which the refrigerant is already fully condensed, but not yet undercooled.

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 introduced into the disc stack such that 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 second region through the first region to a fluid connection of the collector, wherein the tube is in fluid communication with the second region of the first flow channel and the collector.

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 Enthitzungsbereich and the condensation region. 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 direct the entire refrigerant from the second region of the first flow channel into or out of the collector, the tube is dimensioned so that it passes through all the disk elements of the first region and opens into a channel of the second region. This way the refrigerant gets pass the first area directly into the collector or out of the collector.

Furthermore, it is preferable if at least one of the tubes has a taper and / or a shoulder and / or an at least partially encircling flange and / or a widening, by means of which it can be supported on one of the disc elements and fixed in the condenser.

A flange can be produced for example by upsetting, alternatively, the flange can also be designed as a separate component, which is attached to a pipe. The flange serves to support against one or more of the disc elements and contributes to a better seal.

Alternatively, a taper can be provided on one of the tubes, with which the tube can be inserted into an opening. A taper can be generated for example by a pressing or by a machining. An expansion can be generated for example by a hydroforming process.

Via one or more of these elements, a pipe can be supported particularly advantageously on the disk elements of the capacitor and fixed in the capacitor. The elements described above can serve in particular as a stop.

It is also expedient if at least one of the disk elements is designed as a separating disk and / or one of the disk elements as a deflecting disk.

A cutting disk differs essentially from a deflection disk in that the openings in the respective disk element, over which the channel formed between the disks is in fluid communication with an adjacent channel, are provided at different locations. Otherwise, the two disc elements may have a very similar or identical structure. The different arrangement of the openings can for example be achieved by a side-by-side juxtaposition of the disc elements.

A deflection disk is characterized in particular by the fact that it provides no opening with respect to the opening of the adjacent cutting disk, which allows an inflow of a fluid into one of the flow channels, and thus deflects or deflects the inflowing fluid within the channel.

Moreover, it is advantageous if the tube is supported in the condenser on a deflection plate.

By supporting the tube on a deflection plate, the movement of the tube into the condenser, in particular during the assembly process, is already limited by the stop of the tube on the deflection plate. This facilitates assembly and increases the stability of the capacitor.

Furthermore, it is preferable if the tube has radial and / or axial openings.

If the tube rests against a deflection disk, it is particularly advantageous if radial openings are provided through which a fluid can flow out of the pipe or into the pipe. The radial openings may be formed for example by holes, slots or other recesses. The openings are advantageously located at one of the end portions of the tube to create a defined overflow from the tube into one or more of the flow channels.

It is also advantageous if the tube is supported on one of the outer disc elements of the second region.

By an outer disk element is meant here in particular one of the disk elements, which closes off the second area, which is formed from a stack of a plurality of disk elements, to an adjacent area.

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

Moreover, it is expedient if a third tube is provided at the fluid inlet and / or at the fluid outlet of the second flow channel, which is in fluid communication with another channel of the second flow channel.

By connecting the fluid inlet or the fluid outlet of the respective first flow channel or the second flow channel, the fluid flowing through the corresponding flow channel can be guided past adjacent channels and thus introduced or discharged into or out of a predetermined channel. It can thereby be achieved a design of the capacitor, which has both the fluid inlet and the fluid outlet of the respective flow channel at a common end region.

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

In this way, it can be achieved that the refrigerant or the coolant flows through the entire condenser or the flow path provided within the condenser, before it flows back through the pipe through the entire condenser and at the same end region of the disk stack, in which it Slice stack has flowed, also flows out again.

Furthermore, it is preferable if the disc elements have openings with or without passage.

If adjacent disc elements directly adjacent to each other have openings with passages, the fluid flows directly into the next but one channel of the disk stack, since a flow passage is formed by the two opposing passages.

This ensures that a change between channels which belong to the first flow channel and channels which 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.

It is also advantageous if the at least one tube is guided through the openings in the disc elements and is soldered to at least a part of the disc elements, in particular the passages.

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.

Furthermore, it may be particularly advantageous if at least one of the tubes has an at least partially circumferential flange, via which it can be supported on one of the disc elements.

A flange can be generated as by upsetting, alternatively, the flange can also be designed as a separate component, which is attached to a pipe becomes. The flange serves to support against one or more of the disc elements and contributes to a better seal.

A preferred embodiment is characterized in that at least one of the tubes is chamfered at one end region or at both end regions.

A bevelled pipe is advantageously produced by a section through the pipe along a plane which is at a predeterminable angle to the central axis of the pipe. This results in a sweep of the tube. About such a tapered tube can be achieved, that the tube with the resulting tip on a stop surface, in particular on a disc element, can be supported within the capacitor and at the same time a fluid can flow into the tube.

It is also preferable if at least one of the tubes has a flexible region, wherein the tube can be compressed and / or stretched in the axial direction by the flexible region.

Over a flexible range, which allows the compensation of a compression or expansion, a change in length of the capacitor can be compensated. In particular, during the soldering process, a so-called settling occurs in the capacitor. This settlement is caused by a relative movement of the disc elements to each other during the soldering process. A flexible region in the tubes can thus prevent the occurrence of voltages within the capacitor. The flexible area can accommodate both compression due to settlement operations as well as stretching due to other mechanical or thermal influences.

In a particularly favorable embodiment of the invention, it is also provided that the flexible region is formed by a concertina-like design of the tube.

An accordion-like design of the flexible region makes it possible to absorb compressions and / or strains in a particularly simple manner. The flexible area is formed by folded material areas, which are moved towards each other in the event of compression and are moved away from each other in case of an expansion. The tube can be designed such that a compression or elongation can be absorbed once or several times.

In an alternative embodiment of the invention, it may be provided that the flexible region is formed from an elastic material, such as plastic or rubber, wherein a compression or expansion of the tube in the axial direction and / or in the radial direction is reversible.

An embodiment of the flexible body of a material, such as plastic or rubber is particularly advantageous to allow a reversible deformation of the tube. Plastics and rubber have a much higher formability to change than metallic materials.

Furthermore, it is preferable if at least one of the tubes is formed from a plurality of tube sections, wherein the tube sections are connected to one another in a fluid-tight manner.

A tube, which is formed from a plurality of pipe sections, can particularly advantageously represent a length compensation. This can be achieved by the pipe sections perform a relative movement to each other. Advantageously, the pipe sections are inserted into one another, wherein a pipe section has a smaller outer diameter than the inner diameter of the respective other pipe section. A fluid-tight connection of the respective pipe sections with each other is particularly advantageous in order to produce no unwanted mixing of the fluid streams within the capacitor.

Such a pipe construction is particularly suitable for compensating for the changes in length that occur during soldering of the disk stack. In particular The effect of heat can lead to so-called setting processes during soldering, as a result of which the individual disk elements at least partially slide into one another. This change in length can be compensated advantageously by a multi-part tube.

After completion of the soldering process, the pipe sections are then advantageously also soldered together, so that a relative movement of the sections is prevented from each other. In this way, the fluid tightness of the tube can be generated in a simple manner.

It may also be expedient if a first pipe section tapers in a funnel shape in the axial direction and the second pipe section widens in a funnel shape in the axial direction, wherein the two pipe sections are inserted into one another such that the relative movement between the second pipe section and the first pipe section by a striking of the widening area is limited at the tapered area.

By a funnel-shaped configuration of the pipe sections, a relative movement of the pipe sections to each other can be made possible and at the same time a stop are generated, which limits the relative movement. Advantageously, for this purpose, the first pipe section has an inner diameter which is sufficiently large so that the second pipe section can be moved within the first pipe section.

In addition, it is expedient if the tube is received in a connection element and is connected to this fluid-tight.

A connection element can be formed, for example, by a flange on the condenser or on the collector.

Furthermore, it is advantageous if the second region has a plurality of flow paths through which the refrigerant can flow, wherein the flow paths are each formed by individual channels of the first flow channel and / or are formed by subregions of individual channels of the first flow channel.

A plurality of flow paths for guiding the refrigerant in the second region of the first flow channel is advantageous in order to achieve improved heat transfer between the refrigerant and the coolant. In this case, the flow paths can be formed by channels, which are formed between adjacent disc elements, or by subregions of these channels. For this purpose, for example, release agents may be provided in the channels, whereby the channels are subdivided into subregions. Depending on the fluidic connection of the channels or the flow paths with each other, the individual flow paths can be flowed through in parallel or in series by the refrigerant. Furthermore, a flow of the refrigerant can be achieved in cocurrent and / or in countercurrent with the coolant.

It is also preferable if the second region has a plurality of channels, wherein at least individual channels of the second region are in thermal contact with the second flow channel, wherein the coolant and the refrigerant flow in cocurrent and / or countercurrent to each other through the channels of the the second region and the second flow channel are flowable.

A flow of refrigerant and coolant in a plurality of mutually adjacent channels is particularly advantageous in order to realize the largest possible heat transfer can. In this case, a particularly large heat transfer can be achieved in particular by a counterflow arrangement. Also, a mixed arrangement of passages in countercurrent and passages in the DC or a pure DC arrangement may be advantageous.

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, in particular 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.

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 first region or 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 path of the second region is at least partially replaced in one 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 an internal heat exchanger, in this case, refrigerant flows in two different flow channels, which are aligned such that a heat transfer between the fluids in the flow channels is made possible. Advantageously, the fluids flow in countercurrent to each other.

The refrigerant, which 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 fluids in the two flow channels is achieved.

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

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 because in this way a higher temperature difference between the third flow channel and the first flow channel can be achieved. This applies in particular when an additionally cooled fluid is supplied to the third flow channel.

Further, it is preferable if the collector is in fluid communication with the second 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 first 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.

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.

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 connection element, as described above, an advantageous connection of the collector to the condenser 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 storing the collector advantageously also implements the function of drying the refrigerant via suitable means for drying and further the filtering of the refrigerant. In this way, the excess moisture can be removed from the refrigerant and it can be further 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.

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 mit einer Darstellung zweier Strömungskanäle, wobei das Kältemittel den Kondensator seriell durchströmt und das Kühlmittel den Kondensator parallel durchströmt,

Fig. 2

eine schematische Ansicht eines Kondensators, gemäß der Figur 1, wobei das Kältemittel den Kondensator seriell durchströmt und das Kühlmittel den Kondensator seriell durchströmt,

Fig. 3

eine schematische Ansicht eines Kondensators, gemäß der Figuren 1 bis 2, wobei das Kältemittel den Kondensator seriell durchströmt und das Kühlmittel den Kondensator sowohl seriell, als auch parallel durchströmt,

Fig. 4

eine schematische Ansicht eines Kondensators, gemäß der Figuren 1 bis 3, 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. 5

eine schematische Ansicht eines Kondensators, gemäß der Figuren 1 bis 4, wobei das Kältemittel den Kondensator seriell durchströmt und über ein Rohr von oben in den Kondensator eingeleitet wird, wobei das Kühlmittel den Kondensator parallel durchströmt,

Fig. 6

eine schematische Ansicht eines Kondensators, wobei der Unterkühlbereich im Vergleich zu den Figuren 1 bis 5 vergrößert ist,

Fig. 7

eine schematische Ansicht eines Kondensators, wobei der Enthitzungsbereich im Vergleich zu den Figuren 1 bis 6 vergrößert ist,

Fig. 8

eine schematische Ansicht eines Kondensators, wobei zusätzlich zum Enthitzungsbereich und dem Unterkühlbereich ein innerer Wärmeübertrager vorgesehen ist,

Fig. 9

eine Schnittansicht durch den Anbindungsbereich, an welchem der Sammler an den Kondensator angebunden ist,

Fig. 10

eine detailliertere Schnittansicht des Anbindungsbereichs gemäß der Figur 9,

Fig. 11

eine Schnittansicht durch den Anbindungsbereich, wobei das Rohr zwei abgeschrägte Endbereiche aufweist, und

Fig. 12

zwei unterschiedliche Ausgestaltungen eines erfindungsgemäßen Rohres, wobei im linken Teil der Figur ein Rohr mit einem flexiblen Bereich dargestellt ist und im rechten Teil der Figur ein mehrteiliges Rohr.

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

2 a schematic view of a condenser with a representation of two flow channels, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser in parallel,

Fig. 2

a schematic view of a capacitor, according to the FIG. 1 wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser in series,

Fig. 3

a schematic view of a capacitor, according to the FIGS. 1 to 2 wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser both serially and in parallel,

Fig. 4

a schematic view of a capacitor, according to the FIGS. 1 to 3 in which the refrigerant flows through the condenser in series and the coolant flows through the condenser in series, the coolant being conducted through the condenser by means of a tube,

Fig. 5

a schematic view of a capacitor, according to the FIGS. 1 to 4 in which the refrigerant flows through the condenser in series and is introduced into the condenser from above via a tube, the coolant flowing through the condenser in parallel,

Fig. 6

a schematic view of a capacitor, wherein the subcooling area compared to the FIGS. 1 to 5 is enlarged,

Fig. 7

a schematic view of a capacitor, wherein the Enthitzungsbereich compared to the FIGS. 1 to 6 is enlarged,

Fig. 8

a schematic view of a condenser, wherein in addition to the Enthitzungsbereich and the subcooling an internal heat exchanger is provided,

Fig. 9

a sectional view through the connection region, at which the collector is connected to the capacitor,

Fig. 10

a more detailed sectional view of the connection area according to the FIG. 9 .

Fig. 11

a sectional view through the connection region, wherein the tube has two beveled end portions, and

Fig. 12

two different embodiments of a pipe according to the invention, wherein in the left part of the figure, a pipe is shown with a flexible region and in the right part of the figure, a multi-part pipe.

Preferred embodiment of the invention

In the following FIGS. 1 to 8 different embodiments of a capacitor 1, 1a, 70, 80 are shown in stacked disk design. These are capacitors 1, 1a, 70, 80 for use in an air conditioning system for motor vehicles. All shown capacitors 1, 1a, 70, 80 are formed of a plurality of disk elements stacked on each other to form a disk stack 11, 11a, 73, 93.

The essential advantage of the construction as a condenser 1, 1a, 70, 80 in stacked disk design is that the disk elements are largely identical and only the outer terminal plates and individual, built in the stack deflecting or blocking plates, which deflect or block the inner flow channels, differ from the basically identical shape of the disc elements. This allows a low-cost and easy production.

In the FIGS. 1 to 8 the capacitors 1, 1a, 70, 80 are indicated only by a schematic diagram. The individual portions of the capacitors 1, 1a, 70, 80, such as the Enthitzungsbereich 3, 72, 81 or the subcooling 4, 71, 82 and the Area of an internal heat exchanger 88 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.

In this case, the flow channels of the coolant and the flow channels of the refrigerant are arranged adjacent to each other. In simple embodiments, it can be provided that channels for the refrigerant and channels for the coolant are arranged in an equally distributed alternating sequence. Likewise, it is conceivable to choose a distribution deviating from the uniform distribution of refrigerant channels to coolant channels. Also, the alternating rhythm between coolant channels and refrigerant channels can be realized deviating from a ratio of 1: 1.

The flow channels of the coolant and the refrigerant are in the FIGS. 1 to 8 also indicated only schematically. Each of the cuboidal elements is in the FIGS. 1 to 8 flows through only once from a refrigerant passage or a coolant channel. This illustration is intended to illustrate only the flow principle of the individual capacitors 1, 1a, 70, 80 and has no delimiting or restrictive effect.

The flow channels of the refrigerant 25, 25a, 52, 60, 87 are each represented by a dotted line. The flow channels of the coolant 26, 26a, 32, 42, 52, 85 are each represented by a continuous line.

The in the FIGS. 1 to 8 shown flow directions of the refrigerant and the coolant are each only one example and can also counter to those in the FIGS. 1 to 8 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. At the top of the decarburization section 3, a subcooling section 4 is connected. In this subcooling region 4, the completely liquid refrigerant is further cooled below the condensation temperature 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, a volume compensation in the refrigerant circuit can be realized, 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 outlet 12 a tube 5, which is guided through the Enthitzungsbereich 3 and is in the subcooling 4 with the flow channel 25 of the refrigerant in fluid communication. The fluid inlet 6 of the collector 2 is in turn in fluid communication with the flow channel 25 of the refrigerant in the decompression region 3.

After flowing through the collector 2, the refrigerant is passed completely into the subcooling region 4. The collector 2 thus represents the passage of fluid from the decompression area 3 into the subcooling area 4.

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.

Inside the condenser 1 flow channels 25, 26 are shown for a refrigerant and a coolant. The refrigerant flows through the arranged at the lower end portion of the disk stack 11 fluid inlet 7 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.

After flowing through the Enthitzungsbereichs 3, the refrigerant flows through the fluid inlet 6 into the collector 2 into it. There it flows through the collector 2 for the purpose of storage, filtration and drying and then flows through the fluid outlet 12 through the tube 5 into the subcooling region 4 of the condenser 1. After flowing through the subcooling region 4, the refrigerant flows through the fluid outlet 8 at the upper end region the capacitor 1 addition.

The coolant flows through the fluid inlet 9 at the upper end region of the condenser 1 into the subcooling region 4. In contrast to the refrigerant, which flows through the individual channels in series, the coolant flows through the individual channels of the subcooling region 4 and of the de-icing region 3 in parallel. For this purpose, the coolant flows through inner openings from top to bottom through the disk stack 11 and is distributed over the width of the capacitor 1. After the coolant has flowed over the entire width of the capacitor 1, it then flows through a plurality of openings in the disk elements of down to the top through the fluid outlet 10 from the condenser 1. The openings through which the coolant flows in the condenser 1 down, or the openings through which the coolant flows in the condenser 1 upwards, each lie in alignment with each other.

In the condenser 1 results in the construction of both countercurrently flowed through areas as well as in the DC flow areas.

The FIG. 2 shows a similar structure, as it already in the FIG. 1 was presented. The flow channel 25 of the refrigerant is analogous to FIG. 1 through the condenser 1 of FIG. 2 arranged. Deviating from FIG. 1 the coolant flows in FIG. 2 now no longer in parallel 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 upper region of the condenser 1 into the subcooling region 4. There it is distributed over the width of the condenser 1 and flows via an inner opening down into another channel of the subcooling region 4. There, the coolant spreads again over the entire width before it flows through a further opening down into the Enthitzungsbereich 3. Finally, after a redistribution over the width of the condenser 1, the coolant flows out of the condenser 1 through the fluid outlet 31 at the lower end region.

The flow channel 32 of the coolant extends in the FIG. 2 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 the FIG. 2 As shown, the refrigerant flow over the entire condenser 1 is in countercurrent to the coolant flow.

The FIG. 3 shows a capacitor 1 analogous to Figures 1 and 2 , The refrigerant flow channel 25 is analogous to Figures 1 and 2 executed. Deviating from the Figures 1 and 2 Now, the flow channel 42 of the coolant is disposed within the capacitor 1, that both arise areas that are traversed in parallel, as well as areas that are flowed through serially.

For this purpose, the coolant flows through the fluid inlet 40 into the subcooling region 4 of the condenser 1. There it is distributed over both the width of the capacitor 1, as well as down through inner openings within the subcooling 4. The subcooling 4 is thereby completely flows through in parallel. The coolant then flows through openings from the subcooling region 4 into the desuperheating region 3. From there, the coolant flows out of the condenser 1 via the fluid outlet 41. The Enthitzungsbereich 3 is only flows through serially.

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 refrigerant flows in countercurrent with the refrigerant and areas in which the refrigerant flows with the refrigerant in the DC.

The FIG. 4 also shows a capacitor 1 analogous to the embodiments of FIGS. 1 to 3 , The flow channel 25 of the refrigerant is unchanged from the FIGS. 1 to 3 , Notwithstanding the preceding figures, the coolant is now passed completely in series through the condenser 1. The coolant flows through the fluid inlet 50 into the condenser 1 and out of the condenser 1 via the fluid outlet 51. Fluid inlet 50 and fluid outlet 51 lie in this case at a common end region of the condenser 1.

In this case, the coolant flows into the subcooling region 4 and is distributed over the width of the condenser 1. It then flows through openings into an underlying part of the subcooling region 4 and likewise distributes itself again over the entire width of the condenser. It then passes through openings in the interior of the condenser 1 in the Enthitzungsbereich 3. After being distributed across the width of the condenser 1, the coolant flows out of the condenser 1 through the tube 53 via the fluid outlet 51.

The tube 53 is in fluid communication with one of the channels of the second flow channel 52. Through the pipe 53, the coolant can be led out of the Enthitzungsbereich 3 through the entire sub-cooling region 4 from the condenser 1, without it can come to a thorough mixing of the refrigerant with the refrigerant.

The coolant thus flows completely serially through the regions 3 and 4 of the condenser 1. The coolant flowing in the flow channel 52 therefore flows countercurrently to the refrigerant in the flow channel 25 at all times.

The FIG. 5 shows a condenser 1. The course and orientation of the coolant channel 26 correspond to that in FIG. 1 already shown course. The course of the refrigerant channel 60 corresponds in many parts also the course of the flow channel 25 of FIG. 1 ,

Deviating from the fluid inlet 7 arranged at the lower end region of the condenser 1, the fluid inlet 61 is now likewise arranged at the upper end region of the condenser 1, as is the fluid outlet 62. In order to enable such a flow guidance, the condenser 1 has a tube 63 which connects a channel of the de-icing area 3 with the fluid inlet 61.

The refrigerant therefore flows through the pipe 63 into the Enthitzungsbereich 3 and from there as already described in the preceding figures serially through the individual channels of the first flow channel in the Enthitzungsbereich 3 and in the subcooling. 4

The FIG. 6 shows a further view of a capacitor 1a, as in the previous FIGS. 1 to 5 , In addition, the condenser 1a now has a further subcooling path. The subcooling area 4a is thus larger and has more channels than the subcooling area 4 of the previous ones FIGS. 1 to 5 ,

The flow guide of the first flow passage 25a, through which the refrigerant flows, is completely serial. The flow guide of the second flow channel 26a is completely parallel. As a result, regions flowed through in countercurrent and regions of the capacitor 1a flowed through in the direct current flow.

Due to the additional deflection of the refrigerant in the third subcooling, the positioning of the fluid outlet 8a is compared to the arrangement of Fluid outlet 8 of FIG. 1 changed. The fluid outlet 8a is arranged, in contrast to FIG. 1, on the opposite side of the condenser 1a. The fluid inlet 7 and the fluid outlet 8a are in common alignment.

By changing the number of channels, the position and positioning of the fluid inlet 7 and the fluid outlet 8a can thus also be acted upon.

The number of channels associated with the first flow channel 25a and the second flow channel 26a depends mainly on the number of disk elements used in the disk stack 11a. There is always a higher number or a lower number predictable. The embodiments shown here have no limiting character in this regard.

The FIG. 7 shows an embodiment of a capacitor 70, wherein the subcooling region 71 is represented by two cuboidal elements. The Enthitzungsbereich 72, however, is different from the versions of FIGS. 1 to 6 represented by 3 cuboidal elements. An increase or decrease in the number of cuboid elements can be achieved by changing the number of disk elements in the disk stack 73.

In the FIG. 7 For example, at the fluid inlet 74 of the collector 75 and the fluid outlet 76, pipes 77 of different lengths are shown, each of which produces a fluidic connection to the channels of the first flow channel.

In the dewarning region 72 and the subcooling region 71, both serial flows as well as parallel flows can be achieved. This essentially depends on the interconnection of the channels with each other.

The FIG. 8 shows a capacitor 80 with a Enthitzungsbereich 81 at the lower end of the capacitor 80 and two overlying subcooling regions 82. The capacitor 80 is substantially formed by the disk stack 93.

Both the subcooling region 82 and the de-icing region 81 are flowed through in parallel by the coolant. Both the fluid inlet 83 and the fluid outlet 84 of the second flow channel 85 are arranged at the lower end region of the condenser 80.

Furthermore, the fluid inlet 86 of the first flow channel 87 is arranged at the lower end region. The flow through the Enthitzungsbereichs 81 and the subcooling region 82 with the refrigerant is done serially similar to that in the illustrations of FIGS. 1 to 4 ,

Above the subcooling region 82, another cuboidal element is shown. This cuboidal element forms an internal heat exchanger 88.

The inner heat exchanger 88 has a third flow channel 89. At the same time, the refrigerant from the flow channel 87 is guided into the inner heat exchanger 88. Between the fluid of the third flow channel 89 and the refrigerant of the first flow channel 87, a heat transfer in the internal heat exchanger 88 can take place.

The third flow channel 89 can be flowed through either by refrigerant or by a coolant. As with the other areas of the capacitors shown, and the inner heat exchanger 88 can be flowed through in DC and / or in countercurrent. By flowing in countercurrent, a higher heat transfer between the two fluid streams can be achieved.

At the upper end region of the condenser 80, both the fluid inlet 90 and the fluid outlet 91 of the third flow channel 89 are arranged. In addition, the fluid outlet 92 of the first flow channel 87 is arranged.

The in the FIGS. 1 to 8 shown positions of the fluid inlets or fluid outlets are each exemplary. For this purpose, different orientations, such as on the side of the capacitor, are as predictable as the arrangement of a fluid inlet or fluid outlet in a central region of the capacitors.

Furthermore, the capacitors 1, 1a, 70, 80 are optionally to be produced from a combination of desuperheating region 3, 72, 81, subcooling region 4, 71, 82 and internal heat exchanger 88. Optimal configurations can be created depending on the application, all of which follow a simple structure of individual disk elements and are thus very flexible in their construction.

The in the FIGS. 1 to 8 shown pipes 5, 53, 63, 77 are also inexpensive to produce and are introduced in the simplest case in the disk stacks 11, 11a, 73, 92, 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 with the individual tubes 5, 53, 63, 77 can be soldered in one operation. Here, the tubes 5, 53, 63, 77 in particular with the openings, which have passages, soldered.

The FIG. 9 shows a sectional view of a capacitor 100 according to the invention. In the FIG. 9 In particular, the connection region is shown, to which a collector, not shown, is connected via a flange 102 to the disk stack of the capacitor 100. The flange 102 has an inlet 104 and a drain 103. Via this, a fluid from the condenser 100 can drain into a collector or run back from the collector into the condenser 100.

In this case, the outlet 103 opens into a tube 101, which itself opens into a flow channel 107. The flow channel 107 is one of the channels, which results between, for example, two stacked disk elements 105 and 106. A detailed view of the connection of the tube 101 to the disc element 105 is shown in the following FIG. 10 shown.

From the inlet 104, a fluid can flow around the tube 101 and further up into an area below the disc element 105. The exact design of the channels is also in the FIG. 10 shown.

The FIG. 10 shows a detailed view of the arrangement of the tube 101, as it is already in FIG. 9 was shown. It can be seen in FIG. 10 in particular, how the tube 101 is inserted into a drain 103 of the flange 102.

The drain 103 is formed by a horizontally extending bore within the flange 102. The tube 101 is inserted via a vertically opening from the top of the bore 103 of the drain hole. The inlet 104 also opens into a bore within the flange 102.

The larger diameter bore into which the inlet 104 opens, is concentric with the bore, which opens into the drain 103 aligned. The tube 101 is thus flowed around with the fluid which flows along the inlet 104, while it flows through with the fluid which flows to the outlet 103. There is no fluid communication of the fluid flow outside the tube 101 with the fluid flow within the tube 101.

The tube 101 has an at least partially circumferential flange 108 in its upper end region. This flange 108 is in FIG. 10 produced by a compression and a resulting material doubling of the tube 101. The flange 108 abuts against the underside of the disk element 105.

The disc member 105 further includes a passage 112 formed around the opening through which the tube 101 is inserted. Above the disk element 105, a flow channel 107 is formed, below the disk element 105, a flow channel 109 is formed.

In different configurations, multiple numbers of flow channels can also be provided above and below the disk element 105. The presentation of the FIG. 10 is exemplary.

In particular in the region of the passage 112, the tube 101 is primarily connected to the disc element 105. This can be achieved for example by a gluing process or a soldering process.

The flange 102 is fastened to a lower disk element 110 by means of connecting elements 111. The disk element 110 has an opening which has a downward passage. The connecting means 111 are in the FIG. 10 formed over material extensions of the flange 102, which engage behind the passage of the disc member 110 and thus prevent slipping out of the flange 102 from the opening of the disc member 110. Between the flange 102 and the disk element 110 may also be provided, for example, an adhesive connection or a solder joint for permanent connection.

The FIG. 11 also shows a connection of a flange 120 to a capacitor, which is formed from a plurality of disk elements 128, 129 and 132. The structure of the flange 120 corresponds substantially to the already shown flange 102. The flange 120 is also connected to a passage of an opening of the lower disc member 132 to the capacitor again.

The tube 125 has a bevel on both the upper end portion 126 and the lower end portion 127. This chamfer is achieved by a cut, which was generated in a plane which is at a predeterminable angle to the central axis of the tube 125. By the tapered end portions 126, 127, the tube has a sweep at both ends.

In the upper end region, the tube 125 is supported by the tip on the disc element 128 lying on top. The disk element 128 forms a deflection disk for the flow channel 123 shown. The lower disk element 129 forms a separating disk for the flow channel 123.

The tube 125 thus provides fluid communication between the drain 121 and the flow channel 123. Due to the sweep, the tube 125 can abut an area with an end region 126 and thereby position the tube 125 as well as a suitable fluid transfer surface from the tube Form 125 in the flow channel or from a flow channel in the tube 125.

The tube 125 is also connected to a passage 131 which is formed around the opening 130 of the disc member 129 with the disc member 129.

In the lower end region, the tube 125 also has a bevelled end region 127. Via this beveled end region, the tube can be supported in the flange 120 and at the same time represent a suitable flow cross section for the passage of fluid out of the drain 121 into the tube 125.

The FIG. 12 shows two embodiments of a tube 140 and 150. In the left part of FIG. 12 the pipe 140 is shown. This has at the bottom of a peripheral flange 143, with which it can be supported against disc elements or a flange.

In the middle, the tube 140 has a flexible region 141. This flexible region 141 is generated by a concertina-like design of the tube 140. The accordion-like region has a plurality of material folds 142. In this way, the tube 140 can accommodate both compressions and strains, particularly in the axial direction, particularly preferred. In the case of compression, the material folds 142 are moved towards each other, in the case of stretching they are pulled apart.

Depending on the selected material and the selected dimensioning of the flexible region 141, the possible length compensation, which can be achieved via the tube 140, may vary in size.

Particularly during the soldering process of a capacitor, a so-called settling occurs within the capacitor, as a result of which the overall length of the capacitor is shortened. By providing a flexible region 141 in a tube 140, this resulting change in length can be accommodated in such a way that the generation of mechanical or thermal stresses within the capacitor is avoided.

The right part of the FIG. 12 shows an alternative design of a pipe 150. The pipe 150 is formed by a first pipe section 151 and a second pipe section 152. The pipe sections 151, 152 are inserted into one another in such a way that they are movable relative to each other. At the same time, the pipe sections 151, 152 are so fluid-tight to one another that no unwanted mixing between a fluid flowing around the pipe 150 and a fluid flowing through the pipe 150 is produced.

The second pipe section 152 has a funnel-shaped widening cross section in the axial direction upwards. The first pipe section 151 has a funnel-shaped, tapered cross-section viewed in the axial direction downward. At the same time, the inner diameter of the first pipe section 151 is selected such that it is greater than the outer diameter of the second pipe section 152. In this way, the two pipe sections 151, 152 can be moved relative to each other. The design of the funnel-shaped regions of the pipe section 151 or of the pipe section 152 simultaneously realizes a stop which defines a limitation of the maximum possible relative movement of the pipe sections 151, 152 relative to one another.

The configuration of the tubes 140 and 150 of the FIG. 12 is exemplary. For the tube 140 or 150 can advantageously metallic materials, but also more flexible Materials such as plastics or elastomers are used. The embodiments of the FIG. 12 have no limiting character with regard to the design of the pipe.

The in the FIGS. 1 to 8 Illustrations of a capacitor shown also have exemplary character and have no limiting effect. They can be combined with each other and clarify the idea of the invention.

The in the FIGS. 9 to 12 shown representation of the connection of a pipe or a flange to a capacitor is also exemplary. In particular, the various tubes shown the FIGS. 9 to 12 with the different capacitors of the FIGS. 1 to 8 can be combined arbitrarily. It can in the FIGS. 9 to 12 shown pipes are used both for the connection of the collector and for the connection of channels with fluid inlets and fluid outlets in the remaining area of the capacitors.

Claims (19)

1. A condenser (1, 1a, 70, 80, 100) of stacked plate design, having a first flow channel (25, 25a, 60, 87) for a refrigerant and having a second flow channel (26, 26a, 32, 42, 52, 85) 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 number of the channels is associated with the first flow channel (25, 25a, 60, 87) and a second number of the channels is associated with the second flow channel (26, 26a, 32, 42, 52, 85), wherein the first flow channel (25, 25a, 60, 87) has a first region (3, 72, 81) for desuperheating and condensing the vaporous refrigerant and a second region (4, 71, 82) for subcooling the condensed refrigerant, with a receiver (2) for storing a refrigerant, wherein a refrigerant transfer from the first region (3, 72, 81) to the second region (4, 71, 82) leads through the receiver (2), wherein the receiver (2) is in fluid communication with the first region (3, 72, 81) by means of a first connection element, which forms a first fluid connection of the receiver (2), wherein the receiver (2) is in fluid communication with the second region (4, 71, 82) by means of a second connection element, which forms a second fluid connection of the receiver (2), characterised in that the first connection element and/or the second connection element are/is formed by a tube (5, 101, 125, 140, 150) which passes through a number of plate elements by means of openings in the plate elements.
2. The condenser (1, 1a, 70, 80, 100) as claimed in claim 1, characterised in that the first connection element is designed as a tube (5, 101, 125, 140, 150) and the tube (5, 101, 125, 140, 150) leads from the second region (4, 71, 82) through the first region (3, 72, 81) to a fluid connection of the receiver (2), wherein the tube (5, 101, 125, 140, 150) is in fluid communication with the second region (4, 71, 82) of the first flow channel (25, 25a, 60, 87) and with the receiver (2).
3. The condenser (100) as claimed in one of the preceding claims, characterised in that at least one of the tubes (101, 140, 150) has a tapered portion and/or a step and/or an at least partially encircling flange (108, 143) and/or an expanded portion (153) via which it is supportable on one of the plate elements and is fixable in the condenser.
4. The condenser (1, 1a, 70, 80, 100) as claimed in one of the preceding claims, characterised in that at least one of the plate elements is designed as a separating plate and/or one of the plate elements is designed as a deflecting plate.
5. The condenser (1, 1a, 70, 80, 100) as claimed in claim 4, characterised in that the tube (5, 101, 125, 140, 150) is supported in the condenser (1, 1a, 70, 80, 100) on a deflecting plate.
6. The condenser (1, 1a, 70, 80, 100) as claimed in one of the preceding claims, characterised in that the tube (5, 101, 125, 140, 150) has radial and/or axial openings.
7. The condenser (1, 1a, 70, 80, 100) as claimed in one of the preceding claims, characterised in that the tube (5, 101, 125, 140, 150) is supported on one of the outer plate elements of the second region (4, 71, 82) .
8. The condenser (1) as claimed in one of the preceding claims, characterised in that a second tube (63) is provided at the fluid inlet (61) and/or at the fluid outlet (62) of the first flow channel (60), said second tube being in fluid communication with another channel of the first flow channel (60).
9. The condenser (1) as claimed in one of the preceding claims, characterised in that a third tube (53) is provided at the fluid inlet (50) and/or at the fluid outlet (51) of the second flow channel (52), said third tube being in fluid communication with another channel of the second flow channel (52).
10. The condenser (1, 1a, 70, 80, 100) as claimed in one of the preceding claims, characterised in that the at least one tube (5, 53, 63, 101, 125, 140, 150) is passed through the openings in the plate elements and is brazed to at least a subset of the plate elements, in particular to the rim holes.
11. The condenser as claimed in one of the preceding claims, characterised in that at least one of the tubes (125) is bevelled at one end region (126, 127) or at both end regions (126, 127).
12. The condenser as claimed in one of the preceding claims, characterised in that at least one of the tubes (140) has a flexible region, wherein the tube (140) is compressible and/or extendable in the axial direction by means of the flexible region (141).
13. The condenser as claimed in claim 9, characterised in that the flexible region (141) is formed by a concertina-like configuration of the tube (140).
14. The condenser as claimed in one of the preceding claims 8 or 9, characterised in that the flexible region (141) is formed from an elastic material, such as, for example, plastic or rubber, wherein a compression or extension of the tube (140) in the axial direction and/or in the radial direction is reversible.
15. The condenser as claimed in one of the preceding claims, characterised in that at least one of the tubes (150) is formed from a plurality of tube sections (151, 152), wherein the tube sections (151, 152) are connected to one another in a fluid-tight manner.
16. The condenser as claimed in one of the preceding claims, characterised in that a first tube section (151) tapers in a funnel-shaped manner in the axial direction and the second tube section (152) widens in a funnel-shaped manner in the axial direction, wherein the two tube sections (151, 152) are inserted one inside the other in such a manner that the relative movement between the second tube section (152) and the first tube section (151) is limited by the widening region striking against the tapering region.
17. The condenser (100) as claimed in one of the preceding claims, characterised in that the tube (101, 125) is accommodated in a connection element (102, 120) and is connected thereto in a fluid-tight manner.
18. The condenser (1, 1a, 70, 80, 100) as claimed in one of the preceding claims, characterised in that the second region (4, 4a, 71, 82) has a plurality of flow routes through which the refrigerant can flow, wherein the flow routes are each formed by individual channels of the first flow channel (25, 25a, 60, 87) and/or are formed by subregions of individual channels of the first flow channel (25, 25a, 60, 87).
19. The condenser (1, 1a, 70, 80, 100) as claimed in one of the preceding claims, characterised in that the second region (4, 4a, 71, 82) has a plurality of channels, wherein at least individual channels of the second region (4, 4a, 71, 82) are in thermal contact with the second flow channel (26, 26a, 32, 42, 52, 85), wherein the coolant and the refrigerant are flowable in co-current flow and/or in countercurrent flow to each other through the channels of the second region (4, 4a, 71, 82) and through the second flow channel (26, 26a, 32, 42, 52, 85).

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