DE102012220594A1 - capacitor - Google Patents

Abstract

A stacked disc condenser (1, 20, 40, 60) wherein a heat exchanger block (7, 22, 42, 62) is formed of a plurality of disc elements stacked adjacent to one another to form adjacent channels between the disc elements, a first plurality of channels is associated with the first flow channel and a second number of channels is associated with a second flow channel, and through the first flow channel, a refrigerant is flowable and through the second flow channel, a coolant is flowable, wherein the first flow channel has a first area for desuperheating and condensation (34, 54 , 81) of the vaporous refrigerant and having a second area for subcooling (35, 55, 82) the condensed refrigerant, wherein at least a portion of the first flow channel is in thermal contact with at least a portion of the second flow channel, and the first area is a first Fluid supply line (23, 43, 63 ) and a first fluid discharge line (24, 44, 64) and the second area has a second fluid supply line (25, 45, 65) and a second fluid discharge line (26, 46, 66), wherein the condenser (1, 20, 40, 60) has a collector (2, 21, 41, 61) for storing the refrigerant, and a refrigerant transfer from the first region into the second region through the collector (2, 21, 41, 61), wherein the collector (2, 21, 41, 61) via the first fluid discharge (24, 44, 64), which also forms the fluid inlet of the collector (2, 21, 41, 61), is in fluid communication with the first region, and via the second fluid supply line (25 , 45, 65), which also forms the fluid outlet of the collector (2, 21, 41, 61), is in fluid communication with the second region, the collector (2, 21, 41, 61) being attached to an outer surface of the condenser (1 , 20, 40, 60) is arranged.

Description

Technical area

The invention relates to a condenser in stacked disc design, wherein a heat exchanger block is formed of a plurality of disc elements stacked adjacent to each other forming channels between the disc elements, wherein a first number of channels is associated with a first flow channel and a second number of channels associated with a second flow channel is, and through the first flow channel, a refrigerant is flowable and through the second flow channel, a coolant is flowable, wherein the first flow channel has a first region for desuperheating and condensation of the vapor refrigerant and a second region for subcooling the condensed refrigerant.

State of the art

Condensers are used in refrigerant circuits of automotive air conditioning systems to cool the refrigerant to the condensation temperature and then 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. In addition, a stable supercooling of the refrigerant is achieved by the provision of the refrigerant in the collector.

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 passed through a section 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 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.

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 capable of condenser, storage and further subcooling refrigerant, the condenser being characterized by a simple structure and a compact construction, 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.

One embodiment of the invention relates to a stacked disc condenser wherein a heat exchanger block is formed from a plurality of disk elements stacked adjacent channels between the disk elements, wherein a first number of the channels is associated with a first flow channel and a second number of channels is associated with a second one Flow channel is assigned, and through the first flow channel, a refrigerant is flowable and through the second flow channel, a coolant is flowable, wherein the first flow channel has a first region for desuperheating and condensation of the vapor refrigerant and a second region for supercooling the condensed refrigerant, wherein at least a portion of the first flow channel is in thermal contact with at least a portion of the second flow channel, and the first portion is a first fluid supply line and a first one Fluid drainage and the second region having a second fluid supply and a second fluid discharge, wherein the condenser has a collector for storing the refrigerant, and a refrigerant transfer from the first region into the second region through the collector leads, wherein the collector via the first fluid discharge, which also forms the fluid inlet of the accumulator, is in fluid communication with the first portion, and is in fluid communication with the second portion via the second fluid supply line, which also forms the fluid outlet of the accumulator, the accumulator being disposed on an outer surface of the condenser.

A condenser in stacking disc design is particularly compact and can therefore be accommodated in a small space. Particularly advantageous is a good thermal contact between the first flow channel and the second flow channel, so that the heat transfer between the fluids is as efficient as possible. The arrangement of the collector as close as possible to the condenser or to the heat exchanger block of the condenser has the advantage that only short distances have to be overcome by means of fluid lines. The thermal disadvantageous properties, such as the heating of the coolant or the refrigerant by surrounding heat sources, as well as the negative effects on the pressure loss inside the condenser, can therefore be minimized.

In addition, it may be advantageous if the coolant in the second flow channel and the refrigerant in the first flow channel in the DC flow to each other and / or in countercurrent to each other are flowable.

By flowing the coolant and the refrigerant in countercurrent, the maximum amount of heat transferable can be increased, which contributes to an increase in efficiency of the capacitor. A DC current, on the other hand, can be realized particularly easily.

It may also be expedient if the first fluid outlet and / or the second fluid supply line are arranged inside and / or outside the heat exchanger block.

Depending on the position of the collector, it is expedient if the first fluid discharge, which also simultaneously represents the supply line to the collector, and the second fluid supply line, which also simultaneously represents the discharge from the collector, extend inside or outside the condenser. The leadership of the lines outside the capacitor is easier to implement, since the space is less limited and the shaping limits of the individual disc elements must not be considered.

In advantageous embodiments, the lines can also run within the capacitor. For example, the lines can be arranged on the outer disc elements. This can be done for example by integrated into the disc elements channels.

Furthermore, it may be particularly advantageous if the first fluid discharge and / or the second fluid supply line are formed by a pipeline.

A pipeline offers the advantage of very great design freedom for the course and the arrangement of the line. Pipelines can also be used to realize complex pipelines.

It is also preferable if the first fluid supply line and the second fluid supply line, viewed along the main flow direction of a channel between the disc elements, are arranged at the same end region of the condenser, wherein the first fluid discharge line and the second fluid discharge line are arranged at the opposite end region of the condenser.

By arranging the first and the second fluid supply line at a common end region of the condenser and the first and second fluid discharge line at the opposite end region of the condenser, it is possible to realize in a particularly simple manner a countercurrent flow of the fluid streams within the condenser.

In a particularly favorable embodiment of the invention, it is also provided that the first fluid supply line and the second fluid supply line are arranged in the final assembly position of the capacitor at the upper end region of the capacitor.

The supply of the fluid at, in Montageendlage, the upper end portion of the capacitor is particularly advantageous, since the flow within the capacitor is additionally supported by the weight of the fluid. In addition, the resulting pressure loss within the condenser is less than when the fluid must be transported up against the weight.

In an alternative embodiment of the invention, it may be provided that the inner volume fraction of the second region of the first flow channel is a maximum of about 40%, preferably about 20%, preferably between about 5% and about 15% of the total internal volume of the first flow channel.

It is thermally advantageous if the subcooling path, which corresponds to the second region of the first flow channel, the largest possible volume fraction of the total volume of the first Flow channel occupies, as this, the fluid temperature at the condenser outlet can be kept very low. This can improve system performance.

However, by reducing the heat transfer area in the condensation area corresponding to the first area of the first flow passage, the heat transfer is deteriorated. This has a negative effect on the pressure on the high-pressure side of the refrigerant circuit, resulting in an overall poorer system performance.

Therefore, a limitation of the subcooling distance to the above-stated volume fractions is advantageous in terms of the efficiency of the capacitor.

Furthermore, it is preferable if the coolant supply line and the coolant discharge line of the second flow channel, viewed along the flow direction of a channel between the disk elements, are arranged on opposite end regions of the condenser.

The arrangement of the coolant supply and the coolant discharge at opposite end portions of the condenser is particularly advantageous when the coolant is to flow through the condenser without substantial deflection.

According to a particularly preferred development of the invention, provision may be made for the first region and / or the second region of the first flow channel to be deflected one or more times within the main flow direction within the condenser.

By a simple or multiple deflection of the flow direction, it can be achieved that the refrigerant and the coolant flow either in cocurrent or in countercurrent to each other. As a result, the heat transfer between coolant and refrigerant can be influenced.

In addition, it may be advantageous if the second flow channel is deflected within the condenser at least once in its main flow direction by about 180 °.

A deflection of the second flow channel may be advantageous in order to bring the flowing coolant with the refrigerant in cocurrent or countercurrent. The heat transfer between the refrigerant and the coolant can be influenced by a deflection of the second flow channel.

A further preferred embodiment is characterized in that the second flow channel is deflected once in its main flow direction by approximately 180 °, whereby a Hinströmbereich and a Rückströmbereich arises, wherein the inner volume of the inflow region of the second flow channel and the inner volume of the Rückströmbereichs the second flow channel approximately are the same size and / or unequal size.

The inflow region of the second flow channel and the return flow region can advantageously be approximately equal in volume. This is particularly advantageous in particular with regard to the resulting pressure losses for the coolant.

In the event that the separation in Hinströmbereich and Rückströmbereich based on the division into the condensation zone and sub-cooling region, but also an uneven distribution may be advantageous.

It is furthermore advantageous if the coolant flows through the second flow channel in such a way that it first makes thermal contact with the second region of the first flow channel along the main flow direction of the second flow channel or first with the second region and at least a portion of the first region of the second flow channel the first flow channel comes into thermal contact and occurs in each case after the deflection substantially in thermal contact with the first region of the first flow channel.

By flowing the coolant such that essentially thermal contact first takes place between the second region of the second flow channel and the coolant, the outlet temperature of the refrigerant from the condenser can be effectively reduced. The fresh coolant entering the condenser has its lowest temperature directly at the fluid inlet. As a result, the heat transfer is particularly high. In order to avoid an unnecessarily high pressure loss due to the unequal volume fractions between the first region and the second region of the first flow channel for the coolant, the coolant may also be in thermal contact with a portion of the first region of the first flow channel in addition to the thermal contact with the second region Be brought in contact. In this way, the outflow path and the backflow path of the coolant are designed such that an approximately equal internal volume is present, whereby the internal pressure loss is reduced.

Furthermore, it is expedient if there is a thermal separation between the first area for desuperheating and condensation of the vaporous refrigerant and the second area for subcooling the condensed refrigerant.

By a thermal separation between the condensation region and the subcooling region of the condenser, a thermal interaction between the fluids in the subcooling region and in the condensation region can be achieved. In particular, a renewed heating of the refrigerant can be avoided, which can lead to an increase in the system performance of the capacitor.

In an alternative embodiment of the invention, it may be provided that the thermal separation as a thermally insulating disc, as an air gap, as an air-conducting channel, as part of the second flow channel with a multiply executed coolant path and / or as part of the second flow channel with a larger flow cross-sectional area as the remaining second flow channel is formed.

Advantageously, the thermal separation can be realized by one of the disc elements of the capacitor, whereby the design complexity is minimized. Specially prepared disc elements, however, can lead to a strong thermal separation.

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

Brief description of the drawings

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

1 a perspective view of a capacitor in a stacked disk design, with a collector arranged on the outside of the housing,

2 another view of the capacitor of 1 in particular, the line from the collector to the back of the condenser and the discharge of the refrigerant from the condenser can be seen,

3 a schematic representation of a capacitor in stacked disk design with an externally arranged collector, wherein the coolant and the refrigerant flow in the condensation region in countercurrent to each other and flow in the subcooling in DC to each other,

4 a further schematic view of a condenser, wherein the coolant and the refrigerant flow in both the condensation region and the subcooling in countercurrent to each other, and

5 a further schematic view of a condenser, wherein the coolant is deflected within the condenser and thereby arise areas within the condenser, in which the coolant and the refrigerant flow both in cocurrent and countercurrent to each other, the refrigerant through the subcooling from the condensation region in the collector is transferred.

6 a further schematic view of a condenser, wherein between the condensation region and the sub-cooling region, a thermal separation is introduced by a double-executed coolant path.

Preferred embodiment of the invention

The 1 shows a perspective view of a capacitor 1 in stacked disc design. The capacitor 1 consists of a plurality of individual disc elements, which stacked on the heat exchanger block 7 form. The heat exchanger block 7 is designed in its interior so that there are a plurality of channels between the individual disc elements. A number of these channels is associated with a first flow channel, which can be traversed by a refrigerant. A further number of channels is associated with a second flow channel, which can be flowed through by a coolant. The first flow channel is inside the heat exchanger bladder 7 with the second flow channel at least partially in thermal contact, so that a heat transfer between the first flow channel and the second flow channel can take place.

About various configurations of the disc elements can be achieved that in the interior of the heat exchanger Black 7 several flow paths for the first and the second flow channel arise. The fluid flowing through the first flow channel and the second flow channel, respectively, can flow through the various flow paths within the heat exchanger bladder 7 be deflected and so overall a longer flow path within the condenser 1 return.

On an outer surface of the heat transfer unit 7 is a collector 2 arranged. This collector serves to store the refrigerant flowing along the first flow channel. About the collector 2 a volume fluctuation of the refrigerant within the condenser and the rest of the refrigerant circuit can be compensated. In advantageous embodiments, the collector 2 Have means for drying and filtering of the refrigerant.

The in 1 shown collectors 2 has a cylindrical housing and is on the outside of the heat exchanger Black 7 arranged. In alternative embodiments, the collector 2 also have other designs. The representation of the collector 2 is exemplary.

The collector 2 is about collector connections 8th with the first flow channel inside the condenser 1 connected and is in fluid communication with this.

The capacitor 1 also has a refrigerant inlet 3 at its upper left end area. The condenser is at the upper right end 1 a coolant outlet 6 on. The condenser is at the lower right end 1 a coolant inlet 5 on.

A refrigerant can do so via the refrigerant inlet 3 in the first flow channel of the heat exchanger block 7 inflow and distribute through the channels associated with the first flow channel. From the first flow channel 1 The refrigerant then flows through the header connections 8th in the collector 2 , From the collector 2 the refrigerant flows back into the heat exchanger block 7 and further distributed through the first flow channel of the heat exchanger block 7 , Finally, the refrigerant flows through the refrigerant outlet 4 , which on the rear side facing away from the viewer of the capacitor 1 is arranged, from the heat exchanger block 7 of the capacitor 1 out.

The coolant flows through the coolant inlet 5 in the second flow channel of the heat exchanger block 7 and distributes along this flow channel in the heat exchanger block and ultimately flows through the coolant outlet 6 out of the condenser.

The first flow channel is divided into a first region and a second region. The first area extends from the refrigerant inlet 3 until the transition to the collector 2 , The second region of the first flow channel extends from the outlet of the collector 2 to the refrigerant outlet 4 of the capacitor 1 , The coolant, which flows through the second flow channel, is in thermal contact with both the first region and the second region of the first flow channel, resulting in a heat transfer.

The 2 shows a rear view of the capacitor 1 of the 1 , It is in particular the pipeline 10 and the fluid outlet 4 to recognize. The pipeline 10 represents the fluid line, which from the outlet of the collector 2 to the heat exchanger block 7 returns and the refrigerant passes between the disc elements again.

The 3 shows a schematic view of a capacitor 20 , A possible embodiment of the capacitor of 3 to 5 is in the 1 and 2 shown. The courses of the outer pipelines as well as the arrangement of the collector can be determined by the in 1 and 2 differ from the examples shown. Likewise, the number of disc elements used and the arrangement of the individual fluid inlets and fluid outlets on the heat exchanger block.

The in 3 shown capacitor 20 has an outside collector 21 on.

With the reference number 27 is the coolant supply to the condenser 20 shown. With the reference number 28 is the coolant discharge of the condenser 20 shown. The coolant flows along the flow paths 31 . 32 along the previously mentioned second flow channel through the condenser 20 , In 3 the coolant flows without deflection both through the first region of the first flow channel, which has a condensation region 34 represents, as well as through the second region of the first flow channel, which is a subcooling 35 represents.

The condensation area 34 is in relation to the subcooling area 35 larger dimensioned and takes part in the total volume of the first flow channel 1 a larger share.

In order to ensure an optimal function of a capacitor in general, it is desirable that the ratio between the condensation region and the subcooling region is in a certain maximum relationship to each other. It is therefore advisable that the internal volume of the first flow channel, which is assigned to the subcooling region, in relation to the internal volume of the first flow channel, which is assigned to the condensation surface, not greater than 40% of the total internal volume of the first flow channel. Advantageously, it is desirable that the inner volume of the first flow channel, which is assigned to the subcooling, even no greater than 20%, optimally dividing the total inner volume of the first flow channel in about 5% to 15% of the volume for the subcooling and 85th % to 95% of the internal volume for the condensation zone.

The capacitor 20 of the 3 is via the first fluid supply line 23 a refrigerant in the condensation area 34 supplied there, it flows distributed over the individual channels of the condensation region 34 down and step over the first one fluid discharge 24 in the collector 21 one. From the collector 21 becomes the now completely condensed refrigerant along the fluid line 33 via the second fluid supply line 25 in the subcooler area 35 initiated. The discharge of the refrigerant from the condensation zone 34 as well as the supply line in the subcooling area 35 find it at the lower end of the capacitor 20 instead of. The refrigerant then flows in the subcooling area 35 upwards and flows over the second fluid discharge 26 from the condenser 20 out.

About the arrows with the reference numerals 29 and 30 the flow path of the refrigerant is shown inside the condenser. The arrows with the reference numeral 31 and 32 set the flow path of the coolant inside the condenser 20 It can be seen that the coolant in countercurrent to the refrigerant in the condensation region 34 flows and in DC in the subcooling area 35 , By reversing the direction of flow of the coolant, a reversal of these conditions can be achieved.

In 3 is a capacitor 20 in which both within the condensation region 34 as well as the subcooling area 35 no separate deflection of the coolant or the refrigerant takes place.

The 4 shows an alternative embodiment of a capacitor 40 , The capacitor 40 has a heat exchanger block 42 on, which like in the 1 and 2 described, consists of a plurality of disc elements. On the exterior of the condenser 40 is a collector 41 arranged, which with the capacitor 42 is in fluid communication. As in the 3 The coolant is substantially without deflection along its Hauptdurchströmungsrichtung through the condenser 40 flowed. The coolant supply line 47 is at the bottom of the capacitor 40 arranged. The coolant drainage 48 is at the top of the capacitor 40 arranged.

In all 3 to 5 the positioning of both the fluid supply line and the Fiuidableitung for both the coolant and the refrigerant is merely indicated. The schematic representation can not represent the exact positioning of the leads or leads on the outer surfaces of the capacitors. The supply lines or discharges may be arranged primarily on the end faces of the capacitor, which result from the respective uppermost or lowermost disk element of the heat exchanger block. A supply to the side surfaces of the disc elements is structurally very expensive and only partially possible. The supply of the fluids into the individual channels within the condenser can take place by the structural design of the individual disc elements in a wide variety of ways.

For example, the fluid may be directed directly into the first channel that results between the first and second disc members. Alternatively, the fluid can be introduced, for example, by closing individual disc elements or by inserting a dip tube into each other channel between the disc elements. The possibilities of dividing the individual channels into the first flow channel or the second flow channel within the condenser essentially correspond to those which are already known in the prior art.

In 4 the refrigerant flows over the first fluid supply line 43 in the upper part of the condenser 40 in the condensation area 54 , It flows along the flow path 49 in the condensation region down and flows over the first fluid discharge 44 in the collector 41 above. From the collector 41 becomes the fully condensed refrigerant via the fluid line 53 to the second fluid supply line 45 directed. Which in contrast to 3 now in the upper part of the condenser 40 on the side of the subcooled section 55 is arranged. The refrigerant then flows along the flow path 50 in the subcooler area 55 of the capacitor 40 down and ultimately flows over the second fluid drainage 46 from the condenser 40 out.

Due to the undeflected flow of the coolant from bottom to top through the condenser 40 and the supply of the refrigerant in the upper region of the condenser 40 is the coolant with the refrigerant both in the condensation area 54 as well as in the subcooling area 55 in countercurrent.

By reversing the direction of flow of the coolant can be achieved that both in the condensation region 54 as well as in the subcooling area 55 the refrigerant flows in cocurrent with the refrigerant. However, in order to produce a higher heat transfer between the refrigerant and the coolant, a design according to the 4 to prefer.

The 5 shows a further embodiment of a capacitor 60 , The capacitor 60 has a heat exchanger block 62 on, which, as already described above, is formed from the individual disc elements. Furthermore, the capacitor has 60 a condensation area 81 and a subcooling area 82 on. Unlike the previous ones 3 and 4 is now the condensation area 81 in several flow paths 79 . 80 divided up. The condensation area 81 is in the representation of 5 from the flow path 79 and the flow path 80 educated. The subcooling area 82 is from the flow path 77 educated. Between the flow path 80 and the funeral path 79 the refrigerant undergoes a deflection by about 180 °. Each of the flow paths 77 . 79 and 80 the condensation area 81 and the subcooling area 82 may consist of a singular or a plurality of channels of the first flow channel.

In alternative embodiments, a subdivision of both the condensation region and the subcooling region into a different number of flow paths is also conceivable. The subdivision of the condensation area 81 in two flow paths 79 . 80 serves here the better representation. To a flow principle analogous to 5 However, it is advantageous if the number of flow paths in the condensation region 81 straight and in the subcooled area 82 is odd.

Outside the condenser 60 is a collector 61 arranged through which the refrigerant flows. The coolant will differ from the 3 and 4 now not passed through the condenser without deflection but experiences inside the condenser 60 a deflection by 180 °, whereby in the condenser a Hinströmstrecke and a Rückströmstrecke arises.

The coolant is via the coolant supply line 67 in the upper area of the condenser 60 introduced and at the bottom of the capacitor 60 deflected, then continue to flow upward and on the coolant discharge 68 from the condenser 60 emanate. To realize this deflection, the channels are inside the heat exchanger block 62 , which are associated with the second flow channel, assigned to each other via the structural design of the respective disc elements such that the coolant in a portion of the second flow channel from the upper region in the lower region of the capacitor 60 can flow. There it flows in the remainder of the second flow channel over and along the channels of the second flow channel back into the upper region of the condenser.

In the in 5 As shown, the Hinströmstrecke of the coolant extends to the channels of the second flow channel, which in direct thermal exchange with the subcooling 82 the first flow channel and a number of channels of the second flow channel, which are in thermal contact with the condensation region 81 stand the first flow channel. The return flow path of the coolant is limited to the channels of the second flow channel, which in direct thermal exchange with the condensation region 81 stand the first flow channel. A different distribution is also foreseeable.

In order to achieve a pressure loss as uniform as possible both in the outflow section and in the return flow path of the coolant, it is advantageous if the channels which form the second flow channel in total, are assigned approximately equal parts of Hinströmstrecke and the return flow of the coolant.

The division of the second flow channel in Hinströmstrecke and return flow does not have to do so with the division of the first flow channel in the condensation region 81 and the subcooler area 82 be congruent.

The refrigerant becomes the condenser 60 via a first fluid supply line 63 fed in the upper area. The refrigerant then flows along the first flow path 80 along the flow path 69 in the lower part of the condenser 60 , There it undergoes a deflection by a corresponding connection of the inner disc elements and then flows through the flow path 79 along the flow path 71 back to the top of the refrigerant. Both the flow path 80 as well as the flow path 79 are the condensation area 81 assigned. From the top of the flow path 79 the refrigerant flows through a first fluid drainage 64 in the upper area of the collector 61 one.

After flowing through the collector 61 the fully condensed refrigerant flows over a second fluid supply line 65 in the lower part of the condenser 60 which is the subcooling area 82 assigned. The refrigerant then flows in the flow path 77 along the flow path 72 back to the top of the condenser, where it finally crosses the second fluid 66 from the condenser 60 is derived.

About the described guidance of the coolant and the described guidance of the refrigerant results that the coolant and the refrigerant in the entire condenser 60 flow in countercurrent.

The overhead line of the refrigerant from the condensation zone 81 to the collector 61 takes place through the subcooling area 82 of the capacitor 60 , This is realized by a corresponding design of the individual disc elements.

The in 5 shown capacitor 60 has two flow paths 79 . 80 in the condensation area 81 of the first flow channel. The subcooling area 82 has only one flow path. In different versions can also deviating numbers of the flow paths may be provided. To the same flow principle as in 5 It is advantageous if the number of flow paths in the condensation region is straight and the number of flow paths in the sub-cooling region is odd.

In general, here in the 3 to 5 shown line areas between the heat exchanger block and the collector are each realized by externally attached to the condenser piping, but also by a clever interconnection of the inner disc elements and an arrangement of the collector directly to one of the outer surfaces of the heat exchanger block.

The individual connecting lines between heat exchanger block and collector can either be soldered directly to the heat exchanger block or subsequently realized by internal or external pipes. Likewise, it is providable to make the supply or discharge between heat exchanger block and collector via a corresponding design of the two outer disc elements. For example, it is conceivable that channels are integrated into the two outer or in only one of the outer disk elements, which can be used as a supply or discharge.

The 6 shows a schematic sectional view of the capacitor. In particular, the individual disk elements can be seen, between which the channels are formed which belong to the first flow channel or to the second flow channel.

The first flow channel is traversed by a refrigerant. The channels that belong to the first flow channel are hatched and denoted by the reference numeral 93 marked. The channels belonging to the second flow channel are traversed by a coolant and denoted by the reference numeral 94 marked.

Furthermore, in 6 the thermal interface 92 shown, which between the condensation area 90 and the subcooling area 91 of the capacitor is arranged. Through the thermal separation layer 92 is an unwanted heat transfer between the fluids in the subcooling 91 and the condensation area 90 prevented.

The thermal separation layer can be formed, for example, by an air-filled channel between two disk elements, by an air gap between two adjacent disk elements or an arrangement of several coolant channels next to each other. The aforementioned possibilities for forming a thermal separating layer are exemplary and have no limiting character. In particularly advantageous embodiments, in particular the heat transfer to the refrigerant, ie a heating of the refrigerant is avoided.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 2009/0071189 A1 [0007]

Claims (14)

Capacitor ( 1 . 20 . 40 . 60 ) in stacked disk construction, wherein a heat exchanger block ( 7 . 22 . 42 . 62 ) is formed of a plurality of disc elements stacked adjacent to each other forming channels between the disc elements, wherein a first number of channels is associated with a first flow channel and a second number of channels is associated with a second flow channel, and through the first flow channel, a refrigerant flowable and a coolant is flowable through the second flow channel, wherein the first flow channel has a first area for desuperheating and condensation ( 34 . 54 . 81 ) of the vaporous refrigerant and a second area for supercooling ( 35 . 55 . 82 ) of the condensed refrigerant, wherein at least a portion of the first flow channel is in thermal contact with at least a portion of the second flow channel, and the first region is a first fluid supply line ( 23 . 43 . 63 ) and a first fluid discharge ( 24 . 44 . 64 ) and the second region has a second fluid supply line ( 25 . 45 . 65 ) and a second fluid discharge ( 26 . 46 . 66 ), wherein the capacitor ( 1 . 20 . 40 . 60 ) a collector ( 2 . 21 . 41 . 61 ) for storing the refrigerant, and a refrigerant transfer from the first region to the second region by the collector ( 2 . 21 . 41 . 61 ), whereby the collector ( 2 . 21 . 41 . 61 ) via the first fluid discharge ( 24 . 44 . 64 ), which also the fluid inlet of the collector ( 2 . 21 . 41 . 61 ) is in fluid communication with the first region, and via the second fluid supply line ( 25 . 45 . 65 ), which also the fluid outlet of the collector ( 2 . 21 . 41 . 61 ) is in fluid communication with the second region, the collector ( 2 . 21 . 41 . 61 ) on an outer surface of the capacitor ( 1 . 20 . 40 . 60 ) is arranged. Capacitor ( 1 . 20 . 40 . 60 ) according to claim 1, characterized in that the coolant in the second flow channel and the refrigerant in the first flow channel in the DC to each other and / or in countercurrent to each other are flowable. Capacitor ( 1 . 20 . 40 . 60 ) according to one of the preceding claims, characterized in that the first fluid discharge ( 24 . 44 . 64 ) and / or the second fluid supply line ( 25 . 45 . 65 ) inside and / or outside the heat exchanger block ( 7 . 22 . 42 . 62 ) are arranged. Capacitor ( 1 . 20 . 40 . 60 ) according to one of the preceding claims, characterized in that the first fluid discharge ( 24 . 44 . 64 ) and / or the second fluid supply line ( 25 . 45 . 65 ) through a pipeline ( 10 ) are formed. Capacitor ( 1 . 40 ) According to one of the preceding claims, characterized in that the first fluid supply line ( 43 ) and the second fluid supply line ( 45 ), viewed along the main flow direction of a channel between the disc elements, at the same end portion of the capacitor ( 1 . 40 ), wherein the first fluid discharge ( 44 ) and the second fluid discharge ( 46 ) at the opposite end of the capacitor ( 1 . 40 ) are arranged. Capacitor ( 1 . 40 ) according to claim 5, characterized in that the first fluid supply line ( 43 ) and the second fluid supply line ( 45 ) in the mounting end position of the capacitor ( 1 . 40 ) at the upper end of the capacitor ( 1 . 40 ) are arranged. Capacitor ( 1 . 20 . 40 . 60 ) according to any one of the preceding claims, characterized in that the inner volume fraction of the second region of the first flow channel maximally Ca. 40%, preferably about 20%, preferably between about 5% and about 15% of the total inner volume of the first flow channel. Capacitor ( 1 . 20 . 40 ) according to one of the preceding claims, characterized in that the coolant supply line ( 5 . 27 . 47 ) and the coolant discharge ( 6 . 28 . 48 ) of the second flow channel, viewed along the direction of flow of a channel between the disc elements, at opposite end regions of the condenser (FIG. 1 . 20 . 40 ) are arranged. Capacitor ( 1 . 60 ) according to one of the preceding claims, characterized in that the first region and / or the second region of the first flow channel within the condenser ( 1 . 60 ) is deflected one or more times in its main flow direction. Capacitor ( 1 . 60 ) according to one of the preceding claims, characterized in that the second flow channel within the condenser ( 1 . 60 ) is deflected at least once in its main flow direction by about 180 °. Capacitor ( 1 . 60 ) according to one of the preceding claims, characterized in that the second flow channel is deflected once in its main flow direction by about 180 °, whereby a Hinströmbereich and a Rückströmbereich arises, wherein the inner volume of the inflow region of the second flow channel and the inner volume of the Rückströmbereichs the second Flow channels are about the same size and / or unequal size. Capacitor ( 1 . 60 ) according to claim 11, characterized in that the coolant flows through the second flow channel such that it first makes thermal contact with the second region of the first flow channel along the main flow direction of the second flow channel or first with the second region and at least a portion of the first flow channel first contact occurs in thermal contact with the first region of the first flow channel and in each case after the deflection substantially in thermal contact with the first region of the first flow channel occurs. Capacitor ( 1 . 60 ) according to one of the preceding claims, characterized in that there is a thermal separation between the first region for desuperheating and condensation of the vaporous refrigerant and the second region for subcooling the condensed refrigerant. Capacitor ( 1 . 60 ) according to claim 13, characterized in that the thermal separation as a thermally insulating disk, as an air gap, as an air-conducting channel, as part of the second flow channel with a multiple executed coolant path and / or as part of the second flow channel with a larger flow cross-sectional area than the rest second flow channel is formed.

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