WO2013098277A1

WO2013098277A1 - Kit for heat exchanger, a heat exchanger core, and a heat exchanger

Info

Publication number: WO2013098277A1
Application number: PCT/EP2012/076859
Authority: WO
Inventors: Wolfgang Seewald; Falk Viehrig
Original assignee: Behr Gmbh & Co. Kg
Priority date: 2011-12-30
Filing date: 2012-12-21
Publication date: 2013-07-04
Also published as: EP2798297A1; DE102011090182A1; CN204188026U; US20140374072A1; EP2798297B1

Abstract

The invention relates to a kit for producing heat exchangers, comprising at least two types of heat exchanger cores (1, 2) in order to produce more than two different heat exchangers. The kit comprises: • - a first type of heat exchanger core (1) with a plurality of pairs (3) of plates in order to produce a plurality of parallel flow paths between the plate pairs (3) and • - a second type of heat exchanger core (2) with a plurality of groups (7) of three plates in order to produce a plurality of second parallel flow paths, one flow path being produced between two of each three plates.

Description

Kit for heat exchangers, a heat transfer core and a

Heat exchanger

description

TECHNICAL FIELD The invention relates to a construction kit for producing a disk-type heat exchanger, in particular for motor vehicles, having a plurality of

Disk pairs and / or disk groups for the formation of flow paths, a heat transfer core for the formation of heat exchangers and a related heat exchanger,

State of the art

Heat exchangers for motor vehicles are known in the art. Thus, heat exchangers are already used in a variety of configurations and uses in vehicles, such as evaporator, storage evaporator, oil cooler, condenser, intercooler or coolant radiator. All these heat exchangers have different configurations and designs, so that for each type often a different design is applied.

DE 1020060281 17 A1 discloses an evaporator with cold storage, a so-called storage evaporator, in which an evaporator part is formed with double-row flat tubes, wherein adjacent to this evaporator part of the Heat exchanger, a memory part is provided, which is formed einreihig and can flow through an array of double tubes on the one hand, a refrigerant through an inner flat tube and on the other a cold storage medium in one

Interspace between the inner flat tube and the outer flat tube arranged or can flow through this space area. The production of this storage evaporator is a highly complex process, since a large number of tubes and a large number of parts have to be assembled and interconnected. The evaporator part typically represents a modification of a stationary refrigerator, so that this component too does not

is used by default, but at least with regard to some components requires a modification. This storage evaporator is thus a separate solution that can not rely on mass-produced components.

The EP 1817534 B1 also discloses a storage evaporator, wherein in a first embodiment, in turn, flat tubes are inserted into each other, which can be connected by means of connecting elements to different refrigerant or cold storage medium medium cycles. The production of such

Storage evaporator again shows a high parts cost, which leads to significant additional costs.

The embodiment of a disk-type storage evaporator according to the second exemplary embodiment of EP 1817534 B1 also shows that a singular solution has been developed which is only of little use for other purposes.

The heat exchangers in the prior art are thus very specific to the

The needs of each medium adapted in the circuit, so that a broad application is rather excluded for different applications.

Presentation of the invention, object, solution, advantages It is the object of the invention to provide a construction kit for producing a heat exchanger in disk construction, in particular for motor vehicles, with a plurality of disk pairs and / or disk groups for the formation of

To provide flow paths, which allows easier production of different heat exchangers for different applications. Moreover, it is the object of the invention to provide heat exchanger cores, which are used for the formation of heat exchangers and it is the object of the invention to provide such a heat exchanger. This is achieved for the kit with the features of claim 1, wherein a kit is provided for the production of heat exchangers with at least two types of heat transfer cores for the production of more than two different heat exchangers, the kit advantageously a first type heat transfer core with a variety of Pairs of slices for creating a plurality of parallel flow paths between the pairs of slices, and further comprising a second type heat transfer core having a plurality of groups of three slices for producing a plurality of two parallel flow paths, each having a flow path between two of the three slices Ben is formed, wherein a first heat exchanger with a

Heat transfer core of the first type can be generated, wherein a second

Heat exchanger with two heat exchanger cores of the first type can be generated, wherein a third heat exchanger with a heat exchanger core of the first type and a heat transfer core of the second type can be generated, a fourth heat exchanger with two heat exchanger cores of the second type can be generated and a fifth heat exchanger with a heat transfer core of second type can be generated. It is inventively advantageous that the

Heat exchanger cores are designed so that they are used alone, combined with another core of the same type and usable and can also be combined and used with a heat exchanger core of the other type. As a result, in the case of using a heat exchanger core of the first type as a simple narrow evaporator this can be used as space-saving. This can be beneficial in small vehicles with low required

Cooling services done.

At higher required cooling capacities can in the case of using two heat exchanger cores of the first type, these in series or in

Parallel circuit arranged and used to each other, so that an increased cooling capacity can be realized with twice the space required.

When using the heat exchanger as a storage evaporator, a heat transfer core of the first type can be used with a heat transfer core of the second type, in which case the refrigerant can flow in parallel or in series through flow paths of the first core and the second core, wherein the cold storage medium through further flow paths of the second

Heat exchanger core can flow.

Also, two heat exchangers of the second type can be interconnected, so that, for example, an increased cooling capacity at the same time

Cold storage effect can be realized.

Furthermore, the second type of heat exchanger core can be used alone, for example as a double-row evaporator or as a single-row evaporator with cold storage. As a result, for example, a storage evaporator with lower cooling capacity can be realized.

It is advantageous if the Wirmeübertragerkerne of the first and / or second type are provided with connection devices and / or connecting devices for introducing and / or discharging and / or overflow of fluid in or between or from the heat exchanger cores or between

Flow channels of the heat exchanger cores. The object is achieved with respect to the heat transfer core with the features of claim 3, according to which a heat exchanger core is provided in disk construction, in particular for use in a kit, to form a heat exchanger, with a plurality of pairs of disks to form first flow paths, each with two slices a pair of disks form the first flow path between them and between adjacent ones

Disc groups each a space area for second flow paths is formed. The problem is in terms of Wärmeübertragerkerns also achieved with the features of claim 4 _"after which a heat transfer core in

Disk construction, in particular for use in a kit, is provided for forming a heat exchanger, with a plurality of disk groups to form third and fourth flow paths, wherein between each of a first and a second disc of a group of disks, the third flow path and between a second disc and a third disc of the disk group, the fourth flow path is formed and between adjacent disk groups each a space region for fifth flow paths is formed. It is expedient if at least individual disks have openings and / or cups as connecting and connecting areas and have channel-forming structures, such as embossings, for forming flow paths between connecting areas. It is also expedient if the first disc and the second disc of the disc pair each have a respective one at two opposite end regions

Connection region has as an inlet or outlet of the first flow path and in each case a channel-forming structure between the two connection areas for forming the first flow path.

Furthermore, it is expedient if the first disc and / or the second disc of the disc pair has two connection regions at one end region Inlet or outlet of the first flow path and in each case a channel-forming structure between the two connection areas for forming the first flow path. It is also expedient if the first disk _", the second and the third disc of the disc set on two opposite end regions in each case two connection regions having as an inlet or outlet of the third flow path or the fourth flow path, wherein the first and second disk respectively between an opposite terminal region a channel-forming structure between one of the two connection areas for forming the third and the fourth flow path, wherein the third disc between the first and the second disc as a partition wall between the third and the fourth

Flow path is provided. Heat exchanger having at least two Wärmeübertragerkernen according to any one of the preceding claims, characterized in that the distance of the plate pairs or groups of disks of a Wärmeübertragerkerns to form the second and / or fifth flow paths _»is selected in _such» that it is the same for adjacent Wärmeübertragerkernen of a heat exchanger or different, how smaller or larger than the neighboring one

Heat transfer core.

It is also expedient if the depth of the flow channels perpendicular to the plane, which is stretched out by the pairs of disks or groups of disks, is individually selectable for each flow channel.

Furthermore, it is expedient if disk pairs are formed from a paired arrangement of disks and with a partition between adjacent ones

Washers, which form pairs of flow channels, characterized in that the flow channels of a pair of discs are flowed through in countercurrent. Further advantageous embodiments are characterized by the following

Description of the figures and described by the subclaims.

Brief description of the drawings

Hereinafter, the invention will be based on at least one

Embodiment explained in more detail with reference to the drawings. FIG. 1 shows an arrangement of two heat exchanger cores, one

Heat exchanger core of a first type and a heat exchanger core of a second type,

FIG. 2 shows an arrangement of two heat exchanger cores in assembly,

FIG. 3 shows an arrangement of two heat exchanger cores of a first type,

FIG. 4 shows an arrangement of two heat exchanger cores of a second type, FIG. 5 shows a heat exchanger core of a first type,

FIG. 6 shows a heat exchanger core of a second type,

FIG. 7 shows two disks of a disk pair,

FIG. 8 shows three disks of a disk group,

FIG. 9 shows a number of disk pairs, FIG. 10 shows a number of disks and a section of a disk, FIG. 11b shows a pane in the cutout,

FIG. 11c shows a pair of disks of a disk group in the cutout, FIG. 11d shows a pair of disks of a disk group in the cutout,

FIG. 12 shows an arrangement of disk pairs and disk groups in a view, FIG. 13 shows an arrangement of disk pairs with disk groups in a view from the opposite side,

FIG. 14 shows an arrangement of disk pairs and disk groups in a section through the disk pairs and the disk groups,

Figure 1 5 shows a disc with an overflow between adjacent

By trains

FIG. 16 shows the disk of FIG.

FIG. 17 shows a view of a heat exchanger,

18 is a view of disc pairs, FIG. 19 is a view of discs,

FIG. 20 shows a section of discs,

FIG. 21 is a section of discs,

FIG. 22 shows a section of disk pairs, FIG. 23 shows a section through disk pairs according to FIG. 22,

FIG. 24 shows a section through disk pairs according to FIG. 22,

FIG. 25 shows a section of disk pairs,

FIG. 26 shows a section through disk pairs according to FIG. 25,

FIG. 27 shows a section through disk pairs according to FIG. 25,

Figure 28 is a schematic view of a heat exchanger, and

Figure 29 is a schematic view of a pair of discs.

Preferred embodiment of the invention

FIG. 1 shows the arrangement of two heat exchanger cores 1, 2, which can be connected to one another to form a heat exchanger. In this case, the heat transfer core 1 a plurality of pairs of disks 3, which are arranged adjacent to each other, wherein in free spaces between the respective adjacent pairs of disks corrugated fins 4 are arranged, for better heat transfer in the flow of air between the respective adjacent pairs of disks 3. As Zu- and Outlet the disks 3 at their opposite ends connections or openings formed as such as cups 5.6, which also serve to connect the pairs of disks 3 with each other.

The heat transfer core 2 is formed with a plurality of disc groups 7, in turn, adjacent disc groups leave 7 clearances 8 to Throughflow of air, wherein inclusion of corrugated fins for the improved heat exchange may be provided in the flow of air.

Figure 1 thus shows an arrangement of two heat exchanger cores 1, 2, wherein the first heat exchanger core 1 is a first type of heat transfer core formed with a plurality of pairs of disks for generating a plurality of parallel flow paths between the pairs of disks. Within the disk pairs, a flow path is created for flowing the disk through a fluid, allowing entry and exit of the fluid into and from the disk through a port formed through a cup in the disk.

The second heat transfer core 2 represents a heat transfer core of the second type formed with a plurality of groups of three disks for generating a plurality of two parallel flow paths, each forming a flow path between two of the three disks. For this purpose, the disk groups at its two opposite ends in each case two connection openings for inlet and outlet of a first and / or a second fluid, so that either two different fluids can flow through this heat transfer core 2 in each case different flow channels or in another application a fluid in different flow paths can flow in two columns through the heat exchanger core, wherein at one of the two heat exchanger core ends then a deflection of the fluid is provided by the one flow path in the other flow path. However, this deflection is not shown in FIG. In this regard, reference is made to FIGS. 15 and 16, which show a disc 200 in which an overflow channel is provided as a deflection between the cups 201. Evident are the inlets and outlets in the second heat transfer core 2 through the circular or substantially circular openings 10,11, which is arranged at the upper or lower end portion of the respective disc group. The plurality of adjacent disk groups form over the wells formed as wells 10.1 1 as connection areas an inlet or outlet distribution channel, so that a fluid that flows through the opening 10,1 1 and the relevant bowl in the heat traps over the length of the heat exchanger core can be distributed before it can flow through the flow channels along the heat exchanger disk group before it is again collected at the opposite end in the region of the connection of the wells, before the fluid can be discharged from the heat transfer core. This applies both to the flow channel between the first and the second disc and between the second and the third disc. As can be seen, the opening 10 is adjacent to the opening 1 1 and of a smaller cross section, so that quite different flow rates for the different media can be realized. In another embodiment, however, it may also be expedient if the openings 10, 1 1 of the flow paths of the same order of magnitude.

Figure 2 shows the arrangement of the two heat exchanger cores 1, 2 in an arrangement in which the heat exchanger cores are interconnected, thereby producing a heat exchanger having a first core having a plurality of parallel flow paths and a second core, which has a plurality of two adjacent flow paths.

Such a heat exchanger according to FIG. 2 can be used, for example, as a storage evaporator, wherein a first flow path 12 between the opening 5 and the opening 6 is used as the refrigerant flow path and then a diversion takes place as an inlet to the opening 11, so that the refrigerant flows through the flow path between the two openings 1 1, 1 1a can flow as connections and then escape from the evaporator. The flow path 13 between the openings as ports 10, 10a can be used as a storage medium flow path, so that during normal operation of the evaporator, the storage medium is cooled in this flow path and in the event that the refrigerant circuit of the air conditioner For example, is in a start-stop situation, the air flowing through, which is indicated by the arrow 14 can be further cooled by heat exchange between the storage medium in the flow path 13, so that even during a temporary stoppage phase of the refrigerant circuit of the air conditioning in the start-stop Operation still some cooling power can be provided.

It is advantageous if a heat exchanger core of Figure 1, as it is designated by reference numeral 1, is also usable as a stand-alone heat exchanger, see Figure 5, wherein such a heat exchanger 20 can be used for example as a disk evaporator in an air conditioner with little available space. Although this heat exchanger 20 as an evaporator would only provide a reduced cooling capacity available, this may well be sufficient for small vehicles such as small electric vehicles. The heat exchanger 20 consists of a core 25 of a plurality of pairs of disks 26 which are spaced from each other, so that air can flow through the intermediate spaces 24, which is thereby cooled. The air flow direction is indicated by the arrow 27. The pairs of disks 26 have connections which are formed by cups, which serve to form the collecting space and which serve for mutual engagement with adjacent disk pairs. A fluid can flow into a connection region, see arrow 21, and the fluid can flow out from an opposite connection region, see arrow 22. Between the two connection regions lies the flow path 23, which is formed by the pair of discs and through which the fluid flows.

Furthermore, two such heat exchanger cores according to reference numeral 1 of Figure 1 can be used in parallel or in series, so that for example a double-row evaporator assembly can be formed by two heat exchanger cores of the first type. This is shown in FIG. FIG. 3 shows a heat exchanger 30, which consists of two Each of the two heat exchanger cores 31, 32 is composed of a plurality of pairs of disks 33,34 which are each spaced from one another in a row in the respective core, so that through the gaps 35,36 between the pairs of disks 33,34, for example, air can flow, which is thereby cooled. The air flow direction is indicated by the arrow 37. The pairs of disks 33 have connections 38, 39, which are formed by cups, which also serve to form the collecting spaces 40, 41 and which serve for mutual contact with adjacent pairs of disks. The pairs of disks 34 have connections 42,43, which are formed by wells, which also serve to form the collecting spaces 44,45 and which serve for mutual contact with adjacent disk pairs. For example, a fluid can flow into the first core 31 into a connection region 38. The fluid flows through the flow channel 46 and can exit the first core 31 at 39. It is deflected to enter the second core at 43. Subsequently, the fluid flows through the second flow channel 47 and flows out of an opposite connection region 42 out of the second core 32 again. The deflection is not shown, it can be done through a pipe or the like. Alternatively, only one Wirmeübertragerkern according to reference numeral 2 of Figure 1 be used, stand for this figure 6, in which case a double-flow is made possible, since already each disk assembly forms two flow paths, which can be flowed through in different flow direction, so this is a Alternative represents an example evaporator, which can be used with little available space. FIG. 6 shows a heat exchanger 50, which consists of only one heat exchanger core 51 of the second type. The heat transfer core 51 consists of a plurality of disk groups 52 which are each spaced from one another in a row, so that, for example, air can flow through the intermediate spaces 53 between the disk groups 52, which can be cooled thereby. The air flow direction is indicated by the arrow 54 characterized. The pairs of disks 52 form two parallel flow channels 55, 56, which are each formed by two of the three disks of the disk group 52.

The connections of the two flow channels or flow paths 55,56 are formed by the connections 57,58,59,60, which are designed as wells, which also serve to form the respective collecting chambers 61, 62,63,64 and the mutual investment Serve with adjacent pairs of discs or disc group. In a connection region 57, for example, a fluid can flow into the first flow channel 55. The fluid then flows through the flow channel 55 and can exit at the cup 58 as an outlet from the first flow channel 55. The fluid is then deflected to enter the second flow channel 56 at the cup 59. Subsequently, the fluid flows through the second flow channel 56 from the cup 59 to the cup 60 and flows there at the inlet opposite outlet again from the second flow channel. The deflection is not shown, it can be done through a pipe or the like.

Furthermore, it would be possible to connect two heat exchanger cores according to reference numeral 2 of FIG. 1, ie two heat exchanger cores of the second type, to a heat exchanger which provides four flow paths, ie two flow paths per heat exchanger core, in order to allow for example a four-flow throughflow for a given installation space , FIG. 4 shows such a heat exchanger 70, which consists of only a first heat exchanger core 71 of the second type and a second heat exchanger core 72 of the second type. In order to avoid repetition, the mode of action of the two heat exchanger cores 71, 72 according to the heat exchanger core of FIG. 6 is explained. In this example, a fluid is flowed through by a first core 71 and then deflected to a second core 72 and then flows through this second core 72 before the fluid exits from this core 72 again. FIG. 7 shows two disks 80 and 81 of a disk pair 82, which are of identical construction and are arranged laterally reversed relative to one another. The two discs each have a cup 83 and an opposite cup 84 formed on the opposite end portions of the disc. The cups point from the base 85 of the disc in a direction perpendicular thereto so as to project from the base 85 of the disc. Furthermore, the disc has a peripheral rim 86 projecting in the direction perpendicular to the plane of the disc 85, the rim 86 protrudes in the opposite direction than the cup 87 and 88 of the openings 83,84. If now two disks are brought into contact with each other, then they abut against one another at the peripheral edges 86 and can be soldered together sealingly there. This causes between the two discs, a flow channel 89 is formed, which serves to flow through the disc and which is in fluid communication with the openings 83, 84.

FIG. 8 shows a group of disks with the disks 90, 91 and 92. In this case, the disk 90 has a base plane 93 and a circumferential edge 94 protruding therefrom, openings 95 and 96 being provided at each of the two opposite ends, which are provided with circumferential cups are formed, wherein the cups with respect to the ground plane 93 are perpendicular thereto and protrude in a different direction than the peripheral edge 94th

As can be seen, the flow channel 97 is defined between the openings 95 and is in fluid communication therewith, wherein the flow channel is defined by the opening 96 and is not in communication therewith,

The disc 91 is flat and has at the two opposite ends in each case openings 98.99, which are formed without cups, wherein the disc 91 is flat and has no embossed structures. If now the disc 90 is placed on the disc 91, the two discs touch each other in the region of the peripheral edge 94 and can thus be fluid-tight with each other be connected, that on the one hand, the openings 98 are aligned with the openings 95 and between the disc 90 and the disc 91 of the fluid channel 97 is defined, the openings 96 are aligned with the openings 99, but are not in communication with the fluid channel 97.

The disc 92 also has at its opposite ends openings 100, 101, wherein in the base portion 102 of the disc, a fluid channel 103 is formed, which communicates with the openings 101, wherein a peripheral edge 104 is formed in a direction perpendicular to the plane of Base surface 102 protrudes, wherein the openings 100 are embossed in the peripheral edge, and thus are not in Fiuidverbindung with the flow channel 103. The openings 100 and 101 are configured with wells projecting perpendicularly to the direction of the ground plane 102, these projecting rearwardly in FIG. 8 and thus projecting in the opposite direction of the peripheral edge 104.

When connecting the disc 92 with the disc 91, a fluid-tight connection takes place in the edge region 104 between the two discs, with the openings 99 and 101 respectively aligned and Fiuidverbindung to the fluid channel 103 and the openings 98 and 100 aligned with each other However, openings have no Fiuidverbindung to the fluid channel 103. Now, if the discs 90,91 and 92 connected to each other, creating two fluid channels 97 and 103, which are separated by the interposition of the disc 91 from each other and each communicating with openings for the inlet and outlet of a fluid. Thus, the openings 95, 98 and 100 connect the fluid channel 97 and the openings 96, 99 and 101 connect the fluid channel 103.

FIG. 9 shows an arrangement of a plurality of disk pairs according to FIG. 7, wherein the pairs of disks 110 are soldered to one another and subsequently connected to one another so that they touch one another in the region of the protruding cups 11 and thereby define a spacing between the disk pairs which is larger than the extent of the disc perpendicular to the base plane of the disc, so that between the two respective adjacent slices a space portion 112 remains freigespart, for the passage of, for example, air. FIG. 10 shows a similar arrangement example of disk groups 113 according to FIG. 8, whereby these disk groups are in turn connected to one another and adjacent disk groups come into contact with each other via the protruding cups 114, 115. Hiss the disk groups is in turn a free space 116 freiges to flow through, for example, air.

FIG. 11c shows a section of a disk 82 according to FIG. 7, as well as FIG. 11b, wherein the disk 82 has a flat base region 85 opposite to which the peripheral edge 86 protrudes, at the same time the opening 83 has a cup 87 which is opposite the base surface This is also clearly visible in FIG. 11b, so that the cup 87 in FIG. 11b protrudes forward with respect to the base 85, with the peripheral edge 86 protruding to the rear in FIG. 11b.

The same can be seen in FIGS. 11 c and 11 d for the disks 90 and 92, wherein the disk 91 can not be seen in this consideration of FIGS. 11 c and 11 d. The discs 92 and 90 each have at their opposite ends two openings 95 and 100 and 101 and 96, these openings being surrounded by cups projecting from the base portions 97 and 102 of the discs, respectively. As can be seen, the flow channel 103 or the flow channel 97 is in each case fluid-connected to another opening, so that the flow channel 97 is connected to the opening 95, while the flow channel 103 is connected to the opening 101. If these disks are now placed one on top of the other according to FIG. 8, the small openings 95, 100 can be connected to one another, while the large openings 96 and 101 can be connected to one another. The fluid channels 97 and 103 are in communication with the respective openings durchströmbar ausgestaltet, wherein the two flow channels 97 and 103 are separated by the interposition of the disc 91, not shown, but from each other,

FIG. 12 shows the arrangement of disk pairs and disk groups in adjacent arrangement, wherein the disk pairs of the disks 82 are arranged in the air flow direction before the arrangement of the disk groups of the disks 90, 91, 92.

It can be seen that the flow channel 85 of the air flow is first exposed before the flow channel 97 and the flow channel 103, not shown, is flowed around. FIG. 13 shows this from the other side, so that it can be seen that first the flow channel 85 is surrounded by air before the flow channel 103 is flowed around. FIG. 14 again shows this in section, wherein it can be seen that the flow channel 85 is formed by two discs 82, wherein the flow channels 97 and 103 are formed by the discs 90, 91 and 92, the two flow channels 90 and 103 in FIG In a direction perpendicular to the direction of air, in sum, occupy only the space that is occupied by the air channel 85 of the two discs 82.

17 shows a heat exchanger 300 with a heat transfer core, wherein the heat transfer core 301 is formed by a plurality of parallel pairs of discs consisting of two discs which form two flow paths between each disc and the partition wall with the interposition of a partition wall. For this purpose, the heat exchanger 300 has a plurality of disk pairs 302, which are arranged adjacent to one another, wherein corrugated fins 303 are preferably arranged between the disk pairs. Each disk pair, see also FIG. 18, has two inlet openings 304, 305, 306, 307 designed as wells at a first end area and at a second end area. In this case, a cup of an end region 304 or 305 forms an input-side cup, wherein the output-side cup associated with the flow path 308 in the other end region is arranged. Accordingly, an inlet-side and an outlet-side cup are provided as inlet or outlet of the heat exchanger on each side in each end region. For this purpose, FIG. 18 shows three pairs of disks, each shown at a distance, which consist of two disks and an intermediate wall, these pairs of disks being arranged to form a disk package 310.

19 shows the arrangement of a disk pair consisting of the disks 31 1 and 312, the disk 31 1 forms a flow channel 313 and the disc 312 a flow channel 314. These flow channels are formed by embossments between two wells, only two of the four shown cups are connected to the flow channel. Thus, the cup 315 and the cup 316 are connected to the flow channel 313, wherein the cups 317 and 318 are not connected to the flow channel 313. In the disc 312, the cup 319 and the cup 320 are connected to the flow channel 314, with the cup 321 and the cup 322 not connected to the flow channel. If the two discs 31 1 and 312 soldered together with the interposition of the wall 323, so there is a fluid connection between the wells 315 and 321 and 316 and 322 and 318 and 319 and 317 with 320, so that the wells 315, 321 an entrance cup for represent the flow channel 313 and the cups 317 and 320 constitute an outlet cup. The same applies to the arrangement of the flow channel 314. Figures 20 and 21 show the arrangements of the wells 319, 321 of Figure 19 in an enlarged view, wherein the wells 319 and 321 are formed separately in Figure 20 and the cup 319 with the flow channel 314 is fluidly connected while the cup 321 is separated from the flow channel 314. Two wells 330 and 331 are likewise shown in FIG. 21, wherein a transition 332 is provided between the two wells 330, which allows an overflow of a fluid from the bowl 330 to the bowl 331. FIG. 22 shows a disk package with three pairs of disks in a perspective representation, wherein only the uppermost region of the disk package 340 is shown. FIG. 23 shows a section according to section 1 of FIG. 22 and FIG. 24 shows a section according to section 2 of FIG. 22. It can be seen that in each case a pair of discs 350, 351 is provided with an intermediate layer 352, wherein between the discs 350 and 351 a flow kana! 353 is disposed on one side of the partition wall 352, while a second flow channel 354 is disposed on the other side of the partition wall. This pattern is repeated for each disk pair of the three disk pairs shown, so that two flow channels 354, 353 are arranged on both sides of the partition wall 352 between the disk pairs.

FIG. 24 also shows the flow channels 353 and 354 each arranged on one side of the partition wall 352. FIG. 25 shows the disk package 340, wherein FIG. 26 shows a section according to section 3 of FIG. 25 and FIG. 27 shows a section according to section 4 of FIG. 25.

In the figures 26 and 27, the discs 350 and 351 are shown at intermediate would be the partition 352, wherein each of the flow channels 354 and 353 can be seen. It can be seen in section 3 that the flow channels do not extend over the full width of the disc, wherein the flow channels in the figure 27 extend substantially over the entire disc. This is due to the fact that the channel profile to the cup must be returned from the substantially full width to about half the width.

The design of the pairs of disks makes it possible to form a heat exchanger consisting of a series of disk pairs, each of which forms both a first flow channel connected to an inlet header and an outlet header and a second flow channel likewise provided with an inlet header and an outlet header is. there The cups, which are connected in series with each other, the respective inlet collector and outlet collector. The respective disk pair consists of two opposing disks, wherein between the two disks, a partition wall or a partition plate is provided, which separates the flow channels of the respective disks from each other. When the flow channels are countercurrently flowed, the separating plate serves to separate the opposing fluid streams through the flow channels, the cups of the individual pairs of discs arranged in series with one another forming the fluid inlet collector or the fluid outlet collector.

FIG. 28 shows the schematic arrangement of disk pairs 400, 401, which have an inlet-side cup 402 and an outflow-side cup 403. The fluid flow takes place from the inlet-side bowl 402 through the flow channel 401 to a passage 404, from where the fluid can flow into the second flow channel 400 in order to flow to the bowl 403. In the case of the pairs of disks arranged next to one another in each case, this is carried out in each case, the two flow channels 400 and 401 being operated in countercurrent to one another.

FIG. 29 shows this in an enlarged view. The pair of discs 401, 400 is provided with ribs 405 on both sides for the flow around air.

The invention relates to a heat exchanger with internal integrated heat transfer by means of two in a tube in the counter-current flow channels.

The following will describe the construction of a disk-type heat exchanger, alternatively embodiments such as e.g. possible in flat tube design.

The heat exchanger consists of a series of disk pairs, each half in each case a first connected to the inlet header or -napf

Flow channel as well as a second associated with the outlet collector or -napf flow channel. The pair of discs is in turn made of two facing discs and an intermediate therebetween separating plate composed. The separating plate is used to separate the

counter-rotating fluid streams, the interconnected cups of the arrayed pairs of discs form on the one hand the fluid inlet header for distributing the fluid to the individual first flow channels, and on the other hand the fluid outlet header for collecting the fluid from the individual second

Flow channels.

In this case, the two discs 31 1, 312 and only in the

Transition area between the disc channel and the cups, at the

Fluid inlet disc 31 1 is a flow connection between the flow channel 313 and the fluid inlet cup coined, wherein the fluid disc 312 a

Connection between the flow channel 314 and the fluid outlet cup consists.

These connection embossings can be carried out alternately in the disk tool and thus both disks can be produced in one and the same tool with a replacement set. This reduces tool costs and increases the number of identical parts.

The heat exchanger described above is flowed through so that a fluid, such as refrigerant or coolant, etc. on the first collector as

Entrance collector z. B. at the Blockoberseitein a first disc channel half 31 1 flows, then referred to a connecting element between the two opposite collectors, as inlet collector and outlet collector then on the block bottom, is transferred to the second disc channel half 312, flows through them and then from this second channel half over the second collector, as outlet collector then again referred to the block top, again flows out.

The advantage of this type of flow is the homogenization of the

Temperature profiles e.g. as an evaporator, by a homogenization of the

different temperatures of the countercurrent fluid flows due to Heat transfer between the two channel halves on the one hand, and on the other hand by equalizing the temperature of the air flowing around the two channel halves,

The connecting element between the two opposing collectors on the underside of the block can be a separate connecting part or else in a side part with integrated deflection channel or the like. be executed.

In the case of a two-block interconnection, the fluid is distributed simultaneously via the inlet header to all first disc channel halves 31 1 arranged in parallel and, according to the deflection, distributed further to all second disc channel halves 312 by means of a connecting element.

In a Mehrblockverschaltung we the fluid only at a certain number of parallel arranged first disc channel halves 31 1 distributed simultaneously, then the fluid transfer takes place from a collector to the adjacent collector directly into the

Slices, e.g. via embossed connection channels between the adjacent collecting cups of a disk, before then after flowing through the second

Disc channel halves 312 the fluid is forwarded to the next block and there again the same distribution process is continued as in the first block.

The flow channel eübertrager, in particular the disc evaporator, can alternatively be carried out in single-tank design, ie with only one tank on one side of the Würmeübertragers

The interconnection of the individual modules can be varied depending on the arrangement and / or embodiment.

In the evaporator, a pressure drop is generated depending on the mass flow or operating point. Depending on the pressure drop, different absolute pressures and thus

different evaporation pressures between evaporator inlet and outlet. This has the consequence that the evaporation temperature at the evaporator inlet at high pressure drops can be significantly higher than the evaporating pressure associated temperature at the outlet. This results in a temperature response of the evaporating refrigerant as a function of self-adjusting pressure drop across the heat exchanger. In addition, overheating of the refrigerant at the end of evaporation at the evaporator exit is desired to produce a stable overheat signal at the injector (eg, 5K).

However, this creates local hot zones on the evaporator, which can be replaced by suitable measures such. B. multiple connections in the air direction one behind the other, can be homogenized.

By integrating an internal heat transfer surface in the evaporator over substantially the entire height, local warm zones can be minimized between vapors entering and exiting.

Due to the heat transfer at the integrated inner heat transfer surface, a stable overheating can occur between the incoming refrigerant

countercurrent refrigerant can be generated at the outlet. Due to the significantly higher heat transfer, this happens in a much smaller section of the evaporator than in conventional systems with multiple interconnection.

The temperature of the flowing refrigerant through the evaporator sets much faster at a lower average temperature level and the overheating zone can be reduced to a minimum in the evaporator. This results in a high driving average temperature gradient and an associated increase in performance.

Claims

claims

1, building block for the production of heat exchangers with at least two types of heat exchanger cores for the production of more than two

different heat exchangers, the kit consists of:

a first type of heat transfer core with a plurality of

Pairing disks to create a plurality of parallel flow paths between the pairs of disks and

a second type of heat transfer core with a plurality of

Groups of three disks for generating a plurality of two parallel flow paths, each having a flow path between two of the three disks

wherein a first heat exchanger with a heat exchanger core of the first type can be generated, wherein a second heat exchanger with two

Heat exchanger cores of the first type can be generated, wherein a third heat exchanger with a heat exchanger core of the first type and with a heat transfer core of the second type can be generated, a fourth heat exchanger with two heat exchanger cores of the second type can be generated and a fifth heat exchanger with a

Heat transfer core of the second type can be generated.

2. Construction kit according to claim 1, characterized in that the

Heat exchanger cores of the first and / or second type with

Connection devices and / or connection devices are provided for introducing and / or discharging and / or passing fluid into or between or out of the heat exchanger cores. Disk heat exchanger core, in particular for use in a construction kit according to one of the preceding claims _» for forming a heat exchanger, with a plurality of pairs of disks for forming first flow paths, wherein in each case two disks of a

Disc pair form the first flow path between them and between adjacent disc groups each a space region is formed for second flow paths.

Disk heat exchanger core, in particular for use in a kit according to one of the preceding claims 1 and 2, for forming a heat exchanger, with a plurality of disk groups to form third and fourth flow paths, wherein between each of a first and a second disc of a disk group of the third Flow path and between a second disc and a third disc of the disc group, the fourth flow path is formed and between adjacent disc groups each have a space area for fifth

Flow paths is formed.

Heat exchanger core according to claim 3 or 4, characterized in that at least individual disks as connection and connection areas openings and / or wells and for the formation of

Flow paths between terminal areas channel-forming structures, such as embossments have.

Heat exchanger core according to claim 3 or 5, characterized in that the first disc and the second disc of the pair of discs at two opposite end regions each having a connection region as inlet or outlet of the first flow path and a respective channel-forming structure between the two connection areas

Formation of the first flow path.

7. heat transfer core according to claim 3 or 5, characterized in that the first disc and / or the second disc of the disc pair has at one end regions two connection areas as inlet or outlet of the first flow path and a respective channel-forming structure between the two connection areas for forming the first flow path.

8. heat transfer core according to claim 4 or 5, characterized in that the first disc, the second and the third disc of the disc group at two opposite end regions in each case two connection areas as inlet or outlet of the third flow path or of the fourth

Flow path, wherein the first and the second disc each between an opposite terminal portion has a channel-forming structure between one of the two connection areas for forming the third and fourth flow paths, wherein the third disc between the first and the second disc as a partition between the third and the fourth flow path is provided.

9. Heat exchanger with at least two heat exchanger cores according to one of the preceding claims, characterized in that the distance between the pairs of disks or the disk groups of a heat transfer core to form the second and / or fifth flow paths, is selected such that it is the same at adjacent heat exchanger cores of a heat exchanger or different, as smaller or larger than the adjacent heat transfer core.

10. Heat exchanger with at least two heat exchanger cores according to one of the preceding claims, characterized in that the depth of the flow channels perpendicular to the plane, which is stretched by the pairs of disks or groups of disks, is individually selectable for each Strömungskanaf. Heat exchanger according to at least one of the preceding claims, characterized in that disc pairs are formed from a paired arrangement of discs and with a partition wall between adjacent discs, which form pairs of flow channels, characterized

characterized in that the flow channels of a disc pair in

To be flowed through countercurrent.