EP2798297B1 - Method for manufacturing at least two different heat exchangers - Google Patents

Description

Technical area

The invention relates to a method for producing more than two different heat exchangers by means of a modular system.

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, for example as an 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.

The DE 102006028117 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 hand, a cold storage medium in a space 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 is typically a modification of a standard refrigerant evaporator, so that this component is not 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 Anschlußelerrienten to different refrigerant or cold storage media-medium cycles. The production of such a storage evaporator in turn shows a high parts cost, which leads to significant additional costs.

The embodiment of a storage evaporator in disk construction according to the second embodiment of the EP 1817534 B1 shows that once again a singular solution has been developed which is not very suitable for other applications.

The US 2008/0121381 discloses a combined heat exchanger comprising two different plate-type heat exchangers.

The heat exchangers in the prior art are thus very specifically adapted to the needs of the respective medium 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 method for producing more than two different heat exchangers, which are produced by means of a modular system for the production of heat exchangers with at least two types of heat exchanger cores.

This is achieved for the method with the features of claim 1.

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 done advantageously in small vehicles with low cooling capacities required.

At higher required cooling capacities, in the case of using two heat exchanger cores of the first type, these can be arranged and used in series or in parallel with 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 transfer core can flow.

Also, two heat exchangers of the second type can be interconnected, so that, for example, an increased cooling capacity can be realized with simultaneous cold storage effect.

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 heat exchanger cores of the first and / or second type are provided with connecting devices and / or connecting devices for introducing and / or discharging and / or passing fluid in or between or from the heat exchanger cores or between flow channels of the heat exchanger cores.

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 disk and the second disk of the disk pair each have a connection region at two opposite end regions as the inlet or outlet of the first flow path and in each case a channel-forming structure between the two connection regions for forming the first flow path.

Furthermore, it is expedient for the first disk and / or the second disk of the disk pair to have 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 for the first disk, the second and the third disk of the disk group to have two connection regions at two opposite end regions as the inlet or outlet of the third flow path or the fourth flow path, the first and the second disk each between an opposite connection region a channel-forming structure between one of the two connection regions for forming the third and the fourth flow path, wherein the third disc is provided between the first and the second disc as a partition wall between the third and the fourth flow path. It is also expedient that the spacing of the pairs of disks or the groups of disks of a heat transfer core for forming the second and / or fifth flow paths is selected such that it is the same for different heat exchanger cores of a heat exchanger or different, as smaller or larger than in the adjacent 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 wall between adjacent disks, which form pairs of flow channels, characterized in that the flow channels of a disk pair are flowed through in countercurrent.

Further advantageous embodiments are described by the following description of the figures and by the subclaims.

Brief description of the drawings

Figur 1

zeigt eine Anordnung zweier Wärmetauscherkerne, ein Wärmetauscherkern eines ersten Typs und einen Wärmetauscherkern eines zweiten Typs,

Figur 2

zeigt eine Anordnung zweier Wärmetauscherkerne in Zusammenbau,

Figur 3

zeigt eine Anordnung zweier Wärmetauscherkerne eines ersten Typs,

Figur 4

zeigt eine Anordnung zweier Wärmetauscherkerne eines zweiten Typs,

Figur 5

zeigt einen Wärmetauscherkern eines ersten Typs,

Figur 6

zeigt einen Wärmetauscherkern eines zweiten Typs,

Figur 7

zeigt zwei Scheiben eines Scheibenpaares,

Figur 8

zeigt drei Scheiben einer Scheibengruppe,

Figur 9

zeigt eine Anzahl von Scheibenpaaren,

Figur 10

zeigt eine Anzahl von Scheiben und einen Ausschnitt einer Scheibe,

Figur 11b

zeigt eine Scheibe im Ausschnitt,

Figur 11c

zeigt ein Paar von Scheiben einer Scheibengruppe im Ausschnitt,

Figur 11d

zeigt ein Paar Scheiben einer Scheibengruppe im Ausschnitt,

Figur 12

zeigt eine Anordnung von Scheibenpaaren und Scheibengruppen in einer Ansicht,

Figur 13

zeigt eine Anordnung von Scheibenpaaren mit Scheibengruppen in einer Ansicht von der entgegengesetzten Seite,

Figur 14

zeigt eine Anordnung von Scheibenpaaren und Scheibengruppen in einem Schnitt durch die Scheibenpaare und die Scheibengruppen,

Figur 15

zeigt eine Scheibe mit einem Überströmkanal zwischen benachbarten Durchzügen,

Figur 16

zeigt die Scheibe der Fig. 15 von der Rückseite,

Figur 17

eine Ansicht eines Wärmeübertragers,

Figur 18

eine Ansicht von Scheibenpaaren,

Figur 19

eine Ansicht von Scheiben,

Figur 20

ein Abschnitt von Scheiben,

Figur 21

ein Abschnitt von Scheiben,

Figur 22

ein Abschnitt von Scheibenpaaren,

Figur 23

ein Schnitt durch Scheibenpaare gemäß Figur 22,

Figur 24

ein Schnitt durch Scheibenpaare gemäß Figur 22,

Figur 25

ein Abschnitt von Scheibenpaaren,

Figur 26

ein Schnitt durch Scheibenpaare gemäß Figur 25,

Figur 27

ein Schnitt durch Scheibenpaare gemäß Figur 25,

Figur 28

eine schematische Ansicht eines Wärmeübertragers, und

Figur 29

eine schematische Ansicht eines Scheibenpaares.

The method according to the invention will be explained in more detail on the basis of at least one embodiment with reference to the drawings. Show it:

FIG. 1

shows an arrangement of two heat exchanger cores, a 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 discs of a disc pair,

FIG. 8

shows three disks of a disk group,

FIG. 9

shows a number of pairs of discs,

FIG. 10

shows a number of slices and a section of a slice,

FIG. 11b

shows a slice in the neckline,

FIG. 11c

shows a pair of discs of a disc group in the neck,

FIG. 11d

shows a pair of slices of a group of slices 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,

FIG. 15

shows a disc with an overflow between adjacent passages,

FIG. 16

shows the disc the Fig. 15 from the back,

FIG. 17

a view of a heat exchanger,

FIG. 18

a view of disc pairs,

FIG. 19

a view of slices,

FIG. 20

a section of slices,

FIG. 21

a section of slices,

FIG. 22

a section of disc pairs,

FIG. 23

a section through pairs of discs according to FIG. 22 .

FIG. 24

a section through pairs of discs according to FIG. 22 .

FIG. 25

a section of disc pairs,

FIG. 26

a section through pairs of discs according to FIG. 25 .

FIG. 27

a section through pairs of discs according to FIG. 25 .

FIG. 28

a schematic view of a heat exchanger, and

FIG. 29

a schematic view of a pair of discs.

Preferred embodiment of the invention

The FIG. 1 shows the arrangement of two heat transfer cores 1,2, which are connectable to a heat exchanger together. In this case, the heat transfer core 1 has a plurality of disk pairs 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 disk pairs 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 a recording of corrugated fins for the improved heat exchange in the flow of air may be provided.

The FIG. 1 Thus, Figure 1 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 group 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. This diversion is however in the FIG. 1 not shown. In this regard, be on the FIGS. 15 and 16 referenced, which show a disc 200, in which an overflow channel is provided as a deflection between the wells 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 region of the respective disc group. The plurality of adjacent disk groups form over the wells formed as wells 10,11 as port areas, an inlet or outlet manifold, so that a fluid that flows through the opening 10, 11 and the respective bowl into the heat exchanger core can be distributed over the length of the heat exchanger core before flowing through the flow channels along the heat exchanger disk array can, before it is collected at the opposite end in the region of the connection of the wells again, 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 11 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, 11 of the flow paths are of the same order of magnitude.

The FIG. 2 shows the arrangement of the two heat transfer cores 1,2 in an arrangement in which the heat transfer cores are interconnected, thereby producing a heat exchanger having a first core having a plurality of parallel flow paths, and having a second core having 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 a refrigerant flow path and then a deflection takes place to the opening 11 as an inlet, so that the refrigerant through the flow path between the two openings 11,11a as Connections can flow 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 transfer core of the FIG. 1 , as indicated by reference numeral 1, is also usable as a stand-alone heat exchanger, see FIG. 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 transfer cores according to reference numeral 1 of FIG. 1 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 in FIG. 3 shown. The FIG. 3 shows a heat exchanger 30, which consists of two Heat exchanger cores 31,32 of the first type is composed. Each of the two heat exchanger cores 31,32 consists of a plurality of pairs of discs 33,34 which are each spaced from each other in a row in the respective core are arranged so that through the gaps 35,36 between the pairs of discs 33,34, for example, air can flow through it is coolable. 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 at 39 from the first core 31. It is diverted 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 heat transfer core according to reference numeral 2 of FIG. 1 can be used, see this FIG. 6 , In this 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 that this is an alternative to an example evaporator, which can be used with little available space. The 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, two heat exchanger cores according to reference numeral 2 of FIG. 1 So to connect two heat transfer cores of the second type, to each other to a heat exchanger, the four flow paths, so two flow paths per heat exchanger core provides to allow for example a four-flow through-flow with a given space. The FIG. 4 shows such a heat exchanger 70, which consists of only a first heat transfer core 71 of the second type and a second heat transfer core 72 of the second type. To avoid repetition, the operation of the two heat transfer cores 71,72 according to the heat transfer core of the FIG. 6 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.

The FIG. 7 shows two discs 80 and 81 of a disc pair 82, which are identically formed and reversed to each other. 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 protrude from the base 85 of the disc. Furthermore, the disc has a peripheral edge 86 projecting in the direction perpendicular to the plane of the disc 85, the rim 86 projecting in the opposite direction than the cup 87 or 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.

The FIG. 8 shows a disc group with the discs 90, 91 and 92. In this case, the disc 90 has a ground plane 93 and a respective protruding peripheral edge 94, wherein at the two opposite ends openings 95 and 96 are respectively provided, which are formed with encircling cups, the cups being perpendicular to the base plane 93 and projecting in a different direction than the peripheral edge 94.

As can be seen, the flow channel 97 is defined between and communicates with the openings 95 in fluid communication with the flow channel being defined from and not communicating with the opening 96.

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 fluid communication with the flow channel 103. The openings 100 and 101 are configured with wells projecting perpendicular to the direction of the ground plane 102, wherein these in the FIG. 8 protrude to the rear and thus protrude opposite to the peripheral edge 104.

When connecting the disc 92 to the disc 91, a fluid-tight connection takes place in the edge region 104 between the two discs, with the ports 99 and 101 respectively aligned and fluidly connected to the fluid channel 103 and the ports 98 and 100 aligned with each other However, openings have no fluid connection 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.

The FIG. 9 shows an arrangement of a plurality of disc pairs according to the FIG. 7 in that the pairs of discs 110 are soldered together and then joined adjacent to each other, so that they touch each other in the area of the protruding cups 111, thereby defining a distance between the pairs of discs which is greater 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.

The FIG. 10 shows a similar arrangement example of disk groups 113 according to the FIG. 8 , wherein these disk groups are in turn connected to each other 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.

The FIG. 11c shows a section of a disc 82 according to FIG. 7 , as well as the FIG. 11b , wherein the disc 82 has a flat base portion 85 opposite to the peripheral edge 86 protrudes, at the same time the opening 83 has a cup 87 which protrudes from the base 85 in a different direction. This is also in the FIG. 11b good to see, so that the cup 87 in the FIG. 11b protrudes forward relative to the base 85, wherein the peripheral edge 86 in the FIG. 11b protrudes to the rear.

Similar is in the Figures 11c and 11d for the discs 90 and 92, wherein the disc 91 in this regard the Figures 11c and 11d are not recognizable. 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. Are these discs now superimposed according to the FIG. 8 Thus, the small openings 95, 100 are connectable to each other, while the large openings 96 and 101 are connected to each other. The fluid channels 97 and 103 are in communication with the respective openings configured through-flow, wherein the two flow channels 97 and 103 are separated by the interposition of the disc 91, not shown, but from each other.

The FIG. 12 shows the arrangement of disk pairs and disk groups in adjacent arrangement, wherein the pairs of disks of the discs 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. The 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. The FIG. 14 shows this again 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, wherein the two flow channels 90 and 103 in a direction perpendicular to the air direction take in sum only the space area which is occupied by the air channel 85 of the two discs 82.
The FIG. 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 disks 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 pair of discs, see also FIG. 18 , Has at a first end portion and at a second end region in each case two as wells designed inlet openings 304, 305, 306, 307. 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.

The FIG. 18 shows three spaced-apart disc pairs, which consist of two discs and an intermediate wall, said pairs of discs are arranged to a disc package 310.

The FIG. 19 shows the arrangement of a disc pair consisting of the discs 311 and 312, the disc 311 forms a flow channel 313 and the disc 312 a flow channel 314. These flow channels are formed by embossments between two wells, with only two of the four shown cups with the flow channel are connected. 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 disks 311 and 312 are soldered together with the wall 323 interposed, a fluid connection between the wells 315 and 321 and 316 and 322 and 318 and 319 and 317 takes place with 320, so that the wells 315, 321 an inlet cup for the Represent flow channel 313 and the cups 317 and 320 constitute an outlet cup. The same applies to the arrangement of the flow channel 314.

The FIGS. 20 and 21 show the arrangements of the wells 319, 321 of FIG. 19 in an enlarged view, wherein the cups 319 and 321 in FIG. 20 are formed separately from each other and the cup 319 is fluidly connected to the flow channel 314, while the cup 321 is separated from the flow channel 314. In the FIG. 21 two wells 330 and 331 are also shown in each case, 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.

The FIG. 22 shows a disk package with three pairs of disks in a perspective view, wherein only the uppermost portion of the disk package 340 is shown. The FIG. 23 represents a section according to section 1 of FIG. 22 and the FIG. 24 shows a section according to section 2 of FIG. 22 , It can be seen that in each case a pair of disks 350, 351 is provided with an intermediate layer 352, wherein between the disks 350 and 351 a flow channel 353 is arranged on one side of the partition 352, while a second flow channel 354 is arranged on the other side of the partition. 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.

The FIG. 24 FIG. 3 also shows the flow channels 353 and 354 respectively disposed on one side of the partition wall 352. The FIG. 25 shows the disc package 340, wherein the FIG. 26 a section according to section 3 of FIG. 25 represents and the FIG. 27 a section according to section 4 of FIG. 25 ,

In the FIGS. 26 and 27 the disks 350 and 351 are shown with the partition wall 352 interposed, the flow channels 354 and 353 being visible in each case. It can be seen in section 3 that the flow channels do not extend over the full width of the disc, the flow channels in the FIG. 27 essentially run 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. If the flow channels are countercurrently flowed, the separating plate serves to separate the opposing fluid streams through the flow channels, wherein the wells of the individual pairs of disks, which are arranged in series with one another, form the fluid inlet collector or the fluid outlet collector.

The 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.

The 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 following describes the design of a disk-type heat exchanger. The heat exchanger consists of a series of disk pairs, each having in half both a first flow channel connected to the inlet header or bowl and a second flow channel connected to the outlet header or bowl. 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 opposing 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 311, 312 and only in the transition region between the disc channel and the -näpfen, the fluid inlet disc 311 is a flow connection between the flow channel 313 and the fluid inlet cup coined, wherein the fluid disc 312 is a connection between the flow channel 314 and the fluid outlet cup ,

These connection embossings can be carried out alternately in the disk tool and thus both disks are 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 such that a fluid, such as, for example, refrigerant or coolant, etc., is introduced via the first collector as an inlet collector, e.g. on the block top into which a first disc channel half 311 flows, then via a connecting element between the two opposite collectors, referred to as inlet collector and outlet collector on the block bottom, is transferred to the second disc channel half 312, flows through this and then from this second channel half via the second Collector, as exit collector then again referred to the block top, again flows out.

The advantage of this type of flow is in the homogenization of the temperature profile, for example as an evaporator, by equalizing the different temperatures of the countercurrent fluid flows due to the 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 may 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 simultaneously distributed via the inlet header to all first disc channel halves 311 arranged in parallel and, according to the deflection, distributed on all second disc channel halves 312 by means of connecting element.

In a multi-block interconnection, if the fluid is distributed only to a certain number of first disc channel halves 311 arranged in parallel at the same time, then the fluid transfer from one collector to the adjacent collector takes place directly in the discs, e.g. via impressed connection channels between the adjacent collecting cups of a disc, 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 as in the first block is continued.

The heat exchanger, in particular the disk evaporator, can alternatively also be designed in a single-tank design, that is to say with only one tank on one side of the heat exchanger

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 occur 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 removed by suitable measures, such as e.g. Multiple connections in the direction of air one behind the other, can be homogenized.

By integrating an internal heat transfer surface in the evaporator over substantially the entire height, local hot zones between evaporator inlet and outlet can be minimized.

Due to the heat transfer at the integrated inner heat transfer surface can be generated between the incoming refrigerant stable overheating in the countercurrent refrigerant 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 (11)

1. A method for producing more than two different heat exchangers (30, 70) which are produced by means of a kit for producing heat exchangers (30, 70) with at least two types of heat exchanger cores (1, 2, 31, 32), wherein the kit comprises:

   a first type of heat exchanger core (1, 31) with a plurality of pairs of plates (3) to create a plurality of parallel flow paths between the pairs of plates (3); and

   a second type of heat exchanger core (2, 32) with a plurality of groups of three plates (7) to create a plurality of two parallel flow paths, one respective flow path between two of the three plates,

   wherein the more than two different heat exchangers are selected from:

   a second heat exchanger (30) with two heat exchanger cores (1, 31) of the first type, wherein the two heat exchanger cores (1, 31) of the first type are arranged adjacent to each other in the air flow direction,

   a third heat exchanger with a heat exchanger core of the first type (1) and with a heat exchanger core (2) of the second type, wherein the heat exchanger core (1) of the first type and the heat exchanger core (2) of the second type are arranged adjacent to each other in the air flow direction,

   a fourth heat exchanger (70) with two heat exchanger cores (32) of the second type, wherein the two heat exchanger cores (32) of the second type are arranged adjacent to each other in the air flow direction,

   wherein further the following is optionally also provided:

   a first heat exchanger with a heat exchanger core of the first type (1, 31), and

   a fifth heat exchanger with a heat exchanger core of the second type (2, 32).
2. The method according to claim 1, characterised in that the heat exchanger cores (1, 31, 2, 32) of the first and/or second type are provided with connecting devices and/or interconnecting devices for introducing and/or discharging and/or transferring fluid into or between or out of the heat exchanger cores.
3. The method according to one of the preceding claims, wherein the first type of heat exchanger core (1) is a heat exchanger core in plate design for forming a heat exchanger, wherein the heat exchanger core is designed with a plurality of plate pairs (3) for forming first flow paths (13, 23), wherein two plates each of a plate pair form the first flow path between them and a respective region for second flow paths is formed between adjacent plate groups.
4. The method according to one of the preceding claims, wherein the second type of heat exchanger core (2) is a heat exchanger core in plate design for forming a heat exchanger, wherein the heat exchanger core is designed with a plurality of plate groups (7) for forming third and fourth flow paths, wherein the third flow path is formed between a respective first and second plate of a plate group and the fourth flow path is formed between a second plate and a third plate of the plate group, and a respective region for fifth flow paths is formed between adjacent plate groups.
5. The method according to claim 3 or 4, characterised in that at least individual plates have openings and/or cups (5, 6) as connecting and interconnecting regions and have channel-forming structures, such as embossings, for forming flow paths between connecting regions.
6. The method according to claim 3 or 5, characterised in that the first plate and the second plate of the plate pair (3) at two opposite end regions each have a connecting region as an inlet or outlet of the first flow path and a channel-forming structure between the two connecting regions for forming the first flow path.
7. The method according to claim 3 or 5, characterised in that the first plate and/or the second plate of the plate pair (3) at an end region have two connecting regions as an inlet or outlet of the first flow path and a respective channel-forming structure between the two connecting regions for forming the first flow path.
8. The method according to claim 4 or 5, characterised in that the first plate, the second and the third plate of the plate group (7) at two opposite end regions have two respective connecting regions as an inlet or outlet of the third flow path or of the fourth flow path, wherein the first and second plate between a respective opposite connecting region have a channel-forming structure between one of the two connecting regions for forming the third and fourth flow path, wherein the third plate is provided between the first and second plate as a partition wall between the third and fourth flow path.
9. The method according to one of the preceding claims, characterised in that the distance of the plate pairs (3) or the plate groups (7) of a heat exchanger core for forming the second and/or fifth flow paths is selected such that in the case of adjacent heat exchanger cores of a heat exchanger, it is the same or different, such as smaller or larger than in the adjacent heat exchanger core.
10. The method according to claim 9, characterised in that the depth of the flow channels perpendicular to the plane, defined by the plate pairs (3) or plate groups (7), is selected individually for each flow channel.
11. The method according to at least one of the preceding claims 9 or 10, characterised in that plate pairs (3) are formed from the paired arrangement of plates and with a partition wall between adjacent plates, which form pairs of flow channels, characterised in that flow through the flow channels of a plate pair is a counterflow.

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