Heat exchanger

Abstract

A heat exchanger (1), in particular a refrigerant evaporator, has a heat exchanger network (2) comprising fluid passages (3) and corrugated fins (4) and having a specified network height (NZ), network width (NX) and network depth (NY). A liquid or gaseous medium can flow through the fluid passages (3) in a vertical direction (z), which corresponds to the network height (NZ), and air can flow around the corrugated fins (4), which extend parallel to the fluid passages. The heat exchanger network also comprises a distributor unit (6), into which first ends (34) of the fluid passages (3) lead, and a collecting unit (7), into which second ends (35) of the fluid passages (3) lead. Two fluid passages (3) adjoining each other in a horizontal direction (x), which corresponds to the direction of the network width (NX), are connected together by at least one corrugated fin (4). The corrugated fins (4) have flanks (41) extending in the direction of the network width (NX) and in the direction of the network depth (NY), the respective flanks (41) of each corrugated fin (4) are oriented so as to ascend or descend from the air inlet side (22) to the air outlet side (23) entirely or at least predominantly in the direction of the network height (NZ), and two corrugated fins (4) are provided between pairs of adjacent fluid passages (3). The invention further relates to a method for producing a corrugated fin (3) and to a method for deforming a flat tube.

Description

[0001] heat exchanger

[0002] The present invention relates to a heat exchanger according to the preamble of claim 1.

[0003] The invention also relates to a method for producing a corrugated fin for such a heat exchanger.

[0004] Conventional plate-type heat exchangers ensure reliable heat transfer from a medium to be cooled, such as water or oil, within a cooler to the incoming cooling air through permanently soldered corrugated fins. The corrugated fins serve to increase the surface area for the incoming cooling air.

[0005] In the opposite case, if a refrigerant within the heat exchanger is to absorb heat by flowing air, as is the case with evaporators of air conditioning systems or air / water heat pumps, trouble-free operation is only possible above the dew point temperature of the ambient air.

[0006] As soon as condensation forms on the corrugated fins of such a plate heat exchanger, the water collects in the horizontal flanks of the corrugated fins, which leads to a significant loss of heat transfer efficiency.

[0007] In the event of icing, it is necessary to carry out a particularly time-consuming defrosting process on the heat exchanger in order to make the corrugated fins functional again.

[0008] To avoid such accumulation of condensate or icing, conventional heat exchangers must be installed horizontally or at a steep incline in the respective installation space. Since the heat exchanger is the largest component, particularly in the case of a heat pump, a significantly larger footprint is required for such a horizontal or inclined installation than for an upright installation. EP 2 196 758 B1 discloses a plate-type heat exchanger in which a pair of corrugated fins adjacent to a flat tube are aligned at an incline relative to one another, such that a corrugated fin adjacent to an air inlet side has a slope towards the air outlet side, and a corrugated fin adjacent to an air outlet side has a slope towards the air inlet side.A gap remains between the corrugated ribs, through which condensate drops flow along the corrugated ribs towards the gap, breaking the surface tension of the drops meeting at the gap and causing the condensate to flow downwards through the gap due to gravity.

[0009] However, this solution is only suitable to a limited extent for freezing condensate, as the ice components can clog the gap and thus prolong the defrosting process.

[0010] The object of the present invention is to further develop a heat exchanger in such a way that it enables, with good heat transfer properties, at the same time as improved condensate drainage and, in the event of icing, better outflow of the ice water thawed during the defrosting cycle.

[0011] Another object of the invention is to provide a simple method for producing a corrugated fin for such a heat exchanger.

[0012] The first object is achieved by a heat exchanger having the features of claim 1.

[0013] The second object is achieved by a method for producing a corrugated fin for such a heat exchanger having the features of claim 23 and by a method having the features of claim 24.

[0014] A heat exchanger according to the invention, in particular a refrigerant evaporator, has a heat exchanger network having fluid passages and corrugated fins with a predetermined network height, network width and network depth.

[0015] A liquid or gaseous medium can flow through the fluid passages in a vertical direction corresponding to the direction of the mesh height, and air can flow around the corrugated fins extending parallel to the fluid passages. The heat exchanger further comprises a distribution unit into which first ends of the fluid passages open, and a collection unit into which second ends of the fluid passages open.

[0016] Two adjacent fluid passages in a horizontal direction corresponding to the mesh width are connected by at least one corrugated rib. The corrugated ribs have flanks extending in the mesh width and depth directions.

[0017] The flanks of each of the corrugated fins are aligned from the air inlet side to the air outlet side completely or at least predominantly in the direction of the mesh height rising or falling.

[0018] Two corrugated fins are arranged between two adjacent fluid passages.

[0019] With a heat exchanger designed in this way, the inclination of the flanks of the corrugated fins relative to a horizontal plane makes it possible for condensation to drain away along the edges of the corrugated fins when it occurs.

[0020] Advantageous embodiments of the invention are the subject of the subclaims.

[0021] It is particularly preferred that one of the corrugated fins is inclined towards the air inlet side and the second corrugated fin is inclined towards the air outlet side.

[0022] This prevents the air from being deflected in the same direction across the entire heat exchanger network.

[0023] According to a preferred embodiment, an intermediate plate is arranged between the two corrugated fins between the two adjacent fluid passages. According to an advantageous further development, the intermediate plates protrude in the direction of the mesh depth relative to the outer edges of the corrugated fins.

[0024] At these projections, any condensate that forms can be drained downwards from the corrugated fins in a targeted manner and without the formation of obstructive drops. According to another advantageous design variant, the flanks of each of the corrugated fins extend horizontally in a first area near the air inlet side toward the depth of the mesh, and in an adjacent second area, they rise or fall toward the height of the mesh.

[0025] This allows for improved air flow into the air passages of the corrugated fins.

[0026] According to an advantageous embodiment, the flanks of the corrugated ribs are aligned parallel to the direction of the net width in a cross-sectional plane spanned by the direction of the net height and net width.

[0027] In an alternative design variant, the flanks of the corrugated ribs are aligned in a cross-sectional plane spanned by the direction of the net height and net width, inclined to the direction of the net width.

[0028] The inclination towards the width of the net also further promotes the drainage of any condensate that may occur.

[0029] According to a further design variant, the flanks are designed to slope downwards from the air inlet side to the air outlet side and are additionally aligned in a cross-sectional plane spanned by the direction of the mesh height and width at an angle of inclination to the direction of the mesh width.

[0030] Particularly preferably, the flanks of corrugated fins separated from one another by the intermediate plate are inclined towards the intermediate plate.

[0031] According to a further embodiment, the slope of the flanks of each of the corrugated ribs in a cross-sectional plane spanned by the direction of the mesh height and mesh depth increases or decreases continuously in the direction of the mesh depth from an air inlet side to an air outlet side.

[0032] Such an arched design of the corrugated fins also allows any condensation to drain away easily.

[0033] According to a further preferred embodiment, the gradient of the

[0034] Flanks of each of the corrugated fins in a cross-sectional plane spanned by the direction of the mesh height and mesh depth in the direction of the mesh depth from an air inlet side to an air outlet side in a first section adjacent to the air inlet side positive and in a second section adjacent to the air outlet side negative.

[0035] Due to the slope of the flanks in the direction of the air inlet side and the air outlet side, the drainage paths for draining condensate are shorter than if the flank slopes exclusively in the direction of the air inlet side or the air outlet side.

[0036] In addition, the installation of such corrugated fins reduces the area not covered by corrugated fins at the upper and lower ends of the fluid passages compared to the use of corrugated fins that rise or fall on only one side, the air inlet side or the air outlet side.

[0037] In order to enable the condensate to drain off quickly, the pitch angle of the flanks in the first section is, according to a preferred development, at least +10° and in the second section at least -10°.

[0038] According to a further preferred development, a transition section connecting the first section to the second section is provided between the first section and the second section of the flanks.

[0039] This allows the corrugated fins to be easily manufactured by punching and / or rolling.

[0040] In a first embodiment, the first section and the second section of the flanks are flat and the transition section is curved.

[0041] In a second design variant, the flanks are bell-shaped, with a high point of the bell curve with a gradient of zero located in the transition section.

[0042] Preferably, the corrugated ribs are shaped in a cross-sectional plane spanned by the direction of the mesh height and depth, mirror-symmetrically to a central axis extending in the direction of the mesh height along half the mesh depth. This also enables simple production of the corrugated ribs by punching and / or rolling.

[0043] The fluid passages are preferably designed as flat tubes with a plurality of fluid channels.

[0044] Preferably, the ends of the flat tubes are bent parallel to the direction of the network width, wherein the first ends of the flat tubes open one after the other in the direction of the network width into the distribution unit and the second ends of the flat tubes open one after the other in the direction of the network width into the collection unit.

[0045] According to a further advantageous embodiment, parallel flat regions of the flat tubes are connected to one another by bent connecting regions, wherein the connecting regions are continuously bent by 180° around an axis parallel to the network depth and are offset in the same tube region by a tube width viewed in the direction of the network depth plus a predetermined distance between then adjacent and parallel aligned straight regions of the flat tube.

[0046] The distribution unit preferably has a profile with a distribution channel extending in the direction of the network width, which is connected via a slot to a receiving space receiving the first ends of the fluid passages, and a base plate receiving the first ends of the fluid passages, which closes the receiving space towards the heat exchanger network.

[0047] The provision of such a distribution channel enables a particularly even distribution of the refrigerant.

[0048] According to an advantageous further development, respective ends of the fluid passages designed as flat tubes are pushed through openings in the respective base plate and soldered to it.

[0049] According to a preferred embodiment, the width of the slot of the distributor profile is less than or equal to one fifth of the diameter of the distributor channel.

[0050] The method according to the invention for producing a corrugated fin of a heat exchanger comprises the following method steps: a) embossing a symmetrically folded herringbone pattern into a sheet metal strip using a punching and / or folding tool in a continuous process, b) separating the sheet metal strip thus formed lengthwise into two separate identical diagonal fin strips using a cutting tool, and c) cutting the diagonal fin strips to the mesh height of the heat exchanger mesh to produce the corrugated fins.

[0051] In a method according to the invention for deforming a flat tube with a plurality of fluid channels for a heat exchanger as described above, the flat tube, which is flat prior to deformation, is continuously bent by 180° around an axis parallel to the mesh depth in a combined turning and bending process. In the same work step and tube region, the flat tube is offset by a tube width viewed in the direction of the mesh depth plus a predetermined distance between then adjacent and parallel aligned straight sections of the flat tube such that the adjacent parallel aligned straight section is positioned in a plane spanned by the unbent straight section.

[0052] This type of deformation enables a significant saving in pipe length and thus also a reduction in pipe sections protruding from the heat exchanger network.

[0053] Preferred embodiments are explained in more detail below with reference to the accompanying drawings. They show:

[0054] Fig. 1 is a schematic isometric view of an embodiment of a heat exchanger according to the invention,

[0055] Fig. 2 is an enlarged detail of the heat exchange network with a first variant of corrugated fins inclined towards the air outlet side,

[0056] Fig. 3 is a representation corresponding to Fig. 2 of a further embodiment variant with corrugated fins still aligned horizontally in the air inlet area,

[0057] Fig. 4 is a representation corresponding to Fig. 2 with corrugated ribs inclined towards the air outlet side, Fig. 5 is a variant corresponding to Fig. 2 with corrugated ribs inclined alternately upwards and downwards to the width of the net,

[0058] Fig. 6 is a view corresponding to Fig. 5 with partially cut-away corrugated fins, wherein one of the adjacent corrugated fins is inclined towards the air inlet side and the second corrugated fin is inclined towards the air outlet side,

[0059] Fig. 7 is a schematic isometric enlarged detail of a section of the heat exchanger network located near the collection unit, showing the projection of the separating plates to improve water drainage,

[0060] Fig. 8 is an isometric enlarged detail of a section of the heat exchanger network located near the collecting unit to show the deflection between straight pipe sections of the fluid passages designed as flat pipes,

[0061] Fig. 9 is an isometric enlarged detail of a section of the heat exchanger network located near the distribution unit with the first ends of the fluid passages pushed through a base plate of the distribution unit,

[0062] Fig. 10 is an enlarged detail of the lower area of ​​the heat exchanger near the distribution unit with the distribution unit attached,

[0063] Fig. 11 schematic representations for the production of an inclined lamella,

[0064] Fig. 12 an enlarged detail of the heat exchange network with another variant of corrugated fins inclined towards the air inlet and air outlet sides,

[0065] Fig. 13 is a plan view of the corrugated fins inclined towards the air inlet side and air outlet side according to Figure 12, Fig. 14 is an enlarged detail of the heat exchanger network with yet another variant of the corrugated fins inclined towards the air inlet side and air outlet side, and

[0066] Fig. 15 is a plan view of the corrugated fins inclined towards the air inlet and air outlet sides according to Figure 14.

[0067] In the following description of the figures, terms such as top, bottom, left, right, front, rear, etc., refer exclusively to the exemplary representation and position of the heat exchanger, fluid passage, corrugated fin, distribution unit, collection unit, flank, and the like chosen in the respective figures. These terms are not to be understood as limiting; i.e., these references may change due to different operating positions or the mirror-symmetrical design, etc.

[0068] In Figure 1, the reference number 1 denotes an embodiment variant of a heat exchanger according to the invention, in particular in the form of a refrigerant evaporator.

[0069] The heat exchanger 1 essentially consists of a heat exchanger network 2 with a predetermined network height Nz, network width Nx and network depth NY, with fluid passages 3 and corrugated fins 4, as well as a distribution unit 6 and a collection unit 7.

[0070] The fluid passages 3, which are preferably designed as flat tubes, in particular MPE flat tubes (MPE = Micro Multiport Extrusion Aluminum Tube), open with a first end 34, shown in Figures 9 and 10, into the distribution unit 6 and with second ends 35, shown in Figure 1, into the collection unit 7.

[0071] The fluid passages 3 are thereby flowed through by a liquid or gaseous (or a mixture of both phases) medium, in particular by a refrigerant, in a vertical direction Z corresponding to the direction of the network height Nz.

[0072] Air can flow around the corrugated fins 4, which extend parallel to the fluid passages 3. A preferred direction of air flow is shown as an arrow in Figure 1, where A denotes the direction of air flow. As further shown in Figures 1 to 10, 12 and 14, two adjacent fluid passages 3 in a horizontal direction x corresponding to the direction of the mesh width Nx are connected to one another by at least one corrugated fin 4. The corrugated fins 4 have flanks 41 extending in the direction of the mesh width Nx and in the direction of the mesh depth NY. These flanks 41 are connected to one another by backs 42. The corrugated fins 4 are preferably formed in one piece, preferably folded from a single piece of sheet metal.

[0073] The backs 42 can, as shown for example in Figures 1 to 9, be designed in the form of parallelogram or rectangular planes which rest on side surfaces of adjacent fluid passages 3 designed as flat tubes.

[0074] It is also conceivable for the backs 42 of the corrugated ribs 4 to be formed in an almost linear shape, for example in the case of a triangular formation of the folds of the corrugated ribs 4 viewed in the direction of the net height Nz and net width Nx.

[0075] As further shown in Figures 1 to 9, the flanks 41 of each of the corrugated fins 4 extend over the entire network depth NY of the heat exchange network 2, from an air inlet side 22 to an air outlet side 23.

[0076] Furthermore, the flanks 41 of each of the corrugated fins 4 are aligned from the air inlet side 22 to the air outlet side 23 completely or at least predominantly in the direction of the net height Nz rising or falling.

[0077] The rising or falling orientation of the flanks 41 makes it possible for any condensate that may occur during operation of the heat exchanger to not collect on the upper sides of the flanks 41, but to flow towards the air inlet side 22 or the air outlet side 23, depending on the inclination.

[0078] As shown in the embodiment of the heat exchanger 1 shown in Figure 1, as well as in the embodiments of the section of the heat exchanger network 2 shown in Figures 2 to 9, two such corrugated fins 4 are arranged between each two adjacent fluid passages 3. Furthermore, an intermediate plate 5 is arranged between each of the two corrugated fins 4 arranged between two such adjacent fluid passages 3.

[0079] These intermediate plates 5 are preferably designed to protrude in the direction of the mesh depth NY relative to the outer edges of the corrugated fins 4. Due to the somewhat larger width of the intermediate plates 5 (in the Y direction), condensate flowing from the flanks 41 of the corrugated fins 4 can be directed vertically downwards out of the corrugated fins 4 in a targeted manner and without hindering the formation of drops.

[0080] In order to ensure reliable drainage of condensate from the corrugated fins 4, different geometries of the corrugated fins 4 are conceivable.

[0081] Thus, in the embodiment shown in Figure 2, all of the corrugated fins 4 are shaped such that the flanks 41 form elongated rectangular surfaces, while the ridges 42 connecting them form elongated parallelogram surfaces. Accordingly, the flanks 41 are aligned so as to slope completely downwards in the direction of the network height Nz from the air inlet side 22 to the air outlet side 23. As a result, any condensate that forms will flow along the flanks 41 to the air outlet side 23 of the heat exchanger network 2. In the embodiment shown in Figure 3, the flanks 41 of each of the corrugated fins 4 are aligned horizontally in a first region 43 near the air inlet side 22 and only then, in a second region 44, are aligned so as to slope downwards towards the air outlet side 23.

[0082] In the embodiment shown in Figure 4, the corrugated fins 4 are designed such that the slope of the flanks 41 of each of the corrugated fins 4 increases continuously in a cross-sectional plane spanned by the direction of the mesh height Nz and mesh width Nx in the direction of the mesh depth NY from an air inlet side 22 to the air outlet side 23. The flanks 41 of the corrugated fins 4 are accordingly curved, in the embodiment shown, in the shape of a circular arc.

[0083] In the embodiment shown in Figure 5, the corrugated fins 4 are shaped such that the flanks 41 are formed sloping from the air inlet side 22 to the air outlet side 23 and are additionally aligned in a cross-sectional plane spanned by the direction of the mesh height Nz and mesh width Nx at an angle of inclination a to the direction of the mesh width Nx.

[0084] The angle of inclination a is preferably between 5° and 20°. In the embodiment shown in Figure 5, any condensate would thus also flow away from the fluid passages 3 toward the intermediate plates 5.

[0085] In the embodiment shown in Figure 6, a first of two corrugated fins 4 arranged between adjacent fluid passages 3 is designed as shown in Figure 2, in which the flanks 41 are oriented so as to fall in the direction of the air outlet side 23, while the second of the corrugated fins 4 has in principle the same folding, but the flanks 41 of the corrugated fins 4 are designed so as to rise from the air inlet side 22 to the air outlet side 23.

[0086] The design variant shown in Figure 6 has the further advantage that the resulting condensate flows approximately half towards the air inlet side 22 and half towards the air outlet side 23.

[0087] In all embodiments described with reference to Figures 2 to 6, it is of course also conceivable to align the inclination of the flanks 41 of the respective corrugated fins 4 in opposite directions, so that in the embodiments shown in Figures 2, 3, 4, and 5, any condensate would flow toward the air inlet side 22. Furthermore, the flanks can be provided with profiles known from heat exchanger fins, such as waves, dimples, kinks, or angles, to improve the heat transfer from the air to their surface.

[0088] In a further embodiment of corrugated fins 4 shown in Figures 12 and 13, the slope of the flanks 41 of each of the corrugated fins 4 in a cross-sectional plane spanned by the direction of the mesh height Nz and mesh depth NY in the direction of the mesh depth NY from the air inlet side 22 to the air outlet side 23 is positive in a first section 45 adjacent to the air inlet side 22 and negative in a second section 46 adjacent to the air outlet side 23. This allows any condensate to drain away not only to one side, the air inlet side 22 or the air outlet side 23, but to both sides, the air inlet side 22 and the air outlet side 23. As further shown in the plan view according to Figure 13, a pitch angle ß of the flanks 41 in the first section 45 is at least +10° and in the second section 46 is at least -10° relative to the direction of the net depth NY.

[0089] Preferably, a transition section 47 is provided between the first section 45 and the second section 46 of the flanks 41, connecting the first section 45 to the second section 46, which creates a preferably continuous transition between the rising first section 45 and the falling second section 46.

[0090] The length of this transition section 47, viewed in the direction of air flow, is significantly smaller than the length of the first section 45 and the second section 46.

[0091] 12 and 13, the first section 45 and the second section 46 of the flanks 41 are flat, i.e. with a constant gradient, and the transition section 47 is curved, in a further embodiment of the corrugated fins 4 shown in Figures 14 and 15, the flanks 41 are bell-curve-shaped. A high point U of the bell curve with a gradient of zero is located in the transition section 47. Bell curve means an initially slight positive gradient of the first section 45 near the air inlet side 22, followed by an increasing gradient up to the transition section 47, in which the gradient continuously decreases and changes into a negative gradient, i.e. a decline.From there, in the second section adjoining the transition area 47, there follows an initially steep gradient which becomes flatter towards the air outlet side 2 until it preferably has the same gradient as the first section 45 near the air inlet side 22.

[0092] It is also conceivable that the initial gradient of the first section 45 near the air inlet side 22 differs in magnitude from the gradient of the second section 46 near the air outlet side 22. This also applies to the embodiment according to Figures 12 and 13.

[0093] In order to be able to form the corrugated ribs 4 of the two embodiments shown in Figures 132 to 15 in a simple manner, the corrugated ribs 4 are preferably formed in a cross-sectional plane spanned by the direction of the mesh height Nz and mesh depth NY mirror-symmetrically to an axis of symmetry B extending in the direction of the mesh height Nz along half the mesh depth NY.

[0094] Even in the embodiments described with reference to Figures 12 to 15, it is conceivable to provide the flanks with profiles known from heat exchanger fins, such as waves, dimples, kinks or angles, in order to improve the heat transfer from the air to their surface.

[0095] In Figure 7, the projection of the intermediate sheets 5 by a distance s relative to the corrugated fins 4 can be clearly seen.

[0096] Furthermore, Figures 7 and 8 show that the fluid passages 3, which are designed as flat tubes with a plurality of fluid channels 31 (shown in Figure 9), do not correspond to the mesh depth NY in their width viewed in the Y direction, but are significantly narrower and are formed in a meandering manner several times in a plane between two corrugated fins 4 via deflections 33.

[0097] In this case, the initially straight MPE pipe is continuously bent by 180° around an axis in the Y direction by a combined turning and bending process and is offset in the same work step and pipe area and by the pipe width plus the desired distance between the straight areas 32, so that the overhang of the deflection area 33 over the network 2 in the Z direction between the parallel fluid channels 32 is minimized.

[0098] As further illustrated in Figure 9, the first ends 34 of the fluid passages 3, which are designed as flat tubes, are bent parallel to the direction of the network width Nx. The first ends 34 of the fluid passages 3 are preferably bent one behind the other in the direction of the network width Nx, opening into the distribution unit 6.

[0099] The same preferably also applies to the second ends 35 of the fluid passages 3, which accordingly open into the collecting unit 7.

[0100] The distribution unit 6 and the collection unit 7 are aligned parallel to the direction of the network width Nx. A preferred embodiment of a distribution unit 6 is shown in Figure 10. The distribution unit 6 preferably has a profile 61 with a distribution channel 63 extending in the direction of the network width Nx. This distribution channel 63 is connected via a slot 65 to a receiving space 66 accommodating the first ends 34 of the fluid passages 3. A base plate 64 accommodating the first ends 34 of the fluid passages 3 closes the receiving space 66 towards the heat exchanger network 2.

[0101] To accommodate the first ends 34 of the fluid passages 3, openings 641 corresponding to the cross section of the fluid passages 3 designed as flat tubes are provided in the base plate 64, which openings are inserted into the ends 34 of the fluid passages 3.

[0102] As can be seen in Figure 10, for the pre-fixing of the floor plate

[0103] 64 on profile 61 locking lugs 67 are provided.

[0104] The profile 61 of the distribution unit 6 is preferably extruded in a V-shaped spread. The ends of the profile 61 are then pressed together until the desired width of the slot 65 is achieved. The width bs of the slot

[0105] 65 of the distributor profile 6 is preferably less than or equal to one fifth of the diameter dK of the distributor channel 63.

[0106] The collection unit 7 can be designed identically to the distribution unit 6.

[0107] In the embodiment shown here in Figure 1, the collecting unit 7 is designed as a U-shaped profile 71, the free longitudinal side of which is closed by a base plate 74 into which the second ends 35 of the fluid passages 3 designed as flat tubes protrude.

[0108] The distribution unit 6 further has an inlet 62 for the fluid, in particular a refrigerant. Accordingly, the collection unit 7 has an outlet 72 for the fluid.

[0109] In Figure 1, the front sides of the collection or distribution unit are shown open; of course, these are closed by covers.

[0110] The fluid passages 3 are preferably soldered to the corrugated fins 4 and the intermediate plates 5 to form the mesh 2. The end pieces 34, 35 are also soldered to the base plates 64, 74 and the profiles 61, 71, preferably in the same process step as the soldering of the mesh 2. For this purpose, the fluid passages, the intermediate plates, and the base plates are preferably coated with solder (solder and / or flux).

[0111] Figure 11 shows partial steps of a method for producing a corrugated fin 4 of a heat exchanger 1.

[0112] In this process, a symmetrically folded herringbone pattern is first embossed into a sheet metal strip 8 using a punching and / or folding tool in a continuous process. After the herringbone pattern is embossed, the thus formed sheet metal strip 8 is split lengthwise with a cutting tool into two separate, identical diagonal lamella strips 10.

[0113] These diagonal fin strips 10 can then be cut to the mesh height Nz of the heat exchanger mesh 2 to produce the corrugated fins 4.

[0114]

[0115] 1 heat exchanger

[0116] 2 heat exchanger network

[0117] 21 Side wall

[0118] 22 Air inlet side

[0119] 23 Air outlet side

[0120] 3 Fluid passage

[0121] 31 Fluid channel

[0122] 32 straight area

[0123] 33 connecting piece

[0124] 34 first end piece

[0125] 35 second end piece

[0126] 4 corrugated ribs

[0127] 41 flank

[0128] 42 back

[0129] 43 first area

[0130] 44 second area

[0131] 45 first section

[0132] 46 second section

[0133] 47 Transition section

[0134] 5 intermediate plate

[0135] 6 Distribution unit

[0136] 61 Profile

[0137] 62 Entrance

[0138] 63 Distribution channel

[0139] 64 floor panel

[0140] 641 Opening

[0141] 65 slot

[0142] 66 Recording Room

[0143] 67 locking lug

[0144] 7 collection unit

[0145] 71 Profile 72 Outlet

[0146] 73 Collecting channel

[0147] 74 floor panel

[0148] 8 sheet metal strip

[0149] 9 Cutting line

[0150] 10 diagonal slat band

[0151] A Air flow direction s Overhang

[0152] B axis of symmetry

[0153] U high point

[0154] Nx network width

[0155] NY Net Depth

[0156] Nz Net height

[0157] X direction

[0158] Y direction

[0159] Z Direction a Inclination angle dK Diameter of distribution channel bs Width of the slot

Claims

Claims 1. Heat exchanger (1 ), in particular refrigerant evaporator, comprising - a heat exchanger network (2) having fluid passages (3) and corrugated fins (4) with a predetermined network height (Nz), network width (Nx) and network depth (NY), - wherein the fluid passages (3) can be flowed through by a liquid or gaseous medium in a vertical direction (z) corresponding to the direction of the net height (Nz) and the corrugated ribs (4) extending parallel to the fluid passages (3) can be flowed around by air, - a distribution unit (6) into which first ends (34) of the fluid passages (3) open, - a collecting unit (7) into which second ends (35) of the fluid passages (3) open, - wherein two adjacent fluid passages (3) in a horizontal direction (x) corresponding to the direction of the mesh width (Nx) are connected to one another by at least one corrugated rib (4), - wherein the corrugated ribs (4) have flanks (41) extending in the direction of the net width (Nx) and in the direction of the net depth (NY), characterized in that - the flanks (41) of each of the corrugated fins (4) are aligned from the air inlet side (22) to the air outlet side (23) in a completely or at least predominantly ascending or descending manner in the direction of the net height (Nz), - wherein two corrugated fins (4) are arranged between two adjacent fluid passages (3).

2. Heat exchanger (1) according to claim 1, characterized in that a first of the corrugated fins (4) arranged between two adjacent fluid passages (3) is inclined in the direction of the air inlet side (22) and the second corrugated fin (4) is inclined in the direction of the air outlet side (23).

3. Heat exchanger (1) according to claim 1 or 2, characterized in that an intermediate plate (5) is arranged between the two corrugated fins (4) between the two adjacent fluid passages (3).

4. Heat exchanger (1) according to claim 3, characterized in that the intermediate plates (5) protrude in the direction of the mesh depth (NY) relative to outer edges of the corrugated fins (4).

5. Heat exchanger (1) according to one of the preceding claims, characterized in that the flanks (41) of a respective one of the corrugated fins (4) extend horizontally in the direction of the mesh depth (NY) in a first region (43) near the air inlet side (22) and are aligned so as to rise or fall in the direction of the mesh height (Nz) in an adjoining second region (44).

6. Heat exchanger (1) according to one of the preceding claims, characterized in that the flanks (41) of the corrugated fins (4) are aligned parallel to the direction of the mesh width (Nx) in a cross-sectional plane spanned by the direction of the mesh height (Nz) and mesh width (Nx).

7. Heat exchanger (1) according to one of claims 1 to 5, characterized in that the flanks (41) of the corrugated fins (4) are aligned inclined to the direction of the mesh width (Nx) in a cross-sectional plane spanned by the direction of the mesh height (Nz) and mesh width (Nx).

8. Heat exchanger (1) according to one of the preceding claims, characterized in that the flanks (41) are designed to slope downwards from the air inlet side (22) to the air outlet side (23) and are additionally aligned in a cross-sectional plane spanned by the direction of the mesh height (Nz) and mesh width (Nx) at an angle of inclination (α) to the direction of the mesh width (Nx).

9. Heat exchanger (1) according to claim 8, characterized in that the flanks (41) of corrugated fins (4) separated from one another by the intermediate plate (5) are inclined towards the intermediate plate (5).

10. Heat exchanger (1) according to one of claims 1 to 7, characterized in that the slope of the flanks (41) of a respective one of the corrugated fins (4) is in a direction defined by the direction of the mesh height (Nz) and mesh depth (NY). spanned cross-sectional plane in the direction of the mesh depth (NY) from an air inlet side (22) to an air outlet side (23) continuously increases or continuously decreases.

11. Heat exchanger (1) according to one of claims 1 to 7, characterized in that the slope of the flanks (41) of a respective one of the corrugated fins (4) in a cross-sectional plane spanned by the direction of the mesh height (Nz) and mesh depth (NY) in the direction of the mesh depth (NY) from an air inlet side (22) to an air outlet side (23) is positive in a first section (45) adjacent to the air inlet side (22) and negative in a second section (46) adjacent to the air outlet side (23).

12. Heat exchanger (1) according to claim 11, characterized in that a pitch angle (ß) of the flanks (41) in the first section (45) is at least +10° and in the second section (46) is at least -10° relative to the direction of the mesh depth (NY).

13. Heat exchanger (1) according to claim 11 or 12, characterized in that a transition section (47) connecting the first section (45) to the second section (46) is provided between the first section (45) and the second section (46) of the flanks (41).

14. Heat exchanger (1) according to claim 13, characterized in that the first section (45) and the second section (46) of the flanks (41) are flat and the transition section (47) is arcuate.

15. Heat exchanger (1) according to claim 13, characterized in that the flanks (41) are shaped like a bell curve, wherein a high point (U) of the bell curve with a gradient of zero is located in the transition section (47).

16. Heat exchanger (1) according to one of claims 11 to 15, characterized in that the corrugated fins (4) are formed in a cross-sectional plane spanned by the direction of the mesh height (Nz) and mesh depth (NY) mirror-symmetrically to an axis of symmetry (B) extending in the direction of the mesh height (Nz) along half the mesh depth (NY).

17. Heat exchanger (1) according to one of the preceding claims, characterized in that the fluid passages (3) are designed as flat tubes with a plurality of fluid channels (31).

18. Heat exchanger (1) according to claim 17, characterized in that the ends of the flat tubes are bent parallel to the direction of the network width (Nx), the first ends (34) of the flat tubes opening one behind the other in the direction of the network width (Nx) into the distribution unit (6) and the second ends (35) of the flat tubes opening one behind the other in the direction of the network width (Nx) into the collection unit (7).

19. Heat exchanger (1) according to claim 17 or 18, characterized in that parallel flat regions (32) of the flat tubes are connected to one another by bent connecting regions, wherein the connecting regions (33) are continuously bent by 180° about an axis parallel to the network depth (NY) and are offset in the same tube region by a tube width viewed in the direction of the network depth (NY) plus a predetermined distance between then adjacent and parallel aligned straight regions (32) of the flat tube.

20. Heat exchanger (1) according to one of the preceding claims, characterized in that the distributor unit (6) has a profile (61) with a distribution channel (63) extending in the direction of the network width (Nx), which is connected via a slot (65) to a receiving space (66) receiving the first ends (34) of the fluid passages (3), and a base plate (64) receiving the first ends (34) of the fluid passages (3) and closing the receiving space (66) towards the heat exchanger network (2).

21. Heat exchanger (1) according to claim 20, characterized in that respective ends (34, 35) of the fluid passages (3) designed as flat tubes are pushed through openings of the respective base plate (64, 74) and soldered thereto.

22. Heat exchanger (1) according to claim 20, characterized in that the width (bs) of the slot (65) of the distributor profile (6) is less than or equal to one fifth of the diameter (dK) of the distributor channel (63).

23. Method for producing a corrugated fin (3) of a heat exchanger (1) according to one of the preceding claims, with the method steps: a) embossing a symmetrically folded herringbone pattern into a sheet metal strip (8) using a punching and / or folding tool in a continuous process, b) separating the sheet metal strip (8) thus formed lengthwise with a cutting tool into two separate identical diagonal fin strips (10), c) cutting the diagonal fin strips (10) to the mesh height (Nz) of the heat exchanger mesh (2) to produce the corrugated fins (4).

24. Method for deforming a flat tube with a plurality of fluid channels (31) for a heat exchanger (1) according to one of the preceding claims 1 to 22, in which the flat flat tube (4) is bent continuously by 180° about an axis parallel to the mesh depth (NY) in a combined turning and bending process and is offset in the same work step and tube region by a tube width viewed in the direction of the mesh depth (NY) plus a predetermined distance between then adjacent and parallel aligned straight regions (32) of the flat tube in such a way that the adjacent parallel aligned straight region (32) is positioned in a plane spanned by the non-bent straight region (32).

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