Plate heat exchanger

Abstract

Plate heat exchanger (100) made of aluminium, comprising at least two nested cooling fin plates (KRP1; KPR2) having a predefinable material thickness (S2) and designed as flow trays, which are accessible via separate inlet and outlet channels (K1ZU, K1AB; K2ZU, K2AB), wherein the inlet and outlet channels (K1ZU, K1AB; K2ZU, K2AB) are defined by through-openings (1Z, 1A; 2Z, 2A) in the cooling fin plates (KRP1; KPR2) provided with domes (11, 21), characterized in that the cooling fin plates (KRP1; KPR2) have a predefinable material thickness (S1) and a predefinable spacing (T) as well as a height (H). TBTurbulence plates (TB1, TB2) are embedded in the inlet and outlet channels (K1ZU, K1AB; K2ZU, K2AB) through which two heat-exchanging media (1, 2) flow, wherein sinusoidal or trapezoidal turbulence plates (TB1, TB2) have several amplitudes (H+, H-), wherein a division (T) is provided in which a defined periodically recurring distance is defined between two positive amplitudes (H+) and two negative amplitudes (H-), wherein the turbulence plates (TB1, TB2) are arranged in several longitudinal rows offset from one another in an x / y plane as intermediate sections (ZA), wherein a shell plate (101) and a mounting plate (102), between which the cooling fin plates (KRP1, KRP2) are arranged, lie in successive x / y planes,wherein a material-reinforced shell plate (101) with a material thickness (S3) is arranged at one end and a cooling fin plate (KRP2B) with a specified material thickness (S2) is arranged adjacent to the shell plate (101) and through which a second medium (2) flows, the embedded turbulence plate (TB2) of which is flowed by the second medium (2) at a low pressure (p2), the domes (21) of which terminate at the shell plate (101), whereby the first medium (1) at a high pressure (p1) is in contact with the shell plate (101), and depending on a respective predefinable cross-sectional area (A1) of the respective through-openings (1Z, 1A) exerts high pressure forces (F) on the shell plate (101), wherein the plate heat exchanger (100) is assigned a standardized material index (I) for material-reduced manufacturing, which is derived from the mathematical product of the following characteristic values, the material thickness (S1) and the spacing (T) of the turbulence plates (TB1, TB2),the material thickness (S2) of the cooling fin plates (KRP1, KRP2), the material thickness (S3) of the casing plate (101) and the cross-sectional areas (A1) of the through-openings (1Z, 1A) of the domes (21) formed by the cooling fin plate (KRP2B) adjacent to the casing plate (101), wherein each characteristic value is variably selected from a defined range of values ​​with the proviso that the standardized material index (I) formed from the product of the selected characteristic values ​​is < 113 mm, 6 amounts.

Description

[0001] The invention relates to a plate heat exchanger.

[0002] The publication EP 0 623 798 A2 describes an oil / coolant cooler with stacked, trough-shaped heat exchanger plates. By using special designs in which turbulence-generating protrusions or sealing features are incorporated into the heat exchanger plates, the number of internal components, such as turbulence inserts or sealing discs, is reduced.

[0003] The publication DE 10 2004 036 951 A1 also describes an oil cooler and a method for its manufacture. Improved heat transfer between the media is achieved through the better distribution of the flowing media across the plate width of the oil cooler, which is designed as a plate heat exchanger.

[0004] The publication DE 10 2010 001 828 A1 discloses the construction of a stacked disc oil cooler which has a reduced height while saving material and maintaining or increasing strength.

[0005] Documents DE 10 2007 011 762 A1, DE 10 2006 018 532 A1, DE 31 39 154 A1 and DE 10 2009 030 095 A1 also describe plate heat exchangers of the same type.

[0006] The object of the invention is to create a durable plate heat exchanger that has a lower weight.

[0007] The invention starts with a plate heat exchanger made of aluminum.

[0008] The plate heat exchanger is characterized by the features of claim 1.

[0009] The parameters of the plate heat exchanger are given in mm, or the cross-sectional area A1 is given in mm. 2specified, so that for the standardized material index < 113 one unit in mm 6 results.

[0010] This design of the plate heat exchanger according to claim 1 advantageously results in the effect that the plate heat exchanger can withstand the desired pressure stresses and is simultaneously material-reduced, whereby the characteristic values ​​can be varied together.

[0011] Preferably, the selected characteristic value of the spacing of the turbulence plates lies within a defined range of values, which has the limits of 4.5 mm (maximum value) and 3.0 mm (minimum value).

[0012] Preferably, the selected characteristic value of the material thickness of the turbulence plates lies within a defined range of values, which has the limits of 0.25 mm (maximum value) and 0.1 mm (minimum value).

[0013] Furthermore, the characteristic value of the material thickness of the cooling fin plates is preferably selected from a range of values ​​which has the limits 0.5 mm (maximum value) and 0.3 mm (minimum value).

[0014] A preferred value range for the material thickness of the casing plate is between a (maximum value) of 1.6 mm and a (minimum value) of 1.2 mm.

[0015] Preferably, the respective characteristic value of the cross-sectional area of ​​the penetration openings of the domes of the cooling fin plate adjacent to the casing plate is selected from a range of values ​​whose limits are between 165.2 mm 2 (Maximum value) and 38.5 mm 2 (Minimum value) are formed.

[0016] In a preferred embodiment of the invention, the openings through the cooling fin plate adjacent to the casing plate and thus through the domes formed on the openings are circular, so that the characteristic value of the cross-sectional area is obtained by selecting a diameter d from the range of values ​​between a maximum diameter (maximum value) of 14.5 mm and a minimum diameter (minimum value) of 7.0 mm.

[0017] The invention enables the user to create a plate heat exchanger with a standardized material index < 113 mm² that meets the material-reduced standard by changing the characteristic values ​​in the claimed value ranges. 6 to interpret.

[0018] For example, if all the mentioned maximum values ​​of the value ranges are multiplied together, a material index of 148.6 mm is obtained. 6It follows that at least one of the key figures must be adjusted accordingly in order to meet the requirement.

[0019] The provision of claim 1 enables the user to adjust one or more characteristic values ​​within the specified ranges accordingly, resulting in a material-reduced plate heat exchanger which, within the specified ranges, withstands the pressure stresses described below during type approval, regardless of the adjustment chosen by the user, and is therefore superior to plate heat exchangers known from the prior art.

[0020] Multiplying all the mentioned minimum values ​​of the value ranges together results in a material index of 4.1 mm. 6 .

[0021] It follows that all plate heat exchangers with an integer standardized material index that is < 113 mm 6 is between ≤ 112 mm 6and ≥ 4 mm 6 correspond to the standard according to the invention.

[0022] The investigations have shown that, in particular, a reduction in the cross-sectional area of ​​the dome openings, or in other words, the channel cross-sections, especially the channel cross-section of the high-pressure medium, has a particularly large effect on maintaining the integer material index between ≤ 112 mm. ® and ≥ 4 mm 6 performs as described in detail in the exemplary embodiment.

[0023] Reducing the channel cross-section has the positive effect of allowing the material thicknesses of the turbulence plates, cooling fin plates, and casing plate to be reduced, resulting in a material index of < 113 mm. 6This can be easily achieved. The investigations have shown that, surprisingly, reducing the channel cross-section is the most influential parameter for designing a material-reduced, yet durable, plate heat exchanger. The equivalent stresses determined in the turbulence plates before and after reducing the high-pressure-side channel cross-section have demonstrated this influence. Therefore, it is specifically proposed to select the maximum diameter of 14.5 mm as the maximum value for the high-pressure-side channel cross-section. Currently, no plate heat exchangers of this type are known that have such a small high-pressure-side channel cross-section. Even by selecting a cooling fin plate with a thickness of < 0.4 mm, the relevant material index, according to the product formula, is < 113 mm. 6 reached.

[0024] Furthermore, according to the invention, in a preferred embodiment, the number of cooling fin plates that can be installed is changed by varying the height of the turbulence plates, thereby simultaneously optimizing the performance of the material-reduced plate heat exchanger, as is explained in detail in the following description.

[0025] The invention is explained below in exemplary embodiments with reference to the accompanying drawings.

[0026] They show: Fig. 1. A plate heat exchanger in a perspective view in its assembled state; Fig. 2. The plate heat exchanger in a perspective view in an exploded view; Fig. 3-1 a cooling fin plate of a first type; Fig. 3-2 a cooling fin plate of a second type; Fig. 4 the plate heat exchanger in a sectional view; Fig.5 a detailed section of a cross-section through a turbulence plate; Fig. 6 a perspective view of part of the turbulence plate; Fig. 7 a detailed section (Detail B) through a cooling fin plate.

[0027] For the purposes of this description, one direction of a plate heat exchanger 100 will be denoted by "x". "y" denotes the direction orthogonal to the x-direction in the same plane, and "z" denotes the direction vertically orthogonal to the x / y-plane spanned between x and y.

[0028] The Fig. Figure 1 shows the plate heat exchanger 100 in its assembled state.

[0029] The plate heat exchanger 100 is designed as a plate block B, that is, in the assembled state, the individual heat exchanger plates are connected to each other in a known manner to form a block, preferably soldered.

[0030] The heat exchanger plates are subsequently referred to as cooling fin plates.

[0031] The plate block B defined here includes a reinforced cooling fin plate KRP2V and the cooling fin plates KRP1 and KRP2, as well as a casing plate 101 or, in some versions, the casing plate 101 with an insert 103. Turbulence plates TB1 and TB2 are arranged between the cooling fin plates KRP1, KRP2, and KRP2V.

[0032] The height of the plate block B with the aforementioned components is indicated in the figures by the reference symbol H. B marked.

[0033] The plate heat exchanger 100 also includes a mounting plate 102, which is usually individually designed according to the intended structural mounting of the plate heat exchanger 100 and has a predefinable material thickness S5, which will be explained in more detail later.

[0034] The casing plate 101 and the reinforced cooling fin plate KRP2V form the end plates of the plate block B defined here, between which the cooling fin plates KRP1, KRP2 and turbulence plates TB1, TB2 are arranged.

[0035] All components of the plate heat exchanger 100 mentioned above are made of aluminum to reduce weight. The following explanations apply to a plate heat exchanger 100 made of aluminum.

[0036] The Fig. Figure 2 shows the plate heat exchanger 100 at least partially in an exploded view.

[0037] The Fig. Figure 3-1 shows one of the multiple arranged cooling fin plates of a first type KRP1.

[0038] The Fig.Figure 3-2 shows one of the multiple cooling fin plates of a second type, KRP2. One such cooling fin plate, KRP2 of the second type, is arranged as an adjacent cooling fin plate, KRP2B, on the casing plate 101 and is designated KRP2B with reference to its arrangement. Another such cooling fin plate, KRP2 of the second type, is also arranged as an end plate of the defined plate block B and is designated KRP2V with reference to its arrangement. This cooling fin plate, KRP2V, has a reinforced material thickness, S4, since, as an end plate, it is not covered by another cooling fin plate. The material thickness, S4, of the reinforced cooling fin plate, KRP2V, will be discussed further below.

[0039] The Fig. Figure 4 shows the plate heat exchanger 100 in a sectional view along the section line AA according to Fig. 2.

[0040] For the following description regarding the exemplary design of the plate heat exchanger 100, it is recommended to use the following: Fig. To consider points 1 to 4 together.

[0041] The plate heat exchanger 100, selected as an example to illustrate the invention, is bounded on its upper side, as shown in the illustration, by the so-called shell plate 101 and on its lower side, as shown in the illustration, by the mounting plate 102.

[0042] Between the casing plate 101 and the mounting plate 102, viewed from top to bottom, the cooling fin plate KRP2B adjacent to the casing plate 101 and subsequently the cooling fin plates KRP1, KRP2 are arranged alternately, wherein the lowest cooling fin plate of the plate block B is the reinforced cooling fin plate KRP2V.

[0043] The casing plate 101 has an insert 103 in some conventional plate heat exchangers 100; see section AA in the Fig.4, which serves to increase the stiffness of the shell plate 101. The shell plate 101 has an edge web 101-1. The maximum pressure acting on the shell plate 101 forms the design criterion for a material thickness S3 of the shell plate 101, or for the material thickness S3 of the shell plate 101 and the insert 103. The insert 103 is necessary in conventional plate heat exchangers 100 when the design-related required material thickness S3 of the shell plate 101 exceeds a material thickness S3 at which edge forming with the necessary radii of the edge web 101-1 of the shell plate 101 is no longer possible. It is already clear from this that the casing plate 101, or the casing plate 101 and the insert 103, due to the high pressure acting on the casing plate 101, together contribute a significant part to the overall weight of the plate heat exchanger 100 in a detrimental way.The material thickness S3 of the casing plate 101 or of the casing plate 101 and the insert 103 together is in . Fig. 4 applied for.

[0044] In the plate heat exchanger 100, a first fluid heat exchange medium 1 and a second fluid heat exchange medium 2 flow separately from each other.

[0045] In a plate heat exchanger 100 used as an oil cooler for a motor vehicle, the first medium 1 is oil, in particular engine oil or transmission oil, while the second medium 2 is a coolant, in particular a water-glycol mixture with a predefinable mixing ratio. The first medium 1 is the heat-releasing medium, while the second medium 2 absorbs the heat. In the plate heat exchanger 100, the first medium 1 is under a high pressure p1 and the second medium 2 is under a lower pressure p2.

[0046] In a plate heat exchanger 100 of a refrigeration unit, particularly an air conditioning system in a vehicle, the first medium 1 is a refrigerant, while the second medium 2 is also a coolant or air. Pure water or a water-glycol mixture is typically used as the coolant. For example, the refrigerant with the trade name R134a / 1234 and the chemical name 2,3,3,3-tetrafluoropropene is used. In this second case, the second medium 2 is the heat-releasing medium, while the first medium 1 absorbs the heat. In such a plate heat exchanger 100, the first medium 1 is also under a high pressure p1, and the second medium 2 is under a lower pressure p2.

[0047] For the pressure-side design, the components of the plate heat exchangers 100 that are under high pressure p1 must always be taken into account; that is, the components carrying the first medium 1 are particularly relevant for the pressure design and the choice of material thicknesses.

[0048] The inlet openings 1ZU, 2ZU and outlet openings 1AB, 2AB of the fluid heat exchanger media 1, 2 of the plate heat exchanger 100 in the mounting plate 102 are arranged as follows in the exemplary embodiment.

[0049] The inlet opening 1ZU and the outlet opening 1AB of the first medium 1 into the plate block B of the plate heat exchanger 100 and the inlet opening 2ZU and the outlet opening 2AB of the second medium 2 from the plate block B of the plate heat exchanger 100 are arranged diagonally in the exemplary embodiment, whereby the mounting plate 102 also has this diagonal arrangement.

[0050] The plate block B of the plate heat exchanger 100 is made up of several interlocking cooling fin plates KRP of the first and second type 1, 2, each forming a raised, circumferential edge web 12, 22.

[0051] These cooling fin plates KRP1, KRP2 have paired through-openings 1Z, 1A and 2Z, 2A for the heat-exchanging media 1 and 2.

[0052] The circumferential rib 12, 22 formed by each of the cooling fin plates KRP1 and KRP2 (KRP2B, KRP2V) creates a kind of flow trough. The respective rib 12, 22 is designed to overlap the rib 12, 22 of the adjacent cooling fin plate KRP1, KRP2. As mentioned, the outer plate 101, as the end plate, also forms a corresponding rib 101-1.

[0053] The in the Fig.The cooling fin plate KRP1 of the first type for the first medium 1, shown in the exploded view 2 and 3-1, is arranged in a first diagonal with respect to the inlet opening 1Z and the outlet opening 1A analogously to the inlet opening 1ZU and the outlet opening 1AB. The diagonal refers to the domes 11 arranged diagonally to each other, which, in the assembled state, prevent the entry of the second medium 2 into the first cooling fin plate KRP1, so that the so-called layers of the first medium 1 (the so-called oil middle layers) are formed in the cooling fin plate KRP1, which is designed as a flow tray.

[0054] The in the Fig.The cooling fin plates KRP2 and KRP2B of the second type shown in Figures 2 and 3-2 for the second medium 2 are arranged in a second diagonal with respect to the inlet 2Z and outlet 2A. The diagonal refers to the diagonally arranged domes 21, which prevent the inlet of the first medium 1 into the cooling fin plates KRP2 (KRP2B, KRP2V), so that the layers of the second medium 2 (the so-called coolant layers) are formed in the cooling fin plates KRP2, which are designed as a flow tray.

[0055] The diagonals in the corresponding layers (oil middle layer and coolant layer) intersect, so that in the exemplary embodiment it is a plate heat exchanger 100 through which the heat exchanger media 1, 2 lie in the different planes and flow diagonally.

[0056] The invention also applies to plate heat exchangers 100 with parallel or opposite flow of the heat exchanger media 1, 2; in this respect, the illustrated plate heat exchanger 100 represents only an embodiment, which is expressly pointed out.

[0057] The arrangement of the cooling fin plates KRP1 and KRP2 (KRP2B, KRP2V) is such that the through-openings 1Z, 1A and 2Z, 2A are located in the area of ​​the deep-drawn domes 11 of the cooling fin plate KRP1 of the first type or in the area of ​​the deep-drawn domes 21 of the second cooling fin plates KRP2 (KRP2B, KRP2V) of the second type, whose dome height corresponds to the distance between the adjacent cooling fin plates KRP1, KRP2 (KRP2B, KRP2V) of the two types.

[0058] Since the through-openings 1Z, 1A and 2Z, 2A are smaller than the base of the domes 11, 21 of the cooling fin plates KRP1 and KRP2 (KRP2B, KRP2V), respectively, a planar structure supporting the tight connection of the domes 11, 21 is formed between the bases of the projecting domes 11, 21 of adjacent cooling fin plates KRP1, KRP2 around the respective opening edge of the through-openings 1Z, 1A and 2Z, 2A.

[0059] In the exemplary embodiment, the domes 11, 21 are provided diagonally offset in the area of ​​the aligned passage openings 1Z, 1A and 2Z, 2A, always on the same sides of the standardized cooling fin plates KRP1, KRP2, so that fluid-tight passages for each of the two media 1, 2 are created via the domes 11, 21 through every second cooling fin plate KRP1 of the first type and every second cooling fin plate KRP2 (KRP2B, KRP2V) of the second type.

[0060] In this embodiment, the domes 11 for the passage of a cooling fin plate KRP1 (oil middle layer) designed as a flow tray and carrying the first medium 1 are always located on the same sides of the plate opposite the domes 21 of a cooling fin plate KRP2 (KRP2B, KRP2V) designed as a flow tray and carrying the second medium 2 (coolant layer), and the cooling fin plates KRP1, KRP2 are each located in different successive x / y planes.

[0061] If, for example, the first medium 1 is passed through the openings 1Z, 1A and the second medium 2 through the openings 2Z, 2A, with the heat-exchanging media 1, 2 flowing diagonally in counterflow through the flow trays designed as cooling fin plates KRP1, KRP2, the following results according to Fig. 4 (Cut AA after Fig.2) Flow indicated by arrow P1 for the first medium 1 and by arrow P2 for the second medium 2 in an outlet channel K1AB for the first medium 1 and an outlet channel K2AB for the second medium 2. The corresponding inlet channels K1ZU for the first medium 1 and inlet channels K2ZU for the second medium 2 according to Fig. 2 are on average AA of Fig. 4 not visible.

[0062] The flow, with regard to its distribution over the surfaces of the cooling fin plates KRP1, KRP2 (KRP2B, KRP2V), depends on the arrangement of the turbulence plates TB1, TB2 inserted in the flow trays.

[0063] The in the Fig. 2 and Fig. The turbulence plates TB1, TB2, shown with the corresponding through-openings 1Z, 1A and 2Z, 2A, are located on both sides of the adjacent cooling fin plates KRP1, KRP2. The turbulence plates TB1, TB2 have a height H TBon, which corresponds to the height of domes 11, 21 of the cooling fin plates KRP1, KRP2, if in both cooling fin plates KRP1, KRP2, as in the Fig. 2 as well as the Fig. 3-1 and 3-2 are shown, domes 11, 21 are formed, the height of which in the assembled state extends from one cooling fin plate KRP1 to the next cooling fin plate KRP2 according to a first construction principle.

[0064] In a second design principle, the turbulence plates TB1 and TB2 have the same height H. TB on, whereby the height of the domes 11, 21 of the cooling fin plates KRP1, KRP2 is only ½ of the height H TB the turbulence plates TB1, TB2 corresponds if domes 11, 21 are formed in both cooling fin plates KRP1, KRP2, which are directed towards each other and meet in the assembled state of the cooling fin plates between two cooling fin plates KRP1, KRP2.

[0065] This makes it clear that the height H TBThe turbulence plates TB1, TB2 apply equally to both construction principles, or in other words, are independent of the respective construction principle.

[0066] A first turbulence plate TB1 is located in each case (see in particular the Fig. 2 and Fig. 4) A first cooling fin plate KPR1 and a second turbulence plate TB2 are located in the respective second cooling fin plate KRP2 (KRP2B, KRP2V). That is, in the exemplary embodiment, the first turbulence plates TB1 are located in the layer that carries the first medium 1 (oil middle layer) and the second turbulence plates TB2 are located in the layers that carry the second medium 2 (coolant layers).

[0067] Both turbulence plates TB1 and TB2 with height H TB indicate how a forward-looking view of Fig. Figure 5 illustrates, in one embodiment, a sinusoidal geometry with several amplitudes of height H+ and H-.

[0068] Between two positive amplitudes of height H+ or two negative amplitudes of height H- there is a defined periodically recurring distance, which in connection with turbulence plates TB1, TB2 is referred to as the division T of the turbulence plate TB1, TB2.

[0069] In the turbulence plates TB1, TB2, several longitudinal rows are offset from each other and, in one embodiment, are bent sinusoidally out of the x / y plane as intermediate sections ZA, as shown in the Fig. 5 and Fig. 6 can be taken from it.

[0070] When these turbulence plates TB1, TB2 are subjected to flow in the x-direction of the longitudinal rows, the greatest flow resistance occurs, since the intermediate sections ZA do not allow passage in this direction. The lowest flow resistance is therefore found in the transverse y-direction.

[0071] By appropriately angling or tilting the rows within the x / y plane relative to the main flow direction selected between the inlet and outlet openings 1ZU, 1AB; 2ZU, 2AB for the first medium 1 or for the second medium 2, the most favorable flow resistance can be set with respect to the main flow direction running diagonally in the x / y plane in the exemplary embodiment, and an optimal ratio of cooling capacity to flow resistance can be achieved.

[0072] A conventional plate heat exchanger 100 of the applicant has, in summary, the following important characteristic values ​​as a starting point for the material-reduced design and construction of the plate heat exchanger 100. Division T of the turbulence plates TB1, TB2 in mm 4,3 Material thickness S1 of the turbulence plates TB1 and TB2 in mm 0,3 Material thickness S2 of the cooling fin plates KRP1, KRP2 in mm 0,63 Material thickness S3 of the casing plate 101 (including insert 103) in mm 1,6 Cross-sectional area A1 (inflow area) of the passage openings 1Z, 1Ades of the first medium 1 on the casing plate 101 in mm 2 165 Material thickness S4 of the reinforced cooling fin plate KRP2V in mm 1,2 Height H TB of the turbulence plates TB1, TB2 in mm 2,4 Construction height H B of the plate block B in mm 49,41 Number of coolant layers KRP2 / Number of oil center layers KRP1 8 / 7 Weight of one plate block B of the plate heat exchanger 100 in g 454 (100 %) Total weight of the plate heat exchanger 100 in g with mounting plate 102 566 (100 %)

[0073] The division T of the turbulence plates TB1, TB2 at a height H TBThe material thickness S1 of 2.4 mm is, for example, 4.3 mm. The material thickness S1 of the turbulence plates TB1, TB2 is, for example, 0.3 mm. The material thickness S2 of the cooling fin plates KRP1, KRP2 is, for example, 0.63 mm. The material thickness S3 of the casing plate 101 in the exemplary embodiment including insert 103 is 1.6 mm. The material thickness S4 of a reinforced cooling fin plate KRP2V is 1.2 mm. The cross-sectional area A1 of the passage openings 1Z, 1A for the first medium 1 in the casing plate 101 is, for example, 165 mm². 2 Block B includes the reinforced cooling fin plate KRP2V with a material thickness S4 of 1.2 mm and the cooling fin plates KRP1 and KRP2, as well as the casing plate 101 or the casing plate 101 with the insert 103. The overall height H B The diameter of block B, according to Table 1 (see below), is 49.41 mm for eight second cooling fin plates KRP2 (coolant layers) and seven first cooling fin plates KRP1 (oil layers).

[0074] Table 1 illustrates, using a calculation example, the calculation of the overall height of a plate heat exchanger according to the state of the art. Height / Thickness (Column 1) * Number (Column 2) * Solder melting factor (Column 3) = Height (Column 4) Table 1 Height / thickness of the component in mm Number Melting Factor Solder in % Height in mm Reference sign component H TB = 2,4 15,0 1,0 36,0 TB1, TB2 Turbulence plates S2 = 0,63 15,0 0,85 8,03 KRP1, KRP2 Cooling fin plates S4 = 1,2 1,0 0,85 1,02 KRP2V reinforced cooling fin plates S3 = 1,6 1,0 0,85 1,36 101 casing plate 3,0 1,0 1,0 3,0 101-1 Edge overhang of the casing plate 101 Total height of the Block B Total column 4 49,41

[0075] A plate block B of this design weighs approximately 454 g, taking into account the reinforced cooling fin plate KRP2V. This value is subsequently referred to as the first comparative value (100%).

[0076] The weight of the plate block B of the plate heat exchanger 100, taking into account the mounting plate 102 with a material thickness S5 of 4.0 mm, is approximately 566 g as a second comparative value (100 %).

[0077] The current requirements for the fatigue strength of a plate heat exchanger 100 for passenger cars and commercial vehicles for a successful type approval form the basis for the following embodiments of the plate heat exchanger 100 according to the invention.

[0078] Type approval is granted subject to compliance with a pressure fluctuation stress on the high-pressure side p1 of the plate heat exchanger 100 of 2-22 bar, at a temperature of 135 °C for at least 100,000 load cycles.

[0079] Up to now, the steadily increasing requirements, in particular the requirement regarding the pressure increase on the high-pressure side p1 up to 22 bar, have been met by using more material and, for example, by adding additional components, such as the aforementioned insert 103, to stabilize the shell plate 101, or similar components. It is understood that this approach does not reduce the weight of the plate heat exchanger 100 or its costs.

[0080] According to the invention, the procedure is as follows.

[0081] The material thickness S5 and the design of the mounting plate 102 with the inlet opening 1ZU and the outlet opening 1AB for the first medium 1, as well as the inlet opening 2ZU and the coolant outlet opening 2AB for the second medium 2, are not changed, since the wall thicknesses of the mounting plate 102 required for the stable connection of media 1, 2 to the plate heat exchanger 100 cannot be reduced any further. The material thickness S5 of the mounting plate 102 is between 3.0 mm and 6.0 mm and is, for example, 4.0 mm in the exemplary embodiment.

[0082] Extensive investigations were carried out to determine which modifications to the design of the plate heat exchanger 100 would allow for a reduction in material usage and to what extent. These investigations were conducted using equivalent stresses occurring at the turbulence plates TB1 and TB2.

[0083] Based on the insights gained, it is possible to reduce the material used in the production of a plate heat exchanger 100 and to lower the costs, while the tests have shown that at the same time type approval is guaranteed taking into account the pressure fluctuation stress on the oil side of the plate heat exchanger 100 of 2-22 bar, at a temperature of 135 °C and at least 100,000 load cycles.

[0084] According to the invention, optimization measures are carried out on the aforementioned characteristic values ​​T, S1, S2, S3, A1, which are explained one after the other below.

[0085] The key figures are in the Fig. Figures 4 to 7 illustrate this, although it is again recommended to consider the figures together.

[0086] It is stated beforehand that each characteristic value is assigned a characteristic value range from which the characteristic value is selected. It is further emphasized that the aforementioned optimization measures do not only apply to the diagonal design of the plate heat exchanger 100 described above with inlet and outlet openings 1ZU, 1AB; 2ZU, 2AB arranged on one side, but that the characteristic values ​​and characteristic value ranges are transferable to all plate heat exchangers 100 of the same type made of aluminum, regardless of the flow direction of the media 1, 2 and regardless of the arrangement of the media connections or regardless of the chemical composition of the first and second media 1, 2.

[0087] However, the following explanations only apply if the plate block B is as shown in Fig. 2 and Fig.Figure 4 shows that the cooling fin layer is formed on the side of the casing plate 101 with the adjacent second cooling fin plate KRP2B. This means that a coolant layer is formed between the casing plate 101 and the first adjacent cooling fin plate KRP2B, so that, depending on the cross-section and pressure, only the inlet and outlet openings 1Z, 1A of the adjacent cooling fin plate KRP2B can exert a high-pressure force from the first medium 1 on the casing plate 101.

[0088] Optimization of the division T of the turbulence plates TB1, TB2: According to the invention, an optimized characteristic value range between Tmax of a maximum of 4.5 mm and Tmin of a minimum of 3.0 mm is provided for the pitch T of the turbulence plates TB1, TB2, which in one embodiment are sinusoidal. Within this characteristic value range, a flow resistance is generated at the turbulence plates TB1, TB2 in the main flow direction, achieving an optimal ratio between flow resistance and cooling capacity. In an alternative embodiment, the turbulence plates TB1, TB2 are trapezoidal. The aforementioned values ​​can be applied analogously to the trapezoidal turbulence plates TB1, TB2.

[0089] Optimization of the material thickness S1 of the turbulence plates TB1, TB2: According to the invention, as in Fig. 5 and Fig.As illustrated in Figure 6, an optimized characteristic value range between S1max of 0.25 mm and S1min of a minimum of 0.1 mm is provided. Within this characteristic value range, the turbulence plates TB1 and TB2 withstand the required compressive stress and thus exhibit a sufficient material thickness S1, saving weight and costs.

[0090] Optimization of the material thickness S2 of the cooling fin plates KRP1, KRP2 (KRP2B): According to the invention, as in Fig. 7 based on detail B according to the section in Fig. As illustrated in Figure 3-2 by means of a section through a second cooling fin plate KRP2, an optimal material thickness S2 is provided between S2max of a maximum of 0.5 mm and S2min of a minimum of 0.3 mm.

[0091] These parameters apply to all second cooling fin plates KRP2 (KRP2B), but not to the reinforced cooling fin plate KRP2V, and analogously to the first cooling fin plates KRP1.

[0092] Within this characteristic range, the forces acting on the cooling fin plates KRP1, KRP2 (KRP2B) are absorbed without damage, as the corresponding investigations have shown. This material thickness S2, between S2max of 0.5 mm and S2min of a minimum of 0.3 mm, exhibits a sufficient weight- and cost-saving material thickness S2 with regard to the required compressive stress.

[0093] Optimization of the material thickness S3 of the casing plate 101 KRP1, KRP2: According to the invention, as in Fig. As illustrated in Figure 4, an optimized characteristic value range is provided between S3max of a maximum of 1.6 mm and S3min of a minimum of 1.2 mm. Within this optimized characteristic value range, a forming of the edge web 101-1 of the casing plate 101 is possible, so that, according to the invention, an insert 103 can be omitted, thereby also saving weight and costs.

[0094] Optimization of the cross-sectional area A1 of the passage openings 1Z, 1A of the first medium 1 to the casing plate 101: Finally, according to the invention, it is provided as in Fig. 7 based on detail B according to the Fig. 3-2 for a cooling fin plate KRP2B adjacent to the casing plate 101 clarifies that the passage openings 1Z, 1A for the first medium 1 have a cross-sectional area A1 between A1max of a maximum of 165.2 mm² 2 and A1min of a minimum of 38.5 mm 2 can exhibit.

[0095] This optimized characteristic value range is also used analogously for the inlet and outlet openings 1ZU, 1AB of the first medium 1 in the mounting plate 102 and the through-openings 1Z, 1A of the first cooling fin plates KRP1 as well as the through-openings 2Z, 2A of the other second cooling fin plates KRP2 (KPR2B, KRP2V).

[0096] In most cases, but not necessarily, the same cross-sectional areas A1 are selected for the inlet and outlet openings 2ZU, 2AB and the through-openings 2Z, 2A for the second medium 2 in the plate heat exchanger 100. This applies both to the inlet and outlet openings 2ZU, 2AB of the second medium 2 in the mounting plate 102 and the through-openings 2Z, 2A of the reinforced cooling fin plate KRP2V as well as to the other non-reinforced cooling fin plates KRP2 (KRP2B) of the second type.

[0097] However, for the design of the shell plate 101 of the plate heat exchanger 100, the cross-sectional areas A1 (flow areas) of the passage openings 1Z, 1A and the inlet and outlet openings 1ZU, 1AB of the first medium 1 are of particular importance, since the highest expected forces occur depending on the cross-sectional areas A1 of the passage openings 1Z, 1A and depending on the high pressure p1 of the first medium 1 of up to 22 bar, as explained below.

[0098] Because the plate block B, as in Fig. 2 and Fig. As shown in Figure 4, on the side of the casing plate 101 with the adjacent second cooling fin plate KRP2B, i.e. with the coolant layer, the forces acting on the casing plate 101 are determined by the cross-sectional areas A1 (flow surfaces) of the through-openings 1Z, 1A of the end-side second cooling fin plate KRP2B closed by the casing plate 101 and the high pressure p1 applied there.

[0099] The through-openings 1Z, 1A of the end-side second cooling fin plate KRP2B abut the surface of the shell plate 101 facing the domes 21 with their domes 21 opening towards the shell plate 101. This means that the high forces F acting on the shell plate 101 are determined by the cross-sectional areas A1 (flow surfaces) of the through-openings 1Z, 1A acting on the shell plate 101 and the associated pressure p1 between 2 and 22 bar.

[0100] The cross-sectional areas A1 (flow surfaces) are in Fig. 2 indicated by dashed circles and labelled with the reference symbol p1. This clarifies that the highest forces F relevant for the design act on the outer plate 101 in this area of ​​effect.

[0101] In the case of the circular through-openings 1Z, 1A according to the embodiment, the forces F acting on the casing plate 101 according to formula [1] thus depend on the mechanical stress σ (sigma) acting per unit area on the casing plate 101, that is, in the case of circular through-openings 1Z, 1A, the cross-sectional area A1 (inflow area) depends on the diameter d of the through-openings 1Z, 1A of the end-side second cooling fin plate KRP2B. F=σ∗A1 A1=(π∗d2) / 4

[0102] There is a quadratic relationship (formula [2]) between the diameter d and the pressure force F acting on the casing plate 101, as is evident from formulas 1 and 2. Therefore, under the conditions mentioned, contrary to the usual procedure, it is proposed to select the respective diameter d of the through-openings 1Z, 1A of the end-side second cooling fin plate KRP2B as small as possible, depending on a still acceptable pressure loss.

[0103] Since the through-openings 1Z, 1A for all first and second cooling fin plates KRP1 and KRP2 are chosen to be of the same size analogous to the cooling fin plate KRP2B adjacent to the casing plate 101, the cooling fin plates KRP1, KRP2 (KRP2V, KRP2B) have inlet channels for the first medium 1 with the through-openings 1Z and outlet channels for the first medium 1 with the through-openings 1A with the respective cross-sectional area A1 between A1max of a maximum of 165.2 mm². 2and A1min of a minimum of 38.5 mm 2 .

[0104] The above-mentioned investigations have shown that, within the specified characteristic range, starting from a maximum cross-sectional area A1max, a still acceptable pressure loss in the inlet and outlet channels results with decreasing cross-sectional areas down to the minimum cross-sectional area A1min, depending on the application, in which a significant reduction of the forces F acting on the surface of the casing plate 101 is advantageously achieved by reducing the cross-sectional areas.

[0105] The finding of the investigations according to the invention is therefore that it is possible to assign optimized characteristic values ​​to the aforementioned components, the turbulence plates TB1, TB2, the cooling fin plates KRP1, KRP2 (KRP2B) and the shell plate 101, in predetermined characteristic value ranges, in which the fatigue strength of the plate heat exchanger 100 is ensured at a lower weight.

[0106] This saves material, reduces weight and lowers manufacturing costs, in accordance with the object of the invention.

[0107] It has been shown that the allocation of the optimized characteristic values ​​or characteristic value ranges leads to a new standard for plate heat exchangers 100.

[0108] The applicant uses this so-called “VW standard for the design of the material-reduced construction” of plate heat exchangers 100 as follows: The VW standard assigns a plate heat exchanger 100 an index I, also called "material index", which depends on the aforementioned characteristic values ​​T, S1, S2, S3 and A1, with the proviso that the material index (I) formed from the product of the characteristic values ​​is < 113 mm 6 amounts.

[0109] The index I is calculated according to the product formula [3]. I=T∗S1∗S2∗S3∗A1

[0110] An example with key performance indicators of a state-of-the-art plate heat exchanger 100: T in mm 4,0 S1 in mm 0,2 S2 in mm 0,5 S3 in mm 1,6 A1 in mm 2 176,7 (d=15.0 mm) I in mm 6 113

[0111] This conventional plate heat exchanger 100 does not have the material index I according to the invention. The combination of the selected characteristic values ​​does not meet the criteria of the VW standard, since the index is 113 mm. 6 is larger than the required material index (I) < 113 mm 6 In other words, this conventional plate heat exchanger 100 does not meet the standard in terms of material reduction.

[0112] An example with characteristic values ​​of a plate heat exchanger 100 according to the invention: I=T∗S1∗S2∗S3∗A1 T in mm 4 S1 in mm 0,2 S2 in mm 0,35 S3 in mm 1,6 A1 in mm 2 63,6 (d=9.0 mm) I in mm 6 28,5

[0113] Another example with characteristic values ​​of a plate heat exchanger 100 according to the invention: I=T∗S1∗S2∗S3∗A1 T mm 4,3 S1 mm 0,25 S2 mm 0,35 S3 mm 1,6 A1 mm 2 165,2 (d=14.5 mm) I mm 6 99,4

[0114] As previously explained, the invention makes it possible to define the limit ranges with regard to material reduction for the new VW standard of plate heat exchangers 100, whereby, starting from this finding, the material usage or the material usage and the performance of the plate heat exchanger 100 can be optimized within the limits by varying the characteristic values ​​T, S1, S2, S3 and A1.

[0115] The following describes a material-optimized and simultaneously performance-optimized plate heat exchanger 100.

[0116] For example, a preferred material-reduced and performance-optimized plate heat exchanger 100 of the applicant now exhibits the following characteristic values. I=T∗S1∗S2∗S3∗A1 T mm 4,0 S1 mm 0,2 S2 mm 0,42 S3 mm 1,6 A1 mm 2 154 (d=14.0 mm) I mm 6 82,8

[0117] In addition to material optimization, the height H is used as a further key figure for performance optimization. TB the turbulence plates TB1, TB2 ( Fig.5) reduced from 2.4 mm to only 2.0 mm.

[0118] This results in the following values ​​for the material- and performance-optimized plate heat exchanger 100 according to the invention. Division T of the turbulence plates TB1, TB2 in mm 4,0 Material thickness S1 of the turbulence plates TB1 and TB2 in mm 0,2 Material thickness S2 of the cooling fin plates KRP1, KRP2 in mm 0,42 Material thickness S3 of the casing plate 101 (including insert 103) in mm 1,6 Cross-sectional area A1 (inflow area) of the through-openings 1Z, 1A; 2Z, 2A of the first medium 1 at the casing plate 101 in mm² 2 154 Material thickness S4 of a reinforced cooling fin plate KRP2V in mm 1,2 Height H TB of the turbulence plates TB1, TB2 in mm 2,0 Construction height H B Plate block B in mm 50,5 Number of coolant layers KRP 2 / Number of oil center layers KRP1 10 / 9 Weight of one plate block B of the plate heat exchanger 100 in g 401 (88%) Total weight of the plate heat exchanger 100 in g 536 (95%)

[0119] The division T of the turbulence plates TB1, TB2 at a height H TB For example, the material thickness of 2.0 mm is 4.0 mm. The material thickness S1 of the turbulence plates TB1, TB2 is, for example, 0.2 mm. The material thickness S2 of the cooling fin plates KRP1, KRP2 is, for example, 0.42 mm. The material thickness S3 of the casing plate 101 is 1.6 mm. The material thickness S4 of a reinforced cooling fin plate KRP2V is 1.2 mm. The cross-sectional area A1 of the through-openings 1Z, 1A of the first medium 1 in the casing plate 101 is, for example, 154 mm². 2 .

[0120] The building height H BThe thickness of block B, taking into account the reinforced cooling fin plate KRP2V, is 50.56 mm according to Table 2 (see below) with ten layers of the second cooling fin plate KRP2 (coolant layers) and nine layers of the first cooling fin plate KRP1 (oil layers).

[0121] Table 2 illustrates, using a calculation example, the calculation of the overall height of a plate heat exchanger according to the invention, in particular optimized in terms of material and performance.

[0122] Height / Thickness (Column 1) * Number (Column 2) * Solder melting factor (Column 3) = Height (Column 4) Table 2 Height / thickness of the component in mm Number Melting Factor Solder in % Height in mm Reference sign component H TB = 2,0 19,0 1,0 38,0 TB1, TB2 Turbulence plates S2 = 0,42 19,0 0,85 6,78 KRP1, KRP2 Cooling fin plates S4 = 1,2 1,0 0,85 1,02 KRP2V reinforced cooling fin plates S3 = 1,6 1,0 0,85 1,36 101 casing plate 3,4 1,0 1,0 3,4 101-1 Edge overhang of the casing plate 101 Total height of the Block B Total column 4 Total height 50,56

[0123] The building height H B The diameter of block B, taking into account the reinforced cooling fin plate KRP2V, has only increased slightly from 49.41 mm to 50.56 mm compared to the applicant's plate heat exchanger 100 according to Table 1, due to material optimization and simultaneous performance optimization.

[0124] It is further evident that the plate block B of the plate heat exchanger 100, taking into account the reinforced cooling fin plate KRP2V with constant thickness, now weighs only 401 g and is thus reduced by 12% in terms of weight compared to the first comparison value (100%).

[0125] The weight of the plate heat exchanger 100, taking into account the reinforced cooling fin plate KRP2V and including the mounting plate 102, is also reduced by 5% to 536 g compared to the second reference weight (100%). Furthermore, with a height of H B Taking into account the reinforced cooling fin plate KRP2V of the plate block B of only 50.5 mm, ten layers of the second cooling fin plate KRP2 (coolant layers) and nine layers of the first cooling fin plate KRP1 (oil middle layers) are arranged, thereby increasing the performance of the plate heat exchanger 100.

[0126] A predominantly material-optimized plate heat exchanger 100 is presented below for comparison. A preferred material-optimized plate heat exchanger 100 exhibits the following characteristic values. These characteristic values ​​remain unchanged compared to the previous example of the material- and performance-optimized plate heat exchanger 100. I=T∗S1∗S2∗S3∗A1 T mm 4,0 S1 mm 0,2 S2 mm 0,42 S3 m 1,6 A1 mm 2 154 (d=14.0 mm) I mm 6 82,8

[0127] In a material-optimized plate heat exchanger 100, the height H is increased compared to the material- and performance-optimized plate heat exchanger 100. TB The turbulence plates TB1, TB2 were selected to be 2.0 mm thick.

[0128] This results in the following values. Division T of the turbulence plates TB1, TB2 in mm 4,0 Material thickness S1 of the turbulence plates TB1 and TB2 in mm 0,2 Material thickness S2 of the cooling fin plates KRP1, KRP2 in mm 0,42 Material thickness S3 of the casing plate 101 (including insert 103) in mm 1,6 Cross-sectional area A1 (inflow area) of the passage openings 1Z, 1A of the first medium 1 at the casing plate 101 in mm² 2 154 Material thickness S4 of a reinforced cooling fin plate KRP2V in mm 1,2 Height H TB of the turbulence plates TB1, TB2 in mm 2,4 Construction height H B Plate block B in mm 46,73 Number of coolant layers KRP 2 / Number of oil center layers KRP1 8 / 7 Weight of one block B of the plate heat exchanger: 100 g 330 (73%) Total weight of the plate heat exchanger 100 in g 456 (80%)

[0129] The division T of the turbulence plates TB1, TB2 at a height H TBThe thickness of 2.0 mm remains 4.0 mm. The material thickness S1 of the turbulence plates TB1, TB2 remains unchanged at 0.2 mm. The material thickness S2 of the cooling fin plates KRP1, KRP2 remains unchanged at 0.42 mm. The material thickness S3 of the casing plate 101 remains unchanged at 1.6 mm. The material thickness S4 of a reinforced cooling fin plate KRP2V remains 1.2 mm. The cross-sectional area A1 of the through-openings 1Z, 1A for the first medium 1 on the casing plate 101 is also 154 mm². 2 .

[0130] It becomes clear that the plate block B of the plate heat exchanger 100, taking into account the reinforced cooling fin plate KRP2V, now weighs only 330 g and is therefore reduced by 27% in weight compared to the first comparison value (100%).

[0131] The weight of the plate heat exchanger 100, taking into account the reinforced cooling fin plate KRP2V and including the mounting plate 102, is reduced by 20% to 456 g compared to the second reference weight (100%).

[0132] Furthermore, at a building height H B Taking into account the reinforced cooling fin plate KRP2V of the plate block B of only 46.73 mm, eight layers of the second cooling fin plate KRP2 (coolant layers KRP2) and seven layers of the first cooling fin plate KRP1 (oil middle layers) are arranged, thereby reducing the weight of the plate heat exchanger 100 accordingly.

[0133] The building height H B According to Table 3 (see below), the diameter of block B is 46.73 mm with eight layers of the second cooling fin plate KRP2 (coolant layers) and seven layers of the first cooling fin plate KRP1 (oil layers).

[0134] Table 3 illustrates, using a calculation example, the calculation of the overall height of a plate heat exchanger according to the invention, in particular optimized in terms of material and performance.

[0135] Height / Thickness (Column 1) * Number (Column 2) * Solder melting factor (Column 3) = Height (Column 4) Table 3 Height / thickness of the component in mm Number Melting Factor Solder in % Height in mm Reference sign component H TB = 2,4 15,0 1,0 36,0 TB1, TB2 Turbulence plates S2 = 0,42 15,0 0,85 5,355 KRP1, KRP2 Cooling fin plates S4 = 1,2 1,0 0,85 1,02 KRP2V reinforced cooling fin plates S3 = 1,6 1,0 0,85 1,36 101 casing plate 3,0 1,0 1,0 3,0 101-1 Edge overhang of the casing plate 101 Total height of the Block B Total column 4 46,73

[0136] The building height H B The diameter of block B, taking into account the reinforced cooling fin plate KRP2V, has been reduced from 49.41 mm to 46.73 mm compared to the applicant's plate heat exchanger 100, according to Table 1, through material optimization while maintaining the same performance.

[0137] It becomes clear that, in combination with the material index I, within the specified characteristic value ranges, by varying the height H TB The turbulence plates TB1, TB2 advantageously enable performance optimization of a material-optimized plate heat exchanger 100.

[0138] A plate heat exchanger 100 of the generic type is used as an engine oil cooler, transmission oil cooler or as a plate heat exchanger 100 in a refrigeration machine, in particular an air conditioning system of a vehicle, and also in condensers with additional strength measures.

[0139] Vehicles in which such plate heat exchangers of the generic type 100 are used include passenger cars and commercial vehicles, such as ships, construction machinery and buses. Reference symbol list 100 plate heat exchangers 101 Cover plate 101-1 Edge of the casing plate 102 Mounting plate 103 inserts B plate block H B Height of the plate block 1 first medium 2 second medium K1ZU Entry Channel First Medium 1ZU Inlet opening first medium K1AB Exit channel first medium 1AB Drainage opening first medium K2ZU Entry Channel Second Medium 2ZU Inlet opening second medium K2AB exit channel second medium 2AB Drainage opening second medium 1Z Through-opening-inlet first medium 1A Through-opening-drainage first medium 2Z through-opening-inlet second medium 2A Through-opening-drainage second medium KRP1 cooling fin plate first type 11 domes of a cooling fin plate 12 Edge web of a cooling fin plate KRP2 cooling fin plate, second type 21 domes of a cooling fin plate 22 Edge web of a cooling fin plate KRP2V reinforced cooling fin plate KRP2B adjacent cooling fin plate TB1 Turbulence plate TB2 Turbulence plate T division H TB Height of a turbulence plate H+ Amplitude H Amplitude ZA Intermediate Section x direction in a horizontal plane y direction in a horizontal plane perpendicular to the x direction z direction in a vertical plane perpendicular to the x direction x / y plane of 101, KRP1, KRP2, KRP2V, 102, 103 S1 Material thickness of the turbulence plates TB1, TB2 S2 Material thickness of the cooling fin plates between KRP2 S3 Material thickness of the casing plate 101 or of the casing plate 101 and an insert 103 S4 Material thickness of the reinforced cooling fin plate KPR2V S5 Material thickness of the mounting plate 102 A1 Cross-sectional area F Pressure force p1 high pressure (high-pressure side) p2 low pressure (low pressure side) σ mechanical stress d diameter

Claims

[1] Plate heat exchanger (100) made of aluminium, comprising at least two nested cooling fin plates (KRP1; KPR2) having a predefinable material thickness (S2) and designed as flow trays, which are accessible via separate inlet and outlet channels (K1ZU, K1AB; K2ZU, K2AB), wherein the inlet and outlet channels (K1ZU, K1AB; K2ZU, K2AB) are defined by through openings (1Z, 1A; 2Z, 2A) in the cooling fin plates (KRP1; KPR2) provided with domes (11, 21), characterized by , that in the cooling fin plates (KRP1; KPR2) a predefinable material thickness (S1) and a predefinable pitch (T) as well as a height (H) TBTurbulence plates (TB1, TB2) are embedded in the inlet and outlet channels (K1ZU, K1AB; K2ZU, K2AB) through which two heat-exchanging media (1, 2) flow, wherein sinusoidal or trapezoidal turbulence plates (TB1, TB2) have several amplitudes (H+, H-), wherein a division (T) is provided in which a defined periodically recurring distance is defined between two positive amplitudes (H+) and two negative amplitudes (H-), wherein the turbulence plates (TB1, TB2) are arranged in several longitudinal rows offset from one another in an x / y plane as intermediate sections (ZA), wherein a shell plate (101) and a mounting plate (102), between which the cooling fin plates (KRP1, KRP2) are arranged, lie in successive x / y planes,wherein a material-reinforced shell plate (101) with a material thickness (S3) is arranged at one end and a cooling fin plate (KRP2B) with a specified material thickness (S2) is arranged adjacent to the shell plate (101) and through which a second medium (2) flows, the embedded turbulence plate (TB2) of which is flowed by the second medium (2) at a low pressure (p2), the domes (21) of which terminate at the shell plate (101), whereby the first medium (1) at a high pressure (p1) is in contact with the shell plate (101), and depending on a respective predefinable cross-sectional area (A1) of the respective through-openings (1Z, 1A) exerts high pressure forces (F) on the shell plate (101), wherein the plate heat exchanger (100) is assigned a standardized material index (I) for material-reduced manufacturing, which is derived from the mathematical product of the following characteristic values, the Material thickness (S1) and the spacing (T) of the turbulence plates (TB1, TB2),the material thickness (S2) of the cooling fin plates (KRP1, KRP2), the material thickness (S3) of the casing plate (101) and the cross-sectional areas (A1) of the through-openings (1Z, 1A) of the domes (21) formed by the cooling fin plate (KRP2B) adjacent to the casing plate (101), wherein each characteristic value is variably selected from a defined range of values ​​with the proviso that the standardized material index (I) formed from the product of the selected characteristic values ​​is < 113 mm, 6 amounts. [2] Plate heat exchanger (100) according to claim 1, characterized by , that the respective characteristic value of the pitch (T) of the turbulence plates (TB1, TB2) is selected from a range of values ​​which lies between a maximum pitch (Tmax) of 4.5 mm and a minimum pitch (Tmin) of 3.0 mm. [3] Plate heat exchanger (100) according to claim 1, characterized by, that the respective characteristic value of the material thickness (S1) of the turbulence plates (TB1, TB2) is selected from a range of values ​​which lies between (S1max) of 0.25 mm and (S1min) of 0.1 mm. [4] Plate heat exchanger (100) according to claim 1, characterized by , that the respective characteristic value of the material thickness (S2) of the cooling fin plates (KRP1, KRP2) is selected from a range of values ​​which lies between a maximum material thickness (S2max) of 0.5 mm and a minimum material thickness (S2min) of 0.3 mm. [5] Plate heat exchanger (100) according to claim 1, characterized by , that the respective characteristic value of the material thickness (S3) of the casing plate (101) is selected from a range of values ​​which lies between a maximum material thickness (S3max) of 1.6 mm and a minimum material thickness (S3min) of 1.2 mm. [6] Plate heat exchanger (100) according to claim 1, characterized by, that the respective characteristic value of the cross-sectional areas (A1) of the passage openings (1Z, 1A) of the domes of the cooling fin plate (KRP2B) adjacent to the shell plate (101) is selected from a range of values ​​whose limits are formed between 165.2 mm² (maximum value) and 38.5 mm² (minimum value). [7] Plate heat exchanger (100) according to claim 6, characterized by , that the through-openings (1Z, 1A) of the cooling fin plate (KRP2B) adjacent to the shell plate (101) are circular, so that the characteristic value of the cross-sectional area (A1) results from the selection of a diameter (d) from a range of values ​​which lies between a maximum diameter (dmax) of 14.5 mm and a minimum diameter (dmin) of 7.0 mm. [8] Plate heat exchanger (100) according to claim 1 and 2, characterized by that by varying a height (H TB) the number of cooling fin plates (KRP1, KRP2) that can be installed is changed by the turbulence plates (TB1, TB2), thereby optimizing the performance of the plate heat exchanger (100).

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