Plate heat exchanger

Abstract

The invention relates to a plate heat exchanger comprising a number of frames or shells which are stacked one above the other and through which at least two different media, for example liquids or gases, flow. These plate heat exchangers according to the invention, which are of frame-type or shell-type construction, may have various structural configurations, wherein turbulators are used which comprise corrugated rib-like turbulator elements in order to improve heat transfer. The turbulator elements extend either parallel to or at an angle to the longitudinal edges and narrow-side edges of the frames or shells. Furthermore, variants are provided having so-called flow channels and additional turbulator segments, the invention also encompassing various combinations of solutions. The plate heat exchanger according to the invention is also configured for a cross-flow, a straight-through flow, or a U-shaped flow of the media, and / or for a serpentine flow or multi-serpentine flow of the media.

Description

[0001] 00159604-0014 11 / 18 / 2025 PCT / DE0S£^|ößffi115

[0002] 18-1 W14

[0003] Plate heat exchangers - description

[0004] The invention relates initially to a plate heat exchanger with a number of frames arranged stack-like on top of each other between two end plates, wherein

[0005] - a partition plate is located between two adjacent frames to form media-carrying medium passages for the transmission of at least two different media,

[0006] - one or both end plates have inlets for feeding the media into the media passages and outlets for removing the media from the media passages,

[0007] - each separating plate has at least four passages for the passage of media, aligned with the aforementioned inlets and outlets of the end plates, two of which are closed in the assembled or operating state of the plate heat exchanger,

[0008] - the frames, end plates and divider plates are of the same size and have a rectangular or square shape with four straight side edges, two of which are parallel to each other and two of which are perpendicular to these long sides and also parallel to each other.

[0009] - each frame has an outer closed first frame section formed by its longitudinal side edges and narrow side edges, and second frame sections dividing this first frame section into a central flow chamber and at least two collecting channels, wherein 00159604-0015 18.11.2025 PCT / DE0S£^|ößffi115

[0010] IS-L

[0011] 2

[0012] These collecting channels are aligned for the passage of the media onto the respective openings of the adjacent partition plate(s), and

[0013] — in the flow chamber of at least one frame a turbulator is arranged which is designed with corrugated rib-shaped turbulator elements and which run at parallel distances from each other and which extends over the entire area or a part of the flow chamber.

[0014] A plate heat exchanger of the type mentioned above is known from DE 20 2020 105 759 Ul and is referred to there as a heat exchanger. This heat exchanger, or plate heat exchanger, consists of stacked frames, baffles, and end plates and is therefore sometimes called a "stacked shell cooler" in technical terminology, as it is a heat exchanger with a stacked design. In English, the term "Stacked Shell Cooler" (abbreviation: SSC) is also used.

[0015] Such heat exchangers, or plate heat exchangers, have been used in a wide variety of applications for years, particularly in internal combustion engines. They serve both single-phase heat transfer, for example as oil / water heat exchangers, and two-phase heat transfer, for example as evaporators or condensers. For instance, waste heat recovery requires heat exchangers that transfer heat from a liquid or gaseous medium to another working medium, a refrigerant. In Organic Rankine Cycles (ORCs) in internal combustion engines, there are two main heat sources: the exhaust gas and the water / glycol fluid from the engine's cooling circuit. The design of a heat exchanger must therefore be adapted to the different requirements and conditions arising from the heat sources, fluids, system configurations, and geometric dimensions.

[0016] 1B“1 J -Ä1Q25“: OD359S:04-O0a 6

[0017]

[0018] 3

[0019] This results in restrictions, etc. This also applies to the aforementioned plate heat exchangers.

[0020] Generally, such plate heat exchangers are available in two different designs, namely in the “frame design”, as described in the aforementioned DE 20 2020 105 759 Ul, and in the “shell design”.

[0021] A plate heat exchanger in a shell design is described in DE 10 2009 041 526 A1. The basic principle is the same for both designs, frame and shell, as their components are designed with chambers that are sealed against each other and through which at least two different media flow, exchanging heat due to their temperature differences. In the shell design described in DE 10 2009 041 526 A1, stackable, trough-shaped heat exchanger plates are used. These plates are manufactured as deep-drawn sheet metal components and each has several openings for a first fluid and a separate second fluid.In both designs, the frames or shells are shaped to have a certain height and, in conjunction with the baffles, form chambers—that is, medium-carrying passages—to allow the media to pass through once all components of the plate heat exchanger are assembled and sealed. These known heat exchangers, or plate heat exchangers, are designed so that the media used within them do not come into direct contact, meaning they cannot mix.

[0022] The heat exchangers or plate heat exchangers known from DE 20 2020 105 759 Ul and DE 10 2009 015 526 Al also feature turbulators or turbulator inserts, which improve the heat exchange performance. 00159604-0017 18.11.2025 PCT / DE0S£^|ößffi115

[0023] 4

[0024] They serve and are located in the chambers or media passages formed by the frame-shaped or shell / tub-shaped components. In DE 20 2020 105 759 Ul, such a turbulator is located in the flow chamber of a frame that has an outer, closed first frame section formed by its longitudinal and narrow side edges, and second frame sections that divide this first frame section into a flow chamber and at least two collecting channels. The flow chambers are designed such that the flowing medium is evenly distributed over the turbulator, thereby minimizing the pressure loss in the medium. Such a turbulator thus creates turbulence in the flowing medium.DE 20 2020 105 759 Ul also proposes designing the turbulator as a corrugated sheet or plate with round or rectangular corrugated ribs. Particularly in the case of an X-shaped flow through the central flow chambers, the turbulators according to DE 20 2020 105 759 Ul preferably have openings in the rib walls, for example in the form of gills or holes, or these are implemented as a so-called offset design. DE 20 2020 105 759 Ul stipulates that the corrugated ribs of the turbulator run in a direction perpendicular or parallel to the longitudinal side edges of the first frame section.

[0025] Furthermore, DE 20 2020 105 759 Ul also describes the designs already known for such stacked-shell coolers, i.e., heat exchangers or plate heat exchangers, namely the designs for X, I, and U flow, including those with turbulators arranged in the frame. It is also noted that different arrangements of the connections are conceivable to accommodate different flow patterns in the medium passages, such as counterflow, coflow, or meandering flow, possibly 00159604-0018 18.11.2025 PCT / DEflS^ / |ößffi115

[0026] 18" Il -2025-001 59S04-0018

[0027]

[0028] 5

[0029] This can also be achieved with multiple meandering flows or without meandering flows. It is therefore emphasized here that the plate heat exchanger according to the invention is also suitable for all these flow variants and connection arrangements. These different flow variants and arrangements will be discussed in more detail later.

[0030] Furthermore, it is essential to note that, even in the plate heat exchanger according to the invention, each frame or shell is designed for the flow of a medium, such as a fluid. In the case of an X-shaped flow, this means, for example, that with two frames or shells arranged one above the other or adjacent to each other, the different media, when flowing through their respective planes, exhibit a diagonally intersecting flow direction. This means that the medium entering the flow chamber of the frame in question through a collecting channel exits this frame through the diagonally opposite collecting channel and passes through the opening in the adjacent baffle plate into the next plane or the adjacent frame.

[0031] The aforementioned plate heat exchangers, in particular the plate heat exchanger disclosed in DE 20 2020 105 759 Ul, have the disadvantage that the flow conditions prevailing within them are not optimal. Especially in known plate heat exchangers with turbulators, the flow conditions are not optimal for various reasons, for example, due to pressure losses. Furthermore, the solution described in DE 20 2020 105 759 Ul pursues a different purpose, namely the prevention of the mixing of the two media in the event of a leak. 00159604-0019 18.11.2025 PCT / DE0M Qffi115

[0032] 1 - 11-2025- 1 860 -801 8

[0033] 6

[0034] The present invention is therefore based on the objective of improving a plate heat exchanger of the type mentioned at the outset in frame construction in such a way that a more favorable flow behavior of the media is achieved during the operation of the plate heat exchanger and thus ultimately the effectiveness or efficiency of such a plate heat exchanger is increased.

[0035] This problem is solved in accordance with the invention using a plate heat exchanger of the generic type by arranging the corrugated fin elements of the turbulator not perpendicular or parallel, but at an angle to the longitudinal side edges of the first frame section of the frame, wherein this angle is formed between the longitudinal direction of the corrugated fin turbulator elements and one of the two longitudinal side edges of the first frame section of the frame and is between 2° and 88°.

[0036] This plate heat exchanger according to the invention has the initial advantage that the overall flow behavior is more homogeneous, resulting in more uniform heat transfer. The angled arrangement of the corrugated fin elements of the turbulator facilitates longitudinal and transverse flow through the turbulator. This leads to improved or more favorable flow conditions, as the inventive orientation of the corrugated fin turbulator elements results in a more uniform pressure distribution and pressure equalization in the relevant plane with the frame in which the turbulator is located.

[0037] The aforementioned angular alignment of the corrugated rib-shaped elements of the turbulator according to the invention is to be understood, with regard to the corrugated rib sheets or corrugated plates with round or rectangular corrugated ribs known, for example, from the aforementioned DE 20 2020 105 759 Ul, as meaning that these 00159604-0020 18.11.2025 PCT / DE0S£^|ößffi115

[0038] 7

[0039] The corrugated fins have a certain length and run parallel to each other, thus all extending in the same direction, which is referred to here as the longitudinal direction. In the turbulator according to the invention, the angle is therefore formed between this longitudinal direction of the corrugated fin-shaped turbulator elements and one of the two longitudinal side edges of the first frame section, which are spaced parallel to each other. According to the invention, this angle is between 2° and 88°. Angles within this range result in the more favorable flow conditions in a plate heat exchanger of this type, as already explained above, compared to the prior art.

[0040] Preferably, the angle between the longitudinal direction of the turbulator elements and one of the two longitudinal side edges of the first frame section is 20°, 30°, 35°, 40°, 45°, 50°, or 55°. As the applicant's measurements and investigations have shown, these angle values ​​result in particularly favorable flow conditions in the plate heat exchanger. The applicant also conducted simulations as part of its measurements and investigations, which demonstrate the advantageous flow effects that result from using turbulators with corrugated fin-shaped elements exhibiting the aforementioned angles. With such turbulators, it is therefore possible to achieve the highest possible flow velocity of a medium across the entire surface of a frame, meaning that the medium flows at the highest possible velocities even in the edge and corner regions of the frame.

[0041] According to an advantageous embodiment of the plate heat exchanger according to the invention in frame construction, the length / width ratio of the end plates, the frames and the partition plates is dimensioned such that the length of the longitudinal side edges is 4:3 in relation to the length of the narrow side edges and the angle between the longitudinal direction of the turbulator elements and one of the two 00159604-0021 18.11.2025 PCT / DE0S£^|ößffi115

[0042] 1 Sl

[0043] 8

[0044] The angle of the longitudinal side edges of the first frame section of the frame is between 20° and 45°, preferably 20°. Measurements, investigations, and simulations carried out by the applicant have shown that a plate heat exchanger according to the invention, with these dimensions or proportions of the end plates, frame, and partition plates, and the aforementioned angle values ​​for the turbulator elements, achieves the best flow effects, i.e., it produces the greatest pressure equalization in one plane with the frame in question. In this case, the pressure conditions are equalized, and thus heat transfer is most effective.

[0045] According to a further advantageous embodiment of the plate heat exchanger according to the invention, the length-to-width ratio of the end plates, the frames, and the baffles is dimensioned such that the length of the longitudinal side edges is 150 mm and the length of the narrow side edges is 100 mm, and the angle between the longitudinal direction of the turbulator elements and one of the two longitudinal side edges of the first frame section is between 20° and 45°, preferably 20°. In this embodiment, particularly favorable numerical values ​​are thus specified for the lengths of the longitudinal and narrow side edges of the end plates, the frames, and the baffles. These numerical values ​​are very advantageous for the practical application of such plate heat exchangers and, in conjunction with the aforementioned angle values, lead to particularly advantageous flow conditions in the plate heat exchanger.

[0046] Furthermore, the invention comprises an embodiment of the plate heat exchanger in which the inlets and outlets of the end plates, the passages (openings) of the partition plates aligned with them, and the corresponding collecting channels of the frames are each located in their corner regions. This is patented on 00159604-0022 on November 18, 2025 (PCT / DE0S£^|ößffi115).

[0047] 9

[0048] Due to the design, the inlets and outlets of the end plates, the passages (openings) of the baffles aligned with them, and the corresponding collecting channels of the frames are not located at any other arbitrary point, but all in their corner areas. This advantageously makes it possible to utilize the largest possible area between these corner areas for the turbulators in the plate heat exchanger and thus to exploit the resulting beneficial flow effects to a particularly large extent.

[0049] Furthermore, the invention provides three further variants of the plate heat exchanger constructed in a frame design, in which the three flow possibilities already mentioned at the outset, namely X-, I-, and U-flow of the media, can be implemented. For X-flow of the plate heat exchanger, the turbulators located in superimposed adjacent frames are arranged such that their corrugated turbulator elements are positioned at opposite angles to the longitudinal side edges of the first frame section. It has already been briefly explained above that in the case of X-flow, the media flowing through two adjacent superimposed planes, i.e., frames with integrated turbulators, have a diagonally intersecting flow direction.In conjunction with the corrugated turbulator elements arranged at opposite angles within these adjacent frames, heat transfer between these media is particularly advantageous. This is because, in this configuration, the turbulators in the respective frames ensure a particularly favorable pressure equalization or homogenization of the pressure conditions within the respective turbulator or the associated frames for X-shaped flow, and consequently provide a particularly large surface area between these frames. 00159604-0023 18.11.2025 PCT / DE0S^ / |Qßffi115.

[0050] :i ^2025=0010^04-0023

[0051]

[0052] 10

[0053] and the separating plate located between the turbulators causes heat transfer between the two media.

[0054] While not strictly necessary, it leads to favorable flow conditions if the corrugated turbulator elements, according to this design of the plate heat exchanger for X-flow, are arranged at the same angle but in opposite directions to the longitudinal edges of the first frame section. For example, it is possible that the turbulators in adjacent frames, stacked one above the other, each have the same angle of, say, 20°. However, it is equally possible that the turbulator elements of one turbulator are arranged at an angle of, say, 20° to the relevant longitudinal edge, while the turbulator elements of the turbulator in the adjacent horizontal frame have an angle of 40°.

[0055] According to another embodiment of the plate heat exchanger according to the invention, in the case of inertial flow of the media through the plate heat exchanger, the turbulator consists of two turbulator segments of the same size, each covering half of a flow chamber of the frame. The division of the two turbulator segments is located in the middle of the longitudinal side edges of the first frame section, so that the corrugated turbulator elements of the turbulator segments are arranged at opposite angles to the longitudinal side edges of the first frame section. Particularly favorable flow conditions occur with this design of the plate heat exchanger.

[0056] Furthermore, according to the invention, an embodiment for a plate heat exchanger for the purpose of a U-shaped flow of the media is provided. 00159604-0024 18.11.2025 PCT / DE0S£^|ööffi115

[0057] 11-2025-15-3604-082

[0058] 11

[0059] The proposed plate heat exchanger design consists of two turbulator segments of equal size, each covering half of a flow chamber within the frame. The division between the two turbulator segments is located at the midpoint of the narrow edges of the first frame section, so that the corrugated turbulator elements of the segments are oriented at opposite angles to the longitudinal edges of the first frame section. A straight, U-shaped dividing web extends from one narrow edge into the flow chamber at the level of the turbulator segment division. This design of the plate heat exchanger results in particularly favorable flow conditions.

[0060] Apart from the plate heat exchangers with angularly arranged turbulator elements described above, the invention also relates to a plate heat exchanger according to the preamble of claim 10. A plate heat exchanger of the aforementioned type is also known from DE 20 2020 105 759 Ul, so that, in order to avoid repetition, reference is made to the preceding explanations in this regard, in particular to the problem already formulated, namely to achieve a more favorable flow behavior of the media during the operation of the plate heat exchanger in order to ultimately increase its effectiveness or efficiency.

[0061] This problem is solved according to the invention with a plate heat exchanger of the generic type also with the characterizing features of claim 10 in that the turbulator extends only over a partial area of ​​the flow chamber, wherein at least between an outer surface of a straight outer edge of the turbulator and the inner surface of the adjacent inner edge of the first frame section 00159604-0025 18.11.2025 PCT / DE0S£^|ößffi115

[0062] 12

[0063] The cut of the frame contains an open or unobstructed area, meaning that the flow chamber does not completely fill the area through which the medium can flow, thus forming a flow channel.

[0064] This plate heat exchanger according to the invention thus provides one or more flow channels in a plane with a frame and a turbulator arranged therein. The media, when they enter the plane of a frame, flow not only through the turbulator but also through the flow channel(s). Measurements, investigations, and simulations by the applicant have shown that the presence of at least one such flow channel leads to an improved flow situation in the relevant flow plane. The flow conditions and the resulting heat transfer effects then vary depending on the size and shape or design of the flow channel.Since this embodiment of the plate heat exchanger features a straight outer edge of the turbulator, the size and shape of the flow channel initially depend on the arrangement and course of this straight outer edge. For example, the outer edge of the turbulator may be positioned parallel to the adjacent inner edge of the first frame section, resulting in a flow channel with a constant width along its entire length. Consequently, a medium entering the plane of the frame flows through this flow channel with a constant width.Instead, it is also possible that the flow channel has a different shape, i.e., does not have the same width over its entire length, but, for example, that at least one outer edge of the turbulator lies at an acute angle to the adjacent side edge of the first frame section, such that the flow channel thus formed has an essentially triangular shape, with the short 00159604-0026 18.11.2025 PCT / DE0S£^|ößffi115.

[0065] 38-13^025-OT159S04-'©I326

[0066] 13

[0067] The side of this triangular flow channel lies on a collecting channel of the frame, through which the medium flows into the frame and to the turbulator located within it. Measurements, investigations and simulations by the applicant have shown that such a triangular shape of the flow channel, compared to flow channels with a constant width, results in even better uniformity of the pressure conditions in the plane with the frame and turbulator.

[0068] An advantageous further development of the aforementioned design of the plate heat exchanger with a flow channel provides that two parallel, opposing outer edges of the turbulator lie at an acute angle to the respective adjacent side edges of the first frame section, such that the flow channels thus formed have a substantially triangular shape, with the short side of each of these triangular flow channels abutting a manifold of the frame through which the medium flows into the frame and to the turbulator located therein. In this case, there are therefore two triangular flow channels that lie parallel to each other and thus advantageously influence the flow conditions in the plane containing the frame and the turbulator.

[0069] Another variant of the aforementioned plate heat exchanger with a flow channel provides for the possibility that all outer edges of the turbulator lie at an acute angle to the adjacent side edges of the first frame section, such that the flow channels thus formed have an essentially triangular shape, with the short side of each of these triangular flow channels lying against a collecting channel of the frame through which the medium flows into the frame and to the turbulator located within it. In this case, flow channels are therefore present on all side edges of the frame, that is, a total of four flow channels, each with 00159604-0027 18.11.2025 PCT / DE0S£^|ößffi115

[0070] 18-1 1^02S^0IB9ßW-0027

[0071]

[0072] 14

[0073] triangular shape. It is understood that in this case, and also in the aforementioned designs, the flow channels in a plane do not necessarily all have to be the same size or proportions. The triangular shape of the flow channels can therefore vary, particularly depending on the chosen angle.

[0074] Furthermore, the acute angle of the aforementioned triangular flow channels is preferably between 2° and 10°.

[0075] Apart from the plate heat exchanger described above with a flow channel which is bounded on one side by the outer surface of a straight outer edge of the turbulator, the invention also includes another embodiment of the plate heat exchanger according to the preamble of claim 15, in which, to solve the problem already formulated above, it is proposed according to the invention that the turbulator extends only over a partial area of ​​the flow chamber, wherein at least between an outer surface of an outer edge of the turbulator, which is curved or arcuate or wave-shaped, and the inner surface of the adjacent inner edge of the first frame section of the frame, there is an open or unobstructed area, i.e., an area which does not completely fill the flow chamber, through which the medium can flow and thus forms a flow channel.In this design, the outer surface of an outer edge of the turbulator is not straight, but curved, arcuate, or wavy. Unlike a straight outer edge of the turbulator, the curved, arcuate, or wavy shape of the outer edge results in a different flow behavior of the medium as it flows through the resulting flow channel. The curve- or - 00159604-0028 18.11.2025 PCT / DE0S£^|ößffi115.

[0076] 1'8-a 1"2Q25"00.15SSQ4-0028

[0077]

[0078] 15

[0079] The shape of the curved or arc-shaped outer edge, as well as the wave-like shape of the outer edge, is not specifically defined, but can be selected depending on the desired flow behavior. The curved or arc-shaped or wave-like shape can therefore be uniform or uneven, for example. A sinusoidal waveform is one possible option.

[0080] A first advantageous further development of the aforementioned embodiment of the plate heat exchanger with a flow channel, in which the outer surface of an outer edge of the turbulator is curved, arcuate, or wave-shaped, provides that flow channels are located between two opposing outer edges of the turbulator and the respective adjacent side edges of the first frame section. In this case, there are thus two flow channels that are opposite each other and thereby advantageously influence the flow conditions in the plane with the frame and the turbulator.

[0081] As an alternative to the aforementioned first refinement, a second refinement of the aforementioned plate heat exchanger design is proposed, in which flow channels are located between all outer edges of the turbulator and the adjacent side edges of the first frame section. In this case, flow channels are present on all four side edges of the frame, meaning a total of four flow channels.

[0082] In cases where more than one flow channel is provided in the same plane as the frame and the turbulator, the outer edges of the turbulator can, in principle, have the same or a different curved, arc-shaped, or wave-shaped form. It is therefore possible to have all curved, arc-shaped, or wave-shaped outer edges. 00159604-0029 18.11.2025 PCT / DE0efi^|ößffi115

[0083] 1S-.11 -'2025-00159 04-0029

[0084] 16

[0085] edges of the turbulator should be formed in the same way, but instead, different shapes of the outer surfaces or outer edges of the turbulator can also be used.

[0086] Advantageously, a design of the aforementioned plate heat exchangers is specified in which the outer edge(s) of the turbulator is / are curved or arc-shaped, wherein the outer edge(s), viewed from the center of the flow chamber, is / are either convex or concave. This is therefore a specific curve or arc shape, namely a convex or concave shape of the outer edge(s) of the turbulator, whereby it also applies here that, in the case of more than one flow channel, the outer edges of the turbulator either all have the same shape, i.e., are convex or concave, or each has different shapes, that is, for example, two outer edges are convex and the other two outer edges are concave.

[0087] According to an advantageous embodiment of the plate heat exchanger described above with the features of claim 10, an additional turbulator segment is provided between the flow channel and the inner surface of the inner edge of the first frame section, which abuts the inner surface of the inner edge of the first frame section and extends from one of the collecting channels located there towards the collecting channel located at the other end of this inner edge, wherein the side edge of this additional turbulator segment facing the flow channel is either straight or curved or arc-shaped or wavy and thus lies at an acute angle to the adjacent side edge of the first frame section, such that the flow channel thus formed has a substantially triangular shape.In this design, the frames of the plate heat exchanger are given to 00159604-0030 18.11.2025 PCT / DE0S£^|ößffi115.

[0088] 1®” II -2Ö2B- OO153S04-OO3Ü

[0089]

[0090] 17

[0091] To improve heat transfer performance, at least one so-called turbulator segment is used. Depending on their design, shape, and position, these turbulator segments cause a different flow behavior of the media in the respective frame plane of the plate heat exchanger. The turbulator segments can, in particular, also be designed with corrugated fin-shaped turbulator elements running parallel to each other, as already described above in connection with other embodiments, but the design and shape of the turbulator segments are not limited to this. In the aforementioned embodiment, a flow channel is provided that on one side is bounded by the straight outer edge of the turbulator and on the other side by the side edge of the additional turbulator segment, whereby this side edge can, in principle, have any shape.This means that the side edge of the additional turbulator segment is either odd, i.e., curved, arc-shaped, or wavy, or, like the outer edge of the turbulator, straight. In the latter case, the side edge lies at an acute angle to the adjacent side edge of the first frame section, and the resulting flow channel consequently has an essentially triangular shape. The specific choice of shape and position of the various side edges advantageously influences the flow behavior of the media.

[0092] The same applies to an advantageous further development of the plate heat exchanger with the features of claim 15 and the characterizing features of claim 20, according to which the plate heat exchanger has a flow channel which is bounded on one side by an outer edge of the turbulator which, in contrast to the embodiment described above, is not straight but curved or arc-shaped or wave-shaped, and additionally at least one turbulator. 00159604-0031 18.11.2025 PCT / DE0S£^|ööffi115

[0093] 1

[0094] 18

[0095] The design options for this turbulator segment, already explained above, also apply to the present embodiment, so reference is made to the above explanations to avoid repetition. It is understood that additional turbulator segments can be provided in the area of ​​all four side edges of a frame, but also only on one side edge, or on two or three side edges of the frame, with different flow effects resulting depending on the selection. This also applies to the possibility of equipping the individual frames within the plate heat exchanger with additional turbulator segments differently. Numerous possibilities exist here, including varying the number, shape, and position of the individual turbulator segments within the frames of the plate heat exchanger.The invention is therefore not limited to specific embodiments.

[0096] Based on this, the present invention relating to the plate heat exchanger in frame construction also includes various other possible combinations. This applies in particular to the combination solutions according to claims 21, 22, 23, and 24. These four combination solutions are similar in that they relate to plate heat exchangers which, on the one hand, have turbulators whose corrugated fin-shaped elements are arranged at an angle to the longitudinal side edges of the first frame section, and, on the other hand, have at least one of the flow channels already described above. This combination of angled turbulators and flow channels leads to further favorable flow effects for the media flowing through the plate heat exchanger, whereby, here too, the respective flow effects depend on the specific selection or design of the individual components. 00159604-0032 18.11.2025 PCT / DE0S£^|ößffi115

[0097] 19

[0098] The invention proposes, as a first combined solution, a generic plate heat exchanger with the features of claim 5, that is, an advantageous further development of the plate heat exchanger according to claim 5. In order to realize or improve its flow behavior differently, a plate heat exchanger with the characterizing features of claim 21 is proposed according to the invention in such a way that the turbulator extends only over a partial area of ​​the flow chamber, wherein at least between an outer surface of a straight outer edge of the turbulator and the inner surface of the adjacent inner edge of the first frame section of the frame there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber, through which the medium can flow and thus forms a flow channel.This plate heat exchanger combines the already advantageous fluid dynamic effects of the angular arrangement of the turbulator elements and the flow channel(s), as described above. This combination results in even better uniformity of the flow velocity of the medium across the entire surface of the frame.

[0099] The same applies to the second combination solution for a plate heat exchanger with the features of claim 22. The difference between the first and second combination solutions according to claims 21 and 22 is only that in the first combination solution the outer edge of the turbulator is straight, while in the second combination solution this outer edge is not straight, but curved, arc-shaped, or wavy. 00159604-0033 18.11.2025 PCT / DE0S£^|ößffi115

[0100] 18"11

[0101]

[0102] 20

[0103] In contrast, the invention also proposes plate heat exchangers according to the third and fourth combination solutions, in which at least one additional turbulator segment is arranged between the turbulator and the flow channel. In these two combination solutions, the advantageous flow effects of the angularly arranged turbulators, the flow channels, and the additional turbulator segments are combined or superimposed, resulting in different and favorable flow effects and thus also improved heat transfer effects.The third combination solution provides that an additional turbulator segment is located between the flow channel and the inner surface of the inner edge of the first frame section, which rests against the inner surface of the inner edge of the first frame section and extends from one of the collecting channels located there towards the collecting channel located at the other end of this inner edge, wherein the side edge of this additional turbulator segment facing the flow channel is either curved or arc-shaped or wavy, or is straight and thus lies at an acute angle to the adjacent side edge of the first frame section, such that the flow channel thus formed has an essentially triangular shape.

[0104] Alternatively, the fourth combination solution provides a plate heat exchanger in which an additional turbulator segment is located between the flow channel and the inner surface of the inner edge of the first frame section, which rests against the inner surface of the inner edge of the first frame section and extends from one of the existing collecting channels towards the collecting channel located at the other end of this inner edge, wherein the side edge of this additional 00159604-0034 18.11.2025 PCT / DE0S£^|ööffi115

[0105] IS- 11 - 2. Q2E~ßO;r5ä'fi:04-0034

[0106] 21

[0107] The turbulator segment is straight, curved or arc-shaped, or wave-shaped.

[0108] The use of one or more turbulator segments (s) in the variants according to the third and fourth combination solutions, respectively, leads to a different flow behavior of the media compared to the other variants described above and belonging to the invention. This is because the flow properties of the fluids are fundamentally influenced by three factors: the angularly arranged turbulator elements, the presence of one or more flow channels, and the arrangement of one or more turbulator segments in a frame. These three main factors or characteristics can, in turn, be varied in individual cases by selecting the angular dimension of the turbulator elements, the size or area and shape of the flow channels, and the design of the turbulator segments.

[0109] Finally, an advantageous further development of the aforementioned embodiments of the plate heat exchanger according to the invention with turbulator segments is provided, wherein the turbulator segment(s) (e) and the turbulator are designed with corrugated rib-shaped elements that run parallel to each other and are arranged at an angle to the longitudinal side edges of the first frame section of the frame, wherein this angle is formed between the longitudinal direction of the corrugated rib-shaped elements of the respective turbulator segment and one of the two longitudinal side edges of the first frame section of the frame and is between 2° and 88°, and the angle and orientation of the corrugated rib-shaped elements of the turbulator and the additional turbulator segment(s) are the same or different.In this case, the additional turbulator segments therefore look in principle like the turbulator arranged in the relevant frame, that is, they exhibit 00159604-0035 18.11.2025 PCT / DE0S£^|ößffi115.

[0110] J B- 11 -2025- W15ÄßO<-O0B5

[0111]

[0112] 22

[0113] The familiar rib shape is used. It is therefore possible to design the angle, orientation, and spacing of the corrugated rib elements of the turbulator and the additional turbulator segments in the same or different ways, depending on the desired flow behavior. This advantageous design also allows for consistent or different application within the individual frames of the plate heat exchanger; that is, the individual features, such as the angle of the corrugated rib elements, their parallel spacing, the shape and size or area of ​​the flow channels, and the shape, position, and arrangement of the turbulator segments, can be selected according to the desired flow effect.

[0114] It should also be noted that the flow behavior of the fluids, and thus the heat transfer performance, in plate heat exchangers according to the four combination solutions described above can be influenced by numerous factors and parameters, such as the size or area of ​​the flow channel and its shape. Furthermore, the choice of the angle of the corrugated fin elements of the turbulator affects the flow behavior within the frame. This is particularly true if the turbulator segment(s) used, like the turbulator itself, consists of corrugated fin elements spaced parallel to each other, and these corrugated fin elements of the turbulator segment are also arranged at an angle to the longitudinal edges of the first frame section.

[0115] It should also be mentioned at this point that the invention does not fundamentally include any specification as to the height of the turbulators and / or the possibly existing 00159604-0036 18.11.2025 PCT / DE0S£^|ööffi115

[0116] 1 SI l~2Q25“0Ü1596D4“003ß

[0117]

[0118] 23

[0119] The invention comprises turbulator segments. Normally, the turbulators and the additional turbulator segments would have the same height, but the invention also includes the possibility of designing the turbulators and any additional turbulator segments completely or partially at different heights in order to achieve other, potentially improved, flow effects. This also includes the possibility of selecting the same or different spacing between individual wave-ribbed turbulator elements, which also leads to different flow conditions.

[0120] Having described above the embodiments of the plate heat exchanger according to the invention in frame construction, the corresponding embodiments of the plate heat exchanger according to the invention in the shell construction already described above will now be explained. Apart from the differences between the frame and shell construction already described above, these two constructions are otherwise essentially the same, so that, to avoid repetition, reference is generally made to the preceding description with regard to the frame construction. The description of the plate heat exchangers according to the invention in frame construction can therefore, in principle, be applied analogously to the plate heat exchangers according to the invention in shell construction. Nevertheless, the following details will be provided regarding the embodiments of the plate heat exchanger according to the invention in shell construction.

[0121] The invention thus also relates to a plate heat exchanger with a number of shells arranged in a stacked manner above one another, wherein 00159604-0037 18.11.2025 PCT / DE0S£^ößffi115

[0122] IB- 1.1 '-aü25” lB9604^0D37

[0123] 24

[0124] - the bowls have a trough-shaped form such that they have a base plate and side walls located at its side edges,

[0125] - an upper end plate and / or a lower end plate is or are provided,

[0126] - the upper end plate rests on the side walls of the uppermost shell and covers them,

[0127] - the lower end plate rests against the underside of the base plate of the lowest shell and covers it,

[0128] - between two adjacent shells, as well as between the upper end plate and the uppermost shell and / or between the lower end plate and the lowest shell, there is a medium-carrying medium passage for the passage of at least two different media,

[0129] - the upper or lower end plate or both end plates each have inlets for feeding the media into the medium passages and outlets for removing the media from the medium passages,

[0130] - the base plate of each shell has at least four passages for the passage of media, aligned with the aforementioned inlets and outlets of the end plate, two of which passages are surrounded on the upper side of the base plate by annular protrusions or rings on which the underside of the base plate of the shell arranged above rests, so that these two passages are closed in the assembled or operating state of the plate heat exchanger, 00159604-0038 18.11.2025 PCT / DE0S£^|ößffi115

[0131] 1.8-11 “ 025“ ; OÜI5860-^-OÖ38

[0132] 25

[0133] — the shells and the upper and lower end plates are of the same size and have a rectangular or square shape with four straight edges, two of which are parallel to each other and two of which are perpendicular to these long edges and also parallel to each other,

[0134] — the space formed in the assembled or operating state of the plate heat exchanger between the spaced-apart base plates of two superimposed shells forms a flow chamber serving as a medium passage and

[0135] — a turbulator equipped with turbulator elements is arranged in the flow chamber of at least one shell.

[0136] It was already mentioned at the outset that a plate heat exchanger of the aforementioned type in shell construction is known from DE 10 2009 041 526 A1 and is referred to there as a plate heat exchanger. This plate heat exchanger has special design features to prevent the mixing of the liquid media and thus increase the operational reliability of the plate heat exchanger. In particular, the known plate heat exchanger reduces the risk of damage to an associated combustion engine, since an additional seal is provided between the first fluid and the second fluid.Although this plate heat exchanger also provides for the use of a turbulence element, for example in the form of a turbulence plate, to ensure uniform turbulence of the fluids or media during flow through the plate heat exchanger in operation, DE 10 2009 041 526 A1 does not disclose any details on how this turbulence element 00159604-0039 18.11.2025 PCT / DE0S£^|ööffi115.

[0137] IB- 1 l--Ä02S“©035S604- 0019

[0138] 26

[0139] The appearance and flow behavior of the media or fluids in this plate heat exchanger are unclear, especially since the turbulence element is not shown in the drawings of DE 10 2009 041 526 Al. The plate heat exchanger according to DE 10 2009 041 526 Al therefore has the disadvantage that the flow conditions prevailing within it are not optimal.

[0140] The present invention relating to a plate heat exchanger in shell construction is therefore also based on the objective of improving it in such a way that a more favorable flow behavior of the media is achieved during the operation of the plate heat exchanger and thus ultimately its effectiveness or efficiency is increased.

[0141] This problem is solved according to the invention with a plate heat exchanger of the generic type in that the turbulator elements are corrugated, run at parallel distances from each other and extend over the entire area or a part of the flow chamber, and that these corrugated elements of the turbulator are not arranged perpendicular or parallel, but at an angle to the longitudinal side edges of the shell, wherein this angle is formed between the longitudinal direction of the corrugated turbulator elements and one of the two longitudinal side edges of the shell and is between 2° and 88°.

[0142] This plate heat exchanger according to the invention, also in a shell design, initially has the advantage that the flow behavior is more homogeneous overall, resulting in more uniform heat transfer. The angled arrangement of the corrugated turbulator elements facilitates the longitudinal and transverse flow through the turbulator. This leads to better or more favorable flow conditions. 00159604-0040 18.11.2025 PCT / DE0S£^|ößffi115

[0143] 1-2O25^OO1596Q4-:0O<Ö

[0144]

[0145] 27

[0146] The inventive alignment of the turbulator elements results in a homogenization of the pressure conditions or pressure equalization in the relevant plane with the shell in which the turbulator is located. The aforementioned angular alignment of the corrugated fin-shaped elements of the turbulator, as described above, is to be understood and provided for in the shell-type plate heat exchanger design in the same way as in the frame-type plate heat exchanger design described above, so that, to avoid repetition, reference is made to the above explanations. Accordingly, advantageous shell-type plate heat exchangers according to the invention are specified in claims 27 to 34. In principle, these designs offer the same advantages as the corresponding frame-type plate heat exchanger design.

[0147] Apart from the plate heat exchangers with angularly arranged turbulator elements described above, the invention also relates to a plate heat exchanger in shell construction according to the preamble of claim 35, which is also known from the aforementioned DE 10 2009 041 526 A1, so that, in order to avoid repetition, reference is made to the above statements in this regard, in particular to the problem already formulated, namely to achieve a more favorable flow behavior of the media during the operation of the plate heat exchanger in order to ultimately increase its effectiveness or efficiency.

[0148] This problem is solved according to the invention with a plate heat exchanger of the generic type also with the characterizing features of claim 35 in that the turbulator extends only over a partial area of ​​the flow chamber, wherein at least between an outer surface of a straight outer edge of the turbulator and the inner surface 00159604-0041 18.11.2025 PCT / DE0S£^ / |ößffi115

[0149] .1

[0150] 28

[0151] The adjacent side wall of the shell contains an open or unobstructed area, meaning it does not completely fill the flow chamber, through which the medium can flow, thus forming a flow channel. This shell-type plate heat exchanger according to the invention also provides one or more flow channels in the same plane as a frame and a turbulator arranged therein. Therefore, when the media enters the plane of a frame, they flow not only through the turbulator but also through the flow channel(s). As already explained above with regard to the frame-type plate heat exchangers, the presence of at least one flow channel also leads to an improved flow situation in the relevant flow plane for the shell-type plate heat exchanger variant described here.Therefore, to avoid repetition, reference is made to the above explanations regarding the plate heat exchanger in frame construction. The same applies to the advantageous embodiments of the aforementioned plate heat exchanger in shell construction with at least one flow channel according to claims 36 to 39.

[0152] Apart from the plate heat exchangers described above with a flow channel that is bounded on one side by the outer surface of a straight outer edge of the turbulator, the invention also includes another embodiment of the plate heat exchanger in a shell construction according to the preamble of claim 40, in which, to solve the problem already formulated above, it is proposed according to the invention that the turbulator extends only over a partial area of ​​the flow chamber, wherein at least between an outer surface of an outer edge of the turbulator, which is curved, arcuate, or wave-shaped, and the inner surface of the adjacent side wall of the shell, there is an open or

[0153] 1.11

[0154] 29

[0155] The free area, meaning the flow chamber is not completely filled, allows the medium to flow through it, thus forming a flow channel. Analogous to the corresponding design in frame construction, the curved, arc-shaped, or wave-like shape of the turbulator's outer edge results in a different flow behavior of the medium as it flows through the resulting flow channel. Here too, the curved or arc-shaped form, like the wave-like shape of the outer edge, is not specifically defined but can be selected depending on the desired flow behavior.

[0156] Advantageous further developments of the aforementioned embodiment of the plate heat exchanger with a flow channel, in which the outer surface of an outer edge of the turbulator is curved, arcuate, or wave-shaped, are provided for in claims 41 to 43. Analogous to the corresponding further developments of this embodiment for the plate heat exchanger in frame construction, the technical advantages also apply to the present embodiment of the plate heat exchanger in shell construction, so reference is also made to the above statements regarding this.

[0157] The foregoing also applies to an advantageous embodiment of the plate heat exchanger with a flow channel described above according to claim 35, in which an additional turbulator segment is located between the flow channel and the inner surface of the side wall of the shell, the turbulator segment bearing against the inner surface of the side wall of the shell and extending from one of the passages located there towards the passage located at the other end of this side wall, wherein the side edge of this additional turbulator segment facing the flow channel is either curved or flat.

[0158] 30

[0159] The flow channel is shaped in a curved or wave-like form, or is straight and thus lies at an acute angle to the adjacent side wall of the shell, such that the flow channel thus formed has a substantially triangular shape. In addition to at least one flow channel, at least one so-called turbulator segment is used, resulting in a different flow behavior in the respective shell of a plate heat exchanger. The same applies to an advantageous further development of the aforementioned plate heat exchanger in shell construction with the features of claim 45. This also results in the advantages regarding the flow conditions already explained in relation to the corresponding embodiments of the plate heat exchanger in frame construction, so reference is made to the above explanations in this regard to avoid repetition.

[0160] Based on this and analogous to the already described and included plate heat exchangers in frame construction, the present invention relating to the plate heat exchanger in shell construction also includes various other combination possibilities. This applies in particular to the combination solutions according to claims 46, 47, 48 and 49. These four combination solutions correspond in principle to the four combination solutions according to claims 21, 22, 23 and 24 of the plate heat exchanger in frame construction, so that, in order to avoid repetition regarding the design, possible variations and advantages, reference is made to the above statements in this regard.This also applies to the advantageous further development of the embodiments of the plate heat exchangers designated as combination solutions according to claims 44, 45, 48 and 49, in which the additional turbulator segment(s) (e) is or are also designed with corrugated fin-shaped elements running parallel to each other and these at an angle to the longitudinal side edges 00159604-0044 18.11.2025 PCT / DE0S£ / |ößffi115.

[0161] Wl 1-2Q25~OO153۩4-0O44

[0162]

[0163] 31

[0164] the shell is arranged, wherein this angle is formed between the longitudinal direction of the corrugated rib elements of the respective turbulator segment and one of the two longitudinal side edges of the shell and is between 2° and 88°, and the angle and orientation of the corrugated rib elements of the turbulator and the additional turbulator segment(s) are either the same or different. Reference is also made in this respect to the corresponding explanations concerning the possibilities and advantages of using such additional turbulator segments, as already explained above with regard to the plate heat exchangers according to the invention in frame construction.

[0165] The invention is not limited to the embodiments mentioned and shown, as different arrangements of the connections are conceivable, for example, to achieve different flow patterns of the media. The invention therefore also includes variants of the plate heat exchangers of the aforementioned generic types, which have a design suitable for X-, I- or U-shaped flow and / or for meandering or multi-meandering flow of the media.

[0166] Finally, the invention comprises plate heat exchangers according to the aforementioned claims, in which the media are preferably liquids and / or gases.

[0167] Exemplary embodiments of the invention are explained in more detail below with reference to the schematic drawings. These show

[0168] Figs. 1a and 1b are isometric views from two different perspectives of a first embodiment of a plate heat exchanger according to the invention and designed for X-flow in frame construction 00159604-0045 18.11.2025 PCT / DE0S£^|ößffi115

[0169] IB- 11 "io2s-oo:mw -©o<5

[0170] 32

[0171] with several stacked frames arranged one above the other and containing turbulators with angularly arranged turbulator elements,

[0172] Fig. 2a shows a top view of the end plate of the plate heat exchanger shown in Figs. 1a and 1b,

[0173] Fig. 2b shows a side view of a narrow side of the plate heat exchanger according to Figs. 1a and 1b.

[0174] Fig. 2c shows a side view of a longitudinal side of the plate heat exchanger according to Figs. 1a and 1b.

[0175] Fig. 3 is a perspective exploded view of the plate heat exchanger according to Figs. 1a and 1b.

[0176] Fig. 4 shows a further perspective exploded view of the plate heat exchanger shown in Fig. 3, corresponding to the exploded view of Fig. 3, with arrows drawn therein illustrating the flow of media M1 and M2.

[0177] Fig. 5 is a schematic diagram illustrating the flow of media M1 and M2 through the plate heat exchanger shown in Figs. 1a and 1b, 2a, 2b and 2c, 3 and 4, 00159604-0046 18.11.2025 PCT / DEflS^ / |ößffi115

[0178] I - 11 -2©25-00159fi(H-©04€

[0179] 33

[0180] Fig. 6 shows a perspective view of a partition plate of the plate heat exchanger shown in Figs. 1a and 1b, 2a, 2b and 2c, 3 and 4.

[0181] Fig. 7a shows a top view of the partition plate shown in Fig. 6.

[0182] Fig. 7b shows a side view of a longitudinal edge of the partition plate shown in Fig. 7a.

[0183] Fig. 7c shows a side view of a narrow edge of the partition plate shown in Fig. 7a,

[0184] Fig. 8 is a perspective view of a frame that is shown in Figs. 1a and 1b, Fig.

[0185] The plate heat exchanger shown in Figures 3 and 4, 2a, 2b and 2c, is used.

[0186] Fig. 9a shows a top view of the frame shown in Fig. 8,

[0187] Fig. 9b shows a side view of a longitudinal side edge of the frame shown in Fig. 9a,

[0188] Fig. 9c shows a side view of a narrow side edge of the frame shown in Fig. 9a,

[0189] Fig. 10 shows a top view of the frame shown in Fig. 8 and Figs. 9a, 9b and 9c with a turbulator contained therein, des- 00159604-0047 18.11.2025 PCT / DE0S£^|ößffi115

[0190] 19-11 Wl'59604-0 047

[0191]

[0192] 34

[0193] The wave-ribbed elements are arranged at an angle of 25° to the longitudinal side edges of the frame,

[0194] Fig. 11 shows a top view of another embodiment of a frame provided for a plate heat exchanger according to the invention in frame construction with a turbulator, the wave-ribbed elements of which are arranged at an angle of 45° to the longitudinal side edges of the frame,

[0195] Fig. 12 shows a top view of another embodiment of a frame provided for a plate heat exchanger according to the invention in frame construction with a turbulator, the wave-ribbed elements of which are arranged at an angle of 55° to the longitudinal side edges of the frame,

[0196] Fig. 13 shows a representation corresponding to Fig. 10 of the frame shown in Fig. 10 and the turbulator contained therein, with a simplified representation of the corrugated rib-shaped elements of the turbulator, which are arranged at an angle of 25° to the longitudinal side edges of the frame.

[0197] Fig. 14 shows a sectional view along the section line AB shown in Fig. 13 of the frame and turbulator shown in Fig. 13.

[0198] Fig. 15 shows a side view of one longitudinal side of the [part] shown in Figs. 1a and 1b as well as Figs. 2a, 2b and 00159604-0048 18.11.2025 PCT / DE0S£ / |ößffi115

[0199] 35

[0200] 2c shows the design form of the plate heat exchanger in its assembled state,

[0201] Figs. 16a and 16b

[0202] two enlarged section views of the corner area of ​​the plate heat exchanger marked with a circle in Fig. 15, with Fig. 16a showing a perspective view and Fig. 16b a side view of this corner area,

[0203] Fig. 17 shows a perspective view of another embodiment of a turbulator suitable for a plate heat exchanger in frame construction according to the invention, the corrugated fin-shaped elements of which are arranged at an angle of 20° to the longitudinal side edges of the frame.

[0204] Fig. 18a shows a top view of the turbulator shown in Fig. 17,

[0205] Fig. 18b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 18a,

[0206] Fig. 18c shows a side view of a narrow side edge of the turbulator shown in Fig. 18a,

[0207] Fig. 19 shows a perspective and more detailed view of the turbulator shown in Figs. 17 and 18a, b and c, corresponding to Fig. 17, 00159604-0049 18.11.2025 PCT / DE0S£^|ööffi115

[0208] 36

[0209] Fig. 20a shows a top view of the turbulator shown in Fig. 17,

[0210] Fig. 20b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 18a,

[0211] Fig. 20c shows a side view of a narrow side edge of the turbulator shown in Fig. 18a,

[0212] Fig. 21a shows a perspective exploded view of a further embodiment of a plate heat exchanger according to the invention and designed for inertial flow in a frame construction with several stacked frames arranged one above the other and turbulators contained therein with angled turbulator elements.

[0213] Fig. 21b shows a further perspective exploded view of the plate heat exchanger shown in Fig. 21a, corresponding to the exploded view of Fig. 21a, with arrows drawn therein illustrating the flow of media M1 and M2.

[0214] Fig. 22a shows a perspective view of a frame used in the plate heat exchanger shown in Figs. 21a and 21b.

[0215] Fig. 22b shows a top view of the frame shown in Fig. 22a,

[0216] Fig. 22c shows a side view of a longitudinal side edge of the frame shown in Fig. 22b, 00159604-0050 18.11.2025 PCT / DE0S£^|ößffi115

[0217] IB- 11-3025- O 9B04-0050

[0218] 37

[0219] Fig. 22d shows a side view of a narrow side edge of the frame shown in Fig. 22b,

[0220] Fig. 23 is a top view of one shown in the Fig.

[0221] 21a and b and Fig. 22, frame with a turbulator contained therein, which consists of two turbulator segments, the wave-ribbed elements of which are each arranged at an angle of 15° to the longitudinal side edges of the frame,

[0222] Fig. 24 is a top view of one shown in the Fig.

[0223] 21a and b as well as 22a, b, c and d frame with a turbulator contained therein, which consists of two turbulator segments, the wave-ribbed elements of which are each arranged at an angle of 30° to the longitudinal side edges of the frame,

[0224] Fig. 25 is a top view of one shown in the Fig.

[0225] 21a and b as well as 22a, b, c and d frame with a turbulator contained therein, which consists of two turbulator segments, the wave-ribbed elements of which are each arranged at an angle of 45° to the longitudinal side edges of the frame,

[0226] Fig. 26 shows a perspective exploded view of a further embodiment of a plate heat exchanger according to the invention and designed for U-flow in frame construction with several frames arranged stacked on top of each other and therein 00159604-0051 18.11.2025 PCT / DE0S£ / |ößffi115

[0227] '1 1

[0228] 38

[0229] contained turbulators with angularly arranged turbulator elements,

[0230] Fig. 27 shows a further perspective exploded view of the plate heat exchanger shown in Fig. 26, corresponding to the exploded view of Fig. 26, with arrows drawn therein illustrating the flow of media M1 and M2.

[0231] Fig. 28 is a schematic diagram illustrating the flow of media M1 and M2 through the plate heat exchanger shown in Figs. 26 and 27.

[0232] Fig. 29 shows a perspective view of a frame used in the plate heat exchanger shown in Figs. 26 and 27.

[0233] Fig. 30a shows a top view of the frame shown in Fig. 29,

[0234] Fig. 30b shows a side view of a longitudinal side edge of the frame shown in Fig. 30a,

[0235] Fig. 30c shows a side view of a narrow edge of the frame shown in Fig. 30a,

[0236] Fig. 31 shows a top view of the frame shown in Fig. 29 and Figs. 30a, 30b and 30c, containing a turbulator consisting of two turbulator segments. 00159604-0052 18.11.2025 PCT / DE0S£^|ößffi115

[0237] 18-1 l-20t5-0010fi04~ü052

[0238]

[0239] 39

[0240] stands, whose wave-ribbed elements are each arranged at an angle of 20° to the longitudinal side edges of the frame,

[0241] Fig. 32 shows a top view of the frame shown in Fig. 29 and Figs. 30a, 30b and 30c, containing a turbulator consisting of two turbulator segments whose corrugated rib elements are each arranged at an angle of 30° to the longitudinal side edges of the frame.

[0242] Fig. 33 shows a top view of the frame shown in Fig. 29 and Figs. 30a, 30b and 30c, containing a turbulator consisting of two turbulator segments whose corrugated rib elements are each arranged at an angle of 40° to the longitudinal side edges of the frame.

[0243] Fig. 34 shows a perspective view of another embodiment of a turbulator designed for U-shaped flow through a frame-type plate heat exchanger according to the invention, and whose corrugated fin-shaped elements are arranged at an angle of 20°. 0 are arranged along the long side edges of the frame,

[0244] Fig. 35a shows a top view of the turbulator shown in Fig. 34,

[0245] Fig. 35b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 35a, 00159604-0053 18.11.2025 PCT / DE0g)^|ÖQ®115

[0246] 11 =2na5“'001 ; SSR04-© 053

[0247]

[0248] 40

[0249] Fig. 35c shows a side view of a narrow side edge of the turbulator shown in Fig. 35a,

[0250] Fig. 36 shows a perspective exploded view of an embodiment of a plate heat exchanger according to the invention and designed for X-flow in frame construction with several stacked frames arranged one above the other and containing turbulators and flow channels.

[0251] Fig. 37 shows a further perspective exploded view of the plate heat exchanger shown in Fig. 36, corresponding to the exploded view of Fig. 36, with arrows drawn therein illustrating the flow of media M1 and M2.

[0252] Fig. 38 shows a schematic diagram illustrating the flow of media M1 and M2 through the plate heat exchanger shown in Figs. 36 and 37.

[0253] Fig. 39 shows a perspective view of a turbulator used in the plate heat exchanger according to Figs. 36 and 37.

[0254] Fig. 40a shows a top view of the turbulator shown in Fig. 39,

[0255] Fig. 40b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 40a,

[0256] Fig. 40c shows a side view of a narrow side edge of the turbulator shown in Fig. 40a, 00159604-0054 18.11.2025 PCT / DE0S£^|ößffi115

[0257] 1.8- Il -2O25-.ÖD1O604-O054

[0258]

[0259] 41

[0260] Fig. 41 shows a perspective and more detailed view of the turbulator shown in Figs. 39 and 40a, b and c, corresponding to Fig. 39.

[0261] Fig. 42a shows a top view of the turbulator shown in Fig. 41,

[0262] Fig. 42b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 42a,

[0263] Fig. 42c shows a side view of a narrow side edge of the turbulator shown in Fig. 42a,

[0264] Fig. 43 shows a perspective view corresponding to the representation in Fig. 41 of the turbulator shown in Fig. 41 and of a frame surrounding this turbulator,

[0265] Fig. 44a shows a top view of the frame shown in Fig. 43 and the turbulator arranged therein,

[0266] Fig. 44b shows a side view of a longitudinal side edge of the frame shown in Fig. 44a,

[0267] Fig. 44c shows a side view of a narrow side edge of the frame shown in Fig. 44a,

[0268] Fig. 45 shows a side view of a longitudinal side of the embodiment of the plate heat exchanger shown in Figs. 36 and 37 in the assembled state, 00159604-0055 18.11.2025 PCT / DE0S£^|ößffi115

[0269] 18-1 l”2Ü25-001'59ß0 -OOSS

[0270] 42

[0271] Figs. 46a and 46b

[0272] two enlarged section views of the corner area of ​​the plate heat exchanger marked with a circle in Fig. 45, with Fig. 46a showing a perspective view and Fig. 46b a side view of this corner area,

[0273] Fig. 47 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has straight outer edges, for a plate heat exchanger according to the invention with two flow channels.

[0274] Fig. 48 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has straight outer edges, for a plate heat exchanger according to the invention with four flow channels.

[0275] Fig. 49 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has straight outer side edges, for a plate heat exchanger according to the invention with four triangular flow channels.

[0276] Fig. 50 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has curved or arc-shaped outer edges, all of which are concave, for a 00159604-0056 18.11.2025 PCT / DE0S£^ / |ößffi115

[0277] 38-31-2025- 00159604'-Ö05G

[0278] 43

[0279] Plate heat exchanger according to the invention with four flow channels,

[0280] Fig. 51 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has curved or arc-shaped outer edges, wherein two outer edges are concavely curved and two outer edges are convexly curved, for a plate heat exchanger according to the invention with four flow channels.

[0281] Fig. 52a shows a top view of a frame and another embodiment of a turbulator arranged therein, which has curved or arc-shaped outer edges, wherein two outer edges are concavely curved and two outer edges are convexly curved, for a plate heat exchanger according to the invention with four flow channels.

[0282] Fig. 52b shows a sectional view along the section line shown in Fig. 52a.

[0283] A - B of the frame and turbulator shown in Fig. 52a,

[0284] Fig. 52c is an enlarged (scale 1:2) and detailed representation of the sectional view of Fig. 52b,

[0285] Fig. 53 shows a perspective exploded view of an embodiment of an invention- 00159604-0057 18.11.2025 PCT / DE0S£^|ößffi115

[0286] IS-11 “2025” ÖO 159604-W57

[0287]

[0288] 44

[0289] plate heat exchanger in frame construction designed for X-flow with several stacked frames arranged one above the other and turbulators contained therein with angularly arranged turbulator elements, which are provided in combination with flow channels,

[0290] Fig. 54 shows a further perspective exploded view of the plate heat exchanger shown in Fig. 53, corresponding to the exploded view of Fig. 53, with arrows drawn therein illustrating the flow of media M1 and M2.

[0291] Fig. 55 shows a perspective view of a turbulator used in the plate heat exchanger according to Figs. 53 and 54,

[0292] Fig. 56a shows a top view of the turbulator shown in Fig. 55,

[0293] Fig. 56b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 56a,

[0294] Fig. 56c shows a side view of a narrow side edge of the turbulator shown in Fig. 56a,

[0295] Fig. 57 shows a perspective and more detailed view of the turbulator shown in Figs. 55 and 56a, b and c, corresponding to Fig. 55.

[0296] Fig. 58a a top view of the turbulator shown in Fig. 57, 00159604-0058 18.11.2025 PCT / DE0S£^|ööffi115

[0297] Fig. 58b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 58a,

[0298] Fig. 58c shows a side view of a narrow side edge of the turbulator shown in Fig. 58a,

[0299] Fig. 59 shows a side view of a longitudinal side of the embodiment of the plate heat exchanger shown in Figs. 53 and 54 in the assembled state.

[0300] Figs. 60a and 60b

[0301] two enlarged section views of the corner area of ​​the plate heat exchanger marked with a circle in Fig. 59, with Fig. 60a showing a perspective view and Fig. 60b a side view of this corner area,

[0302] Fig. 61 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has angularly (25°) arranged turbulator elements and straight outer edges, for a plate heat exchanger according to the invention with four flow channels,

[0303] Fig. 62 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has angularly arranged turbulator elements and straight outer edges, for a plate heat exchanger according to the invention with four triangular flow channels, 00159604-0059 18.11.2025 PCT / DE0S£^|ößffi115

[0304] .18-1

[0305]

[0306] 46

[0307] Fig. 63 shows a sectional view along the section line A - B of the frame and turbulator shown in Fig. 62, as shown in Fig. 62.

[0308] Fig. 64a shows a top view of a frame and another embodiment of a turbulator arranged therein, which has angularly arranged turbulator elements and curved or arcuate outer edges, wherein two outer edges are concavely curved and two outer edges are convexly curved, for a plate heat exchanger according to the invention with four flow channels.

[0309] Fig. 64b shows a sectional view along the section line shown in Fig. 64a.

[0310] A - B of the frame and turbulator shown in Fig. 64a,

[0311] Fig. 64c is an enlarged (scale 1:2) and detailed representation of the sectional view of Fig. 64b,

[0312] Fig. 65 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has angled turbulator elements and curved or arcuate outer edges, all of which are concave, for a plate heat exchanger according to the invention with four flow channels, 00159604-0060 18.11.2025 PCT / DE0S£^|ößffi115

[0313] 47

[0314] Fig. 66 shows a top view of a frame containing a turbulator consisting of two turbulator segments, the angled turbulator elements of which are each arranged at an angle of 25° to the longitudinal side edges of the frame, in combination with flow channels for a plate heat exchanger in frame construction according to the invention and designed for I-flow.

[0315] Fig. 67 shows a perspective exploded view of an embodiment of a plate heat exchanger according to the invention and designed for U-flow in frame construction with several stacked frames arranged one above the other and turbulators contained therein with angularly arranged turbulator elements, which are provided in combination with flow channels.

[0316] Fig. 68 shows a further perspective exploded view of the plate heat exchanger shown in Fig. 67, corresponding to the exploded view of Fig. 67, with arrows drawn therein illustrating the flow of media M1 and M2.

[0317] Fig. 69 shows a perspective view of the turbulator used in the plate heat exchanger according to Figs. 67 and 68, whose corrugated elements are arranged at an angle of 20° to the longitudinal side edges of the frame and which has curved or arc-shaped outer edges, 00159604-0061 18.11.2025 PCT / DE0S£ / |ößffi115

[0318] 18-1

[0319] 48

[0320] Fig. 70a shows a top view of the turbulator shown in Fig. 69,

[0321] Fig. 70b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 70a,

[0322] Fig. 70c shows a side view of a narrow side edge of the turbulator shown in Fig. 70a,

[0323] Fig. 71 shows a perspective view corresponding to Fig. 69 of the turbulator shown in Fig. 69 and a frame used in the plate heat exchanger shown in Figs. 67 and 68.

[0324] Fig. 72 shows a top view of the frame and turbulator shown in Fig. 71, which has angularly arranged turbulator elements and curved or arc-shaped outer edges, wherein three outer edges are concavely curved and one outer edge is convexly curved, for a plate heat exchanger according to the invention with seven flow channels designed for U-flow.

[0325] Fig. 73 shows a perspective view of the turbulator shown in Fig. 69, corresponding to Fig. 69.

[0326] Fig. 74a a top view of the turbulator shown in Fig. 73, 00159604-0062 18.11.2025 PCT / DE0S2^ / |Qßffi115

[0327] 18- 11"ÄOÄ5-ÖOJ58BO " OD€2

[0328] 49

[0329] Fig. 74b shows a side view of a longitudinal outer edge of the turbulator shown in Fig. 74a,

[0330] Fig. 74c shows a side view of a narrow outer edge of the turbulator shown in Fig. 74a.

[0331] Fig. 75a shows a top view corresponding to the representation in Fig. 72 of the frame shown in Fig. 72 and the turbulator arranged therein,

[0332] Fig. 75b shows a sectional view along the section line AB shown in Fig. 75a of the frame and turbulator shown in Fig. 75a.

[0333] Fig. 75c is an enlarged (scale 1:2) and more detailed representation of the sectional view of Fig. 75b,

[0334] Fig. 76 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has angularly arranged turbulator elements as well as curved or arcuate outer edges, wherein all outer edges are concavely curved, for a plate heat exchanger according to the invention with seven flow channels designed for U-flow,

[0335] Fig. 77 shows a top view of a frame and another embodiment of a turbulator arranged therein, the angular 00159604-0063 18.11.2025 PCT / DE0S£^|ößffi115

[0336] 1 &-11

[0337] 50

[0338] arranged turbulator elements and straight outer edges, for a plate heat exchanger designed for U-flow according to the invention with four flow channels,

[0339] Fig. 78 shows a perspective exploded view of an embodiment of a plate heat exchanger in frame construction according to the invention and designed for X-flow, with several stacked frames arranged one above the other and turbulators contained therein with angularly arranged turbulator elements and with additional turbulator segments, which are provided in combination with flow channels.

[0340] Fig. 79 shows a further perspective exploded view of the plate heat exchanger shown in Fig. 78, corresponding to the exploded view of Fig. 78, with arrows drawn therein illustrating the flow of media M1 and M2.

[0341] Fig. 80 shows a perspective view of a frame and turbulator used in the embodiment of the plate heat exchanger shown in Figs. 78 and 79, which has angled turbulator elements and curved or arc-shaped outer edges, with two outer edges being concave and two outer edges being convex. 00159604-0064 18.11.2025 PCT / DE0S£^|ößffi115

[0342] 18-1 1 -202S-00159604-ODS4

[0343]

[0344] 51

[0345] are, as well as four additional turbulator segments for a plate heat exchanger according to the invention with four flow channels,

[0346] Fig. 81a shows a top view of the frame and turbulator shown in Fig. 80 with the additional turbulator segments,

[0347] Fig. 81b shows a side view of a longitudinal side edge of the frame shown in Fig. 81a,

[0348] Fig. 81c shows a side view of a narrow side edge of the frame shown in Fig. 81a,

[0349] Fig. 82a shows a top view corresponding to Fig. 81a of the frame and turbulator shown in Fig. 80 with the additional turbulator segments,

[0350] Fig. 82b shows a sectional view along the section line A - B shown in Fig. 82a of the section shown in Fig.

[0351] 82a frame and turbulator shown with the additional turbulator segments,

[0352] Fig. 82c is an enlarged (scale 1:2) and detailed representation of the sectional view of Fig. 82b,

[0353] Fig. 83 shows a perspective view corresponding to the representation in Fig. 80 of the turbulator and the four additional turbulator segments shown in Fig. 80, Fig. 81a, b and c and Fig. 82a, b and c, 00159604-0065 18.11.2025 PCT / DE0S£^|ößffi115

[0354] 3-2®25'“O©15 : §€04»üQ'£J5

[0355]

[0356] 52

[0357] Fig. 84a shows a top view of the turbulator shown in Fig. 83 and the additional turbulator segments,

[0358] Fig. 84b shows a side view of a longitudinal side edge of the additional turbulator segment shown in Fig. 84a,

[0359] Fig. 84c shows a side view of a narrow side edge of the additional turbulator segment shown in Fig. 84a,

[0360] Fig. 85 shows a side view of a longitudinal side of the embodiment of the plate heat exchanger shown in Figs. 68 and 69 in the assembled state,

[0361] Figs. 86a and 86b

[0362] two enlarged section views of the corner area of ​​the plate heat exchanger marked with a circle in Fig. 85, where Fig. 86a shows a perspective view and Fig. 86b a side view of this corner area,

[0363] Fig. 87 shows a perspective and more detailed view corresponding to Fig. 80 of the frame and turbulator arranged therein, as shown in Figs. 80 to 84.

[0364] Fig. 88 shows a top view of the frame and turbulator shown in Fig. 87 with the additional turbulator segments, 00159604-0066 18.11.2025 PCT / DE0S£^|ößffi115

[0365] 1 S“lr-a025-0Ü2Wß04-TOfi

[0366]

[0367] 53

[0368] Fig. 89 shows a perspective view of the turbulator shown in Figs. 80 and 88 with the additional turbulator segments.

[0369] Fig. 90 shows a top view of the turbulator shown in Fig. 89 with the additional turbulator segments,

[0370] Fig. 91 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has angularly arranged turbulator elements as well as curved or arcuate outer edges, all of which are concave, and four additional turbulator segments for a plate heat exchanger according to the invention with four flow channels.

[0371] Fig. 92 shows a top view of a frame and another embodiment of a turbulator arranged therein, which has angularly arranged turbulator elements and outer edges, all of which are straight, as well as four additional turbulator segments for a plate heat exchanger according to the invention with four flow channels.

[0372] Fig. 93 shows a perspective exploded view of an embodiment of a plate heat exchanger in frame construction according to the invention and designed for I-flow, with several stacked frames arranged one above the other and turbulators contained therein with angularly arranged turbulator elements and with additional 00159604-0067 18.11.2025 PCT / DE0g)^|ÖQ®115 l'S-1

[0373]

[0374] 54

[0375] Turbulator segments, which are intended to be used in combination with flow channels,

[0376] Fig. 94 shows a further perspective exploded view of the plate heat exchanger shown in Fig. 93, corresponding to the exploded view of Fig. 93, with arrows drawn therein illustrating the flow of media M1 and M2.

[0377] Fig. 95a shows a top view of a frame used in the embodiment of the plate heat exchanger shown in Figs. 93 and 94 and a turbulator arranged therein, which has angularly arranged turbulator elements and curved or arc-shaped outer edges, wherein two outer edges are concavely curved and two outer edges are convexly curved, as well as three additional turbulator segments for a plate heat exchanger according to the invention with three flow channels.

[0378] Fig. 95b shows a sectional view along the section line AB shown in Fig. 95a of the frame and turbulator shown in Fig. 95a.

[0379] Fig. 95c is an enlarged (scale 1:2) and more detailed representation of the sectional view of Fig. 95b,

[0380] Fig. 96 is a top view of the turbulator shown in Fig. 95a, 00159604-0068 18.11.2025 PCT / DE0S£^|ößffi115

[0381] 55

[0382] Fig. 97 is a perspective view of the area shown in Fig.

[0383] 96 shown turbulator,

[0384] Fig. 98 shows a detailed top view of the turbulator shown in Fig. 96, corresponding to Fig. 96.

[0385] Fig. 99 shows a detailed perspective view of the turbulator shown in Fig. 97, corresponding to Fig. 97.

[0386] Fig. 100 shows a more detailed top view corresponding to Fig. 95a of the frame and turbulator shown in Fig. 95a.

[0387] Fig. 101 is a perspective view of the area shown in Fig.

[0388] 100 frames and turbulator shown,

[0389] Fig. 102 shows a top view of another embodiment of the frame and the turbulator arranged therein, which has angularly arranged turbulator elements and straight outer edges, as well as three additional turbulator segments for a plate heat exchanger according to the invention with three flow channels, designed for I-flow.

[0390] Fig. 103 shows a top view of an embodiment of the frame used for U-flow plate heat exchanger in frame construction and the turbulator arranged therein, the angularly arranged turbulator elements and curved or arc-shaped outer edges. 00159604-0069 18.11.2025 PCT / DE0S£^|ößffi115

[0391] 18" 11 "2025" 0'015'9604-0089

[0392]

[0393] 56

[0394] comprising, wherein three outer edges are concavely curved and one outer edge is convexly curved, as well as five additional turbulator segments for a plate heat exchanger according to the invention with six flow channels,

[0395] Fig. 104 shows a top view of an embodiment of a frame provided according to the invention for a plate heat exchanger in frame construction and a turbulator arranged therein, which has straight outer edges, and four additional turbulator segments for a plate heat exchanger according to the invention with four triangular flow channels.

[0396] Figs. 105a and 105b

[0397] Isometric representations from two different perspectives of an embodiment of a plate heat exchanger according to the invention and designed for X-flow in shell construction with several stacked shells arranged one above the other and turbulators contained therein, which have angularly arranged turbulator elements as well as curved or arc-shaped outer edges, wherein two outer edges are concavely curved and two outer edges are convexly curved, and four flow channels,

[0398] Fig. 106a a top view of the upper end plate of the plate heat exchanger shown in Figs. 105a and 105b, 00159604-0070 18.11.2025 PCT / DE0S£^|ößffi115

[0399] 57

[0400] Fig. 106b shows a side view of a narrow side of the plate heat exchanger according to Figs. 105a and 105b,

[0401] Fig. 106c shows a side view of a longitudinal side of the plate heat exchanger according to Figs. 105a and 105b,

[0402] Fig. 107 shows a perspective exploded view of the plate heat exchanger according to the figures.

[0403] 105a and 105b,

[0404] Fig. 108 shows a further perspective exploded view of the plate heat exchanger shown in Fig. 107, corresponding to the exploded view of Fig. 107, with arrows drawn therein illustrating the flow of media M1 and M2.

[0405] Fig. 109a shows a perspective view of a shell used in the plate heat exchanger shown in Figs. 105a and 105b, Figs. 106a, 106b and 106c, Fig. 107 and Fig. 108.

[0406] Fig. 109b shows a top view of the bowl shown in Fig. 109a,

[0407] Fig. 110 shows a perspective view of a shell used in the embodiment of the plate heat exchanger shown in Figs. 103 and 104, with a turbulator arranged therein, the angled arrangement 00159604-0071 18.11.2025 PCT / DE0S£^|ößffi115

[0408] 58

[0409] Turbulator elements as well as curved or arcuate outer edges, wherein two outer edges are concavely curved and two outer edges are convexly curved, for a plate heat exchanger according to the invention with four flow channels,

[0410] Fig. 110 shows a top view of the shell with the turbulator shown in Fig. 110.

[0411] Fig. 111b shows a side view of a longitudinal edge of the bowl shown in Fig. Illa,

[0412] Fig. 111c shows a side view of a narrow edge of the bowl shown in Fig. Illa,

[0413] Fig. 112a shows a top view corresponding to the representation in Fig. Illa, showing the area shown in Fig.

[0414] The shell shown on pages 108 and 110 with the turbulator arranged therein,

[0415] Fig. 112b shows a sectional view along the section line AB shown in Fig. 112a of the shell with the turbulator shown in Fig. 112a.

[0416] Fig. 112c is an enlarged (scale 1:2) and more detailed representation of the sectional view of Fig. 112b,

[0417] Fig. 113 is a perspective view corresponding to Fig. 110 of the turbulator shown in Fig. 110, Fig. 11a, b and c and Fig. 112a, b and c, 00159604-0072 18.11.2025 PCT / DE0S£^|ößffi115

[0418] IS- 11 -2D25“001 9ßXM-0072

[0419] 59

[0420] Fig. 114a shows a top view of the turbulator shown in Fig. 113,

[0421] Fig. 114b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 114a,

[0422] Fig. 114c shows a side view of a narrow side edge of the turbulator shown in Fig. 114a,

[0423] Fig. 115 shows a perspective view corresponding to Fig. 110 of the shell shown in Fig. 110 and the turbulator arranged therein,

[0424] Fig. 116 shows a top view of the shell with the turbulator shown in Fig. 115.

[0425] Fig. 117 shows a perspective view corresponding to Fig. 115 of the turbulator shown in Figs. 115 and 116,

[0426] Fig. 118a shows a top view of the turbulator shown in Fig. 117,

[0427] Fig. 118b shows a side view of a longitudinal side edge of the turbulator shown in Fig. 118a,

[0428] Fig. 118c shows a side view of a narrow side edge of the turbulator shown in Fig. 118a,

[0429] Fig. 119 shows a perspective view of another embodiment of an invention- 00159604-0073 18.11.2025 PCT / DE0S£^|ößffi115

[0430] IB- 11-2025-.001S9B04-0073

[0431]

[0432] 60

[0433] plate heat exchanger suitable for X-flow in shell construction with a shell featuring a turbulator that has angularly arranged turbulator elements as well as curved or arc-shaped outer edges, all of which are concave, and four flow channels,

[0434] Fig. 120 shows a top view of the shell with the turbulator shown in Fig. 119.

[0435] Fig. 121 shows a perspective view of another embodiment of a shell provided for a plate heat exchanger according to the invention and suitable for X-flow, with a turbulator having angularly arranged turbulator elements and straight outer edges, for a plate heat exchanger according to the invention with four flow channels.

[0436] Fig. 122 shows a top view of the shell with the turbulator shown in Fig. 121.

[0437] Fig. 123 shows a perspective view of another embodiment of a shell designed for a plate heat exchanger according to the invention and suitable for X-flow, with a turbulator having angularly arranged turbulator elements and curved or arc-shaped outer edges, where two outer edges are concavely curved. 00159604-0074 18.11.2025 PCT / DE0S£^|ößffi115

[0438] 18-1 l-2025--WlSB6O#->. O©74

[0439]

[0440] 61

[0441] and two outer edges are convexly curved, and four additional turbulator segments as well as four flow channels,

[0442] Fig. 124 shows a top view of the shell with the turbulator and turbulator segments shown in Fig. 123.

[0443] Fig. 125 shows a perspective view of another embodiment of a shell-type plate heat exchanger suitable for an X-flow according to the invention and for an X-flow, with a turbulator having angled turbulator elements whose corrugated fin-shaped elements are arranged at an angle of 25° to the longitudinal side edges of the shell.

[0444] Fig. 126 shows a top view of the shell with the turbulator shown in Fig. 125.

[0445] Fig. 127 shows a top view of another embodiment of a shell-type plate heat exchanger suitable for an X-flow according to the invention, with a turbulator containing angled turbulator elements whose corrugated fin-shaped elements are arranged at an angle of 45° to the longitudinal side edges of the shell.

[0446] Fig. 128 shows a perspective view of an embodiment of a device for an invention- 00159604-0075 18.11.2025 PCT / DE0S£ / |ößffi115

[0447] IB-11-2'025»00153604“ 0075

[0448]

[0449] 62

[0450] plate heat exchanger designed for intermittent flow, shell provided for a plate heat exchanger in shell construction,

[0451] Fig. 129a is a top view of the bowl shown in Fig. 128,

[0452] Fig. 129b shows a side view of a longitudinal side edge of the shell shown in Fig. 129a,

[0453] Fig. 129c shows a side view of a narrow side edge of the bowl shown in Fig. 129a,

[0454] Fig. 130 shows a perspective view of an embodiment of a shell designed for a plate heat exchanger according to the invention and for U-flow,

[0455] Fig. 131a shows a top view of the bowl shown in Fig. 130,

[0456] Fig. 131b shows a side view of a longitudinal side edge of the shell shown in Fig. 131a and

[0457] Fig. 131c shows a side view of a narrow side edge of the shell shown in Fig. 131a.

[0458] In the following figure descriptions, terms such as top, bottom, left, right, front, back, etc., refer exclusively to the exemplary representation and position of the plate heat exchanger and its components as chosen in the respective drawings. These terms are not to be construed as limiting. 00159604-0076 18.11.2025 PCT / DE0S£^|ößffi115

[0459] IB- 11-2O1 ; 5*-OOI59604-OO7€

[0460]

[0461] 63

[0462] To understand this, that is, these relationships can change through different working positions or mirror-symmetrical design or the like.

[0463] Figures 1a to 104 describe, first, embodiments of plate heat exchangers according to the invention in frame construction. This is followed by a description of possible embodiments of plate heat exchangers according to the invention in shell construction, which are described with reference to Figures 105a to 131c.

[0464] First, a plate heat exchanger 1, designed for X-flow, is described with reference to Figures 1a and 1b to 20. Figures 1a and 1b, as well as 2a, 2b, and 2c, show the heat exchanger in its assembled and operating states, respectively. This plate heat exchanger 1 consists of identical frames 2 arranged one above the other in a stacked configuration. A detailed view of one such frame 2 can be found in Figures 8, 9a, 9b, and 9c. Figure 9a shows that the frame 2 has a rectangular shape with four straight edges: two longitudinal edges 3a and 3b, which are parallel to each other, and two narrow edges 4a and 4b, which are perpendicular to these longitudinal edges 3a and 3b and also parallel to each other. The frames 2 of the plate heat exchanger 1 are arranged between two end plates 5 and 6.Between each pair of adjacent frames 2 is a partition plate 7. This partition plate 7 is shown in various views in Figures 6, 7a, 7b, and 7c. It can be seen that the partition plates 7 have the same shape and size as the frames 2. The rectangular partition plates 7 thus have two long edges 8a and 8b and two short edges 9a and 9b perpendicular to them. Furthermore, the partition plates 7 have openings 10a, 10b, and 10c in their four corner areas. 00159604-0077 18.11.2025 PCT / DE0S£^|ößffi115.

[0465] 18" 11-2025-00 155604-0077

[0466]

[0467] 64

[0468] and 10, through which media, for example liquids or fluids or gaseous media, can pass or flow. The end plates 5 and 6 have the same design, that is, the same shape and size, as the partition plates 7. This can be seen particularly in Figures 3 and 4. Thus, the upper end plate 5 of the plate heat exchanger 1 shown in Figure 3 also has inlets 11a and 11b in its corner regions for the two media M1 and M2 flowing into the plate heat exchanger 1, as well as outlets 11c and 11d for discharging these media M1 and M2 from the plate heat exchanger 1. Connection ports 12 are also provided at the inlets 11a and 11b and the outlets 11c and 11d of the end plate 5.

[0469] The passages 10a, b, c, and d of the partition plates 7 are aligned with the inlets 11a and b and outlets 11c and d of the end plates 5 and 6 to allow the passage of media M1 and M2. A possible flow pattern through the plate heat exchanger 1 is shown schematically in Fig. 5, where the arrowheads of the media labeled M1 and M2 indicate their flow direction, analogous to the diagram in Fig.

[0470] Figure 4 contains arrow diagrams. This flow principle is known in plate heat exchangers of the generic type and therefore does not need to be described in detail here. However, it can be seen from Figures 4 and 5 that in the present embodiment of the plate heat exchanger 1, a so-called X-flow takes place. In the case of such an X-flow, the media M1 and M2 enter the plate heat exchanger 1 through the inlets 11a and 11b of the end plate 5. The medium M1 then initially flows diagonally in the uppermost level, i.e., in the frame 2 located at the very top in Fig. 4, towards the diagonally opposite outlet 11c of the end plate 5. However, this flow does not only take place in the uppermost level, i.e., in the uppermost frame 2 of the plate heat exchanger 1, but in all levels of the plate heat exchanger 1, because the media 00159604-0078 18.11.2025 PCT / DE0S£^ / |ößffi115

[0471] ONE

[0472] 65

[0473] As can also be seen in Fig. 5, M1 and M2 pass through the inlets 11a and 11b of the end plate 5 into all other frames 2 and partition plates 7 located below the end plate 5. Thus, as shown in Fig. 4, the medium M2 also flows diagonally in the further frame 2 located below the aforementioned uppermost frame 2, but from the passage 10b of the partition plate 7 to the passage 10d of the partition plate 7. To enable this, the frames 2 have two collecting channels 13a and 13b, which are diagonally opposite each other and allow the passage of media M1 and M2 to the respective passages 10a, b, c and d of the partition plates 7. In the Fig.Figures 8, 9a, 9b, and 9c show that the frame 2 has an outer, closed first frame section 14 formed by its longitudinal side edges 3a and 3b and narrow side edges 4a and 4b, and that this first frame section 14 is subdivided into a central flow chamber 15 and the collecting channels 13a and 13b by second frame sections 16a and 16b. Figures 3 and 4 show that the collecting channels 13a and 13b are aligned with the passages 10a, b, c, and d of the separating plates 7 for the passage of media M1 and M2, i.e., they are positioned one above the other. Overall, Figures 3 and 4 show that the collecting channels 13a and 13b of the frames 2, the passages 10a, b, c and d of the partition plates 7 and the inlets 11a and b as well as outlets 11c and d of the end plates 5 and 6 are all aligned with each other or are located one above the other to allow the flow through the entire plate heat exchanger 1 with the two media M1 and M2.The partition plates 7 arranged between the frames 2 thus form media-carrying medium passages for the passage of media M1 and M2. One can also say that the flow chamber 15 of a frame 2 located between two partition plates 7 in the assembled state of the plate heat exchanger 1 forms such a medium passage for the passage of media M1 and M2. The same applies, incidentally, to the passage between the upper end plate 5 and the partition plate 7 below it, and analogously between the lower end plate 6. 00159604-0079 18.11.2025 PCT / DE0S£^ / |ößffi115.

[0474] IB- 1 l-.Äö2B'-OO15BS04”OQ7S

[0475]

[0476] 66

[0477] and the medium passages formed by the separating plate 7 above it.

[0478] In each flow chamber 15 of the frame 2 of the plate heat exchanger 1, a turbulator 17 is arranged. These turbulators 17 extend over the entire area of ​​the flow chambers 15 of the frame 2. Figures 3 and 4 show the turbulators 17 in a simplified representation, from which it is already evident that the turbulators 17 consist of corrugated rib-shaped turbulator elements 18 that run parallel to each other, with the spacing between them being equal in this embodiment. The arrangement of such a turbulator 17 with turbulator elements 18 in a frame 2 is particularly clear in Figure 10. The frame 2 with the turbulator 17 shown in Figure 10 is the frame 2 or turbulator 17 that is shown in Figures 3 and 4.

[0479] Figures 3 and 4, viewed from the upper end plate 5, represent the second frame 2 and the second turbulator 17 from above, respectively. Figure 10 illustrates that the corrugated rib elements 18 of the turbulator 17 are not arranged perpendicular or parallel, but at an oblique angle to the longitudinal side edges 3a and 3b of the first frame section 14 of the frame 2. This angle is formed between the longitudinal direction of the turbulator elements 18 and one of the two longitudinal side edges 3a and 3b and is 25° in this embodiment. Figures 11 and 12 show the frames 2, including other embodiments of turbulators 19 and 20, whose corrugated rib elements are arranged at an angle of 45° and 55°, respectively, to the longitudinal side edges of the frames 2.

[0480] Fig. 13, like Fig. 10, shows the frame 2 with the turbulator 17, whose turbulator elements 18 have an angle of 25°. To the right of this, Fig. 14 shows a sectional view of this frame 2 with the turbulator 17 according to Fig. 13 along line 00159604-0080 18.11.2025 PCT / DE0S£^|ößß115

[0481] Wl l'“2©25=00159604-WB0

[0482]

[0483] 67

[0484] From Fig. 13. This sectional view in Fig. 14 serves to illustrate the wave-rib shape of the turbulator elements 18.

[0485] Basically, the specific design or

[0486] The shape of these corrugated ribs in the present invention is not limited to the representation in the present figures.

[0487] For the flow of media M1 and M2 through the plate heat exchanger 1 and the turbulators 17 contained therein with

[0488] for the wave-ribbed turbulator elements 18 this means,

[0489] that these media M1 and M2, in the case of the X-flow through this plate heat exchanger 1 shown here, pass the corrugated turbulator elements 18 transversely to their longitudinal direction. In other words, the media M1 and M2 do not flow through the turbulators in the longitudinal direction of the corrugated turbulator elements 18, but at an angle transversely or

[0490] oblique to this longitudinal direction of the turbulator elements 18. This

[0491] In conjunction with the respective selected angular dimensions of the turbulator elements, this leads to particularly advantageous flow conditions and thus to an increased heat transfer performance of the plate heat exchanger 1. In this context, it should be noted that Figures 3 and 4 show that it is advantageously possible to arrange two adjacent turbulators 17 one above the other in the present case of X-flow.

[0492] The plate heat exchanger 1 is to be arranged such that its corrugated turbulator elements 18 run at opposite angles to the longitudinal side edges of the first frame section 14 of the frame 2. The resulting flows or flow directions of the media

[0493] M1 and M2 are represented by the corresponding arrow symbols in

[0494] This is shown in Fig. 4. It can also be seen there that the adjacent frames 2, stacked one above the other, are always arranged rotated 180° relative to each other, so that their respective collecting channels 13a and 13b are also arranged alternately. 00159604-0081 18.11.2025 PCT / DE0S£^|ößffi115

[0495] 1'8-11-2OÄS-W15«€G4--0! O81

[0496]

[0497] 68

[0498] Figures 15, 16a, and 16b further illustrate the individual levels and their components of the assembled plate heat exchanger 1 in its operational state. Figure 15 corresponds to the side view of the plate heat exchanger 1 shown in Figure 2c, with Figure 15 depicting the position of the plate heat exchanger 1 resting on the lower end plate 6 and the upper end plate 5 with the connection ports 12 visible at the top. Accordingly, the enlarged details of the corner area of ​​the plate heat exchanger 1, marked by a circle in the upper right of Figure 15, show details of its components, namely the end plate 5, the frame 2 with the turbulators 17 and their turbulator elements 18, and the baffle plates 7.

[0499] Furthermore, Figures 17, 18a, 18b, and 18c show, by way of example and in a simplified representation, another embodiment of a turbulator 21 in a single view, that is, without the associated frame 2. This turbulator 21 has turbulator elements 22 that are arranged parallel to one another at an angle of 20° to the longitudinal side edges 23a and b of the turbulator 21, which, in the installed state, abut the longitudinal side edges 3a and 3b of the frame 2. The turbulator 21 thus has a rectangular shape, like the turbulators 17, 19, and 20 already described, and therefore, in the installed state, extends over the entire flow chamber 15 of the frame 2. The narrow side edges 24a and 24b of the turbulator 21 can also be seen in Figures 18a, b, and c. The turbulator 21 thus has a rectangular shape with four straight side edges, namely the parallel longitudinal side edges 23a and 23b and the narrow side edges 24a and 24b. Fig.However, figures 17 and 18a illustrate that this turbulator 21 has recesses 25a, b, c and d in its four corner regions. These recesses 25a, b, c and d serve to design the turbulator 00159604-0082 18.11.2025 PCT / DE0S£^|ößffi115.

[0500] .18-11 -20.25-001596© 4-W82

[0501]

[0502] 69

[0503] to be able to insert 21 into a frame 2, such that the collecting channels 13a and b are located in the area of ​​these recesses 23a, b, c and / or d. The recesses 25b and 25c have curved edge sections 26 and 27, the shape of which matches the shape of the second frame sections 16a and 16b. The same applies to the turbulators 17, 19 and 20, which also have recesses in their corner areas.

[0504] Finally, Figures 19, 20a, b, and c also show the turbulator 21 in a single view, that is, without the associated frame 2. In principle, the representations in Figures 19, 20a, b, and c correspond to the representations of the turbulator 21 in Figures 17, 18a, b, and c, so reference is made to the explanations given there to avoid repetition. The angular direction (20°) of the corrugated turbulator elements 22 of the turbulator 21 can also be seen in Figure 20a. The more detailed representation of these turbulator elements 22 in Figures 19, 20a, b, and c is designed to illustrate the shape of the corrugated ribs even more clearly compared to the simplified representations such as those in Figures 11, 12, 13, 17, 18a, b, and c.

[0505] With reference to Figures 21a to 25, a plate heat exchanger 28 designed or suitable for inertial flow, as well as its components and operating principle, will now be described. In its assembled state, this plate heat exchanger 28 looks externally like the plate heat exchanger 1 described above, so reference is made to the corresponding description and the associated Figures 1a and 1b as well as Figures 2a, 2b and c to avoid repetition.

[0506] The plate heat exchanger 28 uses frames 29 which differ from the frames 2 of the plate heat exchanger 1 only in the position or arrangement of the collecting channels 30a and 30b 00159604-0083 18.11.2025 PCT / DE0S£^|ößß115

[0507] 2 1 “202E” Oül 0604“ OME

[0508]

[0509] 70

[0510] The frame 29 also has two longitudinal side edges 31a and 31b and two narrow side edges 32a and 32b, as well as a first frame section 33 and second frame sections 34a and 34b. While in frame 2 the collecting channels 13a and 13b are located diagonally opposite each other in the corner regions of frame 2, in the plate heat exchanger 28, which is designed for I-flow, the collecting channels 30a and 30b are located on one of the two longitudinal side edges, in this case on longitudinal side edge 31a in the two corner regions of frame 29. Figures 21a and 21b show that, as in plate heat exchanger 1, the channels in plate heat exchanger 28 are also adjacent to each other! The horizontal frames 29 are arranged rotated 180° relative to each other, so that their respective collecting channels 30a and 30b are also arranged alternately.This is necessary for a known I-flow through such plate heat exchangers in order to realize the flow of media M1 and M2 through the individual levels of the plate heat exchanger 28 formed by the frames 29, as also illustrated by the arrows in Fig. 21b. While in an X-flow the media M1 and M2 flow diagonally to each other in the respective superimposed frame levels, i.e., they cross each other, in the case of an I-flow the media M1 and M2 flow in the superimposed frame levels essentially parallel to the longitudinal side edges 31a and 31b of the frames 29, i.e., in the longitudinal direction of the rectangular frame 29, with the flow direction being opposite in adjacent superimposed frames 29.For the sake of completeness, it should be noted that plate heat exchanger 28 has the same end plates 5 and 6 and baffle plates 7 as plate heat exchanger 1. These end plates 5 and 6 therefore also have inlets 11a and 11b and outlets 11c and 11d, and baffle plate 7 has passages 10a, b, c, and d. Reference is therefore made to the relevant explanations above regarding plate heat exchanger 1. 00159604-0084 18.11.2025 PCT / DE0S£^|ößffi115.

[0511] i -8-ii

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[0513] 71

[0514] The frames 29 of the plate heat exchanger 28 also have a flow chamber 35 in which a turbulator 36 is arranged. The appearance of this turbulator 36 can be seen in Figures 21a and 21b and Figure 23. It is particularly evident in Figure 23 that this turbulator 36, arranged in the frame 29, consists of two turbulator segments 37a and 37b, which are of the same size and each cover half of the flow chamber 35 of the frame 29. The division of the two turbulator segments 37a and b is located in the middle of the longitudinal side edges 31a and b of the first frame section 33 of the frame 29. The turbulator segments 37a and 37b are each formed from wave-ribbed turbulator elements 38a and 38b arranged at a parallel distance from each other, which run in opposite directions, here at an angle of 15° to the longitudinal side edges 31a and 31b of the frame 29, see Fig. 23.This division and orientation of the turbulator elements 38a and 38b of the turbulator segments 37a and 37b is deliberately chosen for the present case of a known I-flow in order to achieve the most optimal flow conditions and thus the highest possible heat transfer. The flow pattern of the media M1 and M2 is shown with arrows in Fig. 22. The plate heat exchanger 28 is thus prepared such that the inlets 11a and 11b and outlets 11c and 11d of the end plates 5 and 6, the passages 10a, b, c and d of the partition plate 7 and the collecting channels 30a and 30b of the frame 29 are opened or closed in such a way that the media M1 and M2 do not flow diagonally as in the X-flow, but rather flow longitudinally from one narrow side edge 32a to the other narrow side edge 32b of the frames 29 through the turbulators 36 located in two superimposed planes or frames 29.In order to achieve the highest possible heat transfer performance, the turbulators 36 of the plate heat exchanger 28 described in this embodiment are identical in construction, but in opposite orientations or angular directions, as can be clearly seen in Figs. 21a and 21b.

[0515] 1>-1 l-2025-W15^604-.00B5

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[0517] 72

[0518] As can be seen, the arrangement is such that, in the case of two adjacent turbulators 36 placed one above the other, the respective superimposed turbulator segments 37a and 37b with their turbulator elements 38a and 38b also run in opposite angular directions. The two adjacent superimposed turbulators 36 shown in Figs. 21a and 21b are therefore arranged rotated at an angle of 180° to each other.

[0519] Fig. 24 shows another embodiment of a turbulator 39, which is installed in the frame 29 of the plate heat exchanger 28 already described. This turbulator 39 corresponds in principle to the turbulator 36 and differs from it only in that the turbulator elements 40a and 40b of its two turbulator segments 41a and 41b are each arranged at an angle of 30° to the longitudinal side edges 31a and 31b of the frame 29. This larger angle results in a different flow behavior in the flow chamber 35 of the frame 29, since during intermittent flow the media M1 and M2 impinge on the corrugated turbulator elements 40a and 40b at a different angle. This angle of attack also results differently in the case of the turbulator 42 illustrated in Fig. 25. This turbulator 42, like the turbulators 36 and 39, also consists of two turbulator segments 43a and 43b, which are made up of turbulator elements 44a and 44b.Here, the angle between the longitudinal direction of the wave-ribbed turbulator elements 44a and 44b and one of the two longitudinal side edges 31a and 31b of the first frame section 33 of the frame 29 is 45°.

[0520] With reference to Figures 26 to 35c, a plate heat exchanger 45 designed or suitable for U-flow, as well as its components and operating principle, will now be described. In its assembled state, this plate heat exchanger 45 looks externally like the plate heat exchangers described above 00159604-0086 18.11.2025 PCT / DE0S£^|ößffi115

[0521] 18-11 -2O2S-OOT598.04-OÜ86

[0522]

[0523] 73

[0524] 1 and 28, so that, in order to avoid repetition, reference is made to the relevant description and the associated drawing figures.

[0525] In plate heat exchanger 45, frames 46 are used, which differ from frames 2 and 29 of plate heat exchangers 1 and 28 solely in the position or arrangement of the manifolds 47a and 47b. Frame 46 also has two longitudinal side edges 48a and 48b and two narrow side edges 49a and 49b, as well as a first frame section 50 and second frame sections 51a and 51b. While in frame 29 the manifolds 30a and 30b are located on one of the two longitudinal side edges 31a in the two corner regions of frame 29, in plate heat exchanger 45, which is designed for U-flow, the manifolds 47a and 47b are arranged on one of the two narrow side edges, in this case on narrow side edge 49b, in the two corner regions of frame 46.

[0526] Plate heat exchanger 45 has the same end plates 5 and 6 and baffle plates 7 as plate heat exchangers 1 and 28. These end plates 5 and 6 therefore also have inlets 11a and 11b and outlets 11c and 11d, and baffle plate 7 has passages 10a, b, c, and d. Therefore, to avoid repetition, reference is made here to the corresponding descriptions of plate heat exchanger 1.

[0527] Figures 26 and 27 show that, as with plate heat exchangers 1 and 28, the frames 46 in plate heat exchanger 45 are arranged adjacent to each other, rotated by 180° relative to each other, so that their respective collector channels 47a and 47b are also arranged alternately. This is necessary for a U-shaped flow pattern in such plate heat exchangers, as is known per se, in order to achieve the flow pattern of media M1 and M2 through the plate heat exchanger, which is also illustrated by the arrows in Figure 27.

[0528] .18-1

[0529] 74

[0530] to realize the individual levels of the plate heat exchanger 45 formed by the frames 46. Unlike in an X- or I-flow, in the case of a U-flow, the media M1 and M2 flow in the superimposed frame levels essentially in a U-shape, i.e., as in the writing of the capital letter "U", with the flow direction being opposite in adjacent superimposed frames 46. To achieve this, the frame 46 has a partition 52. This extends, as can be clearly seen especially in Fig. 30a, from the narrow side edge 49a of the frame 46 into the flow chamber 53 of the frame 46. A turbulator 54 is arranged in this flow chamber 53. This one-piece turbulator 54, shown in Fig. 31, consists of two turbulator segments 55a and 55b, which are of the same size and each cover half of the flow chamber 53.The division of the two turbulator segments 55a and 55b is located in the area of ​​the separating web 52. This straight separating web 52 thus defines the division of the turbulator segments 55a and 55b. The turbulator segments 55a and 55b consist of corrugated rib-shaped turbulator elements 56a and 56b arranged at a parallel distance from each other, each running in the opposite direction to the longitudinal side edges 48a and 48b of the first frame section 50 of the frame 46, specifically at an angle of 20° in the present embodiment, as shown in Fig.

[0531] 31 can be seen. This division and orientation of the turbulator elements 56a and 56b of the turbulator segments 55a and 55b is deliberately chosen for the present case of a known U-flow in order to achieve the most optimal flow conditions and thus the highest possible heat transfer.

[0532] Figures 34 and 35a, b, and c show the turbulator 54 again in individual views from different perspectives. In this context, it should be noted that Figure 34 00159604-0088 18.11.2025 PCT / DEflSu^|ößffi115

[0533] 1 11-2025-00150604-008

[0534]

[0535] 75

[0536] Figures 35a, b, and c are simplified representations of such a turbulator 54 and its corrugated turbulator elements 56a and 56b. The straight lines used in the drawings to depict these corrugated turbulator elements 56a and 56b are intended to show, in principle, the course or longitudinal direction of these turbulator elements in the patent application. As already explained in the introduction to the description, there are known to be various ways of manufacturing or forming such corrugated turbulator elements, which can also be used in the present invention and its embodiments. In the figures...Figures 35b and 35c are therefore side views of one of the two longitudinal edges 57a and 57b, and one of the two narrow edges 58a and 58b, respectively, of the turbulator 54, which are formed by the outer ends of the turbulator elements 56a and 56b. Figure 35a also shows that the turbulator 54 has recesses 59a, b, c, and d in the corner regions. Like the recesses 25a and 25b of the turbulator 21, the recesses 59b and 59c serve to allow the turbulator 54 to be inserted into the frame 46 such that the recesses 59b and 59c are located in the area of ​​the collecting channels 47a and 47b. The recesses 59b and 59c in the turbulator 54 are thus shaped or formed according to the shape of the second frame sections 51a and 51b. The recesses 59a and 59d improve the possibility of the flow of media M1 and M2 towards the passages 10a, b, c and d of the partition plates 7.

[0537] The U-flow principle of the plate heat exchanger 45 with the media M1 and M2 is also illustrated in Fig. 28. The media M1 and M2 thus enter the plate heat exchanger 45 via the inlets 11a and 11b of the end plate 5 and flow through it in all planes with the frame 46 and the turbulators 54 located therein. Subsequently, the media M1 and M2 exit.

[0538] 18-11->2G25-ÖO159S04-OO89

[0539]

[0540] 76

[0541] M2 the plate heat exchanger 45 through the outlets 11c and 11d of the end plate 5. In order to accomplish this flow, two passages 10a, b, c and d of the partition plates 7 are closed in the assembled or operating state of the plate heat exchanger 45 in a manner known per se.

[0542] In principle, heat transfer occurs between the media M1 and M2 in the turbulators 54, which are located in the stacked frames 46, just as in the plate heat exchangers 1 and 28 already described, which are designed for X- and I-flow, respectively. In the case of the plate heat exchanger 45 as well, the corrugated turbulator elements 56a and 56b, which are arranged at an angle to the longitudinal side edges 48a and 48b of the frames 46, also produce a different heat transfer effect in the case of U-flow. These flow conditions and the resulting heat transfer effects depend on the magnitude of this angle, which can be varied. While the plate heat exchanger 45 has turbulators 54 with turbulator elements 56a and 56b which run at an angle of 20° to the longitudinal side edges 48a and 48b, the angles for the turbulator elements shown in Figs. 32 and 33 are 30° and 40° respectively.The figure.

[0543] Figures 32 and 33 also show turbulators 60 and 61 arranged within frame 46, which, apart from the different angular dimensions, have the same structure and components as turbulator 54. Thus, turbulator 60 has turbulator segments 62a and 62b with turbulator elements 63a and 63b, while turbulator 61 has turbulator segments 64a and 64b with turbulator elements 65a and 65b.

[0544] The following describes a plate heat exchanger 66 with reference to Figures 36 to 46b, which is designed for X-flow and is shown in the assembled and operating states in Figures 45, 46a and 46b respectively, where 00159604-0090 18.11.2025 PCT / DE0S£^|ößffi115

[0545] 18"! 1"ÄO25-OO1596O4-W90

[0546]

[0547] 77

[0548] This plate heat exchanger 66 is also equipped with and operates with turbulators 67, whose corrugated turbulator elements 68, unlike those of the plate heat exchangers 1, 28 and 45 described above, are not arranged at an angle, but rather, in conjunction with the frames 2 surrounding them, form flow channels 69a, b, c and d. These flow channels 69a, b, c and d, which are described in more detail below, produce a special flow behavior and thus different heat transfer effects in the plate heat exchanger 66.

[0549] First, it should be clarified that the design and operation of the plate heat exchanger 66 are essentially identical to those of the plate heat exchanger 1. The plate heat exchanger 66 also comprises the same frames 2, which are arranged between two end plates 5 and 6 and are designed for the flow of two different media, M1 and M2. The flow principle is illustrated again in Fig. 38. Between each pair of adjacent frames 2, there is also a baffle plate 7 to form media-carrying passages for the transfer of media M1 and M2. The design of the frames 2, the end plates 5 and 6, and the baffle plate 7 has already been described above using the example of the plate heat exchanger 1, so reference is made to that description here to avoid repetition.The frames 2 used in the plate heat exchanger 66 also have the flow chamber 15, which here serves to accommodate the turbulator 67, described in detail below with reference to Figures 39 to 46b. The special feature of the turbulator 67 is that it does not extend over the entire flow chamber 15, but only over a portion of it. This is particularly evident in Figure 44a. This portion of the flow chamber 15 of the frame 2 is occupied or filled by the turbulator 67. As can also be seen in Figure 44a, the turbulator 67 has 00159604-0091 18.11.2025 PCT / DE0S£^|ößffi115.

[0550] I - 1.1

[0551] 78

[0552] Four outer edges 70a, b, c, and d. These turbulator outer edges 70a, b, c, and d are arranged adjacent to, or facing, the inner surfaces of the respective neighboring inner edges 71a, b, c, and d of the first frame section 14 of the frame 2. The turbulator outer edge 70a is therefore adjacent to the inner edge 71a of the first frame section 14 of the frame 2. The same applies to the turbulator outer edge 70b and the inner edge 71b, the turbulator outer edge 70c and the inner edge 71c, and the turbulator outer edge 70d and the inner edge 71d. In particular, Fig. 44a illustrates that the outer edges 70a and 70c are curved or arc-shaped, and, viewed from the center of the flow chamber 15, are concavely curved. The outer edges 70b and 70d of the turbulator 67 are also curved or arc-shaped, but convexly curved.The special feature is that between the outer surfaces of the outer edges 70a, b, c and d of the turbulator 67 and the inner surfaces of the adjacent inner edges 71a, b, c and d, there is an open or unobstructed area, meaning that the flow chamber 15 is not completely filled. The media M1 and M2 can flow through this area, thus forming the flow channels 69a, b, c and d. The position, arrangement, and shape of the flow channels 69a, b, c and d, in conjunction with the X-shaped flow pattern provided in this embodiment of the plate heat exchanger 66, result in specific flow conditions within the individual levels formed by the frames 2, leading to particularly advantageous heat transfer effects.

[0553] Figures 36 and 37 also clearly show the turbulator 67 located in frame 2 and the flow channels 69b and 69d formed by it. Figure 43 likewise illustrates the position of the turbulator 67 in frame 2 and the resulting flow channels 69a, b, c, and d. Figure 44b is 00159604-0092 18.11.2025 PCT / DEflSu^|ößffi115

[0554] 79

[0555] a view of an outer surface of one of the two longitudinal side edges, namely the longitudinal side edge 3a of the frame 2, while Fig. 44c is a side view of the outer surface of the narrow side edge 4a.

[0556] Figures 39 to 42c show the turbulator 67 in more detail using several individual views. Figures 39 and 40a, b, and c are simplified representations in which the corrugated turbulator elements 68 are illustrated only by parallel lines. This representation, however, illustrates the longitudinal direction of these turbulator elements 68. The external shape of the turbulator 67 and its outer edges 70a, b, c, and d are also recognizable in Figures 39 and 40a, but not quite as clearly as in Figures 41 and 42a, b, and c. Therefore, it is particularly evident in Figures 41 and 42a that the turbulator 67, like the plate heat exchangers 1, 28, and 45 described above, has a recess 72a, b, c, and d in each of its corner regions.These recesses 72a, b, c, and d serve the same purpose as the previously mentioned recesses 25a, b, c, and d, as well as 59a, b, c, and d of the turbulators 21 and 54, respectively, so that, to avoid repetition, reference is made here to the corresponding explanations. Figure 44a shows that the diagonally opposite recesses 72b and 72d are designed or shaped accordingly to the second frame sections 16a and 16b located in the area of ​​the collecting channels 13a and 13b. Figure 44a also shows a separating plate 7 arranged under the turbulator 67 or frame 2, as well as its two passages 10a and 10c. The recesses 72a and 72c of the turbulator 67 are designed accordingly to these diagonally opposite passages 10a and 10c. The side views according to Figs. 42b and 42c of the outer edges 70a and 70d of the turbulator 67 illustrate more accurately the actual well-rib shape of the turbulator elements 68.00159604-0093 18.11.2025 PCT / DE0S£^|ößffi115.

[0557] 1«- 1 l',2025“ö01B9604-nQ93

[0558]

[0559] 80

[0560] Figures 45, 46a, and 46b further illustrate the individual levels and the components contained therein of the assembled, i.e., operational, plate heat exchanger 66. The representation in Figure 45 corresponds to the side view of the plate heat exchanger 1 shown in Figure 2c, with Figure 45 showing the position of the plate heat exchanger 66 in which it rests on the lower end plate 6 and the upper end plate 5 with the connection nozzles 12 is visible at the top. Accordingly, the enlarged details of the corner area of ​​the plate heat exchanger 66, marked in the upper right of Figure 45 by a circle labeled "A", show details of the components contained therein, namely the end plate 5, the frame 2 with the turbulators 67 and their turbulator elements 68, and the baffle plates 7.

[0561] As already explained, the turbulator 67 is characterized by curved or arc-shaped outer edges 70a, b, c and d, which, in conjunction with the straight inner edges 71a, b, c and d of the frame 2, result in a shape for the flow channels 69a, b, c and d as can be seen in particular in Fig. 44a. However, it has also been pointed out that the shape of the flow channels according to the invention is not limited to this specific shape of the flow channels 69a, b, c and d. In other words, numerous other flow channel shapes are also possible and feasible.The shape of the outer edges of a turbulator is therefore in principle freely selectable, as long as the respective turbulator actually only covers a partial area of ​​the flow chamber 15, i.e., between the outer edges of a turbulator and the inner surfaces of the adjacent inner edges of the first frame section of the frame, there is an open or unobstructed space, i.e., the flow chamber 15 is not completely 00159604-0094 18.11.2025 PCT / DE0S£^|ößffi115.

[0562] I 1 -2©25-=0Ül 53504- ©084

[0563]

[0564] 81

[0565] filling area through which a medium such as ml or M2 can flow.

[0566] Figures 47 to 52c are therefore intended to show some possible alternative shapes of the flow channels by way of example, whereby it should be made clear that numerous other shapes can be implemented which produce advantageous flow effects and thus heat transfer results.

[0567] First, three embodiments of turbulators 73, 74 and 75 are described with reference to Figs. 47 to 49, which have in common that their outer edges are straight, i.e., not curved or arc-shaped.

[0568] The turbulator 73 shown in Fig. 47, like the turbulators 17 and 67, is located in the frame 2 already described, which has the two collecting channels 13a and 13b provided for X-flow. Reference is made to the above explanations to avoid repetition. Fig. 47 shows the specific shape of the turbulator 73, which has corrugated turbulator elements 76 that run parallel to each other, with the longitudinal direction of the turbulator elements 76 running parallel to the narrow side edges 3a and 3b of the frame 2. The turbulator 73 therefore has four straight outer edges 77a, b, c, and d. Between the outer surfaces of the outer edges 77a and 77c and the inner surfaces of the adjacent inner edges 3a and 3b of the first frame section of the frame 2, as shown in Fig.As can be seen in Figure 47, there is a free area, meaning that the flow chamber 15 does not completely fill the area, which in this embodiment forms the flow channels 78a and 78b through which the media M1 and M2 can flow. In contrast, the two outer edges 77b and 77d of the Tur- 00159604-0095 18.11.2025 PCT / DE0S£^|ößffi115.

[0569] IS- 11 -2©25~iOOK 0W095

[0570] 82

[0571] The turbulators 73 are located directly on the inner surfaces of the adjacent inner edges of the narrow side edges 4a and 4b of the frame 2, so that in this embodiment there are no flow channels there. The turbulator 73 thus forms two flow channels 78a and 78b in the frame 2 at its two outer edges 77a and 77c.

[0572] Unlike turbulator 73, turbulator 74 forms four flow channels 79a, b, c, and d within frame 2. The shape of these flow channels 79a, b, c, and d is shown in Fig. 48 and results from the straight outer edges 80a, b, c, and d of turbulator 74. In this case, there is also a gap between the outer edges 80b and 80d and the adjacent narrow side edges 4a and 4b of frame 2, i.e., open or unobstructed areas that do not completely fill the flow chamber 15. In this embodiment of turbulator 74 according to Fig. 48, the flow channels 79a, b, c, and d all have approximately the same width. It is understood that the width of the flow channels can be chosen differently for four flow channels, meaning there can be wider and narrower flow channels, which also results in different flow and heat transfer effects.

[0573] Figure 49 also shows a turbulator 75 arranged in frame 2 with four flow channels 81a, b, c and d. However, the shape of these flow channels 81a, b, c and d is triangular and results from the straight outer edges 82a, b, c and d of the turbulator 75, which each lie at an acute angle to the respective adjacent side edges, i.e. the longitudinal side edges 3a and 3b or the narrow side edges 4a and 4b of the first frame section 14 of the frame 2. In the case of the turbulator 75 shown in Fig. 49, this angle is the same on all four outer edges 82a, b, c and d, so that the flow channels 81a and c have the same 00159604-0096 18.11.2025 PCT / DE0S£^ / |ößffi115

[0574] IS- 11 “Ä©Ä5-Ö0159eO4-OS 96

[0575]

[0576] 83

[0577] have size and shape. The same applies to the flow channels 81b and d. The short side of the triangle of these triangular flow channels 81a, b, c and d is located in the corner regions of the frame 2, respectively, at the two diagonally opposite collecting channels 13a and 13b of the frame 2 in the present embodiment, as well as at the diagonally opposite passages 10b and 10d of the partition plate 7, also shown in Fig. 49. In this context, it should be noted that it would also be possible here to form four triangular flow channels by designing a turbulator such that the angle between its outer edges and the adjacent side edges of the frame is chosen to be of different sizes, in order to achieve other flow and heat transfer effects.

[0578] Figures 50 to 52c describe three further embodiments of turbulators 83, 84, and 85, which again share the characteristic that their outer edges are odd-shaped, i.e., curved or arc-shaped, as in the case of the turbulator 67 of the plate heat exchanger 66. As in the case of the turbulator 67 and also the turbulators 73, 74, and 75, the turbulators 83, 84, and 85 each have four outer edges for forming four flow channels. The turbulators 83, 84, and 85 differ only in their external shape, which is described in detail below.

[0579] The four odd-numbered, namely curved or arc-shaped, outer edges 86a, b, c and d of the turbulator 83 are all concave. The resulting shape of the flow channels 87a, b, c and d can be seen in Figure 50.

[0580] In contrast, in the turbulator 84 shown in Fig. 51, all four outer edges 88a, b, c, and d are convexly curved. This results in the shape of the flow channels 89a, b, c, and d illustrated in Fig. 51. 00159604-0097 18.11.2025 PCT / DE0S£ / |ößffi115

[0581] IB- 1 l-2Ü2b~O015W04-a0S7

[0582]

[0583] 84

[0584] Figure 52a again shows the turbulator 85, which is manufactured with two concavely curved outer edges 90a and 90b and two convexly curved outer edges 90c and 90d. The outer edges 90a and 90b are arranged in pairs opposite each other and face the inner surfaces of the inner edges 71a and 71c of the frame 2 adjacent to them. In contrast, the convexly curved outer edges 90c and 90d face the narrow side edges 4a and 4b, respectively, and the inner edges 71b and 71d of the frame 2 located therein. The resulting shape of the flow channels 91a, b, c, and d can be seen in Figure 52. Fig. 52b shows a cross-sectional view along line AB of Fig. 52a to illustrate the design of the turbulator 85 and the associated frame 2, as well as their components. Fig. 52c is an enlarged (scale 1:2) and even more detailed representation of the cross-sectional view of Fig. 52a.

[0585] 52b, to make the wave-rib shape of the turbulator 85 more clearly visible.

[0586] A plate heat exchanger 92, designed for X-flow, is described below with reference to Figures 53 to 60b. Figures 59, 60a, and 60b show the assembled and operating states, respectively. This plate heat exchanger 92 is also equipped with and operates turbulators 93, which have corrugated turbulator elements 94. In contrast to the plate heat exchangers 1, 28, 45, and 66 already described, the plate heat exchanger 92 with the turbulators 93 represents a first combination solution such that, firstly, the turbulator elements 94 are arranged at an angle to the longitudinal side edges 3a and 3b of the first frame section 14 of the frame 2, and secondly, the turbulator 93 extends only over a portion of the flow chamber 15, resulting in four flow channels 95a, b, c, and d. The following described in more detail: 00159604-0098 18.11.2025 PCT / DE0S£ / |ößffi115

[0587] 28-1 l'-ÄO25-©02S9€O4-OO98

[0588]

[0589] 85

[0590] In comparison to the aforementioned plate heat exchangers 1, 28, 45 and 66, the flow channels 95a, b, c and d result in a different flow behavior for the media M1 and M2 and thus advantageous heat transfer effects in the plate heat exchanger 92.

[0591] It should be noted that the design and operation of the plate heat exchanger 92 are essentially identical to those of the plate heat exchanger 1. The plate heat exchanger 92 also comprises the same frames 2, which are arranged between two end plates 5 and 6 and are designed for the X-shaped flow of the two media M1 and M2. To avoid repetition, reference is made to the corresponding explanations for the plate heat exchanger 1. The frames 2 used in the plate heat exchanger 92 also have the flow chamber 15, which here serves to accommodate the turbulator 93, described in detail below with reference to Figures 55 to 60b. As can be clearly seen in Figures 56a and 58a, the turbulator 93 has four outer edges 96a, b, c, and d.These outer edges 96a, b, c, and d of the turbulator are arranged adjacent to, or facing, the inner surfaces of the respective neighboring inner edges 71a, b, c, and d of the first frame section 14 of the frame 2, just like the outer edges 70a, b, c, and d of the turbulator 67. In contrast to the turbulator elements 68 of the turbulator 67, the turbulator elements 94 of the turbulator 93 are arranged at an angle (25°) to the longitudinal side edges 3a and 3b of the frame 2. The shape of the outer edges 96a, b, c, and d is particularly evident in Figures 56a and 58a. The outer edges 96a-d are therefore not straight, but curved or arc-shaped, with outer edges 96a and 96c being concave and outer edges 96b and 96d being convexly curved. The convex curvature of the outer edges 96b and 96d is very slight in this embodiment. Instead, 00159604-0099 18.11.2025 PCT / DE0S£^|ößffi115.

[0592] IB-11

[0593]

[0594] 86

[0595] It is also possible to make these two or all outer edges straight. The shapes of the flow channels 95a-d resulting from the curved or arcuate outer edges 96a-d are shown in Figures 53 and 54 and are essentially the same as the flow channels 69a-d of the turbulator 67 (see Figure 44a), so that, to avoid repetition, reference is made here to the explanations given there. The position, arrangement, and shape of the flow channels 95a-d, in conjunction with the angular arrangement of the turbulator elements 94 in the individual planes of the plate heat exchanger 92 formed by the frames 2, with the X-flow provided in this embodiment of the plate heat exchanger 92, result in special flow conditions that lead to particularly advantageous heat transfer effects.The media M1 and M2 are further swirled by the angular arrangement of the turbulator elements 94 during the X-flow, resulting in a more homogeneous flow behavior and thus more uniform heat transfer. The additional flow channels 95a-d further enhance these heat transfer effects by helping the media to distribute even more effectively across the entire surface in the plane of the frame 2 and the turbulator 93 located therein. For the sake of completeness, it should be noted that the turbulator 93 also has recesses 97a, b, c, and d, which serve the same purpose as the previously mentioned recesses 25a, b, c, and d, 59a, b, c, and d, and 72a, b, c, and d. Therefore, to avoid repetition, reference is made to the corresponding explanations.

[0596] Figures 59, 60a, and 60b serve to illustrate the individual levels and the components contained therein of the assembled, i.e., operational, plate heat exchanger 92. [The following appears to be unrelated and possibly a separate document:] 00159604-0100 18.11.2025 PCT / DE0S£^|ößffi115

[0597] 18-1 1 -2Q25-OD1SSE©#“O1.0Q

[0598]

[0599] 87

[0600] The position in Fig. 59 corresponds to the side view of the plate heat exchanger 1 shown in Fig. 2c, whereby Fig. 59 shows the position of the plate heat exchanger 92 in which it rests on the lower end plate 6 and the upper end plate 5 with the connection nozzles 12 is visible at the top. Accordingly, the enlarged details of the corner area of ​​the plate heat exchanger 92, marked in the upper right of Fig. 59 by a circle labeled "A", show details of the components contained therein, namely the end plate 5, the frame 2 with the turbulators 93 and their turbulator elements 94, and the baffle plates 7.

[0601] In contrast to the turbulator 93, the turbulator 98 shown in Fig. 61 has four straight outer edges 99a, b, c and d, which are located at a parallel distance from the inner surfaces of the respective adjacent inner edges 71a - d of the frame 2 and thus form four straight flow channels 100a, b, c and d. In this respect, the turbulator 98 is therefore identical to the turbulator 74 and its four similarly straight flow channels 79a, b, c and d (see Fig. 61).

[0602] 48), so that, to avoid repetition, reference is made to the descriptions of turbulator 74 given there. Turbulator 98 also covers only a portion of the flow chamber 15. The only difference between turbulator 98 and turbulator 74 is that the turbulator elements 101 of turbulator 98 run at an angle (25°) to the longitudinal side edges 3a and 3b of the frame 2. Here, too, there is the alternative possibility of using turbulators designed in this way with angled turbulator elements to form four straight flow channels, each with a different width or widths.

[0603] Figures 62 and 63 show another embodiment of a turbulator 102 with angularly arranged turbulator elements 103 for forming four flow channels 104a, b, c and d, 00159604-0101 18.11.2025 PCT / DE0S£^|ößffi115

[0604] l'S- 11

[0605]

[0606] 88

[0607] which have a triangular shape, just like the four triangular flow channels 81a-d of the turbulator 75 (see Fig. 49), so reference is made to the explanations therein to avoid repetition. The only difference between the turbulator 102 and the turbulator 75 is that the turbulator elements 103 of the turbulator 102 run at an angle (here 25°) to the longitudinal side edges 3a and 3b, which leads to different advantageous flow and heat transfer effects. The turbulator 102 has outer edges 105a, b, c, and d. Fig. 63 is a sectional view along line A-B of Fig. 62, which makes the corrugated fin shape of the turbulator 102 more clearly visible.

[0608] Figures 64a, b, c and 65 show by way of example the possibility of turbulators 106 and 107 according to the invention, which are arranged for an X-flow in the frame 2 of a plate heat exchanger and, like the turbulators 93, 98 and 102 already described, represent a combination solution such that both turbulator elements 108 and 109 running at an angle to the longitudinal side edges 3a and 3b are used and flow channels 110a, b, c and d or Illa, b, c and d are present. The turbulator 106 has four outer edges 112a, b, c, and d, which are odd-numbered, i.e., curved or arc-shaped, with outer edges 112a and 112c being concave, while outer edges 112b and 112d are convex. The resulting shape of the flow channels 110a–d is shown in Fig. 64a. Fig. 64b shows a cross-sectional view along line AB of Fig.64a, to illustrate the design of the turbulator 106 and the associated frame 2, as well as their components. Fig. 64c is an enlarged and even more detailed representation of the sectional view of Fig.

[0609] 64b, to make the corrugated rib shape of the turbulator 106 more clearly visible. Finally, Fig. 65 shows the turbulator 107 00159604-0102 18.11.2025 PCT / DE0S£^|ößffi115

[0610] 18-1 l'-2O25-OÜ159®0#=OIO2

[0611]

[0612] 89

[0613] with four odd, i.e. arc- or curve-shaped outer edges 113a, b, c and d, all of which are concavely curved, and the resulting flow channels purple - d.

[0614] Since the turbulators 93, 98, 102, 106, and 107 described above are combination solutions with angularly arranged or extending turbulator elements 94, 101, 103, 108, and 109 designed for X-flow through a plate heat exchanger, the embodiment of a turbulator 114 shown in Fig. 66 is intended to demonstrate that such a combination solution is also applicable to plate heat exchangers suitable for I-flow as already explained above. The turbulator 114, arranged in frame 2 for this purpose, therefore differs from the turbulator 36 shown, for example, in Fig. 23, which is also designed for I-flow, primarily in that the turbulator 114 does not completely cover the flow chamber 35, but extends only over a partial area of ​​the flow chamber 35. This results in four flow channels 115a, b, c and d in the turbulator 114.The shape of these flow channels 115a, b, c, and d, and how they are formed by the turbulator 114, can be seen in Fig. 66. The turbulator 114 therefore consists of two turbulator segments 116a and 116b, which in this embodiment are the same size and each occupy half of the partial area of ​​the flow chamber 35. The division between the two turbulator segments 116a and 116b is located in the middle of the longitudinal side edges 31a and 31b of the first frame section 33 of the frame 29. The design of the frame 29 used for the turbulator 114 thus corresponds to the design of the same frame 29 as in the turbulator 36 (Fig. 23), so that, to avoid repetition, reference is made to the corresponding descriptions therein. 00159604-0103 11 / 18 / 2025 PCT / DE0S£^|ößffi115.

[0615] 1 1 -2'0S5- 00153604-m 03

[0616]

[0617] 90

[0618] The turbulator segments 116a and 116b are each formed from corrugated rib-shaped turbulator elements 117a and 117b arranged at parallel intervals, which run in opposite directions, here at an angle of 25°, to the longitudinal side edges 31a and 31b of the frame 29. Between the outer edge 118a of the turbulator segment 116a and the inner side surface of the adjacent inner edge 119a of the first frame section 33 of the frame 29, there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber 35, which forms the flow channel 115a through which the medium M1 or M2 can flow. The same applies to the flow channel 115b, which lies between the outer edge 120a of the turbulator segment 116b and the longitudinal side edge 31a of the frame 29.Furthermore, flow channels 115c and 115d are formed at the two narrow side edges 32a and 32b of the frame 29. For this purpose, the turbulator segment 116a has an outer edge 118b. The same applies to the outer edge 120b of the turbulator segment 116b. The outer edges 118b and 120b are straight, so that the flow channels 115c and 115d have a triangular shape. This does not apply to the flow channels 115a and 115b, because the outer edges 118a and 120a are irregular, namely curved or arc-shaped, specifically concave. The shape of these flow channels 115a and 115b can be seen in Fig. 66. It is understood that this design of the turbulator 114 will in turn achieve other advantageous flow and heat transfer effects for a plate heat exchanger in the case of I-flow.

[0619] A plate heat exchanger 121, designed for U-shaped flow, is now described with reference to Figures 67 to 75c. It uses frames 46 whose design has already been described in detail with reference to Figures 26, 27, 29 and 30a-c. Therefore, to avoid repetition, reference is made here to 00159604-0104 18.11.2025 PCT / DE0S£^|ößffi115

[0620] “2025~001SS€0#”01’04

[0621]

[0622] 91

[0623] Reference is made to the explanations provided there. In its assembled or operating state, the plate heat exchanger 121 therefore looks like the plate heat exchanger 45 from the outside. The plate heat exchanger 121 differs from the plate heat exchanger 45 only in that the turbulator 122 used therein not only has turbulator segments 123a and 123b with angularly arranged turbulator elements 124a and 124b, but, as with the already described turbulators 67, 73-75, 83-85, 93, 98, 102, 106, 107 and 114, several flow channels 125a, b, c, d, e, f and g are provided, which can be clearly seen, for example, in Fig. 72 and are described in detail below. First, however, it should be noted that end plates 5 and 6 as well as separating plates 7, which are shown in Figures 67 and 68, are also used in the plate heat exchanger 121. The plates shown in Figures 67 and 68 are...The arrows in 68 also show the U-flow patterns of the media M1 and M2 in the individual planes of the plate heat exchanger 121 formed by the frame 46.

[0624] For example, Figures 70a and 72 show that the corrugated turbulator elements 124a and 124b of the two turbulator segments 123a and 123b run at an angle (20°) to the longitudinal side edges 48a and 48b of the frame 46. The special feature is that these turbulator segments 123a and 123b extend only over a portion of the flow chamber 53. This is due to the outer edges 126a, b, c, d, e, f, and g of the turbulator segments 123a and 123b, the shape and position of which are clearly visible, for example, in Figures 72 and 74a. These outer edges 126a–g are not straight, but curved or arc-shaped, with outer edges 126a, b, and c being concave, while outer edges 126d, e, f, and g are convex. The flow channels 125a and 125c lie between the outer edges 126a and 126c and the adjacent longitudinal edges 48a and 48b of the frame 46.The concave outer edge 00159604-0105 18.11.2025 PCT / DE0S£^|ößffi115.

[0625] 18-11“2025“001 : E3€04-0'TQB

[0626]

[0627] 92

[0628] Edge 126b is adjacent to the narrow side edge 49b. The outer edges 126d and 126e are adjacent to the other narrow side edge 49a of the frame 46. In contrast, the outer edges 126f and 126g, which are also convexly curved, are located on one side of each of the two sides of the separating web 52, resulting in the flow channels 125f and 125g, which have an additional effect on the flow conditions in a plane with a turbulator 122 designed in this way. The function of the separating web 52 in a U-shaped flow was already explained above using the example of the plate heat exchanger 45. This example of the plate heat exchanger 121 with the turbulators 122 also clearly illustrates the advantageous combination of the angular orientation of the turbulator elements 124a and 124b with the seven flow channels 125a-g. Fig. 75b shows a sectional view along line AB of Fig.75a, to show more clearly the formation of the turbulator 122 and the surrounding frame 46. Fig. 75c is an enlarged and therefore more detailed representation of the sectional view of Fig.

[0629] 75b and is intended to show the wave-rib shape of the turbulator elements 124a and 124b more clearly than is the case in the simplified representations.

[0630] Figures 76 and 77 show two further embodiments of turbulators 127 and 128, which differ from turbulator 122 and its use for U-shaped flow through a plate heat exchanger only in their external shape, i.e., their outer edges. Both turbulators 127 and 128 are suitable for use in the frame 46 already described. Analogous to the outer edges 126a–g of turbulator 122, turbulator 127 has outer edges 129a, b, c, d, e, f, and g, all of which are curved or arc-shaped, specifically concave. This results in the flow channels 130a, b, c, d, e, f, and g. In contrast, the outer edges 131a, b, c, d, e, f and g of the turbulator 128 are all straight. It follows that the 00159604-0106 18.11.2025 PCT / DEflS^ / |ößffi115

[0631] 1

[0632] 93

[0633] Flow channels 132a, b, c, d, e, f and g have a straight shape, as can be seen in Fig. 77.

[0634] A plate heat exchanger 133 is now described with reference to Figures 78 to 90. Like the plate heat exchanger 1, it is designed or suitable for X-flow and uses the already known frames 2, end plates 5 and 6, and partition plates 7. However, the special feature is that a turbulator 134 with angularly arranged turbulator elements 135 is used, and so-called "additional turbulator segments" are employed, namely the four additional turbulator segments 136a, b, c, and d.This is therefore another combination solution in which, in addition to the combination already applied in the example of the plate heat exchanger 92 with the turbulator 93, consisting of turbulators 93 with angled turbulator elements 94 and flow channels 95a-d, an additional turbulator segment 136a-d is located around the turbulator 134 on the inner surfaces of the inner edges 71a-d of the first frame section 14 of the frame 2. This can be clearly seen, for example, in Fig. 81a.It is also shown there that the additional turbulator segments 136a - d extend over the entire length of the longitudinal side edges 3a and 3b or narrow side edges 4a and 4b, i.e. in the present case of the turbulator 134 intended for an X-flow, from the collecting channels 13a and 13b or the second frame sections 16a and 16b there to the two other corner areas of the frame 2, where the passages 10a and 10c of the partition plate 7 are located in the assembled state.

[0635] The turbulator 134 now corresponds to the turbulator 93 insofar as it also only covers a partial area of ​​the flow chamber 15 and has odd, i.e. curved or arc-shaped, outer edges, namely the 00159604-0107 18.11.2025 PCT / DE0S£^|ößffi115

[0636] 1 «■" 11

[0637] 94

[0638] The outer edges 137a, b, c, and d are formed, with the outer edges 137a and 137c facing the longitudinal side edges 3a and 3b being concavely curved, and the outer edges 137b and 137d facing the narrow side edges 4a and 4b being convexly curved. This results in the four flow channels 138a, b, c, and d, the shape and position of which can be clearly seen, for example, in Fig. 81a. It can also be seen there that the additional turbulator segments 136a–d have a certain width and are straight, meaning that their side edges 139a, b, c, and d facing the flow channels 138a–d are straight. It should therefore be expressly pointed out that this is not necessarily the case, but that the side edges of the additional turbulator segments facing the flow channels 138a - d can also be curved, arc-shaped or wave-shaped.It would also be possible to arrange the side edges of the additional turbulator segments facing the flow channels at an angle to the longitudinal side edges 3a and 3b or the narrow side edges 4a and 4b, respectively, resulting in yet another shape for the flow channels. The details of the turbulator 134 and the additional turbulator segments 136a–d are also shown in the figures.

[0639] Figures 82a to 90 provide further details. The recesses in the four corner regions of the turbulator 134, also shown there, will not be discussed in detail here, as these recesses correspond to recesses 97a-d, as already described in connection with the turbulator 93. The same applies to the side views of the turbulator 134 according to Figures 84b and 84c, as well as to the sectional views according to Figures 82b and 82c of the frame 2 with the turbulator 134 and the additional turbulator segments 136a-d arranged therein.

[0640] Figures 85, 86a, and 86b serve to further illustrate the individual planes and the structures contained therein.

[0641] 95

[0642] The components of the assembled, i.e., operating, plate heat exchanger 133 are shown in Fig. 85. The illustration in Fig. 85 corresponds to the side view of the plate heat exchanger 1 shown in Fig. 2c, with Fig. 85 showing the position of the plate heat exchanger 133 in which it rests on the lower end plate 6 and the upper end plate 5 with the connection nozzles 12 is visible at the top. Accordingly, the enlarged details of the corner area of ​​the plate heat exchanger 133, marked in the upper right of Fig. 85 by a circle labeled "A", show details of the components contained therein, namely the end plate 5, the frame 2 with the turbulators 133, their turbulator elements 135, the additional turbulator segments 136a to d, and the baffle plates 7.In this context, as with the plate heat exchanger 1, it should also be noted here with the plate heat exchanger 133 that, for the purpose of the X-flow, as also shown in Figs. 78 and 79, two turbulators 133 arranged adjacent to one another and the additional turbulator segments 136a - d surrounding them are each rotated by 180° relative to each other.

[0643] Finally, it should be noted that the additional turbulator segments 136a-d, like the turbulator 134, also have corrugated turbulator elements 140a, b, c, and d, and that these turbulator elements 140a-d also run at an angle to the longitudinal side edges 3a and 3b of the frame 2. In the present embodiment, the longitudinal direction of the corrugated ribs of the additional turbulator segments 136a-d is the same angle (25°) as the angle of the longitudinal direction of the turbulator elements 135 of the turbulator 134. Thus, in this embodiment, both the angle and the direction of the angle are identical. It is understood that this is not absolutely necessary, but that the angular dimensions of the turbula- 00159604-0109 18.11.2025 PCT / DE0S£^|ößffi115

[0644] 1 8- 11 -2©25“00159€©4-&l®9

[0645]

[0646] 96

[0647] The torsion elements of the turbulator and the additional turbulator segments may be of different sizes and their angular orientations may also be different.

[0648] Figures 91 and 92 show two further alternatives to the embodiment of the turbulator 134 with corrugated fin-shaped turbulator elements 135, which is intended for X-flow through the plate heat exchanger 133 and described above with reference to Figures 78 to 90. These two alternatives shown in Figures 91 and 92 relate only to the outer edges of the turbulators 141 and 142 shown in Figures 91 and 92, which are each arranged in the frame 2 already described. The turbulator 141 has four odd, namely concavely curved, outer edges 143a, b, c, and d. In addition, further turbulator segments 144a, b, c, and d are provided, which are designed and arranged in the same way as the additional turbulator segments 136a–d. Thus, the flow channels 145a, b, c and d are formed. Unlike the outer edges 143a -d of the turbulator 141, the outer edges 146a, b, c and d of the turbulator 142 are not odd, but even.The additional turbulator segments 147a, b, c, and d are designed and positioned like the additional turbulator segments 136a–d and 144a–d, respectively, so that, in conjunction with the outer edges 146a–d of the turbulator 142, they form the flow channels 148a, b, c, and d. Since the outer edges 146a–d and the additional turbulator segments 147a–d are straight, the flow channels 148a–d are also straight, as illustrated in Fig. 92.

[0649] While the plate heat exchangers 133 and the turbulators 134, 141 and 142 described above with reference to Figures 78 to 92 relate to combination solutions with angularly arranged turbulator elements and additional turbulator segments, which are provided in combination with flow channels, for an X-flow, such a combination solution is now to be provided for a [missing information] also according to the invention 00159604-0110 18.11.2025 PCT / DE0S£^|ößffi115

[0650] 97

[0651] The inertial flow through a plate heat exchanger 149 is illustrated in Figures 93 to 101. Since this is a plate heat exchanger 149 designed for inertial flow, it also uses the frames 29 already described in Figures 21a to 25, the detailed description of which can be omitted here to avoid repetition. The structure of the plate heat exchanger 149 shown in Figures 93 and 94 thus corresponds in principle to the structure of the plate heat exchangers already described above, in particular the plate heat exchanger 28 with the turbulators 36 designed for inertial flow. The same applies to the turbulator 114 shown in Figure 66 and arranged in the frame 29, which has two turbulator segments 116a and 116b with angled, corrugated fin-shaped turbulator elements 117a and 117b.The turbulator 150 intended for the plate heat exchanger 149 looks, in principle, like this turbulator 114, as can be seen in Fig. 95a. This turbulator 150 is also formed in one piece and also consists of two turbulator segments 151a and 151b with turbulator elements 152a and 152b. These turbulator elements 152a and 152b are each arranged at an angle to the longitudinal side edges 31a and 31b of the frame 29, in opposite directions. The special feature of the turbulator 150 for the plate heat exchanger 149 is that three additional turbulator segments 153a, b, c, and d are also arranged in the frame 29. Their position and shape are shown in particular in Fig.

[0652] 95a, but also shown in Figs. 100 and 101. The shape and position of the additional turbulator segments 153a-c correspond to the shape and position of the additional turbulator segments 136a, b, and d in the plate heat exchanger 133, so reference is made to the above explanations in this regard to avoid repetition. The turbulator segment 151a of the turbulator 150 now has the outer surfaces shown in Fig. 95a. 00159604-0111 18.11.2025 PCT / DE0S£^|ößffi115

[0653] 18-111

[0654] 98

[0655] edges 154a and 154b. Accordingly, the turbulator segment 151b has outer edges 155a and 155b. This results in the four flow channels 156a, b, c and d.

[0656] It should also be noted that the additional turbulator segments 153a-c have a corrugated rib shape, which is designed such that the corrugated rib elements of the additional turbulator segments 153a-c also run at an angle to the longitudinal side edges 31a and 31b of the frame 29. In this embodiment, the angular direction and dimension of the turbulator elements 152a and 152b correspond to the angular dimension and direction of the corrugated rib elements of the additional turbulator segments 153a-c. Finally, it should also be noted that in the plate heat exchangers shown in Figs. 93 and 94, the turbulators 150, which are located adjacent to each other, and the additional turbulator segments 153a - c surrounding them, are always arranged rotated or offset by 180° to each other in order to optimally ensure the I-flow of the media M1 and M2.

[0657] Finally, Fig. 102 shows an alternative possibility of a combination solution intended for I-flow, consisting of a turbulator 157, additional turbulator segments 158a, b and c, and three flow channels 159a, b and c. This turbulator 157 also consists of two turbulator segments 160a and 160b, each with turbulator elements 161a and 161b arranged or extending at opposite angles. These turbulator segments 160a and 160b have straight outer edges 162a, b and c. In conjunction with the straight additional turbulator segments 158a-c, the flow channels 159a-c are thus formed, which are also straight. 00159604-0112 18.11.2025 PCT / DE0S£^|ößffi115

[0658] IS-1

[0659] 99

[0660] To demonstrate that the aforementioned combination solution, consisting of a turbulator with angularly arranged turbulator elements, additional turbulator segments, and flow channels, can also be used in frame-type plate heat exchangers for U-shaped flow, a corresponding embodiment will be described with reference to Fig. 103. Fig. 103 shows the frame 46 already described above with reference to Fig. 26, including the partition 52, the longitudinal side edges 48a and 48b, the narrow side edges 49a and 49b, the first frame section 50, and the flow chamber 53. To avoid repetition, reference is made to the description of the frame 46 above in relation to Fig. 30a. In Fig.Figure 103 shows that a turbulator 163 suitable for U-flow is now arranged in the frame 46. This turbulator consists of two turbulator segments 164a and 164b, each having turbulator elements 165a and 165b, which are arranged or run at an angle to the longitudinal side edges 48a and 48b. The separating web 52 is located midway between the turbulator segments 164a and 164b. The turbulator segments 164a and 164b have eight outer edges 166a, b, c, d, e, f, and g, the position and shape of which correspond to the position and shape of the outer edges 126a–g of the turbulator 122. Reference is made to the explanations provided therein (see Figure 72). Overall, the turbulator 163 looks essentially the same as the turbulator 122. The only difference is the use of additional turbulator segments 167a, b, c, d and e.The position and shape of these additional turbulator segments 167a–g are shown in Fig. 103 and therefore do not need to be described in detail here. A special feature exists with regard to the two additional turbulator segments 167d and 167e, as these also extend perpendicularly from the narrow side edge 49a along the separating web 52 towards the flow chamber 53. This leads to yet other flow effects for the media M1 and M2 and thus also to different 00159604-0113 18.11.2025 PCT / DE09£^|ößffi115.

[0661] 1S-1 l-"2Ü25"O0W9eO4-©113

[0662] 100

[0663] Heat transfer results due to the flow channels 168a - g.

[0664] At the end of the description of various embodiments of the plate heat exchanger according to the invention in frame construction, a turbulator 169 designed for X-flow with additional turbulator segments and flow channels will now be described with reference to Fig. 104, in which the turbulator 169 is surrounded by four triangular flow channels 170a, b, c and d. The turbulator 169 and four additional turbulator segments 171a, b, c and d are again arranged in the frame 2. The turbulator 169 has four straight outer edges 172a, b, c and d, which, however, do not run parallel, but rather at an acute angle to the longitudinal side edges 3a and 3b or narrow side edges 4a and 4b. This can be clearly seen in Fig. 104.The same applies to the side edges 173a, b, c and d of the additional turbulator segments 171a-d facing the flow channels 170a-d, which also run obliquely at an acute angle to the longitudinal side edges 3a and 3b as well as the narrow side edges 4a and 4b. It follows that all four flow channels 170a-d have a triangular shape. This also leads to specific flow and heat transfer effects when turbulators 169 designed in this way with additional turbulator elements 171a-d are used in plate heat exchangers.

[0665] The following describes a plate heat exchanger 174 in shell construction with reference to Figures 105a to 118c. This heat exchanger is designed for X-flow and is shown in its assembled and operating states in Figures 105a, 105b, 106a, 106b, and 106c. This plate heat exchanger 174 consists of shells 175 arranged one above the other in a stacked configuration.

[0666] A detailed view of such a bowl 175 can be seen in Figs. 109a, b, c and d. Fig. 109b shows that the 00159604-0114 18.11.2025 PCT / DE0S£^|ößffi115

[0667] ■1«-= 1'1 -2©25=00159B -Q114

[0668] 101

[0669] Shell 175, like the frame 2 described above, has a rectangular shape with four straight edges: two longitudinal edges 176a and 176b, which are parallel to each other, and two narrow edges 177a and 177b, which are perpendicular to these longitudinal edges 176a and 176b and are also parallel to each other. The shells 175 of the plate heat exchanger 174 are arranged between an upper end plate 5 and a lower end plate 6, which have already been used in the plate heat exchangers 1, 28, 45, 66, 92, 121, 133, and 149 described above, meaning they have the same design and function or mode of operation. Thus, the shell 175 shown, for example, in Fig.

[0670] The upper end plate 5 of the plate heat exchanger 174, shown in Fig. 107, has inlets 11a and 11b in its corner areas for the two media M1 and M2 flowing into the plate heat exchanger 174, as well as outlets 11c and 11d for discharging these media M1 and M2 from the plate heat exchanger 174. Connection nozzles 12 are also provided at the inlets 11a and 11b and the outlets 11c and 11d of the upper end plate 5. The flow through the plate heat exchanger 174 is illustrated by the arrows shown in Fig. 108 and corresponds in principle to the flow through the plate heat exchanger 1, which is shown schematically in Fig. 5. Therefore, a further drawing is omitted here. This flow-through principle is known in the plate heat exchangers of the generic type and therefore does not need to be described again in detail here with regard to the plate heat exchanger 174.From the figures.

[0671] However, as can be seen in Figures 107 and 108, in the present embodiment of the plate heat exchanger 174, a so-called X-flow takes place. In this case, the media M1 and M2 enter the plate heat exchanger 174 through the inlets 11a and 11b of the upper end plate 5. The medium M1 then initially flows in the uppermost level, that is, in the uppermost shell 175, which is located at the very top in Figure 108.

[0672] 18-11-2025-W1 596 W-01:15

[0673] 102

[0674] in a diagonal direction, that is, towards the diagonally opposite outlet 11c of the upper end plate 5. This flow, however, does not only take place in the uppermost shell 175, but in all levels of the plate heat exchanger 174, because the media M1 and M2, as can also be seen in Fig. 108, also enter all other shells 175 located below the upper end plate 5 through the inlets 11a and 11b. Thus, as shown in Fig. 108, the medium M2 also flows diagonally in the further shell 175 located below the aforementioned uppermost shell 175, but in a direction corresponding to the diagonal from the inlet 11b to the outlet 11d of the upper end plate 5.To enable this, each bowl 175 has a trough-shaped design such that it has a base plate 178 and passages 179a, b, c and d located in its corner regions and aligned with the four aforementioned inlets 11a and 11b and outlets 11c and 11d of the upper end plate 5 for the passage of the media M1 and M2. The position of these passages 179a-d in the four corner regions of the rectangular bowl 175 is particularly clear in the figure.

[0675] Figure 109b shows that the bowl 175 has a trough-like shape. This is clearly visible, for example, in Figures 107, 108, and 109a. These figures also show that side walls 180a, b, c, and d are present on the four side edges of the base plate 178, i.e., on the longitudinal side edges 176a and 176b and the narrow side edges 177a and 177b of the bowl 175. The four side walls 180a-d have a certain height, which is visible, for example, in the side views of Figures 111b and 111c. It is particularly evident in these drawings that the outer surfaces 181a, b, c, and d of the side walls 180a-d are not perpendicular to the base plate 178, but rather at an angle to it. This makes it possible to arrange several trays 175 on top of each other in a stacked manner, whereby the underside of a tray 175 is received and held in the respective trough-shaped tray 175 below it, without being able to slip sideways.00159604-0116 18.11.2025 PCT / DE0S£^|ößffi115.

[0676] •lÄ-l l-2025-0ffl59ß® ; <-®31£

[0677] 103

[0678] The passages 179a-d of the shells 175 are aligned with the inlets 11a and 11b and outlets 11c and 11d of the upper end plate 5 and the lower end plate 6, respectively, to allow the passage of media M1 and M2. In the present case of the X-flow through the plate heat exchanger 174, the two diagonally opposite passages 179a and 179c of the shell 175 each have an annular projection 182a and 182b, which can be seen, for example, in Figures 107 and 109a. In the assembled or operating state of the plate heat exchanger 174, the underside 178b of the base plate 178 of the shell 175 above rests on these annular projections 182a and 182b. On the underside 178b of the base plate 178, in the area of ​​the two other passages 179b and 179d, there are elevations 183a and 183b, which serve to close the passages 179a and 179c of the shell 175 lying underneath in the assembled state.In this context, it should be noted that here too, in the plate heat exchanger 174, two adjacent shells 175 arranged one above the other are always rotated 180° relative to each other, so that their respective passages 179a-d are also arranged alternately. A medium M1 or M2 can thus flow within a shell 175, as indicated by the arrows in Fig. 108, from passage 179b to passage 179d or vice versa, via the upper surface 178a of the base plate 178. This is also due to the fact that the ring-shaped elevations 182a and 182b on the upper side 178a of the base plate 178 and the elevations 183a and 183b on the lower side 178b of the base plate 178 result in the base plates 178 of two adjacent superimposed shells 175 also being at a distance from each other and serving as a medium passage for the conveyance of the media M1 and M2.The plate heat exchanger 174, in its assembled state, is located between the spaced-apart base plates 178 of two 00159604-0117 18.11.2025 PCT / DE0S£^|ößffi115.

[0679]

[0680] I®- 11 -2025-©01596l34-'0117

[0681] 104

[0682] The space formed by the superimposed shells 175, which serves as a medium passage, therefore also constitutes a so-called flow chamber 184, which corresponds in principle to the flow chamber 15 of the plate heat exchanger 1. To avoid repetition, reference is made here to the relevant explanations. In other words, the space formed by the top surface 178a of the base plate 178 and the inner surfaces 185a, b, c, and d of the side walls 180a-d of the base plate 178 constitutes the flow chamber 184 of the trough-shaped shell 175. It follows that the space formed between the underside of the upper end plate 5 and the top surface 178a of the base plate 178, the uppermost shell 175 in the assembled state, also forms a medium passage for the medium M1 or M2.

[0683] Figures 107 and 108 show that a turbulator 186 is arranged in each of the flow chambers 184 of the shells 175. These turbulators 186 extend over the entire area of ​​the flow chambers 184 of the shells 175. In Figures 107 and 108, the turbulators 186 are shown in a simplified representation, from which it is already evident that they consist of corrugated rib-shaped turbulator elements 187 that run parallel to each other, with the spacing between them being equal in this embodiment. The arrangement and shape of the turbulator 186 with the turbulator elements 187 in a shell 175 are particularly clear in Figure 11. The shell 175 with the turbulator 186 shown in Figure 11 is the shell 175 or the turbulator 186 that is shown in Figures 107 and 108.Figures 107 and 108, viewed from the upper end plate 5, represent the second shell 175 and the second turbulator 186 from above, respectively, in this position and orientation. Figure 12 illustrates that the corrugated turbulator elements 187 are not perpendicular or parallel, but at an oblique angle to the longitudinal side edges 176a and 176b of the shell. 00159604-0118 18.11.2025 PCT / DE0S£^ / |ößffi115.

[0684] 105

[0685] 175 are arranged, with this angle being formed between the longitudinal direction of the turbulator elements 187 and one of the two longitudinal side edges 176a and 176b, and in this embodiment is 25°, i.e., as with the turbulator elements 18 of the turbulator 17. In contrast to the turbulator 17, which extends over the entire area of ​​the flow chamber 15, the turbulator 186 extends only over a partial area of ​​the flow chamber 184. In this embodiment, the turbulator 186 is designed such that it forms four flow channels 188a, b, c and d, the shape and position of which can be seen, for example, in Figs. 111c and 112a. This is therefore again a combination solution for a plate heat exchanger 174, which is designed for X-flow, in which the turbulator elements 187 are arranged at an angle to the longitudinal side edges 176a and 176b of the shell 175 and four flow channels 188a-d are provided.The shell 175 with the turbulator 186 is comparable to the combination solution described in Figures 53 to 60b using the plate heat exchanger 92 as an example. The turbulator 186 therefore also has four outer edges 189a, b, c, and d. These outer edges 189a-d of the turbulator are adjacent to, or face, the inner surfaces 185a-d of the respective neighboring side walls 180a-d of the shell 175. The shape of the outer edges 189a-d can be seen particularly in Figures 11a and 112a, as well as in the detailed views of the turbulator in Figures 113, 114a, 117, and 118a. The outer edges 189a-d are therefore not straight, but curved or arc-shaped, with the outer edges 189a and 189c being convex and the outer edges 189b and 189d being concave.The position, arrangement, and shape of the flow channels 188a-d, in conjunction with the angular arrangement of the turbulator elements 187 in the individual planes of the plate heat exchanger 174 formed by the shells 175, result in the X- 00159604-0119 18.11.2025 PCT / DE0S£^|ößffi115 provided in this embodiment of the plate heat exchanger 174.

[0686]

[0687] IS- 11 19

[0688] 106

[0689] The flow through the heat exchanger creates special flow conditions that lead to particularly advantageous heat transfer effects. Therefore, to avoid repetition, reference is made here again to the above embodiments of the plate heat exchangers manufactured in frame construction, in particular the plate heat exchanger 92, which also combines angularly arranged turbulator elements 94 with four flow channels 95a-d. For the sake of completeness, it should also be noted here that the turbulator 186 also has recesses 190a, b, c and d in the corner areas where its outer edges 189a-d meet, which serve the same purpose as the recesses 97a-d already mentioned in the example of the turbulator 93.

[0690] While Figures 107 to 114a show the corrugated turbulator elements 187 only in a simplified representation to illustrate their longitudinal direction, these turbulator elements 187 are shown in more detail in Figures 115 to 118a. This also applies to the side views according to Figures 118b and 118c. For better understanding, the corrugated shape of the turbulator elements 187 is also made more clearly visible by the enlarged or cross-sectional view according to Figure 112c.

[0691] Figures 119 and 120 show the shell 175, already described with reference to Figures 105a to 118a, with a turbulator 191 arranged therein for X-flow. This differs from the turbulator 186 only in the shape or course of its outer edges 192a, b, c, and d. This different shape is also visible when comparing the shapes of the turbulators 191 and 186 shown in purple in Figures 120 and 120. Unlike the turbulator 186, the turbulator 191 has only four concavely curved outer edges 192a-d. Between these turbulator outer edges 192a-d and the respective adjacent inner surfaces 185a-d of the side- 00159604-0120 18.11.2025 PCT / DE0S£^|ößffi115

[0692]

[0693] IS-I3. -2025-00153604-0120

[0694] 107

[0695] The walls 180a-d of the shell 175 thus form four flow channels 193a, b, c and d through which the media M1 and M2, respectively, can flow. The flow channels 193a-d are therefore located in the open or unobstructed area, i.e., the area that does not completely fill the flow chamber 184. Furthermore, the turbulator 191 also has corrugated rib-shaped turbulator elements 194, which are arranged at an angle to the longitudinal side edges 176a and 176b of the shell 175.

[0696] Figures 121 and 122 now illustrate another embodiment of a combination solution with a shell 175 and a turbulator 195 arranged therein, which is suitable or designed for X-shaped flow through a plate heat exchanger and has angularly arranged turbulator elements 196, wherein the turbulator 195 occupies only a portion of the flow chamber 184, resulting in four flow channels 197a, b, c, and d. As can be seen in Figure 122, the turbulator 195 has four straight outer edges 198a, b, c, and d. These straight outer edges 198a-d run parallel to the known straight inner surfaces 185a-d of the side walls 180a-d of the shell 175. The resulting open or unfilled areas, i.e., areas that do not completely fill the flow chamber 184, form the flow channels 197a-d, which consequently also have a straight course.Therefore, this embodiment of the turbulator 195 is comparable to the one shown in Fig.

[0697] The embodiment of the turbulator 98 shown in 61 is comparable to the straight flow channels 100a-d.

[0698] The embodiment illustrated in Figures 123 and 124, in which a turbulator 199 and four additional turbulator segments 200a, b, c, and d are used in a shell 175 for an X-shaped flow through a plate heat exchanger, resulting in four flow channels 201a-d. This variant is comparable to the embodiment described with reference to Figures 78 to 89, 00159604-0121 18.11.2025 PCT / DE0S£^|ößffi115

[0699] 108

[0700] The frame 2 with the turbulator 134 and the additional turbulator segments 136a-d as well as the flow channels 138a-d are comparable, so that, to avoid repetition regarding the basic operating principle, reference is made here to the description given there. The turbulator 199 also has corrugated rib-shaped turbulator elements 202, which run at an angle (here 25°) to the longitudinal side edges 176a and 176b of the shell 175. Around the turbulator 199, on the inner surfaces 185a-d of the side walls 180a-d of the shell 175, are the additional turbulator segments 200a-d, which extend over the entire length of the longitudinal side edges 176a and 176b and the narrow side edges 177a and 177b, respectively. The additional turbulator segments 200a-d thus extend along the side walls 180a-d from one of the passages 179a-d present there in the direction of the passage 179a-d located at the other end of the respective side wall 180a-d.In the present embodiment, the side edges 203a, b, c, and d of the additional turbulator segments 200a-d facing the flow channels 201a-d are straight. This means that the additional turbulator segments 200a-d have the same width and run straight throughout. In contrast, the four outer edges 204a, b, c, and d of the turbulator 199 are odd, namely curved or arc-shaped, with the opposing outer edges 204a and 204c being convex and the likewise opposing outer edges 204b and 204d being concave. This particular design also leads to particularly advantageous flow conditions and consequently favorable heat transfer effects in a shell-type plate heat exchanger.

[0701] Figures 125 and 126 also show a possible embodiment in which a turbulator 205 with corrugated turbulator elements 206 is arranged in the already described shell 175. These turbulator elements 206 run at an angle (here 25°) to the longitudinal side edges 176a and 176b of the shell. 00159604-0122 18.11.2025 PCT / DE0S£^|ößffi115

[0702] 8- 1:r-i2025-ß0159€04-01Ä2

[0703] 109

[0704] 175 and extend over the entire area of ​​the flow chamber 184. Therefore, in this embodiment, neither additional turbulator segments nor flow channels are provided. The same applies to the variant of a turbulator 207 arranged in a shell 175 shown in Fig. 127. This turbulator 207 differs from the turbulator 205 only in that its turbulator elements 208 run at a different angle (45°) to the longitudinal side edges 176a and 176b of the shell 175.

[0705] It should also be noted that the turbulator elements 187, 194, 196, 202, 206 and 208 of the turbulators 186, 191, 195, 199, 205 and 207 described above all run at an angle to the longitudinal side edges 176a and 176b of the shell 175, but in variants not described in detail here could also run parallel or perpendicular to the longitudinal side edges 176a and 176b.

[0706] Finally, Figures 128 to 129c show a shell 209 designed or suitable for I-flow through a shell-type plate heat exchanger. This shell 209 is comparable to the frame 29 described with reference to Figures 22a-d, which is also designed for I-flow. In the frame 209, the two collecting channels 30a and 30b are located in the two corner regions of the frame 29 on its longitudinal side edge 31a to enable I-flow through a plate heat exchanger 28. For this purpose, the shell 209 includes a base plate 210 with four passages 211a, b, c, and d arranged in its corner regions. The two passages 211c and 211d each have annular projections 213a and 213b on the upper surface 212 of the base plate 210.Figure 129a shows that the two passages 211c and 211d with the ring-shaped elevations 213a and 213b are located in the corner regions of the base plate 210, which lie on the longitudinal side edge 214b of the shell 209. Since the shell 209 also has a rectangular shape 00159604-0123 18.11.2025 PCT / DE0S£^|ößffi115.

[0707]

[0708] IB- 1 l-2. Q25-0Q15:98ü

[0709] 110

[0710] The other longitudinal side edge 214a lies parallel to the longitudinal side edge 214b, i.e., where the passages 211a and 211b are located. On the underside 215 of the base plate 210, in the area of ​​the passages 211a and 211b, projections 216a and 216b are provided, which correspond in their design and function to the projections 183a and 183b on the underside 178b of the base plate 178 of the shell 175, so that, to avoid repetition, reference is made to the relevant explanations. Otherwise, the shell 209, like the already described shell 175, comprises side walls 218a, b, c and d in the area of ​​its longitudinal side edges 214a and 214b and its narrow side edges 217a and 217b. To form the tub shape of the bowl 209, the side walls 218a-d, as well as the already described side walls 180a-d of the bowl 175, are not arranged perpendicular to the base plate 210, but slightly angled to it, in order to better enable the stacking of several bowls 209.Furthermore, the space enclosed by the side walls 218a-d and the top surface 212 of the base plate 210 of the trough-shaped shell 209 also serves here as a flow chamber 219, which acts as a medium passage for the media M1 and M2. A turbulator, which can be arranged in the flow chamber 219, is not shown in Figures 128 and 129a-c. This is possible in principle for the shell 209 just as it is for the previously described embodiments of frames and shells with turbulators for use in plate heat exchangers for intermittent flow. This also applies to corresponding variants already described with angled, corrugated fin-shaped elements of a turbulator and optionally provided flow channels and / or additional turbulator segments. Thus, numerous variants are also possible for a shell like the shell 209 for intermittent flow.

[0711] Finally, Figures 130 to 131c show a shell 220 that is designed or suitable for U-shaped flow through a shell-type plate heat exchanger. This 00159604-0124 18.11.2025 PCT / DE0S£^|ößffi115

[0712] I

[0713]

[0714] B- 1:i'-20e5-0015B6©4“01Ä4

[0715] ill

[0716] Shell 220 is comparable to the frame 46 described with reference to Figures 29 to 30c, which is also designed for U-shaped flow. In the frame 46, the two collecting channels 47a and 47b are located in the two corner regions of the frame 46 at its narrow side edge 49b to enable U-shaped flow in a plate heat exchanger. For this purpose, shell 220 includes a base plate 221 with four passages 222a, b, c, and d arranged in its corner regions. The two passages 222a and 222d each have annular projections 224a and 224b on the upper surface 223 of the base plate 221. Fig. 131a shows that the two passages 222a and 222d with the ring-shaped elevations 224a and 224b are located in the corner areas of the base plate 221, which lies on the narrow side edge 225a of the shell 220.Since the shell 220 also has a rectangular shape, the other narrow side edge 225b lies parallel to the narrow side edge 225a, i.e., where the passages 222b and 222c are located. On the underside 226 of the base plate 221, in the area of ​​the passages 222b and 222c, projections 227a and 227b are provided, which correspond in their design and function to the projections 183a and 183b on the underside 178b of the base plate 178 of the shell 175, so that, to avoid repetition, reference is made to the relevant explanations. Otherwise, the shell 220, like the already described shell 175, comprises side walls 229a, b, c, and d in the area of ​​its narrow side edges 225a and 225b and its long side edges 228a and 228b.To form the trough shape of the shell 220, the side walls 229a-d, like the already described side walls 180a-d of the shell 175, are not arranged perpendicular to the base plate 221, but slightly angled to it, in order to facilitate the stacking of several shells 220. Just as the frame 46 has the separating web 52 extending from the narrow side edge 49a into the flow chamber 53, the shell 220 also includes a separating web 230 extending from the narrow side edge 229b into the flow chamber 231. The design and function of this separating web 230 correspond to 00159604-0125 18.11.2025 PCT / DE0S£^|ößffi115.

[0717]

[0718] IS- 11-ÄO25-'OO1BS604-. O12E

[0719] 112

[0720] The design and function of the separating rib 52 of the shell 46 do not need to be explained again here.

[0721] Furthermore, the flow chamber 231 is also bounded here by the side walls 229a-d and the top surface 223 of the base plate 221. The flow chamber 231 of the trough-shaped shell 220 thus also serves as a medium passage for the media M1 and M2, respectively. Not shown in Figures 130 and 131a-c is a turbulator that can be arranged in the flow chamber 231. This is possible in principle for the shell 220 just as it is for the previously described embodiments of frames and shells with turbulators for use in plate heat exchangers for U-flow. This also applies to corresponding variants already described with angled, corrugated fin-shaped elements of a turbulator and optionally provided flow channels and / or additional turbulator segments. Thus, numerous variants are also possible for a shell like the shell 220 for U-flow.

[0722] Finally, it should be noted that the numerous exemplary embodiments described above do not yet represent all possible variations or combinations of plate heat exchangers according to the invention in frame or shell construction. Despite the multitude of variations already mentioned, many more variations and combinations are possible. All possible size and dimension ratios can also be varied; for example, the lengths of the longitudinal and narrow edges of the frames and shells, as well as the angular dimensions of the turbulator elements and / or the additional turbulator segments, can be freely selected and combined, including in combination with all technically feasible shapes that the outer edges of the turbulators and additional turbulator segments can have.

Claims

00159604-0127 November 18, 2025 PCT / DE0Ö2^|öß@115 I B- 11 -B025^0015Rß04=\01Ä7 113 Plate heat exchanger - patent claims:

1. Plate heat exchanger (1, 28, 45) with a number of frames (2, 29, 46) arranged stacked on top of each other between two end plates (5, 6), wherein - a separating plate (7) for the formation of media-carrying medium passages for the passage of at least two different media (M1, M2) is located between two adjacent frames (2, 29, 46), one or both end plates (5, 6) have inlets (11a, 11b) for feeding the media (M1, M2) into the medium passages and outlets (11c, 11d) for removing the media (M1, M2) from the medium passages, - each partition plate (7) has at least four passages (10a - d) aligned with the aforementioned inlets (11a, 11b) and outlets (11c, 11d) of the end plates (5, 6) for the passage of the media (M1, M2), of which two passages (10a - d) are in the assembled or 00159604-0128 11 / 18 / 2025 PCT / DE0S£^|ößffi115 18-11 "2025-00159604"-01> S 114 The operating state of the plate heat exchanger (1, 28, 45) is closed. - the frames (2, 29, 46), the end plates (5, 6) and the partition plates (7) are of the same size and have a rectangular or square shape with four straight side edges, of which two long side edges (3a, 3b; 8a, 8b; 31a, 31b; 48a, 48b) are parallel to each other and two short side edges (4a, 4b; 9a, 9b; 32a, 32b; 49a, 49b) are perpendicular to these long side edges (3a, 3b; 8a, 8b; 31a, 31b; 48a, 48b) and are also parallel to each other, - each frame (2, 29, 46) has an outer closed first frame section (14, 33, 50) formed by its longitudinal side edges (3a, 3b; 8a, 8b; 31a, 31b; 48a, 48b) and narrow side edges (4a, 4b; 9a, 9b; 32a, 32b; 49a, 49b) and this first frame section (14, 33, 50) dividing into a central flow chamber (15, 35, 53) and at least two collecting channels (13a, 13b; 30a, 30b; 47a, 47b) second frame sections (16a, 16b; 34a, 34b; 51a, 51b) wherein these collecting channels (13a, 13b; 30a, 30b; 47a, 47b) are aligned for the passage of the media (M1, M2) to the respective passages (10a - d) of the adjacent partition plate (n) (7), and - in the flow chamber (15, 35, 53) of at least one frame (2, 29, 46) a turbulator (17, 19, 20, 21; 36, 39, 42; 54, 60, 61) is arranged with corrugated rib-shaped turbulator elements (18, 22; 38a, 38b; 40a, 40b; 44a, 44b; 56a, 56b; 63a, 63b; 65a, 65b) arranged at parallel intervals from each other. 00159604-0129 11 / 18 / 2025 PCT / DE0S£^|ößffi115 18-11 115 extends over the entire area or a part of the flow chamber (15, 35, 53), characterized by that the corrugated rib elements (18, 22; 38a, 38b; 40a, 40b; 44a, 44b; 56a, 56b; 63a, 63b; 65a, 65b) of the turbulator (17, 19, 20, 21; 36, 39, 42; 54, 60, 61) are arranged at an angle to the longitudinal side edges (3a, 3b; 8a, 8b; 31a, 31b; 48a, 48b) of the first frame section (14, 33, 50) of the frame (2, 29, 46), wherein this angle is between the longitudinal direction of the corrugated rib turbulator elements (18, 22; 38a, 38b; 40a, 40b; 44a, 44b; 56a, 56b; 63a, 63b; 65a, 65b) and one of the two longitudinal side edges (3a, 3b; 8a, 8b; 31a, 31b; 48a, 48b) of the first frame section (14, 33, 50) of the frame (2, 29, 46) is formed and is between 2° and 88°.

2. Plate heat exchanger (1, 28, 45) according to claim 1, characterized in that the angle between the longitudinal direction of the turbulator elements (18, 22; 38a, 38b; 40a, 40b; 44a, 44b; 56a, 56b; 63a, 63b; 65a, 65b) and one of the two longitudinal side edges (3a, 3b; 31a, 31b; 48a, 48b) of the first frame section (14, 33, 50) of the frame (2, 29, 46) is preferably 20°, 30°, 35°, 40°, 45°, 50° or 55°.

3. Plate heat exchanger (1, 28, 45) according to one of the preceding claims, characterized in that the length / width ratio of the end plates (5, 6), the frames (2, 29, 46) and the partition plates (7) is dimensioned such that the length of the longitudinal side edges (3a, 3b; 8a, 8b; 31a, 31b; 48a, 48b) is 4:3 in relation to the length of the narrow side edges (4a, 4b; 9a, 9b; 32a, 32b; 49a, 49b) and the angle between the longitudinal direction of the turbulator elements (18, 22; 38a, 38b; 40a, 40b; 44a, 44b; 56a, 56b; 63a, 63b; 65a, 65b) and 00159604-0130 November 18, 2025 PCT / DE0S£^|ößffi115 IS- 11 -2025-00159504^0130 116 one of the two longitudinal side edges (3a, 3b; 8a, 8b; 31a, 31b; 48a, 48b) of the first frame section (14, 33, 50) of the frame (2, 29, 46) is between 20° and 45°, preferably 20°.

4. Plate heat exchanger (1, 28, 45) according to claim 1 or 2, characterized in that the length / width ratio of the end plates (5, 6), the frames (2, 29, 46) and the partition plates (7) is dimensioned such that the length of the longitudinal side edges (3a, 3b; 8a, 8b; 31a, 31b; 48a, 48b) is 150 mm and the length of the narrow side edges (4a, 4b; 9a, 9b; 32a, 32b; 49a, 49b) is 100 mm and the angle between the longitudinal direction of the turbulator elements (18, 22; 38a, 38b; 40a, 40b; 44a, 44b; 56a, 56b; 63a, 63b; 65a, 65b) and one of the two longitudinal side edges (3a, 3b; 8a, 8b; 31a, 31b; 48a, 48b) of the first frame section (14, 33, 50) of the frame (2, 29, 46) between 20° and 45°, preferably 20°.

5. Plate heat exchanger according to one of the preceding claims, characterized in that the inlets (11a, 11b) and outlets (11c, 11d) of the end plates (5, 6), the passages (10a - d) of the partition plates (7) aligned with them and the corresponding collecting channels (13a, 13b; 30a, 30b; 47a, 47b) of the frames (2, 29, 46) are each located in their corner regions.

6. Plate heat exchanger (1) according to one of the preceding claims, characterized in that, for an X-flow of the media (M1, M2) through the plate heat exchanger (1), the turbulators (17, 19, 20, 21) located in superimposed adjacent frames (2) are arranged such that their corrugated turbulator elements (18, 22) are oriented at opposite angles to the 00159604-0131 11 / 18 / 2025 PCT / DE0S£^|ößffi115 IS-l l“2Q 5-0®159g© -0131 117 Longitudinal side edges (3a, 3b) of the first frame section (14) of the frame (2) are arranged.

7. Plate heat exchanger (1) according to claim 6, characterized in that the dimension of the angles between the longitudinal direction of the turbulator elements (18, 22) and one of the two longitudinal side edges (3a, 3b) of the first frame section (14) of the superimposed adjacent frames (2) is the same for all turbulators (17, 19, 20, 21) of the plate heat exchanger (1).

8. Plate heat exchanger (28) according to one of claims 1 to 5, characterized in that, for a flow of the media (M1, M2) through the plate heat exchanger (28), the turbulator (36, 39, 42) consists of two turbulator segments (37a, 37b; 41a, 41b; 43a, 43b) which are of the same size and each cover half of a flow chamber (35) of the frame (29), wherein the division of the two turbulator segments (37a, 37b; 41a, 41b; 43a, 43b) is located in the middle of the longitudinal side edges (31a, 31b) of the first frame section (33), so that the corrugated turbulator elements (38a, 38b; 40a, 40b; 44a, 44b) the turbulator segments (37a, 37b; 41a, 41b; 43a, 43b) are arranged in opposite angular directions to the longitudinal side edges (31a, 31b) of the first frame section (33) of the frame (29).

9. Plate heat exchanger (45) according to one of claims 1 to 5, characterized in that, for a U-shaped flow of the media (M1, M2) through the plate heat exchanger (45), the turbulator (54, 60, 61) consists of two turbulator segments (55a, 55b; 62a, 62b; 64a, 64b) which have the same size and each cover half of a flow chamber (53) of the frame (46), wherein the division of the two turbulator segments (55a, 55b; 62a, 62b; 64a, 64b) is 00159604-0132 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1-8-11-2025-0015004^0132 118 the center of the narrow side edges (49a, 49b) of the first frame section (50) is located, so that the corrugated turbulator elements (56a, 56b; 63a, 63b; 65a, 65b) of the turbulator segments (55a, 55b; 62a, 62b; 64a, 64b) are arranged in opposite angular directions to the longitudinal side edges (48a, 48b) of the first frame section (50) of the frame (46), wherein a straight separating web (52) enabling U-flow extends from a narrow side edge (49a, 49b) into the flow chamber (53) at the level of the division of the turbulator segments (55a, 55b; 62a, 62b; 64a, 64b).

10. Plate heat exchanger with a number of frames (2) arranged stacked on top of each other between two end plates (5, 6), wherein - a separating plate (7) is located between two adjacent frames (2) to form media-carrying medium passages for the passage of at least two different media (M1, M2), one or both end plates (5, 6) have inlets (11a, 11b) for feeding the media (M1, M2) into the medium passages and outlets (11c, 11d) for removing the media (M1, M2) from the medium passages, - each partition plate (7) has at least four passages (10a - d) aligned with the aforementioned inlets (11a, 11b) and outlets (11c, 11d) of the end plates (5, 6) for the passage of the media (M1, M2), of which two passages (10a - d) are closed in the assembled or operating state of the plate heat exchanger (66), 00159604-0133 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1 119 - the inlets (11a, 11b) and outlets (11c, 11d) of the end plates (5, 6), the passages (10a-d) of the partition plates (7) aligned with these and the corresponding collecting channels (13a, 13b) of the frames (2) are each located in their corner areas, - the frames (2), the end plates (5, 6) and the partition plates (7) are of the same size and have a rectangular or square shape with four straight side edges, of which two long side edges (3a, 3b; 8a, 8b) are parallel to each other and two short side edges (4a, 4b; 9a, 9b) are perpendicular to these long side edges (3a, 3b; 8a, 8b) and are also parallel to each other, - each frame (2) has an outer closed first frame section (14) formed by its longitudinal side edges (3a, 3b) and narrow side edges (4a, 4b) and has this first frame section (14) dividing into a central flow chamber (15) and at least two second frame sections (16a, 16b) dividing it into a central flow chamber (15) and at least two collecting channels (13a, 13b), wherein these collecting channels (13a, 13b) are aligned to allow the media (M1, M2) to pass through to the respective passages (10a-d) of the adjacently arranged partition plate (n) (7), and - in the flow chamber (15) of at least one frame (2) a turbulator (73, 74, 75) formed with corrugated rib-shaped turbulator elements (68, 76) running at parallel distances from each other is arranged, characterized by 00159604-0134 November 18, 2025 PCT / DE0S^|ößffi115 18-1 1-2025-Ö01K96Ö4-Ü13 120 that the turbulator (73, 74, 75) extends only over a partial area of ​​the flow chamber (15), wherein at least between an outer surface of a straight outer edge (77a - d, 80a - d, 82a - d) of the turbulator (73, 74, 75) and the inner surface of the adjacent inner edge (71a - d) of the first frame section (14) of the frame (2) there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber (15), through which the medium (M1, M2) can flow and thus forms a flow channel (78a - d, 79a - d, 81a - d).

11. Plate heat exchanger according to claim 10, characterized in that the at least one outer edge (82a - d) of the turbulator (75) lies at an acute angle obliquely to the adjacent side edge of the first frame section (14), such that the flow channel (81a - d) thus formed has a substantially triangular shape, wherein the short side of this triangular flow channel (81a - d) lies on a collecting channel (13a, 13b) of the frame (2), through which the medium (M1, M2) flows into the frame (2) and to the turbulator (75) located therein.

12. Plate heat exchanger according to claim 10, characterized in that two parallel opposing outer edges (82a - d) of the turbulator (75) are inclined at an acute angle to the respective adjacent side edges of the first frame section (14), such that the flow channels (81a - d) thus formed have a substantially triangular shape, wherein the short side of these triangular flow channels (81a - d) is each located at a collecting channel (13a, 13b) of the frame (2), through which the medium (M1, M2) flows into the frame (2) and to the turbulator (75) located therein. 00159604-0135 11 / 18 / 2025 PCT / DE0S£ / |öß®115 IS- 11 -2025“00159«04"Oil 35 121 13. Plate heat exchanger according to claim 10, characterized in that all outer edges (82a - d) of the turbulator (75) are inclined at an acute angle to the respective adjacent side edges of the first frame section (14), such that the flow channels (81a - d) thus formed have a substantially triangular shape, wherein the short side of these triangular flow channels (81a - d) is each located at a collecting channel (13a, 13b) of the frame (2), through which the medium (M1, M2) flows into the frame (2) and to the turbulator (75) located therein.

14. Plate heat exchanger according to one of claims 10 to 12, characterized in that the acute angle is between 2° and 10°.

15. Plate heat exchanger (66) with a number of frames (2) arranged stacked on top of each other between two end plates (5, 6), wherein - a separating plate (7) is located between two adjacent frames (2) to form media-carrying medium passages for the passage of at least two different media (M1, M2), one or both end plates (5, 6) have inlets (11a, 11b) for feeding the media (M1, M2) into the medium passages and outlets (11c, 11d) for removing the media (M1, M2) from the medium passages, - each partition plate (7) has at least four passages (10a - d) aligned with the aforementioned inlets (11a, 11b) and outlets (11c, 11d) of the end plates (5, 6) for the passage of the media, two of which are 00159604-0136 11 / 18 / 2025 PCT / DE0S£^|ößffi115 I S- 1 l-2Ö25-®0159e©4-; Ql 36 122 (10a - d) are closed in the assembled or operating state of the plate heat exchanger (66), - the inlets (11a, 11b) and outlets (11c, 11d) of the end plates (5, 6), the passages (10a - d) of the partition plates (7) aligned with them and the corresponding collecting channels (13a, 13b) of the frames (2) are each located in their corner areas, - the frames (2), the end plates (5, 6) and the divider plates (7) are of the same size and have a rectangular or square shape with four straight side edges, of which two long side edges (3a, 3b; 8a, 8b) are parallel to each other and two short side edges (4a, 4b; 9a, 9b) are perpendicular to these long side edges (3a, 3b; 8a, 8b) and are also parallel to each other, - each frame (2) has an outer closed first frame section (14) formed by its longitudinal side edges (3a, 3b) and narrow side edges (4a, 4b) and has this first frame section (14) dividing into a central flow chamber (15) as well as second frame sections (16a, 16b) dividing at least two collecting channels (13a, 13b), wherein these collecting channels (13a, 13b) are aligned to allow the media (M1, M2) to pass through to the respective passages (10a - d) of the adjacently arranged partition plate (n) (7), and - in the flow chamber (15) of at least one frame (2) a turbulator (67) formed with corrugated rib-shaped turbulator elements (68, 76) running at parallel distances from each other is arranged, 00159604-0137 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1 S-11 -:2Q25=OOI59ß04-©137 123 characterized by that the turbulator (67) extends only over a partial area of ​​the flow chamber (15), wherein at least between an outer surface of an outer edge (70a - d) of the turbulator (67), which is curved or arcuate or wave-shaped, and the inner surface of the adjacent inner edge (71a - d) of the first frame section (14) of the frame (2) there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber (15), through which the medium (M1, M2) can flow and thus forms a flow channel (69a - d).

16. Plate heat exchanger according to claim 15, characterized in that flow channels are located between two opposing outer edges of the turbulator and the respective adjacent side edges of the first frame section.

17. Plate heat exchanger (66) according to claim 15, characterized in that flow channels (69a - d, 86a - d, 88a - d, 90a - d) are located between all outer edges (70a - d, 86a - d, 88a - d, 90a - d) of the turbulator (67, 83, 84, 85) and the respective adjacent side edges of the first frame section (14).

18. Plate heat exchanger (66) according to one of claims 15 to 17, characterized in that the outer edge (n) (70a - d, 86a - d, 88a - d, 90a - d) of the turbulator (67, 83, 84, 85) is / are curved or arc-shaped, wherein the outer edge (n) (70a - d, 86a - d, 88a - d, 90a - d) extends from the center of the 00159604-0138 11 / 18 / 2025 PCT / DE0S£^|ößffi115 l«-ll-“Ä025-©0aS9R04“Ol 38 124 The flow chamber (15) is, or is, either convex or concave when viewed from the outside.

19. Plate heat exchanger according to claim 10, characterized in that an additional turbulator segment (171a-d) is located between the flow channel (170a-d) and the inner surface of the inner edge (71a-d) of the first frame section (14), which abuts the inner side surface of the inner edge (71a-d) of the first frame section (14) and extends from one of the collecting channels (13a, 13b) located therein in the direction of the collecting channel (13a, 13b) located at the other end of this inner edge (71a-d), wherein the side edge (173a-d) of this additional turbulator segment (171a-d) facing the flow channel (170a-d) is formed either straight or curved or arcuate or wavy and thus at an acute angle is positioned obliquely to the adjacent side edge of the first frame section (14), such that the flow channel (170a - d) thus formed has an essentially triangular shape.

20. Plate heat exchanger according to claim 15, characterized in that an additional turbulator segment is located between the flow channel and the inner surface of the inner edge of the first frame section, the turbulator segment bearing against the inner surface of the inner edge of the first frame section and extending from one of the collecting channels located there towards the collecting channel located at the other end of this inner edge, wherein the side edge of this additional turbulator segment facing the flow channel is straight, curved or arcuate or wavy. 00159604-0139 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1 S'- 11 “2025-001 SSßXHHOl 39 125 21. Plate heat exchanger according to claim 5, characterized in that the turbulator (98, 102) extends only over a partial area of ​​the flow chamber (15), wherein at least between an outer surface of a straight outer edge (99a - d, 105a - d) of the turbulator (98, 102) and the inner surface of the adjacent inner side edge (71a - d) of the first frame section (14) of the frame (2) there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber (15), through which the medium (M1, M2) can flow and thus forms a flow channel (100a - d, 104a - d).

22. Plate heat exchanger (92) according to claim 5, characterized in that the turbulator (93, 106, 107) extends only over a partial area of ​​the flow chamber (15), wherein at least between an outer surface of an outer edge (96a - d, 112a - d, 113a - d) of the turbulator (93, 106, 107), which is curved or arc-shaped or wave-shaped, and the inner surface of the adjacent inner edge (71a - d) of the first frame section (14) of the frame (2) there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber (15), through which the medium (M1, M2) can flow and thus forms a flow channel (95a - d, 110a - d, lila - d).

23. Plate heat exchanger according to claim 21, characterized in that an additional turbulator segment (147a - d) is located between the flow channel (148a - d) and the inner surface of the inner edge (71a - d) of the first frame section (14), the turbulator segment being attached to the inner surface of the inner edge (71a - d) of the first frame section (14). 00159604-0140 11 / 18 / 2025 PCT / DE0S£^|ößffi115 18-1 126 section (14) and extends from one of the sanunei channels (13a, 13b) present there in the direction of the collecting channel (13a, 13b) located at the other end of this inner edge (71a - d), wherein the side edge of this additional turbulator segment (147a - d) facing the flow channel (148a - d) is either curved or arc-shaped or wavy or is straight and thus lies at an acute angle obliquely to the adjacent side edge of the first frame section (14), such that the flow channel (148a - d) thus formed has a substantially triangular shape.

24. Plate heat exchanger (133) according to claim 22, characterized in that an additional turbulator segment (136a-d, 144a-d) is located between the flow channel (138a-d, 145a-d) and the inner surface of the inner edge (71a-d) of the first frame section (14), the turbulator segment bearing against the inner surface of the inner edge (71a-d) of the first frame section (14) and extending from one of the collecting channels (13a, 13b) located therein towards the collecting channel (13a, 13b) located at the other end of this inner edge (71a-d), wherein the side edge (139a-d) of this additional turbulator segment (136a-d, 144a) facing the flow channel (138a-d, 145a-d) - d) is straight, curved or arc-shaped or wavy.

25. Plate heat exchanger according to one of claims 19, 20, 23 or 24, characterized in that the additional turbulator segment(s) (136a - d, 144a - d, 147a - d) and the turbulator (134, 141, 142) are designed with corrugated fin-shaped elements (140a - d) extending at parallel intervals from one another, and these 00159604-0141 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1 S - 11 = 2025"©© 1 127 are arranged at an angle to the longitudinal side edges (3a, 3b) of the first frame section (14) of the frame (2), wherein this angle is formed between the longitudinal direction of the wave-ribbed elements of the respective turbulator segment (136a - d, 144a - d, 147a - d) and one of the two longitudinal side edges (3a, 3b) of the first frame section (14) of the frame (2) and is between 2° and 88° and the angle and orientation of the wave-ribbed elements of the turbulator (134, 141, 142) and of the or the additional turbulator segments (s) (136a - d, 144a - d, 147a - d) are the same or different.

26. Plate heat exchanger (174) with a number of shells (175, 209, 220) arranged stacked on top of each other, wherein - the shells (175, 209, 220) have a trough-shaped form such that the shells (175, 209, 220) have a base plate (178, 210, 221) and side walls (180a - d, 218a - d, 229a - d) located at their side edges, - an upper end plate (5) and / or a lower end plate (6) is or are provided, - the upper end plate (5) rests on and covers the side walls (180a - d, 218a - d, 229a - d) of the uppermost shell (175, 209, 220), - the lower end plate (6) rests against the underside (178b, 215, 226) of the base plate (178, 210, 221) of the lowest shell (175, 209, 220) and covers it, 00159604-0142 November 18, 2025 PCT / DE0S^|ößffi115 16-11 -^025-0.015 60 -014 128 - between two adjacent shells (175, 209, 220) as well as between the upper end plate (5) and the uppermost shell (175, 209, 220) and / or between the lower end plate (6) and the lowest shell (175, 209, 220) there is a medium-carrying medium passage for the passage of at least two different media (M1, M2), - the upper or lower end plate (5, 6) or both end plates (5, 6) each have inlets (11a, 11b) for supplying the media (M1, M2) into the medium passages and outlets (11c, 11d) for discharging the media (M1, M2) from the medium passages, - the base plate (178, 210, 221) of each shell (175, 209, 220) has at least four passages (10a - d) aligned with the aforementioned inlets (11a, 11b) and outlets (11c, 11d) of the end plate (5, 6) for the passage of the media (M1, M2), two of which passages (10a - d) on the upper surface (178a, 212, 223) of the base plate (178, 210, 221) are surrounded by annular projections (182a, 182b; 213a, 231b; 224a, 224b) or rings, on which the underside (178b, 215, 226) of the base plate (178, 210, 221) of the above arranged shell (175, 209, 220) rests on the plate, so that these two passages (10a - d) are closed in the assembled or operating state of the plate heat exchanger (174), - the shells (175, 209, 220) and the upper and lower end plates (5, 6) are of the same size and have a rectangular or square shape with four straight side edges, two of which are longitudinal side edges (176a, 176b; 214a, 214b; 228a, 228b) parallel to each other and two of which are parallel to these longitudinal side edges. 00159604-0143 11 / 18 / 2025 PCT / DE0S£^|ößffi115 IS-l T»a025--00:lg'9604'“0143 129 There are narrow side edges (177a, 177b; 217a, 217b; 225a, 225b) that run at right angles and are also parallel to each other. — the space formed in the assembled or operating state of the plate heat exchanger (174) between the spaced-apart base plates (178, 210, 221) of two superimposed shells (175, 209, 220) forms a flow chamber (184) serving as a medium passage and - in the flow chamber (184, 219, 231) at least one shell (175, 209, 220) a turbulator (186, 191, 195, 205, 207) designed with turbulator elements (187, 194, 196, 206) is arranged, characterized by that the turbulator elements (187, 194, 196, 206, 208) are corrugated, run parallel to each other and extend over the entire area or a part of the flow chamber (184, 219, 231) and that these corrugated elements (187, 194, 196, 206, 208) of the turbulator (186, 191, 195, 205, 207) are arranged at an angle to the longitudinal side edges (176a, 176b; 214a, 214b; 228a, 228b) of the shell (175, 209, 220), this angle being between the longitudinal direction of the corrugated turbulator elements (187, 194, 196, 206, 208) and one of the two The longitudinal side edges (176a, 176b; 214a, 214b; 228a, 228b) of the shell (175, 209, 220) are formed and are between 2° and 88°.

27. Plate heat exchanger (174) according to claim 26, characterized in that the angle between the longitudinal direction of the 00159604-0144 11 / 18 / 2025 PCT / DE0S£^|ößffi115 l-2G25-WT$96m-Ü144 130 turbulator elements (187, 194, 196, 206, 208) and one of the two longitudinal side edges (176a, 176b) of the shell (175, 209, 220) preferably at 20°, 30°, 35°, 40°, 45°, 50° or 55°.

28. Plate heat exchanger (174) according to one of the preceding claims, characterized in that the length-to-width ratio of the upper end plate (5) and / or the lower end plate (6) and the shells (175, 209, 220) is dimensioned such that the length of the longitudinal side edges (176a, 176b; 214a, 214b; 228a, 228b) is 4:3 in relation to the length of the narrow side edges (177a, 177b; 217a, 217b; 225a, 225b) and the angle between the longitudinal direction of the turbulator elements (187, 194, 196, 206, 208) and one of the two longitudinal side edges (176a, 176b; 214a, 214b; 228a, 228b) of the shell (175, 209, 220) between 20° and 45°, preferably 20°.

29. Plate heat exchanger (174) according to claim 26 or 27, characterized in that the length / width ratio of the upper end plate (5) and / or the lower end plate (6) and the shells (175, 209, 220) is dimensioned such that the length of the longitudinal side edges (176a, 176b; 214a, 214b; 228a, 228b) is 150 mm and the length of the narrow side edges (177a, 177b; 217a, 217b; 225a, 225b) is 100 mm and the angle between the longitudinal direction of the turbulator elements (187, 194, 196, 206, 208) and one of the two longitudinal side edges (176a, 176b; 214a, 214b; 228a, 228b) of the shell (175, 209, 220) between 20° and 45°, preferably 20°.

30. Plate heat exchanger (174) according to one of the preceding claims, characterized in that the inlets (11a, 11b) and outlets (11c, 11d) of the upper end plate (5) 00159604-0145 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1 -1 Knowledge*“ 01 5 131 and / or the lower end plate (6) and the passages (10a - d) of the shells (175, 209, 220) directed towards it are located in their respective corner areas.

31. Plate heat exchanger (174) according to one of the preceding claims, characterized in that for an X-flow of the media (M1, M2) through the plate heat exchanger (174) the turbulators (186, 191, 195, 205, 207) located in superimposed adjacent shells (175) are arranged such that their corrugated turbulator elements (187, 194, 196, 206, 208) are arranged in opposite angular directions to the longitudinal side edges (176a, 176b) of the shells (175).

32. Plate heat exchanger (174) according to claim 31, characterized in that the dimension of the angles between the longitudinal direction of the turbulator elements (187) and one of the two longitudinal side edges (176a, 176b) of the superimposed adjacent shells (175) is the same for all turbulators (186, 191, 195, 205, 207) of the plate heat exchanger.

33. Plate heat exchanger according to one of claims 26 to 30, characterized in that for an I-flow of the media (M1, M2) through the plate heat exchanger the turbulator consists of two turbulator segments which have the same size and each cover half of the flow chamber of the shell (209), wherein the division of the two turbulator segments is located in the middle of the longitudinal side edges (214a, 214b) of the shell (209), so that the corrugated turbulator elements of the turbulator segments are arranged in opposite angular directions to the longitudinal side edges (214a, 214b) of the shell (209). 00159604-0146 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1«-1 1-2025-00159604^01 46 132 34. Plate heat exchanger according to one of claims 26 to 30, characterized in that, for a U-shaped flow of the media (M1, M2) through the plate heat exchanger, the turbulator consists of two turbulator segments of the same size, each covering half of the flow chamber of the shell (220), wherein the division of the two turbulator segments is located in the middle of the narrow side edges (225a, 225b) of the shell (220), so that the corrugated turbulator elements of the turbulator segments are arranged in opposite angular directions to the longitudinal side edges (228a, 228b) of the shell (220), wherein a straight separating web (230) enabling the U-shaped flow extends from a narrow side edge into the flow chamber at the level of the division of the turbulator segments.

35. Plate heat exchanger with a number of shells arranged stacked on top of each other, wherein the bowls have a trough-shaped design such that they have a base plate and side walls located at its side edges, - an upper end plate and / or a lower end plate is or are provided, the upper end plate rests on the side walls of the uppermost shell and covers it, - the lower end plate rests against the underside of the base plate of the lowest shell and covers it, between two adjacent shells and between the upper end plate and the uppermost shell 00159604-0147 11 / 18 / 2025 PCT / DE0S£^|ößffi115 I B-11 133 and / or between the lower end plate and the lowest shell there is a media-carrying medium passage for the passage of at least two different media, - the upper or lower end plate or both end plates each have inlets for feeding the media into the medium passages and outlets for removing the media from the medium passages, - the base plate of each shell has at least four passages for the passage of media, aligned with the aforementioned inlets and outlets of the end plate, two of which are surrounded on the upper side of the base plate by annular protrusions or rings on which the underside of the base plate of the shell arranged above rests, so that these two passages are closed in the assembled or operating state of the plate heat exchanger, - the inlets and outlets of the upper end plate and / or the lower end plate and the passages of the shells aligned with them are each located in their corner areas, - the shells and the upper and lower end plates are of the same size and have a rectangular or square shape with four straight edges, two of which are parallel to each other and two of which are perpendicular to these long edges and also parallel to each other, 00159604-0148 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1 8-1'1 -2Oa5”fi035S6W=O348 134 — the space formed between the spaced base plates of two superimposed shells in the assembled or operating state of the plate heat exchanger forms a flow chamber serving as a medium passage and — in the flow chamber of at least one shell, a turbulator designed with turbulator elements is arranged, characterized by that the turbulator extends only over a partial area of ​​the flow chamber, wherein at least between an outer surface of a straight outer edge of the turbulator and the inner surface of the adjacent side wall of the shell there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber, through which the medium can flow and thus forms a flow channel.

36. Plate heat exchanger according to claim 35, characterized in that the at least one outer edge of the turbulator lies at an acute angle oblique to the adjacent side edge of the shell, such that the flow channel thus formed has a substantially triangular shape, wherein the short side of this triangular flow channel lies at a passage in the shell through which the medium flows into the shell and to the turbulator located therein.

37. Plate heat exchanger according to claim 35, characterized in that two parallel opposing outer edges of the turbulator lie at an acute angle to the respective adjacent side edges of the shell, 00159604-0149 November 18, 2025 PCT / DE0Ö2^|ößffi115 1S-.1 135 such that the flow channels thus formed have an essentially triangular shape, with the short side of these triangular flow channels each lying at a passage in the shell through which the medium flows into the shell and to the turbulator located in it.

38. Plate heat exchanger according to claim 35, characterized in that all outer edges of the turbulator lie at an acute angle to the respective adjacent side edges of the shell, such that the flow channels thus formed have a substantially triangular shape, wherein the short side of these triangular flow channels lies at a passage in the shell through which the medium flows into the shell and to the turbulator located therein.

39. Plate heat exchanger according to one of claims 35 to 37, characterized in that the acute angle is between 2° and 10°.

40. Plate heat exchanger with a number of shells arranged in a stacked manner, wherein - the bowls have a trough-shaped form such that they have a base plate and side walls located at its side edges, — an upper end plate and / or a lower end plate is or are provided, the upper end plate rests on the side walls of the uppermost shell and covers it, the lower end plate rests against the underside of the base plate of the lowest shell and covers it, 00159604-0150 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1 -8-11-Ä©25“O0T596O4=O35Ü 136 - between two adjacent shells, as well as between the upper end plate and the uppermost shell and / or between the lower end plate and the lowest shell, there is a medium-carrying medium passage for the passage of at least two different media, - the upper or lower end plate or both end plates each have inlets for feeding the media into the medium passages and outlets for removing the media from the medium passages, - the base plate of each shell has at least four passages for the passage of media, aligned with the aforementioned inlets and outlets of the end plate, two of which are surrounded on the upper side of the base plate by annular protrusions or rings on which the underside of the base plate of the shell arranged above rests, so that these two passages are closed in the assembled or operating state of the plate heat exchanger, - the inlets and outlets of the upper end plate and / or the lower end plate and the passages of the shells aligned with them are each located in their corner areas, - the shells and the upper and lower end plates are of the same size and have a rectangular or square shape with four straight side edges, two of which are parallel to each other and two of which are parallel to these long sides 00159604-0151 11 / 18 / 2025 PCT / DE0S£^|ößffi115 l-10a5“00 96Ö4~ÖI51 137 There are narrow edges that run at right angles and are also parallel to each other. — the space formed in the assembled or operating state of the plate heat exchanger between the spaced-apart base plates of two superimposed shells forms a flow chamber serving as a medium passage and - in the flow chamber of at least one shell, a turbulator designed with turbulator elements is arranged, characterized by that the turbulator extends only over a partial area of ​​the flow chamber, wherein at least between an outer surface of an outer edge of the turbulator, which is curved or arc-shaped or wave-shaped, and the inner surface of the adjacent side wall of the shell there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber, through which the medium can flow and thus forms a flow channel.

41. Plate heat exchanger according to claim 40, characterized in that flow channels are located between two opposing outer edges of the turbulator and the respective adjacent side walls of the shell.

42. Plate heat exchanger according to claim 40, characterized in that between all outer edges of the 00159604-0152 11 / 18 / 2025 PCT / DE0S£^|ößffi115 l'S-1 1-2025” ©0159604-0152 138 The turbulators and the adjacent side walls of the shell contain flow channels.

43. Plate heat exchanger according to one of claims 40 to 42, characterized in that the outer edge (n) of the turbulator is or are curved or arc-shaped, wherein the outer edge (n), viewed from the center of the flow chamber, is either convex or concave.

44. Plate heat exchanger according to claim 35, characterized in that an additional turbulator segment is located between the flow channel and the inner surface of the side wall of the shell, the turbulator segment bearing against the inner surface of the side wall of the shell and extending from one of the passages located there towards the passage located at the other end of this side wall, wherein the side edge of this additional turbulator segment facing the flow channel is either curved or arc-shaped or wavy or is straight and thus lies at an acute angle to the adjacent side wall of the shell, such that the flow channel thus formed has a substantially triangular shape.

45. Plate heat exchanger according to claim 40, characterized in that an additional turbulator segment is located between the flow channel and the inner surface of the side wall of the shell, the turbulator segment bearing against the inner surface of the side wall of the shell and extending from one of the passages located therein towards the passage located at the other end of this side wall, wherein the side facing the flow channel 00159604-0153 11 / 18 / 2025 PCT / DE0S£^|ößffi115 1-8-a 1-2025- 00 l 9€04~0ä53 139 The edge of this additional turbulator segment is straight, curved or arc-shaped, or wavy.

46. ​​Plate heat exchanger according to claim 30, characterized in that the turbulator (195) extends only over a partial area of ​​the flow chamber (184), wherein at least between an outer surface of a straight outer edge (198a - d) of the turbulator (195) and the inner surface of the adjacent side wall (180a - d) of the shell (175) there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber (184), through which the medium (M1, M2) can flow and thus forms a flow channel (197a - d).

47. Plate heat exchanger (174) according to claim 30, characterized in that the turbulator (187, 191, 199) extends only over a partial area of ​​the flow chamber (184), wherein at least between an outer surface of an outer edge (189a - d, 192a - d, 204a - d) of the turbulator (187, 191, 199), which is curved or arc-shaped or wave-shaped, and the inner surface of the adjacent side wall (180a - d) of the shell (175) there is an open or unobstructed area, i.e., an area that does not completely fill the flow chamber (184), through which the medium (M1, M2) can flow and thus forms a flow channel (188a - d, 193a - d, 201a - d).

48. Plate heat exchanger according to claim 46, characterized in that an additional turbulator segment is located between the flow channel and the inner surface of the side wall of the shell, the turbulator segment bearing against the inner surface of the side wall of the shell and extending from 00159604-0154 11 / 18 / 2025 PCT / DE0S£^|ößffi115 18-1 l'-2Ö25-OO : 15980 -015 140 one of the passages located there extends in the direction of the passage located at the other end of this side wall, wherein the side edge of this additional turbulator segment facing the flow channel is either curved or arc-shaped or wavy, or is straight and thus lies at an acute angle obliquely to the adjacent side wall of the shell, such that the flow channel thus formed has an essentially triangular shape.

49. Plate heat exchanger according to claim 47, characterized in that an additional turbulator segment (200a - d) is located between the flow channel (201a - d) and the inner surface of the side wall of the shell (175), which rests against the inner surface of the side wall of the shell (175) and extends from one of the passages (179a - d) located therein in the direction of the passage (179a - d) located at the other end of this side wall, wherein the side edge (203a - d) of this additional turbulator segment (200a - d) facing the flow channel (201a - d) is straight, curved or arc-shaped or wavy.

50. Plate heat exchanger according to one of claims 44, 45, 48 or 49, characterized in that the additional turbulator segment(s) is / are designed with corrugated fin-shaped elements arranged at parallel intervals, and these elements are arranged at an angle to the longitudinal side edges of the shell, wherein this angle is formed between the longitudinal direction of the corrugated fin-shaped elements of the respective turbulator segment and one of the two longitudinal side edges of the shell and is between 2° and 88°, and the angle and orientation of the corrugated fin-shaped elements of the turbulator and the additional turbulator segment(s) are determined by the turbulator segment(s). 00159604-0155 11 / 18 / 2025 PCT / DE0S£^|ööffi115 I S-11-2025-®QIS3€04-:0155 141 additional turbulator segments (s) are the same or different.

51. Plate heat exchanger (1, 28, 45, 66, 92, 121, 133, 149, 174) according to one of the preceding claims, characterized in that the plate heat exchanger (1, 28, 45, 66, 92, 121, 133, 149, 174) has a design suitable for an X, I or U flow and / or for a meandering flow or a multiply meandering flow of the media (M1, M2).

52. Plate heat exchanger (1, 28, 45, 66, 92, 121, 133, 149, 174) according to one of the preceding claims, characterized in that the media (M1, M2) are liquids and / or gases.

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