Heat exchanger device for heating or cooling a fluid

Abstract

Heat exchange device (10) for heating or cooling a fluid, in particular a heating device, comprising a cylindrical chamber (12) through which the fluid flows, with several axially arranged, elongated temperature control elements (28) therein, which form exactly a ring (40) around a central axis (42) of the chamber, and with several guide plates (24) which divide the chamber (12) into several superimposed sub-chambers (38), wherein a flow opening (36) is provided on the outer circumference of each guide plate (24), the shape of which corresponds to the cutting of the guide plate (24) at a secant (44) in order to allow the fluid to flow from one sub-chamber (38) into the next, and wherein the flow openings (36) are arranged alternately on one side and the other side, wherein the flow openings (36) are designed and arranged in such a manner as tothat the temperature control elements (28) are not symmetrical with respect to a connecting line (48) of the flow openings (36) of adjacent guide plates (24), wherein the connecting line (48) is perpendicular to the secant (44), runs through the central axis (42) and is considered in a projection onto a cross-section through the chamber (12), so that the fluid in a flow opening (36) neither flows towards a centrally located temperature control element (28) nor flows centrally between two temperature control elements (28).

Description

[0001] The invention relates to a heat exchange device for heating or cooling a fluid according to the preamble of claim 1.

[0002] A heat exchanger is used to transfer thermal energy to or remove it from a fluid. This raises the fluid to a desired higher or lower temperature. An important application is a high-performance heating device that heats a fluid to high temperatures with significant heating power.

[0003] According to a well-known concept, the fluid flow is directed past several temperature control elements, i.e., heating or cooling elements. These temperature control elements can be designed directly as electric heaters or similar devices. Alternatively, they themselves are permeated by a heat transfer fluid or refrigerant. For optimal heat transfer, the contact area between the fluid and the temperature control element should be as large as possible. Flow conditions have a significant impact on a heat exchanger, as they should not only ensure heat transfer but also minimize pressure drop.

[0004] DE 10 2011 015 215 A1 discloses a heat exchanger with a cylindrical flow chamber that is longitudinally permeated by several temperature elements. The fluid is guided through the flow chamber by means of guide plates, similar to a spiral staircase.

[0005] A shell-and-tube heat exchanger is known from DE 10 2015 102 311 A1. The starting point there is a lateral inlet and outlet of the medium, which flows back and forth in the chamber in stages. However, this is later discarded and a different solution is found. EP 1 938 036 B1 also initially shows a similar design, but then switches to more complex, divided flows. With the numerous tubes of such shell-and-tube heat exchangers, a simple design and favorable flow are not achievable anyway.

[0006] DE 26 57 666 A1 deals with a heat exchanger insert with spaced-apart perforated deflecting discs which are fixed on anchor rods, wherein a positive-locking anchoring of the deflecting discs to the anchor rods is provided by corresponding recesses.

[0007] US Patent 4,699,211 A discloses a heat exchanger that has several baffle plates with lateral openings for the flows. The baffle plates are rotated relative to each other at an angle of approximately 90°.

[0008] GB 221 188 A deals with a device for heat exchange between gases. Several semicircular deflector plates are arranged one above the other. The heating tubes, running perpendicular to these plates, form two concentric rings around a central heating tube, twisted relative to each other, with four heating tubes on the inside and eight on the outside.

[0009] In a heat exchanger according to US 2011 / 0146338 A1, deflection plates are also provided to redirect the flow. The heating tubes here form a kind of nested honeycomb or diamond arrangement in cross-section.

[0010] Another heat exchanger according to CA 2 449 314 A1 uses deflector plates that leave an angled segment, similar to a slice of cake, as a flow opening. Five openings for heating tubes form an approximately uniform ring with this flow opening.

[0011] The known solutions therefore have disadvantages in terms of manufacturing costs, space requirements and flow characteristics.

[0012] It is therefore an object of the invention to provide a heat exchange device with improved flow guidance.

[0013] This problem is solved by a heat exchange device for heating or cooling a fluid according to claim 1. The fluid to be heated or cooled flows in a cylindrical chamber. This chamber contains several elongated temperature control elements, in particular heating rods, which are arranged axially within the chamber and thus parallel to one another, and which cool or heat the flowing fluid. Several guide plates, whose geometry preferably corresponds substantially to the cross-section of the chamber, divide the chamber into several stacked sub-chambers, which form, as it were, levels within the chamber parallel to its base. A flow opening is provided on the outer circumference of each guide plate, through which the fluid flows from one sub-chamber to the next, thus forming several flow layers.The flow openings are arranged alternately on opposite sides of the guide plates, so that the fluid flows radially back and forth from sub-chamber to sub-chamber, roughly following the diameter through the cross-section of the chamber and changing in the opposite direction at the respective transition to the adjacent sub-chamber.

[0014] The invention is based on the fundamental idea of ​​providing the fluid, from its perspective, with a non-symmetrical arrangement of temperature control elements in a central or main flow direction. This is achieved by imagining a connecting line between the flow openings of adjacent guide plates, arranged alternately on the radial opposite side. According to the invention, the temperature control elements are not symmetrical with respect to this connecting line; therefore, the connecting line is not an axis of symmetry for the arrangement of the temperature control elements. While the temperature control elements themselves may certainly form a symmetrical arrangement, this is even the preferred option. However, the axis of symmetry deliberately does not coincide with the connecting line; in particular, both are rotated relative to each other. This consideration refers to a cross-section through the chamber corresponding to a guide plate.The axial offset of the flow openings is irrelevant here, or rather, it is projected onto the same cross-section. Spatially, there is no mirror symmetry about an axis, but rather about a corresponding axially aligned plane.

[0015] The invention offers the advantage of enabling the temperature control of different media while transferring large amounts of heat, particularly achieving high heating output. Despite its compact, cost-optimized design, the system achieves efficient and homogeneous heat transfer within a single flow path that occupies a very small space compared to the size of the temperature control elements. Flow conditions are optimized, and pressure drop remains low. Malfunctions and excessive aging are avoided.

[0016] A temperature control element preferably extends through a given flow opening. There can be several temperature control elements; preferably, exactly one temperature control element is located at least partially within each flow opening. It should be noted that different temperature control elements are located in the opposite flow openings, since the temperature control elements are elongated and not curved. The same temperature control elements are then present in the flow opening leading to the next sub-chamber but one. Because at least one temperature control element is located at least partially within the flow opening, the fluid remains in contact with a temperature control element when transitioning from one sub-chamber to the next, so that heat transfer also occurs in this section of the flow. In this context, the inventive, non-symmetrical arrangement of the temperature control elements can also be expressed in other words.Accordingly, the fluid in the flow opening neither flows towards a centrally located temperature control element nor centrally between two temperature control elements. The arrangement of the temperature control elements, flowing with the fluid, differs on the left side from the right side. Put another way, the temperature control element in the flow opening is indeed subject to flow towards or around it, but this flow is biased either to the right or left.

[0017] The temperature control elements are arranged in a ring and uniformly around a central axis of the chamber. This is again a description based on a cross-sectional view. There is exactly one ring of temperature control elements, with the possibility of adding another element on the central axis. A ring-shaped, uniform arrangement of five temperature control elements, forming a pentagram arrangement, is particularly preferred, possibly with a sixth element at the center.

[0018] The diameter of the ring arrangement is preferably larger than half the diameter and / or smaller than three-quarters of the chamber diameter, and in particular is approximately two-thirds of the chamber diameter. This supports optimized flow guidance. As a numerical example, the chamber has a diameter of 66 mm and the ring arrangement a diameter of 42 mm, corresponding to the aforementioned particularly preferred ratio of two-thirds.

[0019] Preferably, one axis of symmetry of the arrangement of the temperature control elements is rotated relative to the connecting line by one-quarter of the angular spacing of the temperature control elements around the central axis of the chamber. This is again described in a cross-section of the chamber. A non-inventive symmetrical arrangement would exist if, instead of one-quarter, the temperature control elements were not rotated at all or were rotated by one-half of the angular spacing. Any other rotation also leads to a loss of symmetry, but the aforementioned one-quarter rotation is particularly advantageous. It should be noted that a rotation of one-quarter corresponds to a rotation of three-quarters in the opposite direction; this distinction is not further discussed here.

[0020] In particular, in a pentagram arrangement, the axis of symmetry is rotated by 18° relative to the connecting line, or equivalently by 54°. This is because five temperature control elements evenly distributed over a ring have an angular spacing of 72°, and one quarter of this is 18°, or three quarters of it is 54°. In contrast, the arrangement of the temperature control elements would be symmetrical, but not according to the invention, if rotated by 0° or 36°, in which case the flow path would lead exactly through the center of a temperature control element of the ring arrangement or exactly between two temperature control elements of the ring arrangement.

[0021] The shape of the flow opening corresponds to the cutting of the guide plate at a secant. This geometry can also be practically achieved by separating the guide plate accordingly at the secant. The otherwise circular guide plate lacks the corresponding circular segment on its outer circumference, and a suitable flow opening is created there.

[0022] The connecting line and the secant are perpendicular to each other. The secant is therefore not perpendicular to any axis of symmetry of the arrangement of the temperature control elements, but rather rotated, particularly by the angles discussed above. With such a flow opening, a flow path is defined for the fluid between the sub-chambers, which advantageously utilizes the asymmetrical arrangement of the temperature control elements, thus creating particularly favorable flow conditions.

[0023] The secant line preferably runs parallel to an axis of symmetry of the arrangement of the temperature control elements. This has the advantage that a guide plate can simply be turned over. Therefore, identical guide plates can be used alternately; it is not necessary to manufacture and install two sets of different guide plates. The aforementioned rotations of one-quarter and three-quarters of the angular spacing of the temperature control elements are particularly advantageous in this context, as these rotations are retained when the guide plate is turned over.

[0024] The guide plate preferably has through-holes for the temperature control elements, at least one of which extends into the flow opening. The preferred arrangements of the through-holes are the same as those described previously for the temperature control elements, since the through-holes correspond to the cross-section of the arrangement of the temperature control elements. At least one of the through-holes of a guide plate preferably extends into its flow opening. The temperature control element in this through-hole is the one located in the flow opening and around which the fluid flows when passing from one sub-chamber to the next. If one considers a secant line that bounds the flow opening, the through-holes extending into it are not symmetrical, but rather shifted to the right or left due to the non-symmetrical arrangement according to the invention.

[0025] Preferably, identical circuit boards are mounted alternately in reversed orientations in circuit board holders; in particular, projections and grooves ensure that only this alternating orientation can be mounted. As already mentioned, suitable geometry of feedthrough holes and flow openings makes it possible to use the same circuit board in alternating orientations, thus requiring only one component type. Manufacturing the heat exchanger is further simplified by using projections and grooves arranged asymmetrically, which force the circuit boards to be mounted in the correct orientation in their respective holders, thus ensuring foolproof assembly (Poka-Yoke).

[0026] The ratio of the diameter of the cooling elements to the diameter of the chamber is preferably at least 1:5 or 1:4. As before, it is preferably implicitly assumed that the cross-sectional geometries are invariant with respect to axial displacement within the chamber. Specifically, this means that the cooling elements have the same diameter everywhere, and in particular, the same diameter between them. The cooling elements are therefore comparatively thick, leaving relatively little free cross-sectional area between them and thus only a small free flow volume within the chamber. This is intended to support a compact design while still ensuring high heat transfer, and according to the invention, an optimized flow pattern is achieved. As a numerical example, a diameter of 16-17 mm for the cooling elements and a chamber diameter of 66 mm can be cited.

[0027] Preferably, an odd number of guide plates is provided. This has the advantage that the flow begins and ends on the same side of the cylinder wall of the chamber. A number of five guide plates is particularly advantageous. This has proven to be the optimum balance between having as many guide plates and thus as many flow layers as possible for prolonged contact with the temperature control elements on the one hand, and minimizing the pressure drop that would result from the close spacing between many guide plates on the other.

[0028] The guide plates preferably have a spacing of 15-25 mm, 18-22 mm, or 18.5-19.5 mm. As a numerical example, this can be compared to a chamber diameter of 66 mm. The length of the chamber results from the cumulative spacing, which defines the heights of the sub-chambers. Corresponding sub-chambers are formed between the top and bottom of the chamber. The spacing, and thus the heights, of the sub-chambers should be regular, otherwise undesirable differences in the flow and pressure conditions within the sub-chambers will occur. In particular, a spacing of 19.2 mm between the guide plates has proven optimal, preferably in conjunction with the other dimensions already mentioned as a numerical example.

[0029] The diameter of the temperature control elements and the distance between the guide plates are preferably of a certain order of magnitude. The distance is, in particular, at most 50%, 40%, 30%, 20%, or 10% greater. Numerical examples have already been given, namely a temperature control element diameter of 16 mm with an optimal distance of 19.2 mm.

[0030] The chamber preferably has a lateral inlet and a lateral outlet for the fluid. The lateral inlet and outlet ensure that the flow begins and ends parallel to the guide plates, mirroring its largely parallel course as it flows through the chamber. The inlet and outlet are preferably located on the same side, as this simplifies the installation of the heat exchanger. As mentioned previously, an odd number of guide plates should be used; with an even number, the flow terminates radially opposite the inlet, necessitating the placement of the outlet there.

[0031] The method can be further developed with similar features as specified by way of example, but not exhaustively, in the dependent claims following the independent device claim, and exhibits similar advantages.

[0032] The invention is further described below with regard to its features and advantages, using exemplary embodiments and with reference to the drawing. The figures in the drawing show: Fig. 1 an exploded view of a heat exchanger; Fig. 2. A longitudinal section of a heat exchanger to illustrate the flow path; Fig. 3 a three-dimensional representation of an arrangement of guide plates inside a chamber of the heat exchanger device; Fig. 4 a top view of a guide plate; Fig. 5. A close-up of a section of a side of a guide plate for mounting in a guide plate holder; and Fig. 6 a sectional view of the guide plates suspended in the guide plate holder.

[0033] Fig. Figure 1 shows an exploded view of a heat exchanger 10. The fluid to be tempered flows through a cylindrical chamber 12, for example made of chromium-nickel steel, with an inlet 14 and outlet 16 for the fluid located at the top and bottom of the same side of the cylinder. The chamber 12 is sealed fluid-tight by a bottom 18 with a sensor 20 for temperature or safety monitoring and a cover 22.

[0034] Several superimposed flow baffles or guide plates 24 are arranged parallel to the base 18 and cover 22, and thus coaxially with the outer shell of the cylindrical chamber 12, thereby dividing the chamber 12 into a plurality of superimposed sub-chambers. They are held in position by guide plate holders 26 and fixed axially by projections and grooves. The base 18, cover 22, and guide plates 24 have a geometry corresponding to the cross-section of the preferably circular cylindrical chamber 12.

[0035] Several elongated or rod-shaped temperature control elements 28 are guided axially through the chamber 12. A sensor coupling 30 connects the temperature control elements 28 to the sensor 20 and the temperature monitoring system. The temperature control elements 28 are received via bushings 32 in the cover 22 and guided through through holes 34 in the guide plates 24. The guide plates 24 also each have an alternating flow opening 36 on opposite sides of their outer circumference. One of the through-holes 34a leads into the flow opening 36.

[0036] The number and arrangement or geometry of the feedthrough holes 34 correspond to the number and arrangement of the temperature control elements 28. This, in combination with the number and arrangement of the guide plates 24 and the geometry of the flow opening 36, is decisive for optimal flow guidance and will be discussed later with reference to the Fig. 2 to 4 explained in detail.

[0037] The heat exchanger 10 is preferably a high-performance heating cartridge with a heating capacity of several kW, for example 6 kW. The temperature control elements 28 are then rod heaters, preferably with a high surface load of > 10 W / cm². 2 It can withstand temperatures below 260°C. This allows for heat transfer without the fluid cracking, for example, if the fluid contains oil that would decompose at excessively high temperatures. This increases the service life of the temperature control medium. The viscosity can be up to 50 mm. 2The flow rate should be 50 cSt per second. The following fluids are particularly suitable: Thermal G, HL30 (water-glycol), Thermal HS, HY, H5, H10, H20S, HL60, HL80, H250S (silicone-based). The operating temperature range can be, for example, between -90 °C and +250 °C. The pressure drop in the heat exchanger 10 preferably remains below 100 mbar. However, these are only advantageous examples; the heat exchanger 10 is a modular system with variable heating capacity and can be used in different applications. Cooling instead of heating is also conceivable, for example, by using cooling elements 28 instead of immersing them in a cooling medium.

[0038] Fig. Figure 2 shows a longitudinal section through the heat exchanger 10 to illustrate the flow path of the fluid. Fig. Figure 3 is a supplementary three-dimensional view of the arrangement of the guide plates 24. Here and in the following, identical reference symbols denote identical features that are not always repeated. The guide plates 24 create several superimposed sub-chambers 38 between guide plates 24 or between a guide plate and the base 18 or cover 22. Arrows in the flow openings 36 indicate how the fluid flows from sub-chamber 38 to sub-chamber in alternating directions.

[0039] This results in multiple flow layers with a longer residence time of the fluid in chamber 12 and thus improved heat transfer between the temperature control elements 28 and the fluid. This is achieved through direct contact between the surface of the temperature control elements 28 and the fluid. According to the invention, the number and arrangement of the temperature control elements 28 and the guide plates 24 are optimized for uniform flow and consistent flow conditions in chamber 12. Only a relatively small volume of chamber 12 is available for the fluid flow, as the temperature control elements 28 occupy a considerable portion to provide a large surface area for heat exchange.

[0040] The inventors have demonstrated through simulations that the application and circulation of the temperature control elements 28 improves with the number of guide plates 24 installed in chamber 12. However, too many guide plates 24 result in very small gaps between them and thus a very small height for the sub-chambers 38, which in turn leads to a greater pressure loss of the fluid. A number of five guide plates 24, as shown in the Fig. 1-3 also shown, proven.

[0041] Even if the preferred number of five is not used, at least an odd number of guide plates 24 is recommended. This allows the ports 14 and 16 to be placed on the same side of the chamber 12. With an even number of guide plates 24, the ports 14 and 16 must be opposite each other not only axially but also radially, which complicates the integration of the heat exchanger 10 into the overall fluid circuit system.

[0042] Simulations can also be used to optimize the spacing between the guide plates 24. This resulted in an optimal spacing of 19.2 mm. A certain tolerance in the ranges of 18.5–19.5 mm, 18–22 mm, or 15–25 mm also promises good results. For comparison, the chamber has a diameter of 66 mm and a length of 122 mm, which, apart from minor deviations for material thickness, corresponds to the axially cumulative spacing. The temperature control elements 28, for example, have a diameter of 16 mm, so it is advantageous if this is of a similar order of magnitude to the spacing of the guide plates 24, or if the spacing only exceeds the diameter by 10%, 20%, or a similar value.

[0043] Fig. Figure 4 shows a top view of a guide plate 24 of a preferred embodiment of the heat exchanger 10. The inventors determined, through flow simulations, the number, geometry, and arrangement of the temperature control elements 28 shown to scale, which is particularly suitable for good heat transfer without excessive pressure drop. This corresponds to the figure representing the temperature control elements 28 in Fig. The number, geometry and arrangement of the feedthrough holes 34 and the flow opening 36 of the illustrated guide plate 24 are shown in Figure 4. A key concept is the deliberate deviation from symmetry, which will now be explained in detail.

[0044] The temperature control elements 28 preferably form a uniform ring 40 around the central axis 42 of the chamber 12. An additional temperature control element 28 on the central axis 42 is possible. As shown, a preferred number of six temperature control elements 28 are provided. Five of these form a ring arrangement, in this case a regular pentagon or pentagram, with another temperature control element 28 at its center. In the optimized numerical example, the diameter of the ring 40 is 42 mm, with a total diameter of the guide plate 24 and thus of the chamber 12 of 66 mm, with the respective diameters of the temperature control elements 28 and the through-holes 34 being 16 mm. More generally, the diameter of the ring 40 should preferably be larger than half the total diameter, but at most three-quarters of the total diameter of the guide plate 24, and preferably about two-thirds.With these dimensions, the relatively small free space remaining for the flow between the temperature control elements 28 is well divided.

[0045] The flow opening 36, located on the outer circumference, for the transfer of fluid flow from one sub-chamber 38 to the next preferably has the geometry of a circular segment truncated at a secant 44. This enables good flow characteristics and is also easy to handle in manufacturing by removing the circular segment. The secant 44 preferably runs parallel to an axis of symmetry 46 of the arrangement of the temperature control elements 28.

[0046] One of the through-holes 34a transitions into the flow opening. This means that a temperature control element 28 is surrounded by flow when the fluid changes from one sub-chamber 38 to the next. This through-hole 34a is not located centrally, but is offset to one side along the secant 44.

[0047] The arrangement of the temperature control elements 28 is symmetrical overall, for example to that shown in Fig. 4 horizontal axis of symmetry 46. However, according to the invention, this symmetry is intentionally not aligned with the flow openings 36 and thus with a main flow direction of the fluid. This can be expressed, for example, by the orientation of a connecting line 48 between the flow openings 36 of two adjacent guide plates 24, which in Fig. 4 runs vertically. This connecting line 48 is not an axis of symmetry. The arrangement of the temperature control elements 28 is therefore twisted out of symmetry. From the perspective of the flowing fluid, this results in an arrangement of temperature control elements 28 that is not symmetrical to the right and left.

[0048] It is particularly advantageous if the arrangement of the temperature control elements 28 is rotated out of symmetry by a quarter of their angular spacing. Depending on the direction of rotation, this is equivalent to a rotation of three-quarters. In the arrangement of the Fig. 4. The angular spacing of the temperature control elements is one-fifth of a full angle, i.e., 360° / 5 = 72°. One quarter of this is 18°, and accordingly, three quarters in the opposite direction are 54°, as shown in Fig. 4 is also shown. This angle of rotation has two advantages. Firstly, it results in a particularly favorable flow. Secondly, it is possible to reverse the guide plates 24 and thus use identical guide plates 24 alternately, as in Fig. 3. The angle of rotation remains the same, since a rotation of one quarter and a rotation of three quarters are interchangeable.

[0049] The Fig. 5 and Fig. Figure 6 illustrates that a foolproof assembly (Poka-Yoke) can be achieved using identical guide plates that are alternately turned to the other side. This shows Fig. 5 a lateral cutout of the guide plate 24. There a projection 50 is attached, which is offset slightly upwards relative to a horizontal diameter of the guide plate 24 due to different dimensions of the gaps 52a-b above and below it.

[0050] Fig. Figure 6 shows a side view of the arrangement of the guide plates 24 in chamber 12. To enable the fluid to flow back and forth from one sub-chamber 38 to the next, the guide plates 24a-b are to be mounted alternately in one orientation and in the orientation rotated by 180° to it in the guide plate holders 26, as shown in Fig.Figure 3 is even more clearly visible in a three-dimensional view. The guide plate holders now have 26 grooves 54a-b, which are alternately offset a short distance upwards and downwards. The respective projection 50 with its corresponding offset ensures, when engaging the offset grooves 54a-b, that the guide plates 24a-b can only be mounted in the correct orientation.

Claims

[1] Heat exchange device (10) for heating or cooling a fluid, in particular a heating device, comprising a cylindrical chamber (12) through which the fluid flows, with several axially arranged, elongated temperature control elements (28) therein, which form exactly a ring (40) around a central axis (42) of the chamber, and with several guide plates (24) which divide the chamber (12) into several superimposed sub-chambers (38), wherein a flow opening (36) is provided on the outer circumference of each guide plate (24), the shape of which corresponds to cutting off the guide plate (24) at a secant (44) in order to allow the fluid to flow from one sub-chamber (38) into the next, and wherein the flow openings (36) are arranged alternately on one side and the other side, wherein the flow openings (36) are designed and arranged in such a manner as tothat the temperature control elements (28) are not symmetrical with respect to a connecting line (48) of the flow openings (36) of adjacent guide plates (24), wherein the connecting line (48) is perpendicular to the secant (44), runs through the central axis (42) and is considered in a projection onto a cross-section through the chamber (12), so that the fluid in a flow opening (36) neither flows towards a centrally located temperature control element (28) nor flows centrally between two temperature control elements (28). [2] Heat exchange device (10) according to claim 1, wherein a further temperature control element (28) is arranged on the central axis (42). [3] Heat exchange device (10) according to claim 1 or 2, wherein a temperature control element (28) passes through a respective flow opening (36). [4] Heat exchange device (10) according to claim 1 or 2, wherein five temperature control elements (28) are provided in a pentagram arrangement. [5] Heat exchange device (10) according to one of the preceding claims, wherein the diameter of the ring arrangement (40) is larger than half the diameter and / or smaller than three quarters of the diameter of the chamber (12), in particular about two thirds of the diameter of the chamber (12). [6] Heat exchange device (10) according to one of the preceding claims, wherein an axis of symmetry (46) of the arrangement of the temperature control elements (28) is rotated relative to the connecting line (48) by a quarter of the angular distance of the temperature control elements (28) about the central axis (42) of the chamber (12), in particular by 18° in the case of a pentagram arrangement. [7] Heat exchange device (10) according to one of the preceding claims, wherein the secant (44) runs parallel to the axis of symmetry (46) of the arrangement of the temperature control elements (28). [8] Heat exchange device (10) according to one of the preceding claims, wherein the guide plate (24) has through holes (34) for the temperature control elements (28), at least one of which (34a) extends into the flow opening (36). [9] Heat exchange device (10) according to one of the preceding claims, wherein identical guide plates (24) are mounted alternately in reversed orientation in guide plate holders (26), in particular by means of projections (50) and grooves (54a-b) only this alternating orientation can be mounted. [10] Heat exchange device (10) according to one of the preceding claims, wherein the ratio of the diameter of the temperature control elements (28) and the diameter of the chamber (12) is at least 1:5 or 1:

4. [11] Heat exchange device (10) according to one of the preceding claims, wherein an odd number of guide plates (24) is provided, in particular five. [12] Heat exchange device (10) according to one of the preceding claims, wherein the guide plates (24) have a distance of 15-25 mm, 18-22 mm or 18.5-19.5 mm, in particular 19.2 mm, from each other. [13] Heat exchange device (10) according to one of the preceding claims, wherein the diameter of the temperature control elements (28) is at most 50% smaller than the distance between the guide plates (24). [14] Heat exchange device (10) according to one of the preceding claims, wherein the chamber (12) has a lateral inlet (14) and a lateral outlet (16) for the fluid, in particular on the same side.

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