Heat Exchanger Device

Abstract

A heat exchanger device having a body for heat exchange and a fluid flow source is provided, the fluid flow source is configured to provide a fluid flow and the body and the fluid flow source are arranged relative to each other such that the fluid flow provided by the fluid flow source interacts with the body for the purpose of heat exchange. The fluid flow source is a fluidic component which includes at least one deflection device for creating an oscillation of the fluid flow.

Claims

1. A heat exchanger device comprises a body for heat exchange and a fluid flow source, wherein the fluid flow source is configured to provide a fluid flow and wherein the body and the fluid flow source are arranged relative to each other such that the fluid flow provided by the fluid flow source interacts with the body for the purpose of heat exchange, and wherein the fluid flow source comprises a fluidic component which comprises at least one deflection device for creating an oscillation of the fluid flow, wherein the at least one means comprises no movable components.

2. The heat exchanger device according to claim 1, wherein the oscillation of the fluid flow is effected in an oscillation plane.

3. The heat exchanger device according to claim 1, wherein the fluidic component includes a flow chamber which can be flowed through by a fluid flow that enters the flow chamber through an inlet opening of the flow chamber and exits from the flow chamber through an outlet opening of the flow chamber, wherein in the flow chamber, the at least one deflection device for creating the oscillation of the fluid flow is provided at the outlet opening.

4. The heat exchanger device according to claim 3, wherein the inlet opening and the outlet opening each have a cross-sectional area which extends substantially perpendicularly to a longitudinal axis of the fluidic component, which is directed from the inlet opening to the outlet opening, and wherein the flow chamber comprises a main flow channel which extends between the inlet opening and the outlet opening, wherein the main flow channel has a cross-sectional area which extends substantially perpendicularly to the longitudinal axis.

5. The heat exchanger device according to claim 4, wherein the cross-sectional area of the inlet opening is smaller than the cross-sectional area of the outlet opening, or the cross-sectional area of the inlet opening and the cross-sectional area of the outlet opening are equal in size.

6. The heat exchanger device according to claim 4, wherein the cross-sectional area of the inlet opening is smaller than the cross-sectional area of the main flow channel at the narrowest point of the main flow channel, or the cross-sectional area of the inlet opening and the cross-sectional area of the main flow channel at the narrowest point of the main flow channel are equal in size.

7. The heat exchanger device according to claim 4, wherein the cross-sectional area of the inlet opening, the cross-sectional area of the outlet opening, and the cross-sectional area of the main flow channel at the narrowest point of the main flow channel are equal in size.

8. The heat exchanger device according to claim 4, wherein the oscillation of the fluid flow is effected in an oscillation plane, wherein the fluidic component comprises a flow chamber which can be flowed through by a fluid flow that enters the flow chamber through the inlet opening of the flow chamber and exits from the flow chamber through the outlet opening of the flow chamber, wherein in the flow chamber, the at least one deflection device for creating an oscillation of the fluid flow is provided at the outlet opening, wherein the inlet opening has a width which, in the oscillation plane, extends substantially perpendicularly to the longitudinal axis, and wherein the fluidic component has a component depth which extends substantially perpendicularly to the oscillation plane, wherein the component depth which is greater than of the width of the inlet.

9. The heat exchanger device according to claim 1, wherein the body for heat exchange has at least one of: at least one surface which interacts with the fluid flow for the purpose of heat exchange and which is oriented with respect to the fluidic component such that an oscillation plane of the fluid flow exiting from the fluidic component includes a first angle with the at least one surface, wherein the first angle is substantially 90, at least two surfaces which interact with the fluid flow for the purpose of heat exchange, which are arranged at a distance to each other and substantially parallel to each other, and which, are oriented with, respect to the fluidic component such that the fluid flow exiting from the fluidic component extends between the at feast two surfaces, wherein the oscillation plane of the fluid flow exiting front the fluidic component includes a second angel with the at least two surfaces, wherein the second angle is substantially 90, and at least one surface which interacts with the fluid flow for the purpose of heat exchange and which is oriented with respect to the fluidic component such that the oscillation plane of the fluid flow exiting from the fluidic component extends substantially parallel to the at least one surface.

10-11. (canceled)

12. The heat exchanger device according to claim 4, wherein the body for heat exchange has at least one surface which interacts with the fluid flow for the purpose of heat exchange and which is oriented with respect to the fluidic component such that the oscillation plane of the fluid flow exiting from the fluidic component includes an angle with the at least one surface, wherein the angle is substantially 90, and wherein the outlet opening of the fluidic component is arranged at a distance to the at least one surface which interacts with the fluid flow for the purpose of heat exchange, and the outlet opening in the oscillation plane transversely to the longitudinal axis has a width, wherein the distance is at least twice as large as the width of the outlet opening.

13. The heat exchanger device according to claim 3, wherein the body for heat exchange is a flow-through device which has an inlet opening through which the fluid flow enters the body, wherein the inlet opening of the body is arranged downstream of the outlet opening of the fluidic component.

14. The heat exchanger device according to claim 1, wherein the body for heat exchange is a flow-through device which includes a flow chamber which can be flowed through by a fluid flow, and wherein the fluidic component is arranged in the flow chamber of the body.

15. The heat exchanger device according to claim 1, wherein the fluid flow source comprises at least one first fluidic component and at least one second fluidic component, each comprising at least one deflection device for creating an oscillation of the fluid flow, wherein the at least one deflection device comprises no movable components, wherein the at least one first fluidic component and the at least one second fluidic component sectionally cross each other, and wherein the at least one first fluidic component and the at least one second fluidic component are not fluidically connected with each other by such crossing.

16. The heat exchanger device according to claim 13, wherein at least one first fluidic component and the at least one second fluidic component each include a flow chamber which can be flowed through by a fluid flow which enters the flow chamber through an inlet opening of the flow chamber and exits from the flow chamber through an outlet opening of the flow chamber, wherein the flow chamber comprises a main flow channel and, as the at least one deflection device for creating an oscillation of the fluid flow at the outlet opening, a secondary flow channel which is fluidically connected with the main flow channel.

17. The heat exchanger device according to claim 14, wherein the main flow channel can be flowed through by at least one of: a fluid flow along a main flow direction which is directed from the inlet opening to the outlet opening, wherein the at least one first fluidic component and the at least one second fluidic component are arranged relative to each other such that the main flow direction of the at least one first fluidic component is opposite to the main flow direction of the at least one second fluidic component, and a fluid flow along a main flow direction which is directed from the inlet opening to the outlet opening, wherein the at least one first fluidic component and the at least one second fluidic component are arranged relative to each other such that the main flow direction of the at least one first fluidic component corresponds to the main flow direction of the at least one second fluidic component.

18. (canceled)

19. The heat exchanger device according to claim 14, wherein, in terms of shape and size, the main flow channel and the at least one secondary flow channel of the at least one first fluidic component are identicalwith the main flow channel and the at least one secondary flow channel of the at least one second fluidic component, respectively.

20. The heat exchanger device according to claim 14, wherein, in terms of shape or size, the main flow channel or the at least one secondary flow channel of the at least one first fluidic component are different from the main flow channel and from the at least one secondary flow channel of the at least one second fluidic component, respectively.

21. The heat exchanger device according to claim 14, wherein a dividing wall extends through the fluid flow source, wherein the at least one first fluidic component located on a first side of the dividing wall and the at least one second fluidic component is located on a second side of the dividing wall, and wherein the dividing wall includes a plurality of concave or respectively convex deformations, which protrude substantially perpendicularly from a main plane of extension of the dividing wall so that, due to the deformations of the dividing wall, the main flow channel and the at least one secondary flow channel of the at least one first fluidic component and the main flow channel and the at least one secondary flow channel of the at least one second fluidic component are formed.

22. The heat exchanger device according to claim 18, wherein the extension of the at least one secondary flow channel of the at least one first fluidic component and of the at least one second fluidic component substantially perpendicularly to the main plane of extension of the dividing wall is not constant over the extension of the at least one secondary flow channel parallel to the main plane of extension of the dividing wall.

23. The heat exchanger device according to claim 18, wherein the fluid flow source includes a front wall and a rear wall which are arranged substantially parallel to each other and to the main plane of extension of the dividing wall, and wherein the dividing wall is arranged between the front wall and the rear wall sectionally rests against the front wall and the rear wall.

Description

[0052] In the drawings:

[0053] FIG. 1 shows a cross-section through a fluidic component parallel to the oscillation plane according to an embodiment of the invention;

[0054] FIG. 2 shows a sectional representation of the fluidic component of FIG. 1 along the line A-A;

[0055] FIG. 3 shows a sectional representation of the fluidic component of FIG. 1 along the line B-B;

[0056] FIG. 4 shows a schematic representation of a heat exchanger device with a fluidic component according to an embodiment of the invention;

[0057] FIG. 5 shows a schematic representation of a heat exchanger device with a fluidic component according to another embodiment of the invention;

[0058] FIG. 6 shows a schematic representation of a heat exchanger device with a fluidic component according to another embodiment of the invention;

[0059] FIG. 7 shows a schematic representation of a heat exchanger device with a fluidic component according to another embodiment of the invention;

[0060] FIG. 8 shows a top view of a dividing wall according to an embodiment of the invention, which is provided for arrangement in a fluid flow source;

[0061] FIG. 9 shows a perspective view of the dividing wall of FIG. 8;

[0062] FIG. 10 shows a sectional representation of the dividing wall of FIG. 8 along the line N-A;

[0063] FIG. 11 shows a perspective view of two dividing walls of FIG. 8, wherein the same are arranged mirror-symmetrically relative to each other;

[0064] FIG. 12 shows a top view of a dividing wall according to another embodiment of the invention, which is provided for arrangement in a fluid flow source;

[0065] FIG. 13 shows a perspective view of the dividing wall of FIG. 12;

[0066] FIG. 14 shows a sectional representation of the dividing wall of FIG. 12 along the line A-A;

[0067] FIG. 15 shows a perspective view of three dividing walls of FIG. 12, wherein two adjacent dividing walls each are arranged mirror-symmetrically relative to each other; and

[0068] FIG. 16 shows a perspective view of a dividing wall according to another embodiment of the invention, which is provided for arrangement in a fluid flow source.

[0069] FIG. 1 schematically shows a cross-section through a fluidic component parallel to its oscillation plane, which can be used as a fluid flow source in the heat exchanger device according to the invention. FIGS. 2 and 3 show sectional representations of this fluidic component 1 along the lines A-A and B-B, respectively. The fluidic component 1 comprises a flow chamber 10 which can be flowed through by a fluid flow. The flow chamber 10 also is known as an interaction chamber.

[0070] The flow chamber 10 comprises an inlet opening 101 via which the fluid flow enters the flow chamber 10, and an outlet opening 102 via which the fluid flow exits from the flow chamber 10. The inlet opening 101 and the outlet opening 102 are arranged on two (fluidically) opposite sides of the fluidic component 1 between a front wall 12 and a rear wall 13. In the flow chamber 10 the fluid flow substantially moves along a longitudinal axis A of the fluidic component 1 (which connects the inlet opening 101 and the outlet opening 102 to each other) from the inlet opening 101 to the outlet opening 102. The inlet opening 101 has an inlet width b.sub.IN and the outlet opening 102 has an outlet width b.sub.EX. The widths in the oscillation plane are defined substantially perpendicularly to the longitudinal axis A.

[0071] The distance between the inlet opening 101 and the outlet opening 102 along the longitudinal axis A is the component length l. The component width b is the extension of the flow chamber 10 in the oscillation plane transversely to the longitudinal axis A. The component depth t is the extension of the flow chamber 10 transversely to the oscillation plane and transversely to the longitudinal axis A. The component width b can lie in a range between 0.05 mm and 0.75 m. In a preferred design variant the component width lies between 0.45 mm and 120 mm. Relative to the component width b, the component length l preferably lies in the following range: .Math.bl4.5.Math.b.

[0072] The width b.sub.EX of the outlet opening 102 is to 1/50 of the component width b, preferably to 1/20. The width b.sub.EX of the outlet opening 102 is chosen in dependence on the volumetric flow rate, the component depth t, the input speed of the fluid and the input pressure of the fluid, respectively, and the desired oscillation frequency of the exiting fluid flow. A preferred frequency range lies between 50-1000 Hz. The width b.sub.IN of the inlet opening 101 is to 1/30 of the component width b, preferably to 1/15.

[0073] The flow chamber 10 comprises a main flow channel 103 which extends centrally through the fluidic component 1. The main flow channel 103 extends substantially linearly along the longitudinal axis A so that the fluid flow in the main flow channel 103 flows substantially along the longitudinal axis A of the fluidic component 1. At its downstream end, the main flow channel 103 transitions into an outlet channel 107, which tapers in the downstream direction as seen in the oscillation plane and ends in the outlet opening 102.

[0074] For a spray cooling situation (as shown for example in FIG. 6) it is advantageous when in addition (not shown in FIG. 1) an outlet expansion for guiding the exiting moving fluid jet is available downstream of the outlet opening 102. The outlet expansion can immediately adjoin the outlet opening and substantially be directed along the longitudinal axis A. For example, this outlet expansion can be achieved by an extension of the front wall 12 and/or the rear wall 13 downstream of the outlet opening 102. In addition, it is also possible to restrict the exiting fluid jet in the oscillation plane. For this purpose, the outlet expansion can include two boundary walls proceeding from the outlet opening, which extend perpendicularly to the oscillation plane between the extended front wall 12 and rear wall 13 and whose distance to each other (transversely to the longitudinal axis in the oscillation plane) increases in the downstream direction. Due to this additional outlet expansion, the projection range of the exiting fluid jet can be increased so that a larger distance is possible between the fluidic component 1 and the surface of the heat exchanger body with which the fluid jet interacts for the purpose of heat exchange.

[0075] For forming an oscillation of the fluid flow at the outlet opening 102, the flow chamber 10 by way of example comprises two secondary flow channels 104a, 104b, wherein the main flow channel 103 is arranged between the two secondary flow channels 104a, 104b (as seen transversely to the longitudinal axis A). Immediately downstream of the inlet opening 101 the flow chamber 10 splits into the main flow channel 103 and the two secondary flow channels 104a, 104b, which then are joined immediately upstream of the outlet opening 102. The two secondary flow channels 104a, 104b here by way of example are identical in shape and are arranged symmetrically with respect to the longitudinal axis A (FIG. 1). According to a non-illustrated alternative, the secondary flow channels cannot be arranged symmetrically.

[0076] Proceeding from the inlet opening 101, the secondary flow channels 104a, 104b in a first portion each initially extend in opposite directions at an angle of substantially 90 with respect to the longitudinal axis A. Subsequently, the secondary flow channels 104a, 104b turn off so that they each extend (second portion) substantially parallel to the longitudinal axis A (in the direction of the outlet opening 102). To again join the secondary flow channels 104a, 104b and the main flow channel 103, the secondary flow channels 104a, 104b at the end of the second portion again change their direction so that they are each directed substantially in the direction of the longitudinal axis A (third portion). In the embodiment of FIG. 1, the direction of the secondary flow channels 104a, 104b changes by an angle of about 120 on transition from the second portion into the third portion. However, for the change in direction other angles than the one mentioned here can also be chosen between these two portions (and between the first and the second portion) of the secondary flow channels 104a, 104b.

[0077] The secondary flow channels 104a, 104b are a means for influencing the direction of the fluid flow flowing through the flow chamber 10 and ultimately a means for creating an oscillation of the fluid flow at the outlet opening 102. The secondary flow channels 104a, 104b therefor each include an inlet 104a1, 104b1 that is formed by the end of the secondary flow channels 104a, 104b facing the outlet opening 102, and each an outlet 104a2, 104b2 that is formed by the end of the secondary flow channels 104a, 104b facing the inlet opening 101. Through the inlets 104a1, 104b1 a small part of the fluid flow, the secondary flows, flows into the secondary flow channels 104a, 104b. The remaining part of the fluid flow (the so-called main flow) exits from the fluidic component 1 via the outlet opening 102. At the outlets 104a2, 104b2 the secondary flows exit from the secondary flow channels 104a, 104b, where they can exert a lateral impulse (transversely to the longitudinal axis A) on the fluid flow entering through the inlet opening 101. The direction of the fluid flow thereby is influenced such that the main flow exiting at the outlet opening 102 oscillates spatially and/or temporally. The oscillation is effected in a plane, the so-called oscillation plane. In the oscillation plane, the main flow channel 103 and the secondary flow channels 104a, 104b are arranged. The oscillation plane is parallel to the main plane of extension of the fluidic component 1. The moving exiting fluid jet 2 oscillates within the oscillation plane with the so-called oscillation angle (see FIG. 6).

[0078] According to a non-illustrated alternative, other means can be used for creating the oscillation of the exiting fluid jet instead of the secondary flow channels. Moreover, the secondary flow channels can be arranged non-symmetrically with respect to the longitudinal axis A. Furthermore, the secondary flow channels can also be positioned outside the illustrated oscillation plane. These channels can be realized for example by means of hoses outside the oscillation plane or by channels which extend at an angle to the oscillation plane.

[0079] In the illustrated design variant, the secondary flow channels 104a, 104b each have a cross-sectional area which is almost constant along the entire length (from the inlet 104a1, 104b1 to the outlet 104a2, 104b2) of the secondary flow channels 104a, 104b. In a design variant not shown here, the cross-sectional areas cannot be constant. On the other hand, the size of the cross-sectional area of the main flow channel 103 substantially steadily increases in the flow direction of the main flow (i.e. in the direction from the inlet opening 101 to the outlet opening 102). The width b.sub.103 of the main flow channel 103 increases in the downstream direction, whereas the depth t remains constant (FIGS. 1 and 2).

[0080] The main flow channel 103 is separated from each secondary flow channel 104a, 104b by an inner block 11a, 11b. In the embodiment of FIG. 1, the two blocks 11a, 11b are identical in shape and size and are arranged symmetrically with respect to the longitudinal axis A. In principle, however, they can also be formed differently and/or be aligned non-symmetrically. In the case of a non-symmetrical alignment, the shape of the main flow channel 103 is not symmetrical to the longitudinal axis A. The shape of the blocks 11a, 11b, which is shown in FIG. 1, only is an example and can be varied. The blocks 11a, 11b of FIG. 1 have rounded edges. The blocks 11a, 11b each have a radius 119a, 119b at their end facing the inlet opening 101 and the main flow channel 103. The edges can also be sharp or have radii with a value of approximately zero. In the downstream direction, the distance of the two inner blocks 11a, 11b to each other steadily increases along the component width b (or the width b.sub.103 of the main flow channel 103) so that they include a wedge-shaped main flow channel 103 (as seen in the oscillation plane). The smallest distance of the two inner blocks 11a, 11b to each other (or b.sub.103) principally is located at the upstream end of the inner blocks 11a, 11b. Due to the radii 119a, 119b the smallest distance (b.sub.103) is slightly shifted in the downstream direction. The width b.sub.103 of the main flow channel 103 at its narrowest point is greater than the width b.sub.IN of the inlet opening 101. The shape of the main flow channel 103 in particular is formed by the inwardly (in the direction of the main flow channel 103) pointing surfaces 110a, 110b of the blocks 11a, 11b, which extend substantially perpendicularly to the oscillation plane. The angle included by the inwardly pointing surfaces 110a, 110b here is referred to as . The inwardly pointing surfaces 110a, 110b can have a (slight) curvature or be formed by one or more radii, a polynomial and/or one or more straight lines or by a mix of the same.

[0081] At the inlet 104a1, 104b1 of the secondary flow channels 104a, 104b there are provided separators 105a, 105b in the form of indentations (into the flow chamber). From the perspective of the flow, the separators are bulges. At the inlet 104a1, 104b1 of each secondary flow channel 104a, 104b an indentation 105a, 105b each protrudes beyond a portion of the circumferential edge of the secondary flow channel 104a, 104b into the respective secondary flow channel 104a, 104b and at this point changes its cross-sectional shape by reducing the cross-sectional area. In FIG. 1 the portion of the circumferential edge is chosen such that each indentation 105a, 105b (among other things also) is directed to the inlet opening 101 (aligned substantially parallel to the longitudinal axis A). Depending on the application, the separators 105a, 105b can be aligned differently or can also be omitted completely. A separator 105a, 105b can also be provided at only one of the secondary flow channels 104a, 104b. The separation of the secondary flows from the main flow is influenced and controlled by the separators 105a, 105b. By the shape, size and alignment of the separators 105a, 105b the amount of fluid which flows into the secondary flow channels 104a, 104b as well as the direction of the secondary flows can be influenced. This in turn leads to an influence on the exit angle of the main flow at the outlet opening 102 of the fluidic component 1 (and hence to an influence on the oscillation angle) as well as the frequency at which the main flow oscillates at the outlet opening 102. By choosing the size, orientation and/or shape of the separators 105a, 105b the profile of the main flow 24 exiting at the outlet opening 102 thus can be influenced in a targeted way. It is particularly advantageous when the separators 105a, 105b (as seen along the longitudinal axis A) are arranged downstream of the position where the main flow separates from the inner blocks 11a, 11b and a part of the fluid flow enters the secondary flow channels 104a, 104b.

[0082] Upstream of the inlet opening 101 of the flow chamber 10 a funnel-shaped attachment 106 is provided, which tapers (in the oscillation plane) in the direction of the inlet opening 101 (in the downstream direction). The boundary walls of the funnel-shaped attachment 106, which extend substantially perpendicularly to the oscillation plane, include an angle c. The flow chamber 10 also tapers (in the oscillation plane) upstream of the outlet opening 102. The taper is formed by the outlet channel 107 mentioned already, which extends between the inlets 104a1, 104b1 of the secondary flow channels 104a, 104b and the outlet opening 102. In FIG. 1, the inlets 104a1, 104b1 of the secondary flow channels 104a, 104b are specified by the separators 105a, 105b. The boundary walls of the outlet channel 107, which extend substantially perpendicularly to the oscillation plane, include an angle . According to FIGS. 1 and 2, the funnel-shaped attachment 106 and the outlet channel 107 taper such that only their width, i.e. their extension in the oscillation plane perpendicularly to the longitudinal axis A, each decreases in the downstream direction. In addition, the funnel-shaped attachment 106 and the outlet channel 107 can also taper along the component depth t in the downstream direction, i.e. perpendicularly to the oscillation plane and perpendicularly to the longitudinal axis A. Furthermore, only the attachment 106 can taper in its depth or width, while the outlet channel 107 tapers both in its width and in its depth, and vice versa. The extent of the taper of the outlet channel 107 influences the directional characteristic of the fluid flow exiting from the outlet opening 102 and thus its oscillation angle. In FIG. 1, the shape of the funnel-shaped attachment 106 and the outlet channel 107 are shown only by way of example. Here, their width each decreases linearly in the downstream direction. Other shapes of the taper are possible.

[0083] The outlet opening can be rounded by a radius 109. This radius 109 preferably is smaller than the width b.sub.IN of the inlet opening 101 or the smallest width b.sub.103 of the main flow chamber 103 (as seen along the longitudinal axis A). When the radius 109 is equal to 0, the outlet opening 102 is sharp-edged.

[0084] The inlet opening 101 and the outlet opening 102 each have a rectangular cross-sectional area (transversely to the longitudinal axis A). The same each have the same depth t, but differ in their width b.sub.IN, b.sub.EX. Alternatively, a non-rectangular cross-sectional area also is conceivable for the inlet opening 101 and the outlet opening 102, for example circular.

[0085] In the embodiment of FIG. 1 the cross-sectional area of the inlet opening 101, which is defined by the inlet width b.sub.IN and the component depth t.sub.IN at the inlet opening 101, is smaller than the cross-sectional area of the outlet opening 102, which is defined by the outlet width b.sub.EX and the component depth t.sub.EX at the outlet opening 101. In particular, the inlet width b.sub.IN is smaller than the outlet width b.sub.EX. Alternatively, the cross-sectional area of the inlet opening 101 and the cross-sectional area of the outlet opening 102 can be the same size. Alternatively or in addition, the cross-sectional area of the inlet opening 101 can be smaller than or equal to the cross-sectional area of the main flow channel 103 at the narrowest point of the main flow channel 103. The narrowest point of the main flow channel 103, where the distance of the two inner blocks 11a, 11b (the width b.sub.103 of the main flow channel 103) is smallest in the oscillation plane transversely to the longitudinal axis A. The cross-sectional area of the main flow channel 103 at the narrowest point of the main flow channel 103 is defined by the width b.sub.103 and the component depth t.sub.103 at this point. At a constant component depth (t.sub.IN=t.sub.EX=t.sub.103) it applies according to the invention: b.sub.INb.sub.EX and/or b.sub.INb.sub.103. In particular, the inlet width b.sub.IN, the outlet width b.sub.EX and the width b.sub.103 can be the same size (b.sub.IN=b.sub.103=b.sub.EX).

[0086] According to FIG. 2, the fluidic component 1 of FIG. 1 has a constant component depth t. According to one embodiment, the component depth t is greater than of the inlet width b.sub.IN. Advantageously, the component depth t is greater than half the inlet width b.sub.IN. It is particularly advantageous when the component depth t is greater than the inlet width b.sub.IN and for some applications even greater than twice the inlet width b.sub.IN. The component depth t, however, also can vary along the longitudinal axis A (or in general). FIG. 3 shows a section through the fluidic component 1 of FIG. 1 along the axis B-B. FIG. 3 shows that the cross-sectional areas of the main flow channel 103 and of the secondary flow channels 104a, 104b each are substantially rectangular. Such cross-sectional shapes are easy to fabricate. However, the cross-sectional areas can also have other shapes, e.g. the secondary flow channels 104a, 104b can have a triangular, polygonal or round cross-sectional area.

[0087] FIG. 4 shows a heat exchanger device 5 according to an embodiment of the invention. The heat exchanger device 5 comprises a fluidic component 1 which preferably is the fluidic component of FIGS. 1 to 3 or one of the alternative embodiments which have been described in connection with FIGS. 1 to 3. The fluidic component 1 generates an oscillating fluid flow 2 which oscillates in its oscillation plane. The oscillation plane corresponds to the plane which in FIG. 4 is defined by the longitudinal axis A of the fluidic component 1 and the double arrow 202.

[0088] Furthermore, the heat exchanger device 5 comprises a heat exchanger body 3. The heat exchanger body 3 comprises a flow chamber 303 which is defined by boundary walls. Two of the boundary walls are shown in FIG. 4. Their surfaces, which each are facing the flow chamber 303, are designated with the reference numerals 304a, 304b and extend substantially perpendicularly to the oscillation plane and parallel to the longitudinal axis A of the fluidic component 1. The two boundary walls or their surfaces 304a, 304b are arranged parallel to each other on either side of the longitudinal axis A of the fluidic component 1. The flow chamber 303 has an inlet opening 301 and an outlet opening 302 which are fluidically disposed opposite each other and are connected with each other by the flow chamber 303. The fluid flow 2 exiting from the fluid flow source 1 can enter the flow chamber 303 of the heat exchanger body 3 through the inlet opening 301 and can again exit from the flow chamber 303 of the heat exchanger body 3 through the outlet opening 302.

[0089] The inlet opening 301 of the heat exchanger body 3 is arranged immediately downstream of the outlet opening 102 of the fluidic component 1 so that the fluid flow from the fluidic component 1 flows directly into the heat exchanger body 3. The fluidic component 1 and the boundary walls (or their surfaces 304a, 304b) are positioned relative to each other such that the oscillation plane is oriented substantially perpendicularly to the surfaces 304a, 304b. The oscillation angle of the oscillating fluid flow 2 and the distance of the surfaces 304a, 304b from the longitudinal axis A of the fluidic component is chosen such that the oscillating fluid jet 2 alternately sweeps over the two surfaces 304a, 304b. This means that the surfaces 304a, 304b experience a temporally variable approach flow situation. In this way, a highly turbulent flow with large-scale coherent (turbulence) structures is generated, which would not be created without the oscillating fluid flow.

[0090] According to a non-illustrated alternative, the fluidic component can be arranged with the flow chamber 303. It is also possible that more than one fluidic component is arranged in the flow chamber 303. The one or more fluidic components then act like turbulators (swirl elements) which additionally swirl the fluid flow. The fluidic components for example can be arranged in series or in parallel.

[0091] FIG. 5 shows another embodiment of the heat exchanger device 5. Among other things, the same differs from the embodiment of FIG. 4 in the relative orientation of the fluidic component 1 and the two boundary walls of the flow chamber 303 (or of their surfaces facing the flow chamber 303). The surfaces are designated with the reference numerals 304c and 304d. In FIG. 5, the surfaces 304c, 304d are oriented substantially parallel to the oscillation plane (not perpendicularly as in FIG. 4). The oscillation plane corresponds to the plane which in FIG. 5 is defined by the longitudinal axis A of the fluidic component 1 and the double arrow 202.

[0092] Moreover, at the surface 304d is provided an additional turbulator 333, which is configured as a web which extends along the surface 304d and substantially perpendicularly to the longitudinal axis A of the fluidic component 1. The turbulator 333 is arranged at a distance I.sub.333 to the outlet opening 102 of the fluidic component 1. This distance I.sub.333 is at least twice as large as the width b.sub.EX of the outlet opening 102. In heat exchanger devices with hole-type nozzles as a fluid flow source this distance I.sub.333 must be at least five times the width b.sub.EX of the outlet opening 102. Thus, with the same heat transport performance the installation space (the size of the flow chamber 303 of the heat exchanger body 3) can be reduced when instead of a hole-type nozzle a fluidic component is used as a fluid flow source.

[0093] The shape and orientation of the turbulator only is an example in FIG. 5. Other shapes and/or orientations also are possible. According to an alternative, the heat exchanger body 3 has no additional turbulator.

[0094] The outlet opening 102 of the fluidic component 1 can have a depth t.sub.EX which corresponds to the distance t.sub.303 between the surfaces 304c, 304d. This distance t.sub.303 is the depth of the flow chamber 303 of the heat exchanger body 3. In this case, the outlet opening 102 of the fluidic component 1 adjoins the two surfaces 304c, 304d. In the embodiment shown in FIG. 5, the depth t.sub.EX of the outlet opening 102 of the fluidic component 1 however is smaller than the depth t.sub.303 of the flow chamber 303 of the heat exchanger body 3. Thus, the outlet opening 102 can adjoin one of the two surfaces 304c, 304d and have a distance t.sub.311 to the other one of the two surfaces 304c, 304d. This distance t.sub.311 preferably is smaller than the extension t.sub.333 of the turbulator 333 along the depth t.sub.303 of the flow chamber 303 of the heat exchanger body 3.

[0095] FIG. 6 shows an embodiment of the heat exchanger device 5 in which the heat exchange is effected according to the impingement flow method. The heat exchanger body 3 or its surface 304e here is approached (for example from outside) by the fluid flow 2 exiting from the fluidic component 1 in order to accomplish a change in temperature of the heat exchanger body 3. The fluidic component 1 therefor is arranged at a distance to the surface 304e. The longitudinal axis A of the fluidic component 1 includes an approach flow angle with the surface 304e, which is not equal to zero. In FIG. 6, the approach flow angle only is an example. The outlet opening 102 of the fluidic component 1 is arranged at a distance I.sub.14 to the surface 304e. The distance I.sub.14 is defined along an axis which extends substantially perpendicularly to the surface 304e. Preferably, the distance I.sub.14 is at least twice as large as the width b.sub.EX of the outlet opening 102 of the fluidic component 1. In heat exchanger devices with hole-type nozzles as a fluid flow source this distance I.sub.14 must be at least five times the width b.sub.EX of the outlet opening 102 in the impingement flow method. Thus, with the same heat transport performance, the installation space (the volume of the heat exchanger device 5) can be reduced when instead of a hole-type nozzle a fluidic component is used as a fluid flow source.

[0096] In the embodiment of FIG. 7, the heat exchange also is effected according to the impingement flow method. The heat exchanger body 3 comprises a flow chamber 303 which is defined by a plurality of boundary walls, three of which are shown in FIG. 7. Their surfaces facing the flow chamber 303 are designated with the reference numerals 304f, 304g, 304h. By way of example, the heat exchanger device 5 comprises three fluidic components 1 as fluid flow sources. However, the number of fluid flow sources can also differ from three. Their outlet openings 102 transition into corresponding inlet openings 301 of the flow chamber 303 of the heat exchanger body 3 and are formed in the boundary wall with the surface 304f. The longitudinal axes A of the fluidic components 1 extend substantially perpendicularly to the surface 304f and the surface 304h, which is arranged parallel to the surface 304f. The fluid flow 2 exits from the outlet openings 102 of the fluidic components 1 through the inlet openings 301 of the heat exchanger body 3 into the flow chamber 303 of the heat exchanger body 3 and then impinges on the surface 304h as an impingement flow at the approach flow angle R. Preferably, the distance I.sub.14 from each outlet opening 102 of the fluidic components 1 to the surface 304h along the longitudinal axis A is at least twice the width b.sub.EX of the outlet openings 102.

[0097] The flow chamber 303 of the heat exchanger body 3 furthermore can have an outlet opening 302 which in FIG. 7 is indicated between the boundary walls with the surfaces 304f, 304h. The fluid flow can flow out of the flow chamber 303 through the outlet opening 302.

[0098] In the illustrated embodiment, the approach flow angle is =90. The approach flow angle can also have other values between 0 and 90, such as for example about 60, as is shown in FIG. 6 by way of example. In principle, the oscillation plane can also be rotated about the longitudinal axis A of the respective fluidic component 1 and have an orientation different from FIG. 7.

[0099] According to a non-illustrated embodiment, the flow chamber 303 has an inlet opening instead of the boundary wall with the surface 304g so that fluid on the one hand can flow through this inlet opening and on the other hand through the inlet openings 301 in the flow chamber 303, which communicate with the fluidic components 1. Due to the additional inlet openings 301 new turbulence sources can be obtained. In addition, a compensation of the temperature difference of the fluids can be achieved very quickly when the fluid which enters the flow chamber 303 through the inlet opening in the surface 304g and the fluid which enters the flow chamber 303 via the fluidic components 1 have different temperatures.

[0100] Depending on the fluid (type, properties) and the specific application, the fluidic component 1 can be configured differently in order to generate different jet paths. In FIG. 7, three different jet paths are shown by way of example. The dashed jet path substantially is sinusoidal, the dotted jet path substantially triangular, and the jet path along the dash-dotted line substantially rectangular. Alternatively, the fluidic components 1 can be configured such that they all generate the same jet path, which can also differ from the jet paths shown in FIG. 7. In particular in the embodiment of FIG. 4, the duration of the interaction of the oscillating fluid flow with the surfaces can vary depending on the jet path.

[0101] FIG. 8 schematically shows a top view of a dividing wall 15 which is provided for arrangement in a fluid flow source. FIG. 9 shows a perspective representation of this dividing wall 15, and FIG. 10 shows a section through this dividing wall 15 along the line A-A. Beside the dividing wall 15, FIG. 10 also shows a front wall 12 and a rear wall 13 of the fluid flow source 1, between which the dividing wall 15 is arranged. The fluid flow source 1 with the dividing wall 15 can be arranged with respect to a heat exchanger body such that the fluid flow exiting from the fluid flow source interacts with the heat exchanger body for the purpose of heat exchange. Alternatively, the heat exchanger body 3 can be formed by the front wall 12 and/or the rear wall 13 so that it is not the fluid flow exiting from the fluid flow source, but the fluid flow flowing in the fluid flow source which interacts with the heat exchanger body for the purpose of heat exchange. The latter alternative is shown in FIG. 10.

[0102] The dividing wall 15 extends in a main plane of extension and has a first side 151 and a second side 152 opposite the first side 151, wherein in FIG. 8 the first side 151 faces the viewer and the second side 152 faces away from the viewer. The dividing wall 15 is not planar, but includes a number of deformations protruding from the main plane of extension, as can be seen in particular in FIGS. 9 and 10. The deformations appearing as concave (convex) on the first side 151 form correspondingly convex (concave) deformations on the second side 152. Thus, both the first side 151 and the second side 152 of the dividing wall 15 sectionally include depressions, wherein the depressions of the first and second sides 151, 152 are complementary in shape and are distributed over the dividing wall 15. The depressions of the first and second sides 151, 152 are shaped such that together with the front wall 12 or rear wall 13 they each form fluidic components 1, 1. The depressions of the first side 151 form a plurality of first fluidic components 1, while the depressions of the second side 152 form a plurality of second fluidic components 1. Concretely, the dividing wall 15 in this embodiment forms three first fluidic components 1 and three second fluidic components 1. The number, however, only is an example and principally can differ therefrom. Preferably, it should at least be two. The first and second fluidic components 1, 1 are not fluidically connected with each other, but also separated from each other by material of the dividing wall 15. The first and second fluidic components 1, 1 are arranged side by side and in alternation along a main flow direction (which will be explained later) of the first and the second fluidic component 1, 1. This provides a repeating pattern transversely to the main flow direction. The smallest unit of the pattern as shown in FIG. 8 is delimited by two dashed lines.

[0103] In their basic construction, the first and second fluidic components 1, 1 (of FIGS. 8 to 10, but also of FIGS. 11 to 16) correspond to the fluidic component 1 of FIGS. 1 to 3. Correspondingly, in FIGS. 8 to 16, which show first and second fluidic components 1, 1, elements which are also formed in the fluidic component 1 of FIGS. 1 to 3 are designated by corresponding reference numerals, which carry the addition (for the first fluidic components) and (for the second fluidic components). For the following description of the first and second fluidic components 1, 1 of FIGS. 8 to 16 reference also is made to the description of the fluidic component of FIGS. 1 to 3 in order to avoid repetitions. In the following, merely the most relevant features will be described.

[0104] Each first and second fluidic component 1, 1 of the embodiment of FIGS. 8 to 10 comprises a flow chamber 10, 10 which can each be flowed through by a fluid flow. The flow chambers 10, 10 each comprise an inlet opening 101, 101 via which the fluid flow enters the flow chambers 10, 10, and an outlet opening 102, 102 via which the fluid flow exits from the flow chambers 10, 10. The first and second fluidic components 1, 1 each are mirror-symmetrical with respect to a plane which extends substantially perpendicularly to the main plane of extension of the dividing wall 15 and centrally through the respective inlet opening 101, 101 and through the respective outlet opening 102, 102. Such a symmetry, however, is not absolutely necessary.

[0105] Each flow chamber 10, 10 comprises a main flow channel 103, 103 and as a means for creating an oscillation of the fluid flow at the outlet opening two secondary flow channels 104a, 104b, 104a, 104b which extend in the main plane of extension of the dividing wall 15, wherein the main flow channel 103, 103 is formed between the two secondary flow channels 104a, 104b, 104a, 104b. The number of secondary flow channels can, however, also be different from two. The fluid flow in the main flow channels 103, 103 substantially moves from the inlet opening 101, 101 to the outlet opening 102, 102 along the so-called main flow direction. In the embodiment of FIGS. 8 to 10 the first and second fluidic components 1, 1 have the same main flow direction, which in FIG. 8 is marked with arrows. This is a so-called cocurrent or co-flow situation. Here (as seen in the main flow direction), the inlet opening 101 and the outlet opening 102 of the first fluidic components 1 are offset from the inlet opening 101 or the outlet opening 102 of the second fluidic components 1 in the downstream direction. The inlet openings 101 (101) of the first fluidic components 1 (second fluidic components 1) are arranged at the same height as seen in the main flow direction. The same applies for the outlet openings 102 (102). In particular, the entire first fluidic component 1 is offset from the entire second fluidic component 1 in the downstream direction. Alternatively, the first fluidic components 1 (the second fluidic components 1) can also be offset from each other in the upstream or downstream direction. For this purpose, the geometry of the flow chambers 10, 10 would have to be adapted.

[0106] Each main flow channel 103, 103 is fluidically connected with its secondary flow channels 104a, 104b, 104a, 104b immediately downstream of the inlet opening 101, 101 and immediately upstream of the outlet opening 102, 102. Immediately upstream of the outlet opening 102, 102 the inlet of the secondary flow channels 104a, 104b, 104a, 104b is located, via which a part of the fluid flow (secondary flow) from the main flow channel 103, 103 flows into the secondary flow channels 104a, 104b, 104a, 104b, while immediately downstream of the inlet opening 101, 101 the outlet of the secondary flow channels 104a, 104b, 104a, 104b is located, via which the secondary flow flows out of the secondary flow channels 104a, 104b, 104a, 104b and gets back into the main flow channel 103, 103, where the secondary flow can exert a lateral impulse (transversely to the main flow direction) on the fluid flow entering through the inlet opening 101, 101. The direction of the fluid flow thereby is influenced such that the main flow exiting from the outlet opening 102, 102 oscillates spatially and/or temporally. The oscillation is effected in a plane, the so-called oscillation plane. The same is parallel to the main plane of extension of the dividing wall 15.

[0107] The two secondary flow channels 104a, 104b, 104a, 104b here by way of example are identically shaped within a fluidic component 1, 1 and arranged symmetrically with respect to the associated main flow channel 103, 103. According to a non-illustrated alternative, the secondary flow channels cannot be shaped identically and/or not be arranged symmetrically.

[0108] The main flow channels 103, 103 each are separated from their secondary flow channels 104a, 104b, 104a, 104b by an inner block 11a, 11b, 11a, 11b. In the embodiment of FIGS. 8 to 10, the second blocks 11a, 11b, 11a, 11b of a first or second fluidic component 1, 1 are identical in shape and size and arranged symmetrically with respect to the main flow channel 103, 103. In principle, however, they can also be formed differently and/or be oriented non-symmetrically. The inner blocks 11a, 11b of the first fluidic component 1, however, differ in shape from the inner blocks 11a, 11b of the second fluidic components 1. The shape of the inner blocks 11a, 11b, 11a, 11b here only is an example. However, the inner blocks 11a, 11b, 11a, 11b always should be shaped and oriented such that the width (extension in the main plane of extension of the dividing wall 15 and substantially perpendicularly to the main flow direction) of the main flow channels increases in the downstream direction.

[0109] The main flow channels 103, 103 have a constant depth (extension substantially perpendicularly to the main plane of extension of the dividing wall 15). The depth both of the main flow channel 103 and of the main flow channel 103 each corresponds to the maximum depth t.sub.max which is obtained by the deformation of the dividing wall 15. The width of the main flow channels 103, 103 increases in the downstream direction.

[0110] On the other hand, the secondary flow channels 104a, 104b, 104a, 104b do not have a constant depth. The secondary flow channels 104a, 104b, 104a, 104b sectionally have the maximum depth t.sub.max and sectionally a reduced depth trey which is smaller than the maximum depth t.sub.max. The reduced depth t.sub.red for example can be half the maximum depth t.sub.max. When several portions of reduced depth t.sub.red are formed, the same can have the same depth or can have different depths. The secondary flow channels 104a, 104b, 104a, 104b of the first fluidic component 1 (second fluidic component 1) have the maximum depth t.sub.max in the portion in which the second fluidic components 1 (first fluidic components 1) have their inner blocks 11a, 11b (11a, 11b). Furthermore, the secondary flow channels 104a, 104b, 104a, 104b have the maximum depth t.sub.max in the region of the transition to the respective main flow channel 103, 103, which likewise has the maximum depth t.sub.max. The portions of maximum depth t.sub.max are interrupted by portions of reduced depth t.sub.red, the so-called crossing portions. In the crossing portions a portion of the secondary flow channel 104a, 104b, 104a, 104b each is formed both for the first fluidic components 1 and for the second fluidic components 1. In these portions of reduced depth trey the fluid hence flows on the first side 151 and on the second side 152 of the dividing wall 15. Thus, the first and second fluidic components 1, 1, which are arranged alternately, are mutually nested in the region of the secondary flow channels 104a, 104b, 104a, 104b and of the inner blocks 11a, 11b, 11a, 11b.

[0111] For the first fluidic components 1 (second fluidic components 1) the depth of the secondary flow channels 104a, 104b (104a, 104b) in the direction from their respective inlet to their respective outlet is as follows:

maximum depth t.sub.max (like the main flow channel 103 (103)).fwdarw.reduced depth t.sub.red (crossing with a portion of the secondary flow channels 104a, 104b (104a, 1040 of the second fluidic components 1 (first fluidic components 1)) 4 maximum depth t.sub.max (formation of the inner blocks 11a, 11b (11a, 11b) of the second fluidic components 1 (first fluidic components 1)) 4 reduced depth t.sub.red (crossing with a portion of the secondary flow channels 104a, 104b (104a, 1040 of the second fluidic components 1 (first fluidic components 1)).fwdarw.maximum depth t.sub.max (like the main flow channel 103 (103)). In the embodiment of FIGS. 8 to 10 the depth for the two portions of reduced depth t.sub.red (crossing portions) is the same and corresponds to half of t.sub.max. However, these two crossing portions can have differently large depths. Moreover, the reduced depth need not be half of t.sub.max. Due to the sectionally reduced depth of the secondary flow channels, the distance between adjacent first and second fluidic components 1, 1 can be reduced.

[0112] Due to crossing or nesting, the outer wall (the wall facing away from the main flow channel 103 (103) and extending substantially perpendicularly to the main plane of extension of the dividing wall 15) of the secondary flow channels 104a, 104b (104a, 104b) of the first fluidic components 1 (of the second fluidic components 1) at the same time forms the inner wall (the wall facing the main flow channel 103 (103) and extending substantially perpendicularly to the main plane of extension of the dividing wall 15) of the inner blocks 11a, 11b (11a, 11b) of the adjacent second fluidic components 1 (first fluidic components 1). Said outer wall is shaped such that for the purpose of creating the oscillation it provides the main flow channel 103 (103) of the adjacent two fluidic components 1 (first fluidic components 1) a suitable shape. Furthermore, the inner wall (the wall facing the main flow channel 103 (103) and extending substantially perpendicularly to the main plane of extension of the dividing wall 15) of the secondary flow channels 104a, 104b (104a, 104b) of the first fluidic components 1 (of the second fluidic components 1) at the same time forms the inner wall (the wall facing the main flow channel 103 (103) and extending substantially perpendicularly to the main plane of extension of the dividing wall 15) of the secondary flow channels 104a, 104b (104a, 104b) of the adjacent second fluidic components 1 (first fluidic components 1).

[0113] At its downstream end, each main flow channel 103, 103 transitions into an outlet channel 107, 107, which tapers in the downstream direction as seen in the oscillation plane and ends in the outlet opening 102, 102. Downstream of the outlet opening 102, 102 an outlet enlargement 108, 108 is provided, which immediately adjoins the respective outlet opening 102, 102. Upstream of the inlet opening 101, 102 of the flow chambers 10, 10 a funnel-shaped attachment 106, 106 is provided, which tapers (in the oscillation plane) in the direction of the inlet opening 101, 101 (in the downstream direction).

[0114] In the embodiment of FIGS. 8 to 10 the first fluidic components 1 differ in shape from the second fluidic components 1. In particular, they differ in the shape of the main flow channel, the secondary flow channels and the inner blocks.

[0115] According to FIG. 10, the front wall 12 and the rear wall 13 each have a planar surface directed towards the dividing wall, with which they sectionally rest against the first and the second side 151, 152, respectively. These surfaces can, however, also be designed uneven. The surfaces should be shaped such that the front wall 12 can rest against the inner blocks 11a, 11b of the first fluidic components 1 and the rear wall 13 can rest against the inner blocks 11a, 11b of the second fluidic components 1 in order to prevent a throughflow of the fluid flow in these regions and to not impair the operation of the secondary flow channels 104a, 104b, 104a, 104b.

[0116] In the embodiment of FIG. 11 two dividing walls 15 of the embodiment of FIGS. 8 to 10 are provided for arrangement in the fluid flow source. For better clarity, only two dividing walls 15 are shown. The dividing walls 15 are arranged (stacked) such that their main planes of extension extend parallel to each other. In particular, the two dividing walls 15 are arranged mirror-symmetrically to each other and sectionally rest against each other. Between the two dividing walls 15, there are sectionally obtained regions in which the depth corresponds to twice the depth t.sub.max of a dividing wall 15. The flow direction of the main flow is designated with arrows for the first and second fluidic components 1, 1. By analogy with FIG. 10, the two dividing walls 15 in the illustrated arrangement can be arranged for example between a front wall and a rear wall in order to form a fluid flow source/heat exchanger device. It is also possible to stack more than two dividing walls 15 by analogy with the embodiment of FIG. 11 so that immediately adjacent dividing walls always are mirror-symmetrical to each other.

[0117] In FIGS. 12 to 14 another embodiment of a dividing wall 15 is shown. FIG. 12 shows a top view of the main plane of extension of the dividing wall 15, FIG. 13 a perspective view, and FIG. 14 a sectional representation transversely to the main plane of extension of the dividing wall 15. FIG. 14 again shows the dividing wall 14 together with a front wall 12 and a rear wall 13, which sectionally rest against the dividing wall 15. Together, they form a heat exchanger device 5. This embodiment of the dividing wall 15 differs from the one of FIGS. 8 to 10 in particular by the fact that the shapes of the main flow channels 103, 103, of the secondary flow channels 104a, 104b, 104a, 104b and of the inner blocks 11a, 11b are more angular (less rounded). In addition, in the embodiment of FIGS. 12 to 14 the first and second fluidic components 1, 1 are identically shaped and oriented with respect to each other such that their main flow directions are opposite to each other. The main flow directions are designated by arrows. This is a so-called countercurrent or counter-flow situation. Furthermore, the draft angle of the concave/convex deformations here is more pronounced than in the embodiment of FIGS. 8 to 10 so that distances parallel to the main plane of extension of the dividing wall 15 strictly speaking are not constant over the depth (extension substantially perpendicular to the main plane of extension of the dividing wall 15).

[0118] FIG. 15 shows three dividing walls 15 of the embodiment of FIGS. 12 to 14 in a stacked arrangement which is provided for arrangement in a fluid flow source. Two immediately adjacent dividing walls 15 are aligned mirror-symmetrically to each other and sectionally rest against each other. This means that the two outer dividing walls have the same orientation. Between two dividing walls 15 first and second fluidic components 1, 1 are formed with twice the depth (as compared to an individual dividing wall, which in FIG. 14 is arranged between a planar front wall 12 and a planar rear wall 13). The arrows in FIG. 15 indicate the main flow direction for the first and second fluidic components 1, 1. By analogy with FIG. 14, the three dividing walls 15 in the illustrated arrangement can be arranged for example between a front wall and a rear wall in order to form a fluid flow source/heat exchanger device. The number of dividing walls 15 is only exemplary in FIG. 15 and can differ from three. Immediately adjacent dividing walls should be arranged mirror-symmetrically with respect to each other.

[0119] In FIG. 16 another embodiment of a dividing wall 15 is shown. Like in the embodiment of FIGS. 8 to 10 the first and second fluidic components 1, 1 here as well have the same main flow direction. Like in the embodiment of FIGS. 8 to 10, the main flow channels 103, 103, secondary flow channels 104a, 104b, 104a, 104b and inner blocks 11a, 11b, 11a, 11b rather have rounded shapes. However, the first and the second fluidic components 1, 1 (main flow channel 103, 103, secondary flow channels 104a, 104b, 104a, 104b and inner blocks 11a, 11b, 11a, 11b) are almost identical in shape. In contrast to the embodiment of FIGS. 8 to 10 the inlet opening 101 and the outlet opening 102 of the first fluidic components 1 here are arranged at the same height (as seen in fluid flow direction) as the inlet opening 101 or the outlet opening 102 of the second fluidic components 1.

[0120] All embodiments of the dividing wall shown in FIGS. 8 to 16 are space-optimized and suitable for compact heat exchanger devices/fluid flow sources. The individual elements (dividing walls, front wall, rear wall) of the heat exchanger device/fluid flow source can be manufactured at low cost for example by means of shaping methods. In addition, these individual elements are releasably connectable with each other, after they have been properly arranged relative to each other. The individual elements can be braced with each other such that they sectionally flatly rest against each other. By bracing, a sealing can be achieved as well. Due to this modular construction of the heat exchanger device, dividing walls can easily be exchanged and cleaning of the individual elements can become possible for maintenance purposes. Furthermore, it is possible to arrange the first fluidic components 1 and the second fluidic components 1 one behind the other in fluid flow direction and fluidically connect the same with each other. In such a series connection, the fluid flow exiting from the outlet opening 102, 102 of an upstream fluidic component 1, 1 can enter the inlet opening 101, 101 of the fluidically connected downstream fluidic component 1, 1. As seen in fluid flow direction, first and second fluidic components 1, 1 can be provided (for example alternate with each other). Alternatively, only first fluidic components 1 or only second fluidic components 1 can be arranged one behind the other as seen in the fluid flow direction and be fluidically connected with each other. Even in a series connection, the fluidic connection is not obtained by the crossing of first and second fluidic components. The series connection can be advantageous to increase the heat exchange.