Heat Exchanger Device

This invention relates to a heat exchanger device according to the preamble of claim 1.

Heat exchanger devices are devices which transfer thermal energy from one material (flow) to another. They can serve for cooling or for heating a material flow or body. For example, there are known cooling devices which dissipate heat in a targeted way. Examples include refrigerators or freezers, internally cooled dies (for example injection molding tools) or also cooling devices in gas turbines.

To transfer the thermal energy between the material flows as efficiently as possible, it is known to increase the surfaces on which the heat transfer takes place, for example by channels extending in the manner of a labyrinth or in a meandering fashion (US 2007/0166017 A1 or EP 2025427 A2). It is furthermore known to increase the turbulence within a fluid flow for example by so-called turbulators (ribs, webs or pins which protrude into the flow) for the purpose of increasing the transfer efficiency (U.S. Pat. No. 6,607,356 B2). To increase the turbulence within a fluid flow it is furthermore possible to increase the velocity of the fluid for example by increasing the input pressure. In doing so, however, the energy consumption and the costs increase.

In the devices mentioned above by way of example, it is the main objective to dissipate the heat from a particular location. In other devices it is the objective to transport heat to a particular location, such as for example in steam spraying devices (for example for steam sterilization).

The object underlying the present invention is to provide a heat exchanger device which provides for an efficient transfer of the thermal energy between two systems (body, material flow). The objective is to generate a high temporal and spatial velocity gradient on the surface to be cooled or dissipating heat.

According to the invention, this object is achieved by a heat exchanger device with the features of claim 1. Aspects of the invention are indicated in the sub-claims.

Accordingly, the heat exchanger device comprises a body for heat exchange (heat exchanger body) and a fluid flow source which is configured to provide a fluid flow. The body for heat exchange is a body which is to be heated or cooled. 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. Thus, the fluid flow can dissipate the heat of the body or vice versa. Interaction here is understood to be a contact which temporally or spatially is designed such that at least the intended transfer of thermal energy can take place between the body and the fluid flow. In particular, interaction is not understood to be an accidental contact.

The heat exchanger device according to the invention is characterized in that the fluid flow source comprises a fluidic component which comprises at least one means for creating an oscillation of the fluid flow. The fluidic component accordingly is configured to generate a moving (oscillating) fluid flow which pulsates temporally and/or moves spatially.

The fluidic component generates a spatially and/or temporally variable flow for the heat exchanger device. The boundary layer of the fluid flow at the boundary to the heat exchanger body thereby can have a high degree of turbulences. Furthermore, secondary flows can be enforced. Due to the movement (oscillation) of the fluid flow, the efficiency of the heat conduction process or heat exchange process in general can be increased.

Furthermore, the fluid flow in the fluidic component experiences almost no pressure loss so that the pressure of the fluid flow available at the inlet of the fluidic component can effectively be used for heat transfer. Thus, the heat exchanger device can also be used at a low input pressure or a low flow velocity.

Another advantage of the fluidic component consists in that due to its shape the exiting fluid flow can interact with a large surface area, and hence a large heat transfer performance can be achieved.

In case the fluid is (tap) water, which usually is calcareous, scale deposits can massively be reduced or even be prevented by means of the fluidic component as a fluid flow source due to the movement (oscillation) of the fluid in the heat exchanger device, whereby the service life of the device can be increased.

In case the heat exchanger device for example employs the so-called impingement cooling method, the heat exchange performance can be increased by using a fluidic component in the impingement cooling configuration.

The fluidic component comprises no movable components which serve to generate the movable fluid flow. The fluid flow source thereby has a low wear.

Depending on its configuration, the fluidic component can produce various fluid flow patterns. For example, a sinusoidal jet oscillation, rectangular, sawtooth-shaped or triangular jet paths, spatial or temporal jet pulsations and switching operations can be produced. Due to the different jet paths, the duration and/or the position of the interaction between the fluid flow and the heat exchanger body can be adapted.

The fluidic component generates a fluid flow which in particular in an oscillation plane oscillates about an oscillation angle. Thus, the fluidic component generates a fan-like fluid jet in which the fluid distribution varies temporally and/or spatially.

According to one embodiment, the fluidic component comprises a flow chamber which can be flowed through by a fluid flow that enters into 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. Preferably, the inlet opening and the outlet opening are arranged on opposite sides of the flow chamber. The fluid flow exiting from the outlet opening is available for the heat exchange process of the heat exchanger device. In this embodiment, the means for creating an oscillation of the fluid flow is provided at the outlet opening in the flow chamber. The means for creating an oscillation for example can be at least one secondary flow channel which is fluidically connected with a main flow channel (to be described later) of the flow chamber and spatially deflects the fluid flow flowing in the main flow channel. Alternatively, other means for creating an oscillation of the fluid flow can also be provided.

The inlet opening and the outlet opening each can have a cross-sectional area which extends substantially perpendicularly to a longitudinal axis of the fluidic component. The longitudinal axis of the fluidic component is directed from the inlet opening to the outlet opening and lies in the oscillation plane. The cross-sectional areas of the inlet opening and the outlet opening here each are understood to be the smallest cross-sectional areas of the fluidic component, which are flowed through by the fluid flow when it enters the flow chamber and again exits from the flow chamber. In particular, the cross-sectional area of the inlet opening can be 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 can be the same size. Due to such a size ratio the fluid experiences a small flow resistance in the fluidic component, which leads to a low pressure loss within the fluidic component. Accordingly, the heat exchanger device can also be used when the inlet pressure or the flow velocity is low.

According to another embodiment, the flow chamber comprises a main flow channel which extends along the longitudinal axis between the inlet opening and the outlet opening. The main flow channel can have a cross-sectional area which extends perpendicularly to the longitudinal axis. The size of the cross-sectional area of the main flow channel can change along the longitudinal axis. In particular, the cross-sectional area of the inlet opening can be smaller than the cross-sectional area of the main flow channel at its narrowest point or the cross-sectional area of the inlet opening and the cross-sectional area of the main flow channel at its narrowest point can be the same size. The narrowest point of the main flow channel is the point along the longitudinal axis at which its cross-sectional area is smallest. Due to such a size ratio the fluid experiences a small flow resistance in the fluidic component, which leads to a low pressure loss within the fluidic component.

According to another embodiment, 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 its narrowest point can be the same size.

The distance between the inlet opening and the outlet opening along the longitudinal axis can be defined as component length. Then, the component width and the component depth extend perpendicularly to the component length and to each other. The component width in the oscillation plane and the component depth extend substantially perpendicularly to the oscillation plane. Correspondingly, the inlet opening and the outlet opening each have a width and a depth which define the size of the respective cross-sectional areas. The main flow channel can have a width and depth which change along the longitudinal axis. The width and depth of the main flow channel at a point along the longitudinal axis determine the cross-sectional area of the main flow channel at this point of the longitudinal axis.

The component depth can be constant for the entire fluidic component. In this case, the width of the inlet opening can be smaller than or equal to the width of the outlet opening. Alternatively or in addition, the width of the inlet opening can be smaller than or equal to the width of the main flow channel at its narrowest point. Furthermore the width of the inlet opening, the width of the outlet opening and the width of the main flow channel at its narrowest point can be the same size. Alternatively, the component depth cannot be constant for the entire fluidic component.

According to another embodiment, the component depth can be greater than ¼ of the width of the inlet opening, preferably greater than ½ of the width of the inlet opening. What is preferred in particular is a component depth which is greater than the width of the inlet opening, and what is preferred quite particularly is a component depth which is greater than twice the width of the inlet opening.

The body which interacts with the fluid flow for the purpose of heat exchange can have at least one surface via which the interaction of the body with the fluid flow can be effected. The surface can be an inner surface, if the body is a hollow body. However, the surface can also be an outer surface of the body. The at least one surface can be aligned 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. In particular, the angle substantially can be 90°. The longitudinal axis of the fluidic component can be aligned substantially parallel to the at least one surface. In this case, the oscillating fluid flow can periodically impinge on the at least one surface (in dependence on the frequency at which the fluid flow oscillates). Here, the interaction periodically changes temporally and spatially. Alternatively, the at least one surface of the body and the longitudinal axis of the fluidic component can include an approach flow angle which is not equal to 0°, for example 90°. Here, the fluid flow acts like an impingement flow. In this case, the oscillating fluid flow can permanently impinge upon the at least one surface, wherein however the position at which the oscillating fluid flow impinges upon the at least one surface changes periodically. Here, the interaction periodically changes spatially.

According to one embodiment, the heat exchanger body can have at least two surfaces which interact with the fluid flow for the purpose of heat exchange. The at least two surfaces can be arranged substantially parallel to each other and have a distance to each other so that they define an interspace or channel. The at least two surfaces can be aligned with respect to the fluidic component such that the fluid flow exiting from the fluidic component extends between the at least two surfaces, hence flows into the interspace or channel. In particular, the oscillation plane of the fluid flow exiting from the fluidic component can include an angle with the at least two surfaces. For example, this angle substantially can be 90°. Thus, the oscillating fluid flow alternately can impinge upon the one and upon the other of the at least two surfaces and hence accomplish a heat exchange with at least two surfaces of the heat exchanger body at the same time. Instead of a heat exchanger body with at least two surfaces, at least two heat exchanger bodies with at least one surface each can also be provided.

According to another embodiment, the body has at least one surface for heat exchange 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. In this case, the longitudinal axis of the fluidic component likewise extends parallel to the at least one surface. The outlet opening of the fluidic component can be oriented with respect to the at least one surface such that the width of the outlet opening extends parallel and the depth of the outlet opening perpendicularly to the at least one surface, wherein as seen along its depth the outlet opening is spaced apart from the at least one surface. Alternatively, there can also be provided at least two surfaces which extend parallel to each other and define a channel or interspace. The distance between the at least two surfaces can be at least as large as the depth of the outlet opening of the fluidic component. The fluid flow then can flow out of the outlet opening into the channel or interspace in parallel with the at least two surfaces.

Although the longitudinal axis of the fluidic component does not extend parallel to the at least one surface, but includes an approach flow angle with the same, which is not equal to 0°, the outlet opening of the fluidic component can be arranged at a distance to the at least one surface, which interacts with the fluid flow for the purpose of heat exchange. The distance is defined along an axis which extends substantially perpendicularly to the at least one surface. This distance between the outlet opening of the fluidic component and the at least one surface in particular can be at least twice as large as the width of the outlet opening.

According to another embodiment, the heat exchanger body can be a flow-through device which includes a flow chamber that can be flowed through by the fluid flow exiting from the fluidic component. The fluidic component can be arranged in the flow chamber of the body. It is also possible that a plurality of fluidic components is arranged in the flow chamber of the heat exchanger body. The same then on the one hand act as a fluid flow source and on the other hand as turbulators (turbulence elements), which additionally swirl the fluid flow. As compared to heat exchanger devices with conventional turbulators, the number of turbulators can be reduced when using fluidic components as turbulators, as the fluidic components already provide for a turbulence due to the oscillation of the exiting fluid flow (even at low flow velocities). Due to a smaller number of turbulators, the pressure loss in the heat exchanger device decreases. Hence it follows that (as compared to heat exchanger devices without a fluidic component as fluid flow source) the desired heat transfer performance can be achieved with lower input pressures or input velocities or that with the same input pressure or input velocity the heat transfer performance can be increased.

Alternatively, the flow-through device can include an inlet opening through which the fluid flow enters the body (the flow chamber of the body). Accordingly, the fluidic component is arranged outside the flow chamber of the heat exchanger body. The inlet opening of the body in particular can be arranged downstream of the outlet opening of the fluidic component. Preferably, the inlet opening of the heat exchanger body immediately adjoins the outlet opening of the fluidic component.

According to another embodiment, turbulators can be provided in the flow chamber of the heat exchanger body, which for example are arranged on at least one surface of the heat exchanger body. Fluid dead zones in the flow chamber of the heat exchanger body thereby can be reduced and the effectiveness of the device can be increased.

The described at least one surface in particular is a planar surface or a surface with planar portions. Alternatively, the surface can have curvatures.

The heat exchanger body can be a hollow body or a solid body. In the hollow body, the inner surfaces or the outer surfaces can interact with the fluid flow. In the solid body, the outer surfaces can interact with the fluid flow.

The heat exchanger device also can include more than one fluidic component as a fluid flow source and/or more than one heat exchanger body.

The fluid flow in particular can be a liquid flow or a gas flow.

The heat exchanger device can be configured as a plate heat exchanger, heat tube or as turbine blades. It is also conceivable to use a fluidic component as a fluid flow source in technically related devices (evaporators, condensers, columns, liquefiers, oil coolers, steam generators, solar collectors and heaters).

By means of deep drawing or embossing the fluidic component can be integrated into a wall of the heat exchanger body. In particular, there can be provided fluidic components which have no sharp edges, but are provided with radii.

What has been said on the above-mentioned fluidic component likewise applies for the fluidic components of the following embodiments.

According to one of these embodiments, the fluid flow source, which is configured to provide a fluid flow, includes at least one first fluidic component and at least one second fluidic component, which each comprise at least one means for creating an oscillation of the fluid flow, wherein the at least one means for creating an oscillation of the fluid flow comprises no movable components. The at least one first fluidic component and the at least one second fluidic component can sectionally cross each other without the at least one first fluidic component and the at least one second fluidic component being connected with each other by such crossing. Fluidic components sectionally crossing each other are understood to be fluidic components which for example spatially intersect or overlap each other. In the crossing portions formed by crossing, two fluidically separate fluid flows can flow. By fluidic components crossing each other, the fluid flow source can be designed in a particularly compact and space-optimized form without the fluidic components influencing/impeding each other when the oscillation is created by the interaction of the fluid flows, and without the occurrence of high pressure losses.

Such a fluid flow source can be part of a heat exchanger device which includes the fluid flow source and a body for heat exchange, 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.

The fluid flow exiting from the fluid flow source or the discharged fluid flow can interact with the heat exchanger body. Alternatively or in addition, the fluid flow provided by the fluid flow source can interact with the heat exchanger body for the purpose of heat exchange, while the fluid flow flows in the fluid flow source and in particular before the fluid flow exits from the fluid flow source. In the latter case, the fluid flow source is arranged relative to the heat exchanger body such that the fluid flow flowing in the fluid flow source interacts with the heat exchanger body for the purpose of heat exchange before the fluid flow exits from the fluid flow source. The heat exchanger body for example can be configured as a boundary wall of the fluid flow source. In this case, the fluid flow source already forms a heat exchanger device with the boundary wall acting as a heat exchanger body. Such a heat exchanger device hence comprises a fluid flow source, which is configured to provide a fluid flow, and a body for heat exchange, wherein the body for heat exchange is part of the fluid flow source and wherein the fluid flow source is configured to conduct the fluid flow such that the fluid flow interacts with the heat exchanger body for the purpose of heat exchange, before the fluid flow exits from the fluid flow source.

In particular, the at least one first fluidic component and the at least one second fluidic component of the fluid flow source each can have a flow chamber which each can be flowed through by a fluid flow. Each flow chamber can have an inlet opening through which the fluid flow enters the respective flow chamber, and an outlet opening through which the fluid flow exits from the respective flow chamber. Each flow chamber can comprise a main flow channel and as the at least one means 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. Thus, each flow chamber can comprise a main flow channel and at least one secondary flow channel. Instead of the at least one secondary flow channel another means can be provided for creating an oscillation of the fluid flow at the outlet opening, which comprises no movable components for forming an oscillation of the fluid flow.

Within each main flow channel, the fluid flow can flow along a main flow direction which is directed from the inlet opening to the outlet opening. Via an inlet of the at least one main flow channel, by which the main flow channel and the at least one secondary channel preferably are fluidically connected with each other at the downstream end of the main flow channel (upstream of the outlet opening), a part of the fluid flow can enter the at least one secondary flow channel instead of exiting (following the main flow direction) from the main flow channel via the outlet opening. Within the at least one secondary flow channel this part of the fluid flow (the so-called secondary flow) can flow in the direction of an outlet of the at least one secondary flow channel, by which the main flow channel and the at least one secondary channel preferably are fluidically connected with each other at the upstream end of the main flow channel (downstream of the inlet opening). At the outlet of the at least one secondary flow channel, the secondary flow channel can laterally act on the fluid flow entering the main flow channel through the inlet opening and thus effect a deflection of the fluid flow. Due to the deflection, the amount of the fluid flow entering the at least one secondary flow channel can decrease so that as a result the deflection of the fluid flow entering the main flow channel through the inlet opening, which is caused by the secondary flow, is less pronounced. The smaller deflection can also lead to an increase of the amount of the fluid flow entering the at least one secondary flow channel. In general, a fluid flow oscillating in a plane (the so-called oscillation plane) thus can be created, which exits from the fluidic component via the outlet opening. In particular, the at least one first fluidic component and the at least one second fluidic component can be arranged relative to each other such that the oscillation planes of the fluid flows which exit from the at least one first and at least one second fluidic component substantially lie in the same plane.

According to one embodiment, 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. Alternatively, the main flow direction of the at least one first fluidic component and the main flow direction of the at least one second fluidic component can be identically directed. In the latter case, the inlet opening (outlet opening) of the at least one first fluidic component and the inlet opening (outlet opening) of the at least one second fluidic component can be offset along the main flow direction or be formed at the same height. Furthermore, it can be provided that as seen along the main flow direction(s) the at least one first fluidic component and the at least one second fluidic component are arranged side by side. In particular, the oscillation plane of the at least one first fluidic component and the oscillation plane of the at least one second fluidic component can extend substantially parallel to each other or in the same plane. The relative orientation of the at least one first fluidic component and of the at least one second fluidic component can depend on the concrete shape of the main flow channel and of the at least one secondary channel of the at least one first fluidic component and of the at least one second fluidic component. It can be provided that 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 identical with the main flow channel and the at least one secondary flow channel of the at least one second fluidic component. In particular, the at least one first fluidic component and the at least one second fluidic component can be completely identical. Alternatively, the main flow channel or the at least one secondary flow channel (or both) of the at least one first fluidic component can differ in shape and/or size from the main flow channel and from the at least one secondary flow channel of the at least one second fluidic component. The number of the secondary flow channels for the at least one first fluidic component and the at least one second fluidic component can also be different.

If a plurality of first fluidic components and/or a plurality of second fluidic components are provided, the same can be arranged relative to each other such that together they form a repeating pattern. For example, the first fluidic components and the second fluidic components and be arranged in alternation (as seen transversely to the main flow directions).

According to one embodiment a dividing wall is provided, which is arranged in the fluid flow source and preferably extends over the entire fluid flow source. The dividing wall has a first side and a second side opposite the first side. The dividing wall separates the at least one first fluidic component and the at least one second fluidic component from each other such that the at least one first fluidic component is disposed on this side (on the first side) of the dividing wall and the at least one second fluidic component is disposed on that side (on the second side) of the dividing wall. The dividing wall is not planar, but includes a plurality of concave or convex deformations which protrude substantially perpendicularly from the main plane of extension of the dividing wall. The dividing wall can include flat portions which extend parallel to or in the main plane of extension of the dividing wall, as well as some portions which extend substantially perpendicularly to the main plane of extension of the dividing wall. Depending on the extent of the draft angle, the angle of the latter portions relative to the main plane of extension of the dividing wall can deviate from 90° more or less. The flat portions which extend perpendicularly to the main plane of extension connect the flat portions which extend parallel to or in the main plane of extension so that the dividing wall can be continuous and without interruptions.

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 can be formed by the deformations of the dividing wall. The deformation which on the first (second) side represents a depression in which the fluid flow can flow can represent an elevation on the second (first) side, which on the second (first) side delimits the main flow channel or the at least one secondary flow channel and through which no fluid can flow. The main plane of extension of the dividing wall extends substantially parallel to the oscillation plane(s) of the at least one first fluidic component and of the at least one second fluidic component.

The dividing wall with the deformations can be produced by deforming an originally planar wall. At the transition between the flat portions, which extend parallel to or in the main plane of extension of the dividing wall, and the flat portions which extend substantially perpendicularly to the main plane of extension of the dividing wall, radii are obtained, whose size substantially depends on the material thickness of the material used. Alternatively, the dividing wall with the deformations can be produced by an injection molding method or by means of a 3D printer. Furthermore, it is possible to work out the dividing wall with deformations from a block of material by means of ablative methods. The dividing wall can have an almost constant material thickness.

To enable crossing of the at least one first fluidic component and the at least one second fluidic component, it can be provided that the depth (extension substantially perpendicularly to the main plane of extension of the dividing wall) 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 is not constant. The dividing wall can be shaped such that each secondary flow channel includes at least one crossing portion in which the at least one first fluidic component and the at least one second fluidic component cross each other. Such a crossing portion is deformed concavely/convexly (depending on the side of viewing) to an extent different from a portion (of the secondary flow channel) adjacent to the crossing portion. The extent of the deformation in the crossing portion corresponds neither to the maximum nor to the minimum (zero) deformation. On the other hand, the extent of the deformation in the adjacent portion can correspond to the maximum or the minimum deformation or to a deformation inbetween. Accordingly, in the crossing portion both the at least one first fluidic component (on the first side of the dividing wall) and the at least one second fluidic component (on the second side of the dividing wall) each has a depression in which the fluid can flow.

The fluid flow source can include 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, wherein the dividing wall is arranged between the front wall and the rear wall. The front wall, rear wall and dividing wall can be connected with each other in a fluid-tight manner so that within the fluidic components the fluid only can flow in the designated areas and only can enter and again exit from the fluid flow source via correspondingly provided openings. In certain portions (i.e. (flat) portions of the dividing wall, which lie in a plane that extends parallel to the main plane of extension of the dividing wall) the dividing wall can rest against the front wall and the rear wall due to its deformation. In these portions, the dividing wall can have openings. Due to the abutment of the portions of the dividing wall against the front wall or rear wall, the openings are closed so that the at least one first fluidic component and the at least one second fluidic component always is delimited completely as seen along the depth (extension substantially perpendicularly to the main plane of extension of the dividing wall or to the oscillation plane). Preferably, however, the dividing wall is formed as a continuous wall without openings. When the front wall faces the first side of the dividing wall and the rear wall faces the second side of the dividing wall, the at least one first fluidic component is formed between the front wall and the dividing wall and the at least one second fluidic component between the rear wall and the dividing wall.

The front wall and the rear wall can be configured as a heat exchanger body of the heat exchanger device. Alternatively, a heat exchanger body can be provided in addition, which for example flatly rests against the front wall and/or against the rear wall.

The invention will be explained in detail below with reference to exemplary embodiments in conjunction with the drawings.

In the drawings:

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

FIG. 2 shows a sectional representation of the fluidic component of FIG. 1 along the line A′-A″;

FIG. 3 shows a sectional representation of the fluidic component of FIG. 1 along the line B′-B″;

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

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

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

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

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;

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

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

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

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;

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

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

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

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.

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.

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_INand the outlet opening 102 has an outlet width b_EX. The widths in the oscillation plane are defined substantially perpendicularly to the longitudinal axis A.

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: ⅓·b≤l≤4.5·b.

The width b_EXof the outlet opening 102 is ⅓ to 1/50 of the component width b, preferably ⅕ to 1/20. The width b_EXof 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_INof the inlet opening 101 is ⅓ to 1/30 of the component width b, preferably ⅕ to 1/15.

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.

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.

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.

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.

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 α (see FIG. 6).

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.

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 b₁₀₃of the main flow channel 103 increases in the downstream direction, whereas the depth t remains constant (FIGS. 1 and 2).

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 b₁₀₃of 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 b₁₀₃) principally is located at the upstream end of the inner blocks 11a, 11b. Due to the radii 119a, 119b the smallest distance (b₁₀₃) is slightly shifted in the downstream direction. The width b₁₀₃of the main flow channel 103 at its narrowest point is greater than the width b_INof 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 γ. 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.

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.

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 δ. 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.

The outlet opening can be rounded by a radius 109. This radius 109 preferably is smaller than the width b_INof the inlet opening 101 or the smallest width b₁₀₃of 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.

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_IN, b_EX. Alternatively, a non-rectangular cross-sectional area also is conceivable for the inlet opening 101 and the outlet opening 102, for example circular.

In the embodiment of FIG. 1 the cross-sectional area of the inlet opening 101, which is defined by the inlet width b_INand the component depth t_INat the inlet opening 101, is smaller than the cross-sectional area of the outlet opening 102, which is defined by the outlet width b_EXand the component depth t_EXat the outlet opening 101. In particular, the inlet width b_INis smaller than the outlet width b_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 b₁₀₃of 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 b₁₀₃and the component depth t₁₀₃at this point. At a constant component depth (t_IN=t_EX=t₁₀₃) it applies according to the invention: b_IN≤b_EXand/or b_IN≤b₁₀₃. In particular, the inlet width b_IN, the outlet width b_EXand the width b₁₀₃can be the same size (b_IN=b₁₀₃=b_EX).

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 ¼ of the inlet width b_IN. Advantageously, the component depth t is greater than half the inlet width b_IN. It is particularly advantageous when the component depth t is greater than the inlet width b_INand for some applications even greater than twice the inlet width b_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.

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.

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.

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.

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.

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.

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 I₃₃₃to the outlet opening 102 of the fluidic component 1. This distance I₃₃₃is at least twice as large as the width b_EXof the outlet opening 102. In heat exchanger devices with hole-type nozzles as a fluid flow source this distance I₃₃₃must be at least five times the width b_EXof 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.

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.

The outlet opening 102 of the fluidic component 1 can have a depth t_EXwhich corresponds to the distance t₃₀₃between the surfaces 304c, 304d. This distance t₃₀₃is 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_EXof the outlet opening 102 of the fluidic component 1 however is smaller than the depth t₃₀₃of 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 t₃₁₁to the other one of the two surfaces 304c, 304d. This distance t₃₁₁preferably is smaller than the extension t₃₃₃of the turbulator 333 along the depth t₃₀₃of the flow chamber 303 of the heat exchanger body 3.

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 β with the surface 304e, which is not equal to zero. In FIG. 6, the approach flow angle β only is an example. The outlet opening 102 of the fluidic component 1 is arranged at a distance I₁₄to the surface 304e. The distance I₁₄is defined along an axis which extends substantially perpendicularly to the surface 304e. Preferably, the distance I₁₄is at least twice as large as the width b_EXof the outlet opening 102 of the fluidic component 1. In heat exchanger devices with hole-type nozzles as a fluid flow source this distance I₁₄must be at least five times the width b_EXof 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.

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 I₁₄from 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_EXof the outlet openings 102.

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.

In the illustrated embodiment, the approach flow angle is β=90°. The approach flow angle β 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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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.

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_maxwhich is obtained by the deformation of the dividing wall 15. The width of the main flow channels 103′, 103″ increases in the downstream direction.

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_maxand sectionally a reduced depth trey which is smaller than the maximum depth t_max. The reduced depth t_redfor example can be half the maximum depth t_max. When several portions of reduced depth t_redare 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_maxin 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_maxin the region of the transition to the respective main flow channel 103′, 103″, which likewise has the maximum depth t_max. The portions of maximum depth t_maxare interrupted by portions of reduced depth t_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′.

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_max(like the main flow channel 103′ (103″))→reduced depth t_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_max(formation of the inner blocks 11a″, 11b″ (11a′, 11b′) of the second fluidic components 1″ (first fluidic components 1′)) 4 reduced depth t_red(crossing with a portion of the secondary flow channels 104a″, 104b″ (104a′, 1040 of the second fluidic components 1″ (first fluidic components 1′))→maximum depth t_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_red(crossing portions) is the same and corresponds to half of t_max. However, these two crossing portions can have differently large depths. Moreover, the reduced depth need not be half of t_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.

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′).

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).

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.

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″.

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_maxof 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.

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).

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.

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″.

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.

Heat Exchanger Device

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