Device for guiding at least two fluid streams, electrochemical system and method for producing a device with a heat transfer element
Patent Information
- Authority / Receiving Office
- EP · EP
- Patent Type
- Applications
- Current Assignee / Owner
- ROLLS ROYCE SOLUTIONS GMBH
- Filing Date
- 2024-08-09
- Publication Date
- 2026-06-17
Smart Images
Figure EP2024072655_13022025_PF_FP_ABST
Abstract
Description
[0001] DESCRIPTION
[0002] Device for guiding at least two fluid streams, electrochemical system and method for producing a device with a heat exchanger body
[0003] The invention relates to a device for guiding and / or transferring heat between at least two fluid flows, a process fluid and a heat exchange fluid, with a heat exchanger body, wherein the heat exchanger body has a gyroidal structure with a main gyroid and a secondary gyroid for intersection in the form of a nested gyroid to form at least a first and second channel system, wherein the first and second channel system each has a first passage width, and to form an intermediate space system, wherein the intermediate space system has a second passage width, wherein the first and second channel system are spatially separated from the intermediate space system.
[0004] The invention also relates to an electrochemical system and a method for producing a device with a heat exchanger body.
[0005] Heat exchangers with monolithic bicontinuous core structures are known in the prior art. These are used for heat transfer between at least two fluids flowing through the heat exchanger. The core structure is intended to maximize the heat transfer surface or volume of the heat exchanger in order to improve the efficiency of heat transfer between the fluid flows passing through the heat exchanger. Known heat exchangers have at least one gyroidal structure with at least one main gyroid, which comprises at least two independent labyrinths for the two fluid flows flowing through the heat exchanger.
[0006] From US 11,181,329 B2, for example, such a heat exchanger is known with a monolithic bicontinuous core structure comprising at least one non-intersecting surface by means of which two independent labyrinth volumes are defined. By selecting suitable lattice parameters, the geometry of the core structure can be changed, whereby the hydraulic diameter, the surface compactness, the flow volume, the heat transfer and the pressure drop within the heat exchanger can be adjusted. The core geometry is created by periodically repeating an elementary cell geometry in the three different spatial directions. Fluid inlets into and fluid outlets from the at least two labyrinths are defined by the structural outer boundaries of the core structure of the heat exchanger. These are created by targeted covering orClosing or leaving open corresponding external areas for introducing and discharging the two fluid streams.
[0007] For certain applications, such core structures of heat exchangers also feature nested gyroidal structures consisting of a main gyroid and a secondary gyroid. The secondary gyroid, particularly within a main gyroid, is formed as a repeating cell structure, which can have a significantly lower lattice constant than the main gyroid.
[0008] The creation of such a nested gyroid is described, for example, in CN 112475319 B, wherein the main gyroid and the secondary gyroid have essentially the same lattice constants but different channel widths prior to intersection. Intersecting to form a nested gyroid structure creates a core structure that includes a first and a second channel system defining the main gyroid, and an interstitial space system defined by the secondary gyroid with a lattice constant smaller than that of the channel systems. The first and second channel systems are spatially separated from each other by the interstitial space system.
[0009] The gyroid structures described above typically have a delicate design, which improves heat transfer efficiency, but is also significantly more susceptible to static and dynamic loads. Particularly during operation of such a device for guiding and / or transferring heat between two fluid flows with a heat exchanger body comprising a gyroidal structure, undesirable deformations can occur due to vibrations and shocks during the flow of the fluid flows or due to differing pressure conditions in the channel systems. This can ultimately lead to the failure of the core structure and the separation between the channel systems and the interstitial space system, as well as to the mixing of the fluids that would otherwise flow separately.This is where the invention comes in. Its object is to provide a device for guiding at least two fluid streams, which avoids the disadvantages described above and thus achieves increased structural integrity. In particular, the invention was based on the object of providing a device for guiding fluids that provides at least one alternative development to known devices.
[0010] It is also the object of designing the device with regard to a heat exchanger not only or alternatively with regard to increased structural integrity, but also or alternatively with regard to improved heat transfer, in particular between a process fluid and a heat exchange fluid.
[0011] The invention solves the underlying problem according to a first aspect by a device for guiding and / or transferring heat between at least two fluid flows, in particular a process fluid and a heat exchange fluid, of the type described at the outset with the features of claim 1.
[0012] The invention is based on a device for guiding and / or transferring heat between at least two fluid flows, a process fluid and a heat exchange fluid, with a heat exchanger body, wherein the heat exchanger body has a gyroidal structure with a main gyroid and a secondary gyroid for intersection in the form of a nested gyroid to form at least a first and second channel system, wherein the first and second channel system each have a first passage width, and to form an intermediate space system, wherein the intermediate space system has a second passage width, wherein the first and second channel system are spatially separated from the intermediate space system.
[0013] According to the invention, the intermediate space system has a support structure which penetrates the intermediate space system.
[0014] In particular, the invention thus proposes, on a heat exchanger body having a nested gyroid structure, comprising a main gyroid and a secondary gyroid with substantially the same lattice constant but different passage widths, which form a first and a second channel system and an intermediate space system spatially separated from the first and second channel system, to equip the intermediate space system with a support structure penetrating the intermediate space system.
[0015] The present invention pursues the approach of stiffening the intermediate space system by means of the support structure so that static or dynamic loads during operation of the device according to the invention, i.e. when fluid flows guided through the heat exchanger flow through the first and second channel systems and preferably also through the intermediate space system, are absorbed, thus efficiently counteracting excessive deformation, in particular plastic deformation, of the gyroid structure. The nested gyroid according to the invention has a main gyroid and a secondary gyroid, with both gyroid structures having essentially the same lattice constant. The main gyroid and secondary gyroid preferably have an almost identical lattice structure. The gyroids differ from one another only in their passage width. In this case, a first and a second channel system are formed by means of the main gyroid.The secondary gyroid defines an interspace system through which the two channel systems are particularly separated from each other. Even with different pressure conditions within the first and second channel systems, and preferably also within the interspace system, excessive deformation of the gyroidal structure of the heat transfer is avoided by the support structure stiffening the interspace system. Furthermore, the passage widths of the channel systems and the interspace system remain advantageously constant, which also has a beneficial effect on the heat transfer efficiency of a device designed according to the invention.
[0016] Advantageous further developments of the invention can be found in the dependent claims and specify in detail advantageous possibilities for realizing the concept explained above within the scope of the task and with regard to further advantages.
[0017] A further development of the invention provides that the intermediate space system is delimited in its passage width by walls and separated from the first and second channel systems. With the help of the walls, a structurally simple spatial demarcation of the intermediate space system from the adjacent first and second channel systems is achieved. The support structure is preferably designed to hold the walls delimiting the intermediate space system relative to one another in the second passage width. This efficiently counteracts the deformation of the gyroid structure of the heat exchanger. Depending on the geometric development of the gyroid structure of the heat exchanger, the walls extend in any spatial direction, wherein the intermediate space system is designed as a type of third labyrinth within the heat exchanger, which is always efficiently divided by the two channel systems by means of the walls.
[0018] According to a preferred development of the device, at least one of the walls is common to the intermediate space system on the one hand and the first channel system or second channel system on the other. The heat exchanger body is thus preferably designed for heat transfer between the at least two fluid flows, in particular the process fluid and the heat exchange fluid. A wall delimiting the intermediate space system on one side preferably simultaneously delimits one of the channel systems arranged adjacent to the intermediate space system, i.e. either the first or the second channel system. The intermediate space system and the first or second channel system thus each share a wall. The wall forms a fluid-impermeable barrier between the intermediate space system and the first or second channel system.second channel system, thereby preventing mixing of the fluid flows passing through the first and second channel systems, and preferably also through the interstitial space system. The walls also form a solid structure, which is inherently dimensionally stable due to their physical properties. In this context, dimensionally stable means that the walls retain their existing shape under normal ambient conditions.
[0019] According to a further development, the first and second channel systems are preferably separated from one another by walls which are formed by means of the walls delimiting the intermediate space system. In particular, it is provided that a first wall is common to the intermediate space system and the first channel system, and a second wall is common to the intermediate space system and the second channel system. The walls by which the intermediate space system is separated from the first and second channel systems simultaneously form the walls by which the first and second channel systems and the fluid flows guided in the first and second channel systems are spatially separated from one another. The intermediate space system thus forms a labyrinth within a wall separating the first and second channel systems. This creates a type of double-walled wall.The first and second channel systems also extend through the heat exchanger in any spatial direction, forming a kind of labyrinth, enabling efficient heat transfer between the fluid flows in the first and second channel systems and preferably the intermediate space system. In a possible development of the invention, one and the same fluid flows through the first and second channel systems, which is divided into two separate fluid flows. In an alternative embodiment, two different fluids are conducted through the first and second channel systems as separate fluid flows.
[0020] In a further development of the device, the second passage width of the intermediate space system is smaller than the first passage width. In particular, the first passage width of the first and second channel systems is different from one another or the same. The intermediate space system formed within the heat exchanger has a significantly smaller total passage cross-section than the channel systems. By means of passage widths of different sizes, the heat transfer can be specifically influenced, in particular when certain temperature differences have to be achieved by means of the heat exchangers. This makes it easy to ensure that the process fluid, which is passed through the intermediate space system, for example, is either cooled down to a correspondingly low temperature or heated up to a correspondingly high temperature upon leaving the heat exchanger.Preferably, the heat exchange fluid is passed through the first and second channel system, which enables an effective temperature increase or temperature reduction of the process fluid due to its larger volume flow compared to the process fluid in the heat exchanger.
[0021] A further development of the device according to the invention provides that the support structure comprises a plurality of support elements that extend between the wall surfaces of walls that define the intermediate space system and connect the walls to one another. Providing a plurality of support elements as a support structure represents a structurally simple way to stiffen the intermediate space system and thus the gyroidal structure as a whole.
[0022] Preferably, it is possible in an improved manner to keep the distance between the walls defining the intermediate space system constant, at least in certain regions, using the support elements. Preferably, the support struts of the support structure are arranged at predetermined distances from one another, with their spacing being selected such that, in the event of a pressure difference between the fluid flows guided on the opposite sides of a wall, only elastic deformation of the wall is permitted. Plastic deformation of the wall and any resulting impairment of the gyroidal structure of the heat exchanger body are thus avoided.
[0023] The support elements are preferably designed as support struts with a cross-section that remains constant in the direction of extension. The support elements, which preferably penetrate the intermediate space system, cause turbulence within the fluid flow as a fluid passing through the heat exchanger flows through the intermediate space, whereby the heat transfer from the intermediate space system towards the adjacent first and second channel systems or towards the intermediate space system is further increased or improved. The support elements can have any cross-section, such as circular or rectangular. In a possible further development, it is also conceivable for the cross-section of the support struts penetrating the intermediate space system to vary in the direction of extension. The central region of a support strut, which lies approximately centrally between the walls delimiting the intermediate space system, can be thickened, in particular compared to their ends.
[0024] Another development provides that a rounded transition is formed in the connection area of a support element with a respective wall, whereby the introduction of force into the support element as well as from the support element into the wall is improved.
[0025] According to a preferred development of the device, the support elements extend substantially transversely, in particular perpendicularly, to a respective adjacent wall surface of the wall. The preferably perpendicular alignment of the support elements to the wall surfaces achieves or further improves optimal force introduction into and out of the support element and into the adjoining wall. The preferably perpendicular alignment to the wall surfaces means that the walls are always connected to one another via the shortest route. Even with different pressure levels on wall surfaces facing away from one another and within the channel systems or intermediate space systems delimited by them, spatial displacement of the walls relative to one another and, under certain circumstances, a change in the passage width and shear stresses in the connection areas between the support element and the wall are avoided.
[0026] According to a preferred development of the invention, the first and second channel systems have walls that limit their passage width, the wall surfaces of which comprise a plurality of depressions that enlarge the surface of the walls, in particular the surface of the wall surfaces; ie, the first and second channel systems have walls that limit their passage width, the wall surfaces of which comprise a plurality of depressions that enlarge the surface of the walls, in particular the surface of the wall surfaces.
[0027] The depressions increase the surface area—particularly within the first and / or second channel system—which also further improves heat transfer between the channel systems and the intermediate space system. The depressions on the wall surface of the wall associated with the first and second channel systems have, starting from the wall surface, a depth dimension that, relative to the width dimension of the wall itself, has a ratio of < 0.3. This ensures that the depressions, which are formed on at least one side of the wall, preferably on the wall surface that delimits the passage width of the first and / or second channel system, do not result in any reduction in the strength of the wall itself.
[0028] According to a preferred embodiment, the depressions are designed as material recesses, which have a preferably circular further development with a concave curvature on the wall surface. The provision of material recesses as depressions represents a structurally simple option for producing a wall surface with a regularly irregular surface, which also generates turbulence for improved heat transfer. The material recesses have a circular shape at the level of the wall surface with a diameter that corresponds to at least half to approximately the entire width of the wall. The base delimiting the material recess has a preferably concave curvature. The depressions preferably have a further development similar to the depressions on the surface of a golf ball.
[0029] A preferred development of the device is characterized by at least two fluid inlets and fluid outlets assigned to the heat exchanger body, wherein the two fluid flows, preferably the process fluid and the heat exchange fluid, are guided in countercurrent through the heat exchanger body. By guiding the fluid flows passing through the heat exchanger body in countercurrent, in conjunction with the development of the heat exchanger body as a nested gyroid, the effectiveness of heat transfer is further improved. Due to the further improved heat transfer, a heat exchanger body can be used whose dimensions are significantly reduced in order to achieve the same heat transfer performance. This enables advantageous material savings for the design of such heat exchanger bodies used for heat transfer.
[0030] Due to the separate design of the first and second channel systems and the intermediate space system in the heat exchanger body, it is possible to conduct three different fluids through the heat exchanger body designed according to the invention.
[0031] In a further development, one and the same fluid, preferably the heat exchange fluid, is passed through the first and second channel systems, and the process fluid is passed through the intermediate space system. The volume fraction of the heat exchange fluid flowing through the first and second channel systems is preferably approximately equal and spatially separated from one another within the heat exchanger body, even if the channels are arranged alternately with one another.
[0032] Depending on the number of fluids used, the device according to the invention has at least two fluid inlets and two fluid outlets. If three different fluids are passed through the heat exchanger, three fluid inlets and three fluid outlets are required. To ensure that only the required channel / space system is exposed to the corresponding fluid, corresponding inlet areas on the heat exchanger are left open to allow the fluid flow to flow in, and adjacent areas are covered or closed to prevent the fluid flow from flowing in.
[0033] According to an alternative development, the heat exchanger body is provided with three fluid inlets and outlets respectively associated with it, wherein the heat exchange fluid in the first and second channel systems is preferably conducted in counterflow to one another and the process fluid in the intermediate space system is conducted in crossflow to the heat exchange fluid. By conducting at least one of the fluid streams in crossflow to the at least one further fluid stream, a simplified fluid supply to the channel systems carrying the fluid streams and to the intermediate space system is achieved. The introduction and discharge of the various fluid streams preferably takes place on wall regions facing away from one another, in particular extending at right angles to one another, which in particular further simplifies the introduction and discharge of various fluids to and from the heat exchanger.According to a second aspect, the present invention relates to an electrochemical system comprising a fuel station or an electrolyzer and at least one device according to one of the preceding developments, in particular according to the features of claims 1 to 12, for guiding at least two fluid flows, in particular a process fluid and a heat exchange fluid for heat transfer between the process fluid and a heat exchange fluid.
[0034] The invention proposes in an independent form according to the second aspect to couple a device for guiding and / or transferring heat according to the features of claim 1 to an electrochemical system comprising a fuel cell or an electrolyzer in order to efficiently dissipate the heat generated during operation of the fuel cell or the electrolyzer, wherein the support structure penetrating the intermediate space system provides the heat exchanger body of the device according to the invention with increased structural strength in conjunction with improved effectiveness in heat transfer.
[0035] The preferred developments described for the device according to the invention for guiding and / or transferring heat between two fluids according to the first aspect are also simultaneously preferred developments of the electrochemical system according to the invention, provided they do not contradict each other. Accordingly, the electrochemical system, in its independent form, has all of the features cited as preferred developments for the device, such as, for example, the walls separating the intermediate space system from the first and second channel systems, the plurality of support elements forming the support structure, and the recesses formed on the wall surface of the first and second channel systems for surface enlargement, to name only at least one of the exemplary preferred developments.
[0036] According to a third aspect, the invention relates to a method for producing a device according to one of the developments described above, in particular according to the features of claims 1 to 12, with a heat exchanger body, wherein the heat exchanger body is produced using an additive manufacturing process.
[0037] Manufacturing using an additive manufacturing process, such as 3D printing, enables the heat exchanger body to be developed as a one-piece component. Upon completion of the component, all structural features, such as the support structure penetrating the intermediate space system or the recesses formed on the wall surfaces of the walls delimiting the first and second channel systems, are thus preferably created.
[0038] The heat exchanger body is thus manufactured without complex subsequent processing, although this is not excluded. In particular, during post-processing, corresponding wall areas defining the outer dimensions of the heat exchanger body are prepared to form corresponding fluid inlets and outlets. For this purpose, inlet areas of the first channel system, for example, to the second channel system / intermediate space system, which are not intended as fluid inlets in this area, are sealed using specially designed cover elements. Alternatively, such sealed areas can also be created using the additive manufacturing process.
[0039] The heat exchanger body is preferably made of aluminum (advantage: light) or copper (better thermal conductivity); ie, in particular, the nested gyroid is made of aluminum or copper.
[0040] Embodiments and configurations of the invention are now described below with reference to the drawing in comparison to the prior art, some of which is also shown. These are not necessarily intended to represent the embodiments to scale; rather, where useful for explanation, the drawing is schematic and / or slightly distorted. With regard to additions to the teachings immediately apparent from the drawing, reference is made to the relevant prior art. It should be noted that many modifications and changes to the form and detail of an embodiment can be made without deviating from the general idea of the invention. The features of the invention disclosed in the description, in the drawing and in the claims can be essential for the further development of the invention, both individually and in any combination.Furthermore, all combinations of at least two of the features disclosed in the description, the drawings, and / or the claims fall within the scope of the invention. The general idea of the invention is not limited to the exact form or detail of the preferred embodiment shown and described below, nor is it limited to an object that would be limited compared to the object claimed in the claims. In the case of specified dimensioning ranges, values within the stated limits are also intended to be disclosed as limit values and can be used and claimed as desired.
[0041] Further advantages, features and details of the invention will become apparent from the following description of the preferred embodiments and from the drawing, which shows:
[0042] FIG. 1: a perspective view of a heat exchanger body according to the invention;
[0043] FIG. 2: a detailed view of the heat exchanger body according to the invention in partial section;
[0044] FIG 3: a perspective view of a first embodiment of a device according to the invention with a heat exchanger body;
[0045] FIG 4: a perspective view of a second embodiment of a device according to the invention with a heat exchanger body, and
[0046] FIG. 5: a schematic representation of an electrochemical system with a device according to the invention.
[0047] FIG. 1 shows a perspective view of a heat exchanger body 12 for a device 10 for guiding at least two fluid flows FS 1, 2, 3, in particular a process fluid and a heat exchange fluid.
[0048] The gyroid structure also serves as a heat exchanger. In a heat exchanger, heat is transferred from a higher-temperature medium to another, or a lower-temperature medium with identical properties.
[0049] The heat exchanger used here is a heat exchanger body 12, which has a gyroidal structure 14, designed as a nested gyroid 14', consisting of a main gyroid 16 and a secondary gyroid 18. The intersection of the main gyroid 16 and the secondary gyroid 18 creates a first channel system 20 and a second channel system 22, as well as an intermediate space system 24 spatially separated from the first and second channel systems 20, 22. The media of the fluid flows FS 1, 2, 3, in particular a process fluid and a heat exchange fluid, are thus spatially separated from one another by a partition wall. During heat transfer, heat is first transferred from a warmer medium to the partition wall, conducted through the partition wall, and then transferred from the partition wall to a colder medium. Such heat transfer therefore involves the transport of thermal energy from one medium through the partition wall back to the other medium and determines the performance quality of the heat exchanger.If this heat transfer performance is to be increased, this can be achieved by enlarging the separating surfaces of the partition wall, since both media have a larger exchange surface available for the transfer of thermal energy.
[0050] By using a nested gyroid—by intersecting the main gyroid 16 and the secondary gyroid 18—the exchange surface can be significantly increased and the amount of heat transferred in the heat exchanger increased without increasing the installation space. Preferably, a gyroid of the same size but with a thinner wall thickness is used. This so-called Boolean intersection creates an additional flow space. This promotes energy transfer between the media; a more compact installation space is created with the same heat exchanger performance.
[0051] Specifically, according to the present preferred embodiment, the first and second channel systems 20, 22 are spatially separated from one another, just as the intermediate space system 24 is spatially separated from the first and second channel systems 20, 22. The first and second channel systems 20, 22 have a passage width DWi, and the intermediate space system 24 has a second passage width DW2. As can be seen in FIG. 1, the second passage width DW2 of the intermediate space system 24 is smaller than the first passage width DWi of the first and second channel systems 20, 22.
[0052] According to the concept of the invention, the intermediate space system 24, as can be seen from FIG. 1, has a support structure 26 which penetrates the intermediate space system 24 and which imparts increased strength to both the intermediate space system 24 and the entire gyroidal structure 14 and thus stabilizes it. The gyroidal structure 14, designed as a nested gyroid 14', has walls 28, 30 which separate the first and second channel systems 20, 22 from one another and also separate the intermediate space system 24 from the first and second channel systems 20, 22. FIG. 2 shows an enlarged detailed view of the gyroid structure 14' in section, which illustrates the spatial configuration of the channel systems 20, 22 and the intermediate space system 24. Both the first and second channel systems 20, 22 as well as the intermediate space system 24 penetrated by the support structure 26 each form a labyrinth system orLabyrinth channels within the heat exchanger body 12 through which at least two fluid streams FSI,2,3 are passed for a corresponding heat transfer between the fluid streams.
[0053] The walls 28, 30 each delimit the two channel systems 20, 22 as well as the intermediate space system 24 in their respective passage widths DWi, DW2. The intermediate space system 24 and the first and second channel systems 20, 22 each have one of the walls 28, 30 in common, i.e., the fluid FS3 flowing through the intermediate space system 24 rests against a wall surface 28", 30' of the walls 28, 30, and the fluid flowing in the first and second channel systems 20, 22 is guided on the opposite wall surface 28', 30" of the walls 28, 30.
[0054] From FIG. 2, it can also be seen that the support structure 26 has a plurality of support elements 32, which extend between the walls 28, 30, in particular their wall surfaces 28", 30'. In particular, the walls 28, 30 are connected to one another by the support elements 32 and thus supported against one another.
[0055] The support elements 32 of the support structure 26 are designed as struts in the present case; however, these can also be designed differently or in a manner different from the struts shown here. The support elements 32 are basically designed according to the concept of the invention to impart increased structural integrity to the heat exchanger body 12, in particular to improve the mechanical stability of the heat exchanger body 12.
[0056] In addition, the support elements 32 of the support structure 26 have proven advantageous because they penetrate the interspace system. Basically, the support elements 32 are designed and arranged to generate turbulence in the fluid flowing in the interspace system 24, namely in the process fluid FS3; in any case, to mix this fluid and / or to project it onto the opposing wall surfaces 28', 30" of the walls 28, 30, thereby increasing or improving heat transfer during heat exchanger operation. The support elements 32 are arranged at a predetermined distance from one another. Preferably, the distance between two support elements 32 corresponds approximately to the largest passage width DWimax of the first and second channel systems 20, 22.
[0057] As FIG. 2 further illustrates, the passage width DW2 of the intermediate space system 24 is essentially constant. It can vary within a range of + / - 10 to 15% relative to the average passage width DW2. The passage width of the first and second channel systems 20, 22 varies within a range from DWimin to DWimax, with the maximum first passage width DWimax corresponding to approximately three times the minimum first passage width DWimin. The passage width DW2 corresponds approximately to one-third of the average passage width DWi.
[0058] In a preferred embodiment, the support elements 32 are designed as support struts 32'. The support elements 32 designed as support struts 32' preferably have an approximately constant cross-section in the direction of extension. Furthermore, the support elements 32 extend substantially transversely, in particular perpendicularly, to a respective adjacent region of the wall surfaces 28", 30' of the walls 28, 30.
[0059] According to a preferred embodiment, as can also be seen from FIG. 2, the first and second channel systems 20, 22 have, on their wall surfaces 28', 30" which delimit the passage width DWi, a plurality of depressions 34 which enlarge the surface of the walls 28, 30; ie the first and second channel systems 20, 22 have walls 28, 30 which delimit their passage width DWi, the wall surfaces 28', 30" of which comprise a plurality of depressions 34 which enlarge the surface of the walls 28, 30, in particular the surface of the wall surfaces 28', 30".
[0060] Such depressions 34 are preferably formed as material recesses on the wall surfaces 28', 30" of the walls 28, 30 and have a preferably circular configuration with a concavely curved surface 35. The depressions 34 form a golf ball structure on the corresponding wall surface 28', 30". This configuration has the advantage of improving heat transfer because the depressions increase the heat transfer surface.
[0061] FIG. 3 shows a first embodiment of a device 10 according to the invention for guiding and transferring heat between at least two fluid streams FSI,2,3, in particular three separately guided fluid streams FSI,2,3. The device 10 comprises a heat exchanger body 12 with the gyroidal structure 14 according to the invention, described in more detail in FIGS. 1 and 2. The device 10 comprises three fluid inlets 36, 36', 36" and three fluid outlets 38, 38', 38" for the three fluid streams FSI,2,3 guided through the heat exchanger body 12.
[0062] The heat exchanger body 12 has the shape of a cuboid, which in the embodiment shown here has square end faces 40, 40' and four equally sized side faces 42, 42'. The side faces 42, 42' of the heat exchanger body 12 are sealed by side walls 44, 44'. The fluid flows FSI,2,3 are directed into and out of the heat exchanger body 12 via the end faces 40, 40'. The respective fluid inlets and outlets 36-38" are fluidically connected only to certain areas of the end faces 40, 40', which lead to the corresponding channel systems 20, 22 or the intermediate space system 24. Areas on the end faces 40, 40' of the heat exchanger body 12 that are not exposed to the fluid flow FSI, 2, 3 adjacent thereto are then designed to be closed. Only the channel system or intermediate space system that is actually intended to communicate with the corresponding fluid inlet or fluid outlet 36-38" is designed to be open.
[0063] In the embodiment shown in FIG. 3, the fluid streams FS 1, 2, 3 are guided in countercurrent to each other.
[0064] In particular, the process fluid FS3 is introduced into the heat exchanger body 12 via the central fluid inlet 36 from the lower end face 40', and the heat exchange fluid FSI,2 is introduced into the heat exchanger body 12 via the fluid inlets 36', 36" from the upper end face 40. The fluid streams introduced via the fluid inlets 36', 36" are formed by one and the same fluid in the present case. However, different fluids could also be used to cool the upwardly directed process fluid FS3 via the fluid inlets 36', 36".
[0065] In particular, the fluid inlet 36 and the fluid outlet 38 are fluidly coupled to the intermediate space system 24, in this case for guiding the process fluid FS3. The outer fluid inlets and outlets 36', 36", 38', 38" are each fluidly connected to the first and second channel systems 20, 22, in this case for guiding the heat exchange fluid FSI,2. FIG. 4 shows a further embodiment of a device 10' according to the invention for guiding and transferring heat between three fluid streams FSI,2,3. The device 10' also comprises a heat exchanger body 12, which comprises a gyroidal structure 14 designed according to the invention.
[0066] In contrast to the previous embodiment, the end faces 40, 40' of the heat exchanger body 12 are fluidly connected to only two fluid inlets 36', 36" and two fluid outlets 38', 38", in this case for guiding the heat exchange fluid FSI,2. In the present embodiment, the fluid inlet 36 and the fluid outlet 38 for the third fluid flow FS3 are formed on the side walls 44' and are thus assigned to two opposite side faces 42' of the heat exchanger body 12. In particular, the fluid inlet and the fluid outlet 36, 38 are fluidly connected to the intermediate space system 24 for guiding the fluid flow FS3, in this case for guiding the process fluid FS3.
[0067] The side surfaces 42' adjacent to the inlet and outlet 36, 38 are sealed by side walls 44.
[0068] In this embodiment, too, the respective inlets and outlets 36-38" are fluidically connected to the respective assigned surface areas of the heat exchanger body 12, so that the fluid flows FSI,2,3 only flow into the respective channels 20, 22 or spaces 24 provided for them.
[0069] The fluid flow FS3 flowing into the heat exchanger body 12 via the fluid inlet 36 and the fluid outlet 38 is guided through the interspace system 24 of the heat exchanger body 12. The fluid flows FS1, FS2, in this case the heat exchange fluid, which are guided through the heat exchanger body 12 via the fluid inlets 36', 36" and the fluid outlets 38', 38", are guided through the heat exchanger body 12 via the first and second channel systems 20, 22.
[0070] The fluid streams FSI,2 flow countercurrently to one another. The fluid stream FS3 flows approximately at a right angle to the fluid streams FS1,2 in crossflow. The heat exchanger body 12 used in the device 10, 10' is particularly designed to be produced by means of an additive manufacturing process, such as a 3D printing process. FIG. 5 shows an electrochemical system 50 comprising a fuel cell or an electrolyzer 52 and a device 10, 10' for conducting and transferring heat between at least two fluid streams FSI,2,3, which is designed according to at least one of the embodiments described above. The fuel cell or the electrolyzer 52 can be fluidly coupled to the device 10, 10' via a fluid line 54, in this case designed as a closed ring line.In the fluid line 54, the process fluid flows in the form of the fluid stream FS3, which is to be brought to a required temperature within the device 10, 10' before it is fed again to the fuel cell or the electrolyzer 52.
[0071] At least one heat exchange fluid in the form of the fluid flow FSI,2 is also supplied to and discharged from the device 10, 10' via fluid lines 56, 56', by means of which the process fluid (FS3) is brought to the required temperature level, preferably cooled. The distribution of the heat exchange fluid (FSI,2) supplied and discharged via lines 56, 56' to the fluid inlets 36', 36", 38', 38" shown in more detail in Figures 3 and 4 takes place at the device 10, 10' itself.
[0072] LIST OF REFERENCE SYMBOLS
[0073] 10, 10' device
[0074] 12 heat exchanger bodies
[0075] 14 gyroidal structure
[0076] 14' nested gyroid
[0077] 16 main gyroid
[0078] 18 secondary gyroid
[0079] 20 first canal system
[0080] 22 second canal system
[0081] 24 Intermediate space system
[0082] 26 Support structure
[0083] 28, 30 wall
[0084] 28', 28" wall surface
[0085] 30', 30" wall area
[0086] 32 Support element
[0087] 32' support struts
[0088] 34 Deepening
[0089] 35 curved surface
[0090] 36, 36', 36" fluid inlet
[0091] 38, 38', 38" fluid outlet
[0092] 40, 40' frontal area
[0093] 42, 42' side surface
[0094] 44, 44' side wall
[0095] 50 electrochemical system
[0096] 52 Fuel cell / electrolyzer
[0097] 54 ring line
[0098] 56, 56' fluid line
[0099] DW i Durchl as sweite
[0100] DW2 passage width
[0101] FSi first fluid stream, in particular heat exchange fluid
[0102] FS2 second fluid stream, in particular heat exchange fluid
[0103] FS3 third fluid stream, especially process fluid
Claims
CLAIMS 1. Device (10, 10') for guiding at least two fluid flows (FS1.2, 3), in particular a process fluid (FS3) and a heat exchange fluid (FS ), with a heat exchanger body (12), wherein the heat exchanger body (12) has a gyroidal structure (14) with a main gyroid (16) and a secondary gyroid (18) for intersection in the form of a nested gyroid (14') to form at least a first and second channel system (20, 22), wherein the first and second channel system (20, 22) each have a first passage width (DWi), and to form an intermediate space system (24), wherein the intermediate space system (24) has a second passage width (DW2), wherein the first and second channel system (20, 22) are spatially separated from the intermediate space system (24), wherein the intermediate space system (24) has a support structure (26) which penetrates the intermediate space system (24).
2. Device according to claim 1, characterized in that the intermediate space system (24) is limited in its passage width (DW2) by walls (28, 30) and the intermediate space system (24) is separated from the first and second channel system (20, 22).
3. Device according to claim 2, characterized in that at least one of the walls (28, 30) is common to the intermediate space system (24) and the first or second channel system (20, 22), preferably designed for heat transfer between the at least two fluid flows (FS1.2,3), in particular the process fluid (FS3) and the heat exchange fluid (FS ).
4. Device according to claim 2 or 3, characterized in that the first and second channel systems (20, 22) are separated from one another by walls (28, 30) which are formed by means of the walls (28, 30) delimiting the intermediate space system (24), in particular wherein a first wall (28) is common to the intermediate space system (24) and the first channel system (20) and a second wall (30) is common to the intermediate space system (24) and the second channel system (22).
5. Device according to one of claims 1 to 4, characterized in that the second passage width (DW2) of the intermediate space system (24) is smaller than the first passage width (DWi), in particular wherein the first passage width (DWi) of the first and second channel systems (20, 22) is different from one another or is the same.
6. Device according to one of claims 1 to 5, characterized in that the support structure (26) has a plurality of support elements (32) which extend between wall surfaces (28", 30') of walls (28, 30) delimiting the intermediate space system (24) and connect the walls (28, 30) to one another.
7. Device according to claim 6, characterized in that the support elements (32) are designed as support struts (32') with a cross-section that remains constant in the direction of extension.
8. Device according to claim 6 or 7, characterized in that the support elements (32) extend substantially transversely, in particular perpendicularly, to the respectively adjacent wall surface (28", 30') of the wall (28, 30).
9. Device according to one of claims 1 to 8, characterized in that the first and second channel systems (20, 22) have walls (28, 30) which limit their passage width (DWi), the wall surfaces (28', 30") of which comprise a plurality of depressions (34) which enlarge the surface of the walls (28, 30), in particular the surface of the wall surfaces (28', 30").
10. Device according to claim 9, characterized in that the depressions (34) are designed as material recesses which have a preferably circular configuration on the wall surface (28', 30") with a concavely curved surface (35).
11. Device according to one of claims 1 to 10, characterized by at least two fluid inlets and fluid outlets (36-36", 38-38") assigned to the heat exchanger body (12), wherein the two fluid streams (FS 1,2,3), preferably the process fluid (FS3) and the heat exchange fluid (FS ), are conducted in countercurrent.
12. Device according to one of claims 1 to 11, with three fluid inlets and fluid outlets (36-36", 38-38") assigned to the heat exchanger body (12), wherein preferably the heat exchange fluid in the first and second channel system (20, 22) is guided in countercurrent to each other and the process fluid in the intermediate space system (24) is guided in crosscurrent to the heat exchange fluid.
13. Electrochemical system (50) comprising a fuel cell or an electrolyzer (52) and at least one device (10, 10') according to one of the preceding claims 1 to 12, for guiding at least two fluid streams (FS 1, 2, 3).
14. A method for producing a device (10, 10') according to one of claims 1 to 12 with a heat exchanger body (12), wherein the heat exchanger body (12) is produced using an additive manufacturing process.