A heat exchanger including fluid tubes with first and second inner walls

Abstract

A heat exchanger includes at least one fluid tube comprising: a first tube section and a second tube section extending along the fluid tube, each tube section being in fluid communication with a pair of manifolds; the first tube section being formed by a first wall, a second wall, a first outer wall, and a first inner wall; the second tube section being formed by a first wall, a second wall, a second outer wall, and a second inner wall; the heat exchanger is configured to guide cooling fluid in the first tube section along a first direction and in the second tube section along a second direction opposite to the first direction; the cooling fluid is guided through the second tube section before entering the first tube section; the first tube section is arranged upstream of the second tube section with respect to airflow direction; the first inner wall and the second inner wall are separated by at least one common area defined by the first inner wall and the second inner wall, the first inner wall and the second inner wall being arranged at a distance from each other; the at least one common area is arranged between the first tube section and the second tube section, the common area including at least one groove.

Description

[0001] This application is a divisional application of the application filed on July 13, 2018, with application number 201880044469.1 and invention title "Heat Exchanger including Fluid Tubes with First and Second Inner Walls". Technical Field

[0002] The present invention relates to a heat exchanger comprising at least one fluid tube configured to extend substantially orthogonally to the wind direction, the fluid tube having a first wall and a second wall, and the fluid tube comprising a first tube section and a second tube section extending along the fluid tube, respectively, arranged such that each tube section is in fluid communication with a pair of manifolds and configured to contain cooling fluid. Background Technology

[0003] Heat exchangers are typically used to lower the operating temperature of engines, generators, and other heat-generating equipment by providing cooled cooling fluid. Heat exchangers are generally classified into two categories: active heat exchangers and passive heat exchangers.

[0004] In fields such as wind turbines, passive heat exchangers are often the preferred choice due to their lower cost and greater functionality. Passive heat exchangers utilize wind—such as the wind flowing around the nacelle of a wind turbine—to cool the cooling fluid, which is guided through multiple fluid pipes to lower its temperature. Once the cooling fluid has cooled, it is then directed back to the heat-generating equipment for further cooling.

[0005] To achieve optimal cooling, large passive heat exchangers are typically required, featuring numerous fluid pipes that define a large cooling area for receiving cooling air. However, the available space in the nacelle under discussion is limited. Furthermore, the relatively high weight of a large heat exchanger can present numerous structural and manufacturing challenges.

[0006] Therefore, traditional heat exchangers have shown that they cannot provide solutions that allow for more efficient cooling and more compact designs. Summary of the Invention

[0007] One object of the present invention is to overcome, in whole or in part, the aforementioned drawbacks and disadvantages of the prior art. More specifically, one object is to provide an improved heat exchanger that provides more efficient cooling.

[0008] The solution according to the invention achieves the above-mentioned objectives, as well as many other objectives, advantages, and features that will become apparent from the following description, by means of a heat exchanger comprising at least one fluid tube configured to extend substantially orthogonally to the wind direction, the fluid tube having a first wall and a second wall, and the fluid tube comprising:

[0009] - A first pipe section and a second pipe section, each extending along a fluid conduit, are arranged such that each pipe section is in fluid communication with a pair of manifolds and is configured to contain cooling fluid.

[0010] The heat exchanger comprises a first pipe section formed by a first wall, a second wall, a first outer wall, and a first inner wall, and a second pipe section formed by a first wall, a second wall, a second outer wall, and a second inner wall. The first inner wall, second inner wall, first outer wall, and second outer wall extend substantially parallel to the fluid pipe and are in fluid-sealed contact with the first and second walls. The heat exchanger is configured to guide cooling fluid in a first direction in the first pipe section and in a second direction in the second pipe section, the first direction being opposite to the second direction. The cooling fluid is guided through the second pipe section before entering the first pipe section, and the first pipe section is arranged upstream of the second pipe section with respect to the airflow direction. Therefore, with the same number of pipes and / or cooling area, the cooling fluid is subjected to more cooling air, thus significantly improving the cooling efficiency of the heat exchanger. Thus, a more efficient heat exchanger can be achieved without increasing the size or number of fluid pipes. Moreover, the cooling air flowing along the airflow direction first cools the cooling fluid with the lowest temperature, which significantly improves the cooling efficiency of the heat exchanger.

[0011] The first and second inner walls are separated by at least one common area defined by the first and second inner walls, which are arranged at a certain distance from each other. The at least one common area is arranged between the first and second pipe sections, and includes at least one slot. Thus, the cooling air entering the heat exchanger is further permitted to pass through the slot, resulting in additional cooling effects and improved cooling efficiency. Furthermore, the slot prevents heat transfer between pipe sections, ensuring a greater temperature difference between them. Therefore, the coldest air is guided to cool the cooling fluid with the lowest temperature. In this way, counterflow is generated, thus achieving more efficient cooling.

[0012] The distance can be between 1 mm and 25 mm, more preferably between 2 mm and 15 mm, and even more preferably between 3 mm and 10 mm.

[0013] Furthermore, the width of the groove can be from 0.1 mm to 20 mm, or more preferably from 0.5 mm to 10 mm, or most preferably from 1.25 mm to 5 mm. In this way, the air gap provided by the groove is sufficient to prevent heat transfer in the tube material.

[0014] In addition, the first wall of both the first pipe section and the second pipe section can be made of a single metal plate.

[0015] Similarly, the second wall of both the first and second pipe sections can be made of a single metal plate.

[0016] In addition, the wall, as well as the inner and outer walls, can be made from a single sheet of metal.

[0017] Furthermore, the first and second outer walls can be formed by a pair of sidewalls of the fluid tube. Since multiple inner walls are not required, this makes the heat exchanger more cost-effective.

[0018] Furthermore, the second outer wall may partially form the inner wall of another pipe section. Alternatively, the first outer wall may partially form the inner wall of an additional pipe section.

[0019] Additionally, the at least one groove can be an elongated groove extending along the longitudinal axis of the fluid tube. Taking advantage of this, the longitudinal axis can be a centerline extending along the length of the fluid tube.

[0020] Furthermore, the at least one fluid tube may be a flat fluid tube.

[0021] Furthermore, each public area may include multiple slots.

[0022] Additionally, a turbulence generator can be installed inside the pipe section. This generator creates turbulence in the cooling fluid flowing through the pipe section. Since turbulence increases the heat exchange capacity between the cooling fluid and the inner wall of the pipe section, this further improves the cooling efficiency of the heat exchanger.

[0023] The turbulence diffuser can be formed by indentations / dimples arranged on the first and / or second walls of the fluid tube. This allows turbulence without introducing any additional components into the heat exchanger, making the manufacturing and assembly process faster, simpler, and more cost-effective.

[0024] The turbulence diffuser can be formed by a turbulence diffuser insert disposed inside the pipe section. Therefore, turbulence can be achieved in a simple and cost-effective manner inside the pipe section by simply arranging the tubular insert above one wall of the fluid pipe during assembly.

[0025] A heat exchanger may include multiple heat sinks, which may be through-type heat sinks / plates, that is, heat sinks that extend from the front end of the heat exchanger to the back end when viewed in the direction of the wind.

[0026] Therefore, the heat exchanger may include multiple fluid tubes and a thin plate, the thin plate being arranged between at least some of the fluid tubes to extend substantially throughout the heat exchanger in the direction of airflow. In this way, improved airflow guidance is achieved, and thus improved cooling. A fin / plate may be attached to the wall of the first or second tube. The fin / plate may be attached to the walls of both the first and second tubes. This allows for control of the heat distribution within the fin / plate.

[0027] Furthermore, the first and second inner walls can be formed from a pair of slender rods.

[0028] Furthermore, the first inner wall may include a pair of first diverging sections, and the second inner wall may include a corresponding pair of second diverging sections, wherein the first diverging sections extend toward the first outer wall, and the second diverging sections extend toward the second outer wall, wherein the first diverging sections and the corresponding second diverging sections are arranged opposite each other to form a common area.

[0029] Additionally, the inner wall may each have a first end and a second end, wherein the sides of the first and second ends of the first pipe section contact the corresponding sides of the first and second ends of the second pipe section. This reduces the risk of any leakage at the connection point between the manifold and the fluid pipe.

[0030] Furthermore, the joints formed on the sides can be sealed with sealant, which reduces the risk of leakage between pipe sections. The sealant can be an adhesive, liquid sealant, or adhesive gasket.

[0031] The connection points / joints can also be welded, for example, by means of laser welding.

[0032] Advantageously, the sealant can be solder paste. This allows for a less complex manufacturing process and also allows for the formation of pipe sections by punching grooves and welding the pipe sections together.

[0033] The first wall and / or the second wall may include at least one protruding element projecting from the first or second wall, wherein the protruding element is configured to retain the first inner wall and the second inner wall to form a common area. The protruding element guides the inner wall during assembly to achieve a straight orientation of the inner wall along the longitudinal axis of the fluid tube, and the protruding element ensures the realization and retention of the common area, thereby enabling a more robust and efficient assembly of the heat exchanger.

[0034] Advantageously, the fluid conduit may include multiple slots and protruding elements along the longitudinal axis of the fluid conduit, wherein the protruding elements are arranged between slots in the first wall and / or slots in the second wall. This allows more air to enter and circulate in the common area between the fluid conduits, which further reduces heat transfer through each wall and thus increases the overall cooling efficiency of the heat exchanger.

[0035] The fluid tubes and inner walls can be made of aluminum, which allows for more efficient heat exchangers due to aluminum's favorable heat transfer properties. Furthermore, aluminum is relatively lighter than steel, allowing for lighter heat exchangers that are easier to install onto heating equipment.

[0036] In addition, the fluid conduit may be configured to extend in a vertical direction, wherein a pair of manifolds includes a first manifold and a second manifold.

[0037] Additionally, at least one end of the first wall and / or the second wall may include a recess configured to receive the first or second end of the inner wall, thereby holding the first or second end in direct contact within the recess. This allows for ensuring a tight seal between the inner walls in a simple and cost-effective manner.

[0038] In addition, the area of ​​the trough can be more than 50% of the public area.

[0039] Furthermore, the length of the groove, or the combined length of the groove along the longitudinal axis of the tube, can be greater than 50%, or greater than 60%, or more preferably greater than 70% of the common area. In this way, heat transfer from one tube to another is effectively prevented.

[0040] The fluid tube can be a flat tube with a substantially rectangular cross-section when viewed perpendicular to the direction of fluid flow. The inner wall can be substantially perpendicular to the sides of the fluid tube.

[0041] In addition, the outer wall can be formed by a pair of slender rods.

[0042] The heat exchanger can be a slat heat exchanger.

[0043] Furthermore, the heat exchanger can be a block heat exchanger.

[0044] Furthermore, the inner walls can be interconnected by means of a common area, which is formed by imprinting a first wall and / or an imprinting a second wall to form the inner walls and the common area.

[0045] The fluid tube may have a first end and a second end, wherein the inner walls are joined at the ends of the fluid tube, and each end extends into a manifold. In this way, no additional parts are needed to achieve a sealing contact between the inner walls of the tubes, and this makes the manufacture and assembly of the heat exchanger more cost-effective.

[0046] Finally, the first inner wall and the second inner wall can be formed by compressing the first wall and the second wall.

[0047] The present invention also relates to a wind turbine comprising a heat exchanger as described above. Attached Figure Description

[0048] The invention and its many advantages will now be described in more detail with reference to the accompanying drawings, which illustrate some non-limiting embodiments for illustrative purposes, wherein:

[0049] Figure 1 A perspective view of a heat exchanger according to one embodiment is shown.

[0050] Figure 2A schematic diagram of the fluid and cooling airflow through a heat exchanger according to one embodiment is shown.

[0051] Figure 3 A cross-sectional view of the fluid tubes of a heat exchanger according to one embodiment is shown.

[0052] Figure 4 A cross-sectional view of the fluid tubes of a heat exchanger according to one embodiment is shown.

[0053] Figure 5a -c shows a cross-sectional view of the fluid pipes of a heat exchanger according to one embodiment.

[0054] Figure 6 A cross-sectional view of the fluid tubes of a heat exchanger according to one embodiment is shown.

[0055] Figure 7 A cross-sectional view of the fluid tubes of a heat exchanger according to one embodiment is shown.

[0056] Figure 8a A perspective view of a stack of fluid tubes having thin plates / heat sinks arranged between fluid tubes, according to an embodiment of the present invention, is shown.

[0057] Figure 8b A cross-sectional view (end view) of a stack of fluid tubes with thin plates / heat sinks arranged between the fluid tubes is shown.

[0058] Figure 8c A perspective view of a single plate for a fluid conduit is shown according to one embodiment, and

[0059] Figures 9a-9e Another embodiment of the fluid tube is shown. Detailed Implementation

[0060] All accompanying drawings are highly schematic and not necessarily drawn to scale, and they only show those parts necessary to illustrate the invention, while omitting or only implying other parts.

[0061] Figure 1 A perspective view of a heat exchanger (i.e., a radiator) is shown, which can be configured to be mounted, for example, on a wind turbine nacelle. The heat exchanger 1 includes a pair of manifolds 9, 10 connected by at least one, but preferably multiple, fluid pipes 2 extending between the manifolds 9, 10. The multiple fluid pipes 2 define a cooling zone configured orthogonal to the wind direction WD, allowing air to flow between the fluid pipes through the heat exchanger 1 to cool the cooling fluid within the fluid pipes 2.

[0062] Advantageously, the fluid pipe 2 can be a flat fluid pipe. Therefore, the plurality of fluid pipes 2 forming the cooling zone of the heat exchanger 1 can be flat fluid pipes, wherein the heat exchanger 1 can be a flat fluid pipe heat exchanger.

[0063] The fluid tube includes a first wall 5 and a second wall 6, which are joined together by means of a first outer wall 7 and a second outer wall 8 to form a substantially rectangular cross-section.

[0064] like Figure 1 As shown, the first outer wall 7 and the second outer wall 8 can be formed by a pair of sidewalls of the fluid pipe 2. The first outer wall 7 and the second outer wall 8 can be formed by a pair of elongated bars, while the first wall 5 and the second wall 6 can be formed by a pair of plates.

[0065] Preferably, each fluid tube of the heat exchanger 1 can be formed by the pair of plates and bars, thus the heat exchanger 1 can be a plate-and-bar heat exchanger.

[0066] refer to Figure 1 The heat exchanger 1 can be an upper and lower heat exchanger, or in other words, a heat exchanger 1 in which the fluid pipe 2 is configured to extend in a vertical direction, wherein a pair of manifolds 9, 10 includes a first manifold 9 and a second manifold 10.

[0067] Refer again Figure 1 The fluid pipe 2 has a first end 21 and a second end 22, each extending into one of the pair of manifolds 9, 10. Therefore, the heat exchanger 1 may include a plurality of fluid pipes 2, each having a first end 21 and a second end 22, each extending into one of the pair of manifolds.

[0068] Furthermore, the heat exchanger 1 may include heat sinks 81 configured to optimize airflow through the heat exchanger 1. The heat sinks 81 may be through-flow fins, i.e., thin plates extending from the front to the rear of the heat exchanger along the airflow direction. Advantageously, the heat sinks 81 extend from the frontmost to the rearmost part of the heat exchanger along the airflow direction. Therefore, the heat exchanger 1 may include a plurality of fluid pipes 2 and heat sinks 81 in the form of thin plates, which are arranged between at least some of the flat tubes in the fluid pipes 2, thereby extending substantially along the entire length of the heat exchanger 1 in the airflow direction.

[0069] Preferably, the heat exchanger 1 includes a plurality of fluid pipes, wherein heat sinks / plates can be connected to the walls of either the first or second fluid pipe. Alternatively, the heat sinks / plates can be connected to the walls of both the first and second fluid pipes. Therefore, control of the heat distribution within the heat sinks / plates is possible.

[0070] Now refer to Figure 2To further improve cooling efficiency, the heat exchanger can be configured to guide cooling fluid in a first pipe section along a first direction and in a second pipe section along a second direction, the first direction being opposite to the second direction. The cooling fluid is guided through the second pipe section before entering the first pipe section, and the first pipe section is arranged in front of the second pipe section in the windward direction (as indicated by arrows and WD). In other words, the first pipe section is arranged in front of the second pipe section to receive cooling air moving in the windward direction before the second pipe section.

[0071] This allows the cooling fluid with the lowest temperature—that is, the cooling fluid already cooled in the second pipe section—to be cooled by the coldest air (that is, the cooling air that first enters heat exchanger 1). In terms of cooling efficiency, this has proven to be very advantageous because it effectively reduces the lowest temperature reached in the heat exchanger.

[0072] As those skilled in the art will recognize, guiding the cooling fluid through a second pipe section and then through a first pipe section can be done in a variety of ways. For example, the manifold may include an inner well section constructed to prevent the cooling fluid from passing through / flowing through the manifold and instead guide it through the fluid pipe. This can also be achieved by means of a pressure difference between the manifolds, which simply forces the cooling fluid to flow along the desired flow path.

[0073] Further reference Figure 2 The heat exchanger manifolds 9 and 10 may include a cooling fluid inlet 98 and a cooling fluid outlet 99, each of which is connected to the cooling system of the heat-generating device. Thus, cooling fluid is introduced into the heat exchanger 1 via the inlet in one of the manifolds, and after being cooled within the heat exchanger, it is guided back to the heat-generating device via the outlet in one of the manifolds. The first manifold 9 may include an inlet 98 and an outlet 99. The first manifold 9 is divided into two separate compartments by a partition wall 110 extending along the length of the first manifold 9. Thus, the inlet 98 is in fluid communication with one compartment of the first manifold 9, and the outlet 99 is in fluid communication with the other compartment of the first manifold 9. Therefore, cooling fluid is allowed to move from the inlet 98 to the outlet 99 via the fluid pipe and the second manifold 10 in the advantageous manner described above.

[0074] The above measures achieve a highly efficient rear-to-front counter-flow heat exchanger. However, a problem with this type of heat exchanger is that its cooling efficiency is highly dependent on the temperature difference between the rear and front sections of the heat exchanger, making it very susceptible to any increase in the temperature of the lowest cooling fluid in the front section of the heat exchanger. (Reference) Figure 3 The arrangement structure used to mitigate this drawback will be described.

[0075] Reference Figure 3 The diagram shows a cross-section along the length of fluid pipe 2. Therefore, Figure 2The second wall 6 is shown as the bottom surface. As shown, the heat exchanger includes at least one fluid tube configured to extend substantially orthogonally to the wind direction, wherein the fluid tube has a first wall 5 (in... Figure 1 (shown in the image) and second wall 6. The fluid conduit 2 includes a first pipe section 18 and a second pipe section 19 extending along the fluid conduit, each in fluid communication with a pair of manifolds 9, 10 and configured to contain cooling fluid. The first pipe section 18 is formed by a first wall, i.e., a first thin plate (not visible), a second wall 6, a first outer wall 7, and a first inner wall 11, while the second pipe section is formed by a first wall 5, a second wall 6, a second outer wall 8, and a second inner wall 12. The first outer wall 7 and the second outer wall 8 extend substantially parallel to the fluid conduit and are in fluid-tight contact with the first wall (not visible) and the second wall 6.

[0076] Therefore, the first pipe section 18 and the second pipe section 19 each form a fluid-impermeable compartment extending along the entire length of the fluid pipe inside the fluid pipe. Thus, all the cooling fluid flowing through the fluid pipe can flow through both the first pipe section 18 and the second pipe section 19.

[0077] This allows for more efficient cooling because the cooling fluid flowing through fluid pipe 2 encounters more cooling air along its path through the heat exchanger, as the flow path of the cooling fluid through the heat exchanger is lengthened. Therefore, more efficient cooling can be achieved with the same external proportions of the heat exchanger. Furthermore, dividing the cooling fluid by simply inserting an additional inner wall allows for improved cooling efficiency in a simple and relatively inexpensive manner.

[0078] The fluid tube 2 or more fluid tubes and the inner walls 11, 12 are preferably made of aluminum. This is particularly advantageous due to its excellent heat transfer properties, and furthermore, it allows for a lighter heat exchanger due to the material's light weight.

[0079] The first inner wall 11 and the second inner wall 12 are separated by at least one common area 30 defined by the first inner wall 11 and the second inner wall 12, thereby arranging the first inner wall 11 and the second inner wall 12 at a distance d from each other, wherein the at least one common area is arranged inside the fluid pipe 2 and includes at least one groove 31. This allows air to enter through the fluid pipe 2 through the groove 31, thereby further improving cooling efficiency because the surface area of ​​the pipe receiving the cooling air is increased. Therefore, the groove 31 is configured to guide cooling air through the fluid pipe 2.

[0080] Furthermore, the groove 31 may be an elongated recess extending along a longitudinal axis C, which extends along the length of the fluid tube 2. The longitudinal axis is preferably a centerline.

[0081] like Figure 3 As shown, the distance d can vary across the longitudinal axis C, thus the width of the common area 30 can be of any shape.

[0082] Furthermore, and most importantly, the slot 31 provides insulation that prevents heat transfer between pipe sections and thus ensures a temperature difference between them. Therefore, as the cooling fluid circulates through the fluid pipe compartment, the temperature of the cooling fluid in the first pipe section remains lower, making cooling more efficient. Thus, the slot provides a solution to the aforementioned problem of providing and maintaining a temperature difference across the heat exchanger, because the hotter cooling fluid inside the second pipe section, and therefore the hotter walls of that pipe section, does not affect the temperature of the cooling fluid in the first pipe section via the walls of the first pipe section. This method has proven to be very effective, improving cooling efficiency by approximately 2-10%.

[0083] Furthermore, the arrangement of fluid compartments with grooves allows for a simpler solution for achieving an effective counter-current heat exchanger that is less expensive to manufacture and more compact, as it eliminates the need for additional fluid piping to achieve the desired counter-current effect. Instead, counter-current flow can be provided within each fluid pipe.

[0084] The width of the groove can be from 0.1 mm to 20 mm, more preferably from 0.5 mm to 10 mm, or most preferably from 1.25 mm to 5 mm. In this way, the air gap provided by the groove is sufficient to prevent heat transfer in the tube material.

[0085] Further reference Figure 3 The first inner wall 11 includes a pair of first diverging segments 73, and the second inner wall 12 includes a corresponding pair of second diverging segments 74, wherein the first diverging segments 73 extend toward the first outer wall 7, and the second diverging segments 74 extend toward the second outer wall 8, thereby arranging the first diverging segments 73 and the corresponding second diverging segments 74 opposite each other to form a common area 30. Thus, these diverging segments form a wider section of the common area, with a maximum distance d between the first and second curved sections, in which the slots 31 can be arranged. Therefore, a slot arrangement structure that allows for more efficient cooling can be provided in a space-saving manner, because the first inner wall 11 and the second inner wall 12 can be arranged very close to each other while still providing the common area and the slots, thus achieving a more compact cooling arrangement structure. Each common area 30 may include multiple slots 31.

[0086] like Figure 3 As shown, the first inner wall 11 and the second inner wall 12 can be formed by a pair of elongated rods. Therefore, the inner walls 11, 12 and the outer walls 7, 8 can be formed by rods, thereby the first wall and the second wall can be formed by plates.

[0087] It is worth noting that the pair of first diverging segments 73 and the pair of second diverging segments 74 may be curved portions of the elongated bars forming the first inner wall 11 and the second inner wall 12. Therefore, the elongated bars forming the inner walls 11, 12 extend along the longitudinal axis C, with a portion of them bent to form the common area 30.

[0088] The pair of first diverging sections 73 define a first intermediate portion 13 of the first inner wall 11, which extends substantially along the longitudinal axis C of the fluid tube. Similarly, the pair of second diverging sections 74 define a second intermediate portion 14 of the second inner wall 12, which also extends substantially along the longitudinal axis C of the fluid tube. The intermediate portions are preferably arranged to be spaced apart from each other by a distance d.

[0089] In one embodiment, the length of the groove 31, or the combined length of the grooves along the length of the fluid pipe, is more than 50% or 60% of the common area, or more preferably more than 70%. In this way, heat transfer from one fluid pipe to another is effectively stopped.

[0090] The distance d can therefore be between 1 mm and 25 mm, more preferably between 2 mm and 15 mm, and even more preferably between 3 mm and 10 mm. However, as mentioned earlier, it can vary along the length of the fluid tube.

[0091] Reference Figure 3 To achieve a seal between the inner walls, the inner walls can be joined at the first and second ends of the fluid tube, allowing both ends to extend into the manifold. Therefore, there is no need for another portion to seal the gap between the tubes, making the manufacturing process more cost-effective.

[0092] This is achieved by means of the inner walls 11, 12 of the pipes, each having first ends 43, 44 and second ends 41, 42, whereby the sides 63, 61 of the first ends 43 and 41 of the first pipe section 18 contact the corresponding sides 62, 64 of the first ends 44 and 42 of the second pipe section 19. Therefore, the risk of leakage at the connection between the fluid pipe and the manifolds 9, 10 is reduced. This sealing effect can be further improved by means of a sealant. Therefore, the joint formed by sides 61, 63 and sides 62, 64 can be sealed by means of a sealant. For example, the sealant can be an adhesive, a liquid sealant, or an adhesive gasket.

[0093] Sealant can also be solder paste. This makes the manufacturing process less complicated, as it allows pipe sections to be formed by punching grooves and welding them together.

[0094] Advantageously, the end of the fluid tube can extend into the manifold of the heat exchanger. Thus, the first and second ends can be made to contact directly only within their respective manifolds, thereby providing a seal without any risk of heat transfer between the inner walls 11, 12 due to direct contact.

[0095] In one embodiment, the aforementioned sides can be joined by welding (i.e., laser welding). Therefore, a simple and reliable seal can be achieved, while the joint is more robust compared to sides joined by, for example, brazing.

[0096] Furthermore, at least one end of the first wall 5 and / or the second wall 6 includes a recess 78 configured to receive a first end 43, 44 or a second end 41, 42 of the inner walls 11, 12 in a position where the first end 43, 44 or the second end 41, 42 is in direct contact within the recess 78. This allows for a tight seal between the inner walls in a simple and cost-effective manner. This is particularly advantageous when the first inner wall 11 and the second inner wall 12 are formed by a pair of elongated bars, as the recess serves to bend and retain the bars to achieve direct contact between them. Therefore, the installation of the heat exchanger is more efficient and simpler due to the bars being held in place by the recess.

[0097] In some embodiments, the heat exchanger may include a plurality of common regions 30, each common region 30 being formed by direct contact between a segment of a first inner wall 11 and a segment of a second inner wall 12; and a plurality of pairs of diverging segments 73, 74 configured to form the common regions 30. Preferably, the diverging segments are interconnected by intermediate segments extending straight along the longitudinal axis C of the fluid tube.

[0098] In other embodiments, the first inner wall 11 and the second wall 12 can be formed by extruding the first wall 5 and the second wall 6. Thus, the fluid tube may include two U-shaped profiles extruded together along the length of the fluid tube at their edges to form the first wall 5, the second wall 6, the first outer wall 7, and the second outer wall 8. Therefore, the common area 30 can be formed by punching along the center of the fluid tube, thereby forming the groove 31 by punching the resulting common area 30.

[0099] Figure 4A cross-section of the fluid tube is shown, with the inner wall and the first wall removed. Referring to the figure, the first wall (not shown) and / or the second wall 6 includes at least one protruding element 51 projecting from the first or second wall, wherein the protruding element 51 is configured to hold the first and second inner walls to form a common area. When the inner wall is on top of one of the walls 5 or 6, the protruding element 51 guides the inner wall along the longitudinal axis C of the fluid tube. This achieves a simple way to align the inner walls, thereby reducing the complexity of assembling the heat exchanger and thus lowering the overall production cost. Therefore, the protruding elements (multiple) are used to hold the inner walls in place, thereby ensuring, in a simple way, the common area is realized and maintained by means of the inner walls.

[0100] like Figure 4 As shown, the fluid conduit may include a plurality of grooves 31 and protruding elements 51, the grooves 31 and the protruding elements 51 extending along the longitudinal axis C of the fluid conduit, whereby the protruding elements 51 are arranged on the first wall 5 (in Figure 1 (shown in the diagram) and / or between the groove 31 of the second wall 6. This allows more cooling air to enter via the fluid pipe through the groove 31, thus achieving more efficient cooling. Furthermore, multiple protruding elements 51 allow for more stable mounting of the inner wall.

[0101] Go to Figure 5a -c, Baffles may be arranged inside pipe sections 18 and 19. As those skilled in the art will recognize, baffles are flow guiding elements configured to guide the flow of cooling fluid to generate turbulence. Because an adiabatic boundary layer does not exist in the contact between the cooling fluid and the wall of the fluid pipe when the cooling fluid is in a laminar flow mode, the turbulence achieved by the baffles allows for improved cooling efficiency. Conversely, the random motion of fluid molecules caused by the baffles disrupting the boundary layer increases the heat exchange capacity of the cooling fluid.

[0102] exist Figure 5a and Figure 5b The image shows a cross-section of the fluid pipe 2. In these embodiments, the flow disruptors arranged inside pipe sections 18 and 19 are formed by flow disruptor inserts 32. By placing the flow disruptor inserts within the fluid sections, a simple and cost-effective way to achieve turbulence within the fluid pipe is achieved.

[0103] Reference Figure 5cAn embodiment is shown in which the flow disruptor 24 arranged in the pipe section is a recess disposed on the first and / or second wall of the fluid pipe. The recess redirects the cooling fluid to achieve a turbulent cooling flow. This further makes it possible to imprint the recess onto the first and / or second wall 6. Imprinting the recess is a fairly cost-effective process, thereby achieving a more cost-effective way to achieve turbulence. In addition, the number of components in the heat exchanger is reduced, which makes the manufacturing process less complex and further reduces production costs.

[0104] Go to Figure 6 The second outer wall may be an additional inner wall 93 that partially forms another pipe section. A fluid pipe is shown, wherein a first pipe section 18 is formed by a first wall, a second wall, a first outer wall 7, and a first inner wall 11. A second pipe section 19 is formed by a first wall, a second wall, a second outer wall 93, and a second inner wall 12, wherein the first inner wall 11, the second inner wall 12, the first outer wall 7, and the second outer wall 93 are in fluid-sealed contact with the first and second walls and extend substantially parallel to the fluid pipe.

[0105] Therefore, the second outer wall 93 is another inner wall, which together with the outer wall 8 of the fluid pipe forms another pipe section 20. Furthermore, the second outer wall 93 can form another common area 30 together with another inner wall 94, which is provided with a groove 31, i.e. includes the groove 31. The flow of the cooling fluid is indicated by arrow FD. Thus, the heat exchanger is configured to guide the cooling fluid through the additional pipe section 20 via the second pipe section 19 and the manifold 10 to the manifold 9 and the first pipe section 18. The first pipe section 18 is preferably arranged ahead of the other pipe sections in the windward direction WD, i.e., the first pipe section is arranged to receive cooling air before the other pipe sections.

[0106] As will be readily apparent to those skilled in the art, the fluid conduit may include any number of inner walls forming separate sections extending along the fluid conduit. Furthermore, each of these sections may be separated by a common area provided with grooves.

[0107] Reference Figure 7 The ends 41, 42 of the inner walls 11, 12—which may be a pair of elongated bars forming the inner walls—can be connected by transverse bars 49. Preferably, the transverse bars 49 are joined to the inner walls 11, 12 by means of welding (i.e., laser welding).

[0108] Since bending is not required to provide sufficient sealing at the ends of the fluid tube and to allow for a common area for desired cooling, transverse bars allow for a less complex manufacturing process that is less affected by tolerances.

[0109] As shown in the figure, the flat tube can extend into the manifold. This is particularly advantageous because the inner walls 11, 12 are joined together. When the flat tube extends into the manifold, the second ends 41, 42 of the inner walls are arranged within the manifold. However, this problem is mitigated if the joined ends are arranged within a manifold where no heat exchange occurs, while achieving the desired seal between the tube sections.

[0110] It is obvious to a technician that both the first and second ends of the inner wall can be extended into the manifold by means of a flat tube extending into the manifold.

[0111] Turn Figure 8a -b shows a plurality of fluid pipes 2. These pipes, as flat tubes, are in fluid communication with a pair of manifolds. The fluid pipes 2 are separated by heat sinks 81 in the form of thin plates, which extend from the front to the rear of the heat exchanger in the windward direction WD. Therefore, the heat exchanger comprises a plurality of fluid pipes 2 and heat sinks 81 in the form of thin plates arranged between at least some of the fluid pipes 2 so as to extend substantially along the entire heat exchanger in the windward direction.

[0112] As shown in the accompanying drawings, the fluid pipes 2 can be separated and rest one on top of the other only by means of heat sinks 81 in the form of thin plates. Therefore, the fluid pipes 2 can be arranged in a block heat exchanger manner, wherein each fluid pipe is separated from the other by means of heat sinks 81 in the form of thin plates and gaskets. Thus, the heat exchanger can be a block heat exchanger.

[0113] The inner walls 11 and 12 are interconnected by means of a common area 30, which is formed by pressing a first wall 5 and / or a second wall 6 to form the inner walls 11 and 12 and the common area 30. As seen in the foregoing figures, the outer walls 7 and 8 can be formed by folding a joint that extends along the length of the fluid tube 2.

[0114] In the Figure 8a In -b, both the first wall 5 and the second wall 6 have been imprinted; however, it is obvious to a technician that the common area 30 and the first inner wall 11 and the second inner wall 12 can be achieved by imprinting either the first wall 5 or the second wall 6.

[0115] With this design, the entire fluid tube can be manufactured by folding and stamping a single metal sheet and then welding (i.e., laser welding) the remaining joint (i.e., one of the outer walls 7 and 8). This can also be achieved by separately stamping two separate metal sheets and independently stamping and welding them together along their length at the outer walls 7 and 8. As seen in the above figures, the outer walls 7 and 8 are formed by folding the joint extending along the length of the fluid tube 2.

[0116] These manufacturing techniques are more cost-effective compared to other conventional methods of constructing pipe sections. Furthermore, no additional bars are required to construct these sections. The absence of any solid bars makes the heat exchanger lighter and therefore easier to install on heat-generating equipment.

[0117] The heat exchanger can be a block heat exchanger, in which heat sinks 81 in the form of fins / plates are required to create a distance between the fluid tubes that allows cooling air to pass through the heat exchanger between the fluid tubes 2.

[0118] Reference Figure 8c The diagram shows a cross-section of the fluid tube. The fluid preferably extends into the manifold, with the end of the fluid tube thus extending into one of the manifolds.

[0119] To achieve a seal between the inner walls, the inner walls can be joined at the first and second ends 22 of the fluid tube, thereby allowing the first and second ends to extend into the manifold. Therefore, no additional components are needed to seal the gap between the tubes, making the manufacturing process more cost-effective.

[0120] This is achieved by arranging the groove 31 to extend all the way to the end of the fluid pipe, wherein the inner wall is directly joined by a common area 30.

[0121] exist Figure 9a Another embodiment of the fluid conduit is shown in the figure. In this embodiment, the common area is formed by embossing the first wall 5 and / or the second wall 6 to form the inner walls 11, 12 and the common area 30. At one end of the common area 30, a receiving section 66 is formed by embossing.

[0122] exist Figure 9b The receiving section 66 is shown in more detail. The receiving section is substantially square and has a first section side 67, a second section side 68, and a section end 69. The end opposite to the section end is open. The receiving section 66 is configured to receive a bar portion having an external geometry similar to the external geometry of the receiving section.

[0123] exist Figure 9c In the middle, the bar section 38 is arranged in the receiving section. Figure 9d The image shows an enlarged view, in which the bar portion 38 is arranged in the embossed receiving section. The construction and shape of the receiving section and the bar portion 38 facilitate sealing of this area, thereby substantially preventing leakage between the first pipe section and the second pipe section and the surrounding environment, as tests have shown that the brazing and sealing of this design provides a higher degree of sealing compared to other designs.

[0124] In addition, bars have been arranged to provide the first outer wall 7 and the second outer wall 8. For example... Figure 9dAs further shown, the public area also includes one or more slots 31. Figure 9e Also shown are bars arranged to provide the first outer wall 7 and the second outer wall 8, and bar portions 38 arranged in the receiving section 66.

[0125] Reception sections can be provided by imprinting at each end of the public area; however, in this embodiment, reception section 66 is provided only at one end. At the opposite end of this embodiment, a flow path is provided between the first and second pipe sections to provide flow between the first and second pipe sections themselves and / or to provide flow between the first and second pipe sections via an auxiliary manifold.

[0126] Although the invention has been described above in conjunction with preferred embodiments thereof, several variations will be apparent to those skilled in the art without departing from the invention as defined in the following claims.

Claims

1. A heat exchanger (1), comprising: - At least one fluid tube (2) configured to extend substantially orthogonally to the wind direction, the fluid tube (2) being made of a first plate defining a first wall (5) and a second plate defining a second wall (6), and the fluid tube (2) comprising: - A first pipe section (18) and a second pipe section (19) extending along the fluid pipe (2), respectively, arranged such that each pipe section is in fluid communication with the first manifold (9) and the second manifold (10) and configured to contain cooling fluid. The first pipe section (18) is formed by the first wall (5), the second wall (6), the first outer wall (7), and the first inner wall (11). The second pipe section (19) is formed by the first wall (5), the second wall (6), the second outer wall (8, 93), and the second inner wall (12). The first inner wall (11), the second inner wall (12), the first outer wall (7), and the second outer wall (8, 93) extend substantially parallel to the fluid pipe (2) and are in impermeable contact with the first wall (5) and the second wall (6), wherein the heat exchanger (1) is configured to guide the cooling fluid in a first direction in the first pipe section (18) and in a second direction in the second pipe section (19), the first direction being opposite to the second direction, wherein the cooling fluid is guided through the second pipe section (19) before entering the first pipe section (18), and the first pipe section (18) is arranged upstream of the second pipe section (19) with respect to the wind direction, such that the cooling air flowing with the wind direction first cools the cooling fluid with the lowest temperature. The first inner wall (11) and the second inner wall (12) are separated by at least one common area (30) defined by the first inner wall (11) and the second inner wall (12), the first inner wall (11) and the second inner wall (12) are arranged at a distance (d) from each other, and the at least one common area (30) is arranged between the first pipe section (18) and the second pipe section (19), and the common area (30) includes at least one groove (31). The inner wall has a first end and a second end, and a seal is provided between the first inner wall and the second inner wall at the first end and the second end, the inner wall is joined at the first end and the second end, the joined inner wall at the first end extends into the first manifold, and the joined inner wall at the second end extends into the second manifold.

2. The heat exchanger (1) according to claim 1, wherein, The first outer wall (7) and the second outer wall (8) are formed by a pair of sidewalls of the fluid pipe (2).

3. The heat exchanger (1) according to claim 2, wherein, The at least one groove (31) is an elongated groove extending along the longitudinal axis (C) of the fluid pipe (2).

4. The heat exchanger (1) according to any one of claims 1-3, wherein, The at least one fluid tube (2) is a flat fluid tube.

5. The heat exchanger (1) according to any one of claims 1-3, wherein, Baffles (24, 32) are arranged inside the pipe sections (18, 19).

6. The heat exchanger (1) according to claim 5, wherein, The flow disruptor (24) is formed by a recess arranged on the first wall (5) and / or the second wall (6) of the fluid pipe (2).

7. The heat exchanger (1) according to any one of claims 1-3, wherein, The heat exchanger includes a plurality of fluid tubes (2) and a plate arranged between at least some of the fluid tubes in a manner that extends substantially through the entire heat exchanger (1) in the direction of airflow.

8. The heat exchanger (1) according to claim 1, wherein, The first inner wall (11) and the second inner wall (12) are formed by a pair of slender rods.

9. The heat exchanger (1) according to claim 1, wherein, The first inner wall (11) includes a pair of first diverging segments (73), and the second inner wall (12) includes a corresponding pair of second diverging segments, wherein the first diverging segments (73) extend toward the first outer wall (7), and the second diverging segments (74) extend toward the second outer wall (8, 93), wherein the first diverging segments (73) and the corresponding second diverging segments (74) are arranged opposite to each other to form the common area (30).

10. The heat exchanger (1) according to claim 8 or 9, wherein, The first wall (5) and / or the second wall (6) includes at least one protruding element (51) protruding from the first or second wall, wherein the protruding element (51) is configured to retain the first inner wall (11) and the second inner wall (12) to form the common area (30).

11. The heat exchanger (1) according to any one of claims 1-3, wherein, The fluid tube (2) includes a plurality of grooves (31) and protruding elements (51) along the longitudinal axis (C) of the fluid tube (2), wherein the protruding elements (51) are arranged between the grooves (31) of the first wall (5) and / or between the grooves (31) of the second wall (6).

12. The heat exchanger (1) according to any one of claims 1-3, wherein, The fluid tube (2) is configured to extend in the vertical direction.

13. The heat exchanger (1) according to any one of claims 1-3, wherein, The heat exchanger (1) is a block heat exchanger.

14. The heat exchanger (1) according to any one of claims 1-3, wherein, The inner walls (11, 12) are interconnected by means of the common area (30), wherein the common area (30) is formed by embossing the first wall (5) and / or the second wall (6) to form the inner walls (11, 12) and the common area (30).

15. A wind turbine comprising a heat exchanger (1) according to any one of claims 1-14.

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