Heat transfer arrangement
By adopting a common fluid pipeline circuit and a specific heat exchanger arrangement in industrial facilities, the problems of high cost and complex maintenance of heat transfer components in the prior art are solved, and efficient heat transfer to multiple heat dissipation components and reliable cooling of high-priority component sets are achieved.
Patent Information
- Application Number
- CN202380073311.8
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Priority Date
- 2022-10-21
- Filing Date
- 2023-09-22
- Publication Date
- 2025-05-30
AI Technical Summary
In the prior art, separate heat transfer components are provided to meet the cooling requirements of different heat dissipation components, resulting in increased costs and complex maintenance, especially in environments such as offshore wind turbines.
Using a common fluid pipeline circuit and two heat exchangers arrangement, the flow-based temperature priority sort is achieved through the specific shape of the fluid pipeline junction (each outflow line enters the common fluid pipeline at an acute angle of up to 75°), ensuring that the high-priority component group always receives colder heat transfer fluid.
Efficient heat transfer to multiple heat dissipation components is achieved, reducing cost and maintenance complexity, ensuring reliable cooling of high-priority component sets without the need for additional valves or control devices.
Smart Images
Figure CN120077239A_ABST
Abstract
Description
Background Art
[0001] Industrial facilities or equipment in which heat dissipating components (such as generators, motors, power converters, one or more electrical cabinets, etc.) are deployed are typically provided with some means for removing heat from these components. Cooling such components may be necessary to avoid damage caused by overheating, but also because the efficiency of such components may decrease as the temperature increases. Various heat transfer modes are known. For example, a wind turbine may be equipped with a heat transfer system that circulates a heat transfer fluid (commonly referred to as a "coolant fluid") between a heat source (such as a heat dissipating component such as a high voltage power converter) and a liquid-to-air heat exchanger. Various heat transfer modes are known, and the basic principle is to circulate a heat transfer fluid through fluid lines disposed within or adjacent to the heat source and remove heat from the warmed fluid. For example, a liquid-to-air heat exchanger is connected to the heat source by fluid lines, and the arrangement of fins or plates allows heat to be transferred from the warmed heat transfer fluid to the ambient air. The cooled fluid is then returned to the heat source. For example, in the case of a wind turbine, a large liquid-to-air heat exchanger may be implemented externally and may be installed near the rear of the nacelle such that the airflow over the heat exchanger can efficiently remove heat from the heat transfer fluid.
[0002] Equipment such as a wind turbine will typically include various types of heat dissipating components, and these components may have different cooling requirements. A common way to address this aspect is to provide separate heat transfer assemblies for different component types. Each heat transfer assembly has an outflow line for transporting coolant from the heat exchanger to the heat dissipating component and a return line for conveying the warmed heat transfer fluid back to the heat exchanger.
[0003] However, the need to provide separate heat transfer assemblies is associated with higher costs because each heat transfer arrangement requires fluid lines or pipes, pumps for transporting the heat transfer fluid in the pipes, one or more temperature sensors, various valves for regulating the fluid flow, and an arrangement of control interfaces. In addition, the maintenance and repair of several heat transfer assemblies increases the overall operating cost of equipment such as a wind turbine, especially in the case of an offshore wind turbine.
[0004] Accordingly, it is an object of the present invention to provide a more economical way to provide efficient heat transfer from multiple heat dissipating components.
[0005] This object is achieved by the claimed heat transfer arrangement, by the claimed wind turbine, and by the claimed method of connecting multiple heat dissipating components in a heat transfer arrangement. Summary of the Invention
[0006] In the following, it is assumed that the device includes a plurality of heat dissipating components having different cooling requirements, and the components are virtually or physically arranged in "groups" according to their cooling requirements.
[0007] According to the present invention, the heat transfer arrangement for the first and second groups of heat dissipating components includes: a fluid pipeline loop through which a heat transfer fluid is conveyed; a first heat exchanger arranged to circulate the heat transfer fluid through the fluid pipeline loop; and a second heat exchanger arranged to circulate the heat transfer fluid through the same fluid pipeline loop. The fluid pipeline loop of the heat transfer arrangement of the present invention includes a common fluid pipeline between the first and second groups of heat dissipating components, the common fluid pipeline having a first portion leading to the first component group and a second portion leading to the second component group. The fluid pipeline loop further includes a fluid pipeline junction formed by the confluence of the outflow pipelines of the first heat exchanger, the outflow pipelines of the second heat exchanger, and the two portions of the common fluid pipeline. In the heat transfer arrangement of the present invention, the outflow pipeline forms an acute entry angle of up to 75° with the second portion of the common fluid pipeline.
[0008] It may be necessary to keep the temperature in one of the component groups below a certain threshold in order to ensure that the device can remain operational, and thus the cooling of this component group is given a higher priority. In the context of the present invention, the second component group should be understood to include at least one heat-sensitive component that is crucial for the operation of the device, such as a computer for controlling the device, an uninterruptible power supply for the components of the device, a function-related electrical module housed in a cabinet, etc. Generally, the temperature of such a device is monitored, and when the temperature rises to the threshold (e.g., 50 °C), a device shutdown procedure can be initiated to avoid the risk of catastrophic thermal damage to the electrical device. The cooling of the second component group is therefore given a high priority, and in the following, this second component group may be referred to as the "high-priority component group" or simply the "high-priority group".
[0009] The other component group should be understood to include heat dissipating components such as power converters, transformers, auxiliary converters, various hydraulic devices, bearings, etc. Such components may have very large heat losses compared to the components in the "high-priority" group. However, when such a component overheats, the rated power of the device can be limited or reduced, thereby allowing the temperature of the overheated component to return to the normal level. Since the overheating of such a component can be handled without shutting down the device, this first component group may be referred to as the "low-priority component group" or simply the "low-priority group" in the following. The terms "high-priority" and "low-priority" are only related to the cooling requirements of the component groups; these terms are not related to the functional relevance of the components in any way.
[0010] The heat exchangers can be of similar size, i.e., the heat exchangers can be of comparable size and can have similar cooling capabilities. Using the heat transfer arrangement of the present invention, a group of components can be cooled with the heat transfer fluid sourced from any one of the heat exchangers, as will be explained below. Hereinafter, the terms "coolant" and "heat transfer fluid" can be used interchangeably. A fluid line circuit or "cooling circuit" can include means for moving the coolant through the fluid lines, such as a pump arranged in the fluid lines.
[0011] The coolant fluid in the first outlet line and the coolant fluid in the second outlet line may have the same temperature, but will generally have different temperatures. In the type of heat transfer arrangement discussed herein, the hotter coolant fluid in the fluid line generally has a higher flow rate than the cooler coolant fluid in the same fluid line and thus has greater kinetic energy. The present invention takes advantage of this behavior at the fluid line junction. Instead of using a conventional 90° joint or "T-joint" to join each outlet line to the common fluid line, each outlet line joins the common fluid line at an acute angle. The momentum of the heat transfer fluid with the higher flow rate will carry it forward into the first part of the common fluid line, while the heat transfer fluid with the lower flow rate will always be forced to "turn the corner" into the second part of the common fluid line. The assumption on which this behavior is based is that the heat transfer fluid with the lower flow rate is likely to have a lower temperature than the heat transfer fluid with the higher flow rate: at the fluid line junction, the momentum of the heat transfer fluid with the higher flow rate (the hotter fluid) will carry it towards the low-priority group, and the heat transfer fluid with the lower flow rate (the cooler fluid) will be forced towards the high-priority group. In fact, the heat transfer arrangement of the present invention ensures that the cooler heat transfer fluid is always directed towards the high-priority group of components. In other words, the heat exchanger with the lowest flow rate (and presumably the cooler fluid) will cool the high-priority group of components, and the other heat exchanger will cool the low-priority group of components.
[0012] For example, even if the first heat exchanger may have been cooling the low-priority group of components and the second heat exchanger may have been cooling the high-priority group of components, a "switch" between the groups of components will occur when the heat transfer fluid leaving the first heat exchanger is cooler than the heat transfer fluid leaving the second heat exchanger. The advantage of the present invention is that this "switch" is achieved in a completely passive manner, so the heat transfer arrangement does not require any additional valves or control means to ensure that the high-priority group of components always receives the cooler heat transfer fluid, i.e., the present invention achieves flow-based temperature prioritization for the different cooling requirements of the groups of components.
[0013] According to the invention, the industrial installation is a wind turbine and comprises a first group of heat dissipating components; a second group of heat dissipating components; and an embodiment of the heat transfer arrangement of the invention for circulating a heat transfer fluid to the groups of components. As described above, the cooling requirements of the "high priority" group of components exceed those of the other group of components, and taking into account the specific shape of the fluid line junctions of the heat transfer arrangement of the invention, such a "high priority" group will be reliably cooled by the heat transfer arrangement.
[0014] According to the invention, a method of connecting a first group of heat dissipating components and a second group of heat dissipating components in a fluid line circuit of a heat transfer arrangement comprises the steps of: arranging a first heat exchanger for circulating a heat transfer fluid through the pipes of the fluid line circuit; arranging a second heat exchanger for circulating a heat transfer fluid through the pipes of the fluid line circuit; providing a common fluid line having a first part leading to the first group of components and a second part leading to the second group of components; and forming a fluid line junction between the common fluid line and the outflow line of the heat exchanger by connecting each outflow line to the second part of the common fluid line at an acute entry angle of at most 75°.
[0015] Particularly advantageous embodiments and features of the invention are given by the dependent claims, as revealed by the following description. Features of different claim categories may be combined as appropriate to give further embodiments not described herein.
[0016] In the following, without in any way limiting the invention, it may be assumed that the industrial installation in which the heat transfer arrangement is deployed is a wind turbine, for example a direct drive wind turbine. A wind turbine generally comprises a plurality of heat dissipating components. In the context of the present invention, these components are spatially and / or functionally grouped into a "high priority group" (having one or more components with more stringent cooling requirements) and a "low priority group" (having components that can tolerate higher temperatures), as explained above.
[0017] The first heat exchanger may be of any suitable type. In the following, it may be assumed that the first heat exchanger is implemented as a liquid-to-air heat exchanger mounted outside the nacelle (e.g. near the rear of the nacelle). A fluid line carrying the thermally varying heat transfer fluid leads to this heat exchanger.
[0018] The second heat exchanger can also deploy any suitable heat transfer mode to remove the waste heat from the component group and the heat dissipated by the generator. Hereinafter, it can be assumed that the second heat exchanger is a liquid-to-air heat exchanger installed inside near the hub (for example, in the generator space (a cavity inside a direct-drive generator)). A fluid pipeline for transporting the variably warm heat transfer fluid leads to this heat exchanger. The fins or plates extending outward from the heat exchanger are preferably exposed to a cooling air flow, which is actively sucked into the generator space through an air inlet in the floor of the nacelle, for example.
[0019] The outflow pipeline from the heat exchanger to the fluid pipeline junction, the common fluid pipeline, and the return pipeline from the component group together form the cooling circuit of the heat transfer arrangement. For example, a pump arranged in the fluid pipeline can cause a liquid coolant (such as water, a mixture of water and ethylene glycol, etc.) to continuously circulate through this circuit. In the heat transfer arrangement of the present invention, the fluid pipeline junction in the common fluid pipeline allows the colder liquid from one of the heat exchangers to be led to the high-priority component group, that is, the fluid pipeline leading to the high-priority component group will transport the liquid from the coldest outflow pipeline.
[0020] The common fluid pipeline extends between the component groups, and the fluid outflow pipeline from the heat exchanger joins the common fluid pipeline at the fluid pipeline junction. The common fluid pipeline thus includes a first part extending between the fluid pipeline junction and one component group and a second part extending between the fluid pipeline junction and another component group. As described above, the heat exchanger outflow pipeline forms an acute entry angle of a maximum of 75°, more preferably a maximum of 65° with the second part of the common fluid pipeline. In a particularly preferred embodiment of the present invention, the heat exchanger outflow pipeline forms an acute entry angle of at least 45° with the second part of the common fluid pipeline.
[0021] Although the entry angles of the outflow pipelines can be slightly different, in a particularly preferred embodiment of the present invention, the outflow pipelines preferably form substantially the same entry angle with the second part of the common fluid pipeline. This can ensure consistent fluid behavior at the fluid pipeline junction even when "switching" occurs during the inversion of the temperature difference in the heat exchanger outflow pipeline.
[0022] In a preferred embodiment of the present invention, the common fluid pipeline and the heat exchanger outflow pipeline have the same diameter. For example, all the pipes and conduits in the cooling circuit can have a diameter of about 100 mm.
[0023] The fluid line connection can be implemented in any suitable manner. In a particularly preferred embodiment of the present invention, the fluid line connection includes a manifold or pipe fitting, the shape of which is arranged such that each heat exchanger outlet line is oriented at a desired inlet angle relative to the second part of the common fluid line. The pipe fitting can be made of a suitable material, for example, made of a block of aluminum.
[0024] During the operation of the wind turbine, the armature and field of the generator generate heat, and the generator is air-cooled by sucking in ambient air from the outside. For example, an air intake can be provided in the floor of the nacelle. The second heat exchanger is positioned in the path of the air intake, which thereby removes heat from the fluid in the return line of the second heat exchanger.
[0025] Similarly, if the relative humidity inside the nacelle is high (e.g., due to a shutdown), the return line of the second heat exchanger can be used to deliberately convey warm fluid into the path of the air intake in order to reduce the relative humidity. This avoids damage caused by water condensation, such as damage due to short circuits and / or corrosion that might otherwise occur due to water droplets condensing on exposed metal surfaces. In the heat transfer arrangement of the present invention, the waste heat from the low-priority component group can be directed to the second heat exchanger to raise the temperature in the generator space. By transferring some of the typically significantly warmer fluid from the low-priority component group to the second heat exchanger, the air intake entering the generator space can be efficiently warmed, thereby reducing the relative humidity in the generator space. BRIEF DESCRIPTION OF THE DRAWINGS
[0026] Other objects and features of the present invention will become apparent from the following detailed description considered in conjunction with the accompanying drawings. However, it should be understood that the drawings are designed for illustrative purposes only and are not a limitation of the scope of the present invention.
[0027] Figure 1 A block diagram of a direct-drive wind turbine is shown;
[0028] Figure 2 and Figure 3 An illustration of a configuration with a converging cooling circuit;
[0029] Figure 4 An illustration of the fluid behavior at the fluid line connection of the heat transfer arrangement of the present invention;
[0030] Figure 5 An illustration of the configuration of the converging cooling circuit of the present invention;
[0031] Figure 6 An illustration of the fluid behavior at the fluid line connection of the heat transfer arrangement of the present invention;
[0032] Figure 7is a block diagram of the configuration of the convergent cooling circuit of the present invention;
[0033] FIG. 8 shows a block diagram of a prior art wind turbine.
[0034] In the schematic diagrams, the same numbers refer to the same objects throughout. The objects in the schematic diagrams are not necessarily drawn to scale. DETAILED DESCRIPTION
[0035] Figure 1 A block diagram of a direct drive wind turbine 2 is shown, schematically showing various heat dissipating components. The components are arranged in groups GL, GH according to their cooling requirements. Here, one group GL includes the power converter and any other heat sources located close to the rear of the nacelle, while the other group GH includes the hydraulic unit in the hub 21, the electrical cabinet, and any other heat sources located close to the front or "hub end" of the nacelle 20.
[0036] The wind turbine 2 is equipped with an embodiment of the heat transfer arrangement 1 of the present invention. This includes a first heat exchanger H1 and a second heat exchanger H2 that are arranged to circulate a coolant fluid through fluid lines of a cooling circuit.
[0037] In the prior art, as illustrated in FIG. 8, heat transfer arrangements for wind turbines having such heat dissipating components typically include a first cooling circuit connecting a group of components G1 or heat sources to the first heat exchanger H1 and a second cooling circuit connecting another group of components G2 or heat sources to the second heat exchanger H2. These heat transfer arrangements are functionally and spatially separate and are controlled independently of each other.
[0038] Such cooling circuits can be made to converge, as Figure 2 illustrated. Here, a common fluid line extends between the component groups G1, G2, and the outlet lines H1 out , H2 out of the heat exchangers H1, H2 are connected to the common fluid line L 12 . However, as explained above, different component groups G1, G2 can have different cooling requirements. For example, the second component group G2 can include temperature-sensitive components that must be cooled below a certain threshold to avoid wind turbine shutdown. In addition, the fluid in one outlet line can have a higher flow rate than the fluid in the other outlet line, i.e., it moves faster than the fluid in the other outlet line. Generally, the fluid with the higher flow rate is also warmer than the other fluids. This can lead to undesirable effects as Figure 3 illustrated. Here, the left outlet line H1 out is transporting a fluid that is moving faster (warmer) than the right outlet line H2 out . The outlet line H1 out, H2 out Both are connected by a conventional T-shaped pipe fitting 30 to a common fluid line L 12 , such that each outlet line intersects the common fluid line at a 90° angle. As a result, the warmer fluid (from the first heat exchanger H1 in this example) dominates in the flow distribution to the component groups, and a significant portion of the warmer fluid may be delivered to the second component group G2. However, as described above, the addition of the warm coolant fluid may have an adverse effect on the performance of the components in this second component group G2.
[0039] The heat transfer arrangement 1 of the present invention overcomes this problem, as Figure 4 and Figure 5 illustrated. The schematic diagram shows a fluid line junction 10 formed by the convergence of the outlet line H1 out of the first heat exchanger H1, the outlet line H2 out of the second heat exchanger H2, the first part L1 of the common fluid line L 12 and the second part L2 of the common fluid line L 12 . The outlet lines H1 out , H2 out of the heat exchangers H1, H2 both form acute entry angles β1, β2 with the second part L2 of the common fluid line L 12 . The acute entry angles β1, β2 are preferably not greater than 75°. In addition, the acute entry angles β1, β2 are preferably at least 45°.
[0040] When the outlet lines H1 out , H2 out both form the same entry angle with the second part L2 of the common fluid line L 12 , the fluid line junction can be substantially symmetric about the common fluid line. As Figure 4 illustrated, the fluid lines H1 out , H2 out , L1, L2 can be connected by a suitably formed pipe fitting 10F or manifold, and the shape of the pipe fitting 10F or manifold is set such that each outlet line H1 out , H2 out intersects the common fluid line L 12 at the same angle. The fluid lines H1 out , H2 out intersecting at the manifold or pipe fitting 10F preferably all have the same diameter, for example a diameter of about 100 mm.
[0041] Figure 4 illustrates that the flow rate in the outlet line H1 out of the first heat exchanger H1 is higher than that in the outlet line H2 of the second heat exchanger H2out The case of the flow rate in. Generally, this is related to the outflow pipeline H1 of the first heat exchanger H1 out with a higher fluid temperature and the outflow pipeline H2 of the second heat exchanger out with a lower fluid temperature. Therefore, the hotter fluid is transported forward towards the low-priority component group by its own momentum (higher flow rate). The colder fluid from the second heat exchanger H2 is forced to turn around the corner and enter the second part L2 of the common fluid pipeline. The warm and cold fluids do not mix to any significant extent at the fluid pipeline junction 10. Therefore, the warmer fluid is mainly transported to the low-priority component group and the colder fluid is mainly transported to the high-priority component group. This favorable distribution is achieved only through the orientation of the outflow pipeline relative to the second part of the common fluid pipeline, that is, the favorable fluid distribution is achieved through the fluid pipeline junction.
[0042] In the example case, the coolant from the first heat exchanger H1 has a temperature of 45 °C, while the coolant from the second heat exchanger H2 has a temperature of 40 °C; through the first outflow pipeline H1 out the flow rate is 600 liters per minute, while through the second outflow pipeline H2 out the flow rate is 200 liters per minute. In other words, 800 liters per minute reaches the fluid pipeline junction 10 with a flow rate distribution of 3:1. The dynamics of the faster-moving (and also warmer) fluid dominates the fluid behavior at the fluid pipeline junction 10. The faster-moving fluid will tend to continue flowing in the same direction, that is, from the first outflow pipeline H1 out into the first part L1 of the common fluid pipeline L 12 and flowing towards the low-priority component group GL. As a result, the slower-moving (and colder) fluid in the second outflow pipeline H2 out is forced to turn around the angled corner of the fluid pipeline junction 10 and flow into the second part L2 of the common fluid pipeline L 12 and flowing towards the high-priority component group GH.
[0043] Fluid dynamics causes the fast-moving fluid to "grab" a part of the colder fluid from the second outflow pipeline H2 out and the slower-moving fluid to "grab" a part of the hotter fluid from the first outflow pipeline H1 out (represented by short arrows). However, the degree of mixing between the faster-moving fluid and the slower-moving fluid is negligible because the momentum of the faster-moving fluid will effectively transport most of it in the direction of the low-priority component group GL into the first part L1 of the common fluid pipeline.
[0044] Thus, the geometry at the fluid line junction 10 of the heat transfer arrangement structure 1 of the present invention ensures that the slower moving, cooler fluid will be effectively and reliably transported to the high-priority component group GH, while the momentum of the faster moving, warmer fluid will always carry it towards the low-priority component group GL. In this example, the common fluid line L 12 The slower moving fluid in the second part L2 of has a temperature of 40.6 °C, which is only slightly warmer than the temperature (40 °C) of the fluid in the outlet line from the second heat exchanger H2.
[0045] The total input flow rate is the same as the total output flow rate. Thus - continuing with the above example - 800 liters per minute must pass through the common fluid line L 12 and leave. The flow distribution in the common fluid line L 12 is now in a ratio of 4:1, where 640 L / min moves towards the low-priority component group and 160 L / min moves towards the high-priority component group.
[0046] Figure 6 shows another scenario where the cooling fluid for the high-priority component group is provided by the first heat exchanger. In this case, the faster moving (warmer) fluid from the second heat exchanger H2 is carried forward towards the low-priority component group GL by its own momentum. The slower moving (cooler) fluid from the first heat exchanger H1 is forced to turn around a corner and enter the second part L2 of the common fluid line. In this example case, the coolant from the first heat exchanger H1 can have a flow rate of 200 liters per minute (at a temperature of 40 °C), while the faster moving coolant from the second heat exchanger H2 has a flow rate of 600 liters per minute (at a temperature of 45 °C). As explained above, the dynamics of the faster moving (and generally warmer) fluid determine the fluid behavior at the fluid line junction 10, so the slower moving (and generally cooler) fluid in the first outlet line H1 out is forced to turn around the angled corner of the fluid line junction 10 and enter the second part L2 of the common fluid line L 12 and flow towards the high-priority component group GH. Here, the outlet lines H1 out and H2 out both intersect the common fluid line L 12 at the same angle β.
[0047] Figure 7shows a simplified schematic diagram of the converging cooling circuit in the heat transfer arrangement 1 of the present invention. The schematic diagram shows a first liquid-to-air heat exchanger H1 exposed to the ambient air flow A20 outside the nacelle 20 and a second liquid-to-air heat exchanger H2 exposed to the ambient air flow A22 drawn into the interior of the generator housing 22. This air flow A22 is used to cool the generator during operation of the wind turbine 2. The outflow pipelines H1 out , H2 out meet at the fluid pipeline junction 10 as described above. This ensures that the slower (cooler) moving fluid is always directed to the high-priority component group GH, while the faster (warmer) moving fluid is always directed to the low-priority component group GL. The warmed fluid passes through the fluid pipelines GL out and GH out and leaves the component groups GL and GH.
[0048] In the present exemplary embodiment, the first heat exchanger H1 receives the warmed fluid from the high-priority component group GH, while the second heat exchanger H2 can receive the warmed fluid from the low-priority component group GL alone, or it can receive a mixture of the warmed fluids from both the component groups GL and GH. For this purpose, a mixing valve 11 is included in the cooling circuit as schematically shown. For example, if it is desired to reduce the relative humidity in the generator space, some of the warmed fluid from the fluid pipeline GH out is mixed with the warmed fluid from the fluid pipeline GL out and sent to the second heat exchanger H2. In this way, the heat transfer arrangement of the present invention can use the waste heat emitted by the components of the low-priority component group (such as a transformer or a power converter) to improve the climate conditions in the generator space. The schematic diagram illustrates this further function, where a part of the faster (hotter) moving fluid leaving the low-priority component group GL is directed to the return pipeline H2 in of the second heat exchanger H2. This warmer fluid then heats the air A22 passing through the second heat exchanger H2, thereby allowing the air in the generator space to become warmer, for example, to reduce the relative humidity. The mixing valve 11 can be controlled as appropriate based on the measurement of the relative humidity.
[0049] Although the present invention has been disclosed in the form of preferred embodiments and their variants, it will be understood that numerous modifications and variations can be made thereto without departing from the scope of the present invention.
[0050] For clarity, it should be understood that the use of "a" or "an" throughout this application does not exclude a plurality, and "comprising" does not exclude other steps or elements.
Claims
1. A heat transfer arrangement (1) for a first group (GL) and a second group (GH) of heat dissipating components, comprising - a fluid pipeline circuit (14); - a first heat exchanger (H1) arranged to circulate a heat transfer fluid through the fluid pipeline circuit (14); - a second heat exchanger (H2) arranged to circulate a heat transfer fluid through the fluid pipeline circuit (14); wherein, the fluid pipeline circuit (14) comprises - Common fluid pipeline (L 12 ), the common fluid pipeline (L 12 ) includes a first part (L1) leading to the first component group (GL) and a second part (L2) leading to the second component group (GH); and - Fluid pipeline joint (10), said fluid pipeline joint (10) being formed by the confluence of the outflow pipeline (H1 out ) of the first heat exchanger (H1), the outflow pipeline (H2 out ) of the second heat exchanger (H2), the first part (L1) of the common fluid pipeline (L 12 ) and the second part (L2) of the common fluid pipeline (L 12 ), wherein the outflow pipelines (H1 out , H2 out ) of each heat exchanger (H1, H2) form an acute angle (β, β1, β2) of at most 75° with the second part (L2) of the common fluid pipeline (L 12 ).
2. The heat transfer arrangement according to the preceding claim, wherein, The outflow pipeline (H1 out , H2 out ) and the second part (L2) of the shared fluid pipeline (L 12 ) form an acute angle (β, β1, β2) of up to 60°, more preferably up to 45°.
3. The heat transfer arrangement according to any one of the preceding claims, wherein, Outlet pipelines (H1 out , H2 out ) both form the same angle (β) with the second part (L2) of the said common fluid pipeline (L 12 ).
4. The heat transfer arrangement according to any one of the preceding claims, wherein, The fluid pipeline joint (10) is symmetric about the common fluid pipeline (L 12 ).
5. The heat transfer arrangement according to any one of the preceding claims, wherein, The fluid pipeline joint (10) includes a manifold (10F), and the shape of the manifold (10F) is configured such that the heat exchange fluid outflow pipelines (H1 out , H2 out ) enter the second part (L2) of the common fluid pipeline (L 12 ) at the acute entry angles (β, β1, β2).
6. The heat transfer arrangement according to any one of the preceding claims, wherein, The first part (L1) and the second part (L2) of the shared fluid pipeline (L 12 ) are substantially collinear.
7. The heat transfer arrangement according to any one of the preceding claims, wherein, the cooling circuit (14) comprises a mixing valve (11), the mixing valve (11) being arranged to combine heat transfer fluids from both component groups (GL, GH).
8. A wind turbine (2), comprising, - a first group of heat dissipating components (GL); and - a second group of heat dissipating components (GH), wherein, the cooling requirement of the second component group (GH) exceeds the cooling requirement of the first component group (GL); and - the heat transfer arrangement (1) according to any one of claims 1 to 7, which is used to circulate a heat transfer fluid to the component groups (GL, GH).
9. The wind turbine according to the preceding claim, wherein, the first component group (GL) comprises any one of a power converter, a transformer, a hydraulic device, a bearing.
10. The wind turbine according to any one of claims 8 to 9, wherein, the second component group (GH) comprises any one of a computer, an uninterruptible power supply, an electrical cabinet.
11. The wind turbine according to any one of claims 8 to 10, wherein, the first heat exchanger is implemented as a liquid-to-air heat exchanger (H1), which is arranged in the ambient air flow (A20) outside the nacelle (20).
12. The wind turbine according to any one of claims 8 to 11, wherein, the second heat exchanger is implemented as a liquid-to-air heat exchanger (H2), which is arranged in the air flow (A22) sucked into the internal space of the wind turbine (2).
13. A method of connecting a first group (GL) of heat dissipating components and a second group (GH) of heat dissipating components in a fluid pipeline circuit (14) of a heat transfer arrangement (1), comprising the steps of: - arranging a first heat exchanger (H1) to circulate a heat transfer fluid through the fluid pipeline circuit (14); - arranging a second heat exchanger (H2) to circulate a heat transfer fluid through the fluid pipeline circuit (14); - Provide a common fluid pipeline (L 12 ), the common fluid pipeline (L 12 ) having a first portion (L1) leading to the first component group (GL) and a second portion (L2) leading to the second component group (GH); - By connecting each outlet pipeline (H1 out , H2 out ) to the second part (L2) of the shared fluid pipeline (L 12 ) at an acute angle of up to 60°, a fluid pipeline joint (10) is formed between the outlet pipeline (H1 out ) of the first heat exchanger (H1), the outlet pipeline (H2 out ) of the second heat exchanger (H2), the first part (L1) of the shared fluid pipeline (L 12 ) and the second part (L2) of the shared fluid pipeline (L 12 ).
14. The method according to the preceding claim, comprising the steps of: determining the relative humidity in the interior space and, when the relative humidity exceeds a predetermined threshold, directing the warmed fluid from the first component group (G1) to the second heat exchanger (H2).