Two-phase heat sink for cooling heat source

Abstract

Embodiments of the invention relate to a two-phase heat sink (100) for cooling an electrical heat source (200). The two-phase heat sink (100) comprises a cavity (110) for accommodating a cooling fluid (F). In order to improve cooling and heat dissipation, the cavity (110) in the two-phase heat sink inner surface (112 '') comprises a core region (134) for converting the cooling fluid (F) from a liquid phase to a gas phase. The core region (134) and the attachment region (132) at least partially overlap each other. Therefore, the cooling effect is improved. In addition, embodiments of the invention also relate to a heat sink comprising two or more such two-phase heat sinks.

Description

Technical Field

[0001] Embodiments of the present invention relate to two-phase heat sinks for cooling an electric heat source and heat sinks including two or more such two-phase heat sinks. Background Art

[0002] With the development of communication technology, outdoor base station equipment has shown the characteristics of faster transmission speed, greater power output and higher heat consumption. Especially for remote radio units (RRU) and multiple input multiple output (MIMO) devices in 3GPP 5G networks, base station equipment systems are highly integrated and highly dependent on the natural cooling capacity of cooling equipment.

[0003] Due to the flexibility of base station deployment and the long-term reliability requirements in complex environments, cooling fans or circulating liquid cooling are rarely used in RRU and MIMO equipment. Therefore, how to further improve the natural heat dissipation capacity of cooling equipment is crucial for future base stations. Summary of the invention

[0004] The purpose of the embodiments of the present invention is to provide a solution to reduce or solve the disadvantages and problems of the prior art.

[0005] Another object of embodiments of the present invention is to provide a solution that enables improved cooling compared to conventional solutions.

[0006] The above objects and other objects are achieved by the subject matter claimed in the independent claims. Further embodiments of the invention are provided in the dependent claims.

[0007] According to a first aspect of the present invention, the above and other objects are achieved by a two-phase radiator for cooling an electric heat source, the two-phase radiator comprising:

[0008] a cavity for containing a cooling fluid, the cavity comprising a first wall portion and a second wall portion disposed opposite the first wall portion;

[0009] a cooling fin coupled to the cavity so that the cooling fluid can circulate between the cavity and the cooling fin during operation;

[0010] an attachment area disposed on an outer surface of the first wall portion and used to attach a heat source to the first wall portion;

[0011] a core region for converting the cooling fluid from a liquid phase to a gas phase, the core region being arranged on an inner surface of the first wall portion,

[0012] Therein, the attachment region and the core region at least partially overlap each other.

[0013] The expression "in operation" above may mean that the two-phase radiator is installed and ready for use or is in actual use. In the latter case, it operates according to the disclosed technical features.

[0014] The advantage of the two-phase radiator according to the first aspect is that the cooling capacity is improved compared to a conventional two-phase radiator. This is because the capillary effect of the core region improves the phase transition of the cooling fluid. This also means that the volume of cooling fluid required in the two-phase radiator can be reduced, i.e. the two-phase radiator is lighter and smaller in size.

[0015] In an implementation of the two-phase heat sink according to the first aspect, the core region is a porous core region.

[0016] An advantage of this implementation is that the cooling capacity is further increased due to the porous core region, which means that it is possible to increase the conversion factor of the cooling fluid from the liquid phase to the gas phase.

[0017] In an implementation of the two-phase heat sink according to the first aspect, the core area is larger than the attachment area.

[0018] An advantage of this implementation is that cooling of the heat source is improved due to the larger core area.

[0019] In an implementation of the two-phase heat sink according to the first aspect, the core region and the attachment region are aligned with respect to each other.

[0020] The advantage of this implementation is that the heat generated by the heat source will have a shorter heat transfer path, thereby reducing thermal resistance and improving heat dissipation capacity.

[0021] In an implementation of the two-phase heat sink according to the first aspect, the core region and the attachment region are offset relative to each other.

[0022] An advantage of this implementation is that by offsetting the core region from the attachment region, the height of the cooling fluid in the two-phase heat sink can be adjusted by capillary forces, and thus the charge amount of the cooling fluid can be reduced.

[0023] In an implementation of the two-phase radiator according to the first aspect, the core region is offset relative to the attachment region in a gravity direction when the two-phase radiator is in operation.

[0024] The advantage of this implementation is that the height of the cooling fluid in the two-phase radiator can be further adjusted.

[0025] In an implementation of the two-phase radiator according to the first aspect, the cooling fins are roll-bonded cooling fins.

[0026] The roll-bonded cooling fin may have a honeycomb structure.

[0027] An advantage of this implementation is that the roll-bonded cooling fins maximize the condensation area, thereby increasing the cooling capacity of the two-phase heat sink. The roll-bonded cooling fins also provide a mechanically robust cooling fin structure.

[0028] In an implementation of the two-phase radiator according to the first aspect, the roll-bonded cooling fin includes a first plate portion and a second plate portion and a plurality of supporting elements arranged between the first plate portion and the second plate portion, wherein a distance between two adjacent supporting elements is in the range of 1.0 mm to 5.0 mm, preferably in the range of 3.0 mm to 4.0 mm.

[0029] The advantage of this implementation is that the cooling capacity of the two-phase radiator is further improved.

[0030] In an implementation of the two-phase heat sink according to the first aspect, the support element is integrated with the first plate portion and the second plate portion.

[0031] In one implementation of the two-phase heat sink according to the first aspect, the cavity is coupled to the roll-bonded cooling fin via one or more input / output ports.

[0032] In an implementation of the two-phase radiator according to the first aspect, a distance between the core region and an inner surface of the second wall portion is in the range of 1.0 mm to 10.0 mm, preferably in the range of 1.5 mm to 7 mm, and more preferably in the range of 1.5 mm to 5 mm.

[0033] The advantage of this implementation is that the above given gap range between the core area and the inner surface of the second wall portion makes it easier for the cooling fluid to boil.Thus, by this boiling enhancement, the weight of the two-phase radiator can be reduced while the cooling capacity is increased.

[0034] In an implementation of the two-phase heat sink according to the first aspect, the second wall portion is formed by a cover plate, and the cooling fins extend perpendicularly to the first wall portion and through the cover plate.

[0035] In an implementation manner of the two-phase heat sink according to the first aspect, the second wall portion is parallel to the first wall portion.

[0036] According to a second aspect of the present invention, the above and other objects are achieved by a heat sink for cooling an electric heat source, the heat sink comprising a first two-phase heat sink according to an embodiment of the present invention and at least one second two-phase heat sink according to an embodiment of the present invention.

[0037] Thus, a simplified mechanical design and integration solution is provided for a heat sink including two or more two-phase heat sinks. The multi-partition design of the substrate receiving cavity and the number and shape of the independent cavities can be adjusted according to the requirements of the cooling application. Thus, the cooling fluid filling amount can also be flexibly adjusted.

[0038] In an implementation of the radiator according to the second aspect, the cooling fluid of the first two-phase radiator is separated from the cooling fluid of the second two-phase radiator.

[0039] The advantage of this implementation is that the two separate two-phase radiators can perform phase conversion without interfering with each other. This is because the evaporation cycle and the condensation cycle in the different two-phase radiators are performed independently, thereby improving the overall temperature uniformity of the radiator and thus improving the cooling capacity of the radiator.

[0040] In an implementation manner of the heat sink according to the second aspect, the first two-phase heat sink and the second two-phase heat sink have a common substrate plate.

[0041] The advantage of this implementation is that the common substrate makes the design simpler. In addition, the common substrate improves the uniformity of the heat sink temperature, thereby improving the cooling capacity.

[0042] In an implementation manner of the radiator according to the second aspect, the first two-phase radiator and the second two-phase radiator are mechanically connected to each other.

[0043] The advantage of this implementation is that the overall strength of the heat sink structure is improved, thereby providing a strong heat sink.

[0044] Other applications and advantages of embodiments of the present invention will be apparent from the following detailed description. BRIEF DESCRIPTION OF THE DRAWINGS

[0045] The accompanying drawings are intended to illustrate and explain different embodiments of the present invention, in which:

[0046] - Figures 1 to 3 A two-phase heat sink according to an embodiment of the present invention is shown;

[0047] - Figure 4a and Figure 4b An exemplary core structure used in a two-phase heat sink according to an embodiment of the present invention is shown in detail;

[0048] - Figures 5 to 8 The design, layout and function of a heat sink according to an embodiment of the present invention are shown. DETAILED DESCRIPTION

[0049] At present, conventional base station cooling equipment is mainly made of die-cast aluminum alloy, and generally includes a solid substrate and a plurality of heat dissipation cooling fins located on the back of the solid substrate. The solid substrate contacts the printed circuit board, and the heat generated by the heat source on the printed circuit board is transferred from the printed circuit board to the cooling fins through the solid substrate. The cooling fins dissipate heat to the surrounding air through convection and radiation. In conventional schemes, the heat dissipation effect of the entire heat transfer path is affected by the low thermal conductivity of the die-cast aluminum solid substrate (e.g., less than 200W / mK).

[0050] Therefore, if the equivalent thermal conductivity of the substrate and the cooling fins can be improved, the cooling capacity of the cooling device can be improved. Therefore, a two-phase radiator is disclosed herein for two-phase cooling using a cooling fluid, which is more efficient than conventional solutions. Therefore, the cooling fluid (also referred to as a refrigerant in the art) can have a maximized boiling zone, thereby reducing the non-boiling zone. This means that the amount of cooling fluid used can be reduced, which also means that the weight of the two-phase radiator can be reduced.

[0051] Figures 1 to 3 1 shows a cross-sectional side view of a two-phase heat sink 100 according to an embodiment of the present invention. Figure 1 , the two-phase heat sink 100 includes a cavity 110 for accommodating a cooling fluid F. The cavity 110 includes a first wall portion 112 and a second wall portion 114 disposed opposite the first wall portion 112. The first wall portion 112 and the second wall portion 114 may extend from a bottom portion 116 of the cavity 110 to a top portion 118. The two-phase heat sink 100 also includes a cooling fin 120 coupled to the cavity 110 so that the cooling fluid F can circulate between the cavity 110 and the cooling fin 120 during operation. The two-phase heat sink 100 also includes an attachment area 132, which is disposed on an outer surface 112′ of the first wall portion 112 and is used to attach the heat source 200 ( Figure 2 and Figure 3 Finally, the two-phase heat sink 100 includes a cooling fluid F for transferring the cooling fluid F from the liquid phase F V Convert to gas phase F L In an embodiment of the present invention, the core region 134 is disposed on the inner surface 112 ″ of the first wall portion 112 , and the attachment region 132 and the core region 134 at least partially overlap each other.

[0052] The attachment area 132 may include any suitable attachment means for attaching the heat source 200 to the first wall portion 112. Non-limiting examples of attachment means are adhesives, such as different types of thermal glue, solder bonds, thermal interface materials, etc. The heat source 200 may be any type of heat source that requires cooling to function properly, such as processors, memory chips, and other electronic devices.

[0053] Therefore, depending on the temperature, the cooling fluid F can have a liquid phase or a gas phase in the two-phase radiator 100. By converting the cooling fluid F from a liquid phase to a gas phase, the heat dissipation is increased compared to a radiator that does not apply the two-phase principle. Non-limiting examples of cooling fluids that can be used are water, R1233ZD, R1336MZZ, HP-1, etc.

[0054] In addition, Figure 1 As shown, in the embodiment of the present invention, the second wall portion 114 is parallel to the first wall portion 112. This can be understood as the first wall portion 112 extending in the first plane P1 and the second wall portion 114 extending in the second plane P2. Figure 1 In operation, the first plane P1 and the second plane P2 and the first wall portion 112 and the second plane P2 can be arranged substantially vertically, so that the bottom portion 116 and the top portion 118 are arranged substantially horizontally. Therefore, the cooling fluid F can flow downward in the two-phase heat sink 100 more quickly. The cavity 110 is connected to the cooling fins 120 through one or more input / output ports 124. Figure 1 The three input / output ports 124 shown in FIG. 1 are arranged at different vertical heights in the two-phase heat sink 100. The sizes of the different input / output ports 124 may also vary, such as Figure 1 shown.

[0055] Therefore, in the present invention, a cooling scheme is provided that can significantly improve the equivalent thermal conductivity along the heat transfer path from the heat source to the surrounding air without expanding the overall size of the two-phase heat sink 100. The solid substrate in the conventional scheme is replaced by a housing cavity 110 for housing the cooling fluid F. The cavity 110 is connected to a cooling fin 120 with microchannels to ensure sufficient evaporation and condensation reflux of the cooling fluid F in three-dimensional space. Therefore, through the liquid-vapor phase change of the cooling fluid F in the disclosed scheme, a higher equivalent thermal conductivity, for example, above 2000 W / mK, can be achieved. In addition, in order to enhance the boiling capacity and make the cooling fluid F easier to boil, the inner surface area of ​​the cavity 110 includes a core area 134 that can have a microstructure. For example, the core area 134 can be aluminum-based and thus directly formed on the inner surface area 112′ of the cavity 110.

[0056] Depending on the cooling application, the relationship between the size of the core region 134 and the size of the attachment region 132 may vary from one embodiment of the present invention to another. For example, in some cooling applications, the core region 134 and the attachment region 132 may have a size such as Figure 1 However, in other applications, the core area 134 is larger than the attachment area 132, such as Figure 2 The relationship between the two regions may depend on the heat load of one or more heat sources. For example, if the heat loss is large and the temperature is high, a larger core area is required to dissipate the heat.

[0057] Another parameter that may be considered when designing the two-phase heat sink 100 disclosed herein is the spatial relationship between the core area 134 and the attachment area 132. Figure 1 As noted in FIG. 1 , the core region 134 and the attachment region 132 may be aligned relative to each other in the first plane P1. However, the core region 134 and the attachment region 132 may be offset relative to each other in other applications, such as Figure 3 In this particular example, the core region 134 is offset relative to the attachment region 132 in the direction of gravity G during operation of the two-phase heat sink 100. The direction of gravity G is indicated by a bold arrow.

[0058] Figure 4a and Figure 4b An example of a core structure used in the two-phase radiator 100 of the present invention is shown in detail. In an embodiment of the present invention, the core region 134 can be a porous core microstructure for improving boiling capacity, thereby further reducing the excessive temperature of the boiling surface and making the boiling of the cooling fluid F more efficient. The porous core microstructure can be implemented in many different structural configurations. For example, the porous core microstructure can be directly processed on the inner surface of the cavity 110 to replace the computer numerical control (CNC) processing of the smooth surface. The surface of the accommodating cavity 110 can be processed to form an aluminum-based core porous microstructure. The porous core microstructure can be formed by different processes such as micro-fin processing, powder sintering, and laser processing. Another option is to integrate the pre-processed core microstructure module with the substrate through a welding process, rather than directly processing the core microstructure on the substrate surface. The core microstructure module can be welded after the cooling fins 120 have been brazed to avoid high brazing temperatures affecting the core microstructure.

[0059] Figure 4aA cross-sectional side view of a porous core microstructure 120 disposed on the inner surface of the first wall portion 112 of the cavity 110 is shown. Compared to a smooth surface, the porous core microstructure 120 can increase boiling nucleation cores and enable the cooling fluid F to boil more easily. The porous core microstructure 120 can also attract the cooling fluid F to a higher vertical position in the two-phase heat sink 100 by capillary force, which means that less cooling fluid F needs to be used to improve heat dissipation capacity, thereby reducing weight. Figure 4a The direction of gravity when the two-phase radiator 100 is in operation is also shown by a bold arrow.

[0060] Figure 4b A cross-sectional perspective view of another core microstructure is shown in detail. Figure 4b The shape of the core microstructure in Figure 4a The shape of the core microstructure shown in Figure 4a Compared with the porous microstructure shown, Figure 4b The microstructure in has a micro-fin geometry that is easier to manufacture. Figure 4b The height of the micro-fins in the TFT may be less than 1000 μm and have a pitch in the range of 400 μm to 500 μm, but is not limited thereto.

[0061] Figures 5 to 8 The design, layout and function of a heat sink 300 according to an embodiment of the present invention are shown and described. Generally, the heat sink 300 disclosed herein for cooling an electric heat source 200 includes a first two-phase heat sink 100′ according to an embodiment of the present invention and at least one second two-phase heat sink 100″ according to an embodiment of the present invention. Therefore, according to an embodiment of the present invention, the heat sink 300 may include two or more two-phase heat sinks 100. The number of two-phase heat sinks may depend on the cooling application.

[0062] Figure 5 A cross-sectional side view of a heat sink 300 comprising a plurality of two-phase heat sinks 100', 100" is shown. Figure 5 (a) shows how different cooling fins 120', 120" are partitioned and arranged relative to their corresponding cavities 110', 110" and heat sources 200', 200", while Figure 5 (b) shows the circulation of cooling fluids F', F" in separate two-phase radiators 100', 100" of a common radiator 300. In this particular example, the cooling fins 120 are roll-bonded cooling fins having a honeycomb structure, which is also shown.

[0063] There are different types of roll-bonded cooling fins in the art, and in the examples of the present invention, the roll-bonded cooling fins include: Figure 5The first plate portion 126 and the second plate portion 126' shown in (c) in FIG. . A plurality of support elements 122 are disposed between the first plate portion 126 and the second plate portion 126', so that microchannels are formed in the space between the support elements 122, thereby forming a honeycomb structure as described above. Therefore, the cooling fluid F can circulate in the microchannels between the support elements 122, so that heat is dissipated from the cooling fins 120 and transferred to the surrounding air. In an embodiment of the present invention, the support element 122 can be integrated with the first plate portion 126 and the second plate portion 126' by brazing, hot pressing or any other suitable technique. In addition, according to an embodiment of the present invention, the distance between two adjacent support elements 122 can be in the range of 1.0 mm to 5.0 mm, preferably in the range of 3.0 mm to 4.0 mm. As another example Figure 5 As shown in FIG. 5( c ), the cavity 110 may be coupled to a roll-bonded cooling fin 122 via one or more input / output ports 124 .

[0064] Figure 6 A cross-sectional side view of a heat sink 300 is shown. In this example, the heat sink 300 includes four independent two-phase heat sinks 100', 100" arranged in a stacked structure according to an embodiment of the present invention. The independent two-phase heat sinks 100', 100" each include a heat source 200 and its attachment area and a corresponding core area 134. See Figure 1 , the second wall portion 114 of the cavity 110 may be formed by the cover plate 140, so that the cooling fins 120 may extend through the cover plate 140 (in the plane P3 shown by the dashed arrow) perpendicularly to the first wall portion 112 and also perpendicularly to the gravity direction G. The individual cooling fins 120 may be structurally connected to each other at the far end relative to the cover plate 140 by a common louver plate 142. The louver plate 142 mechanically fixes the cooling fins 120, making their structure more rigid.

[0065] In an embodiment of the present invention, the distance or gap d between the core region 134 and the inner surface 114″ of the second wall portion 114 is in the range of 1.0 mm to 10.0 mm, preferably in the range of 1.5 mm to 7 mm, and more preferably in the range of 1.5 mm to 5 mm. The distance d is as Figure 4a As shown. These distance ranges provided between the core region 134 and the inner surface 114″ of the second wall portion 114 have been verified to provide an optimal boiling space for the working fluid. In addition to enhancing the boiling ability of the cooling fluid F, the core region 134 can also attract the cooling fluid F to a higher vertical position in the heat sink by capillary force, which means that only less cooling fluid F needs to be used, but still provides better heat dissipation and reduces the weight of the heat sink.

[0066] Figure 7A perspective side view of a heat sink 300 is shown comprising five separate two-phase heat sinks 100', 100" arranged in a stacked configuration. Figure 7 The dashed curved arrow passing through the heat source 200′ in the figure shows the internal flow of the cooling fluid F′, F″ in the corresponding two-phase radiator 100′, 100″ between the cavity 110 and the cooling fin 120. Therefore, in order to maximize the boiling and evaporation phase changes of the cooling fluid F while avoiding the drying of the liquid in the cavity 110, the radiator 300 is divided into a plurality of independent two-phase radiators 100 that can be arranged according to the heat source distribution of the radiator 300. Specifically, by setting a plurality of two-phase radiators 100 according to the distribution of the heat sources 200′, 200″, the temperature uniformity of the entire radiator 300 can be greatly improved. Therefore, the present invention discloses that the cooling fluid F′ of the first two-phase radiator 100′ is separated from the cooling fluid F″ of the second two-phase radiator 100″, and so on, which means that the cooling fluids of different cavities of different two-phase radiators 100′, 100″ are separated without any interconnection between them.

[0067] However, the general design of the heat sink 300 indicates that the first two-phase heat sink 100' and at least one second two-phase heat sink 100" have a common substrate plate 144, and further as shown in FIG. Figures 5 to 7 The mechanical connection means that there will be heat transfer between the two-phase heat sinks 100', 100".

[0068] Figure 8 An exploded perspective side view of a heat sink 300 according to an embodiment of the present invention is shown. The disclosed heat sink 300 includes a substrate plate 144 having a receiving cavity 110, a cover plate 140 for the receiving cavity, a cooling fin 120 having a roll-bonded microchannel, and a louver plate 142. The substrate plate 144, the cover plate 140, and the cooling fin 110 can be integrated by brazing, that is, each receiving cavity 110', 110" is connected to its corresponding cooling fin 120', 120", thereby ensuring a larger three-dimensional space for evaporation and condensation of the cooling fluid F. The five independent cavities 110', 110" can be arranged according to the distribution of the heat source, that is, the placement of the heat source ( Figure 8 The number, shape and volume of the independent chambers 110', 110" may vary. In addition, the partition design of the cooling fins corresponds to the partition design of each chamber to ensure that the cooling fluid of each chamber can perform condensation cycles without interfering with each other. The partition design of the cooling fins may also be changed according to the heat consumption of the corresponding one or more heat sources. In general, a region with high heat generation can be said to "borrow" the condensation space of a region with low heat generation through partitioning. Through this layout, the temperature uniformity and cooling capacity of the substrate and the cooling fins can be greatly improved.

[0069] In addition, the upper and lower side openings of the cooling fins need to be brazed with other components of the heat sink 100 to form a loop. However, according to an embodiment of the present invention, only the openings close to the substrate 144 need to be brazed with the cover plate 140. This means that the brazing area can be reduced by about 50%, and the risk of leakage of the cooling fluid F is also reduced. In addition, in the case of multiple different cavity partition designs, only one type of cooling fin can be used, which means higher flexibility and easier manufacturing, thereby reducing production costs.

[0070] Finally, it should be understood that the present invention is not limited to the embodiments described above, but also relates to and incorporates all embodiments within the scope of the attached independent claims.

Claims

1. A two-phase radiator (100) for cooling an electric heat source (200), characterized in that: The two-phase radiator (100) comprises: A chamber (110) for containing a cooling fluid (F), the chamber (110) comprising a first wall portion (112) and a second wall portion (114) disposed opposite to the first wall portion (112); a cooling fin (120) coupled to the cavity (110) so that the cooling fluid (F) can circulate between the cavity (110) and the cooling fin (120) during operation; an attachment area (132) disposed on an outer surface (112') of the first wall portion (112) and used to attach a heat source (200) to the first wall portion (112); A core region (134) for converting the cooling fluid (F) from a liquid phase to a gas phase, the core region (134) being arranged on an inner surface (112″) of the first wall portion (112), wherein the attachment region (132) and the core region (134) at least partially overlap each other.

2. The two-phase radiator (100) according to claim 1, characterized in that: The core region (134) is a porous core region.

3. The two-phase radiator (100) according to claim 1 or 2, characterized in that: The core area (134) is larger than the attachment area (132).

4. The two-phase radiator (100) according to any one of claims 1 to 3, characterized in that: The core region (134) and the attachment region (132) are aligned relative to each other.

5. The two-phase radiator (100) according to any one of claims 1 to 3, characterized in that: The core region (134) and the attachment region (132) are offset relative to each other.

6. The two-phase radiator (100) according to claim 5, characterized in that: The core region (134) is offset relative to the attachment region (132) in the direction of gravity when the two-phase heat sink (100) is in operation.

7. The two-phase radiator (100) according to any one of the preceding claims, characterized in that: The cooling fin (120) is a roll-bonded cooling fin.

8. The two-phase radiator (100) according to claim 7, characterized in that: The roll-bonded cooling fin comprises a first plate portion (126) and a second plate portion (126′) and a plurality of supporting elements (122) arranged between the first plate portion (126) and the second plate portion (126′), wherein a distance between two adjacent supporting elements (122) is in the range of 1.0 mm to 5.0 mm, preferably in the range of 3.0 mm to 4.0 mm.

9. The two-phase radiator (100) according to claim 8, characterized in that: The support element (122) is integrated with the first plate portion (126) and the second plate portion (126').

10. The two-phase radiator (100) according to claim 8 or 9, characterized in that: The cavity (110) is coupled to the roll-bonded cooling fin via one or more input / output ports (124).

11. The two-phase radiator (100) according to any one of the preceding claims, characterized in that: The distance between the core region (134) and the inner surface (114″) of the second wall portion (114) is in the range of 1.0 mm to 10.0 mm, preferably in the range of 1.5 mm to 7 mm, more preferably in the range of 1.5 mm to 5 mm.

12. The two-phase radiator (100) according to any one of the preceding claims, characterized in that: The second wall portion (114) is formed by a cover plate (140), and the cooling fins (120) extend through the cover plate (140) perpendicularly to the first wall portion (112).

13. The two-phase radiator (100) according to any one of the preceding claims, characterized in that: The second wall portion (114) is parallel to the first wall portion (112).

14. A radiator (300) for cooling an electric heat source (200), characterized in that: The radiator (300) comprises a first two-phase radiator (100') according to any one of the preceding claims and at least one second two-phase radiator (100") according to any one of the preceding claims.

15. The heat sink (300) according to claim 14, characterized in that: The cooling fluid (F') of the first two-phase radiator (100') is separated from the cooling fluid (F") of the second two-phase radiator (100") .

16. The heat sink (300) according to claim 14 or 15, characterized in that: The first two-phase heat sink (100') and the second two-phase heat sink (100") have a common substrate plate (144).

17. The heat sink (300) according to any one of claims 14 to 16, characterized in that: The first two-phase radiator (100') and the second two-phase radiator (100") are mechanically connected to each other.

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