Parallel flow channels and heat sinks

Abstract

This invention provides a parallel flow channel and a radiator, wherein the parallel flow channel includes multiple heat exchange channels, which are connected in parallel through at least two sets of flow paths; each heat exchange channel includes at least two heat exchange sub-channels, each heat exchange sub-channel in the same heat exchange channel corresponds to a set of flow paths, and each set of flow paths is connected to a corresponding heat exchange sub-channel in each heat exchange channel; each set of flow paths includes an inlet channel and an outlet channel, and the inlet channel and the outlet channel in the same set of flow paths are connected to a corresponding heat exchange sub-channel in each heat exchange channel.

Description

Technical Field

[0001] This invention relates to the field of liquid cooling technology, and more particularly to a parallel flow channel and a heat sink. Background Technology

[0002] In the existing field of heat dissipation, such as Figure 1 As shown, the system's cooling water channel has only one inlet channel 10 and one outlet channel 20. Therefore, this results in a high flow resistance in both the inlet channel 10 and the outlet channel 20. When two or more modules 30 to be cooled are connected in parallel on the cooling water channel via this single inlet channel 10 and outlet channel 20, please refer to... Figure 2 and Figure 3 This can cause uneven flow field in the module to be cooled, uneven flow distribution within the module itself, and uneven flow between modules, which in turn leads to a large temperature difference between modules and may cause the module to overheat and fail. Summary of the Invention

[0003] To address the aforementioned problems, the present invention provides a parallel flow channel comprising multiple heat exchange channels connected in parallel via at least two sets of flow paths. Each heat exchange channel includes at least two sub-channels, each sub-channel corresponding to a set of flow paths, and each set of flow paths communicating with a corresponding sub-channel within each heat exchange channel. Each set of flow paths includes an inlet channel and an outlet channel, with the inlet channel and outlet channel on the same set of flow paths communicating with a corresponding sub-channel within each heat exchange channel.

[0004] Preferably, the liquid inlet channel is provided with multiple branch outlets, each of the heat exchange sub-channels is provided with a liquid guiding inlet, and each branch outlet is connected to the corresponding liquid guiding inlet through a first liquid guiding channel.

[0005] Preferably, the liquid outlet channel is provided with multiple diversion inlets, each of the heat exchange sub-channels is provided with a liquid guide outlet, and each diversion inlet is connected to the corresponding liquid guide outlet through a second liquid guide channel.

[0006] Preferably, all the said flow paths are distributed sequentially from the outside to the inside.

[0007] Preferably, all liquid inlets and liquid outlets are distributed on both sides of the heat exchange channel, all liquid inlet channels are located on the side where the liquid inlet is located, and are distributed sequentially from the outside to the inside; all liquid outlet channels are located on the side where the liquid outlet is located, and are distributed sequentially from the outside to the inside.

[0008] Preferably, the flow directions of two adjacent heat exchange sub-channels in the same heat exchange channel are the same.

[0009] Preferably, the flow directions of two adjacent heat exchange sub-channels in the same heat exchange channel are opposite.

[0010] Preferably, two adjacent heat exchange sub-channels of the same heat exchange channel are separated by a baffle wall.

[0011] Preferably, the baffle wall is inclined, and the two adjacent heat exchange sub-channels are both gradually narrowing channels, with the liquid inlet of the heat exchange sub-channel located at the end with the larger cross-section.

[0012] Preferably, the parallel flow channel further includes a base, the base having multiple liquid inlets and multiple liquid outlets, and the base having multiple liquid inlet channels and multiple liquid outlet channels. Each liquid inlet is connected to one end of a corresponding liquid inlet channel, and each liquid outlet is connected to a corresponding liquid outlet channel. The liquid inlets of the liquid inlet channels and the liquid outlets of the liquid outlet channels on the same flow path are located on the same side or both sides of the base.

[0013] The upper surface of the base is provided with multiple mounting slots, which are configured as the heat exchange channels.

[0014] The present invention also provides a heat sink, including the above-mentioned parallel flow channels and a plurality of heat exchange modules to be cooled, wherein the plurality of heat exchange modules are respectively installed on the plurality of heat exchange flow channels.

[0015] This invention does not limit the specific type of heat sink, such as a pin fin or a plate fin.

[0016] Compared with the prior art, the present invention has the following technical advantages:

[0017] This invention significantly reduces flow resistance by adding at least one inlet flow channel and at least one outlet flow channel, achieving uniform flow distribution between modules and more uniform temperature between modules; at the same time, it improves the uniform flow distribution within the module flow channels, making the module temperature more uniform. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1This is a schematic diagram of the system's heat dissipation channels in the prior art;

[0020] Figure 2 This is a schematic diagram of the structure of the heat dissipation module installed on the system cooling water channel in the prior art;

[0021] Figure 3 This is a flow distribution diagram of each heat dissipation module installed on the system cooling water channel in the prior art;

[0022] Figure 4 This is a flow resistance distribution diagram of the parallel flow channel provided in Embodiment 1 of the present invention;

[0023] Figure 5 This is a perspective view of the parallel flow channel provided in Embodiment 1 of the present invention;

[0024] Figure 6 This is a plan view of the parallel flow channel provided in Embodiment 1 of the present invention;

[0025] Figure 7 This is a schematic diagram of the cross-sectional structure of the parallel flow channel provided in Embodiment 1 of the present invention;

[0026] Figure 8 This is a schematic diagram of the structure of the parallel flow channel in cross section 2 provided in Embodiment 1 of the present invention;

[0027] Figure 9 This is a schematic diagram of the parallel flow channel (with bends) provided in Embodiment 1 of the present invention;

[0028] Figure 10 This is a flow diagram showing the flow directions of two adjacent heat exchange sub-channels in the same adjacent heat exchange channel provided in Embodiment 1 of the present invention.

[0029] Figure 11 This is a schematic diagram of a structure in Embodiment 1 of the present invention, which shows a baffle wall between two adjacent heat exchange sub-channels in the same adjacent heat exchange channel.

[0030] Figure 12 This is a structural schematic diagram of the cross-section 3 of the parallel flow channel provided in Embodiment 1 of the present invention;

[0031] Figure 13 This is a structural schematic diagram of the cross-section 4 of the parallel flow channel provided in Embodiment 1 of the present invention;

[0032] Figure 14 This is a schematic diagram of the structure of the heat dissipation module installed on the system cooling water channel according to Embodiment 1 of the present invention;

[0033] Figure 15 This is a flow distribution diagram of each heat dissipation module installed on the system cooling water channel, as provided in Embodiment 1 of the present invention;

[0034] Figure 16 This is a front view of the parallel flow channel provided in Embodiment 2 of the present invention;

[0035] Figure 17 This is a side view of the parallel flow channel provided in Embodiment 2 of the present invention. Detailed Implementation

[0036] The present invention provides a parallel flow channel, including multiple heat exchange channels, which are two or more heat exchange channels connected in parallel through at least two sets of flow paths: each heat exchange channel includes at least two heat exchange sub-channels, each heat exchange sub-channel in the same heat exchange channel corresponds to a set of flow paths, and each set of flow paths is connected to a corresponding heat exchange sub-channel in each heat exchange channel.

[0037] For ease of understanding, the heat exchange channels are numbered sequentially, such as heat exchange channel 1, ..., heat exchange channel N, where N is an integer greater than or equal to 2.

[0038] Each heat exchange channel has the same structure, and the number of heat exchange sub-channels is the same as the number of flow paths. Therefore, the heat exchange sub-channels in each heat exchange channel are numbered sequentially, such as heat exchange sub-channel No. 1, ..., heat exchange sub-channel No. M, where M is an integer greater than or equal to 2.

[0039] The circulation paths are numbered sequentially, such as circulation path 1, ..., circulation path M, where M is an integer greater than or equal to 2.

[0040] Flow path 1 is connected to heat exchange sub-channel 1 in each heat exchange channel, meaning that heat exchange sub-channel 1 in each heat exchange channel is connected in parallel through flow path 1; and so on, flow path M is connected to heat exchange sub-channel M in each heat exchange channel, meaning that all heat exchange sub-channels M are connected in parallel through flow path M.

[0041] Each flow path includes an inlet channel and an outlet channel. The inlet channel is used to introduce coolant, so one end of the inlet channel has an inlet port and the other end is closed. The outlet channel is used to discharge coolant, so one end of the outlet channel has an outlet port and the other end is closed. Each inlet channel has N branch outlets, each outlet channel has N branch inlets, and each heat exchange sub-channel has a liquid guiding inlet and a liquid guiding outlet. The N branch outlets on the inlet channel of flow path 1 are connected to the liquid guiding inlet of each heat exchange sub-channel 1 through a first liquid guiding channel. The N branch inlets on the outlet channel of flow path 1 are connected to the liquid guiding outlet of each heat exchange sub-channel 1 through a second liquid guiding channel. Similarly, the N branch outlets on the inlet channel of flow path M are connected to the liquid guiding inlet of each heat exchange sub-channel M through a first liquid guiding channel. The N branch inlets on the outlet channel of flow path M are connected to the liquid guiding outlet of each heat exchange sub-channel M through a second liquid guiding channel.

[0042] This embodiment does not limit the number of liquid inlets and outlets on each heat exchanger subchannel; there can be one or more.

[0043] In this invention, all flow paths are distributed sequentially from the outside to the inside, that is, flow path 1 is located on the outermost side and corresponds to heat exchange sub-channel 1; flow path M is located on the innermost side and corresponds to heat exchange sub-channel M.

[0044] The flow directions of two adjacent heat exchange sub-channels on the same heat exchange channel can be the same or opposite. If the flow directions are the same, the two adjacent heat exchange sub-channels can be connected. If the flow directions are opposite, in order to prevent coolant short circuit (coolant entering from the liquid inlet of one heat exchange sub-channel flows out from the liquid outlet of the adjacent heat exchange sub-channel, which is a coolant short circuit), a baffle is required between the two adjacent heat exchange sub-channels.

[0045] In this invention, the number of heat exchange channels, flow paths, and heat exchange sub-channels on each heat exchange channel are all integers greater than or equal to 2, and the number of flow paths is equal to the number of heat exchange sub-channels on each heat exchange channel.

[0046] In this invention, parallel flow channels are arranged on a base. The upper surface of the base has N mounting slots, each housing a heat exchange module to be cooled. The heat exchange module can seal the opening of the mounting slot, such as through a sealing ring, welding, or other means, thereby preventing coolant overflow or leakage. These N mounting slots are designated as heat exchange channels 1, ..., and N. The base has M inlets and M outlets, and the base contains M inlet channels and M outlet channels. One end of each inlet channel is connected to an inlet, and one end of each outlet channel is connected to an outlet. The inlets and outlets of the inlet channels and outlet channels along the same flow path can be located on the same side of the base or on opposite sides.

[0047] The inlet and outlet channels can be circular pipes directly installed in the base, or they can be circular pipes separate from the base. The base has corresponding circular channels, and the circular pipes are inserted into the corresponding circular channels.

[0048] The cross-sectional areas of multiple inlet and outlet channels can be equal or unequal, and can be adjusted according to the flow distribution requirements. If the cross-sectional areas are equal, the temperature difference between modules caused by the flow distribution can meet the required target, and no additional adjustment is needed; otherwise, a more precise flow distribution adjustment can be achieved by using variable cross-sections.

[0049] The inlet and outlet areas at corresponding positions in the same heat exchange channel may be equal or unequal, and their shapes may be similar or dissimilar. However, the distribution of flow resistance along the flow direction of the inlet or outlet channel is symmetrical about the heat exchange channel axis.

[0050] Compared to existing parallel flow channels with one inlet and one outlet, this invention adds at least one inlet flow channel and at least one outlet flow channel, which has the following beneficial effects:

[0051] 1. Both the inlet and outlet flow channels have been increased by at least 100%, the speed has been reduced by at least half, the flow resistance has been reduced, the flow resistance between the heat dissipation modules is uniform, and the total pressure drop has been significantly reduced.

[0052] Taking the addition of one inlet channel and one outlet channel as an example, when the diameters of the inlet and outlet channels are equal, the flow cross-sectional area doubles, and the velocity is halved (e.g., in the prior art, the flow rate of one inlet channel is 10 L / min; in this embodiment, an additional inlet channel is added, so the flow rate of each inlet channel is 5 L / min). According to the formula hf = ζV 2 / 2g, this formula represents the friction loss along the pipeline, where ζ is the friction coefficient, V is the coolant velocity, and g is the acceleration due to gravity. Since the coolant velocity is significantly reduced, the friction loss along the pipeline decreases. According to the formula, the local resistance loss Hζ = ζV 2 / 2g, where ζ is the local resistance coefficient. Due to the significant reduction in coolant flow velocity, the local resistance loss decreases. In summary, the flow resistance of the inlet and outlet channels is reduced. This reduction in resistance of the inlet and outlet channels will result in more uniform flow resistance among the modules to be cooled.

[0053] The total pressure drop (the pressure drop between the inlet and outlet) consists of friction loss and local resistance loss. As the friction loss and local resistance loss decrease, the total pressure drop is significantly reduced, which can effectively reduce the pump's operating energy consumption and achieve energy saving.

[0054] 2. For parallel flow channels, the parallel flow characteristics between modules are K, K = (flow resistance of the first liquid guiding channel + flow resistance of the heat exchange channel + flow resistance of the second liquid guiding channel) / (flow resistance of the inlet channel or flow resistance of the outlet channel).

[0055] When K is larger, the flow distribution between modules is more uniform. That is, when the flow resistance of the inlet or outlet channel is smaller, the flow resistance of the liquid guiding channel is larger, and the flow resistance of the heat exchange channel is larger, the flow distribution between modules is more uniform.

[0056] ① Increasing the number of inlet / outlet channels reduces the fluid velocity and decreases the flow resistance of the inlet / outlet channels;

[0057] ② The increase in the number of liquid guide ports (liquid guide inlet / liquid guide outlet) reduces the total inlet / outlet flow area of ​​the heat exchange channel in a single module and increases the flow resistance of the liquid guide channel;

[0058] ③ The flow resistance of the inlet / outlet flow channel can be reduced by increasing the flow resistance of the heat exchange channel or the flow resistance of the liquid guiding channel while keeping the total flow resistance constant or reducing it.

[0059] By using the above three points, the traffic distribution between modules can be made more even. Please refer to [the relevant documentation / reference]. Figure 15 .

[0060] 3. For existing parallel flow channel single modules, due to inertia, a vortex region forms on the left side of the guide channel along the flow direction of the inlet channel. This causes the flow resistance to gradually decrease and the flow velocity to gradually increase, i.e., the flow rate to gradually increase, resulting in an uneven flow field inside the module. This application can achieve a more uniform flow field inside the module through the following points; please refer to them. Figure 15 :

[0061] ① The increase in the number of liquid guide ports (liquid guide inlet / liquid guide outlet) reduces the width of the liquid guide channel, reduces the area of ​​the vortex zone, and makes the velocity distribution of a single liquid guide port more uniform;

[0062] ② Along the flow direction of the inlet channel, the liquid guide ports are connected to the inlet channel or the outlet channel in order from the inside to the outside to form liquid guide channels. Since all the flow paths are distributed from the outside to the inside, the path of the liquid guide channel formed by connecting the liquid guide inlet of the inner M heat exchange sub-channel with the branch outlet of the inlet channel of the inner M flow path is greater than the path of the liquid guide channel formed by connecting the liquid guide inlet of the outer 1 heat exchange sub-channel with the branch outlet of the inlet channel of the 1 flow path. As the flow path increases, the flow resistance gradually increases, making the flow distribution between different liquid guide ports more uniform.

[0063] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0064] The technical solution of the present invention will be described in detail below with reference to specific embodiments. These specific embodiments can be combined with each other, and the same or similar concepts or processes may not be described again in some embodiments.

[0065] Example 1

[0066] Please refer to Figures 4 to 15 This embodiment provides a parallel flow channel, including three heat exchange channels, which are heat exchange channel 1, heat exchange channel 2, and heat exchange channel 3, respectively. Each heat exchange channel includes a heat exchange sub-channel 101 and a heat exchange sub-channel 102. The two ends of the heat exchange sub-channel 101 are respectively provided with a liquid inlet 1011 and a liquid outlet 1012, and the two ends of the heat exchange sub-channel 102 are respectively provided with a liquid inlet 2 and a liquid outlet 2.

[0067] These three heat exchange channels are connected in parallel through two sets of flow paths, namely flow path 4 (number 1) and flow path 5 (number 2). Each flow path includes an inlet channel and an outlet channel. Flow path 4 includes an inlet channel 401 and an outlet channel 406. The inlet channel 401 has three branch outlets at intervals. These three branch outlets are branch outlet 1-402, branch outlet 2, and branch outlet 3. Branch outlet 1-402 is connected to the inlet 1011 of the heat exchange sub-channel 101 of heat exchange channel 1 through the first liquid guide channel 403. Branch outlet 1-2 is connected to the inlet 1011 of the heat exchange sub-channel 101 of heat exchange channel 2 through the first liquid guide channel 2. Branch outlet 1-3 is connected to the inlet 1011 of the heat exchange sub-channel 101 of heat exchange channel 3 through the first liquid guide channel 3. Three No. 1 diversion inlets are provided at intervals on the No. 1 liquid outlet channel 406. These three No. 1 diversion inlets are No. 1 diversion inlet one 405, No. 1 diversion inlet two, and No. 1 diversion inlet three. No. 1 diversion inlet one 405 is connected to the No. 1 liquid outlet 1012 of the No. 1 heat exchange sub-channel 101 of the No. 1 heat exchange channel 1 through No. 1 second liquid guide channel one 404. No. 1 diversion inlet two is connected to the No. 1 liquid outlet 1012 of the No. 1 heat exchange sub-channel 101 of the No. 2 heat exchange channel 2 through No. 1 second liquid guide channel two. No. 1 diversion inlet three is connected to the No. 1 liquid outlet 1012 of the No. 1 heat exchange sub-channel 101 of the No. 3 heat exchange channel 3 through No. 1 second liquid guide channel three.

[0068] Similarly, flow path 5 includes inlet channel 501 and outlet channel 506. Inlet channel 501 has three branch outlets at intervals. These three branch outlets are branch outlet 1 502, branch outlet 2 2 and branch outlet 3. Branch outlet 1 502 is connected to the inlet 1021 of heat exchange sub-channel 102 of heat exchange channel 1 through first liquid guide channel 1 503. Branch outlet 2 2 is connected to the inlet 1021 of heat exchange sub-channel 102 of heat exchange channel 2 through first liquid guide channel 2. Branch outlet 2 2 is connected to the inlet 2 of heat exchange sub-channel 102 of heat exchange channel 2 through first liquid guide channel 2. Branch outlet 3 2 is connected to the inlet 2 of heat exchange sub-channel 102 of heat exchange channel 3 through first liquid guide channel 3. Three No. 2 diversion inlets are provided at intervals on the No. 2 liquid outlet channel 506. These three No. 2 diversion inlets are No. 2 diversion inlet one 505, No. 2 diversion inlet two, and No. 2 diversion inlet three. No. 2 diversion inlet one 505 is connected to the No. 2 liquid outlet 1022 of the No. 2 heat exchange sub-channel 102 of the No. 1 heat exchange channel 1 through the No. 2 second liquid guide channel 504. No. 2 diversion inlet two is connected to the No. 2 liquid outlet of the No. 2 heat exchange sub-channel 102 of the No. 2 heat exchange channel 2 through the No. 2 second liquid guide channel two. No. 2 diversion inlet three is connected to the No. 2 liquid outlet of the No. 2 heat exchange sub-channel 102 of the No. 3 heat exchange channel 3 through the No. 2 second liquid guide channel three.

[0069] In this embodiment, parallel flow channels are arranged on a base 6. Three mounting slots are provided on the upper surface of the base 6. The heat exchange module 9 to be cooled is installed in each of these mounting slots. The heat exchange module 9 can seal the opening of the mounting slot, such as through a sealing ring, welding, or other means, thereby preventing coolant overflow or leakage. These three mounting slots are designated as heat exchange channel 1 (number 1), heat exchange channel 2 (number 2), and heat exchange channel 3 (number 3). The base 6 is provided with two liquid inlets (liquid inlet 1 and liquid inlet 2) and two liquid outlets (liquid outlet 1 and liquid outlet 2). The base 6 contains two liquid inlet channels (liquid inlet channel 1 401 and liquid inlet channel 2 501) and two liquid outlet channels (liquid outlet channel 1 406 and liquid outlet channel 2 506). Liquid inlet 1 is connected to one end of liquid inlet channel 1 401, liquid inlet 2 is connected to one end of liquid inlet channel 2 501, liquid outlet 1 is connected to one end of liquid outlet channel 1, and liquid outlet 2 is connected to one end of liquid outlet channel 2. The liquid inlets of the liquid inlet channels and the liquid outlets of the liquid outlet channels on the same flow path can be located on the same side of the base 6 or on opposite sides of the base 6.

[0070] The inlet and outlet channels can be circular pipes directly opened in the base 6, or they can be circular pipes separate from the base 6. The base 6 is provided with corresponding circular channels, and the circular pipes are inserted into the corresponding circular channels.

[0071] The cross-sectional areas of multiple inlet and outlet channels can be equal or unequal, and can be adjusted according to the flow distribution requirements. If the cross-sectional areas are equal, the temperature difference between modules caused by the flow distribution can meet the required target, and no additional adjustment is needed; otherwise, a more precise flow distribution adjustment can be achieved by using variable cross-sections.

[0072] The inlet and outlet areas at corresponding positions in the same heat exchange channel may be equal or unequal, and their shapes may be similar or dissimilar. However, the distribution of flow resistance along the flow direction of the inlet or outlet channel is symmetrical about the heat exchange channel axis.

[0073] All flow paths are distributed sequentially from the outside to the inside. In one implementation, the flow directions of two adjacent heat exchange sub-channels within the same heat exchange channel are the same. That is, in the same heat exchange channel, the liquid inlets of all heat exchange sub-channels are located on the same side of the heat exchange channel, and all liquid inlet channels are located on the side where the liquid inlet is located, distributed sequentially from the outside to the inside. The liquid outlets of all heat exchange sub-channels are located on the other side of the heat exchange channel, and all liquid outlet channels are located on the side where the liquid outlet is located, distributed sequentially from the outside to the inside. All flow paths are distributed sequentially from the outside to the inside; that is, the liquid inlet channel of flow path 4 is located outside the liquid inlet channel of flow path 5, and the liquid outlet channel of flow path 4 is located outside the liquid outlet channel of flow path 5. In this embodiment, the length of the first liquid guiding channel 503 of the second flow path 5 on the inner side is greater than the length of the first liquid guiding channel 403 of the first flow path 4 on the outer side, and the length of the second liquid guiding channel 504 of the second flow path 5 on the inner side is greater than the second liquid guiding channel 404 of the first flow path 4 on the outer side. Due to the increase in the flow path, the flow resistance gradually increases, making the flow distribution between different liquid guiding ports (liquid guiding inlet or liquid guiding outlet) more uniform.

[0074] Compared to existing parallel flow channels with one inlet and one outlet, this invention adds at least one inlet flow channel and at least one outlet flow channel, which has the following beneficial effects:

[0075] 1. Both the inlet and outlet flow channels have been increased by at least 100%, the speed has been reduced by at least half, the flow resistance has been reduced, the flow resistance between the heat dissipation modules is uniform, and the total pressure drop has been significantly reduced.

[0076] This embodiment adds one inlet channel and one outlet channel. When the diameters of the inlet and outlet channels are equal, the flow cross-sectional area is doubled, and the velocity is halved (e.g., in the prior art, the flow rate of one inlet channel is 10 L / min; in this embodiment, with the addition of an inlet channel, the flow rate of each inlet channel is 5 L / min). According to the formula hf = ζV 2 / 2g, this formula represents the friction loss along the pipeline, where ζ is the friction coefficient, V is the coolant velocity, and g is the acceleration due to gravity. Since the coolant velocity is significantly reduced, the friction loss along the pipeline decreases. According to the formula, the local resistance loss Hζ = ζV 2 / 2g, where ζ is the local resistance coefficient. Due to the significant reduction in coolant flow velocity, the local resistance loss decreases. In summary, the flow resistance of the inlet and outlet channels is reduced. This reduction in resistance of the inlet and outlet channels will result in more uniform flow resistance among the modules to be cooled.

[0077] The total pressure drop (the pressure drop between the inlet and outlet) consists of friction loss and local resistance loss. As the friction loss and local resistance loss decrease, the total pressure drop is significantly reduced, which can effectively reduce the pump's operating energy consumption and achieve energy saving.

[0078] 2. For parallel flow channels, the parallel flow characteristics between modules are K, K = (flow resistance of the first liquid guiding channel 403 + flow resistance of the heat exchange channel 1 + flow resistance of the second liquid guiding channel 404) / (flow resistance of the inlet channel 401 or the flow resistance of the outlet channel 406).

[0079] When K is larger, the flow distribution between modules is more uniform. That is, when the flow resistance of the inlet or outlet channel is smaller, the flow resistance of the liquid guiding channel is larger, and the flow resistance of the heat exchange channel is larger, the flow distribution between modules is more uniform.

[0080] ① Increasing the number of inlet / outlet channels reduces the fluid velocity and decreases the flow resistance of the inlet / outlet channels;

[0081] ② The increase in the number of liquid guide ports (liquid guide inlet / liquid guide outlet) reduces the total inlet / outlet flow area of ​​the heat exchange channel in a single module and increases the flow resistance of the liquid guide channel;

[0082] ③ The flow resistance of the inlet / outlet flow channel can be reduced by increasing the flow resistance of the heat exchange channel or the flow resistance of the liquid guiding channel while keeping the total flow resistance constant or reducing it.

[0083] The above three points make the flow distribution between modules more even.

[0084] 3. For existing parallel flow channel single modules, due to inertia, a vortex region forms on the left side of the guide channel along the flow direction of the inlet channel, causing the flow resistance to gradually decrease and the flow velocity to gradually increase, i.e., the flow rate to gradually increase, resulting in an uneven flow field inside the module. This application can achieve a more uniform flow field inside the module through the following points:

[0085] ① The increase in the number of liquid guide ports (liquid guide inlet / liquid guide outlet) reduces the width of the liquid guide channel, reduces the area of ​​the vortex zone, and makes the velocity distribution of a single liquid guide port more uniform;

[0086] ② Along the flow direction of the inlet channel, the liquid guide ports are connected to the inlet channel or the outlet channel in order from the inside to the outside to form liquid guide channels. Since all the flow paths are distributed from the outside to the inside, the path of the liquid guide channel formed by connecting the liquid guide inlet of the inner M heat exchange sub-channel with the branch outlet of the inlet channel of the inner M flow path is greater than the path of the liquid guide channel formed by connecting the liquid guide inlet of the outer 1 heat exchange sub-channel with the branch outlet of the inlet channel of the 1 flow path. As the flow path increases, the flow resistance gradually increases, making the flow distribution between different liquid guide ports more uniform.

[0087] 4. In practical applications of flow channels, for the sake of compact structure and space saving, there may be bends or angles in the pipes, such as... Figure 9 As shown, the present invention can significantly reduce local losses in bends and folds by diverting the flow (e.g., in the prior art, the flow rate of one inlet channel is 10L / min, while in this embodiment, an additional inlet channel is added, so the flow rate of each inlet channel is 5L / min).

[0088] In an embodiment where two adjacent heat exchange sub-channels of the same heat exchange channel have the same flow direction, the two adjacent heat exchange sub-channels may or may not be separated by a baffle wall.

[0089] Please refer to Figures 10 to 13 In another implementation, if the flow directions of two adjacent heat exchange sub-channels in the same heat exchange channel are opposite, then the coolant entering from the liquid inlet of one heat exchange sub-channel can easily flow out from the liquid outlet of the adjacent heat exchange sub-channel, which will cause a coolant short circuit. Therefore, a baffle 7 needs to be set between two adjacent heat exchange sub-channels.

[0090] In this embodiment, the coolant flows in opposite directions, which reduces the impact of thermal cascading and results in a more uniform temperature distribution within the module. The baffle 7 can be parallel to the flow direction or at a certain angle to the flow direction.

[0091] The heat exchanger channel can be a channel with a constant cross-section or a variable cross-section. The cross-sectional area gradually decreases along the flow direction, which can further improve the flow uniformity.

[0092] When the baffle 7 is at a certain angle to the flow direction (e.g., 0 to 90°), the two adjacent heat exchange sub-channels are both gradually narrowing channels, with the liquid inlet of the heat exchange sub-channel located at the end with the larger cross-section. As the coolant flows, the channel area gradually decreases, the flow velocity gradually increases, and the heat transfer coefficient gradually increases, which can reduce the impact of thermal cascading. At the same time, the flow field distribution within the module will be more uniform (along the flow direction, the flow distance gradually increases, and the flow resistance gradually increases).

[0093] Example 2

[0094] Please refer to Figure 16 and Figure 17 In this embodiment, an additional flow path is added based on embodiment 1. Thus, each heat exchange channel is supplemented with a heat exchange sub-channel. That is, each heat exchange channel includes heat exchange sub-channel 101, heat exchange sub-channel 102 and heat exchange sub-channel 103. Heat exchange sub-channel 103 has a liquid inlet and a liquid outlet at both ends.

[0095] The No. 3 flow path includes the No. 3 liquid inlet channel 801 and the No. 3 liquid outlet channel 802. The No. 3 liquid inlet channel 801 is provided with three No. 3 diversion outlets at intervals. These three No. 3 diversion outlets are No. 3 diversion outlet one, No. 3 diversion outlet two, and No. 3 diversion outlet three. No. 3 diversion outlet one is connected to the No. 3 liquid inlet of the No. 3 heat exchange sub-channel 103 of the No. 1 heat exchange channel through the No. 3 first liquid guide channel one. No. 3 diversion outlet two is connected to the No. 3 liquid guide inlet of the No. 3 heat exchange sub-channel 103 of the No. 2 heat exchange channel through the No. 3 first liquid guide channel three. No. 3 diversion outlet three is connected to the No. 3 liquid guide inlet of the No. 3 heat exchange sub-channel 103 of the No. 3 heat exchange channel 3 through the No. 3 first liquid guide channel three. Three No. 3 diversion inlets are provided at intervals on the No. 3 liquid outlet channel 802. These three No. 3 diversion inlets are No. 3 diversion inlet one, No. 3 diversion inlet two, and No. 3 diversion inlet three. No. 3 diversion inlet one is connected to the No. 3 liquid outlet of the No. 3 heat exchange sub-channel 103 of the No. 1 heat exchange channel 1 through No. 3 second liquid guide channel one. No. 3 diversion inlet two is connected to the No. 3 liquid outlet of the No. 3 heat exchange sub-channel 103 of the No. 2 heat exchange channel 2 through No. 3 second liquid guide channel two. No. 3 diversion inlet three is connected to the No. 3 liquid outlet of the No. 3 heat exchange sub-channel 103 of the No. 3 heat exchange channel 3 through No. 3 second liquid guide channel three.

[0096] This embodiment uses three sets of flow paths (including three inlet channels and three outlet channels) connected in parallel to form three heat exchange channels. This results in lower flow resistance in the heat exchange channels and a more uniform flow field and temperature distribution between the heat exchange channels. To further achieve this technical effect, the pipe diameters of the inlet and outlet channels can be reduced.

[0097] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A parallel flow channel, characterized by, The system includes multiple heat exchange channels connected in parallel via at least two sets of flow paths. Each heat exchange channel includes at least two sub-channels. Each sub-channel in the same heat exchange channel corresponds to one set of flow paths. Each set of flow paths is connected to one of the corresponding sub-channels in the same heat exchange channel. The flow directions of two adjacent sub-channels in the same heat exchange channel are opposite. Two adjacent sub-channels in the same heat exchange channel are separated by a baffle wall, which is inclined. Both adjacent sub-channels are gradually narrowing channels, and the liquid inlet of each sub-channel is located at the end with the larger cross-section. Each set of flow paths includes an inlet channel and an outlet channel. The inlet channel and outlet channel in the same set of flow paths are connected to one of the corresponding sub-channels in the same heat exchange channel.

2. The parallel flow passage of claim 1 wherein, The liquid inlet channel is provided with multiple branch outlets, and each of the heat exchange sub-channels is provided with a liquid guiding inlet. Each branch outlet is connected to the corresponding liquid guiding inlet through a first liquid guiding channel.

3. The parallel flow passage of claim 2 wherein, The liquid outlet channel is provided with multiple diversion inlets, and each of the heat exchange sub-channels is provided with a liquid guide outlet. Each diversion inlet is connected to the corresponding liquid guide outlet through a second liquid guide channel.

4. The parallel flow channel according to claim 3, characterized in that, All the aforementioned flow paths are distributed sequentially from the outside in.

5. The parallel flow channel according to claim 4, characterized in that, All liquid inlets and outlets are distributed on both sides of the heat exchange channel. All liquid inlet channels are located on the side where the liquid inlet is located, and are distributed sequentially from the outside to the inside. All liquid outlet channels are located on the side where the liquid outlet is located, and are distributed sequentially from the outside to the inside.

6. The parallel flow channel according to claim 1, characterized in that, It also includes a base, on which multiple liquid inlets and multiple liquid outlets are provided. The base contains multiple liquid inlet channels and multiple liquid outlet channels. Each liquid inlet is connected to one end of a corresponding liquid inlet channel, and each liquid outlet is connected to a corresponding liquid outlet channel. The liquid inlets of the liquid inlet channels and the liquid outlets of the liquid outlet channels on the same flow path are located on the same side or both sides of the base. The upper surface of the base is provided with multiple mounting slots, which are configured as the heat exchange channels.

7. A radiator, characterized in that, It includes the parallel flow channels as described in any one of claims 1 to 6 and a plurality of heat exchange modules to be cooled, wherein the plurality of heat exchange modules to be cooled are respectively installed on the plurality of heat exchange flow channels.

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