Multi-cooling working medium parallel heat exchanger and nuclear power system

Abstract

The invention discloses a multi-cooling-medium parallel heat exchanger and a nuclear power system. The multi-cooling-medium parallel heat exchanger comprises a main body, channel partition plates and protruding parts. An accommodating space is formed in the main body; the channel partition plates are arranged in the containing space so as to isolate a plurality of working medium channels distributed in parallel in the containing space, the working medium channels comprise cooling working medium channels and high-temperature working medium channels, and the high-temperature working medium channels are located among the cooling working medium channels in which different cooling working media circulate; the protruding parts are arranged on the channel partition plates corresponding to the high-temperature working medium channels, and the geometric parameters of the protruding parts making contact with different cooling working media are different so that the different cooling working media can meet the working temperature intervals of the different cooling working media. According to the heat exchanger, under the condition that the macroscopic size of the channel and the material characteristics are not changed, synchronous heat transfer of one high-temperature working medium to multiple refrigerating working media can be achieved, the purpose of synchronous heat exchange through different cooling working media is achieved, the energy utilization efficiency is improved, and the operation cost is reduced.

Description

Technical Field

[0001] The present application relates to the technical field of nuclear power heat exchangers, and particularly to a multi-coolant parallel heat exchanger and a nuclear power system. Background Art

[0002] In industrial fields such as refrigeration, power generation, and high-performance computing, heat exchange equipment has always been the focus of research. Conventional heat exchangers generally only use one high-temperature working fluid and one cooling working fluid, and achieve heat transfer through convective heat transfer and heat conduction from high temperature to low temperature. To maximize the utilization of heat, a series connection of multiple heat exchangers is usually adopted to achieve heat exchange between one high-temperature working fluid and different cooling working fluids in sequence.

[0003] However, since different cooling working fluids often have different working temperature ranges, the differences in the physical properties of the two refrigerants will cause that during the synchronous heat transfer process, often one of the cooling working fluids will exceed its working temperature range after receiving the heat from the high-temperature working fluid. Therefore, it is actually difficult to simply set up parallel channels to enable the high-temperature working fluid to transfer heat to different cooling working fluids simultaneously. Summary of the Invention

[0004] In view of this, the present application provides a multi-coolant parallel heat exchanger and a nuclear power system, which realizes the synchronous heat transfer from a high-temperature working fluid to two cooling working fluids without changing the macroscopic magnitude of the single-channel flow of the two cooling working fluids.

[0005] According to one aspect of the present application, a multi-coolant parallel heat exchanger is provided. The heat exchanger includes:

[0006] A main body having an accommodation space therein;

[0007] A channel partition disposed in the accommodation space to isolate a plurality of juxtaposed working fluid channels in the accommodation space. The plurality of working fluid channels include a cooling working fluid channel and a high-temperature working fluid channel, and the high-temperature working fluid channel is located between the cooling working fluid channels through which different cooling working fluids flow;

[0008] A protrusion provided on the channel partition corresponding to the high-temperature working fluid channel, and the geometric parameters of the protrusion in contact with different cooling working fluids are different, so that different cooling working fluids meet their working temperature ranges.

[0009] Optionally, the heat exchanger further includes:

[0010] A partition connection part provided on the main body and located in the accommodation space, and the channel partition is detachably connected to the partition connection part to form the working fluid channels;

[0011] A seal is provided between the partition connection part and the channel partition.

[0012] Optionally, the heat exchanger further includes: a high-temperature working fluid inlet pipe, a high-temperature working fluid outlet pipe, a cooling working fluid inlet pipe, and a cooling working fluid outlet pipe;

[0013] The high-temperature working fluid inlet pipe and the high-temperature working fluid outlet pipe are in communication with the high-temperature working fluid channel, the cooling working fluid inlet pipe and the cooling working fluid outlet pipe are in communication with the cooling working fluid channel, the high-temperature working fluid inlet pipe is disposed close to the cooling working fluid outlet pipe, and the high-temperature working fluid outlet pipe is disposed close to the cooling working fluid inlet pipe, so that the flow directions of the high-temperature working fluid and the cooling working fluid are opposite.

[0014] Optionally, the heat exchanger further includes:

[0015] A temperature sensor for detecting the inlet temperature and the outlet temperature of the cooling working fluid, and the extreme values of the working temperature range of the cooling working fluid are the target cooling working fluid inlet temperature and the target cooling working fluid outlet temperature, respectively.

[0016] Optionally, the convex portion is configured as a polyhedral structure, and the geometric parameters of the convex portion include the size of the convex portion and the periodic pitch of the convex portion.

[0017] Optionally, the cooling working fluid channel and the high-temperature working fluid channel have the same size, and the geometric parameters of the convex portion satisfy the following formula:

[0018]

[0019] where a 1 and a 2 are the lengths of the convex portions in contact with the first cooling working fluid and the second cooling working fluid, respectively, b 1 and b 2 are the widths of the convex portions in contact with the first cooling working fluid and the second cooling working fluid, respectively, h 1 and h 2 are the heights of the convex portions in contact with the first cooling working fluid and the second cooling working fluid, respectively, d 1 and d 2 are the periodic pitches of the convex portions in contact with the first cooling working fluid and the second cooling working fluid, respectively, T i1 and T o1 are the extreme values of the working temperature range of the first cooling working fluid, T i2 and T o2 are the extreme values of the working temperature range of the second cooling working fluid, c 1 and c 2 are the specific heat capacities at constant pressure of the first cooling working fluid and the second cooling working fluid, respectively, w 1 and w2 are the flow rates of the first cooling working fluid and the second cooling working fluid respectively, is the temperature of the high-temperature working fluid.

[0020] Optionally, the length, width, and height of the raised portion are all less than 100 μm.

[0021] Optionally, multiple said channel partitions are made of the same material; the raised portion is made by femtosecond laser technology.

[0022] According to another aspect of the present application, a nuclear power system is provided, including the above multi-cooling working fluid parallel heat exchanger.

[0023] By means of the above technical solution, the geometric parameters of the modified surface are designed according to the physical property differences of the cooling working fluids, realizing the customized regulation of the heat transfer amount from the high-temperature working fluid to multiple cooling working fluids, so that different cooling working fluids all meet the requirements of the working temperature range after receiving heat. Thus, without changing the macroscopic dimensions and material properties of the channels, the synchronous heat transfer from one high-temperature working fluid to multiple refrigeration working fluids is achieved, achieving the purpose of synchronous heat exchange using different cooling working fluids, improving the energy utilization efficiency, and reducing the operating cost.

[0024] The above description is only an overview of the technical solution of the present application. In order to be able to understand the technical means of the present application more clearly, it can be implemented according to the content of the specification. And in order to make the above and other purposes, features, and advantages of the present application more obvious and understandable, the specific embodiments of the present application are specifically exemplified below. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] The drawings described herein are used to provide a further understanding of the present application and constitute a part of the present application. The schematic embodiments of the present application and their descriptions are used to explain the present application and do not constitute an improper limitation to the present application. In the drawings:

[0026] Figure 1 shows a schematic structural diagram of the multi-cooling working fluid parallel heat exchanger provided by the embodiment of the present application;

[0027] Figure 2 shows a schematic layout diagram of the working fluid channels provided by the embodiment of the present application;

[0028] Figure 3 shows a topographic diagram of the raised portion provided by the embodiment of the present application;

[0029] Figure 4 shows a schematic structural diagram of the microstructural unit in the multi-cooling working fluid parallel heat exchanger provided by the embodiment of the present application;

[0030] Figure 5 shows a top view of the microstructural unit in the multi-cooling working fluid parallel heat exchanger provided by the embodiment of the present application;

[0031] Figure 6 The perspective view of the microstructure unit in the multi-cooling working medium parallel heat exchanger provided by the embodiment of the present application is shown.

[0032] Reference numerals:

[0033] 10 Main body, 11 Channel partition, 12 Working medium channels, 121 High-temperature working medium channel, 122 First cooling working medium channel, 123 Second cooling working medium channel, 131 High-temperature working medium inlet pipe, 132 High-temperature working medium outlet pipe, 133 Cooling working medium inlet pipe, 134 Cooling working medium outlet pipe. Detailed implementation manners

[0034] In the following, the present application will be described in detail with reference to the drawings and in conjunction with the embodiments. It should be noted that, without conflict, the embodiments in the present application and the features in the embodiments may be combined with each other.

[0035] The embodiments of the present application will be described in detail below. The examples of the embodiments are shown in the drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and are only used to explain the present application, and should not be construed as a limitation to the present application.

[0036] Those skilled in the art of the present technology can understand that, unless specifically stated otherwise, the singular forms "a", "an", "the" and "said" used herein may also include the plural forms. It should be further understood that the term "including" used in the description of the present application means the presence of the described features, integers, steps, operations, elements and / or components, but does not exclude the presence or addition of one or more other features, integers, steps, operations, elements, components and / or their groups. It should be understood that when we say an element is "connected" or "joined" to another element, it can be directly connected or joined to other elements, or there may also be intermediate elements. In addition, the "connection" or "joining" used herein may include wireless connection or wireless coupling. The term "and / or" used herein includes all or any unit and all combinations of one or more related listed items.

[0037] Now, the exemplary embodiments according to the present application will be described in more detail with reference to the drawings. However, these exemplary embodiments can be implemented in many different forms and should not be construed as being limited only to the embodiments set forth herein. It should be understood that these embodiments are provided so that the disclosure of the present application is thorough and complete, and the concept of these exemplary embodiments is fully conveyed to those of ordinary skill in the art.

[0038] In the present embodiment, a multi-cooling working medium parallel heat exchanger is provided, as Figure 1As shown, the heat exchanger includes: a main body 10, a channel partition 11 and a protrusion (not shown in the figure).

[0039] The main body is provided with a solid wall surface, and the solid wall surface encloses a containing space. A channel partition 11 is arranged in the containing space to isolate a plurality of parallel working medium channels 12 in the containing space. The raised portion is arranged on the channel partition 11 corresponding to the working medium channel 12 where the high-temperature working medium flows, and the raised portion in contact with different cooling working mediums has different geometric parameters, so that different cooling working mediums meet their working temperature ranges.

[0040] Specifically, Figure 2 As shown, the multiple working fluid channels are in a rectangular structure, and the multiple working fluid channels include cooling working fluid channels (122, 123) and a high-temperature working fluid channel 121. The cooling working fluid channels (122, 123) can be set to at least two according to different types of cooling working fluids. The high-temperature working fluid channel 121 is located between the cooling working fluid channels (122, 123) in which different cooling working fluids flow, that is, the channel partitions constituting the high-temperature working fluid channel 121 are in contact with different cooling working fluids respectively, so that the high-temperature working fluid can exchange heat with multiple different cooling working fluids at the same time.

[0041] The extreme values ​​of the working temperature range of the cooling medium can be the target cooling medium inlet temperature and the target cooling medium outlet temperature required by the user, which is not specifically limited in the embodiments of the present application. For example, under normal pressure, the working temperature range of liquid water is 0-100°C, and the working temperature range of liquid organic medium is 0-65°C.

[0042] It is understandable that for high-temperature working fluids flowing in different high-temperature working fluid channels, the multiple cooling working fluids for heat exchange therewith may be the same or different. For any high-temperature working fluid, the multiple cooling working fluids for heat exchange therewith are different. For example, high-temperature working fluid 1 is heat exchanged by cooling working fluid 1 and cooling working fluid 2, and high-temperature working fluid 2 is heat exchanged by cooling working fluid 2 and cooling working fluid 3.

[0043] It should be noted that the present application does not specifically limit the position and number of the working fluid channels provided in the main body. Taking the provision of five working fluid channels as an example, in one embodiment, Figure 2 As shown, a 3+2 layout can be adopted, so that the high-temperature working medium channel 121 is sandwiched between the first cooling working medium channel 122 and the first cooling working medium channel 123, so that the high-temperature working medium can exchange heat with the first cooling working medium and the second cooling working medium at the same time. In another embodiment, a layout can also be adopted in which four cooling working medium channels surround the high-temperature working medium channel of equal width and height structure.

[0044] The parallel heat exchanger with multiple cooling working fluids provided by the embodiments of the present application designs the geometric parameters of the modified surface according to the physical property differences of the cooling working fluids, realizes the customized regulation of the heat transfer amount from the high-temperature working fluid to multiple cooling working fluids, and enables different cooling working fluids to meet the requirements of the working temperature range after receiving heat. Thus, without changing the macroscopic size (>1 mm) of the channel and the material properties, the synchronous heat transfer from one high-temperature working fluid to multiple refrigeration working fluids is achieved, the purpose of synchronous heat exchange using different cooling working fluids is realized, the energy utilization efficiency is improved, and the operation cost is reduced.

[0045] In one embodiment, as Figure 3 、 Figure 4 、 Figure 5 shown, the convex part is configured as a polyhedron structure.

[0046] Specifically, the polyhedron structure includes a square column convex, a conical convex, etc.

[0047] In this embodiment, by manufacturing the convex part of the polyhedron structure on the channel partition, the heat transfer surface area can be increased, the heat transfer efficiency can be improved, and further the energy utilization rate can be improved and the operation cost can be reduced. Moreover, the polyhedron structure can better optimize the flow path of the working fluid, play a role in disturbing the flow of the working fluid, enhance the turbulent effect during the flow of the working fluid, reduce the flow dead zone, make the heat exchange of the working fluid more uniform, and further improve the heat exchange performance.

[0048] Specifically, the geometric parameters of the convex part include the size of the convex part and the periodic pitch of the convex part, and the unit of the geometric parameters is μm. As Figure 3 、 Figure 4 and Figure 5 shown, taking the convex part as a square column convex as an example, the size of the convex part includes the length a of the convex part, the width b of the convex part, the depth (height h) from the bottom surface of the convex part to the upper surface, and the periodic pitch of the convex part (the length / width of the convex part + the gap width between two convex parts).

[0049] It can be understood that the number of convex parts on the channel partition can be reasonably set according to the heat exchange requirements. Multiple convex parts are evenly distributed on the channel partition to facilitate the control of the heat transfer surface area of the channel partition.

[0050] It is worth mentioning that multiple convex parts can be manufactured on the channel partition by femtosecond laser technology. The femtosecond laser technology has high processing accuracy and can manufacture convex parts with complex shapes and micron or even nanometer-level processing accuracy, so as to control the modification and optimization of the channel partition within 1 mm range, so that as many original pipelines, interfaces and installation structures as possible can be retained, saving the cost and time of re-design, and taking into account the optimization convenience and cost while improving the heat exchange efficiency of the heat exchanger.

[0051] Among them, femtosecond laser is a kind of ultra-short pulse laser, and the pulse duration is in the femtosecond order of magnitude (1 femtosecond = 10 -15 seconds).

[0052] Furthermore, the channel partition for heat exchange includes two contact surfaces that can contact the working medium. The channel partition can be provided with hollow protrusions only on one of the contact surfaces to increase the heat exchange area of the two working media in contact with it at the same time. For example, the surfaces of the two channel partitions in contact with the high-temperature working medium are respectively called surface A and surface B (surface A is the heat exchange surface of the first cooling working medium, and surface B is the heat exchange surface of the second cooling working medium). The surface in contact with the first cooling working medium in these two channel partitions is called surface C1, and the surface in contact with the second cooling working medium is called surface C2. If surface A / B is a modified surface treated by femtosecond laser, surface C1 / C2 does not need laser treatment. If surface C1 / C2 is a modified surface treated by femtosecond laser, surface A / B does not need laser treatment.

[0053] Taking the Figure 2 middle channel layout and the protrusion being configured as a square column protrusion as an example. When the sizes of the cooling working medium channels and the high-temperature working medium channels and the materials used in manufacturing are the same, the heat transfer coefficients of the different channel partitions corresponding to the high-temperature working medium are the same, and the heat exchange areas of the two cooling working medium channels are also equal. If the working temperature range of the first cooling working medium of the heat exchanger is (T i1 , T o1 ), and the working temperature range of the second cooling working medium is (T i2 , T o2 ), then the heat transfer capacities that the first cooling working medium and the second cooling working medium can bear are respectively: P w1 = c 1 w 1 (T o1 - T i1 ), P w2 = c 2 w 2 (T o2 - T i2 ).

[0054] From this, the ratio of the heat flux density q obtained by the two cooling working media can be calculated as:

[0055]

[0056] In the formula, c 1 , c 2 are the specific heat capacities at constant pressure of the first cooling working medium and the second cooling working medium respectively, w 1 , w 2 are the flow rates of the first cooling working medium and the second cooling working medium respectively, T i1 , T o1 are the extreme values of the working temperature range of the first cooling working medium, Ti2 and T o2 is the extreme value of the working temperature range of the second cooling working fluid.

[0057] The heat flux density q obtained from these two cooling working fluids is also the ratio of the heat transfer amount between the A surface of the high-temperature working fluid channel close to the first cooling working fluid channel and the B surface of the high-temperature working fluid channel close to the second cooling working fluid channel. According to the heat transfer amount formula, the heat transfer amount Q has the following relationship with the heat transfer coefficient K, the heat transfer area S, and the temperature difference △T:

[0058] Q = K × S × △T.

[0059] Therefore, the heat transfer amount ratio of the modified A / B surface should satisfy:

[0060]

[0061] Since the materials of the A / B surface are the same, the heat transfer coefficient K from the high-temperature working fluid to the A / B surface is the same. Then, according to the working temperature ranges of each working fluid, the high-temperature working fluid temperature and the difference △T 1 between the average temperatures of the two cooling working fluids 2 are:

[0062]

[0063] Therefore, to achieve customized heat transfer from the high-temperature working fluid to the first cooling working fluid and the second cooling working fluid, it is necessary to control the heat transfer area ratio of the A / B surface, which is:

[0064]

[0065] As Figure 4 and Figure 6 shown, for the surface with square column protrusions after modification, taking four square column protrusions as a microstructural unit for heat transfer area calculation, the heat transfer area of the microstructural unit is divided into one bottom contact surface, 4 top contact surfaces, and 8 lateral contact surfaces. The total area of the top contact surface and the bottom contact surface constitutes a rectangle with an area of (a + d) × (b + d). According to the microstructural size parameters, the heat transfer area of the working fluid for one unit micro-structure (unit: m 2 ) is:

[0066] A = (a + d) × (b + d) + 4ah + 4bh.

[0067] On the unit area, the distribution density of the above microstructural unit (unit: m -2 ) is:

[0068]

[0069] Then, under the condition of the same area, the heat transfer area ratio of the A / B surface is:

[0070]

[0071] An equation relationship is established through the heat transfer area ratio of the A / B sides as follows:

[0072]

[0073] In the formula, a 1 and a 2 are the lengths of the protrusions in contact with the first cooling medium and the second cooling medium respectively (unit: μm), b 1 and b 2 are the widths of the protrusions in contact with the first cooling medium and the second cooling medium respectively (unit: μm), h 1 and h 2 are the heights of the protrusions in contact with the first cooling medium and the second cooling medium respectively (unit: μm), d 1 and d 2 are the periodic spacings of the protrusions in contact with the first cooling medium and the second cooling medium respectively (unit: μm), T i1 and T o1 are the extreme values of the working temperature range of the first cooling medium (unit: °C), T i2 and T o2 are the extreme values of the working temperature range of the second cooling medium (unit: °C), c 1 and c 2 are the specific heat capacities at constant pressure of the first cooling medium and the second cooling medium respectively (unit: kJ / (kg°C)), w 1 and w 2 are the flow rates of the first cooling medium and the second cooling medium respectively (unit: kg / h), is the temperature of the high-temperature medium (unit: °C).

[0074] It can be seen that when designing the heat exchanger structure, based on different cooling media, the working temperature ranges, flow rates, and physical properties of the high-temperature medium, on the basis of laser modification, by controlling the geometric parameters of the microstructures to satisfy the following formula, a multi-cooling-medium parallel rectangular channel heat exchanger structure with synchronized heat transfer capacity matching can be obtained, meeting the purpose of synchronous heat exchange using different cooling media.

[0075] In one embodiment, the lengths, widths, and heights of the protrusions can be controlled to be less than 100 μm, so that the optimization of the heat exchanger does not rely on changing the macroscopic scale dimensions of a single channel (>1 mm), and the original pipelines, interfaces, and installation structures can be retained, saving the cost and time of re-design. Moreover, the micron-scale structure can avoid energy loss caused by too large a structure, contributing to improving the heat transfer efficiency.

[0076] In one embodiment, the heat exchanger further includes: a partition connecting portion and a seal.

[0077] Wherein, the partition connecting portion is disposed on the main body and is located in the accommodating space. The channel partition is detachably connected to the partition connecting portion to form a working medium channel. The seal is disposed between the partition connecting portion and the channel partition.

[0078] In this embodiment, by providing the partition connecting portion, the channel partition can be detachably connected in the main body. This is not only convenient for regular cleaning or replacement to prevent dirt or deposits from affecting the heat exchange efficiency, but also can conveniently adjust the layout of the working medium channel according to the actual required cooling working medium without affecting the synchronous heat transfer of different cooling working media, improving the flexibility of the multi-cooling working medium parallel heat exchanger, facilitating expansion or transformation to adapt to different process requirements. At the same time, the detachable design of the partition allows the channel partition to have a certain degree of freedom during thermal expansion or contraction, reducing the influence of thermal stress on the main body structure and helping to extend the service life of the heat exchanger.

[0079] Furthermore, a seal is provided between the partition connecting portion and the channel partition. By sealing the detachable connection gap between the partition connecting portion and the channel partition, the leakage of the working medium can be effectively prevented, ensuring that the two working media flow in their respective channels, so that the working medium will not be short-circuited or mixed, and ensuring the effectiveness and safety of heat transfer.

[0080] Specifically, the seal can be a sealing gasket or a sealing strip.

[0081] In one embodiment, as Figure 1 shown, the heat exchanger further includes: a high-temperature working medium inlet pipe 131, a high-temperature working medium outlet pipe 132, a cooling working medium inlet pipe 133, and a cooling working medium outlet pipe 134.

[0082] Wherein, a working medium inlet and a working medium outlet are opened at both ends of each working medium channel 12, and the working medium inlet and the working medium outlet are connected by pipelines to form a high-temperature working medium inlet pipe 131, a high-temperature working medium outlet pipe 132, a cooling working medium inlet pipe 133, and a cooling working medium outlet pipe 134. The high-temperature working medium inlet pipe 131 and the high-temperature working medium outlet pipe 132 are communicated with the high-temperature working medium channel 121, and the cooling working medium inlet pipe 133 and the cooling working medium outlet pipe 134 are communicated with the cooling working medium channels (122, 123). And the high-temperature working medium inlet pipe 131 is disposed close to the cooling working medium outlet pipe 134, and the high-temperature working medium outlet pipe 132 is disposed close to the cooling working medium inlet pipe 133, so that the flow directions of the high-temperature working medium and the cooling working medium are opposite.

[0083] In this embodiment, a working medium inlet pipe and a working medium outlet pipe are connected to both ends of each working medium channel to ensure the fluidity of the working medium in the channel. In addition, the cooling working medium inlet pipe and the high-temperature working medium inlet pipe are arranged in reverse order to form a countercurrent arrangement of the high-temperature working medium and the cooling working medium, which not only realizes a more uniform heat transfer between the high-temperature working medium and the cooling working medium, but also enables the high-temperature working medium and the cooling working medium to always maintain a large temperature difference during the entire heat exchange process, which can make fuller use of heat, reduce energy waste, help improve heat exchange efficiency, and thus reduce the amount of cooling working medium used.

[0084] In one embodiment, the heat exchanger further includes: a temperature sensor.

[0085] Wherein, the temperature sensor can be arranged at the working medium inlet and the working medium outlet of each working medium channel, so as to detect the cooling working medium inlet temperature and the cooling working medium outlet temperature.

[0086] In this embodiment, the inlet and outlet temperatures of each working fluid channel can be monitored in real time by the temperature sensor, which facilitates the understanding of the operating status of the heat exchanger to ensure that the working fluid temperature meets the process requirements, which helps to improve product quality and process stability. At the same time, by measuring the inlet and outlet temperatures, the actual heat exchange efficiency of each working fluid channel can be calculated, and the heat exchanger structure can be optimized in time, and the flow rate, pressure or temperature of the working fluid can be adjusted, providing data support for optimized design and operation, so that the heat exchanger can operate in the best working condition.

[0087] It can be understood that when the coolant inlet temperature and the coolant outlet temperature monitored in real time by the temperature sensor are between the target coolant inlet temperature and the target coolant outlet temperature, it can be determined that the heat of the coolant bed meets its operating temperature range.

[0088] The embodiment of the present application provides a nuclear power system, which includes the above-mentioned multi-cooling medium parallel heat exchanger. The nuclear reactor core generates a large amount of heat through nuclear fission, and the heat generated by radioactive decay can be safely discharged through the heat exchanger to prevent the core from overheating and melting, thereby ensuring the operational safety of the nuclear power system.

[0089] Those skilled in the art will appreciate that the accompanying drawings are only schematic diagrams of a preferred implementation scenario, and the modules or processes in the accompanying drawings are not necessarily necessary for implementing the present application. Those skilled in the art will appreciate that the modules in the devices in the implementation scenario can be distributed in the devices of the implementation scenario according to the description of the implementation scenario, or can be changed accordingly and located in one or more devices different from the present implementation scenario. The modules of the above-mentioned implementation scenario can be combined into one module, or can be further split into multiple submodules.

[0090] The above serial numbers of this application are only for description and do not represent the advantages or disadvantages of the implementation scenarios. The above disclosure is only several specific implementation scenarios of this application. However, this application is not limited thereto, and any changes that can be conceived by those skilled in the art should fall within the protection scope of this application.

Claims

1. A multi-cooling medium parallel heat exchanger, characterized in that: The heat exchanger comprises: A main body, wherein the main body has a containing space; A channel baffle, the channel baffle being arranged in the accommodating space to isolate a plurality of parallel working medium channels in the accommodating space, the plurality of working medium channels comprising a cooling working medium channel and a high-temperature working medium channel, the high-temperature working medium channel being located between the cooling working medium channels through which different cooling working mediums flow; The raised portion is arranged on the channel partition corresponding to the high-temperature working medium channel, and the raised portion contacting different cooling working medium has different geometric parameters so that different cooling working medium can meet its working temperature range.

2. The multi-cooling medium parallel heat exchanger according to claim 1, characterized in that: The heat exchanger also includes: A partition connecting portion is provided on the main body and is located in the accommodating space, and the channel partition is detachably connected to the partition connecting portion to form the working medium channel; A sealing member is arranged between the partition connecting portion and the channel partition.

3. The multi-cooling medium parallel heat exchanger according to claim 2, characterized in that: The sealing element includes a sealing gasket or a sealing rubber strip.

4. The multi-cooling medium parallel heat exchanger according to claim 1, characterized in that: The heat exchanger further comprises: a high-temperature working medium inlet pipe and a high-temperature working medium outlet pipe, a cooling working medium inlet pipe and a cooling working medium outlet pipe; The high-temperature working fluid inlet pipe and the high-temperature working fluid outlet pipe are connected to the high-temperature working fluid channel, the cooling working fluid inlet pipe and the cooling working fluid outlet pipe are connected to the cooling working fluid channel, the high-temperature working fluid inlet pipe is arranged close to the cooling working fluid outlet pipe, and the high-temperature working fluid outlet pipe is arranged close to the cooling working fluid inlet pipe, so that the flow directions of the high-temperature working fluid and the cooling working fluid are opposite.

5. The multi-cooling medium parallel heat exchanger according to claim 1, characterized in that: The heat exchanger also includes: A temperature sensor is used to detect a cooling medium inlet temperature and a cooling medium outlet temperature, wherein the extreme values ​​of the cooling medium operating temperature range are a target cooling medium inlet temperature and a target cooling medium outlet temperature.

6. The multi-cooling medium parallel heat exchanger according to claim 1, characterized in that: The protrusions are configured as a polyhedral structure, and geometric parameters of the protrusions include the size of the protrusions and a periodic spacing of the protrusions.

7. The multi-cooling medium parallel heat exchanger according to claim 6, characterized in that: The cooling medium channel and the high temperature medium channel have the same size, and the geometric parameters of the protrusion satisfy the following formula: Wherein, a1 and a2 are the lengths of the protrusions in contact with the first coolant and the second coolant, b1 and b2 are the widths of the protrusions in contact with the first coolant and the second coolant, h1 and h2 are the heights of the protrusions in contact with the first coolant and the second coolant, d1 and d2 are the periodic spacings of the protrusions in contact with the first coolant and the second coolant, and T i1 , T o1 is the extreme value of the working temperature range of the first cooling medium, T i2 , T o2 is the extreme value of the working temperature range of the second cooling medium, c1 and c2 are the constant pressure specific heat capacities of the first cooling medium and the second cooling medium respectively, w1 and w2 are the flow rates of the first cooling medium and the second cooling medium respectively, is the temperature of the high temperature working fluid.

8. The multi-cooling medium parallel heat exchanger according to claim 6, characterized in that: The length, width and height of the protrusion are all less than 100 μm.

9. The multi-cooling medium parallel heat exchanger according to claim 1, characterized in that: The plurality of channel partitions are made of the same material; The protrusion is manufactured by adopting femtosecond laser technology.

10. A nuclear power system, comprising the multi-cooling medium parallel heat exchanger according to any one of claims 1 to 9.

Images