CN107144158A - A kind of compact heat exchanger of supercritical carbon dioxide and water heat exchange - Google Patents
A kind of compact heat exchanger of supercritical carbon dioxide and water heat exchange Download PDFInfo
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- CN107144158A CN107144158A CN201710454446.5A CN201710454446A CN107144158A CN 107144158 A CN107144158 A CN 107144158A CN 201710454446 A CN201710454446 A CN 201710454446A CN 107144158 A CN107144158 A CN 107144158A
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- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 title claims abstract description 62
- 239000001569 carbon dioxide Substances 0.000 title claims abstract description 31
- 229910002092 carbon dioxide Inorganic materials 0.000 title claims abstract description 31
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 15
- VUZPPFZMUPKLLV-UHFFFAOYSA-N methane;hydrate Chemical compound C.O VUZPPFZMUPKLLV-UHFFFAOYSA-N 0.000 title abstract description 7
- 239000000758 substrate Substances 0.000 claims description 3
- 230000002411 adverse Effects 0.000 claims 3
- 238000010992 reflux Methods 0.000 claims 2
- 239000000498 cooling water Substances 0.000 abstract description 13
- 239000012530 fluid Substances 0.000 abstract description 6
- 230000000704 physical effect Effects 0.000 abstract description 5
- 238000012546 transfer Methods 0.000 description 10
- 238000010248 power generation Methods 0.000 description 6
- 238000013461 design Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000009792 diffusion process Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 238000003486 chemical etching Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 229910000601 superalloy Inorganic materials 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0081—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
本发明公开了一种超临界二氧化碳和水换热的紧凑式换热器，包括基板及以及位于基板上的若干热侧平板及若干冷侧平板，其中，各冷侧平板及各热侧平板自上到下依次交错分布，其中，热侧平板的底面上开设有若干热侧通道，冷侧平板的底面上开设有若干冷侧通道，其中，所有冷侧通道横截面的面积之和为所有热侧通道横截面的面积之和的1/3，该换热器能够有效的解决超临界二氧化碳布雷顿循环预冷器中冷热侧流体物性极大差异带来的流量匹配问题，并且能够保证换热系数的情况下减小循环冷却水的流量。
The invention discloses a compact heat exchanger for exchanging heat between supercritical carbon dioxide and water, comprising a base plate and several hot side plates and several cold side plates located on the base plate, wherein each cold side plate and each hot side plate are self-contained The distribution is staggered from top to bottom, wherein, there are several hot side channels on the bottom surface of the hot side plate, and several cold side channels are opened on the bottom surface of the cold side plate, wherein the sum of the cross-sectional areas of all the cold side channels is all hot side channels. 1/3 of the sum of the cross-sectional areas of the side channels, the heat exchanger can effectively solve the flow matching problem caused by the great difference in the physical properties of the hot and cold side fluids in the supercritical carbon dioxide Brayton cycle precooler, and can ensure the exchange In the case of thermal coefficient, reduce the flow rate of circulating cooling water.
Description
技术领域technical field
本发明属于换热技术领域，涉及一种超临界二氧化碳和水换热的紧凑式换热器。The invention belongs to the technical field of heat exchange, and relates to a compact heat exchanger for exchanging heat between supercritical carbon dioxide and water.
背景技术Background technique
超临界二氧化碳布雷顿循环是目前公认的最具潜力的先进动力循环之一。由于超临界二氧化碳具有能量密度大、传热效率高等特点，超临界二氧化碳布雷顿循环高效发电系统可以在620℃温度范围内达到常规蒸汽朗肯循环700℃的效率，不需要再开发新型的高温合金，且设备尺寸小于同参数的蒸汽机组，应用前景非常好。The supercritical carbon dioxide Brayton cycle is currently recognized as one of the most potential advanced power cycles. Because supercritical carbon dioxide has the characteristics of high energy density and high heat transfer efficiency, the high-efficiency power generation system of supercritical carbon dioxide Brayton cycle can reach the efficiency of conventional steam Rankine cycle of 700°C in the temperature range of 620°C, and there is no need to develop new superalloys , and the equipment size is smaller than the steam unit with the same parameters, the application prospect is very good.
目前，在超临界二氧化碳布雷顿循环发电系统中，印刷电路板换热器被普遍认为是最适用的换热器。印刷电路板换热器是一种新型高效的紧凑式换热器，是将交替布置的冷、热侧平板通过扩散焊的方式焊接在一起的换热器，其冷、热侧换热平板上的流道均为通过化学蚀刻方法得到的细小通道。在相同换热量的条件下，印刷电路板换热器的尺寸只有传统管壳式换热器尺寸的1/5-1/10。因此，印刷电路板换热器可以很好的用作超临界二氧化碳布雷顿循环发电系统的回热器和预冷器。At present, in the supercritical carbon dioxide Brayton cycle power generation system, the printed circuit board heat exchanger is generally considered to be the most suitable heat exchanger. The printed circuit board heat exchanger is a new type of high-efficiency compact heat exchanger. It is a heat exchanger that welds alternately arranged cold and hot side plates together by diffusion welding. The flow channels are small channels obtained by chemical etching. Under the condition of the same heat transfer capacity, the size of the printed circuit board heat exchanger is only 1/5-1/10 of the size of the traditional shell-and-tube heat exchanger. Therefore, the printed circuit board heat exchanger can be well used as the regenerator and precooler of the supercritical carbon dioxide Brayton cycle power generation system.
在超临界二氧化碳布雷顿循环发电系统的预冷器中，热侧的超临界二氧化碳工作在拟临界温度点附近(即超临界流体的大比热区)，而冷侧的水则处于过冷区，热侧工质和冷侧工质的定压比热容差异非常大。若仍采用传统的逆流结构或者顺流结构的印刷电路板换热器作为预冷器，则会出现冷侧通流面积偏大的现象，使得循环冷却水可能工作于层流区，导致换热系数偏低。因此，必须充分考虑超临界二氧化碳布雷顿循环发电系统预冷器中的超临界二氧化碳和冷却水在工作条件下的物性特点，合理的设计换热器的流道，避免该问题的出现。In the precooler of the supercritical carbon dioxide Brayton cycle power generation system, the supercritical carbon dioxide on the hot side works near the quasi-critical temperature point (that is, the large specific heat region of the supercritical fluid), while the water on the cold side is in the supercooled region , the constant pressure specific heat capacity of the hot side working fluid and the cold side working fluid is very different. If the printed circuit board heat exchanger with the traditional counter-flow structure or down-flow structure is still used as the pre-cooler, there will be a phenomenon that the flow area of the cold side is too large, so that the circulating cooling water may work in the laminar flow area, resulting in heat transfer. The coefficient is low. Therefore, it is necessary to fully consider the physical properties of supercritical carbon dioxide and cooling water in the supercritical carbon dioxide Brayton cycle power generation system precooler under working conditions, and design the flow path of the heat exchanger reasonably to avoid this problem.
然而经调研，目前国内外均鲜有公开成果和专利介绍涉及用于超临界二氧化碳布雷顿循环发电系统中超临界二氧化碳和水换热的印刷电路板预冷器。而印刷电路板换热器作为预冷器时，若设计不当，则会出现所需的循环冷却水量过大或者预冷器换热系数偏低等情况。However, after research, there are few public achievements and patent introductions at home and abroad related to the printed circuit board precooler used for heat exchange between supercritical carbon dioxide and water in supercritical carbon dioxide Brayton cycle power generation systems. When the printed circuit board heat exchanger is used as a pre-cooler, if the design is not proper, the required circulating cooling water will be too large or the heat transfer coefficient of the pre-cooler will be low.
发明内容Contents of the invention
本发明的目的在于克服上述现有技术的缺点，提供了一种超临界二氧化碳和水换热的紧凑式换热器，该换热器能够有效的解决超临界二氧化碳布雷顿循环预冷器中冷热侧流体物性极大差异带来的流量匹配问题，并且能够保证换热系数的情况下减小循环冷却水的流量。The purpose of the present invention is to overcome the above-mentioned shortcoming of prior art, provide a kind of compact heat exchanger of supercritical carbon dioxide and water heat exchange, this heat exchanger can effectively solve supercritical carbon dioxide Brayton cycle precooler cooling The flow matching problem caused by the great difference in the physical properties of the hot side fluid can reduce the flow rate of the circulating cooling water while ensuring the heat transfer coefficient.
为达到上述目的，本发明所述的超临界二氧化碳和水换热的紧凑式换热器包括基板及以及位于基板上的若干热侧平板及若干冷侧平板，其中，各冷侧平板及各热侧平板自上到下依次交错分布，其中，热侧平板的底面上开设有若干热侧通道，冷侧平板的底面上开设有若干冷侧通道，其中，所有冷侧通道横截面的面积之和为所有热侧通道横截面的面积之和的1/3。In order to achieve the above object, the compact heat exchanger for heat exchange between supercritical carbon dioxide and water according to the present invention includes a base plate and some hot side plates and some cold side plates located on the base plate, wherein each cold side plate and each heat The side plates are distributed in a staggered order from top to bottom, wherein, there are several hot side channels on the bottom surface of the hot side plate, and several cold side channels are opened on the bottom surface of the cold side plate, wherein the sum of the cross-sectional areas of all the cold side channels 1/3 of the sum of the areas of the cross-sections of all the hot side channels.
各热侧通道从左到右依次平行分布，且每个热侧通道均为直线型结构。The hot side channels are distributed in parallel from left to right, and each hot side channel is a linear structure.
各冷侧通道均呈折线型且等间距分布，各冷侧通道均包括依次相连通的冷侧入口、冷侧入口引流段、低温逆流段冷侧通道、第一叉流段冷侧通道、顺流段冷侧通道、第二叉流段冷侧通道、冷侧出口汇集段及热侧出口。Each cold side channel is zigzagging and distributed at equal intervals. Each cold side channel includes a cold side inlet, a cold side inlet drainage section, a cold side channel in a low-temperature counterflow section, a cold side channel in the first fork flow section, and a sequentially connected cold side channel. The cold side channel of the flow section, the cold side channel of the second fork flow section, the cold side outlet converging section and the hot side outlet.
冷侧入口引流段及第二叉流段冷侧通道位于冷侧平板位于前侧，第一叉流段冷侧通道及冷侧出口汇集段位于冷侧平板的后侧，低温逆流段冷侧通道、顺流段冷侧通道及高温逆流段冷侧通道均呈直线型分布。The cold-side inlet drainage section and the second cross-flow section cold-side channel are located on the cold-side plate on the front side, the first fork-flow section cold-side channel and the cold-side outlet collection section are located on the rear side of the cold-side plate, and the low-temperature counterflow section cold-side channel , the cold side passages in the downstream section and the cold side passages in the high temperature counterflow section are all distributed in a straight line.
各热侧通道的横截面及各冷侧通道的横截面均为半圆形结构。The cross section of each hot side passage and the cross section of each cold side passage are semicircular structures.
热侧通道的数量为低温逆流段冷侧通道的数量、顺流段冷侧通道的数量及高温逆流段冷侧通道的数量之和。The number of hot-side channels is the sum of the number of cold-side channels in the low-temperature counter-flow section, the number of cold-side channels in the downstream section, and the number of cold-side channels in the high-temperature counter-flow section.
本发明具有以下有益效果：The present invention has the following beneficial effects:
本发明所述的超临界二氧化碳和水换热的紧凑式换热器采用印制电路板换热器的结构形式，即包括基板以及依次交错设置于所述基板上的若干热侧平板及若干冷侧平板，同时为避免传统逆流结构或者顺流结构的印刷电路板换热器出现的冷侧流通面积偏大、换热系数偏低的问题，本发明中各冷侧通道横截面的面积之和为各热侧通道横截面的面积之和的1/3，从而有效的避免循环冷却水工作于层流区，保证换热器足够的对流换热系数，同时冷却水的沿程阻力增加较少，并且换热器的体积较小，循环冷却水的用量较少，从而有效的解决超临界二氧化碳布雷顿循环预冷器中冷热侧流体物性极大差异带来的流量匹配问题。The compact heat exchanger for exchanging heat between supercritical carbon dioxide and water in the present invention adopts the structural form of a printed circuit board heat exchanger, that is, it includes a substrate and several hot side plates and several cold side plates arranged alternately on the substrate in sequence. side plate, and in order to avoid the problems of large cold side circulation area and low heat transfer coefficient in the printed circuit board heat exchanger with traditional counterflow structure or downstream structure, the sum of the cross-sectional areas of each cold side channel in the present invention It is 1/3 of the sum of the cross-sectional area of each hot side channel, so as to effectively prevent the circulating cooling water from working in the laminar flow area, ensure sufficient convective heat transfer coefficient of the heat exchanger, and at the same time, the resistance of the cooling water along the way increases less , and the volume of the heat exchanger is small, and the amount of circulating cooling water is small, thus effectively solving the flow matching problem caused by the great difference in the physical properties of the cold and hot side fluids in the supercritical carbon dioxide Brayton cycle precooler.
附图说明Description of drawings
图1为本发明的截面图；Fig. 1 is a sectional view of the present invention;
图2为本发明中热侧平板1的俯视图；Fig. 2 is the plan view of hot side plate 1 in the present invention;
图3为本发明中冷侧平板2的俯视图。Fig. 3 is a top view of the middle cold side plate 2 of the present invention.
其中，1为热侧平板、2为冷侧平板、3为热侧入口、4为热侧通道、5为冷侧出口汇集段、6为冷侧出口、7为冷侧入口引流段、8为低温逆流段冷侧通道、9为第一叉流段冷侧通道、10为顺流段冷侧通道、11为第二叉流段冷侧通道、12为高温逆流段冷侧通道。Among them, 1 is the hot side plate, 2 is the cold side plate, 3 is the hot side inlet, 4 is the hot side channel, 5 is the cold side outlet collection section, 6 is the cold side outlet, 7 is the cold side inlet drainage section, 8 is The cold side channel of the low-temperature reverse flow section, 9 is the cold side channel of the first fork flow section, 10 is the cold side channel of the downstream section, 11 is the cold side channel of the second fork flow section, and 12 is the cold side channel of the high temperature counterflow section.
具体实施方式detailed description
下面结合附图对本发明做进一步详细描述：The present invention is described in further detail below in conjunction with accompanying drawing:
参考图1，本发明所述的超临界二氧化碳和水换热的紧凑式换热器包括基板及以及位于基板上的若干热侧平板1及若干冷侧平板2，其中，各冷侧平板2及各热侧平板1自上到下依次交错分布，其中，热侧平板1的底面上开设有若干热侧通道4，冷侧平板2的底面上开设有若干冷侧通道，其中，所有冷侧通道横截面的面积之和为所有热侧通道4横截面的面积之和的1/3。With reference to Fig. 1, the compact heat exchanger of supercritical carbon dioxide of the present invention and water heat exchange comprises base plate and and some hot side plates 1 and some cold side plates 2 that are positioned on the base plate, wherein, each cold side plate 2 and Each hot-side plate 1 is arranged alternately from top to bottom, wherein, the bottom surface of the hot-side plate 1 is provided with a number of hot-side channels 4, and the bottom surface of the cold-side plate 2 is provided with a number of cold-side channels, wherein all the cold-side channels The sum of the areas of the cross sections is 1/3 of the sum of the areas of the cross sections of all the hot side channels 4 .
各热侧通道4从左到右依次平行分布，且每个热侧通道4均为直线型结构。The hot side channels 4 are arranged in parallel from left to right, and each hot side channel 4 is a linear structure.
各冷侧通道均呈折线型且等间距分布，各冷侧通道均包括依次相连通的冷侧入口6、冷侧入口引流段7、低温逆流段冷侧通道8、第一叉流段冷侧通道9、顺流段冷侧通道10、第二叉流段冷侧通道11、冷侧出口汇集段5及热侧出口3；冷侧入口引流段7及第二叉流段冷侧通道11位于冷侧平板2位于前侧，第一叉流段冷侧通道9及冷侧出口汇集段5位于冷侧平板2的后侧，低温逆流段冷侧通道8、顺流段冷侧通道10及高温逆流段冷侧通道12均呈直线型分布。Each cold side channel is zigzagging and distributed at equal intervals. Each cold side channel includes a cold side inlet 6, a cold side inlet drainage section 7, a cold side channel 8 in a low-temperature counterflow section, and a cold side of the first fork flow section. Channel 9, cold side channel 10 of downstream section, cold side channel 11 of second cross flow section, cold side outlet converging section 5 and hot side outlet 3; cold side inlet drainage section 7 and second fork flow section cold side channel 11 are located The cold side plate 2 is located on the front side, the cold side channel 9 of the first fork flow section and the cold side outlet converging section 5 are located on the rear side of the cold side plate 2, the cold side channel 8 of the low temperature counterflow section, the cold side channel 10 of the downstream section and the high temperature The cold side passages 12 in the counterflow section are distributed in a straight line.
各热侧通道4的横截面及各冷侧通道的横截面均为半圆形结构；热侧通道4的数量为低温逆流段冷侧通道8的数量、顺流段冷侧通道10的数量及高温逆流段冷侧通道12的数量之和。The cross section of each hot side passage 4 and the cross section of each cold side passage are semicircular structures; the number of hot side passages 4 is the number of cold side passages 8 in the low temperature counterflow section, the number of cold side passages 10 in the downstream section and The sum of the number of cold-side channels 12 in the high-temperature counterflow section.
参见图1，相邻热侧平板1与冷侧平板2之间通过扩散焊的工艺进行焊接；热侧平板1上的热侧通道4和冷侧平板2上的冷侧通道均通过化学蚀刻方法得到；热侧通道4及冷侧通道的通道节距等于通道直径的1.2-1.4倍，热侧平板1与冷侧平板2的厚度均为通道半径的1.3-1.5倍。Referring to Fig. 1, the adjacent hot-side plate 1 and the cold-side plate 2 are welded by diffusion welding; the hot-side channel 4 on the hot-side plate 1 and the cold-side channel on the cold-side plate 2 are all chemically etched It is obtained that the channel pitch of the hot side channel 4 and the cold side channel is equal to 1.2-1.4 times of the channel diameter, and the thickness of the hot side plate 1 and the cold side plate 2 are both 1.3-1.5 times of the channel radius.
本发明的具体工作过程如下所示：Concrete work process of the present invention is as follows:
热侧平板1上的各热侧通道4左到右依次平行分布，超临界二氧化碳由各热侧通道4的热侧入口进入各热侧通道4中，再将热量传递给冷侧工质，然后再将各热侧通道4的热侧出口流出。Each hot-side channel 4 on the hot-side plate 1 is distributed in parallel from left to right in turn, supercritical carbon dioxide enters each hot-side channel 4 from the hot-side inlet of each hot-side channel 4, and then transfers heat to the cold-side working medium, and then Then the hot side outlets of each hot side channel 4 flow out.
冷侧通道的数量为热侧通道4数量的1/3，循环冷却水依次流经冷侧入口6、冷侧入口引流段7、低温逆流段冷侧通道8、第一叉流段冷侧通道9、顺流段冷侧通道10，第二叉流段冷侧通道11、高温逆流段冷侧通道12及冷侧出口汇集段5，并最后经冷侧通道的热侧出口3流出，并在流通过程中与超临界二氧化碳进行换热升温。The number of cold-side channels is 1/3 of the number of hot-side channels 4, and the circulating cooling water flows through the cold-side inlet 6, the cold-side inlet drainage section 7, the cold-side channel 8 of the low-temperature counterflow section, and the cold-side channel of the first fork flow section. 9. The cold-side channel 10 of the downstream section, the cold-side channel 11 of the second cross-flow section, the cold-side channel 12 of the high-temperature counter-flow section, and the cold-side outlet converging section 5, and finally flow out through the hot-side outlet 3 of the cold-side channel, and Heat exchange with supercritical carbon dioxide during the circulation process.
本发明的设计原理如下：Design principle of the present invention is as follows:
由于超临界二氧化碳布雷顿循环中预冷器的工作特性，采用传统逆流结构或者顺流结构的印刷电路板换热器作为预冷器，则会出现冷侧通流面积偏大的现象，使得循环冷却水可能工作于层流区，导致换热系数偏低。针对该问题，本发明通过对循环冷却水和临界温度点附近超临界二氧化碳的物性和换热能力进行计算及评估，发现当冷侧通道的横截面面积为热侧通道4的横截面的面积的1/3时，可以有效的避免循环冷却水工作于层流区，保证循环冷却水足够的对流换热系数，并且不会增加大多的沿程阻力。Due to the working characteristics of the precooler in the supercritical carbon dioxide Brayton cycle, if a printed circuit board heat exchanger with a traditional countercurrent structure or a downstream structure is used as a precooler, the flow area on the cold side will be too large, making the cycle The cooling water may work in the laminar flow region, resulting in a low heat transfer coefficient. Aiming at this problem, the present invention calculates and evaluates the physical properties and heat exchange capacity of supercritical carbon dioxide near the circulating cooling water and the critical temperature point, and finds that when the cross-sectional area of the cold-side channel is equal to the cross-sectional area of the hot-side channel 4 1/3, it can effectively prevent the circulating cooling water from working in the laminar flow area, ensure sufficient convective heat transfer coefficient of the circulating cooling water, and not increase most of the resistance along the way.
以上所述的具体实施方式，对本发明的目的、技术方案和有益效果进行了进一步详细说明，所应理解的是，以上所述仅为本发明的具体实施方式而已，并不用于限制本发明，凡在本发明的精神和原则之内，所做的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。The specific embodiments described above have further described the purpose, technical solutions and beneficial effects of the present invention in detail. It should be understood that the above descriptions are only specific embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present invention shall be included within the protection scope of the present invention.
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107816905A (en) * | 2017-09-25 | 2018-03-20 | 西安热工研究院有限公司 | A kind of high efficiency ultracritical carbon dioxide precooling device of circulating cooling water direct heat-exchange |
| CN108344316A (en) * | 2018-02-09 | 2018-07-31 | 西安热工研究院有限公司 | A kind of high-efficiency compact formula heat exchanger of gas-liquid two-phase carbon dioxide and water heat exchange |
| CN109443043A (en) * | 2018-09-05 | 2019-03-08 | 西安交通大学 | A kind of lead-supercritical carbon dioxide Intermediate Heat Exchanger |
| CN111895822A (en) * | 2020-08-05 | 2020-11-06 | 哈尔滨锅炉厂有限责任公司 | Micro-channel heat exchanger for supercritical carbon dioxide power generation circulation |
| CN114727478A (en) * | 2022-04-27 | 2022-07-08 | 西安热工研究院有限公司 | Printed circuit board heat exchanger flow channel structure suitable for liquid metal and processing method thereof |
| CN115143811A (en) * | 2022-07-01 | 2022-10-04 | 西安交通大学 | Variable cross-section printed circuit board heat exchanger for heat transfer at cold end of SCO2 power cycle |
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| CN117470003A (en) * | 2023-12-27 | 2024-01-30 | 中国核动力研究设计院 | Heat exchanger based on thermal cycle pinch point problem is solved and brayton cycle system |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1690636A (en) * | 2000-03-14 | 2005-11-02 | 换气控股有限公司 | Heat exchanger |
| CN202793140U (en) * | 2012-09-13 | 2013-03-13 | 风凯换热器制造(常州)有限公司 | Heat exchanger plate with asymmetric heat exchanging areas |
| DE102014102954A1 (en) * | 2013-03-12 | 2014-09-18 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Improved microchannel fin design based on an equivalent temperature gradient |
| CN205027181U (en) * | 2015-09-25 | 2016-02-10 | 航天海鹰(哈尔滨)钛业有限公司 | Industrial grade microchannel heat exchanger |
| US20160053638A1 (en) * | 2014-08-22 | 2016-02-25 | Peregrine Turbine Technologies, Llc | Power generation system including multiple cores |
| CN106839832A (en) * | 2017-01-23 | 2017-06-13 | 中国科学技术大学 | A kind of bend flow channel heat exchanger in the thermodynamic cycle for supercritical fluid |
| CN206832097U (en) * | 2017-06-14 | 2018-01-02 | 西安热工研究院有限公司 | A kind of close-coupled forecooler for supercritical carbon dioxide Brayton cycle |
-
2017
- 2017-06-14 CN CN201710454446.5A patent/CN107144158B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1690636A (en) * | 2000-03-14 | 2005-11-02 | 换气控股有限公司 | Heat exchanger |
| CN202793140U (en) * | 2012-09-13 | 2013-03-13 | 风凯换热器制造(常州)有限公司 | Heat exchanger plate with asymmetric heat exchanging areas |
| DE102014102954A1 (en) * | 2013-03-12 | 2014-09-18 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Improved microchannel fin design based on an equivalent temperature gradient |
| US20160053638A1 (en) * | 2014-08-22 | 2016-02-25 | Peregrine Turbine Technologies, Llc | Power generation system including multiple cores |
| CN205027181U (en) * | 2015-09-25 | 2016-02-10 | 航天海鹰(哈尔滨)钛业有限公司 | Industrial grade microchannel heat exchanger |
| CN106839832A (en) * | 2017-01-23 | 2017-06-13 | 中国科学技术大学 | A kind of bend flow channel heat exchanger in the thermodynamic cycle for supercritical fluid |
| CN206832097U (en) * | 2017-06-14 | 2018-01-02 | 西安热工研究院有限公司 | A kind of close-coupled forecooler for supercritical carbon dioxide Brayton cycle |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107816905A (en) * | 2017-09-25 | 2018-03-20 | 西安热工研究院有限公司 | A kind of high efficiency ultracritical carbon dioxide precooling device of circulating cooling water direct heat-exchange |
| CN108344316A (en) * | 2018-02-09 | 2018-07-31 | 西安热工研究院有限公司 | A kind of high-efficiency compact formula heat exchanger of gas-liquid two-phase carbon dioxide and water heat exchange |
| CN108344316B (en) * | 2018-02-09 | 2024-01-30 | 西安热工研究院有限公司 | Efficient compact heat exchanger for heat exchange between gas-liquid two-phase carbon dioxide and water |
| CN109443043A (en) * | 2018-09-05 | 2019-03-08 | 西安交通大学 | A kind of lead-supercritical carbon dioxide Intermediate Heat Exchanger |
| CN109443043B (en) * | 2018-09-05 | 2019-09-27 | 西安交通大学 | A lead-supercritical carbon dioxide intermediate heat exchanger |
| CN111895822A (en) * | 2020-08-05 | 2020-11-06 | 哈尔滨锅炉厂有限责任公司 | Micro-channel heat exchanger for supercritical carbon dioxide power generation circulation |
| CN114727478A (en) * | 2022-04-27 | 2022-07-08 | 西安热工研究院有限公司 | Printed circuit board heat exchanger flow channel structure suitable for liquid metal and processing method thereof |
| CN115143811A (en) * | 2022-07-01 | 2022-10-04 | 西安交通大学 | Variable cross-section printed circuit board heat exchanger for heat transfer at cold end of SCO2 power cycle |
| CN116013558A (en) * | 2023-01-17 | 2023-04-25 | 中国核动力研究设计院 | Dual super nuclear power system and nuclear energy utilization method |
| CN116013558B (en) * | 2023-01-17 | 2024-04-05 | 中国核动力研究设计院 | Dual super nuclear power system and nuclear energy utilization method |
| CN117470003A (en) * | 2023-12-27 | 2024-01-30 | 中国核动力研究设计院 | Heat exchanger based on thermal cycle pinch point problem is solved and brayton cycle system |
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