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Article(id=1239215312642560472, tenantId=1146029695717560320, journalId=1238823019242635269, issueId=1239215308985136031, articleNumber=null, orderNo=null, doi=10.12465/j.issn.0253-4339.2025.04.036, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=research-article, receivedDate=1709222400000, receivedDateStr=2024-03-01, revisedDate=1721836800000, revisedDateStr=2024-07-25, acceptedDate=1722441600000, acceptedDateStr=2024-08-01, onlineDate=1773381554041, onlineDateStr=2026-03-13, pubDate=1755273600000, pubDateStr=2025-08-16, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1773381554041, onlineIssueDateStr=2026-03-13, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1773381554041, creator=13701087609, updateTime=1773381554041, updator=13701087609, issue=Issue{id=1239215308985136031, tenantId=1146029695717560320, journalId=1238823019242635269, year='2025', volume='46', issue='4', pageStart='1', pageEnd='170', issueExtLink='null', onlineDate='null', pubDate='null', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1773381553169, creator=13701087609, updateTime=1773381893131, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1239216734947824534, tenantId=1146029695717560320, journalId=1238823019242635269, issueId=1239215308985136031, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1239216734947824535, tenantId=1146029695717560320, journalId=1238823019242635269, issueId=1239215308985136031, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=36, endPage=43, ext={EN=ArticleExt(id=1239215313615639021, articleId=1239215312642560472, tenantId=1146029695717560320, journalId=1238823019242635269, language=EN, title=Influence of Heat Exchanger Structure on System Performance in Trans-Critical CO2 Heat Pump Air Conditioning Systems for Trains, columnId=null, journalTitle=Journal of Refrigeration, columnName=null, runingTitle=null, highlight=null, articleAbstract=

To further study the influence of heat exchanger structures on system performance and overall power consumption in transcritical CO2 heat pump air conditioning systems for high-speed trains to improve performance and reduce power consumption, this study builds a numerical simulation model based on the AMEsim simulation platform. The simulation results show that, in the high-speed train heat pump air conditioning system, the influence of the gas cooler structure on system performance is greater than that of the evaporator structure. In terms of the selection of heat exchanger structure, the optimal structure is that during refrigeration, the outdoor heat exchanger adopts the countercurrent arrangement and the indoor heat exchanger adopts the concurrent arrangement (vice versa for heating). At the rated cooling condition of 35 ℃ ambient temperature, the COP is increased by 20.38% compared to the concurrent arrangement in outdoor heat exchangers, and at a rated heating condition of 7 ℃ ambient temperature, the COP is increased by 68.04% compared to the concurrent arrangement of indoor heat exchangers. Considering both the degree of backflow and fan power consumption, in the "fully heat exchange state", system COP increases with backflow degree, while system COP decreases with backflow degree when the air flow rate is insufficient.

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Song Yulong, male, associate professor, School of Energy and Power Engineering, Xi'an Jiaotong University, 86-13488264214, E-mail: . Research fields: new energy vehicle heat pump air conditioning and thermal management technology, transcritical CO2 refrigeration and heating technology.
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为研究高速动车上跨临界CO2热泵空调系统中换热器结构对系统性能、整体功耗的影响，以达到提升性能、减少功耗的目的，基于AMEsim仿真平台搭建了数值仿真模型。结果表明：在高速动车热泵空调系统中，气体冷却器结构对系统性能的影响大于蒸发器结构对系统性能的影响；而在换热器的结构选择上，制冷模式下室外换热器采用逆流、室内换热器采用顺流（对应制热模式下采用室外换热器顺流，室内换热器逆流）的结构为最优结构，其在额定制冷工况35 ℃下，比室外换热器顺流布置时的COP提升20.38%，额定制热工况7 ℃下，比室内换热器顺流布置时的COP提升68.04%。综合考虑逆流程度和风机功耗，在“充分换热状态”，系统COP会随着逆流程度的增大而升高，在“风量过小状态”，系统COP会随着逆流程度的增大而减小。

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宋昱龙，男，副教授，西安交通大学能源与动力工程学院，13488264214，E-mail：。研究方向：新能源车辆热泵空调及热管理技术、跨临界CO2制冷制热技术。
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figureFileSmall=HyHoVM5PKOA4Q8i7Q5a5tg==, figureFileBig=FInalFS/ZUyv2fphm3kxVg==, tableContent=null), ArticleFig(id=1239232344662537045, tenantId=1146029695717560320, journalId=1238823019242635269, articleId=1239215312642560472, language=CN, label=图7, caption=不同模式逆流程度系统p-h图, figureFileSmall=HyHoVM5PKOA4Q8i7Q5a5tg==, figureFileBig=FInalFS/ZUyv2fphm3kxVg==, tableContent=null), ArticleFig(id=1239232344750617433, tenantId=1146029695717560320, journalId=1238823019242635269, articleId=1239215312642560472, language=EN, label=Tab.1, caption=Operating condition parameters of heat pump air conditioning, figureFileSmall=null, figureFileBig=null, tableContent=
工况室外干球温度/℃室外湿球温度/℃室内干球温度/℃室内湿球温度/℃
135—2923
245—2923
3762015
4-7-82015
5-20—2015
6-25—2015
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工况室外干球温度/℃室外湿球温度/℃室内干球温度/℃室内湿球温度/℃
135—2923
245—2923
3762015
4-7-82015
5-20—2015
6-25—2015
), ArticleFig(id=1239232344893223779, tenantId=1146029695717560320, journalId=1238823019242635269, articleId=1239215312642560472, language=EN, label=Tab.2, caption=Experimental equipments, figureFileSmall=null, figureFileBig=null, tableContent=
设备描述
热电偶实时测量温度，如压缩机进出口、蒸发器/气体冷却器进出口等，测量误差为±0.5 ℃
压力变送器测量系统中不同位置的实时压力，测试误差为测试值的±0.5%
功率计测量压缩机和风机的功率以计算COP，型号为8902F2
铠装热电偶用于采样风管中环境风的实时温度测量，测量误差为测试值的±0.5 ℃
), ArticleFig(id=1239232344956138344, tenantId=1146029695717560320, journalId=1238823019242635269, articleId=1239215312642560472, language=CN, label=表2, caption=实验设备, figureFileSmall=null, figureFileBig=null, tableContent=
设备描述
热电偶实时测量温度，如压缩机进出口、蒸发器/气体冷却器进出口等，测量误差为±0.5 ℃
压力变送器测量系统中不同位置的实时压力，测试误差为测试值的±0.5%
功率计测量压缩机和风机的功率以计算COP，型号为8902F2
铠装热电偶用于采样风管中环境风的实时温度测量，测量误差为测试值的±0.5 ℃
), ArticleFig(id=1239232345031635822, tenantId=1146029695717560320, journalId=1238823019242635269, articleId=1239215312642560472, language=EN, label=Tab.3, caption=COP simulation/experimental results of systems with different combinations of indoor and outdoor units in forward and backward flow under cooling mode, figureFileSmall=null, figureFileBig=null, tableContent=
温度/℃COP
室外逆流室外顺流
室内顺流室内逆流室内逆流室内顺流
352.232.221.831.84
451.951.951.671.67
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温度/℃COP
室外逆流室外顺流
室内顺流室内逆流室内逆流室内顺流
352.232.221.831.84
451.951.951.671.67
), ArticleFig(id=1239232345228768115, tenantId=1146029695717560320, journalId=1238823019242635269, articleId=1239215312642560472, language=EN, label=Tab.4, caption=COP simulation/experimental results of systems with different combinations of indoor and outdoor units in forward and backward flow under heating mode, figureFileSmall=null, figureFileBig=null, tableContent=
温度/℃COP
室外逆流室外顺流
室内顺流室内逆流室内逆流室内顺流
71.793.013.011.79
-71.652.522.521.65
-201.542.112.111.54
-251.451.961.961.45
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温度/℃COP
室外逆流室外顺流
室内顺流室内逆流室内逆流室内顺流
71.793.013.011.79
-71.652.522.521.65
-201.542.112.111.54
-251.451.961.961.45
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温度/℃COP
3层4层6层12层
351.451.681.851.60
451.341.471.581.37
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温度/℃COP
3层4层6层12层
351.451.681.851.60
451.341.471.581.37
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温度/℃COP
6层8层10层12层
72.042.552.612.01
-71.912.102.151.83
-201.751.791.831.12
-251.681.711.780.56
), ArticleFig(id=1239232345677558668, tenantId=1146029695717560320, journalId=1238823019242635269, articleId=1239215312642560472, language=CN, label=表6, caption=制热工况下逆流程度对性能的影响, figureFileSmall=null, figureFileBig=null, tableContent=
温度/℃COP
6层8层10层12层
72.042.552.612.01
-71.912.102.151.83
-201.751.791.831.12
-251.681.711.780.56
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换热器结构对高速动车跨临界CO2热泵空调系统性能的影响
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谢宏生 1 , 白刚 2 , 杨梦莹 1 , 宋昱龙 1 , 曹锋 1
制冷学报 | 2025,46(4): 36-43
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制冷学报 | 2025, 46(4): 36-43
换热器结构对高速动车跨临界CO2热泵空调系统性能的影响
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谢宏生1, 白刚2, 杨梦莹1, 宋昱龙1 , 曹锋1
作者信息
  • 1西安交通大学能源与动力工程学院　西安　710049
  • 2中车大连机车研究所有限公司　大连　116000

通讯作者:

宋昱龙，男，副教授，西安交通大学能源与动力工程学院，13488264214，E-mail：。研究方向：新能源车辆热泵空调及热管理技术、跨临界CO2制冷制热技术。
Influence of Heat Exchanger Structure on System Performance in Trans-Critical CO2 Heat Pump Air Conditioning Systems for Trains
Hongsheng Xie1, Gang Bai2, Mengying Yang1, Yulong Song1 , Feng Cao1
Affiliations
  • 1.School of Energy and Power Engineering, Xi'an Jiaotong University, Xi'an, 710049, China
  • 2.CRRC Dalian Locomotive Research Institute Co., Ltd., Dalian, 116000, China
出版时间: 2025-08-16 doi: 10.12465/j.issn.0253-4339.2025.04.036
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摘要
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为研究高速动车上跨临界CO2热泵空调系统中换热器结构对系统性能、整体功耗的影响，以达到提升性能、减少功耗的目的，基于AMEsim仿真平台搭建了数值仿真模型。结果表明：在高速动车热泵空调系统中，气体冷却器结构对系统性能的影响大于蒸发器结构对系统性能的影响；而在换热器的结构选择上，制冷模式下室外换热器采用逆流、室内换热器采用顺流（对应制热模式下采用室外换热器顺流，室内换热器逆流）的结构为最优结构，其在额定制冷工况35 ℃下，比室外换热器顺流布置时的COP提升20.38%，额定制热工况7 ℃下，比室内换热器顺流布置时的COP提升68.04%。综合考虑逆流程度和风机功耗，在“充分换热状态”，系统COP会随着逆流程度的增大而升高，在“风量过小状态”，系统COP会随着逆流程度的增大而减小。

跨临界CO2热泵空调  /  高速动车  /  换热器顺逆流  /  最优结构

To further study the influence of heat exchanger structures on system performance and overall power consumption in transcritical CO2 heat pump air conditioning systems for high-speed trains to improve performance and reduce power consumption, this study builds a numerical simulation model based on the AMEsim simulation platform. The simulation results show that, in the high-speed train heat pump air conditioning system, the influence of the gas cooler structure on system performance is greater than that of the evaporator structure. In terms of the selection of heat exchanger structure, the optimal structure is that during refrigeration, the outdoor heat exchanger adopts the countercurrent arrangement and the indoor heat exchanger adopts the concurrent arrangement (vice versa for heating). At the rated cooling condition of 35 ℃ ambient temperature, the COP is increased by 20.38% compared to the concurrent arrangement in outdoor heat exchangers, and at a rated heating condition of 7 ℃ ambient temperature, the COP is increased by 68.04% compared to the concurrent arrangement of indoor heat exchangers. Considering both the degree of backflow and fan power consumption, in the "fully heat exchange state", system COP increases with backflow degree, while system COP decreases with backflow degree when the air flow rate is insufficient.

transcritical CO2 heat pump air conditioning  /  rail vehicles  /  heat exchanger co-current and counter-current  /  optimal structure
谢宏生, 白刚, 杨梦莹, 宋昱龙, 曹锋. 换热器结构对高速动车跨临界CO2热泵空调系统性能的影响. 制冷学报, 2025 , 46 (4) : 36 -43 . DOI: 10.12465/j.issn.0253-4339.2025.04.036
Hongsheng Xie, Gang Bai, Mengying Yang, Yulong Song, Feng Cao. Influence of Heat Exchanger Structure on System Performance in Trans-Critical CO2 Heat Pump Air Conditioning Systems for Trains[J]. Journal of Refrigeration, 2025 , 46 (4) : 36 -43 . DOI: 10.12465/j.issn.0253-4339.2025.04.036
正文
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在各类长距离交通工具中，高速动车（简称：高铁）具有便捷、快速的优势，自2008年以来，中国已开通超过25 000 km的高铁专用线，远远超过世界其他地区的高铁运营总量，目前，轨道交通出行占我国长距离出行的56%[1]。高铁的开通及发展对金融经济发展具有显著的正向促进效果，能够凸显地区地域优势，影响整个社会城市的经济发展，发展前景广阔[2-3]。
在“双碳”目标的时代背景下，高速发展的高铁行业也需要与时俱进[4]。2006—2016年，我国交通业的CO2排放总量增长了94%，且碳排放强度年均增长6.3%[5]，出于环境保护的目的，高铁领域需要寻找更加节能有效的技术环保方案。对于高铁上的能源系统，其能源使用量大，基础设施能耗达104 PJ[6]，而热泵空调部分的能耗是高铁领域较为重要的能源消耗分支，是节能调控的重要部分。
目前行业中广泛使用的高铁热泵空调的循环工质为R407C，其GWP（全球变暖潜值，Global Warming Potential）为1 774，对气候变化影响较大[7]，故R407C的使用受到《蒙特利尔议定书基加利修正案》的限制，被其列为限制使用的强温室效应气体[8]。另一方面，R407C的冬季制热能力欠佳，搭配一般列车使用的PTC（正温度系数，positive temperature coefficient）电加热使用会导致能耗过高[9-10]。故综合考虑环保效益和能耗因素，R407C难以长久使用，亟待寻找新的替代方案。
在新型制冷剂的选择方面，CO2作为纯天然的自然工质，具有无毒、不可燃、易获取等特点[11]，低温流动性好[12]，同时CO2的ODP（臭氧损耗潜值，ozone depletion potential）为0，GWP为1[13]，与其他类型制冷剂相比具有更优秀的环保性能。在G. Lorentzen教授首次提出跨临界CO2循环应用模式后[14]，跨临界CO2热泵技术在各个领域迅速发展。目前已经存在大量有关跨临界CO2的探索：一方面，相关人员对跨临界CO2循环数值分析、系统组件研究、CO2作为新型制冷剂优势[15-16]等有关理论层面进行了研究；另一方面，在实际应用中，也涉及了如太阳能辅助热泵[17]、超低温跨临界CO2研究[18]、电动车辆热泵[19-21]等领域。
结合学者对流体流向的研究[22]，本文认为，对于CO2制冷剂独特的跨临界循环模式，逆流换热更适合作为跨临界CO2系统的热交换方式。在换热器中，CO2在每一片换热翅片中与空气的换热均为垂直交叉的错流换热形式，在前一片换热翅片完成换热后进入下一片继续与空气进行热交换，故每一片间流过的方向与空气流动方向存在顺/逆流关系。同时考虑到制冷模式和制热模式切换时存在制冷剂流向切换的问题，顺流和逆流会因此而改变，换热效果也会相应受到影响，因此需要对换热器的结构进行优化设计。目前关于高铁跨临界CO2热泵空调的换热器流向、流程相关研究较少，本文基于AMEsim仿真平台，对相关的系统进行研究计算，同时搭建高铁跨临界CO2热泵空调系统进行实验以定性验证计算结果。
1 系统构建
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本文搭建了一种高铁跨临界CO2热泵空调系统，如图1所示，整套系统由跨临界CO2压缩机、三通阀、室内换热器、室外换热器、节流阀、回热器及气液分离器等组成，用于研究在高铁跨临界CO2系统中，换热器结构对系统整体性能的影响。
该系统在不同运行模式下分别以制冷/制热模式运行。当系统运行制冷模式时，较低温度和压力的CO2进入跨临界压缩机，被压缩至高温高压，从三通阀b口进入，a口流出，在室外换热器放出热量，途经回热器进行余热回收，然后进入节流阀节流降温降压，在室内换热器吸热为乘员舱提供冷量，之后经过电磁阀1（此时电磁阀2关闭）进入气液分离器，在回热器内吸收余热，增加压缩机的吸气过热度，最后回到压缩机；同理，当系统运行制热模式时，CO2经压缩后从三通阀b口进入，c口流出，直接进入室内换热器进行放热为乘员舱提供热量，之后经过节流阀降温降压，流经回热器进入室外换热器吸收热量，流过电磁阀2（此时电磁阀1关闭），经过气液分离器、回热器，最终回到压缩机。
在图1所示的系统基础上，本文对室内换热器和室外换热器进行了结构的差异化设计，改变其顺流和逆流的换热形式，选择出最适合高铁跨临界CO2的换热器结构；同时在最优结构下进行流程的设计选择。
2 模型搭建
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2.1 模型参数
本文根据TB/T 1804—2017《铁道车辆空调　空调机组》[23]制定了室内外制冷制热模式参数，如表1所示，额定制冷工况为：室外干球温度35 ℃，室内干/湿球温度29 ℃/23 ℃；额定制热工况为：室外干/湿球温度7 ℃/6 ℃，室内干/湿球温度20 ℃/15 ℃；此外本模型添加了其他典型工况进行对照，详细工况选择如表1所示。
参照GB/T 7928—2003《地铁车辆通用技术条件》[24]，高铁提供人均新风量为10 m3/h，本模型选用500 m3/h的新风。
2.2 模型建立
基于图1的系统流程，在AMESim仿真软件中搭建了高铁跨临界CO2热力学仿真模型，如图2所示。以室内外换热器的顺/逆流换热形式为自变量进行排列组合，在不同的工作模式和不同的工况点下分别进行模拟，寻找最优排气压力，对比所得结果，从而得出最合适的换热器结构。
图2（a）和（b）分别为制冷模式与制热模式系统，在图中对关键部件（如压缩机、室内外换热器、节流阀等）进行了标注，并对系统中2个PID的控制对象进行了介绍。
为进一步挖掘系统特点，本文在最优结构下，同时考虑了风机功耗、风机风量等变量因素，研究逆流程度大小对系统性能的影响。换热器流程设置如图3所示，在图3（a）的顺流结构中，风流向如红色箭头所示，制冷剂在管中的方向如蓝色箭头所指，分为6路进入管道，其在换热器片之间的流向为从进风方向流到出风方向，与空气流动方向一致，故为顺流；而在图3（b）、（c）中，制冷剂先进入靠近出风的管道，再从出风方向流回进风方向，与空气流动方向相反达成逆流；其中，大程度逆流如图3（b）所示，在总换热管道数（即总传热面积）不变的情况下切换逆流程度，换热片数增多，每一片面积减小，增加了制冷剂和空气接触的时间；小程度逆流如图3（c）所示，换热器片数减小，每一片面积变大。通过改变逆流程度进行仿真计算，得到换热器流程设置对系统的影响趋势，进而确定最优的布置形式，达到减小功耗，提升系统COP（性能系数，coefficient of performance）的目标。
2.3 系统参数的控制方法
本模型使用比例积分微分（proportion integration diffe，PID）控制器进行系统参数的控制，控制逻辑如图4所示，具体为：1）调节阀开度控制压缩机的排气压力以寻找最优排气压力；2）调节压缩机转速以控制车厢的送风温度。上述2个控制量均在式（1）、式（2）调控下进行输出量的控制。
式中：v为调控结果输出值；c为被控量实际反馈值；r为被控量的目标控制值；Kp为比例系数；Ki为积分系数；Kd为微分系数；t0为控制开始时间，s；t为控制结束时间，s。
3 实验设备
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为准确评估模拟结果，搭建了高铁跨临界CO2热泵空调实验台，如图5所示，图5（a）为室外环境室，通过冷机、加热器与加湿器控制温度、湿度以模拟室外环境，车顶部分安装于此，搭载有跨临界CO2热泵空调系统，系统分别与室内外进行换热，室内送风进入图5（b）所示的室内环境室，通过风道流入风箱进行温度、湿度等参数的测量，然后流入环境室。同时，室内环境室也使用同样的设备对室内环境进行控制。按照表1所示的工况进行实验验证。
同时，本实验采用了相应的测量仪器、仪表对高铁热泵空调系统上的具体参数进行测量分析，如表2所示。
对比大量仿真结果与实验结果，可以得出仿真模型较为可靠，计算数据误差不超过5%，误差对比如图6所示。
4 结果与讨论
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本文通过更改空调热泵系统中换热器的结构，即改变室内外换热器中制冷剂与风的顺/逆流形式及逆流时制冷剂的逆流程度，在不同运行工况下分别探求最佳的换热器布置方法。
4.1 顺流与逆流对比
在不同环境温度下，制冷运行模式下的仿真结果如表3所示。当室外换热器（制冷模式下为气体冷却器）结构不变时，室内换热器顺流与逆流的结果基本相同，而当室内换热器（制冷模式下为蒸发器）不变时，室外换热器顺流与逆流结果差距较大。可以得出，气体冷却器的结构形式对系统性能的影响更显著，这是由于在跨临界CO2系统中，气体冷却器中的CO2处于超临界状态，换热时温度持续变化，而在蒸发器中，CO2处于两相区，CO2本身的温度基本不变（压力损失导致少量温度变化），所以气体冷却器的顺/逆流形式改变使系统换热变化更为显著，故气体冷却器的结构影响更大；同时也可以得出，当室外换热器为逆流时，换热效果明显优于顺流模式，系统循环COP更高，这是由于当室外换热器为逆流时，CO2流过室外换热器的换热更充分，气体冷却器的出口温度可以达到的温度更低，传热温差更小，整体换热更好，因此，在额定制冷工况，室外换热器为逆流时COP更高，比室外换热器为顺流时COP提升了20.38%。
同理，制热模式下的仿真结果如表4所示，此时室内换热器为气体冷却器，逆流时效果更好，在额定制热工况，室外温度为7 ℃时，比室内换热器为顺流时的COP提升约68.04%，综合制冷与制热模式下的性能表现，可以得出，气体冷却器的结构布置是系统性能的主要影响因素。
同时以最优结构为基础，额定制冷工况室外35 ℃为例，可以计算得到，更换气体冷却器的结构布置对系统COP影响为20.38%；更换蒸发器的结构布置对系统COP影响为0.45%，远小于更换气体冷却器结构布置产生的影响。
综上，考虑到实际工程运用时，更换制冷/制热模式需要使用四通换向阀，制冷剂变换流向，因此为了实现高铁跨临界CO2热泵空调系统的最佳换热效果，室内/外换热器的布置形式应为：制冷时室外换热器（气体冷却器）为逆流，室内换热器（蒸发器）为顺流；制热时室外换热器（蒸发器）为顺流，室内换热器（气体冷却器）为逆流。
4.2 小程度与大程度逆流对比
基于4.1节得出的最佳换热器结构，对处于逆流结构的换热器进行逆流程度分析，此时需综合考虑换热器片数、总管路数、风机风量、风机功耗等因素，研究高铁跨临界CO2热泵空调系统中换热器逆流程度的影响程度。
如4.1节所述，维持相同的换热管路数量，通过改变换热片数以及每一片的管路排数以改变逆流程度，此时换热器总传热面积不变（即换热器总管数不变），同时风机风压会随着换热片数的改变而改变，风机功耗和风量也随之变化。更换逆流程度进行仿真，制冷工况仿真结果如表5所示，对于室外换热器，COP随着换热片数的增多而增大（此时换热器选择3层、4层、6层），本文将该过程中换热器所处的状态定义为“充分换热状态”，换热器换热良好，与风机风量匹配。换热器片数从较低升高时，逆流程度增大，一方面，压力损失变大，换热效果变好，压缩机的功耗也变小；另一方面，风机风压需要增大以匹配增多的换热器片数，每增加一片换热器需要相应增加近20 Pa的风压以维持换热效果良好，同时，风压提升也会导致风量的减小以及风机功耗的降低，此时风量充足，风量的下降不会成为影响COP的主要原因，故COP提高；而当换热器片数从6层增至12层，COP随着换热片数的增多而减小，本文将此过程中换热器所处的状态定义为“风量过小状态”，换热片数过多，风压进一步升高，风量下降过大，导致换热器虽然逆流程度大、效果好，但换热不足，需要更大的转速以维持换热量，故功耗提升，COP降低。制热工况仿真结果如表6所示，对于室内换热器，也出现了同样的趋势，换热片数选择6层、8层与10层时，COP处于上升趋势，本文将此过程中换热器所处的状态定义为“充分换热状态”；换热片数从10层增至12层时，COP呈下降趋势，本文将此过程中换热器所处的状态定义为“风量过小状态”。
在额定制冷工况下：若室外换热器处于“充分换热状态”，换热片数从3层增至4层，COP上升15.86%，从4层增至6层，COP上升10.11%；若室外换热器处于“风量过小状态”，换热片数从6层增至12层，系统COP下降13.51%。
在额定制热模式下：若室内换热器处于“充分换热状态”，换热片数从6层增至8层，COP上升25.01%，从8层增至10层，COP上升2.35%；若室外换热器处于“风量过小状态”，换热片数从10层增至12层，系统COP下降22.98%。
制冷制热循环内部参数的变化如图7所示，可以看到，在制热时，处于“充分换热状态”的换热器随着逆流程度增大，系统循环图逐渐向左移动，系统单位换热量升高，压缩起止点在改变逆流程度后基本不变，即一个循环内压缩机功耗基本不变，故在同一工况下，为达到目标换热量，总功耗会上升；而处于“风量过小状态”的换热器换热不充分，风机风量过小，换热不足，系统循环图整体向右移动，总功耗大幅增加。制冷模式下也呈现同样的趋势，如图7（b）所示。
5 结论
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本文搭建了一台高铁跨临界CO2热泵空调系统，分别选取了制冷/制热不同工况进行仿真模拟及实验研究，分析了换热器顺/逆流布置形式、换热器的逆流程度对系统性能的影响，得到结论如下：
1）在高铁跨临界CO2热泵空调系统中，气体冷却器的结构形式对系统性能的影响更大，当气体冷却器逆流布置时，换热效果更好，额定制冷工况35 ℃下，比气体冷却器顺流布置时的COP提升20.38%，额定制热工况7 ℃下，比气体冷却器顺流布置时的COP提升68.04%，结合制冷制热模式切换变向，确定制冷模式下室外换热器逆流布置、室内换热器顺流布置（制热模式下室外换热器顺流布置、室内换热器逆流布置）为最优流向布置方式。
2）在换热器逆流程度的研究中，逆流程度和风机功耗同时制约影响着换热器换热性能，本文按换热器片数不同将其定义为“充分换热状态”和“风量过小状态”：在“充分换热状态”，COP随逆流程度的上升呈现升高的趋势，在“风量过小状态”，COP随逆流程度的上升而下降，在本文所搭建的模型中，在室外换热器6层，室内换热器10层时达到最优效果。
基金
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  • 国家自然科学基金(52006161)
文献
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2025年第46卷第4期
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doi: 10.12465/j.issn.0253-4339.2025.04.036
  • 接收时间：2024-03-01
  • 首发时间：2026-03-13
  • 出版时间：2025-08-16
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  • 收稿日期：2024-03-01
  • 修回日期：2024-07-25
  • 录用日期：2024-08-01
基金
National Natural Science Foundation of China(52006161)
国家自然科学基金(52006161)
作者信息
    1西安交通大学能源与动力工程学院　西安　710049
    2中车大连机车研究所有限公司　大连　116000

通讯作者:

宋昱龙，男，副教授，西安交通大学能源与动力工程学院，13488264214，E-mail：。研究方向：新能源车辆热泵空调及热管理技术、跨临界CO2制冷制热技术。
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