Article(id=1239175122997801913, tenantId=1146029695717560320, journalId=1238823019242635269, issueId=1239175122226049974, articleNumber=null, orderNo=null, doi=10.12465/j.issn.0253-4339.2025.02.028, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1699632000000, receivedDateStr=2023-11-11, revisedDate=1702483200000, revisedDateStr=2023-12-14, acceptedDate=1706457600000, acceptedDateStr=2024-01-29, onlineDate=1773371972082, onlineDateStr=2026-03-13, pubDate=1744732800000, pubDateStr=2025-04-16, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1773371972082, onlineIssueDateStr=2026-03-13, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1773371972082, creator=13701087609, updateTime=1773371972082, updator=13701087609, issue=Issue{id=1239175122226049974, tenantId=1146029695717560320, journalId=1238823019242635269, year='2025', volume='46', issue='2', 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=1773371971898, creator=13701087609, updateTime=1773372071198, updator=13701087609, preIssue=null, nextIssue=null, ext={EN=IssueExt(id=1239175538779148683, tenantId=1146029695717560320, journalId=1238823019242635269, issueId=1239175122226049974, language=EN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=), CN=IssueExt(id=1239175538779148684, tenantId=1146029695717560320, journalId=1238823019242635269, issueId=1239175122226049974, language=CN, specialIssueTitle=, coverIllustrator=null, specialIssueEditor=, specialIssueAbout=)}, issueFiles=null}, startPage=28, endPage=37, ext={EN=ArticleExt(id=1239175123157185466, articleId=1239175122997801913, tenantId=1146029695717560320, journalId=1238823019242635269, language=EN, title=Comparative Study on the Main Performance Improvement Methods of Transcritical CO2 Heat Pump Air-Conditioning System for New Energy Vehicles, columnId=null, journalTitle=Journal of Refrigeration, columnName=null, runingTitle=null, highlight=null, articleAbstract=

Transcritical CO2 heat pump air-conditioning systems have gained prominence in new energy vehicle thermal management due to their energy-saving and environmentally friendly characteristics. However, the relatively low coefficient of performance (COP) in cooling mode remains a significant obstacle to developing transcritical CO2 heat pump air conditioning systems. To enhance system performance, five technical approaches are proposed: internal heat exchangers (IHX), expanders, vortex tubes, ejectors, and combined multiple evaporation steps with vapor injection. The performances of these methods were evaluated through one-dimensional theoretical calculations under vehicle operating conditions. Results indicate that optimizing discharge pressure is critical for all methods, with varying degrees of COP improvement. Expanders provide the most comprehensive benefits, ejectors perform well under specific design conditions, IHX shows notable enhancements in cooling mode, and vortex tubes and combined multiple evaporation steps with vapor injection exhibit broad adaptability across working conditions. These findings offer valuable insights for practical engineering applications and support the adoption of transcritical CO2 heat pump systems in new energy vehicles.

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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: novel applications of the transcritical CO2 technology.
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为了提升新能源车辆跨临界CO2热泵空调系统的性能,针对回热器、膨胀机、涡流管、喷射器和多蒸发温度补气5种技术方法,采用一维理论计算,在新能源车辆运行工况下得到各系统性能并进行对比。结果表明:采用不同性能提升方法的系统均需考虑排气压力的优化,制冷模式下系统COP均得到一定程度提升。膨胀机在综合工况下具有最佳效果,喷射器在设计工况下表现良好,回热器在制冷模式下效果明显,涡流管和多蒸发温度补气全工况适应性较好。结果可为各个性能提升方法的实际工程应用提供一定参考,促进跨临界CO2热泵空调系统的推广应用。

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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:跨临界CO2应用新技术。
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system, figureFileSmall=null, figureFileBig=null, tableContent=
优化方法计算式
基础循环
COPC=QC/W
COPH=QH/W
回热器[28]
COPC=QC/W
COPH=QH/W
膨胀机
COPC=QC/W
COPH=QH/W
多蒸发温度补气
COPC=QC/W
COPH=QH/W
涡流管[31]
COPC=QC/W
COPH=QH/W
喷射器[32]
COPC=QC/W
COPH=QH/W
), ArticleFig(id=1239175136700592629, tenantId=1146029695717560320, journalId=1238823019242635269, articleId=1239175122997801913, language=CN, label=表1, caption=各个循环一维模型搭建及性能计算方法, figureFileSmall=null, figureFileBig=null, tableContent=
优化方法计算式
基础循环
COPC=QC/W
COPH=QH/W
回热器[28]
COPC=QC/W
COPH=QH/W
膨胀机
COPC=QC/W
COPH=QH/W
多蒸发温度补气
COPC=QC/W
COPH=QH/W
涡流管[31]
COPC=QC/W
COPH=QH/W
喷射器[32]
COPC=QC/W
COPH=QH/W
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新能源车辆跨临界CO2热泵空调系统主要性能提升方法对比
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杨梦莹 1 , 丁静雯 2 , 谢宏生 1 , 宋昱龙 1 , 曹锋 1 , 戴向阳 3
制冷学报 | 2025,46(2): 28-37
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制冷学报 | 2025, 46(2): 28-37
新能源车辆跨临界CO2热泵空调系统主要性能提升方法对比
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杨梦莹1, 丁静雯2, 谢宏生1, 宋昱龙1 , 曹锋1, 戴向阳3
作者信息
  • 1西安交通大学能源与动力工程学院 710049 西安
  • 2中国汽车技术研究中心有限公司 300300 天津
  • 3深圳市英维克科技股份有限公司 518110 深圳

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:跨临界CO2应用新技术。
Comparative Study on the Main Performance Improvement Methods of Transcritical CO2 Heat Pump Air-Conditioning System for New Energy Vehicles
Mengying Yang1, Jingwen Ding2, Hongsheng Xie1, Yulong Song1 , Feng Cao1, Xiangyang Dai3
Affiliations
  • 1.School of Energy and Power Engineering, Xi'an Jiaotong University, Xi'an, 710049, China
  • 2.China Automotive Technology & Research Center Co., Ltd., Tianjin, 300300, China
  • 3.Shenzhen Envicool Technology Co., Ltd., Shenzhen, 518110, China
出版时间: 2025-04-16 doi: 10.12465/j.issn.0253-4339.2025.02.028
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为了提升新能源车辆跨临界CO2热泵空调系统的性能,针对回热器、膨胀机、涡流管、喷射器和多蒸发温度补气5种技术方法,采用一维理论计算,在新能源车辆运行工况下得到各系统性能并进行对比。结果表明:采用不同性能提升方法的系统均需考虑排气压力的优化,制冷模式下系统COP均得到一定程度提升。膨胀机在综合工况下具有最佳效果,喷射器在设计工况下表现良好,回热器在制冷模式下效果明显,涡流管和多蒸发温度补气全工况适应性较好。结果可为各个性能提升方法的实际工程应用提供一定参考,促进跨临界CO2热泵空调系统的推广应用。

Transcritical CO2 heat pump air-conditioning systems have gained prominence in new energy vehicle thermal management due to their energy-saving and environmentally friendly characteristics. However, the relatively low coefficient of performance (COP) in cooling mode remains a significant obstacle to developing transcritical CO2 heat pump air conditioning systems. To enhance system performance, five technical approaches are proposed: internal heat exchangers (IHX), expanders, vortex tubes, ejectors, and combined multiple evaporation steps with vapor injection. The performances of these methods were evaluated through one-dimensional theoretical calculations under vehicle operating conditions. Results indicate that optimizing discharge pressure is critical for all methods, with varying degrees of COP improvement. Expanders provide the most comprehensive benefits, ejectors perform well under specific design conditions, IHX shows notable enhancements in cooling mode, and vortex tubes and combined multiple evaporation steps with vapor injection exhibit broad adaptability across working conditions. These findings offer valuable insights for practical engineering applications and support the adoption of transcritical CO2 heat pump systems in new energy vehicles.

杨梦莹, 丁静雯, 谢宏生, 宋昱龙, 曹锋, 戴向阳. 新能源车辆跨临界CO2热泵空调系统主要性能提升方法对比. 制冷学报, 2025 , 46 (2) : 28 -37 . DOI: 10.12465/j.issn.0253-4339.2025.02.028
Mengying Yang, Jingwen Ding, Hongsheng Xie, Yulong Song, Feng Cao, Xiangyang Dai. Comparative Study on the Main Performance Improvement Methods of Transcritical CO2 Heat Pump Air-Conditioning System for New Energy Vehicles[J]. Journal of Refrigeration, 2025 , 46 (2) : 28 -37 . DOI: 10.12465/j.issn.0253-4339.2025.02.028
随着科学技术的发展,能源短缺和环境污染问题逐渐加剧[1]。近年来,交通运输领域已成为人为CO2排放的主要贡献者之一[2]。在“双碳”目标背景下,新能源车辆的发展备受关注[3]。不同于传统内燃机车辆,新能源汽车没有发动机余热[4],寒冷条件下通常需要采用PTC(positive temperature coefficient)加热器进行辅助加热,会导致续航里程显著缩短[5]。此外,包含乘员舱和电池、电动机、电控系统的新能源整车热管理系统向着一体化不断发展[6],对其紧凑、高效的要求越来越严格[7]。因此对于新能源车辆,能够实现制冷、制热功能且能效比更高的热泵空调系统的发展至关重要[8]
R134a是新能源乘用车广泛使用的制冷剂,但其GWP(全球变暖潜值,Global Warming Performance)高达1 430,被《蒙特利尔议定书基加利修正案》列为限制使用的强温室效应气体[9]。此外,R134a在冬季蒸发压力会急剧下降,导致质量流量严重减小,制热能力不能满足需求[10],仍需采用PTC加热器协同制热[11]。因此从节能和环保两方面均亟待寻找新的制冷剂。
CO2作为一种天然流体,GWP为1、ODP(臭氧损耗潜值,ozone destruction potential)为0,具有环保、安全[12]、热稳定性高[13]等优点。20世纪90年代,G. Lorentzen等[14]提出了跨临界CO2循环,并将其应用于汽车空调。此后,跨临界CO2系统不断发展和繁荣。CO2在低温下也具有优异的制热性能[15],跨临界CO2热泵可在-20 ℃甚至-25 ℃的环境温度下提供足够的制热量,并具有较高的COP[16]。因此,无论从节能还是环保角度,CO2均具有良好的发展前景。针对跨临界CO2系统也展开了多方面的研究,如组件优化[17-18],最优排气压力[19-20],最优充注量[1,21]等。
但跨临界CO2循环制冷能效比略有不足,并且随着环境温度升高,劣化程度加深[22],一定程度上限制了新能源车辆跨临界CO2热泵空调系统的推广。很多学者围绕可能的优化措施展开了研究。有研究表明,在跨临界CO2系统中引入IHX(回热器,internal heat exchanger)的效果是积极的,环境温度越高效果越好[23]。采用膨胀机的跨临界CO2循环的COP(性能系数,coefficient of performance)理论计算上可比基本系统高6%~10%[24]。大量实验研究表明,在设计工况下引入喷射器一般能显著改善跨临界CO2循环的性能[25]。Yu Binbin等[26]提出一种采用涡流管的跨临界CO2制冷系统构型。但各优化技术仍具有掣肘,投入市场之前需要更多的研究论证。
本文针对回热器、膨胀机、多蒸发温度补气、涡流管和喷射器5种性能提升方法,详细介绍采用各个方法的系统流程图以及p-h图,对各个系统性能进行一维计算,并在新能源乘用车工况下与基准循环进行对比。
常规新能源乘用车跨临界CO2热泵空调系统如图1(a)所示。低温低压的CO2被跨临界压缩机压缩进入超临界区域,在气体冷却器中与外部介质发生类显热放热。蒸发器后气液分离器的存在能够极大程度避免压缩机吸气带液[27]。此外,采用一个四通阀进行系统制冷、制热模式的切换。
系统循环p-h图如图2(a)所示,详细表明了CO2的热力学性质在循环中各个部位的变化过程。CO2高压放热部分是位于临界点之上的冷却过程,不同于传统制冷剂的冷凝过程,此时压力与温度相互独立。
虽然跨临界CO2基本循环产生的节流损失大于常规亚临界循环,蒸发器入口制冷剂干度较大,导致系统制冷能效比较低,但大量的改进技术有望使跨临界CO2循环的实际效率等于甚至优于常规的亚临界循环[26],下文对上述技术进行详细阐述。
1)回热器。
在基础新能源乘用车跨临界CO2热泵空调系统上引入回热器,让气体冷却器出口的CO2和气液分离器出口的饱和CO2气体进行热交换[28],降低阀前温度,提高压缩机吸气过热度。引入回热器的系统具体流程如图1(b)所示。此时为保证制冷或制热模式下,流经回热器两侧的制冷剂温度不同,采用2个四通阀进行系统制冷、制热模式的切换。
引入回热器的系统循环p-h图如图2(b)所示。其中3-4和6-1为回热器内的换热过程。以制冷模式为例,由于阀前温度的降低,循环的比制冷量增加,同时,压缩机吸气过热度提高,循环的比功也有变化[29],COP整体呈提高的趋势。需要注意的是,压缩机吸气过热度增加会导致吸气密度减小,质量流量减小。随着回热率增加,压缩机吸排气温度不断升高,受排气温度限制,回热率可能具有限度。
2)膨胀机。
膨胀机能以一定等熵效率回收膨胀机入口高压流体的压力能,通过连轴将其转化为轴功,来替代压缩机的部分功耗,且能增加循环比制冷量,从而提高循环的能效比。采用膨胀机代替节流阀的新能源乘用车跨临界CO2热泵空调系统具体流程如图1(c)所示。由于膨胀机的高低压制冷剂进出口固定,因此采用2个四通阀进行制冷、制热模式的切换。
采用膨胀机代替节流阀的系统循环p-h图如图2(c)所示,图中4s点为等熵节流后对应的状态点,4h点为等焓节流后对应的状态点。膨胀机的等熵效率很大程度决定着系统的性能提升程度,因此需要对膨胀机的结构进行优化以期达到更高的等熵效率。膨胀过程中具有易受摩擦损失的两相区域,而跨临界循环中的膨胀过程单相部分占比更大,在两相过程中,CO2液体和气体的密度与常规制冷剂循环的密度相差较小。因此,膨胀机应用于跨临界CO2循环较常规制冷剂循环更具优势。
3)多蒸发温度补气。
能够满足宽温域下车厢和电池多目标温度控制的综合热管理系统逐渐受到关注,实际中热管理系统含有车内换热器和用于电池温度控制的水冷换热器[30]。两级压缩中间补气是跨临界CO2制冷性能优化的可行技术方案之一,采用多蒸发温度补气的新能源乘用车CO2热泵空调系统具体流程如图1(d)所示。实际运行中车厢和电池回路的制冷、制热模式组合情况多变,本文以车厢制冷或制热时电池均需制冷的情况为例,采用2个四通阀进行制冷、制热模式的切换。
系统循环p-h图如图2(d)所示,可知蒸发温度较高的支路质量流量占比越大,系统COP越高,但对系统的制冷能力起反作用。实际新能源乘用车跨临界CO2热泵空调系统应用时,压缩机两级排量比设计能使系统同时满足高温制冷模式下的制冷能力和性能要求。
4)涡流管。
涡流管是一种能够回收高压流体压力能的节流装置。涡流管可以依靠内部双向涡之间复杂的传热传质作用,将进口气体分离成两股不同温度的气流,并分别从两个出口流出。若温度较低的那股流体状态位于两相区,则在高速涡的离心作用下,将会分离为饱和液体和饱和气体并分别从近壁区和中心区流高压流体入口以及不同状态温度流体的出口均固定,因此采用2个四通阀进行制冷、制热模式的切换。出[25]。有理论结果表明,Maurer模型在系统COP和总成本方面更优[31],因此本文选择Maurer模型计算优化结果。采用涡流管的新能源乘用车跨临界CO2热泵空调系统具体流程如图1(e)所示。由于涡流管系统循环p-h图如图2(e)所示,气体冷却器出口的CO2经过涡流管节流,分成了3股不同状态的流体、饱和液体(4)、饱和气体(C)和过热气体(H)。饱和液体(4)和饱和气体(C)再次混合至两相状态(6)进入蒸发器吸热,达到制冷效果。过热气体在去过热器中被冷却(5),并与蒸发器出来的CO2混合(1)再进入压缩机完成压缩过程。
5)喷射器。
采用喷射器作为节流装置,气体冷却器出口的一次流体的压力通过喷嘴转化为动能,蒸发器出口的二次流体可以被夹带并与一次流体混合达到一定的速度,然后将混合流体的动能再次转化为压力,实现膨胀功的回收[25]。喷射器的使用减少了节流前后的压差,压缩机的功耗减少,相当于回收了使用膨胀阀节流损失的部分压能,从而提高了系统COP。采用喷射器的新能源乘用车跨临界CO2热泵空调系统具体流程如图1(f)所示,喷射器主喷嘴、次喷嘴等位置固定,因此采用2个四通阀进行制冷、制热模式的切换。
系统循环p-h图如图2(f)所示,一次流经压缩机压缩后进入气体冷却器、喷射器主喷嘴和气液分离器(1-2-3-4-6-7-1)循环,二次流在节流阀、蒸发器、喷射器次喷嘴和气液分离器(8-8a-9-5-6-7-8)中循环,一次流和二次流在混合室(6)处混合。此时压缩机的吸气压力(1)高于基础循环(9)的吸气压力,意味着采用喷射器循环的压缩机功耗小于基础循环的功耗。
对新能源乘用车跨临界CO2热泵空调系统以及不同性能提升方法的研究,主要可采用一维理论和仿真计算、三维数值模拟、实验研究等。本文采用MATLAB软件调用REFPROP软件的制冷剂物性进行一维理论计算。从p-h图的角度进行研究,不考虑压力损失,对于多变过程,采用常数值的等熵效率进行表示。实际中部件需要结构优化以期保证变工况下的效率稳定及优化。在不同的系统循环下,制冷制热量计算有所不同,具体的计算式如表1所示。
制冷模式下环境温度设为30~45 ℃,制热模式下环境温度设为-20~7 ℃,分析每个性能提升方法下系统性能的变化趋势,并综合对比采用各性能提升方法下系统COP的优化程度。
由于CO2的热物性,跨临界CO2循环在气体冷却器出口温度较高时,存在最优排气压力令COP最大[33],因此各性能提升方法以及不同运行工况下的运行数据结果均考虑排气压力的优化。
1)回热器。
制冷模式以环境温度35 ℃为例,制热模式以环境温度0 ℃为例,改变回热率的大小以及排气压力,计算结果如图3所示。制冷模式下,回热器的使用能够明显提升新能源乘用车CO2空调系统的性能,回热率越高,系统COP越高。此外,引入回热器之后,系统的最优排气压力下降,随着回热率的增加,最优排气压力不断下降。制热模式下,回热器的使用也可以使系统COP略有提升,降低系统的最优排气压力。但此时回热率达到1的理想情况带来的提升效果也不显著。本次计算时制热模式气体冷却器出口温度较高,实际气体冷却器出口温度可能会更低,采用回热器系统性能甚至可能不如基础循环[28]。因此实际应用时,当新能源乘用车CO2系统切换为制热模式,令回热器两侧制冷剂温度均为蒸发温度,回热器失效。
2)膨胀机。
制冷模式以环境温度35 ℃为例,制热模式以环境温度0 ℃为例,改变排气压力,采用膨胀机后系统的性能计算结果如图4所示。随着排气压力的提高,系统制冷量、制热量和功耗均不断提高,初始制冷量和制热量随着排气压力的提高出现大幅增加,后续增幅逐渐减小,功耗增幅较为稳定,COP在综合作用下呈先升高后下降的趋势。因此存在最优排气压力,使系统COP达到最大,各环境工况下的系统COP均为最优排气压力下的最优值。
3)多蒸发温度补气。
制冷模式以环境温度35 ℃为例,制热模式以环境温度0 ℃为例,采用多蒸发温度补气系统性能计算结果如图5所示。实际中两支路的质量流量之比取决于新能源乘用车电池和车厢所需换热量的比值,而电池换热量需求和车厢需求相比一般较小,简化将电池路制冷剂流量占比设定为0.15,该路蒸发温度设定为11 ℃[34]。随着排气压力的提高,系统制冷量、制热量和功耗均不断提高,但制冷量和制热量增幅也逐渐减小,因此COP呈先升高后下降的趋势,存在最优排气压力。最终各环境工况下的系统COP均为最优排气压力下的最优值。
4)涡流管。
制冷模式以环境温度35 ℃为例,制热模式以环境温度0 ℃为例,采用涡流管后系统性能计算结果如图6所示。此时各工况下去过热器出口温度均定为气冷出口温度。类似的,单个工况下,随着排气压力的提高,COP呈先升高后下降的趋势。最终各环境工况下的系统COP均为最优排气压力下的最大值。
5)喷射器。
制冷模式以环境温度35 ℃为例,制热模式以环境温度0 ℃为例,采用喷射器后系统性能计算结果如图7所示。喷射器的设计工况环境温度定为45 ℃。类似的,随着排气压力的提高,COP呈先升高后下降的趋势。最终各环境工况下系统COP均为最优排气压力对应的最大值。
针对跨临界CO2循环制冷能效比较低的问题,不同的性能提升方法在制冷模式下均能够有效提升新能源乘用车跨临界CO2热泵空调系统的性能,但随着环境温度的变化,各性能提升方法的提升效果也会发生变化。在制热模式下各性能提升方法也具有一定的影响。因此将各个性能提升方法进行综合对比,结果如图8所示。
采用膨胀机对系统性能提升的效果最为显著,在全工况范围内均为各个性能提升方法最佳。制冷模式下,当环境温度为45 ℃时,系统COP能提高14.9%,随着环境温度下降,提升效果逐渐减弱。制热模式下,性能提升基本约为7%。
当环境温度较高,接近喷射器的设计工况时,喷射器也能够有较为优良的提升效果,具有和膨胀机接近的提升效果,当环境温度为45 ℃时,系统COP提高约12.3%。当工况逐渐偏离设计工况时,提升效果逐渐衰减甚至不如基本循环,如制热模式环境温度较低的-20~-10 ℃。喷射器内部原理和流动过程较为复杂,且成本及适应性问题仍需进一步的研究优化。
回热器的使用在制冷模式下对系统的性能也具有提升效果,当环境温度为45 ℃时,系统COP提高约8.4%,但随着环境温度即气体冷却器出口温度的下降性能提升程度衰减。制热模式下作用微小。需要注意的是,部分工况,如高温45 ℃,低温-20 ℃等,由于排气温度的限制,即使在理论计算下也无法达到1的回热率。回热器的作用机理较为明晰,使用较为方便,已广泛应用于跨临界CO2热泵空调系统。
采用涡流管的循环系统,各工况下去过热器出口温度均定为气冷出口温度。制冷模式下,采用涡流管技术对新能源乘用车CO2空调系统性能的提升百分比随着环境温度的升高而不断增大。与基础循环相比,当环境温度为45 ℃时,系统COP能够提升7.8%。制热模式下,采用涡流管技术对统性能的提升百分比随着环境温度降低而不断增大。
采用多蒸发温度的提升效果变化总体和涡流管较为类似,制冷模式也是环境温度越高提升效果越明显,环境温度为45 ℃时,系统COP能够提升6.3%。制热模式下,性能优化百分比随着环境温度的降低效果逐渐提升,趋势逐渐变缓。
本文基于一维理论计算,分析了不同性能提升方法应用于新能源乘用车跨临界CO2热泵空调系统及不同运行工况下的提升效果和变化趋势,得到如下结论:
1)不同的性能提升方法下系统均需考虑排气压力的优化,优化后的COP均为最优排气压力下的数值。
2)不同的性能提升方法均能够一定程度提升跨临界CO2热泵空调系统在制冷模式下较低的COP,在制冷模式下优化效果均随环境温度的升高而提升。
3)在不同运行工况下,各个性能优化技术对系统的提升效果各不相同。膨胀机在全工况范围内均最佳,喷射器在设计工况下表现良好,回热器在制冷模式下效果明显,涡流管和多蒸发温度补气适应性较好。
4)在跨临界CO2热泵空调系统具有优势的制热模式下,膨胀机、涡流管、多蒸发温度补气等技术也具有一定的提升效果。
这些性能提升方法技术在系统制冷COP提升上具有广阔的应用前景,一维理论计算仍具有局限性,需要进一步的三维仿真以及实验研究。此外,各个性能提升方法技术应用的经济成本和结构复杂程度均需进行考量。
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doi: 10.12465/j.issn.0253-4339.2025.02.028
  • 接收时间:2023-11-11
  • 首发时间:2026-03-13
  • 出版时间:2025-04-16
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  • 收稿日期:2023-11-11
  • 修回日期:2023-12-14
  • 录用日期:2024-01-29
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    1西安交通大学能源与动力工程学院 710049 西安
    2中国汽车技术研究中心有限公司 300300 天津
    3深圳市英维克科技股份有限公司 518110 深圳

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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:跨临界CO2应用新技术。
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