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Article(id=1319293224221520832, tenantId=1146029695717560320, journalId=1316781260334530699, issueId=1319293151651676781, articleNumber=null, orderNo=null, doi=10.3969/j.issn.1005-0329.2025.05.003, pmid=null, cstr=null, oa=null, hot=null, price=null, onlineType=0, articleFormat=0, articleType=null, articleTypeStr=null, receivedDate=1725379200000, receivedDateStr=2024-09-04, revisedDate=1742054400000, revisedDateStr=2025-03-16, acceptedDate=null, acceptedDateStr=null, onlineDate=1792473615937, onlineDateStr=2026-10-20, pubDate=1748534400000, pubDateStr=2025-05-30, doiRegisterDate=null, doiRegisterDateStr=null, onlineIssueDate=1792473615937, onlineIssueDateStr=2026-10-20, onlineJustAcceptDate=null, onlineJustAcceptDateStr=null, onlineFirstDate=null, onlineFirstDateStr=null, sourceXml=null, magXml=null, createTime=1792473615937, creator=13701087609, updateTime=1792473615937, updator=13701087609, issue=Issue{id=1319293151651676781, tenantId=1146029695717560320, journalId=1316781260334530699, year='2025', volume='53', issue='5', pageStart='1', pageEnd='118', issueExtLink='null', onlineDate='null', pubDate='1748534400000', pubDateStr='2025-05-30', beforeIssueId=null, nextIssueId=null, price=null, status=1, issueComplete=1, articleOrder=1, issueType=-1, specialIssue=null, createTime=1792473598634, creator='13701087609', updateTime=1792473598634, updator='13701087609', preIssue=null, nextIssue=null, articleTotal=null, ext=null, issueFiles=null, downloadFileDto=null}, startPage=15, endPage=21, ext={EN=ArticleExt(id=1319293227845399489, articleId=1319293224221520832, tenantId=1146029695717560320, journalId=1316781260334530699, language=EN, title=Experimental study on refrigerant direct‑condensation floor radiant heating air‑source heat pump, columnId=null, journalTitle=Fluid Machinery, columnName=null, runingTitle=null, highlight=null, articleAbstract=

To address the dual challenges of high building energy consumption and increasing occupant comfort demands，a direct‑condensation capillary radiant floor heating terminal was designed.A refrigerant direct‑condensation floor heating air‑source heat pump system was constructed in an environmental chamber.Temperature characteristics of the heating terminal and heat pump heating performance variations under different outdoor temperatures were investigated，with comparative analysis against bare‑tube capillary radiant terminals.Results show that under varying outdoor temperatures，bare‑tube capillary walls heat faster than capillary walls under cement layers.Cement floor surface temperature stabilization lags behind capillary wall temperature stabilization.At 0 ℃ outdoor temperature，the temperature difference between exhaust and subcooled sections of bare‑tube capillaries is only 1.6 ℃，whereas for cement floors it reaches 4.4 ℃.At -10 ℃ outdoor temperature，the cement‑embedded capillary floor system achieves heating capacity of 1.67 kW and COP of 4.20，representing 21.6% and 13.9% decreases compared to bare‑tube capillary terminals.This study provides reference for designing capillary radiant floor heating systems.

, authors=Jianhui NIU, Tianshu LYU, Haichao WANG, Yongliang LI, Yuegang BU, authorsList=Jianhui NIU, Tianshu LYU, Haichao WANG, Yongliang LI, Yuegang BU, authorCompany=null, correspAuthors=Yuegang BU, authorNote=null, correspAuthorsNote=null, copyrightStatement=null, copyrightOwner=null, extLink=null, articleAbsUrl=null, sourceXml=null, magXml=null, pdfUrl=null, pdf=null, pdfFileSize=null, pdfExtLink=null, richHtmlUrl=null, mobilePdfUrl=null, reviewReport=null, pdfFirstPage=null, abstractGraph=null, abstractGraphContent=null, abstractVideo=null, citation=null, cebUrl=null, magXmlContent=null, mapNumber=null, fund=null), CN=ArticleExt(id=1319293231502832604, articleId=1319293224221520832, tenantId=1146029695717560320, journalId=1316781260334530699, language=CN, title=制冷剂直凝地板辐射供暖空气源热泵试验研究, columnId=1317484286475883136, journalTitle=流体机械, columnName=试验研究, runingTitle=null, highlight=null, articleAbstract=

针对建筑能耗大、居民舒适性要求提高的现状，设计一种直凝毛细管地板辐射供暖末端，并在环境控制室搭建制冷剂直凝地板辐射供暖空气源热泵系统，研究不同室外温度下直凝毛细管地板辐射供暖末端温度特性及热泵制热性能变化，并与光管毛细管辐射末端性能进行对比分析。结果表明，不同室外温度下，光管毛细管壁升温速率高于水泥层下毛细管壁升温速率，水泥地板表面温度稳定时间滞后于其下毛细管壁温稳定时间；当室外温度为0 ℃时，光管毛细管壁排气段与过冷段之间温差仅为1.6 ℃，而水泥地板表面两者温差则为4.4 ℃；当室外温度为-10 ℃时，敷设水泥层后的毛细管地板供暖系统制热量与制热COP分别达到1.67 kW和4.20，比光管毛细管末端系统分别下降21.6%和13.9%。研究结果可为毛细管地板辐射供暖系统的设计与应用提供参考。

, authors=牛建会, 吕天舒, 王海超, 李永亮, 卜跃刚, authorsList=牛建会, 吕天舒, 王海超, 李永亮, 卜跃刚, authorCompany=null, correspAuthors=卜跃刚, authorNote=

牛建会（1981），女，博士，副教授，研究方向为新型制冷热泵系统及其节能环保技术，E-mail：。

, correspAuthorsNote=
卜跃刚（1992），男，硕士，讲师，研究方向为新能源利用技术，通信地址：075000河北省张家口市经开区朝阳西大街13号河北建筑工程学院能源工程系，E-mail：。
, copyrightStatement=作者向本刊所投稿件一经本刊录用，则该论文的复制权、发行权、信息网络传播权、翻译权、汇编权等权利视为自动转让给本刊。本刊为国内各主要数据库收录期刊，本刊所发表的稿件将同时通过互联网进行网络出版或提供信息服务。, copyrightOwner=null, extLink=null, articleAbsUrl=null, sourceXml=BaYvXDpKzSvhaNMVnurOEQ==, magXml=72KbvmAAZzF0Ijl+rlM93g==, pdfUrl=null, pdf=null, pdfFileSize=null, pdfExtLink=null, richHtmlUrl=null, mobilePdfUrl=null, reviewReport=null, pdfFirstPage=null, abstractGraph=1JMWd/O49yHUBUJcEg3fAA==, abstractGraphContent=null, abstractVideo=null, citation=null, cebUrl=null, magXmlContent=ZENoL3vB1bQc/osYRxd/vQ==, mapNumber=null, fund=null)}, authors=[Author(id=1319293231792239585, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293224221520832, orderNo=0, firstName=null, middleName=null, lastName=null, nameCn=null, orcid=null, stid=null, country=null, authorPic=null, dead=0, email=zjknjh@163.com, emailSecond=null, emailThird=null, correspondingAuthor=0, authorType=1, ext={EN=AuthorExt(id=1319293231863542755, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293224221520832, authorId=1319293231792239585, language=EN, stringName=Jianhui NIU, firstName=Jianhui, middleName=null, lastName=NIU, prefix=null, suffix=null, authorComment=null, nameInitials=null, affiliation=null, department=null, xref=null, address=Hebei Renewable Energy Heating Engineering Technology Center，Hebei University of Architecture，Zhangjiakou 075000，China, bio=null, bioImg=null, bioContent=null, aboutCorrespAuthor=null), CN=AuthorExt(id=1319293231934845924, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293224221520832, authorId=1319293231792239585, language=CN, stringName=牛建会, firstName=null, middleName=null, lastName=null, prefix=null, suffix=null, authorComment=null, nameInitials=null, affiliation=null, department=null, xref=null, address=河北建筑工程学院 河北省可再生能源供热工程技术中心，河北 张家口 075000, bio={"content":"

牛建会（1981），女，博士，副教授，研究方向为新型制冷热泵系统及其节能环保技术，E-mail：。

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牛建会（1981），女，博士，副教授，研究方向为新型制冷热泵系统及其节能环保技术，E-mail：。

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1-压缩机；2-四通阀；3-蒸发器；4-电子膨胀阀；5-毛细管地板辐射供暖末端；6-流量计；7-干燥过滤器；8-视液镜；9-压力表；10-压力变送器；11-温度传感器

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ArticleFig(id=1319293237563600923, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293224221520832, language=EN, label=Tab.1, caption=

Parameter of measuring instrument

, figureFileSmall=null, figureFileBig=null, tableContent=
项目设备型号测量范围精度/%
末端温度铜-康铜-150~200 ℃±0.2
机组温度PT100-150~150 ℃±0.15
压力Huba-0.1~4.0 MPa±0.2
压缩机功率PD60000~10 kW±0.5
制冷剂流量FRK-ER010~150 kg/h±0.2
数据采集Agilent34972A±0.2
), ArticleFig(id=1319293237639098396, tenantId=1146029695717560320, journalId=1316781260334530699, articleId=1319293224221520832, language=CN, label=表1, caption=

测量仪表参数

, figureFileSmall=null, figureFileBig=null, tableContent=
项目设备型号测量范围精度/%
末端温度铜-康铜-150~200 ℃±0.2
机组温度PT100-150~150 ℃±0.15
压力Huba-0.1~4.0 MPa±0.2
压缩机功率PD60000~10 kW±0.5
制冷剂流量FRK-ER010~150 kg/h±0.2
数据采集Agilent34972A±0.2
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制冷剂直凝地板辐射供暖空气源热泵试验研究
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牛建会 , 吕天舒 , 王海超 , 李永亮 , 卜跃刚
流体机械 | 试验研究 2025,53(5): 15-21
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流体机械 |试验研究 2025 , 53 (5) : 15 -21
制冷剂直凝地板辐射供暖空气源热泵试验研究
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牛建会 , 吕天舒, 王海超, 李永亮, 卜跃刚
作者信息
  • 河北建筑工程学院 河北省可再生能源供热工程技术中心，河北 张家口 075000
通讯作者:
卜跃刚（1992），男，硕士，讲师，研究方向为新能源利用技术，通信地址：075000河北省张家口市经开区朝阳西大街13号河北建筑工程学院能源工程系，E-mail：。
作者简介:

牛建会（1981），女，博士，副教授，研究方向为新型制冷热泵系统及其节能环保技术，E-mail：。

Experimental study on refrigerant direct‑condensation floor radiant heating air‑source heat pump
Jianhui NIU , Tianshu LYU, Haichao WANG, Yongliang LI, Yuegang BU
Affiliations
  • Hebei Renewable Energy Heating Engineering Technology Center，Hebei University of Architecture，Zhangjiakou 075000，China
出版时间: 2025-05-30 doi: 10.3969/j.issn.1005-0329.2025.05.003
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针对建筑能耗大、居民舒适性要求提高的现状，设计一种直凝毛细管地板辐射供暖末端，并在环境控制室搭建制冷剂直凝地板辐射供暖空气源热泵系统，研究不同室外温度下直凝毛细管地板辐射供暖末端温度特性及热泵制热性能变化，并与光管毛细管辐射末端性能进行对比分析。结果表明，不同室外温度下，光管毛细管壁升温速率高于水泥层下毛细管壁升温速率，水泥地板表面温度稳定时间滞后于其下毛细管壁温稳定时间；当室外温度为0 ℃时，光管毛细管壁排气段与过冷段之间温差仅为1.6 ℃，而水泥地板表面两者温差则为4.4 ℃；当室外温度为-10 ℃时，敷设水泥层后的毛细管地板供暖系统制热量与制热COP分别达到1.67 kW和4.20，比光管毛细管末端系统分别下降21.6%和13.9%。研究结果可为毛细管地板辐射供暖系统的设计与应用提供参考。

空气源热泵  /  制冷剂直凝  /  地板辐射  /  制热性能

To address the dual challenges of high building energy consumption and increasing occupant comfort demands，a direct‑condensation capillary radiant floor heating terminal was designed.A refrigerant direct‑condensation floor heating air‑source heat pump system was constructed in an environmental chamber.Temperature characteristics of the heating terminal and heat pump heating performance variations under different outdoor temperatures were investigated，with comparative analysis against bare‑tube capillary radiant terminals.Results show that under varying outdoor temperatures，bare‑tube capillary walls heat faster than capillary walls under cement layers.Cement floor surface temperature stabilization lags behind capillary wall temperature stabilization.At 0 ℃ outdoor temperature，the temperature difference between exhaust and subcooled sections of bare‑tube capillaries is only 1.6 ℃，whereas for cement floors it reaches 4.4 ℃.At -10 ℃ outdoor temperature，the cement‑embedded capillary floor system achieves heating capacity of 1.67 kW and COP of 4.20，representing 21.6% and 13.9% decreases compared to bare‑tube capillary terminals.This study provides reference for designing capillary radiant floor heating systems.

air‑source heat pump  /  refrigerant direct‑condensation  /  floor radiation  /  heating performance
牛建会, 吕天舒, 王海超, 李永亮, 卜跃刚. 制冷剂直凝地板辐射供暖空气源热泵试验研究. 流体机械, 2025 , 53 (5) : 15 -21 . DOI: 10.3969/j.issn.1005-0329.2025.05.003
Jianhui NIU, Tianshu LYU, Haichao WANG, Yongliang LI, Yuegang BU. Experimental study on refrigerant direct‑condensation floor radiant heating air‑source heat pump[J]. Fluid Machinery, 2025 , 53 (5) : 15 -21 . DOI: 10.3969/j.issn.1005-0329.2025.05.003
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0　引言
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空气源热泵作为众多清洁能源应用产品之一，以其高效、节能、环保、适用性广、性价比高等优势脱颖而出，可有效代替燃煤锅炉供暖，在户式住宅、别墅、学校、酒店等商业建筑中已广泛应用［1-4］。目前，空气源热泵供暖末端方式主要有3种：空气源热泵散热器供暖、风机盘管热风供暖、热水地板辐射供暖［5-7］。这3种供暖末端通常存在吹风感觉明显、皮肤体感差、水泵噪声大、功耗高等问题［8-10］。同时，空气源热泵在严寒地区运行能效受室外温度影响较大［11］。因此，近年科学研究集中在热泵机组性能提升和供暖末端的新材料与新结构方面［12-13］。
直凝毛细管地板辐射供暖是将高温高压制冷剂直接输送至毛细管供暖末端进行循环供热，省去了中间换热过程，系统能效更高。魏新利等［14］以制冷剂为热媒，搭建了空气源热泵直接地板辐射供暖系统实验平台，研究表明，地板盘管进出口温差稳定，地板表面温度、室内温度均满足郑州冬季室内供暖设计要求；ZHENG等［15］采用复合相变材料作为地板模块，使制冷剂直接冷凝并向地板释放热量，结果表明，该系统不仅提高了除霜过程中室内的热舒适性，而且满足冬季的采暖需求；MA等［16-17］建立了空气源热泵直接地板辐射供暖系统物理模型，数值模拟分析结果显示，系统运行时制热量随室外温度上升而逐渐增大，耗电量随室外温度上升逐渐减少，逐时能效比随室外温度的上升逐渐变大；ZHAO等［18］搭建了空气源热泵毛细管辐射供暖与热水地板辐射供暖两种不同系统并进行对比试验，结果表明，毛细管辐射供暖末端供回水温度高于地板辐射供暖末端，但耗电量比较低；BAE等［19］对地板辐射供暖和对流供暖的系统性能参数进行比较，结果发现，地板辐射供暖系统的供暖系数比对流换热供暖系统约高19%；王琳等［20］设计了一种新型制冷剂毛细管地板供暖的空气源热泵系统，通过现场测试，室内设定温度为24，22 ℃工况时，系统稳定运行阶段的平均COP分别为2.52，2.92，全天COP平均值为3.38，3.50。
目前，国内外学者对毛细管地板辐射供暖系统研究主要集中在理论计算、仿真模拟与实际工程测试等方面，而直凝毛细管壁温度及地板表面温度变化特性研究尚不充分。本文设计一种直凝毛细管地板辐射供暖末端，并加工出热泵系统在环境控制室对其性能进行测试，研究在不同室外温度下，直凝毛细管地板辐射供暖末端温度变化特性及热泵机组制热性能变化。
1　系统原理
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制冷剂直凝地板辐射供暖空气源热泵系统如图1所示。该系统由压缩机、蒸发器、毛细管地板辐射供暖末端、电子膨胀阀等主要设备组成。热泵机组运行时，压缩机排出的高温制冷剂直接进入毛细管地板辐射供暖末端进行凝结放热，从而加热房间，经过膨胀阀节流进入室外蒸发器，吸收室外空气热量汽化回到压缩机，完成供热循环。高温制冷剂在毛细管中通过地板结构层加热整个地板表面，热量由下向上传递，避免强制对流带来的吹风感，提高室内热舒适性，达到供暖目的。
2　实验台搭建
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试验装置搭建在某实验中心的环境控制室内，环境控制室分为室内环境间和室外环境间，温度均控制在-15~40 ℃，精度±0.2 ℃；湿度均控制在30%~85%，不确定度5%。
空气源热泵室外机组安装在室外环境间，由额定功率为1.0 HP某品牌滚动转子压缩机、翅片管式蒸发器、电子膨胀阀等组成。在室内环境间搭建毛细管地板辐射供暖末端地面，其尺寸为2 m（长）×1.5 m（宽），采用16根外径4 mm、壁厚0.2 mm的等长铜管平行布置于水泥层下，相邻毛细管间距为100 mm，为使分液均匀，采用两组8分支的分液器分流。自室内环境间地面依次往上敷设厚度50 mm聚苯乙烯保温板、铝箔镜面反射膜、铁丝网、毛细管和厚度20 mm水泥填充层。
在试验测试过程中，供暖末端温度采用T型热电偶、室外机组上温度采用PT100、压力采用Huba压力变送器测量，制冷剂为R410a，采用某品牌流量计测制冷剂质量流量，压缩机功率由功率表获得。在机组主要设备进出口装有温度、压力测量仪表，监测其参数动态变化。所有测量参数均由数据采集仪采集，最终由计算机导出Excel数据。试验装置如图2所示，试验所用测量仪表参数如表1所示。
为监测毛细管壁及地板表面温度变化，在毛细管壁及水泥地板表面均布置5个位置相同的温度测点，水泥层下毛细管壁温度测点为1a，2a，3a，4a，5a；地板表面温度测点为1b，2b，3b，4b，5b。为了与未铺设水泥填充层的光管毛细管辐射末端对比，相同位置处光管毛细管壁温度测点编号为1c，2c，3c，4c，5c。地板结构与温度测点布置见图3。
3　试验结果与误差分析
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试验中的温度、压力、功率和制冷剂流量等参数为测量仪表直接测得，间接测量参数如压缩机吸排气焓值、冷凝器进出口焓值，由测得的温度、压力经查询物性参数软件REFPROP 9.1获得，系统制热量由冷凝器进出口焓差乘以制冷剂质量流量获得：
Q=Mrhi-ho
式中，Q为制热量，kW；Mr为制冷剂质量流量，kg/s；hi，ho为冷凝器进口、出口制冷剂焓值，kJ/kg。
系统制热性能系数（COP）按下式计算：
COP=Q/P
式中，P为压缩机功率，kW。
数据采集间隔时间为10 s，取每20个连续测量数据的平均值作为一个测量值，采用文献［21］中误差计算公式，经计算，制热量测量误差为2.84%，制热COP测量误差为5.39%。
试验过程中室内环境间维持20 ℃，室外环境间分别为5，0，-5，-10 ℃，相对湿度30％，电子膨胀阀控制压缩机吸气过热度为5 ℃左右。
图4、图5示出室内温度20 ℃、室外温度0 ℃时，直凝毛细管地板辐射供暖水泥层下毛细管壁及地板表面温度变化。
由图4可以看出，热泵机组运行前，5个测点温度均在19 ℃左右。开机运行后，压缩机排出的高温制冷剂最先流经1a点所处的排气段，该点温升速率最快，运行120 min后稳定在26.5 ℃；恒温段的毛细管温度分布相对均匀，2a，3a，4a点温度基本维持在22.1~22.8 ℃之间；制冷剂在毛细管内冷凝放热后经过冷段流出，因此，位于过冷段的5a点在运行中的温升不明显，基本稳定在20.1 ℃。排气段与过冷段温差达6.4 ℃。
由图5可以看出，热泵机组开机运行后，地板表面温升速率均小于其水泥层下毛细管壁温升速率。温度稳定所需时间滞后20 min，排气段1b点仍表现出温升快、温度高的特点，稳定后平均温度为24.4 ℃；恒温段3个测点温度在22.1~22.6 ℃之间，温度分布更加均匀；过冷段5b点温升仍不明显，维持在20.0 ℃左右。与图4对比发现，地表温度相较水泥层下毛细管壁5个测点平均温度衰减0.5 ℃。水泥层的敷设可使排气段与过冷段温差减小，且恒温段更趋于均匀，但水泥层也会导致传热过程的热阻增大，地板表面升温速率减缓。
图6、图7示出室内温度20 ℃、室外温度-5 ℃时，直凝毛细管地板辐射供暖水泥层下毛细管壁及地板表面温度变化。
由图6可以看出，热泵机组开机运行120 min后，毛细管壁温度趋于稳定。5个测点的升温速率在0.035 ℃/min以内。温度稳定后，排气段1a点温度最高，平均温度24.6 ℃；恒温段2a，3a，4a点平均温度分别为21.5，20.9，21.2 ℃，温度相差不超过0.6 ℃；过冷段5a点温度最低，平均温度19.6 ℃，与1a点相比，排气进口段与过冷段温差为5.0 ℃。与室外0 ℃工况相比，各测点稳定后的温度下降约0.5~1.9 ℃。
由图7可以看出，热泵机组开机运行130 min后，地板表面温度达到稳定。5个测点的升温速率在0.018 ℃/min以内。温度稳定后，排气段1b点温度最高，基本维持在22.9 ℃左右；恒温段2b，3b，4b点温度分别为21.1，20.7，21.2 ℃，3个测点温度相差不超过0.5 ℃；过冷段5b点温度最低，为19.5 ℃左右，与1b点相比，排气进口段与过冷段温差为3.4 ℃。温度分布趋势与室外温度0 ℃时的地表温度基本相同，但随着室外温度降低，地表温升速率整体变缓，且稳定后的温度也降低0.5~1.5 ℃。
图8、图9示出室内温度20 ℃、室外温度-10 ℃时，直凝毛细管地板辐射供暖水泥层下毛细管壁及地板表面温度变化。
由图8可以看出，热泵机组开机运行130 min后，毛细管壁温度趋于稳定。稳定后，排气段1a点温度最高，平均温度23.3 ℃；恒温段2a，3a，4a点平均温度分别维持在20.8，20.0，20.4 ℃，温度相差不超过0.8 ℃；过冷段5a点平均温度19.1 ℃。相较室外-5 ℃工况，毛细管壁温度整体下降0.5~1.3 ℃。由图9可以看出，热泵机组开机运行140 min后，地板表面温度达到稳定。5个测点的升温速率在0.017 ℃/min以内。温度稳定后，排气段1b点温度最高，平均温度21.6 ℃；恒温段2b，3b，4b点平均温度分别为20.1，19.6，20.3 ℃，温度相差不超过0.7 ℃；过冷段5b点温度最低，平均温度18.9 ℃，与1b点相比，排气进口段与过冷段温差为2.7 ℃。室外温度由0 ℃下降到-10 ℃，水泥地板表面排气进口段与过冷段的温差则减小1.7 ℃。室外温度由-5 ℃降至-10 ℃，对地板表面温升速率的影响较小，但使地表测点温度普遍下降0.6~1.3 ℃。
观察以上水泥层下毛细管壁温度与地板温度趋势可发现，在该类型供暖末端的设计与施工过程中，由于水泥的导热性和储热性，其设计应综合考虑机组的总制热量和室内毛细管的换热面积，并将其适用的室外环境温度范围考虑进去，使得地板的排气段、恒温段及过冷段的温差不至于过大，因而影响地板表面温度的均匀性及采暖体验。
为对比敷设水泥层前后毛细管壁温度变化，不改变毛细管布置方式，用相同的热泵室外机对光管毛细管末端进行制热运行试验。图10示出室内温度20 ℃、室外温度0 ℃时，光管毛细管壁温度变化情况。
从图10可以看出，在热泵机组运行至15 min后，毛细管壁温度趋于稳定，5个测点的升温速率均在0.31~0.44 ℃/min之间。机组运行稳定后，排气段1c点温度最高，平均温度维持为26.4 ℃；恒温段2c，3c，4c点平均温度分别为25.6，25.3，26.1 ℃，3个测点温差均在0.8 ℃以内，管壁温度分布均匀；过冷段5c点温度最低，平均温度24.8 ℃，与1c点相比，两者温差仅为1.6 ℃。相比图5，由于水泥层的存在，水泥层下毛细管壁5个测点温度比光管毛细管壁温度整体下降2.0~4.8 ℃；地板表面恒温段3个测点之间温差比光管毛细管恒温段温差低0.3 ℃，地表温度分布更加均匀，但排气段与过冷段温差增大了2.8 ℃，达到4.4 ℃。
图11示出室内温度20 ℃、室外温度为-5 ℃时，光管毛细管壁温度变化情况。在热泵机组运行至17 min后，毛细管壁温度趋于稳定，5个测点的升温速率均在0.22~0.31 ℃/min之间。机组运行稳定后，排气段1c点温度最高，平均温度维持为25.8 ℃；恒温段2c，3c，4c点平均温度分别为24.6，24.9，25.4 ℃，3个测点温差均在0.8 ℃以内；过冷段5c点温度最低，平均温度24.4 ℃，与1c点相比，两者温差为1.4 ℃。室外温度从0 ℃下降至-5 ℃时，光管毛细管温升速率下降了29%，各测点稳定后的平均温度下降变化不大（下降0.4~1.0 ℃）。恒温段测点温差基本不变，毛细管温度分布均匀程度良好。
综上分析，单回路多个等长毛细管的温度分布上，呈现出如下规律：单根毛细管温度随着制冷剂流向逐渐降低，是因为制冷剂逐步放热的结果。同一流通长度上，不同毛细管相同位置处最大温差小于1℃。由于敷设水泥层阻碍了毛细管散热，敷设水泥层后的管壁升温速率低于光管毛细管壁升温速率，管壁温度达到稳定的时间也大幅增加；温度稳定后，光管毛细管两种工况下，各测点温度均在微小范围内波动；敷设水泥前、后恒温段3个测点温差接近。另外，水泥层的敷设对毛细管排气段与过冷段温差影响较大，使进出口毛细管壁温差明显增大。
图12示出光管毛细管在不同室外温度下的系统制热量与制热COP变化。可以看出，制热量与制热COP均随室外温度的降低而减小。室外温度5 ℃时，制热量与制热COP分别为3.04 kW和6.08；室外温度-5 ℃时，制热量与制热COP分别为2.56 kW和5.50，两种工况相比，后者制热量与制热COP比前者分别下降15.8%和9.5%。室外温度-10 ℃时，制热量与制热COP分别为2.13 kW和4.88。当室外温度由5 ℃降至-10 ℃时，制热量与制热COP分别降低29.9%与19.7%。
图13示出敷设厚度20 mm水泥层后系统制热量及制热COP的变化。
可以看出，室外温度5 ℃时，制热量与制热COP分别为2.72 kW和5.68，与5 ℃时光管毛细管末端相比，两者分别降低10.5%和6.6%。室外温度-5 ℃时，制热量与制热COP分别为2.06 kW和4.81，与室外温度0 ℃时相比，两者分别下降15.2%和9.9%。室外温度-10 ℃时，制热量与制热COP分别为1.67 kW和4.20，与-10 ℃时光管毛细管末端相比，两者分别下降21.6%和13.9%。这是因为水泥层的填充在影响系统制热性能的同时，随着室外环境温度的降低，加剧了系统制热性能下降程度。
4　结论
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（1）由于水泥层热阻影响，地板表面升温速率小于水泥层下毛细管壁升温速率，地表温度达到稳定时间有所滞后。光管毛细管时，毛细管壁进出口温度均匀；敷设厚度20 mm水泥层后，毛细管壁进出口温差达6.4 ℃。
（2）随着室外温度降低，光管毛细管壁、水泥层下毛细管壁及水泥地板表面的各测点温度均逐步降低，且排气进口段与过冷段之间温差也逐渐减小。当室外温度为0 ℃时，光管毛细管壁排气段与过冷段之间温差仅为1.6 ℃，而水泥地板表面两者温差则达4.4 ℃。室外温度由0 ℃下降到-10 ℃，水泥地板表面排气进口段与过冷段的温差则减小1.7 ℃。
（3）不同室外温度下，敷设水泥层后的毛细管地板供暖末端受水泥层热阻的影响，系统制热性能较光管毛细管有所下降。当室外温度为-10 ℃时，其制热量与制热COP分别比光管毛细管末端下降21.6%和13.9%，此时前者制热量和制热COP依然能分别达到1.67 kW和4.20，系统制热性能良好。
（4）直凝毛细管地板辐射供暖的温度均匀性是系统设计特别注意的问题，应在设计初期和施工过程中保证制冷剂流量分配均匀，特别是分气器/集液器的选择和管路的长度等结构参数选取。另外，敷设毛细管时可以冷热逆流间隔布置，同时在铺设水泥前对光管毛细管末端进行开机试运行，保证均匀度在可接受的范围内。

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1
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4
乔桂楠，王宇，李艳菊，等.基于空气源热泵与新型通水地板的辐射供暖系统应用分析［J］.流体机械，2022，50（3）：88-95.
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王伟，倪龙，马最良.空气源热泵技术与应用［M］.北京：中国建筑工业出版社，2017.
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潘雷刚，徐昭炜，杨强，等.户式空气源热泵供暖系统不同末端形式分析［J］.暖通空调，2018，48（2）：40-43.
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7
张璐.夏热冬冷地区空气源热泵结合散热器供暖研究［D］.合肥：合肥工业大学，2019.
ZHANG L.Research on air source heat pump combined with radiator heating in hot summer and cold winter［D］.Hefei：Hefei University of Technology，2019.
8
贾庆贤，杨九铭，赵夫峰，等.家用空调器舒适性问题探讨［J］.建筑热能通风空调，2010，29（3）：63-66.
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邹通，王烨，孙鹏宝.地板供暖和散热器供暖综合性能对比分析［J］.制冷与空调，2015，29（6）：744-748.
ZOU T，WANG Y，SUN P B.Comprehensive performance comparison of floor radiation heating and radiator heating［J］.Refrigeration and Air‑conditioning，2015，29（6）：744-748.
10
杨强，徐昭炜，潘雷刚，等.户式空气源热泵供暖系统中循环水泵能耗测试研究［J］.暖通空调，2018，48（2）：24-29.
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11
黄凯良，侯旭，冯国会.基于TRNSYS的严寒地区地热辅助的空气源热泵系统研究［J］.流体机械，2023，51（7）：83-90.
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12
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2025年第53卷第5期
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doi: 10.3969/j.issn.1005-0329.2025.05.003
  • 接收时间：2024-09-04
  • 首发时间：2026-10-20
  • 出版时间：2025-05-30
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  • 收稿日期：2024-09-04
  • 修回日期：2025-03-16
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    河北建筑工程学院 河北省可再生能源供热工程技术中心，河北 张家口 075000

通讯作者:

卜跃刚（1992），男，硕士，讲师，研究方向为新能源利用技术，通信地址：075000河北省张家口市经开区朝阳西大街13号河北建筑工程学院能源工程系，E-mail：。
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2种不同金属材料的力学参数
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Number of
genus		 种数
Number of
species		 占总种数比例
Percentage of
total species (%)		 属
Genus		 种数
Number of
species		 占总种数比例
Percentage of total
species (%)
鹅膏菌科Amanitaceae 2 11 5.26 鹅膏菌属 Amanita 10 4.78
小菇科 Mycenaceae 2 12 5.74 丝盖伞属 Inocybe 5 2.39
多孔菌科 Polyporaceae 8 14 6.70 蜡蘑属 Laccaria 5 2.39
红菇科 Russulaceae 3 23 11.00 小皮伞属 Marasmius 6 2.87
小菇属 Mycena 11 5.26
光柄菇属 Pluteus 5 2.39
红菇属 Russula 17 8.13
栓菌属 Trametes 5 2.39
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