跨临界CO2热泵供暖系统循环优化与环境经济性评估

doi:10.3969/j.issn.2097-0706.2026.04.009

综合智慧能源 ›› 2026, Vol. 48 ›› Issue (4): 81-89.doi: 10.3969/j.issn.2097-0706.2026.04.009

• 优化配置与负荷调节 • 上一篇

跨临界CO₂热泵供暖系统循环优化与环境经济性评估

黄帅¹(), 向新宇²(), 李昂²(), 金旭³^,^*(), 阿如娜³(), 张家鹏³()

¹ 杭州市电力设计院有限公司，杭州 310009
² 国网浙江省电力有限公司杭州供电公司，杭州 310016
³ 东北电力大学能源与动力工程学院，吉林吉林 132012

收稿日期:2025-05-29 出版日期:2025-12-01
通讯作者: * 金旭（1977），男，教授，博士生导师，博士，从事制冷热泵理论与应用技术、烟气深度回收、系统集成、智慧热网及区域供冷供热管网优化技术等方面的研究，jinxu7708@sina.com。
作者简介:黄帅（1991），女，高级工程师，硕士，从事智能电网、能源互联网关键技术等方面的研究，shuai91629@126.com；
向新宇（1984），男，高级工程师，硕士，从事智能电网、能源低碳转型关键技术等方面的研究，314394694@qq.com；
李昂（1988），男，高级工程师，硕士，从事智能电网、能源低碳转型关键技术等方面的研究，52656798@qq.com；
阿如娜（1995），女，助教，博士，从事能源动力方面的研究，1273816224@qq.com；
张家鹏（2000），男，硕士生，从事CO₂双级压缩热泵低温适应性等方面的研究，3269259648@qq.com。
基金资助:
浙江大有集团有限公司科技项目(DY2023-01);国家自然科学基金项目(51976027)

Cycle optimization and environmental economic evaluation of transcritical CO₂ heat pump heating systems

HUANG Shuai¹(), XIANG Xinyu²(), LI Ang²(), JIN Xu³^,^*(), Aruna ³(), ZHANG Jiapeng³()

¹ Hangzhou Electric Power Design Institute Compony Limited， Hangzhou 310009， China
² Hangzhou Power Supply Company， State Grid Zhejiang Electric Power Company Limited， Hangzhou 310016， China
³ School of Energy and Power Engineering， Northeast Electric Power University， Jilin 132012， China

Received:2025-05-29 Published:2025-12-01
Supported by:
Science and Technology Project of Zhejiang Dayou Group Corporation Limited(DY2023-01);National Natural Science Foundation of China(51976027)

摘要/Abstract

摘要：

空气源热泵作为清洁供暖的代表，可有效降低建筑能耗，但其在寒冷地区的应用存在技术瓶颈，且传统制冷剂对环境有负面影响。为此，以跨临界CO₂热泵供暖系统为研究对象，基于Dymola软件对系统性能进行仿真分析；对比研究CO₂单级循环、双级循环及耦合机械过冷的双级循环系统在不同工况下的制热性能表现；结合全年实际供热量对系统进行环境分析和经济性评估，综合探讨不同系统形式的适用性和可持续性。研究结果表明：双级循环系统的制热性能系数（COP）较单级循环系统提升了26%；耦合前机械过冷的跨临界CO₂一级节流中间不完全冷却双压缩循环热泵系统（OTHS+FMC）可有效降低系统的最优高压，且在蒸发温度为-30 ℃时，其COP较原始跨临界CO₂热泵系统最大可提升12.70%，最优高压下COP提升了5.08%。经济性分析表明：OTHS+FMC的初始投资成本较高，但其长期运营的能效提升和减排效益使其更具环境经济性。

关键词: 跨临界CO₂热泵, 供暖系统, 制热性能, 经济性分析, 循环优化

Abstract:

As a representative of clean heating， air-source heat pumps can effectively reduce building energy consumption， but their application in cold regions faces technical bottlenecks， and traditional refrigerants have negative impacts on the environment. Therefore， taking the transcritical CO₂ heat pump heating system as the research object， the system performance was simulated and analyzed based on Dymola software. The heating performance of CO₂ single-stage cycle， two-stage cycle and two-stage cycle coupled with mechanical subcooling under different operating conditions was compared and studied. Combined with the annual actual heat supply， environmental analysis and economic evaluation of the system were conducted， and the applicability and sustainability of different system forms were comprehensively discussed. The research results showed that the heating coefficient of performance（COP） of the two-stage cycle was increased by 26% compared with the single-stage cycle. The transcritical CO₂ one-stage throttling intermediate incomplete cooling dual-compression cycle heat pump system + front mechanical subcooling（OTHS+FMC） could effectively reduce the optimal high pressure of the two-stage cycle system. When the evaporation temperature was -30 ℃， its COP could be increased by up to 12.70% compared with the initial transcritical CO₂ heat pump system， with a 5.08% COP improvement under optimal high pressure. The economic analysis showed that the initial investment cost of OTHS+FMC was higher， but the energy efficiency improvement and emission reduction benefits of long-term operation made it more environmentally economical.

Key words: transcritical CO₂ heat pump, heating system, heating performance, economic analysis, cycle optimization

中图分类号:

TK172

黄帅, 向新宇, 李昂, 金旭, 阿如娜, 张家鹏. 跨临界CO₂热泵供暖系统循环优化与环境经济性评估[J]. 综合智慧能源, 2026, 48(4): 81-89.

HUANG Shuai, XIANG Xinyu, LI Ang, JIN Xu, Aruna , ZHANG Jiapeng. Cycle optimization and environmental economic evaluation of transcritical CO₂ heat pump heating systems[J]. Integrated Intelligent Energy, 2026, 48(4): 81-89.

图/表 15

图1

图2

图3

图4

图5

表1

各热泵系统功耗及制热量理论计算公式

热泵	W_total	Q_H
单级循环	${q}_{m}({h}_{\mathrm{c}\mathrm{o}\mathrm{m},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{c}\mathrm{o}\mathrm{m},\mathrm{i}\mathrm{n}})$	${q}_{m,\mathrm{g}\mathrm{a}\mathrm{s}}({h}_{\mathrm{g}\mathrm{a}\mathrm{s},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{g}\mathrm{a}\mathrm{s},\mathrm{i}\mathrm{n}})$
双级循环	$\begin{array}{l}{q}_{m,\mathrm{H}}({h}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{H},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{H},\mathrm{i}\mathrm{n}})+\\ {q}_{m,\mathrm{L}}({h}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{L},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{L},\mathrm{i}\mathrm{n}})\end{array}$	${q}_{m,\mathrm{g}\mathrm{a}\mathrm{s}}({h}_{\mathrm{g}\mathrm{a}\mathrm{s},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{g}\mathrm{a}\mathrm{s},\mathrm{i}\mathrm{n}})$
机械过冷+ 双级循环	$\begin{array}{l}{q}_{m,\mathrm{H}}({h}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{H},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{H},\mathrm{i}\mathrm{n}})+\\ {q}_{m,\mathrm{L}}({h}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{L},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{L},\mathrm{i}\mathrm{n}})+\\ {q}_{m,\mathrm{M}\mathrm{c}}({h}_{\mathrm{M}\mathrm{c},\mathrm{c}\mathrm{o}\mathrm{m},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{M}\mathrm{c},\mathrm{c}\mathrm{o}\mathrm{m},\mathrm{i}\mathrm{n}})\end{array}$	$\begin{array}{l}{q}_{m,\mathrm{g}\mathrm{a}\mathrm{s}}({h}_{\mathrm{g}\mathrm{a}\mathrm{s},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{g}\mathrm{a}\mathrm{s},\mathrm{i}\mathrm{n}})+\\ {q}_{m,\mathrm{M}\mathrm{c}}({h}_{\mathrm{M}\mathrm{c},\mathrm{c}\mathrm{o}\mathrm{m},\mathrm{o}\mathrm{u}\mathrm{t}}-{h}_{\mathrm{M}\mathrm{c},\mathrm{c}\mathrm{o}\mathrm{m},\mathrm{i}\mathrm{n}})\end{array}$

表1

表2

表3

图6

图7

图8

图9

图10

图11

图12

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设备	公式	编号
低压级压缩机	${C}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{L}}=10\mathrm{ }167.5\mathrm{ }{W}^{0.46}$	(3)
高压级压缩机	${C}_{\mathrm{c}\mathrm{o}\mathrm{m}\mathrm{H}}=9\mathrm{ }624.2\mathrm{ }{W}^{0.46}$	(4)
R134a压缩机	${C}_{\mathrm{c}\mathrm{o}\mathrm{m},\mathrm{R}134\mathrm{a}}=758.15\mathrm{ }{W}^{0.872\mathrm{ }8}$	(5)
套管式换热器	C_{HX,tube-in-tube} = 2 382.4 A^0.68	(6)
板式换热器	${C}_{\mathrm{H}\mathrm{X},\mathrm{P}\mathrm{l}\mathrm{a}\mathrm{t}\mathrm{e}}=1\mathrm{ }874.4\mathrm{ }{A}^{0.983\mathrm{ }5}$	(7)

污染物	a_g/[kg∙(kW∙h)^-1]	b_g/(元∙t^-1)
CO₂	0.997	34.94
SO₂	0.030	2.50
NO_x	0.015	5.00

跨临界CO₂热泵供暖系统循环优化与环境经济性评估

Cycle optimization and environmental economic evaluation of transcritical CO₂ heat pump heating systems

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