CO2跨临界水源热泵两级供热系统理论比较

在供热系统中，需要的水温较高时，由于回水温度高而导致CO2跨临界水源热泵能效比下降。如果降低回不温度，就要求不同温度的热水分级处理。CO2跨临界水源热泵两级供热系统可以实现能量的分级利用。分析对比了3种形工的CO2跨临界水源热泵两级供热系统，发现它们各有特点，可根据不同的使用要求采用适宜的两组系统。     

燃气机驱动CO2工质跨临界循环热泵系统评价

阐述了燃气机驱动的以CO2为工质的跨临界循环热泵系统的原理，计算了总有效温室效应评价指标和一次能源利用率，进行了技术经济分析。此热泵系统总有效温室效应评价指标低，一次能源利用率高，环境污染小，运行费用低于普通电动热泵。     

CO_2跨临界水——水热泵循环系统的实验研究

在作者设计和建立的实验台上进行了CO2 跨临界水—水热泵多种工况的循环性能实验研究 ,系统运行稳定、调节方便。实验结果表明 ,系统运行时的最大制冷 (热 )系数取决于系统的蒸发温度和气体冷却器出口温度。CO2 跨临界循环热泵较之传统工质热泵具有较大优势 ,尤其是在高温热泵领域。指出了系统的改善措施     

CO2跨临界水—水热泵循环系统的实验研究

在作者设计和建立的实验台上进行了CO2跨临界水-水热泵多种工况的循环性能实验研究,系统运行稳定、调节方便,实验结果表明,系统运行时的最大制冷（热）系数取决于系统的蒸发温度和气体冷却器出口温度,CO2跨临界循环热泵较之传统工质热泵具有较大优势,尤其是在高温热泵领域,指出了系统的改善措施。     

超临界流体及超(跨) 临界循环的特性研究

通过对自然工质CO2的研究发现，超临界流体具有应用范围广，实用性强的特点，作为超临界流体技术应用研究的一个方面，空调制冷系统超（跨）临界循环是一个通用循环，该循环与传统的亚临界循环相比具有不同的特性，如用于热泵供暖、供应热水时，换热效率较高，COP有极大值等，从研究CO2跨临界循环中发现，许多特性关非CO2所固有，而且有一定的通用性。     

CO2水源热泵驱动溶液除湿新风系统性能研究

提出了一套多功能CO2水源热泵驱动的溶液除湿新风系统,该系统以CO 2跨临界循环压缩机高温排气实现LiCl溶液再生,提高了热泵驱动溶液除湿系统的溶液再生效率,并以地下水为再冷源,减小了CO2跨临界循环节流损失.通过建立系统稳态数学模型,模拟分析了标准环境工况下,新风量、 除湿/再生内循环比、 溶液总流量、 再生空气流量等4个可控关键因素对系统性能的影响,并将系统应用于西安市某200 m2办公建筑,得到了4个可控参数设置的最佳组合.     

太阳能冷管和跨临界CO2热泵联合供能设计

本文设计了一个由太阳能冷管和跨临界CO2热泵组成的联合供能系统,可以实现制冷+供热水、制热+供热水、单独制冷、单独制热、单独供热水的功能。夏天用太阳能冷管制冷并提供生活热水,当太阳能不足或阴雨天气时,由跨临界CO2系统替代;冬天用跨临界CO2热泵制热并提供热水;过渡季节晴天时由太阳能冷管提供热水,阴雨天气时由跨临界CO2系统替代。这是一种将太阳能冷管吸附式制冷技术和跨临界CO2热泵技术联合的可实现制冷、制热和供热水功能的联合系统,集空调热泵和热水器于一体,是一个利用新能源、环保节能的紧凑型系统。     

跨临界循环C02热泵热水器研究现状及展望

天然环保型工质CO2在系统采用跨临界循环后,与传统制冷剂相比具有独特的优点.基于可持续发展观,CO:成为热泵热水器系统最有潜力的替代工质之一.近15年来,挪威等欧洲国家、日本和美国对CO:热泵热水器系统进行了广泛深入的研究.本文详细介绍了CO:热泵热水器样机的研究状况,总结了核心部件压缩机和换热器的研发现状,并探讨了有待进一步开展的研究内容.     

意大利：CO2热泵在养老院的应用

Villa Laura养老院临近意大利的佛罗伦萨，这个养老院的供热和空调系统包括4套装有跨临界CO2循环的水-水交换的地下水源热泵系统，此技术已被用来为独立的居住建筑提供热水，尤其在日本使用的较多。Villa Laura养老院共有3层，总面积为4500m^2，需要的制冷／制热量比较大，而这种系统的运行效果也相当好。     

C02跨临界水-水热泵供热系统应用理论探讨

运用当量温度概念对CO2跨临界水-水热泵供热系统进行了研究，指出根据实际情况选择气体冷却器的出口温度和压缩机的出口压力能提高系统的运行效率，并对供热过程中采用能量梯级利用进行了研究，结果表明对热水侧进行梯级利用可提高系统的制热性能系数。     

太阳能辅助CO_2热泵系统回热器设计及实验研究

在CO2跨临界循环系统中,节流损失相对较大。通过增加回热器的方法以提高跨临界CO2热泵系统的COP。根据相关的换热关联式对CO2热泵系统的回热器进行了设计计算并且进行了相关的实验研究。计算得到的回热器,长度为1.27 m,内管内径6 mm,外管内径13 mm,壁厚1 mm。并且在相同环境工况下,利用自行搭建的CO2热泵系统实验台,分别在有回热器与无回热器时进行了实验研究。实验结果表明:当系统引入回热器后,压缩机排气压力、温度上升,压缩机耗功上升速率加快,制热量增加速率亦加快,且制热量增加速率大于压缩机耗功增加速率,系统制热COP增加,带回热器时系统平均COP达到3.34,无回热器时系统平均COP为3.03,提高约10.2%。     

带膨胀机CO2跨临界热泵系统运行特性

建立了带膨胀机CO2跨临界热泵系统的数学模型,将模拟计算结果与实验测量结果进行了比较,验证了模型的准确性。利用数学模型分析了冷却水进口温度和质量流量、冷冻水进口温度和质量流量对带膨胀机CO2跨临界热泵系统的制冷性能系数及最佳高压侧压力的影响。降低冷却水进口温度和提高其质量流量不仅有利于提高制冷性能系数,而且能降低最佳高压侧压力。提高冷冻水进口温度及质量流量有利于提高制冷性能系数,对最佳高压侧压力影响不大。     

A thermodynamic analysis of a transcritical cycle with refrigerant mixture R32/R290 for a small heat pump water heater

In this study, a thermodynamic analysis on the performance of a transcritical cycle using azeotropic refrigerant mixtures of R32/R290 with mass fraction of 70/30 has been performed. The main purpose of this study is to theoretically verify the possibility of applying the chosen refrigerant mixture in small heat pumps for high temperature water heating applications. Performance evaluation has been carried out for a simple azeotropic mixture R32/R290 transcritical cycle by varying evaporator temperature, outlet temperature of gas cooler and compressor discharge pressure. Furthermore, the effects of an internal heat exchanger on the transcritical R32/R290 cycle have been presented at different operating conditions. The results show that high heating coefficient of performance (COP_h) and volumetric heating capacity can be achieved by using this transcritical cycle. It is desirable to apply the chosen refrigerant mixture R32/R290 in small heat pump water heater for high temperature water heating applications, which may produce hot water with temperature up to 90 °C.     

Combined air conditioning and tap water heating plant using CO2 as refrigerant

A combined air conditioning and tap water heating plant using carbon dioxide (CO₂) as refrigerant has been investigated theoretically and experimentally. The system is suitable for countries with year around cooling demand, such as Indonesia or Singapore, and a need for hot tap water. A unique CO₂ transcritical cycle characteristic for heating process can afford an improvement to a CO₂ air conditioning system when rejected heat from the system is recovered. Some parameters affecting performance of the combined system are discussed.     

Performance analysis of a transcritical N2O refrigeration cycle with vortex tube

In the present study, vortex tube is used in transcritical vapour compression cycle as expansion device to improve the coefficient of performance (COP). The thermodynamic analysis has been performed using nitrous oxide in transcritical cycle with vortex tube (TCVT) and its results are compared with those of a transcritical cycle with expansion valve (TCEV). The evaporator and the gas cooler temperatures have been varied between ?55°C and 5°C and between 35°C and 60°C, respectively, for the analysis. The COP of the TCVT improves by 1.72–27.01% compared to TCEV. A decrease in evaporator temperature and an increase in gas cooler exit temperature result in a decrease in COP. The increase in cold mass fraction brings a negligible increase in maximum COP. The performance comparison of N₂O and CO₂ in TCVT shows that maximum cooling COP for N₂O is higher than for CO₂, but the optimum pressure required for N₂O is lower than for CO₂.     

Performance characteristics of a two-stage transcritical N2O refrigeration cycle with vortex tube

ABSTRACT

The thermodynamic analysis has been presented in this article using nitrous oxide as the refrigerant in a two-stage transcritical cycle with the vortex tube (TSTCVT) instead of the expansion valve and its results are compared with the two-stage transcritical cycle with the expansion valve (TSTCEV). The evaporator and the gas cooler temperature ranges in both the cycles have been considered between ?55°C to 5°C and 35°C to 60°C for the analysis. Gas cooler and intercooler pressures are simultaneously optimised to obtain the maximum cooling coefficient of performance (COP). The COP of the TSTCVT improves by 1.97–27.19% in comparison to TSTCEV. A decrease in evaporator temperature and an increase in gas cooler exit temperature reduce the COP of TSTCVT. The comparison of refrigerants N₂O and CO₂ in TSTCVT shows that N₂O exhibits higher cooling COP, higher second law of efficiency and lower optimum gas cooler pressure under the considered operating conditions.