【摘要】：隨著空氣源二氧化碳熱泵熱水器的不斷發(fā)展,熱泵熱水器也開(kāi)始在我國(guó)逐步應(yīng)用。由于二氧化碳熱泵熱水器應(yīng)用于商業(yè)或者是工業(yè)上更具有經(jīng)濟(jì)性優(yōu)勢(shì),因此本文就根據(jù)GB/T21362--2008《商業(yè)或工業(yè)用及類似用途的熱泵熱水機(jī)》規(guī)定的測(cè)試工況,對(duì)制冷劑充注量、水的質(zhì)量流量等影響因素進(jìn)行了實(shí)驗(yàn),實(shí)驗(yàn)結(jié)果表明： (1)C02熱泵熱水系統(tǒng)存在最佳C02充注量,充注過(guò)少,通過(guò)壓縮機(jī)和蒸發(fā)器的制冷劑流量較小,造成設(shè)備浪費(fèi),同時(shí)所得熱水溫度過(guò)低；充注過(guò)多會(huì)使操作壓力過(guò)大,降低系統(tǒng)COP。本文確定了最佳C02充注量為8MPa。 (2)水的質(zhì)量流量對(duì)COP和出口水溫的影響是相反的,增大水的流量會(huì)增加COP,但會(huì)降低出口水溫,需綜合考慮系統(tǒng)對(duì)于COP和熱水水溫的要求來(lái)確定最佳流量。 (3)本文通過(guò)實(shí)驗(yàn)確定了在CO2充注量為8MPa,水流量為800ml/min、壓縮機(jī)排氣壓力為8.5MPa時(shí)能夠滿足GB/T21362—2008的要求。 在實(shí)驗(yàn)的基礎(chǔ)之上,對(duì)空氣源C02熱泵熱水器進(jìn)行了(?)分析,建立了壓縮機(jī)等系統(tǒng)各部件的(?)分析模型,計(jì)算了各個(gè)部件的(?)損失和系統(tǒng)的(?)效率。經(jīng)過(guò)計(jì)算發(fā)現(xiàn),系統(tǒng)的(?)效率只有27.7%,系統(tǒng)(?)效率較低。同時(shí)比較各個(gè)部件的(?)損失發(fā)現(xiàn),壓縮機(jī)的炯損失所占總的(?)損失的百分比最大,其次是節(jié)流閥,然后是氣體冷卻器,蒸發(fā)器最小。而且壓縮機(jī)和節(jié)流閥處的(?)損失相差不大,相比較而言,對(duì)于節(jié)流設(shè)備的優(yōu)化改進(jìn)不管是從可行性還是經(jīng)濟(jì)性上來(lái)說(shuō)都更具優(yōu)勢(shì),因此本文決定利用噴射器來(lái)代替節(jié)流閥作為節(jié)流設(shè)備。 設(shè)計(jì)了應(yīng)用于空氣源二氧化碳熱泵熱水器的噴射器,對(duì)噴射器的設(shè)計(jì)方法、噴射系數(shù)、噴射器的結(jié)構(gòu)尺寸等進(jìn)行了詳細(xì)的介紹,并利用Visual Basic對(duì)噴射器的設(shè)計(jì)計(jì)算過(guò)程進(jìn)行了程序設(shè)計(jì),經(jīng)過(guò)計(jì)算,噴射器可達(dá)到的最大噴射系數(shù)為0.7。 采用數(shù)值模擬的方法對(duì)噴射器的內(nèi)部流場(chǎng)進(jìn)行了分析。計(jì)算得到的噴射系數(shù)與理論計(jì)算的誤差為11.4%。分析了噴射器內(nèi)部的速度場(chǎng)和壓力場(chǎng),同時(shí)還對(duì)工作流體壓力、引射流體壓力等工作參數(shù)對(duì)超臨界C02噴射器的性能影響進(jìn)行了分析,分析發(fā)現(xiàn),提高混合流體壓力會(huì)降低噴射系數(shù),在確定噴射器設(shè)計(jì)參數(shù)時(shí),應(yīng)該兼顧噴射系數(shù)和混合流體出口壓力的關(guān)系,適當(dāng)降低升壓比(Pc/Ph),可以提高噴射器可達(dá)到的最大引射能力。
[Abstract]:With the development of air-source carbon dioxide heat pump water heater, heat pump water heater is gradually applied in our country. Since CO2 heat pump water heaters are more economical in commercial or industrial applications, the refrigerant is charged according to the test conditions specified in GB/ T21362--2008 for commercial or industrial heat pump water heaters. The experimental results show that: (1) the optimal charge of CO2 exists in the C02 heat pump hot water system, and the flow rate of refrigerant through compressor and evaporator is small, which results in waste of equipment. At the same time, the temperature of the obtained hot water is too low, too much filling will make the operating pressure too large, and reduce the system COP. In this paper, it is determined that the optimal charge of CO2 is 8 MPA. (2) the effect of water mass flow on cop and outlet water temperature is opposite. Increasing the water flow will increase COP, but decrease the outlet water temperature. The optimal flow rate should be determined by considering the cop and the water temperature of hot water. (3) the experiment results show that the system can meet the requirements of GB / T21362-2008 when the CO _ 2 charge is 8MPa, the water flow is 800ml / min, and the compressor exhaust pressure is 8.5MPa. Based on the experiment, the air source heat pump water heater C02 has been carried out. Analysis and establishment of compressor and other components of the system (?) By analyzing the model, the (?) Loss and system (?) Efficiency. After calculation, it is found that the system's (?) Efficiency is only 27. 7%, system (?) Low efficiency. At the same time, compare the (?) Losses are found to account for the total loss of compressors (?) The percentage loss is highest, followed by throttle valves, then gas coolers, and evaporators the smallest. And compressor and throttle place (?) The loss is not different, compared to the throttling equipment, the optimization and improvement of the throttling equipment is more advantageous in terms of feasibility and economy, so this paper decides to use the ejector instead of the throttle valve as the throttling equipment. The ejector used in air source carbon dioxide heat pump water heater is designed. The design method, ejector coefficient and structure size of ejector are introduced in detail. The design and calculation process of the ejector is programmed by Visual basic, and the maximum ejector coefficient is 0.7. The internal flow field of the ejector is analyzed by numerical simulation. The error between the calculated injection coefficient and the theoretical calculation is 11.4. The velocity field and pressure field inside the ejector are analyzed. The influence of working fluid pressure and ejection fluid pressure on the performance of supercritical C02 injector is also analyzed. When the ejector design parameters are determined, the relationship between the ejection coefficient and the outlet pressure of the mixed fluid should be taken into account, and the maximum ejection capacity of the ejector can be improved by properly reducing the pressure boost ratio (Pc / Ph).
【學(xué)位授予單位】：大連理工大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2014
【分類號(hào)】：TU822

【參考文獻(xiàn)】

相關(guān)期刊論文 前10條

1 汪南;朱冬生;;家用熱泵熱水器的研究及發(fā)展趨勢(shì)[J];日用電器;2006年11期

2 王玉軍,劉軍,顧小剛;空氣源熱泵熱水機(jī)綜合技術(shù)分析[J];中國(guó)建設(shè)信息(供熱制冷�？�);2005年11期

3 李嫵，陶文銓，，康海軍，李惠珍，辛榮昌;整體式翅片管換熱器傳熱和阻力性能的試驗(yàn)研究[J];機(jī)械工程學(xué)報(bào);1997年01期

4 史暢;當(dāng)前國(guó)內(nèi)熱水器市場(chǎng)現(xiàn)狀與趨勢(shì)分析[J];家電科技;2003年05期

5 管海清 ,馬一太 ,楊俊蘭;日本家用CO_2熱泵熱水器研究開(kāi)發(fā)現(xiàn)狀分析[J];家電科技;2004年06期

6 羅清海,湯廣發(fā),龔光彩,唐海兵;建筑熱水節(jié)能途徑分析[J];煤氣與熱力;2004年06期

7 王侃宏,王景剛,侯立泉,馬一太,魏東,洪芳軍;CO_2跨臨界水——水熱泵循環(huán)系統(tǒng)的實(shí)驗(yàn)研究[J];暖通空調(diào);2001年03期

8 王如竹;吳靜怡;許煜雄;;高效節(jié)電的空氣能熱泵熱水器[J];上海電力;2004年06期

9 劉寶明,何家雄,夏斌,張樹(shù)林;國(guó)內(nèi)外CO_2研究現(xiàn)狀及發(fā)展趨勢(shì)[J];天然氣地球科學(xué);2004年04期

10 姜云濤;馬一太;劉和成;張鵬;;帶回?zé)崞鞯母咝Э缗R界CO_2水-水熱泵的實(shí)驗(yàn)研究[J];天津大學(xué)學(xué)報(bào);2010年04期

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