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Thermal rectification refers to the phenomenon that heat fluxes or equivalent thermal conductivities are different under the same temperature difference when temperature gradient directions are different. The nature of the thermal rectification is that the structure has different effective thermal conductivities in different directions. Most of previous studies focused on thermal rectification of temperature-dependent thermal conductivity materials or variable cross section area structure, and the effect of thermal contact resistance at the interface was investigated very rarely. In the present paper we present the analytical and finite element numerical solution of temperature field and thermal rectification ratios of a composite structure with variable cross section area and thermal conductivity under different interface thermal contact resistances. The prescribed temperature boundary condition is introduced by penalty method, and the temperature jump condition at the interface is implemented by the definition of thermal contact resistance directly. The nonlinear heat conduction problem caused by temperature-dependent thermal conductivity and interface thermal contact resistance is then solved with a direct iteration scheme. Comparisons between experimental results and the present theoretical and numerical results show the feasibility of the proposed model. Then parameter investigations are also conducted to reveal the effect of some key geometric and material parameters. Numerical results show that thermal contact resistance plays an important role in the temperature field and thermal rectification ratio of the two-segment thermal rectifier. With the increase of the length ratio, thermal ratification ratio increases first and decreases then, and the optimal length ratio varies with both thermal contact resistance and cross-section radius change rate of the two segments. In general, the existence of thermal contact resistance can increase the total thermal resistance of the rectifier and magnify the distinction of the heat flux in forward and reverse cases. However, if the thermal contact resistance is too large, this distinction will decrease and correspondingly the thermal rectification ratio becomes low. With the increase of the boundary temperature difference, thermal rectification ratio increases due to the effect of temperature-dependent thermal conductivity. In the present study, we propose a theoretical and numerical approach to designing and optimizing the length ratio, cross-section radius change rate, thermal conductivity, boundary temperature difference and interface thermal contact resistance to obtain the maximal thermal rectification ratio of a bi-segment thermal rectifier, as well as the manipulation of thermal flux in engineering applications.
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图 1 变截面变热导率一维组合热整流器模型 (a) 热量自左向右正向流动; (b) 热量自右向左反向流动
Fig. 1. Schematic of the one-dimensional composite thermal rectifier model with variable cross section area and thermal conductivity: (a) Forward heat flows from left to right; (b) reverse heat flows from right to left.
图 3 热整流器的温度场分布对比 (Reverse与Forward分别代表LaCoO3和La0.7Sr0.3CoO3材料位于高温端的情况)
Fig. 3. Comparisons of temperature distribution of the thermal rectifier (Reverse and Forward denote the case of that LaCoO3 and La0.7Sr0.3CoO3 materials locate in high-temperature side respectively).
图 4 不同温差下热整流器的响应 (a) 热量; (b) 热整流系数
Fig. 4. Response of the thermal rectifier with different temperature differences: (a) Heat flux; (b) thermal rectification ratio.
图 5 横截面面积变化趋势与截面半径变化率的关系
Fig. 5. Relationship between cross-section area and cross-section radius change rate.
图 6 不同长度比热整流器的温度场 (a) 长度比0.5; (b) 长度比0.2
Fig. 6. Temperature distribution of the thermal rectifier with different length ratios: (a) Length ratio is 0.5; (b) length ratio is 0.2.
图 7 不同接触热阻下热整流系数随长度比的变化 (a)
${\beta _{{x_1}}} = $ $ - 0.03$ ,${\beta _{{x_2}}} = 0.03 $ ; (b)${\beta _{{x_1}}} = - 0.03$ ,${\beta _{{x_2}}} = - 0.03 $ Fig. 7. Variations of thermal rectification coefficient with length ratio under different contact thermal resistance: (a)
${\beta _{{x_1}}} = - 0.03, \; {\beta _{{x_2}}} = 0.03$ ; (b)${\beta _{{x_1}}} = - 0.03, \; {\beta _{{x_2}}} = $ –0.03
图 9 不同长度变化率下热整流系数随长度比
Fig. 9. Variations of thermal rectification coefficient with length ratio at different length variation ratio.
图 8 不同边界温差下热整流系数随长度比的变化 (a)
${\beta _{{x_1}}} = $ $ - 0.03, \; {\beta _{{x_2}}} = 0.03$ ; (b)${\beta _{{x_1}}} = - 0.03, \; {\beta _{{x_2}}} = - 0.03$ Fig. 8. Variations of thermal rectification coefficient with length ratio at different boundary temperature differences: (a)
${\beta _{{x_1}}} \!=\! - 0.03, \; {\beta _{{x_2}}} \!=\! 0.03$ ; (b)${\beta _{{x_1}}} \!=\! - 0.03,\; {\beta _{{x_2}}} \!=\! - 0.03$ -
[1] Li B W, Wang L, Casati G 2004 Phys. Rev. Lett. 93 184301
Google Scholar
[2] Zhu J, Hippalgaonkar K, Shen S, Wang K V, Abate Y, Lee S, Wu J Q, Yin X B, Majumdar A, Zhang X 2014 Nano. Lett. 14 4867
Google Scholar
[3] Paolucci F, Marchegiani G, Strambini E, Giazotto F 2018 Phys. Rev. Appl. 10 024003
Google Scholar
[4] Li N B, Ren J, Wang L, Zhang G, Hänggi P, Li B W 2012 Rev. Mod. Phys. 84 1045
Google Scholar
[5] 单小东, 王沫然 2014 工程热物理学报 35 1401
Google Scholar
Shan X D, Wang M R 2014 J. Eng. Thermophys. 35 1401
Google Scholar
[6] 张茂平, 钟伟荣, 艾保全 2011 物理学报 60 060511
Google Scholar
Zhang M P, Zhong W R, Ai B Q 2011 Acta Phys. Sin. 60 060511
Google Scholar
[7] 温家乐, 徐志成, 古宇, 郑冬琴, 钟伟荣 2015 物理学报 64 216501
Google Scholar
Wen J L, Xu Z C, Gu Y, Zheng D Q, Zhong W R 2015 Acta Phys. Sin. 64 216501
Google Scholar
[8] Nobakht A Y, Gandomi Y A, Wang J Q, Bowman M H, Marable D C, Garrison B E, Kim D, Shin S 2018 Carbon. 132 565
Google Scholar
[9] Machrafi H, Lebon G, Jou D 2016 Int. J. Heat Mass Transfer. 97 603
Google Scholar
[10] 鞠生宏, 梁新刚 2013 物理学报 62 026101
Google Scholar
Ju S H, Liang X G 2013 Acta Phys. Sin. 62 026101
Google Scholar
[11] 李威, 冯妍卉, 唐晶晶, 张欣欣 2013 物理学报 62 076107
Google Scholar
Li W, Feng Y H, Tang J J, Zhang X X 2013 Acta Phys. Sin. 62 076107
Google Scholar
[12] 李威, 冯妍卉, 陈阳, 张欣欣 2012 物理学报 61 136102
Google Scholar
Li W, Feng Y H, Chen Y, Zhang X X 2012 Acta Phys. Sin. 61 136102
Google Scholar
[13] Meng Z, Gulfam R, Zhang P, Ma F 2020 Int. J. Heat Mass Transfer. 147 118915
Google Scholar
[14] Wang H, Hu S, Takahashi K, Zhang X, Takamatsu H, Chen J 2017 Nat. Commun. 8 15843
Google Scholar
[15] Aiyiti A, Zhang Z, Chen B, Hu S, Chen J, Xu X, Li B 2018 Carbon 140 673
Google Scholar
[16] Peyrard M 2006 Europhys. Lett. 76 49
Google Scholar
[17] Kobayashi W, Teraoka Y, Terasaki I 2009 Appl. Phys. Lett. 95 171905
Google Scholar
[18] Shih T M, Gao Z J, Guo Z Q, Merlitz H, Pagni P J, Chen Z 2015 Sci. Rep. 5 12677
Google Scholar
[19] Sadat H, Le Dez V 2016 Mech. Res. Commun. 76 48
Google Scholar
[20] Go D B, Sen M 2010 J. Heat Transfer 132 124502
Google Scholar
[21] Majdi T, Pal S, Puri I K 2017 Int. J. Therm. Sci. 117 260
Google Scholar
[22] Sawaki D, Kobayashi W, Moritomo Y, Terasaki I 2011 Appl. Phys. Lett. 98 081915
Google Scholar
[23] Tian H, Xie D, Yang Y, Ren T L, Zhang G, Wang Y F, Zhou C J, Peng P G, Wang L G, Liu L T 2012 Sci. Rep. 2 523
Google Scholar
[24] Dames C 2009 J. Heat Transfer 131 061301
Google Scholar
[25] Yang Y, Chen H, Wang H, Li N B, Zhang L F 2018 Phys. Rev. E 98 042131
Google Scholar
[26] Sayer R A 2013 Proceedings of the ASME International Mechanical Engineering Congress and Exposition-2012, Albuquerque, November 9–15, 2012 p86065
[27] Chumak K, Martynyak R 2012 Int. J. Heat Mass Transfer 55 5603
Google Scholar
[28] 朱玉鑫, 王珏, 罗爽, 王军, 夏国栋 2016 中国科学: 技术科学 46 175
Google Scholar
Zhu Y X, Wang J, Luo S, Wang J, Xia G D 2016 Sci. China, Ser. 46 175
Google Scholar
[29] 汤宇轩, 李凡, 王淼, 王中元, 王军, 夏国栋 2018 中国科技论文 13 1244
Google Scholar
Tang Y X, Li F, Wang M, Wang Z Y, Wang J, Xia G D 2018 China Science Paper 13 1244
Google Scholar
[30] Wehmeyer G, Yabuki T, Monachon C, Wu J Q, Dames C 2017 Appl. Phys. Rev. 4 041304
Google Scholar
[31] Reddy J N 1993 An Introduction to The Finite Element Method (2nd Ed.) (New York: McGraw-Hill) pp105–117
[32] Cengel Y A 2007 Heat and Mass Transfer: A Practical Approach (3rd Ed.) (Boston: McGraw-Hill) pp844–846
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