Li et al 2023g - Revision history

Rimni at 09:24, 19 December 2023

2023-12-19T09:24:45Z

Rimni at 09:23, 19 December 2023

2023-12-19T09:23:02Z

Rimni at 09:21, 19 December 2023

2023-12-19T09:21:53Z

Rimni: /* 3.1 Prestress modal */

2023-12-19T09:20:47Z

‎3.1 Prestress modal

Rimni at 09:18, 19 December 2023

2023-12-19T09:18:09Z

Rimni at 08:37, 19 December 2023

2023-12-19T08:37:20Z

Rimni at 08:18, 19 December 2023

2023-12-19T08:18:46Z

Rimni at 15:06, 18 December 2023

2023-12-18T15:06:24Z

Rimni at 15:05, 18 December 2023

2023-12-18T15:05:34Z

Rimni at 15:05, 18 December 2023

2023-12-18T15:05:00Z

← Older revision		Revision as of 09:24, 19 December 2023
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−	From [[#img-8\|Figure 8]], it can be obtained that the sealing ring compression rate, sealing ring diameter, sealing groove width and depth have a sensitive nonlinear relationship on the contact stress, especially the sealing ring compression rate has a significant impact on the sealing performance of diaphragm compressor. With the same sealing ring and groove structure, the contact pressure between the sealing ring and groove increases significantly with the increasing compression rate. With the increase of compression ratio by 20% and 25%, the contact pressure increased by 42.0% and 77.5%, respectively. From Figure 9, it can be concluded that for the sealing ring with diameter of 5.3mm, the contact pressure changes slightly when the seal groove width is appropriately increased without changing the seal groove depth. However, for the sealing ring with diameter of 7.0 mm, the contact pressure decreases significantly when the sealing groove width is increased, especially at high compression rate. At c=25%, d=7.~~0mm~~, the maximum contact pressure is reduced by 8.1% by increasing the groove width by 0.5 mm. Therefore, at the same compression rate of the sealing ring, the contact pressure at the sealing interface increases with the increase of the diameter of the seal ring, and the structural size of the sealing groove has a significant nonlinear impact on the contact pressure of the large-diameter sealing ring.	+	From [[#img-8\|Figure 8]], it can be obtained that the sealing ring compression rate, sealing ring diameter, sealing groove width and depth have a sensitive nonlinear relationship on the contact stress, especially the sealing ring compression rate has a significant impact on the sealing performance of diaphragm compressor. With the same sealing ring and groove structure, the contact pressure between the sealing ring and groove increases significantly with the increasing compression rate. With the increase of compression ratio by 20% and 25%, the contact pressure increased by 42.0% and 77.5%, respectively. From [[#img-9\|Figure 9]], it can be concluded that for the sealing ring with diameter of 5.3mm, the contact pressure changes slightly when the seal groove width is appropriately increased without changing the seal groove depth. However, for the sealing ring with diameter of 7.0 mm, the contact pressure decreases significantly when the sealing groove width is increased, especially at high compression rate. At <math>c=25</math>%, <math>d=7.0</math>mm, the maximum contact pressure is reduced by 8.1% by increasing the groove width by 0.5 mm. Therefore, at the same compression rate of the sealing ring, the contact pressure at the sealing interface increases with the increase of the diameter of the seal ring, and the structural size of the sealing groove has a significant nonlinear impact on the contact pressure of the large-diameter sealing ring.

	<div id='img-9'></div>		<div id='img-9'></div>

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 |style="text-align: center;padding:10px;"| [[Image:Review_326545415492-image8.png|600px]]
-[[Image:Review_326545415492-image9.png|550px]]
+[[Image:Review_326545415492-image9.png|600px]]
 |-
 | style="background:#efefef;text-align:left;padding:10px;font-size: 85%;"| '''Figure 8'''. Stress distribution diagram of sealing system under different working condition

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 In order to study the influence of bolt preload distribution on the mode of compressor sealing system, the working condition is defined by the distribution state of bolt preload on the joint surface, as shown in [[#tab-2|Table 2]]. <math display="inline">F_0</math> is the rated preload of single bolt. The marks 1~20 represent the pre-tightening force of each bolt. The definition of the operating condition reflects the process of the bolt group from degradation to loosening during operation. Case-1 is the normal working condition and the rated pre-tightening force. Case-2 and Case-3 mainly reflect the overall deterioration of the pre-tightening force of the bolt group. Case-4 and Case-5 mainly reflect the partial loosening and damage of the bolt group.
-<<div class="center" style="font-size: 75%;">'''Table 2'''.  Working conditions</div>
+<div class="center" style="font-size: 75%;">'''Table 2'''.  Working conditions</div>
 <div id='tab-1'></div>
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 {| class="wikitable" style="margin: 0em auto 0.1em auto;border-collapse: collapse;width:auto;"
 |-style="background:white;"
-|style="text-align: center;padding:10px;"| [[Image:Review_326545415492-image5.png|600px]]
+|style="text-align: center;padding:10px;"| [[Image:Review_326545415492-image5.png|500px]]
 |-
 | style="background:#efefef;text-align:left;padding:10px;font-size: 85%;"| '''Figure 5'''. Modal analysis results of diaphragm compressors under different operating conditions
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 {| class="wikitable" style="margin: 0em auto 0.1em auto;border-collapse: collapse;width:auto;"
 |-style="background:white;"
-|style="text-align: center;padding:10px;"| [[Image:Review_326545415492-image6.png|600px]]
+|style="text-align: center;padding:10px;"| [[Image:Review_326545415492-image6.png|500px]]
 |-
 | style="background:#efefef;text-align:left;padding:10px;font-size: 85%;"| '''Figure 6'''. Frequency domain analysis of the air cavity pressure

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 {| class="wikitable" style="margin: 1em auto 0.1em auto;border-collapse: collapse;font-size:85%;width:auto;"
 |-style="text-align:center"
-! Case !! Pretensioning force distribution
+! style="text-align: left;| Case !! Pretensioning force distribution
 |-
 |  style="text-align: center;vertical-align: top;"|Case-1

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 ==References==
-[1] Wilberforce T., El-Hassan Z., Khatib F N., et al. Developments of electric cars and fuel cell hydrogen electric cars. International Journal of Hydrogen Energy, 42(40):25695-25734, 2017.
+[1] Wilberforce T., El-Hassan Z., Khatib F.N., Al-Makky A., Baroutaji A., Carton J.G., Olabi A.G. Developments of electric cars and fuel cell hydrogen electric cars. International Journal of Hydrogen Energy, 42(40):25695-25734, 2017.
-[2] Kang J.E., Brown T., Rockers W.W., et al. Refueling hydrogen fuel cell vehicles with 68 proposed refueling stations in California: Measuring deviations from daily travel patterns. International Journal of Hydrogen Energy, 39(7):3444-3449, 2014.
+[2] Kang J.E., Brown T., Rockers W.W., Samuelsen G.S. Refueling hydrogen fuel cell vehicles with 68 proposed refueling stations in California: Measuring deviations from daily travel patterns. International Journal of Hydrogen Energy, 39(7):3444-3449, 2014.
-[3] Wang Y., Xin D., Feng J., Peng X., et al. Research on sealing performance and self-acting valve reliability in high-pressure oil-free hydrogen compressors for hydrogen refueling stations. International Journal of Hydrogen Energy, 35(15):8063-8070, 2010.
+[3] Wang Y., Xin D., Feng J., Peng X. Research on sealing performance and self-acting valve reliability in high-pressure oil-free hydrogen compressors for hydrogen refueling stations. International Journal of Hydrogen Energy, 35(15):8063-8070, 2010.
-[4] Weinert J.X., Liu S., Ogden J.M., et al. Hydrogen refueling station costs in Shanghai. International Journal of Hydrogen Energy, 32(16):4089-4100, 2007.
+[4] Weinert J.X., Liu S., Ogden J.M., Ma J. Hydrogen refueling station costs in Shanghai. International Journal of Hydrogen Energy, 32(16):4089-4100, 2007.
 [5] Wang T., Tang Z., Jia X. Study on the stress and deformation of a diaphragm compressor cylinder head under extreme conditions. IOP Conference Series Materials Science and Engineering, 604:012029, 2019.
-[6] Wang T., Jia X., Li X., et al. Thermal-structural coupled analysis and improvement of the diaphragm compressor cylinder head for a hydrogen refueling station. International Journal of Hydrogen Energy, 45(1):809-821, 2020.
+[6] Wang T., Jia X., Li X., Ren S., Peng X. Thermal-structural coupled analysis and improvement of the diaphragm compressor cylinder head for a hydrogen refueling station. International Journal of Hydrogen Energy, 45(1):809-821, 2020.
-[7] Jia X., Zhao Y., Chen J., et al. Research on the flowrate and diaphragm movement in a diaphragm compressor for a hydrogen refueling station. International Journal of Hydrogen Energy, 41(33):14842-14851, 2016.
+[7] Jia X., Zhao Y., Chen J., Peng X. Research on the flowrate and diaphragm movement in a diaphragm compressor for a hydrogen refueling station. International Journal of Hydrogen Energy, 41(33):14842-14851, 2016.
-[8] Ren S, Jia X, Jiang J, Peng X. Effect of hydraulic oil compressibility on the volumetric efficiency of a diaphragm compressor for hydrogen refueling stations[J]. International Journal of Hydrogen Energy, 2022, 47(1): 15224-15235.
+[8] Ren S., Jia X., Jiang J., Peng X. Effect of hydraulic oil compressibility on the volumetric efficiency of a diaphragm compressor for hydrogen refueling stations. International Journal of Hydrogen Energy, 47(1):15224-15235, 2022.
-[9] Li J., Liang L., Jia X., et al. A new generatrix of the cavity profile of a diaphragm compressor[J]. Proceedings of the Institution of Mechanical Engineers Part C: Journal of Mechanical Engineering Science, 2014, 228(10):1754-1766.
+[9] Li J., Liang L., Jia X., Peng X. A new generatrix of the cavity profile of a diaphragm compressor. Proceedings of the Institution of Mechanical Engineers Part C: Journal of Mechanical Engineering Science, 228(10):1754-1766, 2014.
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+[10] Hu Y., Xu X., Wang W. A new cavity profile for a diaphragm compressor used in hydrogen fueling stations. International Journal of Hydrogen Energy, 42(38):24458-24469, 2017.
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-[13] Jia X, Chen J, Wu H, Peng X. Study on the diaphragm fracture in a diaphragm compressor for a hydrogen refueling station[J]. International Journal of Hydrogen Energy, 2016,41(15): 6412-6421.
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-[14] Liu X, Tian J, Chen R, et al. Fluid characteristics analysis and structure optimization in diaphragm compressor[C]. Third international conference on mechanical design and simulation. SPIE, 2023, 12639: 863-873.
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-[15] Solovev M, Leonhardt A, Graf A, et al. Development of geometry variants and forming technology for metal diaphragms to increase the efficiency of diaphragm compressor[C]. IOP Conference Series: Materials Science and Engineering. IOP Publishing, 2023, 1284(1): 012009.
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-[16] Bayrak G. Wavelet transform-based fault detection method for hydrogen energy-based distributed generators[J]. International Journal of Hydrogen Energy, 2018, 43(44):20293-20308.
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-[17] Li X, Chen J, Wang Z, et al. A non-destructive fault diagnosis method for a diaphragm compressor in the hydrogen refueling station[J]. International Journal of Hydrogen Energy, 2019, 44(44):24301:24311.
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 {| class="wikitable" style="margin: 1em auto 0.1em auto;border-collapse: collapse;font-size:85%;width:auto;"
 |-style="text-align:center"
-! Case !! ''c'' (%) !! ''d'' (mm) !! ''b'' (mm) !! ''h'' (mm)
+! Case !! <math display="inline"> c </math> (%) !! <math display="inline">  d</math> (mm) !! <math display="inline">  b</math> (mm) !! <math display="inline"> h </math> (mm)
 |-
 |  style="text-align: center;"|1

@@ Line 308: / Line 308: @@
 (2) Based on the numerical simulation model of diaphragm compressor sealing performance, the influence of sealing ring compression rate, sealing ring diameter, and sealing groove structure on the sealing performance of diaphragm compressor was obtained. The compression rate of the sealing ring has a significant impact on the sealing performance of the diaphragm compressor. As the compression rate increases by 20% and 25%, the contact pressure increases by 42.0% and 77.5%, respectively. When the compression rate is 25%, for a sealing ring with the diameter of 7.0mm, an increase of 0.5mm in groove width results in a decrease of 8.1% in maximum contact pressure. For the selection of large-diameter sealing rings and the design of sealing groove structures, it is necessary to comprehensively analyze the significant effects of sealing ring compression rate and sealing groove width on the contact pressure of the sealing interface, providing a design basis for improving sealing performance.
-==Acknowledge==
+==Acknowledgements==
 The work was supported by Key Science and Technology Project in Henan Province (221100240200), Chinese Postdoctoral Science Foundation (2023M733196), Henan Provincial Department of Science and Technology Research Project (232102241030&222102240028), and by Key Science and technique R&D Program of Henan Province (212102210275).

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 {| class="wikitable" style="margin: 0em auto 0.1em auto;border-collapse: collapse;width:auto;"
 |-style="background:white;"
-|style="text-align: center;padding:10px;"| [[Image:Review_326545415492-image10.png|600px]]
+|style="text-align: center;padding:10px;"| [[Image:Review_326545415492-image10.png|500px]]
 |-
 | style="background:#efefef;text-align:left;padding:10px;font-size: 85%;"| '''Figure 9'''. Stress distribution diagram of sealing system under different working condition