Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis

Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The...
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Gespeichert in:

Autor*in:	Huo, Junzhou [verfasserIn] Wu, Hanyang [verfasserIn] Ji, Wenbo [verfasserIn]

Format:	E-Artikel
Sprache:	Englisch

Erschienen:	2020

Schlagwörter:	Dynamics Field vibration test Multi-degree of freedom dynamic model Vibration absorption structure Vibration characteristics TBM

Übergeordnetes Werk:	Enthalten in: Journal of mechanical science and technology - Berlin : Springer, 2005, 34(2020), 11 vom: Nov., Seite 4405-4421
Übergeordnetes Werk:	volume:34 ; year:2020 ; number:11 ; month:11 ; pages:4405-4421

Links:	Volltext

DOI / URN:	10.1007/s12206-020-0703-5

Katalog-ID:	SPR042079047

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520			\|a Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. To minimize system vibration, the optimal design parameters of the system was determined. The maximum amplitude of the axial and horizontal overturning vibration of the support frame was reduced by 26.7 % and 13 %, and the maximum amplitude of the cutterhead’s axial vibration was reduced by 23.2 %.
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650		4	\|a Vibration absorption structure \|7 (dpeaa)DE-He213
650		4	\|a Vibration characteristics \|7 (dpeaa)DE-He213
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author_variant	j h jh h w hw w j wj
matchkey_str	article:19763824:2020----::niirtodsgfrbmidieytmaeomliietoaculndn
hierarchy_sort_str	2020
publishDate	2020
allfields	10.1007/s12206-020-0703-5 doi (DE-627)SPR042079047 (SPR)s12206-020-0703-5-e DE-627 ger DE-627 rakwb eng 620 ASE Huo, Junzhou verfasserin aut Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis 2020 Text txt rdacontent Computermedien c rdamedia Online-Ressource cr rdacarrier Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. To minimize system vibration, the optimal design parameters of the system was determined. The maximum amplitude of the axial and horizontal overturning vibration of the support frame was reduced by 26.7 % and 13 %, and the maximum amplitude of the cutterhead’s axial vibration was reduced by 23.2 %. Dynamics (dpeaa)DE-He213 Field vibration test (dpeaa)DE-He213 Multi-degree of freedom dynamic model (dpeaa)DE-He213 Vibration absorption structure (dpeaa)DE-He213 Vibration characteristics (dpeaa)DE-He213 TBM (dpeaa)DE-He213 Wu, Hanyang verfasserin aut Ji, Wenbo verfasserin aut Enthalten in Journal of mechanical science and technology Berlin : Springer, 2005 34(2020), 11 vom: Nov., Seite 4405-4421 (DE-627)58714016X (DE-600)2467571-4 1976-3824 nnns volume:34 year:2020 number:11 month:11 pages:4405-4421 https://dx.doi.org/10.1007/s12206-020-0703-5 lizenzpflichtig Volltext GBV_USEFLAG_A SYSFLAG_A GBV_SPRINGER GBV_ILN_11 GBV_ILN_20 GBV_ILN_22 GBV_ILN_23 GBV_ILN_24 GBV_ILN_31 GBV_ILN_32 GBV_ILN_39 GBV_ILN_40 GBV_ILN_60 GBV_ILN_62 GBV_ILN_63 GBV_ILN_65 GBV_ILN_69 GBV_ILN_70 GBV_ILN_73 GBV_ILN_74 GBV_ILN_90 GBV_ILN_95 GBV_ILN_100 GBV_ILN_105 GBV_ILN_110 GBV_ILN_120 GBV_ILN_138 GBV_ILN_150 GBV_ILN_151 GBV_ILN_152 GBV_ILN_161 GBV_ILN_170 GBV_ILN_171 GBV_ILN_187 GBV_ILN_213 GBV_ILN_224 GBV_ILN_230 GBV_ILN_250 GBV_ILN_281 GBV_ILN_285 GBV_ILN_293 GBV_ILN_370 GBV_ILN_602 GBV_ILN_636 GBV_ILN_702 GBV_ILN_2001 GBV_ILN_2003 GBV_ILN_2004 GBV_ILN_2005 GBV_ILN_2006 GBV_ILN_2007 GBV_ILN_2008 GBV_ILN_2009 GBV_ILN_2010 GBV_ILN_2011 GBV_ILN_2014 GBV_ILN_2015 GBV_ILN_2020 GBV_ILN_2021 GBV_ILN_2025 GBV_ILN_2026 GBV_ILN_2027 GBV_ILN_2031 GBV_ILN_2034 GBV_ILN_2037 GBV_ILN_2038 GBV_ILN_2039 GBV_ILN_2044 GBV_ILN_2048 GBV_ILN_2049 GBV_ILN_2050 GBV_ILN_2055 GBV_ILN_2056 GBV_ILN_2057 GBV_ILN_2059 GBV_ILN_2061 GBV_ILN_2064 GBV_ILN_2065 GBV_ILN_2068 GBV_ILN_2088 GBV_ILN_2093 GBV_ILN_2106 GBV_ILN_2107 GBV_ILN_2108 GBV_ILN_2110 GBV_ILN_2111 GBV_ILN_2112 GBV_ILN_2113 GBV_ILN_2118 GBV_ILN_2119 GBV_ILN_2122 GBV_ILN_2129 GBV_ILN_2143 GBV_ILN_2144 GBV_ILN_2147 GBV_ILN_2148 GBV_ILN_2152 GBV_ILN_2153 GBV_ILN_2188 GBV_ILN_2190 GBV_ILN_2232 GBV_ILN_2336 GBV_ILN_2446 GBV_ILN_2470 GBV_ILN_2472 GBV_ILN_2507 GBV_ILN_2522 GBV_ILN_2548 GBV_ILN_4035 GBV_ILN_4037 GBV_ILN_4046 GBV_ILN_4112 GBV_ILN_4125 GBV_ILN_4126 GBV_ILN_4242 GBV_ILN_4246 GBV_ILN_4249 GBV_ILN_4251 GBV_ILN_4305 GBV_ILN_4306 GBV_ILN_4307 GBV_ILN_4313 GBV_ILN_4322 GBV_ILN_4323 GBV_ILN_4324 GBV_ILN_4325 GBV_ILN_4326 GBV_ILN_4328 GBV_ILN_4333 GBV_ILN_4334 GBV_ILN_4335 GBV_ILN_4336 GBV_ILN_4338 GBV_ILN_4393 GBV_ILN_4700 AR 34 2020 11 11 4405-4421
spelling	10.1007/s12206-020-0703-5 doi (DE-627)SPR042079047 (SPR)s12206-020-0703-5-e DE-627 ger DE-627 rakwb eng 620 ASE Huo, Junzhou verfasserin aut Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis 2020 Text txt rdacontent Computermedien c rdamedia Online-Ressource cr rdacarrier Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. To minimize system vibration, the optimal design parameters of the system was determined. The maximum amplitude of the axial and horizontal overturning vibration of the support frame was reduced by 26.7 % and 13 %, and the maximum amplitude of the cutterhead’s axial vibration was reduced by 23.2 %. Dynamics (dpeaa)DE-He213 Field vibration test (dpeaa)DE-He213 Multi-degree of freedom dynamic model (dpeaa)DE-He213 Vibration absorption structure (dpeaa)DE-He213 Vibration characteristics (dpeaa)DE-He213 TBM (dpeaa)DE-He213 Wu, Hanyang verfasserin aut Ji, Wenbo verfasserin aut Enthalten in Journal of mechanical science and technology Berlin : Springer, 2005 34(2020), 11 vom: Nov., Seite 4405-4421 (DE-627)58714016X (DE-600)2467571-4 1976-3824 nnns volume:34 year:2020 number:11 month:11 pages:4405-4421 https://dx.doi.org/10.1007/s12206-020-0703-5 lizenzpflichtig Volltext GBV_USEFLAG_A SYSFLAG_A GBV_SPRINGER GBV_ILN_11 GBV_ILN_20 GBV_ILN_22 GBV_ILN_23 GBV_ILN_24 GBV_ILN_31 GBV_ILN_32 GBV_ILN_39 GBV_ILN_40 GBV_ILN_60 GBV_ILN_62 GBV_ILN_63 GBV_ILN_65 GBV_ILN_69 GBV_ILN_70 GBV_ILN_73 GBV_ILN_74 GBV_ILN_90 GBV_ILN_95 GBV_ILN_100 GBV_ILN_105 GBV_ILN_110 GBV_ILN_120 GBV_ILN_138 GBV_ILN_150 GBV_ILN_151 GBV_ILN_152 GBV_ILN_161 GBV_ILN_170 GBV_ILN_171 GBV_ILN_187 GBV_ILN_213 GBV_ILN_224 GBV_ILN_230 GBV_ILN_250 GBV_ILN_281 GBV_ILN_285 GBV_ILN_293 GBV_ILN_370 GBV_ILN_602 GBV_ILN_636 GBV_ILN_702 GBV_ILN_2001 GBV_ILN_2003 GBV_ILN_2004 GBV_ILN_2005 GBV_ILN_2006 GBV_ILN_2007 GBV_ILN_2008 GBV_ILN_2009 GBV_ILN_2010 GBV_ILN_2011 GBV_ILN_2014 GBV_ILN_2015 GBV_ILN_2020 GBV_ILN_2021 GBV_ILN_2025 GBV_ILN_2026 GBV_ILN_2027 GBV_ILN_2031 GBV_ILN_2034 GBV_ILN_2037 GBV_ILN_2038 GBV_ILN_2039 GBV_ILN_2044 GBV_ILN_2048 GBV_ILN_2049 GBV_ILN_2050 GBV_ILN_2055 GBV_ILN_2056 GBV_ILN_2057 GBV_ILN_2059 GBV_ILN_2061 GBV_ILN_2064 GBV_ILN_2065 GBV_ILN_2068 GBV_ILN_2088 GBV_ILN_2093 GBV_ILN_2106 GBV_ILN_2107 GBV_ILN_2108 GBV_ILN_2110 GBV_ILN_2111 GBV_ILN_2112 GBV_ILN_2113 GBV_ILN_2118 GBV_ILN_2119 GBV_ILN_2122 GBV_ILN_2129 GBV_ILN_2143 GBV_ILN_2144 GBV_ILN_2147 GBV_ILN_2148 GBV_ILN_2152 GBV_ILN_2153 GBV_ILN_2188 GBV_ILN_2190 GBV_ILN_2232 GBV_ILN_2336 GBV_ILN_2446 GBV_ILN_2470 GBV_ILN_2472 GBV_ILN_2507 GBV_ILN_2522 GBV_ILN_2548 GBV_ILN_4035 GBV_ILN_4037 GBV_ILN_4046 GBV_ILN_4112 GBV_ILN_4125 GBV_ILN_4126 GBV_ILN_4242 GBV_ILN_4246 GBV_ILN_4249 GBV_ILN_4251 GBV_ILN_4305 GBV_ILN_4306 GBV_ILN_4307 GBV_ILN_4313 GBV_ILN_4322 GBV_ILN_4323 GBV_ILN_4324 GBV_ILN_4325 GBV_ILN_4326 GBV_ILN_4328 GBV_ILN_4333 GBV_ILN_4334 GBV_ILN_4335 GBV_ILN_4336 GBV_ILN_4338 GBV_ILN_4393 GBV_ILN_4700 AR 34 2020 11 11 4405-4421
allfields_unstemmed	10.1007/s12206-020-0703-5 doi (DE-627)SPR042079047 (SPR)s12206-020-0703-5-e DE-627 ger DE-627 rakwb eng 620 ASE Huo, Junzhou verfasserin aut Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis 2020 Text txt rdacontent Computermedien c rdamedia Online-Ressource cr rdacarrier Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. To minimize system vibration, the optimal design parameters of the system was determined. The maximum amplitude of the axial and horizontal overturning vibration of the support frame was reduced by 26.7 % and 13 %, and the maximum amplitude of the cutterhead’s axial vibration was reduced by 23.2 %. Dynamics (dpeaa)DE-He213 Field vibration test (dpeaa)DE-He213 Multi-degree of freedom dynamic model (dpeaa)DE-He213 Vibration absorption structure (dpeaa)DE-He213 Vibration characteristics (dpeaa)DE-He213 TBM (dpeaa)DE-He213 Wu, Hanyang verfasserin aut Ji, Wenbo verfasserin aut Enthalten in Journal of mechanical science and technology Berlin : Springer, 2005 34(2020), 11 vom: Nov., Seite 4405-4421 (DE-627)58714016X (DE-600)2467571-4 1976-3824 nnns volume:34 year:2020 number:11 month:11 pages:4405-4421 https://dx.doi.org/10.1007/s12206-020-0703-5 lizenzpflichtig Volltext GBV_USEFLAG_A SYSFLAG_A GBV_SPRINGER GBV_ILN_11 GBV_ILN_20 GBV_ILN_22 GBV_ILN_23 GBV_ILN_24 GBV_ILN_31 GBV_ILN_32 GBV_ILN_39 GBV_ILN_40 GBV_ILN_60 GBV_ILN_62 GBV_ILN_63 GBV_ILN_65 GBV_ILN_69 GBV_ILN_70 GBV_ILN_73 GBV_ILN_74 GBV_ILN_90 GBV_ILN_95 GBV_ILN_100 GBV_ILN_105 GBV_ILN_110 GBV_ILN_120 GBV_ILN_138 GBV_ILN_150 GBV_ILN_151 GBV_ILN_152 GBV_ILN_161 GBV_ILN_170 GBV_ILN_171 GBV_ILN_187 GBV_ILN_213 GBV_ILN_224 GBV_ILN_230 GBV_ILN_250 GBV_ILN_281 GBV_ILN_285 GBV_ILN_293 GBV_ILN_370 GBV_ILN_602 GBV_ILN_636 GBV_ILN_702 GBV_ILN_2001 GBV_ILN_2003 GBV_ILN_2004 GBV_ILN_2005 GBV_ILN_2006 GBV_ILN_2007 GBV_ILN_2008 GBV_ILN_2009 GBV_ILN_2010 GBV_ILN_2011 GBV_ILN_2014 GBV_ILN_2015 GBV_ILN_2020 GBV_ILN_2021 GBV_ILN_2025 GBV_ILN_2026 GBV_ILN_2027 GBV_ILN_2031 GBV_ILN_2034 GBV_ILN_2037 GBV_ILN_2038 GBV_ILN_2039 GBV_ILN_2044 GBV_ILN_2048 GBV_ILN_2049 GBV_ILN_2050 GBV_ILN_2055 GBV_ILN_2056 GBV_ILN_2057 GBV_ILN_2059 GBV_ILN_2061 GBV_ILN_2064 GBV_ILN_2065 GBV_ILN_2068 GBV_ILN_2088 GBV_ILN_2093 GBV_ILN_2106 GBV_ILN_2107 GBV_ILN_2108 GBV_ILN_2110 GBV_ILN_2111 GBV_ILN_2112 GBV_ILN_2113 GBV_ILN_2118 GBV_ILN_2119 GBV_ILN_2122 GBV_ILN_2129 GBV_ILN_2143 GBV_ILN_2144 GBV_ILN_2147 GBV_ILN_2148 GBV_ILN_2152 GBV_ILN_2153 GBV_ILN_2188 GBV_ILN_2190 GBV_ILN_2232 GBV_ILN_2336 GBV_ILN_2446 GBV_ILN_2470 GBV_ILN_2472 GBV_ILN_2507 GBV_ILN_2522 GBV_ILN_2548 GBV_ILN_4035 GBV_ILN_4037 GBV_ILN_4046 GBV_ILN_4112 GBV_ILN_4125 GBV_ILN_4126 GBV_ILN_4242 GBV_ILN_4246 GBV_ILN_4249 GBV_ILN_4251 GBV_ILN_4305 GBV_ILN_4306 GBV_ILN_4307 GBV_ILN_4313 GBV_ILN_4322 GBV_ILN_4323 GBV_ILN_4324 GBV_ILN_4325 GBV_ILN_4326 GBV_ILN_4328 GBV_ILN_4333 GBV_ILN_4334 GBV_ILN_4335 GBV_ILN_4336 GBV_ILN_4338 GBV_ILN_4393 GBV_ILN_4700 AR 34 2020 11 11 4405-4421
allfieldsGer	10.1007/s12206-020-0703-5 doi (DE-627)SPR042079047 (SPR)s12206-020-0703-5-e DE-627 ger DE-627 rakwb eng 620 ASE Huo, Junzhou verfasserin aut Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis 2020 Text txt rdacontent Computermedien c rdamedia Online-Ressource cr rdacarrier Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. To minimize system vibration, the optimal design parameters of the system was determined. The maximum amplitude of the axial and horizontal overturning vibration of the support frame was reduced by 26.7 % and 13 %, and the maximum amplitude of the cutterhead’s axial vibration was reduced by 23.2 %. Dynamics (dpeaa)DE-He213 Field vibration test (dpeaa)DE-He213 Multi-degree of freedom dynamic model (dpeaa)DE-He213 Vibration absorption structure (dpeaa)DE-He213 Vibration characteristics (dpeaa)DE-He213 TBM (dpeaa)DE-He213 Wu, Hanyang verfasserin aut Ji, Wenbo verfasserin aut Enthalten in Journal of mechanical science and technology Berlin : Springer, 2005 34(2020), 11 vom: Nov., Seite 4405-4421 (DE-627)58714016X (DE-600)2467571-4 1976-3824 nnns volume:34 year:2020 number:11 month:11 pages:4405-4421 https://dx.doi.org/10.1007/s12206-020-0703-5 lizenzpflichtig Volltext GBV_USEFLAG_A SYSFLAG_A GBV_SPRINGER GBV_ILN_11 GBV_ILN_20 GBV_ILN_22 GBV_ILN_23 GBV_ILN_24 GBV_ILN_31 GBV_ILN_32 GBV_ILN_39 GBV_ILN_40 GBV_ILN_60 GBV_ILN_62 GBV_ILN_63 GBV_ILN_65 GBV_ILN_69 GBV_ILN_70 GBV_ILN_73 GBV_ILN_74 GBV_ILN_90 GBV_ILN_95 GBV_ILN_100 GBV_ILN_105 GBV_ILN_110 GBV_ILN_120 GBV_ILN_138 GBV_ILN_150 GBV_ILN_151 GBV_ILN_152 GBV_ILN_161 GBV_ILN_170 GBV_ILN_171 GBV_ILN_187 GBV_ILN_213 GBV_ILN_224 GBV_ILN_230 GBV_ILN_250 GBV_ILN_281 GBV_ILN_285 GBV_ILN_293 GBV_ILN_370 GBV_ILN_602 GBV_ILN_636 GBV_ILN_702 GBV_ILN_2001 GBV_ILN_2003 GBV_ILN_2004 GBV_ILN_2005 GBV_ILN_2006 GBV_ILN_2007 GBV_ILN_2008 GBV_ILN_2009 GBV_ILN_2010 GBV_ILN_2011 GBV_ILN_2014 GBV_ILN_2015 GBV_ILN_2020 GBV_ILN_2021 GBV_ILN_2025 GBV_ILN_2026 GBV_ILN_2027 GBV_ILN_2031 GBV_ILN_2034 GBV_ILN_2037 GBV_ILN_2038 GBV_ILN_2039 GBV_ILN_2044 GBV_ILN_2048 GBV_ILN_2049 GBV_ILN_2050 GBV_ILN_2055 GBV_ILN_2056 GBV_ILN_2057 GBV_ILN_2059 GBV_ILN_2061 GBV_ILN_2064 GBV_ILN_2065 GBV_ILN_2068 GBV_ILN_2088 GBV_ILN_2093 GBV_ILN_2106 GBV_ILN_2107 GBV_ILN_2108 GBV_ILN_2110 GBV_ILN_2111 GBV_ILN_2112 GBV_ILN_2113 GBV_ILN_2118 GBV_ILN_2119 GBV_ILN_2122 GBV_ILN_2129 GBV_ILN_2143 GBV_ILN_2144 GBV_ILN_2147 GBV_ILN_2148 GBV_ILN_2152 GBV_ILN_2153 GBV_ILN_2188 GBV_ILN_2190 GBV_ILN_2232 GBV_ILN_2336 GBV_ILN_2446 GBV_ILN_2470 GBV_ILN_2472 GBV_ILN_2507 GBV_ILN_2522 GBV_ILN_2548 GBV_ILN_4035 GBV_ILN_4037 GBV_ILN_4046 GBV_ILN_4112 GBV_ILN_4125 GBV_ILN_4126 GBV_ILN_4242 GBV_ILN_4246 GBV_ILN_4249 GBV_ILN_4251 GBV_ILN_4305 GBV_ILN_4306 GBV_ILN_4307 GBV_ILN_4313 GBV_ILN_4322 GBV_ILN_4323 GBV_ILN_4324 GBV_ILN_4325 GBV_ILN_4326 GBV_ILN_4328 GBV_ILN_4333 GBV_ILN_4334 GBV_ILN_4335 GBV_ILN_4336 GBV_ILN_4338 GBV_ILN_4393 GBV_ILN_4700 AR 34 2020 11 11 4405-4421
allfieldsSound	10.1007/s12206-020-0703-5 doi (DE-627)SPR042079047 (SPR)s12206-020-0703-5-e DE-627 ger DE-627 rakwb eng 620 ASE Huo, Junzhou verfasserin aut Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis 2020 Text txt rdacontent Computermedien c rdamedia Online-Ressource cr rdacarrier Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. To minimize system vibration, the optimal design parameters of the system was determined. The maximum amplitude of the axial and horizontal overturning vibration of the support frame was reduced by 26.7 % and 13 %, and the maximum amplitude of the cutterhead’s axial vibration was reduced by 23.2 %. Dynamics (dpeaa)DE-He213 Field vibration test (dpeaa)DE-He213 Multi-degree of freedom dynamic model (dpeaa)DE-He213 Vibration absorption structure (dpeaa)DE-He213 Vibration characteristics (dpeaa)DE-He213 TBM (dpeaa)DE-He213 Wu, Hanyang verfasserin aut Ji, Wenbo verfasserin aut Enthalten in Journal of mechanical science and technology Berlin : Springer, 2005 34(2020), 11 vom: Nov., Seite 4405-4421 (DE-627)58714016X (DE-600)2467571-4 1976-3824 nnns volume:34 year:2020 number:11 month:11 pages:4405-4421 https://dx.doi.org/10.1007/s12206-020-0703-5 lizenzpflichtig Volltext GBV_USEFLAG_A SYSFLAG_A GBV_SPRINGER GBV_ILN_11 GBV_ILN_20 GBV_ILN_22 GBV_ILN_23 GBV_ILN_24 GBV_ILN_31 GBV_ILN_32 GBV_ILN_39 GBV_ILN_40 GBV_ILN_60 GBV_ILN_62 GBV_ILN_63 GBV_ILN_65 GBV_ILN_69 GBV_ILN_70 GBV_ILN_73 GBV_ILN_74 GBV_ILN_90 GBV_ILN_95 GBV_ILN_100 GBV_ILN_105 GBV_ILN_110 GBV_ILN_120 GBV_ILN_138 GBV_ILN_150 GBV_ILN_151 GBV_ILN_152 GBV_ILN_161 GBV_ILN_170 GBV_ILN_171 GBV_ILN_187 GBV_ILN_213 GBV_ILN_224 GBV_ILN_230 GBV_ILN_250 GBV_ILN_281 GBV_ILN_285 GBV_ILN_293 GBV_ILN_370 GBV_ILN_602 GBV_ILN_636 GBV_ILN_702 GBV_ILN_2001 GBV_ILN_2003 GBV_ILN_2004 GBV_ILN_2005 GBV_ILN_2006 GBV_ILN_2007 GBV_ILN_2008 GBV_ILN_2009 GBV_ILN_2010 GBV_ILN_2011 GBV_ILN_2014 GBV_ILN_2015 GBV_ILN_2020 GBV_ILN_2021 GBV_ILN_2025 GBV_ILN_2026 GBV_ILN_2027 GBV_ILN_2031 GBV_ILN_2034 GBV_ILN_2037 GBV_ILN_2038 GBV_ILN_2039 GBV_ILN_2044 GBV_ILN_2048 GBV_ILN_2049 GBV_ILN_2050 GBV_ILN_2055 GBV_ILN_2056 GBV_ILN_2057 GBV_ILN_2059 GBV_ILN_2061 GBV_ILN_2064 GBV_ILN_2065 GBV_ILN_2068 GBV_ILN_2088 GBV_ILN_2093 GBV_ILN_2106 GBV_ILN_2107 GBV_ILN_2108 GBV_ILN_2110 GBV_ILN_2111 GBV_ILN_2112 GBV_ILN_2113 GBV_ILN_2118 GBV_ILN_2119 GBV_ILN_2122 GBV_ILN_2129 GBV_ILN_2143 GBV_ILN_2144 GBV_ILN_2147 GBV_ILN_2148 GBV_ILN_2152 GBV_ILN_2153 GBV_ILN_2188 GBV_ILN_2190 GBV_ILN_2232 GBV_ILN_2336 GBV_ILN_2446 GBV_ILN_2470 GBV_ILN_2472 GBV_ILN_2507 GBV_ILN_2522 GBV_ILN_2548 GBV_ILN_4035 GBV_ILN_4037 GBV_ILN_4046 GBV_ILN_4112 GBV_ILN_4125 GBV_ILN_4126 GBV_ILN_4242 GBV_ILN_4246 GBV_ILN_4249 GBV_ILN_4251 GBV_ILN_4305 GBV_ILN_4306 GBV_ILN_4307 GBV_ILN_4313 GBV_ILN_4322 GBV_ILN_4323 GBV_ILN_4324 GBV_ILN_4325 GBV_ILN_4326 GBV_ILN_4328 GBV_ILN_4333 GBV_ILN_4334 GBV_ILN_4335 GBV_ILN_4336 GBV_ILN_4338 GBV_ILN_4393 GBV_ILN_4700 AR 34 2020 11 11 4405-4421
language	English
source	Enthalten in Journal of mechanical science and technology 34(2020), 11 vom: Nov., Seite 4405-4421 volume:34 year:2020 number:11 month:11 pages:4405-4421
sourceStr	Enthalten in Journal of mechanical science and technology 34(2020), 11 vom: Nov., Seite 4405-4421 volume:34 year:2020 number:11 month:11 pages:4405-4421
format_phy_str_mv	Article
institution	findex.gbv.de
topic_facet	Dynamics Field vibration test Multi-degree of freedom dynamic model Vibration absorption structure Vibration characteristics TBM
dewey-raw	620
isfreeaccess_bool	false
container_title	Journal of mechanical science and technology
authorswithroles_txt_mv	Huo, Junzhou @@aut@@ Wu, Hanyang @@aut@@ Ji, Wenbo @@aut@@
publishDateDaySort_date	2020-11-01T00:00:00Z
hierarchy_top_id	58714016X
dewey-sort	3620
id	SPR042079047
language_de	englisch
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To minimize system vibration, the optimal design parameters of the system was determined. 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author	Huo, Junzhou
spellingShingle	Huo, Junzhou ddc 620 misc Dynamics misc Field vibration test misc Multi-degree of freedom dynamic model misc Vibration absorption structure misc Vibration characteristics misc TBM Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis
authorStr	Huo, Junzhou
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topic_title	620 ASE Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis Dynamics (dpeaa)DE-He213 Field vibration test (dpeaa)DE-He213 Multi-degree of freedom dynamic model (dpeaa)DE-He213 Vibration absorption structure (dpeaa)DE-He213 Vibration characteristics (dpeaa)DE-He213 TBM (dpeaa)DE-He213
topic	ddc 620 misc Dynamics misc Field vibration test misc Multi-degree of freedom dynamic model misc Vibration absorption structure misc Vibration characteristics misc TBM
topic_unstemmed	ddc 620 misc Dynamics misc Field vibration test misc Multi-degree of freedom dynamic model misc Vibration absorption structure misc Vibration characteristics misc TBM
topic_browse	ddc 620 misc Dynamics misc Field vibration test misc Multi-degree of freedom dynamic model misc Vibration absorption structure misc Vibration characteristics misc TBM
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title	Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis
ctrlnum	(DE-627)SPR042079047 (SPR)s12206-020-0703-5-e
title_full	Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis
author_sort	Huo, Junzhou
journal	Journal of mechanical science and technology
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author_browse	Huo, Junzhou Wu, Hanyang Ji, Wenbo
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doi_str_mv	10.1007/s12206-020-0703-5
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title_sort	anti-vibration design for tbm main drive system based on multi-directional coupling dynamic characteristics analysis
title_auth	Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis
abstract	Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. To minimize system vibration, the optimal design parameters of the system was determined. The maximum amplitude of the axial and horizontal overturning vibration of the support frame was reduced by 26.7 % and 13 %, and the maximum amplitude of the cutterhead’s axial vibration was reduced by 23.2 %.
abstractGer	Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. To minimize system vibration, the optimal design parameters of the system was determined. The maximum amplitude of the axial and horizontal overturning vibration of the support frame was reduced by 26.7 % and 13 %, and the maximum amplitude of the cutterhead’s axial vibration was reduced by 23.2 %.
abstract_unstemmed	Abstract Extreme vibration often occurs on TBM main system during the tunneling process. This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. To minimize system vibration, the optimal design parameters of the system was determined. The maximum amplitude of the axial and horizontal overturning vibration of the support frame was reduced by 26.7 % and 13 %, and the maximum amplitude of the cutterhead’s axial vibration was reduced by 23.2 %.
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container_issue	11
title_short	Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis
url	https://dx.doi.org/10.1007/s12206-020-0703-5
remote_bool	true
author2	Wu, Hanyang Ji, Wenbo
author2Str	Wu, Hanyang Ji, Wenbo
ppnlink	58714016X
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doi_str	10.1007/s12206-020-0703-5
up_date	2024-07-04T00:43:35.823Z
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This paper established the mathematical model for TBM main system considering the impact load, time-varying internal incentive and the complex coupling relationship between each vibration degree of freedom. The dynamic model was modified by the multi-point vibration measured data. The calculation error of the system response of the main support frame’s main vibration direction was within 10%. And it was found that the overturning vibration and axial vibration of the system were the main forms of vibration of the system. It was determined that the low-frequency vibration of 15–20 Hz was a coupled vibration of system’s first to fourth mode vibration mode. Based on the vibration characteristics of TBM main system, this paper designed a tuned mass vibration absorption structure (TMVAS) that can adapt to the multi degree of freedom (MDOF) coupling vibration of TBM main system during the actual tunneling process. 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Anti-vibration design for TBM main drive system based on multi-directional coupling dynamic characteristics analysis

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