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Contents
1. 8 Fig 9 Eccentrically contacted of coupling flange C I 30mm 3 8 40mm Photo 8 Pinion gear of Ist reduction2. 1 1969 2 LP 3 4 E 5 6 35
3. 8 Lower Photo 10 Rear bearing of deauction gear 2 mm 9 as c 11 12 31 Photo 1 1 View of lst reduction gear Photo 12 View of bearing and shaft ID A B 9 a c
4. 25 nip b Fig 7 Disposition of reduction gear turbine roter main shaft and coupling etc Photo 4 Front bearing of steam turbine 560 ZO S PZzb5n D WI DM IOBRUSTED 2 ngot I 26 Photo 5 Rear bearing of steam turbine Photo 6 Mounting bolts of bearing 3
5. A d A I 2 20 ig 2 Sketch of metanophosed main shaft Unit mm 2 A BB SNC 21
6. 4 c 5 c d 5 a B B A A 4 b d 6 7 B B 4 7 C C2 6 4
7. 5s Canemil turbine 3m 2 ie JEF 286KW 380HP 357 5KW 450H P
8. B 2 7 6
9. 9 d A 9 10 Fig 10 Rotation of turbine and pinion shaft 32 C
10. 4 15m SM Toe o Borat LN 23 i Fig 4 Disposition of cane mill shop and place of flinders 3 3 23 Photo 3 II uuo PUTA 3 5 h 6
11. 65mm 22 1 25kg mm
12. B 4 3 21 B 7 Photo 7 4
13. 5 6 9 10 2 29 AHG y o E Y A URE OIEIRSEECZHPT Table 5 Breakage exrent of Ist reduction pinion ETS B 1 3 cm 13 2 Hi fiii Heil O DEARI TEL RR 3 d Hem BA O _ YI HEBEL BCRHBIEL IL GA eX BERE HOKAR o EM BR 33 HHBORX HCKIRA 5 6
14. 1 Table Clearance of bearing of steam turbine x i 0 13 0 24 0 30 XE 0 13 0 35 0 40 0 18 0 20 0 15 0 20 0 25 F 0 10 0 30 0 40 yeya RFP i 0 30 0 40 R 0 10 0 30 0 40 0 25 0 27 y WU wx 0 20 _ 0 50 0 60 0 25 0 27 _ GR R 020 0 50 0 60 0 25 0 27 8 2 3 3 3 1 100 150 2 100 mm
15. 0 36mm n Do 1 10 12 14kg cm 230 270 1 19 Q 7 80 P 6 E I IIT Mite z pU di Muki 6 9 Td xg 60 n a H BE EA 1 AIDAN D beet NIC a Na JA 50 ii lut lt A 3 10 9 F kg X m PLE ET 0 2n 3 02 WE 6W 20 341 10 20 312 30 3 10 27 1968f 1969ff Fig 1 Bearing temperatureof steam turbine Photo 1 Recording of steam pressure 4
16. 150 HJ 7 B B 4 5
17. 11 11 Sh a xD e f 2 3 90 ES Hi Fig 11 Eccentric rotation of turbine shaft and pinion shaft 5 c
18. 4 Fig 7 Detormation of coupling flange Table 4 Flexure volume of coupling flanges N y EMA y P O JRA y TY Y ZDR A 9g mm 9r mm 9 cm 9x nm 0 48 1 05 3 17 55 1 69 0o0 2 0 49 LH ID 5 1 01 3 0 36 09 MI 0 89 0 54 4 56 0 10 3 04 5 19 0 09 0 2 31 3 60 on is 17 19 28 CLR 24 26 4 7 8 9E dr doli 7 II GBDO AE F GRO A ER be cL pee 8iXvc7TuEIXIUCOGS5 Il0xX55bh5k5uct n5 7J972708
19. OKE S UE T wis 5 1
20. 13kg cm 280C 1 Okg cm 4 500RPM 2 98 yi 2 5E sp FIE 500mm 50 126 95mm 4 23 686 mm 4 166 ID 74mm w ikib 7 ig 2 m H 6 kg cm g Q 5kg cm g 666 6RPM UE AIT 35mm 25mm 4 150RPM C Jil y a o 24 0 DA 18 3 1961 8 8
21. Q M B RR University of the Ryukyus Ime rrnnnnnpnnnnnnnnr mm Buldnof Science amp Citation Engineering 2 University of the Ryukyus Engineering 4 17 3 http ir li b u ryukyu ac j p handle 123456789 24008 BiRAC UUNUGSTZHU the mU EE An Investigation of Damged Turbines and Reduction Gears in Cane Sugar Mill Plant Cane sugar making has been a principal industry in Oinawa for a long time and recently the equipments and processes of the sugarmaking has been modernized by introducing high pressure boilers and steam turbines So the proper operation and maintenance of every mechanical unit in the factory have become important tasks from the viewpoint of engineers because a single trouble of the mechanical unit will possibly cause a large damage in the operation of the mill plant This paper deals with systematic analysis of a mechanical accident of the mill turbines and reduction gears at one of the cane sugar mill plants in Okinawa The work includes the investigation of the operative and maintenance conditions at every mechanical unit visual identification of the damaged parts mill turbine axis teeth of the reduction gears metal bearings and the couplings and the composition analysis of the turbine axis material Through a close examination of these minor analyses the main factors which have caused the accident are pointed out as follows 1 The
22. NiCr 2 0 34 0 64 0 014 0 24 0 082 Table 2 Component of turbine shaft 2 3 Photo 2 Broken faces of stean turbine shaft Fig 3 Sketch of broken face N 4 150 RPM P 286 KW
23. fatigue phenomenon on the face of the damaged turbine axis 2 The eccentric revolution of the turbine axis due to the wear of the metal bearings arings 3 Axial forces between the flanges of the couplings while the eccentric running of the turbine axis 4 Scratched flaws on the thrust faces of the metal bearings 5 The large clearance between the metal bearing and the turbine axis x Yasuji Makishi le 10 15 x 1970 12 15 BE Dore IL FE 17 20kg em2
24. 5 h VIN SN A SANI As 99 Cn Zr zx IX 4i Table 3 Wear volume of Po 5 ErWIMEAATM XX 4 TIE NE YT h 1 0 955 ETE JP i 675 9 E NB N L 4 455 9 D do 67 8 69 0 0 8 1 1 8 7 89 Lr 0 5 SER 0 _ 69 0 EI 4 682 89 3 0 9 67 8 68 9 0 5 5 684 69 8 LO 6 5 50 03 LK mri m T 67 5 68 8 ASY 0 1 2209 29053 2157 67 8 68 8 0 6 E1298 9 0 2 908 0 9 3 1 STOLO 458829 9 672 5 3 TREE HA 70 0 24 68 2 66 7 24 TER lo 8 BR Y B amp B 5 4 3 31 E 4 4 5 B 7 B 3 I AR 4 Bp Lo Fig 6 Wear volume condition 2 5 mm 5
25. 5k8bth 5 33 x amp d s am S Tan SF amp gd il FTF E pet 2 Er gi Me 5 N pum s 1 zf 1 N LEES i c i D E k M x scu Fig 12 Relation of every causc EERO WRN Y A 6a E A 4 IE 12
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