LJUNGAN BRIDGE, ANGE SWEDEN
|
|
- Darcy Lewis
- 6 years ago
- Views:
Transcription
1 LJUNGAN BRIDGE, ANGE SWEDEN Design of dampers for the hangers 3 to 6 Documentation of the installation procedure and the verification Measurements from Report: W983/115 Contract: M-79-5
2 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 2 Ljungan Bridge, Ange Sweden Design of dampers for the hangers 3 to 6 Documentation of the installation procedure and the verification Measurements from Client: MULTICON GMBH WESEL Prepared by: Prof. Sedlacek & Partner Technologien im Bauwesen GmbH TRAGWERKSPLANUNG BAUDYNAMIK WINDINGENIEURWESEN STAHLBAU KONSTRUKTIVER GLASBAU SOFTWAREENTWICKLUNG Pauwelsstraße 19 D Aachen Authors: Dr.-Ing. Michael Hortmanns This report consists of 5 pages. Aachen, November 28 th 25
3 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 3 Content 1 Objectives Design of the dampers Maximum allowable amplitudes Maximum amplitudes without dampers Required structural damping of the hangers Damper Design Measurements Results Conclusion References...21 Annex A Detailed Results of manual excitation
4 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 4 1 Objectives At a railway bridge crossing the river Ljungan close to Ange in Sweden full-scale tests were performed in order to measure the first eigen-frequencies and the structural damping of each hanger. These data have been used for the design of dampers, which were installed in September 25. This report describes the design of the dampers and the measurements at the bridge after the installation of the dampers. Figure 1.1 Sight view on the bridge from North (the bridge in the front is not connected to the arch bridge)
5 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 5 2 Design of the dampers 2.1 Maximum allowable amplitudes The maximum allowable amplitudes were given by the client Bankverket in Sweden. The following table shows the tolerable values, which will ensure, if they are not exceeded, that no additional fatigue-damage problems will occur. Table 2.1 Tolerable amplitudes Hanger maximum tolerable amplitudes given by Bankverket perpendicular =y parallel =x mm mm SW-6O 2, 2, SW-5OO 2, 2, SW-4OO 1,5 1,5 SW-3OO 1, 1, 2.2 Maximum amplitudes without dampers For the design of the dampers the maximum vibration amplitudes of the hangers, induced by trains crossing the bridge, have to be known. These amplitudes can be obtained from the report [3]. In this report long term measurements at the hangers SW-3OO, SW-4OO, SW- 5OO and SW-6OO are documented. In the figures and Time histories of the response for different kind of trains are reported. Based on these results the following maximum amplitudes for each hanger will be used.
6 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 6 Table 2.2 Maximum measured vibration amplitudes of the hangers, obtained from [3], yellow fields estimated based on measured damping values and maximum amplitudes for hangers SW- 5OO SW-3OO Hanger measured maximum vibration amplitudes ID9 perpendicular =y ID9 parallel =x ID19 perpendicular =y ID19 parallel =x maximum tolerable amplitudes given by Bankverket perpendicular =y parallel =x measured structural damping mean value perpendicular =y measured structural damping mean value parallel =x mm mm mm mm mm mm - - SW-3WO 19,8 1,67 7,2 8, 1, 1,,1,6 SW-4WO 24,23 8,8 2,77 3,6 1,5 1,5,13,1 SW-5WO 16, 2,33 2,5 1,33 2, 2,,15,3 SW-6O 2,8 4,2 3,25 2,4 2, 2,,14,11 SW-5OO 16, 7, 2,5 4, 2, 2,,15,1 SW-4OO 35, 11, 4, 4,5 1,5 1,5,9,8 SW-3OO 11, 4, 4, 3, 1, 1,,18,16 SW-3WU 22, 6,4 8, 4,8 1, 1,,9,1 SW-4WU 26,25 4,4 3, 1,8 1,5 1,5,12,2 SW-5WU 8, 1,273 1,25,727 2, 2,,3,55 SW-6U 22,4 7,7 3,5 4,4 2, 2,,13,6 SW-5OU 2,4,778,375,444 2, 2,,1,9 SW-4OU 22,5 6,769 2,571 2,769 1,5 1,5,14,13 SW-3OU 6, 8, 2,182 6, 1, 1,,33,8 2.3 Required structural damping of the hangers For the design of the dampers it will be assumed, that the maximum amplitudes will occur for a quasi resonant vibrations. This allows to calculate the maximum required structural damping by using the following formulae: δ = required, i δ, i * y y max, i tolerable, i with: δ required required logarithmic decrement of damping for hanger i δ o,i y max,i y tolerable,i existing logarithmic decrement of damping without damper for hanger i maximum measured vibration amplitude for hanger I tolerable vibration amplitude for hanger i and the additional damping δ i for hanger i is then: δ = δ i required, i δ, i For the damper design both directions, parallel and perpendicular are considered. The following table shows the required damping for each hanger. The values, marked yellow are values which are calculated assuming, that the maximum amplitudes for these hangers are
7 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 7 the same than for the hangers which were analysed in the long term measurements of the university of Stockholm [3]. Table 2.3 Required damping values for each hanger for vibrations parallel and perpendicular Frequency (without dampers) Frequency (without dampers) gen. Mass (with d=8mm and m=39,46 kg/m) minimum log. Decrement of structural damping mimimum log. Decrement of structural damping total log. Decrement of damping required total log. Decrement of damping required additional Damping required additional Damping required Hanger perpendicular parallel Length d=8mm perpendicular parallel perpendicular parallel perpendicular parallel Hz Hz m kg SW-3WO 6,25 7,81 6,24 123,1,1,6,198,64,188,58 SW-4WO 5,67 6,45 7,36 145,1,13,1,21,59,197,49 SW-5WO 4,98 5,71 8, 157,8,15,3,12,35,15,5 SW-6O 4,35 4,98 8,23 162,4,1,1,146,23,136,13 SW-5OO 3,71 4,3 8, 157,8,13,6,12,35,17,29 SW-4OO 5,96 7,23 7,36 145,1,8,5,21,59,22,54 SW-3OO 6,6 7,72 6,24 123,1,8,12,198,64,19,52 SW-3WU 7,52 8,3 6,24 123,1,9,1,198,64,189,54 SW-4WU 4,69 5,57 7,36 145,1,12,2,21,59,198,39 SW-5WU 5,8 6,25 8, 157,8,3,55,12,35,9, SW-6U 5,3 5,96 8,23 162,4,13,6,146,23,133,17 SW-5OU 4,79 5,67 8, 157,8,1,9,12,35,2, SW-4OU 5,47 6,16 7,36 145,1,14,13,21,59,196,46 SW-3OU 6,84 8,5 6,24 123,1,33,8,198,64,165, Damper Design The dynamic properties of the damper shave been calculated based on the provisions given by den Hartog. The calculation is given exemplary for the damper 4WO in the following tables. The exciting force amplitude of F =2 N in the calculation was estimated based on the results of the long term full scale tests. Assuming a quasi resonant response of the hangers, the force amplitude can be calculated with: F = y δ ω m π i 2, i max, i i gen, i with: y max,i maximum amplitude measured at hanger i δ i ω i m gen,i For hanger 4WU this gives: existing logarithmic decrement of damping without damper for hanger i circular-frequency for hanger I generalized mass for hanger i F,4WU,13 = π = π 2 24, 23/1 (2 5, 67) ,5 N In the calculations the exciting force has been taken constant for all hangers.
8 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 8 The first table shows the calculation result for a damper which increases the damping up to the required damping value. Table 2.4 Calculation sheet for the damper properties of hanger 4WU, for the required damping value SW-4WO log. Decrement δvorh,13 gen. Mass M gen 145 kg Eigenfrequenc y f e 5,67 Hz Exciting Force F err 2 N gen. Stiffness c gen N/m min. massratio required 1,9 µerf % min. mass m erf required 1,589 kg opt. Dampig ratio in % D opt,63 opt. Damping constant k opt 7 kg/s Frequency damper f D 5,61 Hz Stiffness damper c D N/m Amplitude Hauptma. y 1,47 mm rel. Ampl. y Damper Dämpfer 1,82 mm It can be seen, that the relative amplitude of the damper is very large. Therefore the calculation has been optimised such, that the relative amplitude is in a range of only 3 mm. This ensures, that no fatigue problems will occur at the cantilever beams inside the damper boxes. The result for the second calculation is given in Table 2.5. These calculations were done for all hangers and all directions. The final dampers design consists of 4 boxes for each hanger, which means, that the damper mass calculated in Table 2.5 is divided into 4 parts. This procedure allows to minimize the size of the cantilever spring inside the boxes and to minimize the external dimensions of the entire damper for each hanger. Due to the mass, which is larger than the mass which is necessary to reach the required damping value, the maximum additional damping will become larger and the dampers will work in a broad range of frequencies. This gives additional safety and ensures, that the dampers will be effective also when trains with different weight, and therefore different influence on the eigen-frequencies of the hangers, will pass the bridge. The damping inside of the boxes is realized with silicon oil. Due to the low temperatures, which may occur at the site in Sweden a Silicon oil with properties, which are comparable over a wide range of temperatures has been used.
9 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 9 Table 2.5 Calculation sheet for the damper properties of hanger 4WU, for rel. Amplitudes of ca. 3mm SW-4WO log. Decrement δvorh,13 gen. Mass M gen 145 kg Eigenfrequenc y f e 5,67 Hz Exciting Force F err 2 N gen. Stiffness c gen N/m min. massratio required 4,9 µerf % min. mass m erf required 5,933 kg opt. Dampig ratio in % D opt,1166 opt. Damping constant k opt 49 kg/s Frequency damper f D 5,45 Hz Stiffness damper c D 6.95 N/m Amplitude Hauptma. y,77 mm rel. Ampl. y Damper Dämpfer 3,2 mm The dampers consist of 4 boxes filled with silicon oil, a cantilever beam with circular cross section and a mass, which is connected at the end of the beam. The length of the cantilever beams can be adjusted by screws at the top of the boxes. The amount of silicon oil can be changed by removing the cantilever beams and then to fill in or to remove silicon oil. This procedure is necessary to get the correct height of silicon oil inside of the boxes. The height of the silicon oil in the boxes has to be in a specific range, because the distance on which the damper masses are dipped into the silicon oil is the dominant parameter to get the correct damper constant. This process was done in the laboratory in Aachen. Therefore, the dampers could be delivered to the bridge with their final adjustment. During the installation process only two times the dampers have been readjusted (5WU and 3 WU). The following figure shows the sketches prepared by the company Multicon.
10 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 1 Figure 2.1 Drawings of the dampers, prepared by Multicon GmbH The dampers have been installed in the middle of each hanger. The position of the dampers are illustrated in the following figure.
11 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 11 Figure 2.2 Position of the dampers The damper have been installed with the help of a rail bus on the bridge. The following figures show some images of the installation procedure. Figure 2.3 Fixation of the bottom ring
12 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 12 Figure 2.4 Connecting the two halves of the damper with screws Figure 2.5 Control of the screws and fixation with Logtite
13 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 13 Figure 2.6 Installing the "cones" and sealing with Silicone Figure 2.7 Damper installed with measurement equipment
14 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 14 Figure 2.8 Almost all dampers installed Figure 2.9 Full scale bridge with all dampers installed
15 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 15 3 Measurements The hangers are excited by hand in resonance parallel and perpendicular to the bridge axis. The vibration amplitudes are measured with 2 sensors (accelerometers), which are fixed at a level close to the middle of each hanger. The definition of hanger numbering and the numbering of the sensors are shown in the following figure. Please note, only the accelerometers A and B have been used for the verification measurements. The numbering of the hangers is the same like in the first measurements. Figure 3.1 Definition of hanger numbering and of the positions of the accelerometers The hangers are numbered as follows: iwo iwu ioo iou Hanger number i, West upstream Hanger number i, West downstream Hanger number i, East upstream Hanger number i, East downstream During the installation and measurement process the bridge was occupied by a rail-bus, which was used to get access to the hangers. The following figure shows the rail-bus on the bridge.
16 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 16 Bild 3.1 Rail bus in the middle of the bridge The weight of the rail bus is much larger that the weight of the tractor, which was used in the first measurements. Due to the weight of the rail bus the normal forces in the hangers were increased and the eigen-frequencies have been larger, than those expected in the calculations for the damper design. This effect was large for all measurements, where the railbus was standing completely on the bridge. In the comparisons of the results (see 4) it can be seen, that for the hangers on the West-side of the bridge the measured frequencies are much closer to the expected frequencies than the frequencies on the East Side of the bridge. Bild 3.2 Signboard at the rail bus with characteristic data, especially weight = 28,3 t
17 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 17 4 Results The following table shows a comparison of the damping values required and the measured damping values. Table 4.1 Comparison of measured damping values with damper with the damping values required total log. Decrement of damping required total log. Decrement of damping required total log. Decrement of damping measured with damper (mean value of evaluable range of amplitudes) safety factor: damping measured/ damping required Hanger perpendicular parallel perpendicular parallel perpendicular parallel SW-3WO,198,64,3,16 1,5 2,5 SW-4WO,21,59,31,4 1,5 6,8 SW-5WO,12,35,27,23 2,3 6,6 SW-6O,146,23,25,15 1,7 6,5 SW-5OO,12,35,33,17 2,8 4,9 SW-4OO,21,59,4,16 1,9 2,7 SW-3OO,198,64,33,12 1,7 1,9 SW-3WU,198,64,25,2 1,3 3,1 SW-4WU,21,59,3,32 1,4 5,5 SW-5WU,12,35,2,2 1,7 5,7 SW-6U,146,23,2,35 1,4 15,2 SW-5OU,12,35,27,4 2,3 11,4 SW-4OU,21,59,3,22 1,4 3,8 SW-3OU,198,64,2,11 1, 1,7 The measured damping values are always equal or larger than the required values. The maximum safety factors are 2,8 for vibrations perpendicular to the bridge axis and 15,2 for vibrations parallel to the bridge axis. Table 4.2 shows a comparison of the eigen-frequencies. As mentioned already the rail bus had a significant influence on the eigen-frequencies. Almost all eigen-frequencies on the East side of the bridge are larger than the expected ones. Anyway, even the frequencies were not always in the expected range, the effectiveness of the dampers is always sufficient. Another special effect can be seen at hanger 5WU. In the first measurements already, the eigen-frequencies for this hanger were lower with the tractor on the bridge. This result was
18 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 18 marked with stars in figure 3.2 and figure 3.3. of report W967/65). Obviously the dynamic behaviour of this hanger is influenced by the connection between the hanger and the arch. Figure 4.1 shows this in detail. The relatively small gap between the hanger and the borders of the lower flange of the arch lead to a direct contact between the hanger and the flange if the hanger starts vibrating. Therefore it is difficult to excite the hanger without the hanger touching the bottom flange. Even the frequencies are not in the expected range the damping values with damper are sufficient, also for this hanger. Very small gap Figure 4.1 Detail of the connection between hanger 5WU and the arch
19 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 19 Table 4.2 Comparison of the Eigen-frequencies for the first mode perpendicular and parallel to the bridge axis, results of the first measurements, expected frequencies with dampers and the measured values with the rail bus on the bridge Hanger Frequencies without Frequencies expected with Frequencies measured with damper damper damper (and railbus) perpendicular parallel perpendicular parallel perpendicular parallel =y =x =y =x =y =x Hz Hz Hz Hz Hz Hz SW-3WO 6,25 7,81 5,8 7,24 5,86 7,22 SW-4WO 5,67 6,45 5,32 6,5 5,8 6,25 SW-5WO 4,98 5,71 4,69 5,38 4,3 6,1 SW-6O 4,35 4,98 4,1 4,7 4,6 5,4 SW-5OO 3,71 4,3 3,5 4,5 3,9 4,7 SW-4OO 5,96 7,23 5,59 6,78 5,47 7,4 SW-3OO 6,6 7,72 5,62 7,16 6,26 8,1 SW-3WU 7,52 8,3 6,97 7,7 6,64 7,6 SW-4WU 4,69 5,57 4,4 5,22 4,5 5,27 SW-5WU 5,8 6,25 4,79 5,89 3,6 4,6 SW-6U 5,3 5,96 4,75 5,62 4,6 5,8 SW-5OU 4,79 5,67 4,51 5,34 4,2 5,7 SW-4OU 5,47 6,16 5,13 5,77 5,8 6,74 SW-3OU 6,84 8,5 6,34 7,88 6,25 8,6
20 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 2 5 Conclusion The damping values with dampers are much large than without damper. The required values at each hanger are reached or exceeded. The maximum safety factor is 2,1 for vibrations perpendicular to the bridges axis and 13, for vibrations parallel to the bridge axis. Due to the mass of the dampers itself and due to the weight of the rail bus, which is much larger than the weight of the tractor, the frequencies are different compared with the results of the first measurements. The influence of the rail bus will increase the frequencies of the hangers. Due to that, the dampers are not working in their optimal design point. Anyway, this will happen every time when trains will pass the bridge. This was the reason why the dampers were designed such, that they are working in a broad band of frequencies. Therefore the effect of the dampers is anytime sufficient, even so when the frequencies of the hangers are not in the optimal range. The conclusion of the measurements is: The required damping values for all hangers are reached or exceeded. Therefore, the performance of the bridge has reached the required value.
21 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 21 6 References [1] EN , Zylindrische Schraubenfedern aus runden Drähten und Stäben Berechnung und Konstruktion Teil 3: Drehfedern, Dezember 25 [2] Hortmanns M., Ljungan Bridge, Ange Sweden Full Scale Measurements, , Report W967/65, PSP-Technologien im Bauwesen GmbH [3] Andersson A., Malm R.; Measurement evaluation and FEM Simulation of Bridge dynamcis A case study of a langer beam bridge, Technical report from Royal Institute of Technology Department of Mechanics, Stockholm Sweden, January 24
22 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 22 Annex A Detailed Results of manual excitation
23 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wo-1k-a Figure A. 1 Hanger 3WO (West, upstream, perpendicular) with damper
24 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wo-3k-b Figure A. 2 Hanger 3WO (West, upstream, parallel) with damper
25 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wo-2n_a Figure A. 3 Hanger 4WO (West, upstream, perpendicular) with damper
26 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wo-4n-b Figure A. 4 Hanger 4WO (West, upstream, parallel) with damper
27 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wo-5-bp Figure A. 5 Hanger 5WO (West, upstream, perpendicular) with damper
28 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page E-5 2.5E-5 2E-5 1.5E-5 1E-5 5E wo-4-b-b Figure A. 6 Hanger 5WO (West, upstream, parallel) with damper
29 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page o-1n-a_ Figure A. 7 Hanger 6WO (upstream, perpendicular) with damper
30 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page o-3n-b_ Figure A. 8 Hanger 6WO (upstream, parallel) with damper
31 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page oo-2n-a Figure A. 9 Hanger 5OO (East, upstream, perpendicular) with damper
32 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page oo-5n-b Figure A. 1 Hanger 5OO (East, upstream, parallel) with damper
33 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page o-1n-a Figure A. 11 Hanger 4OO (East, upstream, perpendicular) with damper
34 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page oo-3n-b Figure A. 12 Hanger 4OO (East, upstream, parallel) with damper
35 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page oo-1n-a Figure A. 13 Hanger 3OO (East, upstream, perpendicular) with damper
36 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page oo-4n-b Figure A. 14 Hanger 3OO (East, upstream, parallel) with damper
37 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wu-1k-a Figure A. 15 Hanger 3WU (West, downstream, perpendicular) with damper
38 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wu-3k-b Figure A. 16 Hanger 3WU (West, downstream, parallel) with damper
39 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wu-2-bp Figure A. 17 Hanger 4WU (West, downstream, perpendicular) with damper
40 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wu-5-bp Figure A. 18 Hanger 4WU (West, downstream, parallel) with damper
41 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wu-1k-a Figure A. 19 Hanger 5WU (West, downstream, perpendicular) with damper
42 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page wu-3k-b Figure A. 2 Hanger 5WU (West, downstream, parallel) with damper
43 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page u-2_a Figure A. 21 Hanger 6U (downstream, perpendicular) with damper
44 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page u-4-b-bp Figure A. 22 Hanger 6U (downstream, parallel) with damper
45 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page ou-1n-a Figure A. 23 Hanger 5OU (East, downstream, perpendicular) with damper
46 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page ou-4n-b Figure A. 24 Hanger 5OU (East, downstream, parallel) with damper
47 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page ou-1n-a Figure A. 25 Hanger 4OU (East, downstream, perpendicular) with damper
48 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page ou-3n-b Figure A. 26 Hanger 4OU (East, downstream, parallel) with damper
49 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page ou-1n-a Figure A. 27 Hanger 3OU (East, downstream, perpendicular) with damper
50 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page ou-3k-b- Figure A. 28 Hanger 3OU (East, downstream, parallel) with damper
51 Ljungan Bridge, Ange Schweden W983/95 Design of the Dampers and Verification-measurements, Page 51 Tragwerksplanung Baudynamik Konstruktiver Glasbau Windingenieurwesen Stahlbau Softwareentwicklung Pauwelsstraße 19 D-5274 Aachen Phone: 49 () 241 / Fax. - / mail@psp-tech.de Internet:
Switch design optimisation: Optimisation of track gauge and track stiffness
1 Switch design optimisation: Optimisation of track gauge and track stiffness Elias Kassa Professor, Phd Department of Civil and Transport Engineering, NTNU Trondheim, Norway E-mail: elias.kassa@ntnu.no
More informationAPMP TCAUV Workshop The application of acoustics, vibration and ultrasound metrology in transportation industry
APMP TCAUV Workshop The application of acoustics, vibration and ultrasound metrology in transportation industry The Analysis of Pole and Viaduct Structural Vibration Induced by High Speed Train Speaker
More informationA Comparison of the Effectiveness of Elastomeric Tuned Mass Dampers and Particle Dampers
003-01-1419 A Comparison of the Effectiveness of Elastomeric Tuned Mass Dampers and Particle Dampers Copyright 001 Society of Automotive Engineers, Inc. Allan C. Aubert Edward R. Green, Ph.D. Gregory Z.
More informationGT-Suite Users Conference
GT-Suite Users Conference Thomas Steidten VKA RWTH Aachen Dr. Philip Adomeit, Bernd Kircher, Stefan Wedowski FEV Motorentechnik GmbH Frankfurt a. M., October 2005 1 Content 2 Introduction Criterion for
More informationParameter optimisation design for a six-dof heavy duty vehicle seat suspension
11 th World Congress on Structural and Multidisciplinary Optimisation 07 th -12 th, June 2015, Sydney Australia Parameter optimisation design for a six-dof heavy duty vehicle seat suspension Donghong Ning,
More informationDevelopment and validation of a vibration model for a complete vehicle
Development and validation of a vibration for a complete vehicle J.W.L.H. Maas DCT 27.131 External Traineeship (MW Group) Supervisors: M.Sc. O. Handrick (MW Group) Dipl.-Ing. H. Schneeweiss (MW Group)
More informationInfluential Criteria on the Optimization of a Gearbox, with Application to an Automatic Transmission
Influential Criteria on the Optimization of a Gearbox, with Application to an Automatic Transmission Peter Tenberge, Daniel Kupka and Thomas Panéro Introduction In the design of an automatic transmission
More informationDamping in. Prepared by: Steven Hale, M.S.M.E Senior Engineering Manager
in ANSYS/LS-Dyna Prepared by: Steven Hale, M.S.M.E Senior Engineering Manager ANSYS/LS-Dyna allows Rayleigh damping constants α and β only. What is damping? The energy dissipation mechanism that causes
More informationCHAPTER 1 BALANCING BALANCING OF ROTATING MASSES
CHAPTER 1 BALANCING Dynamics of Machinery ( 2161901) 1. Attempt the following questions. I. Need of balancing II. Primary unbalanced force in reciprocating engine. III. Explain clearly the terms static
More informationMultiphysics Modeling of Railway Pneumatic Suspensions
SIMPACK User Meeting Salzburg, Austria, 18 th and 19 th May 2011 Multiphysics Modeling of Railway Pneumatic Suspensions Nicolas Docquier Université catholique de Louvain, Belgium Institute of Mechanics,
More informationSTIFFNESS CHARACTERISTICS OF MAIN BEARINGS FOUNDATION OF MARINE ENGINE
Journal of KONES Powertrain and Transport, Vol. 23, No. 1 2016 STIFFNESS CHARACTERISTICS OF MAIN BEARINGS FOUNDATION OF MARINE ENGINE Lech Murawski Gdynia Maritime University, Faculty of Marine Engineering
More informationDevelopment of a multi-passive tuned mass damper, theory and experiments
Proceedings of the 9th International Conference on Structural Dnamics, EURODYN 4 Porto, Portugal, 3 June - Jul 4 A. Cunha, E. Caetano, P. Ribeiro, G. Müller (eds.) ISSN: 3-9; ISBN: 978-97-7-6-4 Development
More informationMinimizing Noise. Marybeth G. Nored Dr. Klaus Brun Eugene Buddy Broerman Augusto Garcia Hernandez Dennis Tweten. Southwest Research Institute
Minimizing Noise Marybeth G. Nored Dr. Klaus Brun Eugene Buddy Broerman Augusto Garcia Hernandez Dennis Tweten Southwest Research Institute Gas Electric Partnership Workshop September 9, 2010 Photo courtesy
More information2. Write the expression for estimation of the natural frequency of free torsional vibration of a shaft. (N/D 15)
ME 6505 DYNAMICS OF MACHINES Fifth Semester Mechanical Engineering (Regulations 2013) Unit III PART A 1. Write the mathematical expression for a free vibration system with viscous damping. (N/D 15) Viscous
More informationDriving techniques and strategies for freight trains
Driving techniques and strategies for freight trains P. Lukaszewicz Railway Technology KTH (Royal Institute of Technology), Sweden. Abstract Driving techniques for freight trains are affected by parameters
More informationPROCEEDINGS. High Tech in Heavy Haul
PROCEEDINGS International Heavy Haul Conference Specialist Technical Session Kiruna, Sweden June 11-13, 2007 High Tech in Heavy Haul International Heavy Haul Association Hosted by: Conference Sponsors:
More informationSTRUCTURAL BEHAVIOUR OF 5000 kn DAMPER
STRUCTURAL BEHAVIOUR OF 5000 kn DAMPER I.H. Mualla Dr. Eng. CTO of DAMPTECH A/S E.D. Jakupsson Dept. of Civil Engineering, Technical University of Denmark L.O. Nielsen Professor, Dept. of Civil Engineering,
More informationOperation Manual for Torque Sensors
Operation Manual for Torque Sensors For below and similar Types DV-14 DH-15 D-2431 DFW-25 DFW-35 D-2223 D-2268 D-2209 DF-30 D-2553 Page 1 of 11 Imprint LORENZ MESSTECHNIK GmbH Manufacturer, Place Lorenz
More informationFEASIBILITY STYDY OF CHAIN DRIVE IN WATER HYDRAULIC ROTARY JOINT
FEASIBILITY STYDY OF CHAIN DRIVE IN WATER HYDRAULIC ROTARY JOINT Antti MAKELA, Jouni MATTILA, Mikko SIUKO, Matti VILENIUS Institute of Hydraulics and Automation, Tampere University of Technology P.O.Box
More informationSpecial edition paper
Countermeasures of Noise Reduction for Shinkansen Electric-Current Collecting System and Lower Parts of Cars Kaoru Murata*, Toshikazu Sato* and Koichi Sasaki* Shinkansen noise can be broadly classified
More informationSeismic-upgrading of Existing Stacks of Nuclear Power Station using Structural Control Oil Dampers
October 12-17, 28, Beijing, China ABSTRACT : Seismic-upgrading of Existing Stacks of Nuclear Power Station using Structural Control Oil Dampers Ryu Shimamoto 1, Fukashi Mori 2, Tomonori Kitaori 2, Satoru
More informationControlling Forces. Vibration Damper Hydrodamp
Controlling Forces. Vibration Damper Hydrodamp 1 Vibration Damping Means Economy. Modern engines with high torques and optimized fuel consumption are making significantly higher demands on today s drive
More informationConstructive Influences of the Energy Recovery System in the Vehicle Dampers
Constructive Influences of the Energy Recovery System in the Vehicle Dampers Vlad Serbanescu, Horia Abaitancei, Gheorghe-Alexandru Radu, Sebastian Radu Transilvania University Brasov B-dul Eroilor nr.
More informationw o r k o G E x - p e S i n c e r t Elegance and Strength BBR HiAm CONA Strand Stay Cable Damping Systems
o b a l N e t w o r k l o G f A E x - p e S i n c e 1 9 4 4 - s r t Elegance and Strength BBR HiAm CONA Strand Stay Cable Damping Systems 1 Cable vibration and damping Despite the wide use of cable-stayed
More informationInfluence of Kink Protection Systems on a Tram Passing Through Curve
Influence of Kink Protection Systems on a Tram Passing Through Curve Grzegorz Fira, Tomas Załuski, Albert Szałajko,, Augsburg, 8-9 October www.ec-e.pl Content Existing system of kink protection for a tram
More informationPassive Vibration Reduction with Silicone Springs and Dynamic Absorber
Available online at www.sciencedirect.com Physics Procedia 19 (2011 ) 431 435 International Conference on Optics in Precision Engineering and Nanotechnology 2011 Passive Vibration Reduction with Silicone
More informationOscillating Mountings
Type HS for hanging screens H B F E HS 7 38 D A HS 45 50 HS 50- Z C G M L M L M L Art. o. Type Load capacity Gmin. G [] A unloaded A* load B unloaded B* load C D E F H L M Weight [kg] 07 311 001 HS 7 500
More informationa. Open the Lab 2 VI file in Labview. Make sure the Graph Type is set to Displacement (one of the 3 tabs in the graphing window).
Lab #2 Free Vibration (Experiment) Name: Date: Section / Group: Part I. Displacement Preliminaries: a. Open the Lab 2 VI file in Labview. Make sure the Graph Type is set to Displacement (one of the 3 tabs
More informationFull Scale Experimental Evaluation for Cable Dampers
Full Scale Experimental Evaluation for Cable Dampers Liang Dong, Tian Jingxian, Du Chuang, Ma Jinlong Abstract One of the key techniques for building long span cable-stayed bridge is the mitigation of
More informationAN EXPERIMENTAL STUDY OF THE AERODYNAMICS FORCES ACTING ON A TRUCK
AN EXPERIMENTAL STUDY OF THE AERODYNAMICS FORCES ACTING ON A TRUCK Mustofa* * Abstract The aim of this project is to show the aerodynamics experiment results of a truck in terms of drag coefficient (C
More informationEXTERNAL DAMPING OF STAY CABLES USING ADAPTIVE AND SEMI-ACTIVE VIBRATION CONTROL
EXTERNAL DAMPING OF STAY CABLES USING ADAPTIVE AND SEMI-ACTIVE VIBRATION CONTROL Andreas Andersson, Alan O Connor 2, Raid Karoumi 3 Researcher, Royal Institute of Technology (KTH, Stockholm, Sweden 2 Associate
More informationDESIGN OF A MODULAR STEERING SYSTEM TEST BENCH FOR DURABILITY, PERFORMANCE AND CHARACTERIZATION TESTS
DESIGN OF A MODULAR STEERING SYSTEM TEST BENCH FOR DURABILITY, PERFORMANCE AND CHARACTERIZATION TESTS Elif KILINÇ, Dr. Orhan ATABAY, Şeref Server ERSOLMAZ, Hatice ERDOĞAN, Automotive Technologies Research
More informationProceedings of the World Congress on Engineering 2008 Vol II WCE 2008, July 2-4, 2008, London, U.K.
Development and Optimization of Vibration Protection Seats (Tempered Springs) for Agricultural Tractor Ch.Sreedhar 1, Assoc. Professor; Dr. K.C.B. Raju 2, Dy.G.M.BHEL; Dr. K. Narayana Rao 3, AICTE; Abstract:
More informationhofer powertrain GmbH
Berlin, 2.12.2009 Your Partner for energy-efficient powertrain systems hofer powertrain GmbH A company of hofer AG 72644 Oberboihingen Nürtinger Strasse 78 E-Mail: info@hofer.de www.hofer.de www.hofer.de
More informationVIBRATION ANALYSIS OPERATIONAL DEFLECTION SHAPES & MODE SHAPES VERIFICATION OF ANALYTICAL MODELLING MATTIA PIRON GIOVANNI BORTOLAN LINO CORTESE
VIBRATION ANALYSIS OPERATIONAL DEFLECTION SHAPES & MODE SHAPES VERIFICATION OF ANALYTICAL MODELLING MATTIA PIRON GIOVANNI BORTOLAN LINO CORTESE 27 June, 2018 ABSTRACT 2 In the process of designing an alternator
More informationDYNAMIC TESTS ON A CONCRETE SLAB WITH A TUNED MASS DAMPER
MATEC Web of Conferences, 6 ( 15) DOI: 1.151/ matecconf/ 15 6 C Owned by the authors, published by EDP Sciences, 15 DYNAMIC TESTS ON A CONCRETE SLAB WITH A TUNED MASS DAMPER Jorge Eliécer Campuzano Carmona
More informationExperimental investigation on vibration characteristics and frequency domain of heavy haul locomotives
Journal of Advances in Vehicle Engineering 3(2) (2017) 81-87 www.jadve.com Experimental investigation on vibration characteristics and frequency domain of heavy haul locomotives Lirong Guo, Kaiyun Wang*,
More informationNew Concept for Higher Speed on Existing Catenary System: Auxiliary Pantograph Operation
New Concept for Higher Speed on Existing Catenary System: Auxiliary Pantograph Operation Zhendong Liu, Sebastian Stichel, Per-Anders Jönsson KTH Royal Institute of Technology, Sweden Anders Rønnquist NTNU
More informationSystem. Hefei University of Technology, China. Hefei University of Technology, China. Hefei University of Technology, China
Automobile Power-train Coupling Vibration Analysis on Vehicle System Heng DING 1 ; Weihua ZHANG 2 ; Wuwei CHEN 3 ; Peicheng Shi 4 1 Hefei University of Technology, China 2 Hefei University of Technology,
More informationLocation of Noise Sources in Fluid Power Machines
International Journal of Occupational Safety and Ergonomics (JOSE) 2007, Vol. 13, No. 4, 441 450 Location of Noise Sources in Fluid Power Machines Wiesław Fiebig Institute of Machine Design, Wrocław University
More informationForced vibration frequency response for a permanent magnetic planetary gear
Forced vibration frequency response for a permanent magnetic planetary gear Xuejun Zhu 1, Xiuhong Hao 2, Minggui Qu 3 1 Hebei Provincial Key Laboratory of Parallel Robot and Mechatronic System, Yanshan
More informationNUMERICAL ANALYSIS OF LOAD DISTRIBUTION IN RAILWAY TRACK UNDER WHEELSET
Journal of KONES Powertrain and Transport, Vol., No. 3 13 NUMERICAL ANALYSIS OF LOAD DISTRIBUTION IN RAILWAY TRACK UNDER WHEELSET Piotr Szurgott, Krzysztof Berny Military University of Technology Department
More informationCompatibility DME and engine oil
Compatibility DME and engine oil Energirelaterad fordonsforskning 2017 Henrik Salsing, Volvo Group Trucks Technology, Research Institutes of Sweden Content Introduction The project DME background Problem
More informationNEW INNOVATION. Shock Absorber Tester. Model: MAHA-Shock-Diagnostic MSD 3000
Wir im Allgäu. Shock Absorber Tester Model: MAHA-Shock-Diagnostic MSD 3000 NEW INNOVATION For easy and accurate testing of the shock absorbers - Indirect shock absorber test based on the new Theta principle.
More informationU X Y W L. Gear wheels. Linkage. In option: Stainless steel AISI 304L , AISI 316L or painted steel (standard RAL)
Commercial dampers of the U range are designed to control or shut off ductworks with airtightness classifi cation going from non-classifi ed to class 4 according to EN1751. The handling and installation
More informationModeling of 17-DOF Tractor Semi- Trailer Vehicle
ISSN 2395-1621 Modeling of 17-DOF Tractor Semi- Trailer Vehicle # S. B. Walhekar, #2 D. H. Burande 1 sumitwalhekar@gmail.com 2 dhburande.scoe@sinhgad.edu #12 Mechanical Engineering Department, S.P. Pune
More informationFAILURE ANALYSIS & REDESIGN OF A BRAKE CALLIPER SUPPORT. Prof. A. Bracciali, Dr. F. Piccioli, T. De Cicco
FAILURE ANALYSIS & REDESIGN OF A BRAKE CALLIPER SUPPORT Prof. A. Bracciali, Dr. F. Piccioli, T. De Cicco Dipartimento di Meccanica e Tecnologie Industriali Università di Firenze, via Santa Marta 3, 50139
More informationRETRACTED. Vibration Mitigation of Shazand Railway Bridge Induced by Train Using Tuned Mass Damper (TMD) P Periodica Polytechnica
P Periodica Polytechnica Mechanical Engineering P 59(4), pp. 189-198, 2015 DOI: 10.3311/PPme.8327 Creative Commons Attribution b research article Vibration Mitigation of Shazand Railway Bridge Induced
More informationElbtalwerk GmbH. Universität Karlsruhe Elektrotechnisches Institut. Switched Reluctance Motor. Compact High-torque Electric Motor. Current.
Elbtalwerk GmbH Switched Reluctance Motor Compact High-torque Electric Motor Current B1 Winding A1 D4 C1 C4 Pole D1 Rotation B4 A2 Rotor tooth Shaft A4 B2 Field line D3 C2 C3 D2 Stator A3 B3 Cooling air
More informationPermissible Track Forces for Railway Vehicles
British Railways Board Page 1 of 11 Part A Synopsis This document prescribes design and maintenance requirements for traction and rolling stock and for on track plant to ensure that interactive forces
More informationMulti-axial fatigue life assessment of high speed car body based on PDMR method
MATEC Web of Conferences 165, 17006 (018) FATIGUE 018 https://doi.org/10.1051/matecconf/01816517006 Multi-axial fatigue life assessment of high speed car body based on PDMR method Chaotao Liu 1,*, Pingbo
More informationinter.noise 2000 The 29th International Congress and Exhibition on Noise Control Engineering August 2000, Nice, FRANCE
Copyright SFA - InterNoise 2000 1 inter.noise 2000 The 29th International Congress and Exhibition on Noise Control Engineering 27-30 August 2000, Nice, FRANCE I-INCE Classification: 7.6 ROLLING NOISE FROM
More informationA study on the evaluation method of the characteristics of the contact point between wheel and rail
Computers in Railways XI 73 A study on the evaluation method of the characteristics of the contact point between wheel and rail M. Adachi 1 & T. Shimomura 2 1 National Traffic Safety and Environment Laboratory,
More informationSuppression of chatter vibration of boring tools using impact dampers
International Journal of Machine Tools & Manufacture 40 (2000) 1141 1156 Suppression of chatter vibration of boring tools using impact dampers Satoshi Ema a,*, Etsuo Marui b a Faculty of Education, Gifu
More informationModeling and Vibration Analysis of a Drum type Washing Machine
Modeling and Vibration Analysis of a Drum type Washing Machine Takayuki KOIZUMI, Nobutaka TSUJIUCHI, Yutaka NISHIMURA Department of Engineering, Doshisha University, 1-3, Tataramiyakodani, Kyotanabe, Kyoto,
More informationAXLE HOUSING AND UNITIZE BEARING PACK SET MODAL CHARACTERISATION
F2004F461 AXLE HOUSING AND UNITIZE BEARING PACK SET MODAL CHARACTERISATION 1 Badiola, Virginia*, 2 Pintor, Jesús María, 3 Gainza, Gorka 1 Dana Equipamientos S.A., España, 2 Universidad Pública de Navarra,
More informationExperimental Verification of the Implementation of Bend-Twist Coupling in a Wind Turbine Blade
Experimental Verification of the Implementation of Bend-Twist Coupling in a Wind Turbine Blade Authors: Marcin Luczak (LMS), Kim Branner (Risø DTU), Simone Manzato (LMS), Philipp Haselbach (Risø DTU),
More informationFundamental Specifications for Eliminating Resonance on Reciprocating Machinery
1 Fundamental Specifications for Eliminating Resonance on Reciprocating Machinery Frank Fifer, P.Eng. Beta Machinery Analysis Ltd. Houston, Texas Introduction Question: What is the purpose of performing
More informationVALMONT MITIGATOR TR1
VALMONT MITIGATOR TR1 Research Verification of the Valmont TR1 Damper Performance MITIGATOR TR1 VIBRATION DAMPER The Valmont TR1 damper has been specifically designed using vibration theory and innovative
More informationDamping Ratio Estimation of an Existing 8-story Building Considering Soil-Structure Interaction Using Strong Motion Observation Data.
Damping Ratio Estimation of an Existing -story Building Considering Soil-Structure Interaction Using Strong Motion Observation Data by Koichi Morita ABSTRACT In this study, damping ratio of an exiting
More informationShimmy Identification Caused by Self-Excitation Components at Vehicle High Speed
Shimmy Identification Caused by Self-Excitation Components at Vehicle High Speed Fujiang Min, Wei Wen, Lifeng Zhao, Xiongying Yu and Jiang Xu Abstract The chapter introduces the shimmy mechanism caused
More informationDetermination of Spring Modulus for Several Types of Elastomeric Materials (O-rings) and Establishment of an Open Database For Seals*
Determination of Spring Modulus for Several Types of Elastomeric Materials (O-rings) and Establishment of an Open Database For Seals* W. M. McMurtry and G. F. Hohnstreiter Sandia National Laboratories,
More informationActive Suspensions For Tracked Vehicles
Active Suspensions For Tracked Vehicles Y.G.Srinivasa, P. V. Manivannan 1, Rajesh K 2 and Sanjay goyal 2 Precision Engineering and Instrumentation Lab Indian Institute of Technology Madras Chennai 1 PEIL
More informationEurocode 3 Design of steel structures
BRITISH STANDARD BS EN 1993-3-2:2006 Eurocode 3 Design of steel structures Part 3-2: Towers, masts and chimneys Chimneys ICS 91.010.30; 91.060.40; 91.080.10 National foreword This British Standard is the
More informationRIGIFLEX -N RADEX -N. Steel laminae coupling. Steel laminae coupling. You will find continuously updated data in our online catalogue at
117 Table of contents 117 Coupling selection steel laminae coupling 119 Description of coupling 121 General information 122 Types and applications 123 Technical data 124 Standard types 126 Special types
More informationRELIABILITY IMPROVEMENT OF ACCESSORY GEARBOX BEVEL DRIVES Kozharinov Egor* *CIAM
RELIABILITY IMPROVEMENT OF ACCESSORY GEARBOX BEVEL DRIVES Kozharinov Egor* *CIAM egor@ciam.ru Keywords: Bevel gears, accessory drives, resonance oscillations, Coulomb friction damping Abstract Bevel gear
More informationTesting Of Fluid Viscous Damper
Testing Of Fluid Viscous Damper Feng Qian & Sunwei Ding, Jingjing Song Shanghai Research Institute of Materials, China Dr. Chien-Chih Chen US.VF Corp, Omni Device, China SUMMARY: The Fluid Viscous Damper
More informationinter.noise 2000 The 29th International Congress and Exhibition on Noise Control Engineering August 2000, Nice, FRANCE
Copyright SFA - InterNoise 2000 1 inter.noise 2000 The 29th International Congress and Exhibition on Noise Control Engineering 27-30 August 2000, Nice, FRANCE I-INCE Classification: 1.3 CURVE SQUEAL OF
More informationLab Electrical Power Engineering I
INSTITUT FÜR ELEKTRISCHE MASCHINEN RHEINISCH-WESTFÄLISCHE TECHNISCHE HOCHSCHULE AACHEN Lab Electrical Power Engineering I Test 3: Induction machine with squirrel cage rotor and slip ring rotor 1 Experiment
More informationInnovative designs and methods for VHST 2 nd Dissemination Event, Brussels 3 rd November 2016
Capacity for Rail Innovative designs and methods for VHST 2 nd Dissemination Event, Brussels 3 rd November 2016 Miguel Rodríguez Plaza Adif Introduction C4R WP 1.2: VHST 2 Objectives: To identify market
More informationDrivetrain Simulation and Load Determination using SIMPACK
Fakultät Maschinenwesen, Institut für Maschinenelemente und Maschinenkonstruktion, Lehrstuhl Maschinenelemente Drivetrain Simulation and Load Determination using SIMPACK SIMPACK Conference Wind and Drivetrain
More informationAPS 400 ELECTRO-SEIS. Long Stroke Shaker Page 1 of 5. Applications. Features
Long Stroke Shaker Page 1 of 5 The APS 400 ELECTRO-SEIS is a force generator specifically designed to be used alone or in arrays for studying dynamic response characteristics of various structures. It
More informationInvestigation of edge strength dependent on different types of edge processing
Investigation of edge strength dependent on different types of edge processing Jonas KLEUDERLEIN *, Frank ENSSLEN a, Jens SCHNEIDER b * Technische Universität Darmstadt, Institut für Werkstoffe und Mechanik
More informationDevelopment of a Dual Mode Vibration Isolator for a Laser Communication Terminal
Development of a Dual Mode D-Strut@ Vibration Isolator for a Laser Communication Terminal Dale T. Ruebsamen, James Boyd*, Joe Vecera. and Roger Nagel Abstract This paper provides a review of the development
More informationModeling tire vibrations in ABS-braking
Modeling tire vibrations in ABS-braking Ari Tuononen Aalto University Lassi Hartikainen, Frank Petry, Stephan Westermann Goodyear S.A. Tag des Fahrwerks 8. Oktober 2012 Contents 1. Introduction 2. Review
More informationThe Transrapid Guideway Switch Test and Verifikation
The Transrapid Guideway Switch Test and Verifikation (*) Karl Fichtner, (**) Franz Pichlmeier (*) ThyssenKrupp Transrapid GmbH, Moosacher Str. 58, 80809 Munich, Germany Phone +49 89 35 46 91 19, Fax: +49
More informationTechnical Guide No. 7. Dimensioning of a Drive system
Technical Guide No. 7 Dimensioning of a Drive system 2 Technical Guide No.7 - Dimensioning of a Drive system Contents 1. Introduction... 5 2. Drive system... 6 3. General description of a dimensioning
More informationFinite Element Modeling and Analysis of Vehicle Space Frame with Experimental Validation
Finite Element Modeling and Analysis of Vehicle Space Frame with Experimental Validation Assoc. Prof Dr. Mohammed A.Elhaddad Mechanical Engineering Department Higher Technological Institute, Town of 6
More informationMAURER Cable damper systems
Head Office Frankfurter Ring 193, 80807 München/Germany Telephone +49 89 323 94-0 Telefax +49 89 323 94-329 Branch Office Zum Holzplatz 2, 44536 Lünen/Germany Telephone +49 231 434 01-0 Telefax +49 231
More informationElectromagnetic clutch-brake combinations INTORQ
Electromagnetic clutch-brake combinations INTORQ 14.800 14.867 7.5 120 Nm setting the standard 2 CBC en 5/2005 Contents Clutch-brake combinations Product information 4 Type code 6 Design selection 8 Overview
More informationAPS 420 ELECTRO-SEIS Long Stroke Shaker with Linear Ball Bearings Page 1 of 5
Long Stroke Shaker with Linear Ball Bearings Page 1 of 5 The APS 420 ELECTRO-SEIS shaker is a long stroke, electrodynamic force generator specifically designed to be used alone or in arrays for studying
More informationKINEMATICAL SUSPENSION OPTIMIZATION USING DESIGN OF EXPERIMENT METHOD
Jurnal Mekanikal June 2014, No 37, 16-25 KINEMATICAL SUSPENSION OPTIMIZATION USING DESIGN OF EXPERIMENT METHOD Mohd Awaluddin A Rahman and Afandi Dzakaria Faculty of Mechanical Engineering, Universiti
More information1962: HRCS Circular 482 one-page document, specified vehicle mass, impact speed, and approach angle for crash tests.
1 2 3 1962: HRCS Circular 482 one-page document, specified vehicle mass, impact speed, and approach angle for crash tests. 1973: NCHRP Report 153 16-page document, based on technical input from 70+ individuals
More informationLoad Analysis and Multi Body Dynamics Analysis of Connecting Rod in Single Cylinder 4 Stroke Engine
IJSRD - International Journal for Scientific Research & Development Vol. 3, Issue 08, 2015 ISSN (online): 2321-0613 Load Analysis and Multi Body Dynamics Analysis of Connecting Rod in Single Cylinder 4
More informationDynamic Response of High-Speed-Moving Vehicle Subjected to Seismic Excitation Considering Passengers' Dynamics
Dynamic Response of High-Speed-Moving Vehicle Subjected to Seismic Excitation Considering Passengers' Dynamics A. Shintani, T. Ito, C. Nakagawa & Y. Iwasaki Osaka Prefecture University, Japan SUMMARY:
More informationAPPLICATION OF A NEW TYPE OF AERODYNAMIC TILTING PAD JOURNAL BEARING IN POWER GYROSCOPE
Colloquium DYNAMICS OF MACHINES 2012 Prague, February 7 8, 2011 CzechNC APPLICATION OF A NEW TYPE OF AERODYNAMIC TILTING PAD JOURNAL BEARING IN POWER GYROSCOPE Jiří Šimek Abstract: New type of aerodynamic
More informationDetermination and improvement of bevel gear efficiency by means of loaded TCA
Determination and improvement of bevel gear efficiency by means of loaded TCA Dr. J. Thomas, Dr. C. Wirth, ZG GmbH, Germany Abstract Bevel and hypoid gears are widely used in automotive and industrial
More informationMulti-Body Simulation of Powertrain Acoustics in the Full Vehicle Development
Page 1 Multi-Body Simulation of Powertrain Acoustics in the Full Vehicle Development SIMPACK User Meeting 2011 Alexander Schmid, IABG mbh Andreas Raith, BMW Group Salzburg, Page 2 Powertrain Acoustics
More informationEFFECTIVE SOLUTIONS FOR SHOCK AND VIBRATION CONTROL
EFFECTIVE SOLUTIONS FOR SHOCK AND VIBRATION CONTROL Part 1 Alan Klembczyk TAYLOR DEVICES, INC. North Tonawanda, NY Part 2 Herb LeKuch Shocktech / 901D Monsey, NY SAVIAC Tutorial 2009 Part 1 OUTLINE Introduction
More informationREDUCTION OF SEAT VIBRATION IN AN ATV THROUGH DESIGN MODIFICATION
REDUCTION OF SEAT VIBRATION IN AN ATV THROUGH DESIGN MODIFICATION 1 C. LAKSHMIKANTHAN, 2 DISHEED MULLANGATH, 3 NITIN KUMAR S, 4 SUBBU DHEIVARAYAN S, 5 GOUTHAMAN S 1 Assistant Professor, 2,3,4,5 Student,
More informationMULTI-PARAMETER OPTIMIZATION OF BRAKE OF PISTON
3 2 1 MULTI-PARAMETER OPTIMIZATION OF BRAKE OF PISTON Á. Horváth 1, I. Oldal 2, G. Kalácska 1, M. Andó 3 Institute for Mechanical Engineering Technology, Szent István University, 2100 Gödöllő, Páter Károly
More informationVehicle Dynamic Simulation Using A Non-Linear Finite Element Simulation Program (LS-DYNA)
Vehicle Dynamic Simulation Using A Non-Linear Finite Element Simulation Program (LS-DYNA) G. S. Choi and H. K. Min Kia Motors Technical Center 3-61 INTRODUCTION The reason manufacturers invest their time
More informationRigid-Flexible Coupling Dynamics Simulation Analysis of Wheel/Rail Interaction in High-speed Turnout Zone
Rigid-Flexible Coupling Dynamics Simulation Analysis of Wheel/Rail Interaction in High-speed Turnout Zone 1 China Academy of Railway Sciences Beijing, 100081, China E-mail: ym890531@163.com Weidong Wang
More informationAbstract In this paper, we developed a lateral damper to improve the running safety of railway vehicles
Improvement of Running Safety of Railway Vehicles against an Earthquake Kohei Iida, Mitsugi Suzuki, Takefumi Miyamoto, Yukio Nishiyama, Daichi Nakajima Railway Technical Research Institute, Tokyo, JAPAN
More informationOn the prediction of rail cross mobility and track decay rates using Finite Element Models
On the prediction of rail cross mobility and track decay rates using Finite Element Models Benjamin Betgen Vibratec, 28 Chemin du Petit Bois, 69130 Ecully, France. Giacomo Squicciarini, David J. Thompson
More informationRegulation: R16 Course & Branch: B.Tech EEE
SIDDHARTH GROUP OF INSTITUTIONS :: PUTTUR Siddharth Nagar, Narayanavanam Road 517583 QUESTION BANK (Descriptive) Subject with Code : Electrical Machines-II (16EE215) Regulation: R16 Course & Branch: B.Tech
More informationSW160 Bogie Dynamics Analysis with Magic Formula Damper Model at CARS
SW160 Bogie Dynamics Analysis with Magic Formula Damper Model at CARS China Academy of Railway Science (CARS), Beijing, P.R.China, 100081 Zhan Wenzhang Wang Chengguo Qian Lixin ZF Sachs AG, Bogestrasse
More informationDynamic characteristics of railway concrete sleepers using impact excitation techniques and model analysis
Dynamic characteristics of railway concrete sleepers using impact excitation techniques and model analysis Akira Aikawa *, Fumihiro Urakawa *, Kazuhisa Abe **, Akira Namura * * Railway Technical Research
More informationOPTIMISING CHASSIS ALIGNMENT USING VEHICLE SENSORS
Link: https://www.springerprofessional.de/en/optimising-chassis-alignment-using-vehicle-sensors/6115514 SPECIAL ASSEMBLY OPTIMISING CHASSIS ALIGNMENT USING VEHICLE SENSORS The commissioning processes at
More informationAPS 113 ELECTRO-SEIS Long Stroke Shaker with Linear Ball Bearings Page 1 of 5
Long Stroke Shaker with Linear Ball Bearings Page 1 of 5 The ELECTRO-SEIS shaker is a long stroke, electrodynamic force generator specifically designed to be used alone or in arrays for studying dynamic
More information