Academic literature on the topic 'Splined shaft connections'
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Journal articles on the topic "Splined shaft connections"
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Kahn-Jetter, Zella L., Eugene Hundertmark, and Suzanne Wright. "Comparison of Torque Transmitting Shaft Connectivity Using a Trilobe Polygon Connection and an Involute Spline." Journal of Mechanical Design 122, no. 1 (January 1, 2000): 130–35. http://dx.doi.org/10.1115/1.533556.
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The results of a finite element analysis of a trilobe polygon shaft connection used as an alternative for a spline for torque transmission is presented. These results are compared to the results of a finite element analysis previously performed on an involute spline. It is shown that the tensile stress in the polygon shaft is significantly smaller than in the involute spline and is smaller than all the other stresses in both the shaft and the hub in the polygon connection. Furthermore, the magnitudes and distributions of the maximum principal compressive stress, the shear stress, and the Von Mises stress are nearly the same on the shaft and the hub. It appears that polygonal connections can be more advantageous than splined connections because of lower stresses and the lack of stress concentrations typical of splines. [S1050-0472(00)00601-2]
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Шишкин, Сергей, and Sergey Shishkin. "APPLICATION OF FINISH-STRENGTHENING PROCESS WITH DIAMOND SMOOTHING FOR BEARING CAPACITY INCREASE OF JOINTS WITH TIGHTNESS." Bulletin of Bryansk state technical university 2019, no. 6 (June 27, 2019): 4–10. http://dx.doi.org/10.30987/article_5d10851eda9a19.64369355.
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The test results of stress joints with a regular micro-relief with the purpose of the assessment of their operation properties increase at finish-strengthening are shown. Thus, shaft endurance in insertions increases at relief application on the surface of a bush hole. It is explained with the pressure concentration decrease caused by a fit at the expense of the growth of joint contact flexibility. A similar effect is achieved at the creation of an artificial camber of a surface with the purpose of obtaining a characteristic diagram of a con-tact load distribution. The formation of a regular relief on the shaft surface results in, besides strengthening, the insignificant increase of the fatigue strength in joints.
The static strength increase in stressed joints with the regular micro-relief is explained by the contact interaction character of an unevenness at a cross as-semblage and by the increase of an actual contact area at mechanical pressing-in. At that at reassemblies it was observed a lesser decrease of their strength. A sharp increase of bearing capacity is typical for the mating at a balance of micro-relief high-step parame-ters on contact surfaces of a shaft and a bush. The results obtained lead to the idea of the creation of joints like threaded or splined joints at transferring an axial load or a rotational moment.
At the relief formation at the expense of some metal extrusion in overflows there is a raising of a sur-face “plateau” which is used for tightness increase of loose connections and also for rejects correction during manufacturing parts.
In such a way the application of efficient tech-nologies of regular micro-relief coatings along with strengthening increases considerably fatigue and static strength in joints with tightness.
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Kozlov, V. B., A. B. Istomin, and I. N. Gemba. "Repair and restoration of shafts, couplings, splined and keyed joints." Glavnyj mekhanik (Chief Mechanic), no. 7 (June 11, 2021): 32–42. http://dx.doi.org/10.33920/pro-2-2107-03.
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The article provides an overview of the methods of restoration and repair of various parts of the equipment: shafts, couplings, splined and keyed joints. Recommendations on the choice of methods, equipment and tools are given. In case of wear, the keyway is repaired by welding the face with subsequent milling. At the same time, the keyway size set by the standard is maintained. Such repairs are also possible: the keyway is expanded and deepened, completely eliminating the traces of wear, after which a stepped key is made to it. However, with such repairs, a high-quality connection is not provided and, therefore, it is used in exceptional cases (during inspections and ongoing repairs). When repairing keyed joints, the worn keyed joints are not repaired, but new ones are made, fitting them to achieve a firm contact with the side surfaces of the grooves of the connected parts. The exception is the taper keys: they are driven into the keyway with a hammer blow so that they are jammed in height. The taper key should also be hammered in such a way that, when loosened, it can be deposited. Between the head of the key and the end of the part, there must be a distance equal to the height of the key. The connection with the help of splines is used for fixing gears, gear wheels, and bushings on the shafts. It has a number of advantages over other types of connection. The component parts of this joint are more easily centered. This significantly reduces mechanical deformations at the bushing boundary. During operation, under the influence of various loads, the spline joint loses its properties. In this case, the splines or grooves in which they are placed are restored. Splines of small rollers are usually not repaired; the parts with worn splines are mostly replaced with new ones. Such work is carried out in specialized workshops. In some cases, the repair and restoration of such products is carried out in a small workshop, but equipped with the necessary machines.
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Jia, Jian Jun, Hong Xi Wang, and Ling Wang. "Precision Generating Cutting Research of Rectangle Spline Based on Parameters Superposition." Advanced Materials Research 411 (November 2011): 117–20. http://dx.doi.org/10.4028/www.scientific.net/amr.411.117.
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Aiming at the precision generating cutting problem of rectangle spline shaft, the multi-parameter fusion method to modified cutting edge of rectangle spline hob is presented. The method based on the analysis of workpiece machining errors to establish a fusion model about the rectangle spline hob cutting parameters and the rectangle spline shaft deformation quantity, the model can indicate the connection between rectangle spling hob theoretics profile and actual cutting profile, therefore, the rectangle spline hob’s profile is modified and to simulate by polynomials. The simulation experiment indicates that the method exact approximation the hob’s modified profile. Compare with the methods of the double-circular-arc and the least square fitting, the multi-parameter fusion method can enhance both design precision and design efficiency.
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Verbovyi, A., C. Neamtu, M. Sieryk, B. Vashyst, V. Pavlenko, V. Simonovskiy, and I. Pavlenko. "Ensuring the Vibration Reliability of Rotors Connected by Spline Joints." Journal of Engineering Sciences 6, no. 2 (2019): d14—d19. http://dx.doi.org/10.21272/jes.2019.6(2).d3.
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This article is devoted to the development of refined numerical mathematical models of rotor dynamics of high-performance turbomachines having a spline connection. These models consider the dependence of the critical frequencies of the shaft on the angular stiffness of the spline connection, as well as the procedure of virtual balancing. As a result of the complex application of this approach, the methods of calculation of vibration characteristics taking into ac-count variable values of angular rigidity of splined connection are offered. In addition, the method of evaluating the system of initial imbalances with the corresponding displacements of the rotor axis in the correction and calculation sections has also been improved. The proposed approaches, based on the integrated application of CAE software and computational intelligent systems, allow for modal and harmonic analysis and implement virtual balancing with a significant reduction in preparation and machine time without loss of relative accuracy. In addition, the developed mathematical model of free and forced vibrations of rotor systems have been implemented in the program code operational files “Critical Frequencies of the Rotor” and “Forced Oscillations of the Rotor” of the computer algebra system MathCAD that allows improving the dynamic balancing procedure for evaluating primary imbalances. The high accuracy of the proposed approach is confirmed by checking the dynamic deviations of the rotor axis by the system of residual imbalances in accordance with the standards of vibration stability. Keywords: turbomachine, spline connection, angular stiffness, virtual balancing, modal analysis, harmonic analysis.
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Sun, Hua. "Optimization Design of the Composite Hub Connection Structure Based on ANSYS Software Technology." Advanced Materials Research 139-141 (October 2010): 1068–72. http://dx.doi.org/10.4028/www.scientific.net/amr.139-141.1068.
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This article through analysing coupler's structure, involute spline's stress situation, the tooth face contact intensity, the tooth root bending strength, the tooth root shearing strength, tooth face wear ability and the external spline reverse and curving bearing capacity carry on the precise computation and the examination, simultaneously a multianalysis bulge tight joint set of structure and the correlation computation examination, has established the shaft bossing compound coupler main spare part structure type. In this article based on the shaft bossing composite construction optimization design is targeted mainly flexibility swelling ring shape to optimize the design, change that flexibility swelling ring cone-cone angle, which makes flexible swelling ring Auxiliary T-twisting greater. In the analysis, it is necessary to use the software ANSYS, through the creation of the shaft bossing composite construction of the parametrization model, a flexible swelling ring cone-cone angle of the design variables and flexibility swelling ring allowable material stress as binding conditions, bulging with flexible support ring-twisting as the objective function of T,right propeller shaft coupler hub composite structure axisymmetric analysis, contact analysis and design optimization, inflation reached a flexible support ring largest T-twisting, work stress does not exceed the allowable material stress, elastic swelling ring-cone angle of the optimal solution.
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Bodzás, Sándor. "Manufacturing of the surfaces of spline fitting connection." International Journal of Advanced Manufacturing Technology 111, no. 3-4 (October 6, 2020): 909–20. http://dx.doi.org/10.1007/s00170-020-06194-w.
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Abstract The aim of this publication is the analysis of the geometric establishment and the manufacturing designing and development of spline fitting promoting the engineer’s designing works. There are many connection possibilities according to the utilization on different constructions. Based on them, different technologies are needed for the manufacturing of the spline shaft and the spline hole. Generally, milling and grinding technologies are needed. These technologies will be analysed. We design mathematical models for the analysis of the milling technologies by mathematical way. We define the technological parameters and the computed machine time for the manufacturing designing process and recommend technologies for the different shapes.
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Shen, L. J., A. Lohrengel, and G. Schäfer. "Plain–fretting fatigue competition and prediction in spline shaft-hub connection." International Journal of Fatigue 52 (July 2013): 68–81. http://dx.doi.org/10.1016/j.ijfatigue.2012.11.012.
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Luo, You Xin, Heng Shu Li, Hui Jun Wen, and Yu Zhou. "The Propulsion Mechanism with Logarithmic Spiral Profile Shaft Connection." Applied Mechanics and Materials 152-154 (January 2012): 1377–80. http://dx.doi.org/10.4028/www.scientific.net/amm.152-154.1377.
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This paper deals with the existing propulsion mechanism, analyzes the disadvantages of the flat key and the spline, studies the features of the logarithmic spiral profile shaft connection. In an existing chain propulsion mechanism, we change the fit of the inner hole of sprocket gear and the outer circle of intermediate shaft to get a logarithmic spiral profile shaft connection(a keyless joint), then introduce the propulsion mechanism with logarithmic spiral profile shaft connection. At last, applying Solidworks2010 software，we create the three-dimensional modeling of the propulsion mechanism, which would lay a solid foundation for the further study. This new propulsion mechanism has such advantages as self- centralizing, easy disassembly, low stress concentration, with a simple fit cross-section, transmitting big torque, suitable for the heavy loads of rock drilling.
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Luo, You Xin, Heng Shu Li, Hui Jun Wen, and Yu Zhou. "The Propulsion Mechanism with Cosine Tooth Profile Shaft Connection." Applied Mechanics and Materials 152-154 (January 2012): 1389–92. http://dx.doi.org/10.4028/www.scientific.net/amm.152-154.1389.
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This paper consists of research for actuality of propulsion mechanism, analysis of the disadvantage of flat key and spline, and analysis of features of the cosine tooth profile shaft connection. Based on existing chain propulsion mechanism, the propulsion mechanism with cosine tooth profile shaft connection is introduced, in which the cosine tooth profile shaft connection without key is composed of inner hole of sprocket gear and the outer circle of intermediate shaft with cosine tooth profile. The three-dimensional modeling is made by Solidworks2010 for the propulsion mechanism with cosine tooth profile shaft connection and provides fundamental base for the further research and application. This new propulsion mechanism has such advantages as self-centralizing, easy disassembly, low stress concentration, with a simple fit cross-section, transmitting big torque, suitable for the heavy loads of rock drilling
Dissertations / Theses on the topic "Splined shaft connections"
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Daryusi, Ali. "Beitrag zur Ermittlung der Kerbwirkung an Zahnwellen mit freiem und gebundenem Auslauf." Doctoral thesis, Saechsische Landesbibliothek- Staats- und Universitaetsbibliothek Dresden, 2009. http://nbn-resolving.de/urn:nbn:de:bsz:14-ds-1240915811153-56748.
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Durch die zunehmende technologische Entwicklung des Getriebe-, Gelenkwellen-, Werkzeugmaschinen-, Kraftfahrzeug-, sowie Landmaschinenbaus steigen die zu übertragenden Leistungen und Drehmomente enorm. Dies führt zu einem wachsenden Bedarf an formschlüssigen Profilwellenverbindungen und deren erhöhter Lebensdauer und Genauigkeit. Hierbei bilden die Zahnwellenverbindungen (ZWVen) mit Evolventenflanken nach DIN 5480 /N1/ den Regelfall für eine Vielzahl der Anwendung. Abhängig von Festigkeitsüberlegungen, Herstellungsverfahren und Platzbedarf treten in der Praxis nahezu ausschließlich die folgenden zwei Grundtypen auf. Es handelt sich dabei zum Ersten um die Zahnwelle (ZW) mit freiem Auslauf.Die zweite Geometrievariante ist die Zahnwelle mit gebundenem Auslauf, die eine nach DIN 471 /N2/ genormte Sicherungsringnut (SRN) enthalten kann. Zahnwellenverbindungen dienen zur Übertragung großer, wechselnder und stoßartiger Drehmomente ohne zusätzliches Verbindungselement durch die Profilierung der Welle und Nabe. Axiale Verschiebbarkeit unter Last, Profilverschiebungsmöglichkeit, einfache Montage und Demontage sowie die Herstellung mit hochleistungsfähigen umformenden und spanenden Massenfertigungsverfahren, die die Herstellungskosten verhältnismäßig niedrig halten, sind technisch bedeutsame Eigenschaften, die zum ansteigenden Einsatz von ZWVen führen (z.B. /N1/, /Vil84/, /Koh86/ und /Wes96/). Starke Kerbwirkung und erhebliche Überdimensionierung benachbarter Gestaltungszonen sind die wesentlichen Schwachpunkte der Profilverbindungen. Eine große Anzahl (ca. 80 %) von Ausfällen im Maschinenbau ist auf Schäden an Achsen und Wellen infolge konstruktiv bedingter Kerben zurückzuführen (z.B. /N3/ und /Hai89/). Speziell im Bereich der hochbeanspruchten Profilwellen-Verbindungen kommt es auf Grund der starken Querschnittsveränderungen und der häufig angewandten Ausläufe und Formelemente, z. B. Zahn- und Keilwellen zu Kerbwirkungen, die erhebliche örtliche Spannungskonzentrationen sowohl im Zahnfußbereich und Zahnlückenauslauf als auch im Bereich der Verbindung selbst verursachen. Diese Beanspruchungskonzentrationen sind fast in der Hälfte aller Zahnwellenbrüche die häufigste Ursache für Dauerbrüche (Ermüdungs- bzw. Schwingungsbrüche) und für Schäden (bleibende Verformung, Anriss, Gewaltbruch) infolge Maximalbelastung. Hier trifft die Lastüberhöhung am Welle-Nabe-Verbindungsrand mit dem Steifigkeitssprung des Verzahnungsendes auf der Welle zusammen /Die93/. Die erwähnten Schadensfälle belegen, dass der heutige Kenntnisstand über eine beanspruchungsgerechte Auslegung von Zahnwellen noch recht lückenhaft ist. Deshalb sind neue Erkenntnisse über Form- bzw. Kerbwirkungszahlen bei Einzel- und Mehrfachkerben von scharf und weniger scharf gekerbten Zahnwellen mit Auslauf für eine treffsichere Festigkeitsberechnung erforderlich und stellen damit die Hauptschwerpunkte dieser Arbeit dar. Das vorliegende Forschungsprojekt, welches sich erstmals mit der Ermittlung der Beanspruchungen in torsions-, und biegebelasteten Zahnwellen mit freiem und gebundenem Auslauf befasst, wurde im Rahmen der Forschungsvereinigung für Antriebstechnik e.V. (FVA) unter der Nummer T 467 und dem Forschungsthema „ Ermittlung der Kerbwirkung bei Profilwellen für die praktische Getriebeberechnung von Zahnwellen“ initiiert und untersucht.
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Shen, Longjiang [Verfasser]. "Fretting and plain fatigue competition mechanism and prediction in spline shaft-hub connection / Longjiang Shen." Clausthal-Zellerfeld : Universitätsbibliothek Clausthal, 2012. http://d-nb.info/1021671967/34.
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Daryusi, Ali. "Beitrag zur Ermittlung der Kerbwirkung an Zahnwellen mit freiem und gebundenem Auslauf." Doctoral thesis, 2008. https://tud.qucosa.de/id/qucosa%3A23690.
Full textAbstract:
Durch die zunehmende technologische Entwicklung des Getriebe-, Gelenkwellen-, Werkzeugmaschinen-, Kraftfahrzeug-, sowie Landmaschinenbaus steigen die zu übertragenden Leistungen und Drehmomente enorm. Dies führt zu einem wachsenden Bedarf an formschlüssigen Profilwellenverbindungen und deren erhöhter Lebensdauer und Genauigkeit. Hierbei bilden die Zahnwellenverbindungen (ZWVen) mit Evolventenflanken nach DIN 5480 /N1/ den Regelfall für eine Vielzahl der Anwendung. Abhängig von Festigkeitsüberlegungen, Herstellungsverfahren und Platzbedarf treten in der Praxis nahezu ausschließlich die folgenden zwei Grundtypen auf. Es handelt sich dabei zum Ersten um die Zahnwelle (ZW) mit freiem Auslauf.Die zweite Geometrievariante ist die Zahnwelle mit gebundenem Auslauf, die eine nach DIN 471 /N2/ genormte Sicherungsringnut (SRN) enthalten kann. Zahnwellenverbindungen dienen zur Übertragung großer, wechselnder und stoßartiger Drehmomente ohne zusätzliches Verbindungselement durch die Profilierung der Welle und Nabe. Axiale Verschiebbarkeit unter Last, Profilverschiebungsmöglichkeit, einfache Montage und Demontage sowie die Herstellung mit hochleistungsfähigen umformenden und spanenden Massenfertigungsverfahren, die die Herstellungskosten verhältnismäßig niedrig halten, sind technisch bedeutsame Eigenschaften, die zum ansteigenden Einsatz von ZWVen führen (z.B. /N1/, /Vil84/, /Koh86/ und /Wes96/). Starke Kerbwirkung und erhebliche Überdimensionierung benachbarter Gestaltungszonen sind die wesentlichen Schwachpunkte der Profilverbindungen. Eine große Anzahl (ca. 80 %) von Ausfällen im Maschinenbau ist auf Schäden an Achsen und Wellen infolge konstruktiv bedingter Kerben zurückzuführen (z.B. /N3/ und /Hai89/). Speziell im Bereich der hochbeanspruchten Profilwellen-Verbindungen kommt es auf Grund der starken Querschnittsveränderungen und der häufig angewandten Ausläufe und Formelemente, z. B. Zahn- und Keilwellen zu Kerbwirkungen, die erhebliche örtliche Spannungskonzentrationen sowohl im Zahnfußbereich und Zahnlückenauslauf als auch im Bereich der Verbindung selbst verursachen. Diese Beanspruchungskonzentrationen sind fast in der Hälfte aller Zahnwellenbrüche die häufigste Ursache für Dauerbrüche (Ermüdungs- bzw. Schwingungsbrüche) und für Schäden (bleibende Verformung, Anriss, Gewaltbruch) infolge Maximalbelastung. Hier trifft die Lastüberhöhung am Welle-Nabe-Verbindungsrand mit dem Steifigkeitssprung des Verzahnungsendes auf der Welle zusammen /Die93/. Die erwähnten Schadensfälle belegen, dass der heutige Kenntnisstand über eine beanspruchungsgerechte Auslegung von Zahnwellen noch recht lückenhaft ist. Deshalb sind neue Erkenntnisse über Form- bzw. Kerbwirkungszahlen bei Einzel- und Mehrfachkerben von scharf und weniger scharf gekerbten Zahnwellen mit Auslauf für eine treffsichere Festigkeitsberechnung erforderlich und stellen damit die Hauptschwerpunkte dieser Arbeit dar. Das vorliegende Forschungsprojekt, welches sich erstmals mit der Ermittlung der Beanspruchungen in torsions-, und biegebelasteten Zahnwellen mit freiem und gebundenem Auslauf befasst, wurde im Rahmen der Forschungsvereinigung für Antriebstechnik e.V. (FVA) unter der Nummer T 467 und dem Forschungsthema „ Ermittlung der Kerbwirkung bei Profilwellen für die praktische Getriebeberechnung von Zahnwellen“ initiiert und untersucht.
Books on the topic "Splined shaft connections"
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McLean, David I. Noncontact lap splices in bridge column-shaft connections. [Olympia]: Washington State Dept. of Transportation, 1997.
Find full textConference papers on the topic "Splined shaft connections"
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Bhatta, Ravi, and Wendy Reffeor. "Comparison of Load Carrying Capacity of Three and Four Lobed Polygonal Shaft and Hub Connection for Constant Grinding Diameter." In ASME 2016 International Mechanical Engineering Congress and Exposition. American Society of Mechanical Engineers, 2016. http://dx.doi.org/10.1115/imece2016-65745.
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Polygonal shafts are used in power transmission as alternatives to keyed and splined shafts. They are designed using DIN standards. This research explores the loading strength of the standardized three lobed (P3G) and four lobed (P4C) polygonal shafts and hubs manufactured from the same stock size, subjected to torsional bending load at various fits. Due to complex conformal contact (nonlinear model) between the shaft and the hub, there is no analytical solution and, therefore, Finite Element Method had been used to determine the stresses, after validating experimentally and using the DIN standard. From the analysis, it was found that the hub experienced greater stress than the shaft in all cases and the major stress in a polygonal shaft and hub connection is the contact stress. The clearance fit was found to be the most detrimental fit and the interference fit to be the most suitable for larger power transmission. Owing to its small normal axial stress and hub displacement, the P4C clearance fit has its use in low power transmission where a sliding fit is a requirement. The maximum von Mises stress was located below the surface for P4C and P3G clearance fit, suggesting failure from pitting and fretting on these shafts. All of the stresses were found to be higher in P4C than P3G for similar loading. Therefore, for general use, the P3G profile with an interference fit is recommended.
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Bhandari, Ayush. "Vallée Poussin kernels, shift-invariant subspaces and the spline connection." In 2017 International Conference on Sampling Theory and Applications (SampTA). IEEE, 2017. http://dx.doi.org/10.1109/sampta.2017.8024438.
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Hong, Jie, Meng Chen, Yanhong Ma, and Liming Zhang. "Rotordynamic Analysis Method of Small Turbo-Fan Engine Based on Finite Element Models." In ASME Turbo Expo 2010: Power for Land, Sea, and Air. ASMEDC, 2010. http://dx.doi.org/10.1115/gt2010-22565.
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Small size, light weight and high speed are remarkable characteristics of modern small aero-engines. The rotor components of engine are always series connected by spline joints or face tooth joints, so dynamic interaction of different rotor components have to be taken into account in aero-engine vibration analysis. Firstly, a modal analysis of the integral series connected rotor is performed as well as the analysis of each rotor components including fan rotor, compressor rotor and turbo rotor. The result captures the effects of the rotor components on the integral rotor, the modes of the integral rotor are composed of the modes of the rotor components and the coupled modes of them. Secondly, one special characteristic of this rotor is that No.3, 4, and 5 compressor disks and compressor shaft is interference connected initially. Based on calculation of connecting state, two models of the compressor rotor are presented, including a model with connecting state effects and a general model without connecting state effects, and a rotordynamic analysis is performed with the two models. The effect of the connecting state between shaft and disks of compressor rotor on rotordynamics is captured, as well as the true critical speeds and vibration modes. Thirdly, due to different assembly state and variable mechanical force, typical parameters which affect rotordynamics directly, such as rotor support stiffness and joints structure stiffness are not constant. A sensitivity analysis of critical speeds and vibration modes with respect to typical parameters (joints structure stiffness) is performed with finite difference method, two approaches are carried out, including relative sensitivity analysis and absolute sensitivity analysis. The effect of the parameters on rotordynamics is captured, as well as the variation range of critical speed. Finally, the analysis of test data validates the author’s method.
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Sim, Kyuho, Jin Woo Song, Yong-Bok Lee, and Tae Ho Kim. "Thermal Performance of a Bump Type Gas Foil Bearing Floating on a Hollow Shaft for Increasing Rotating Speed and Static Load." In ASME 2011 Turbo Expo: Turbine Technical Conference and Exposition. ASMEDC, 2011. http://dx.doi.org/10.1115/gt2011-46499.
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Identifying thermal characteristics of gas foil bearings (GFBs) provides an insight for successful implementation into high speed oil-free turbomachinery. The paper presents temperature measurements of a bump type GFB floating on a hollow shaft for various operating conditions. Two angular ball bearings support the hollow shaft at one end (right), and the other end (left) is free. Test GFB has the outer diameter of 100 mm and the axial length of 45 mm, and the hollow shaft has the outer and inner diameters of 60 mm and 40 mm, respectively. An electric motor drives the hollow shaft using a spline coupling connection. A mechanical loading device provides static loads on test GFB upward via a metal wire, and a strain gauge type load cell placed in the middle of the wire indicates the applied loads. During experiments for shaft speeds of 5 krpm, 10 krpm, and 15 krpm and with static loads of 58.86 N (6 kgf), 78.48 N (8 kgf), and 98.1 N (10 kgf), twelve thermocouples measure the outer surface temperatures of test GFB at four angular locations of 45 deg, 135 deg, 215 deg, and 315 deg, with an origin at the top foil free end, and three axial locations of bearing centerline and both side edges at each angle. Two infrared thermometers measure the outer surface temperature of the hollow shaft at free and supported ends close to test GFB. Test results show that GFB temperatures increase as the shaft speed increases and as the static load increases, with higher temperatures in the loading zone (135 deg and 215 deg) than those in the unloading zone (45 deg and 315 deg). In general, the recorded temperatures are highest at 225 deg where a highest hydrodynamic pressure is expected to build up. Measured temperatures at the bearing centerline are higher than those at the side edges, as expected. In addition, large thermal gradients are recorded in the hollow shaft along the axial direction with higher temperatures at the supported end. Angular ball bearings and lip seal supporting the hollow shaft might produce significant heat generation due to mechanical contact as the shaft speed increases. The axial thermal gradient of the shaft is thought to cause higher temperatures at the bearing right edge facing the ball bearing support than those at the left edge. The present test data along with detailed test GFB/shaft geometries and material properties benchmark thermohydrodynamic (THD) model predictions of test GFB with a rotating hollow shaft.
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Strehlau, Ulrik, and Arnold Ku¨hhorn. "Experimental and Numerical Investigations of HPC Blisks With a Focus on Travelling Waves." In ASME Turbo Expo 2010: Power for Land, Sea, and Air. ASMEDC, 2010. http://dx.doi.org/10.1115/gt2010-22463.
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The motivation for the usage and a further development of blade integrated disk (blisk) technology is driven by a rising demand for efficient, economical and environment-friendly aero engines. In contrast to conventional bladed disks with separated blade and disk design, blisks are either manufactured from solid or disk and blades are assembled by friction welding. Due to an optimized stress distribution, the integrated design leads to potentially higher maximum rotational speeds of the HP-shaft and thus to an improved pressure ratio. This fact offers the opportunity to reduce the number of blades or even to save whole compressor stages. In order that a significant mass-reduction is achieved, which is increased since heavy blade-disk connections of the conventional design are not necessary anymore. Apart from the advantages of the integrated design, the vibration behaviour of a real blisk is more sophisticated compared to the conventional bladed disk design. Due to the very low mechanical damping, effects like mode-localization and amplitude magnification can lead to high cycle fatigue problems of such complex structures. Extensive experimental and numerical investigations are carried out considering a real rotor-stage 1 blisk of the Rolls-Royce E3E/1 demonstrator-HPC. In order to identify “blade individual frequencies” and “blade individual damping”- values, a new patented blade by blade measurement method is used, that provides FRFs characterized by an unique resonance, as known from SDOF-systems. Based on the adjusted FE-model, numerical and experimental investigations of the vibration behaviour in the frequency range of splitted double eigenvalues are carried out. In doing so the expressions “travelling wave” and “standing waves” are commonly used to characterize the eigenmodes and forced modes of vibration respectively. The splitting of eigenvalues could be proved and a novel criterion to distinguish travelling and standing waves is introduced.