I. Allgemeine Angaben II. Angaben zum Promotionsthema

Transcription

I.
Allgemeine Angaben
DAAD Programm:
„International Promovieren in Deutschland (IPID)“
Programmlinie 2: Bi-nationale Promotionsnetzwerke
Kurzbezeichnung
des Vorhabens:
Deutsch-Ukrainisches Promotionsprogramm (DUPro)
Beteiligte Partner:
Deutschland:
Otto-von-Guericke-Universität Magdeburg
1. Fakultät für Elektrotechnik und Informationstechnik
2. Fakultät für Maschinenbau
Ukraine
1. Nationale Technische Universität Kiew (NTU Kiew)
2. Nationale Technische Universität Donezk (DonNTU)
3. Nationale Technische Universität Kharkiv (NTU Kharkiv)
Dauer der Förderung:
II.
Beginn:
Ende:
Mai 2011
Dezember 2013
Angaben zum Promotionsthema:
Thema der Promotion:
Diagnostics of assembling errors in high-precision spindle units on
rolling bearings
Beteiligte Partner
Deutschland:
Fakultät für Maschinenbau
Lehrstuhl Technische Dynamik
Ukraine:
Nationale Technische Universität Kiew (NTU Kiew)
Fakultät für Mechanik und Maschinenbau
Lehrstuhl Angewandte Mechanik
Doktorand
Andriy Petryshin
Betreuer
Deutschland:
Prof. Dr. -Ing. habil. Jens Strackeljan
Ukraine:
Prof. Dr.-Ing. habil Yurii Danylchenko
Beginn:
11/2011
Ende:
11/2013
Dauer der Promotion
Zwischenbericht 2012 Petryshin
Ziel der Arbeit:
The objective of the project is the research of factors having impact on the quality of static and
dynamic characteristics of spindle unit elastic systems in order to decrease their vibrations.
Wissenschaftliche Aktualität:
One of the most effective methods of technical condition estimation of the spindle units on rolling
bearings is considered to be vibration diagnostic. Advantage of this method is highly determined
frequencies structures of mechanical vibrations, which appears due to inner vibration disturbances of
kinematic nature. The sources of these disturbances are bearings. Basing on this, and collecting data
about current values of static and dynamic characteristics of spindle unit elastic system it is possible to
identify assembly errors on the stage of its manufacturing.
Main idea of this method is using internal disturbances sources and dynamical properties of spindle
units to estimate quality of the assembly and rotating errors of spindle units in its operating range of
rotational frequencies. Method is basing on measuring of forced vibration amplitudes, that are caused
by manufacturing and assembling errors of the bearings in spindle unit supports, on spindle unit local
resonance frequencies.
Arbeitsplan
In the frame of the project the following problems will be solved:
1) Analysis of the methods of assembling errors diagnostic in high-precision spindle units on rolling
bearings.
1.1) Analysis of well-known vibration diagnostic methods of rolling bearings.
1.2) Analysis of well-known vibration diagnostic methods of spindle units on rolling bearings.
1.3) Theoretical foundation of rolling bearings and spindle units vibration researches.
1.4) Aim and goals of research.
2) Theoretical validation of the diagnostic method.
2.1)
Processing and comparing experimental results with results that were obtained from
test rig mathematical model.
2.2)
Mathematical modeling of “spindle unit” system vibration.
2.3)
Validation of test rig design.
3) Experimental research of the “spindle unit” system vibration.
3.1)
Method of research.
3.2)
Results of research.
4) Practical application of research results.
Zwischenbericht zum Promotionsthema
Stand Dezember 2012
Test rig description. In order to research dynamical behavior of the spindle system with assembling
errors, in NTUU “KPI” a test rig (Fig. 1) has been upgraded and assembled. Spindle system on test rig
has been considered as complex mechanical vibration system, which consists of 4 subsystems: work
piece/tool, spindle and quill, mounted on frame construction with elastic supports and spring/beam for
setting and varying system stiffness. All system is mounted on the foundation. The mathematical
model has been developed and validated within the scope of an investigation at university Magdeburg
during summer staying.
Figure 1. Test rig
During that stay in Otto-von-Guericke-University a number of experiments has been performed on test
rig for the purpose of developed mathematical model approbation.
On the rotor research rig with changeable concentrated masses, experimental research of natural
frequencies varying, depending on number and position of concentrated masses, was performed. The
same research was performed on test rig mathematical model, which was created using theoretical
principles and computational algorithms of spindle unit mathematical model basing on method of initial
parameters and method of dynamical compliances.
Comparison of experimental and theoretical results shows sufficiently high level of their correlation
(Table. 1), which confirms possibility of developed spindle unit mathematical model usage in research
purposes of rotor systems dynamical behavior.
Table №1. Definition of natural frequencies of rotor systems
Scheme №
1-
2-
3-
4-
Experimental results,
Results of calculation,
Hz
Hz
р1=28
р1=28.8
р2=57
р2=59.3
р1=17
р1=17.6
р2=170
р2=173.9
р1=14.5
р1=14.57
р2=56
р2=56.3
р1=13.3
р1=13.4
р2=72
р2=77
Current state of the work. The general analytical model of the test rig is shown in Fig. 2.
All subsystems are connected with each other by joints with elastic-dissipative properties (bearings,
interfacial joints). This model takes into account subsystem’s distributed mass; concentrated masses;
angular, radial stiffness and damping properties of supports, disturbing forces applied in various
system points, including internal bearing disturbances due to inaccuracies of fabrication. Each
subsystem is divided on number of sections that is necessary for its accurate description.
At present numerous measurements on test rig in Ukraine has been performed in order to track
vibration spectrum formation depending on system kitting. Significant influence of design, system
kitting, mounting conditions and operating regimes on natural frequencies array forming was
established, which shows necessity of their complex consideration during spindle unit construction and
choosing its operating modes. Also, analysis of mode shapes of the overall system shows potential to
evaluate not only dynamical quality of machine design, but also subsystems interaction results.
Figure 2. General analytic model
Experimental data (Fig. 3)
Each of pointed peaks can be explained by mathematical model and correspond to certain subsystem
natural frequency, which was calculated by using this model. Complete understanding of the nature of
vibration spectrum forming and its changing due to system kitting, mounting and other factors,
mentioned above, is still in process and requires further research, which is confirmed by comparing
experimental data and one, obtained by calculation. They are correlating pretty well, but require more
detailed system joint’s parameters definition in order to increase accuracy of calculation.
Figure 3. Experimental data obtained on test rig

I. Allgemeine Angaben II. Angaben zum Promotionsthema

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