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The analysis of influence of parameters of chain transfer on change of force of deformation of the elastic element...
Djuraev Anvar Djuraevich, technical sciences associate, professor, Tashkent institute of textile and light industry, Republic of Uzbekistan.
E-mail: [email protected]
Tyrdalieyv Vohidjon Maxsudovich, candidate for technical sciences, Tashkent institute of textile and light industry E-mail: [email protected]
Qosimov Azamjon Adixamjonovich, senior scientific employee-researcher, Namangan Engineering Pedagogical Institute, Republic of Uzbekistan
The analysis of influence of parameters of chain transfer on change of force of deformation of the elastic element of the compound conducted asterisk
Abstract: In article the technique of definition and calculations of deforming force and factor of rigidity of an elastic element of a compound conducted asterisk of chain transfer is resulted. Results of the analysis of the constructed graphic dependences of change deforming forces of the elastic plug of a conducted asterisk of chain transfer are resulted. Necessary parameters of system are proved.
Keywords: Chain transfer, asterisk, the elastic element, deforming force, rigidity factor, angular speed, weight, radius, tension roller, resource.
It is necessary to take into consideration the factor of deformation of flexible element when interconnection of gear with chain transmission. In figure-1 the impact of tension roller and scheme of bearing gear us shown. When chain 2 is co-worked with
gear 1 the following forces are generated [1]: tension forces F1 and F2, chain 2 and trailing gear 1 generalized force Qi. The system to be in balance:
F + F2'+AF2 + Fv + QC = 0. (1)
Fig. 1. Scheme of chain transmission trailing gear, where 1-component trailing gear, 2-chain, 3-tension roller
If we take tension forces of general horizontal axis organizer: Ft cos£ = Ficosae - (F2' + AF2)cos0, (2)
where, ^,ae,6 - angles, generated by horizontal axis vectors.
If we define chain weight as q, tension force of AB length is calculated taking into consideration [1; 2]: cos a,
F = F
1 cos§
/
( + r3 )ag
V
n a O2E1
—+ 0 -arccos——-
2 O,O,
+ AF
cos
(3).
In general chain connected with trailing gear, as per projection center escape affecting forces:
F = m2®2 r2
cos£
a I I a cos I a2, +1 + cos I a22 +— | +
a I I a
+cos I a 3 + 1 + ...cos I a2i
(4)
In the condition shown above we will determine flexible element deformation force:
F cos a
Qc =-m2a2r2
cos I +a
cos
(r + r3 )Ctg
f.
—+ 6 — arccos
2
OA
O2O3
-AF
cos6
(5)
cos E,v
Hardness coefficient of flexible element of trailing gear is determined by the following expression:
F cosa2
C= -1 "
cos I a+a
(r2+r3 )Ctg
cos
" a OE
—+ 6 - arccos—
V 2 O2O3
f
-AF
cos 6
cos
(6)
where, SA -is distance shift of gears of flexible element.
Section 7. Technical sciences
Thus it is recommended to determine distance between gear axis: A = t3 • n3/cosas-8A, (7)
where, t3 - is the step of between teeth of gean; n3 - number of sections in the branch of trailing gear.
To get solutions as per expressions (5), (6), (7) the calculation parameters are taken in the following values:
t3 = 15.0 -21.0 mm.; nl = 200 - 400min.-1;[P] = 28 -31MPa; n = 938, z1 = 22, Z2 = 25; r2 = (5.5 - 6.5) • 10 2 m; m2 = 0.015 * 0.035kg.
In the fig. 2a the chain transmission trailing gear deformation force is shown in values generated in additional tension. The obtained diagram connections show that the increase of angle speed brings to nonlinear decrease. The tension belt working in transmission brings to increase Q force. When additional tension force increases from 60 H. to i05 H. and the difference between force is = 18c 1 and when 4.15 • 102H is generated by it is generated pro ratio.
The main reason for it is the tension rolling influence in rotating frequency is not high, i. e. in this the momentum role is increased. It is necessary to state that the force which deforms flexible element by increasing radius of gear. We can see it the diagram already reviewed before. This law can be explained as follows. When the branches of chain the more its momentum force i. e. it decreases deformation force of flexible element. However, the long term operation of transmission is affected by deformation of flexible element. The deformation around axis of chain transmission with trailing element to be avoided from increase 2.0 V 3.0 mm when radius of gear is r2 = (5.5^6.5)-10 2m it is good select (3.2 ^ 5.4) -105 N / m . It is necessary to state that trailing gear shaft is working body connected with plug drum. Resistance fluctuation is decreased significantly at the expense of flexible element. I. e. vibration coming from clay brick to chain come with decreased force.
1 - AF? = 105N;2 - AF? = 80N; 3 - AF? = 60N
1 -m2 = 0.015kg; 2 - m2 = 0.025kg; 3 - m2 = 0.036kg.
Fig. 2. a - Diagram of chain transmission connected with angle speed; b - diagram bound with change of radius force and deformation of flexible element
References:
Glushenko I. P., Semenov, Lysenko. About determining of minimum tension of chain loose side of chain transmission//Mechanical transmissions. - Tr. Kubanskiy institute, 1976. - P. 31-37.
Gotovtsev A. A. Chain transmissions and chain equipment elements/A. A. Gotovtsev, G. B. Stoblin//Machine parts. Calculation and construction: Reference book T. A./under edition N. S. Acherkana. - M.: 1969. - P. 279-345.
Khakimov Zafar,
Vice rector of the Tashkent University of Information Technologies,
Ph. DDoctor of Philosophy E-mail: [email protected]
Research and application of acousto-optical tunable filters for modern telecommunications systems
Abstract: In article are considered integrated acousto-optical tunable filters, the analysis of possibility of adjustment of the surface acoustic wave is carried out and acousto optical conversion of modes on their basis, integration of optical technologies also is inspected.
Keywords: Acoustic waves, Electro-optical tunable filter (EOTF), Acusto-optic tunable filter (AOTF), Optical and Acoustic beam, interdigital transducer (IDT).
The idea of acousto-optical tunable filters (AOTF) was pro- are inspected according to them, the surface acoustic wave and
posed in 1969 by Harris and Wallace [1] and was demonstrated by acousto-optical mode conversion is analyzed as well as the inte-
Harris and his colleagues. The flat (planar) integrated elements of grated optical technology is considered.
acousto-optics, including filters, frequency switchers and modula- The processes involved in the work AOTF are quite com-
tors have been discussed in [2]. In this paper, the integrated AOTF plex. The piezoelectric wave linked to a surface acoustic wave can
