ACTA TECHNICA CORVINIENSIS – Bulletin of EngineeringWorms are loaded with axial force on the pressure orbuckling. It depends on the ratio of worm length andits diameter. It is therefore necessary to calculate theslenderness ratio (λ).Figure 2. Diagram of a simple worm [7]Figure 1 shows a diagram of a simple worm, wherethey are displayed basic geometric parameters too.Total volume of material transported by worm can becalculated from the basic relationship [4]:β ΔPQ = α.n− ⋅η Lwhere:Q – total volume of the worm material per unit time[mm 3 .s ‐1 ],n – rotational speed [s ‐1 ],∆P – pressure gradient in the direction of the wormaxis [MPa],η – viscosity of the polymer [kg.m ‐1 .s ‐1 ],D – worm diameter [mm]STRENGTH CALCULATION OF SIMPLE WORM EXTRUDERSWorms are much stressed functional parts of theworm extruders. They are stored in the bearings,which allow rotational movement of the worm andcapture the axial and radial forces. [3] [7]Figure 3. Load a single wormThe sizes of forces acting on the bearings arecalculated from the following relations:2DFA= π ⋅ p ;4qLFB = 2b;qLF C = ( 1 + 2b)2bwhere:D – worm diameter [mm],p – pressure at the end of the worm [MPa],q – continuous load [N.mm ‐1 ]2L λ = 0iwhere:λ – slenderness ratio [‐],L 0 – reduced length [mm],i – radius of inertia [mm]Worms whose slenderness ratio exceeds 50 (λ> 50)are strained to the bar and worm whose slendernessratio is less than 50 (λ> 50) are stressed by thepressure. When stress is calculated on the pressurereduced stress (σ r ), which must be less than theallowed voltage (σ D ). [6] [7]2max2maxσ r = σ + 4τ≤σDF MσOmax = σ + σ O = + ;S WOMKmaxτ max =Wwhere:σ r – reduced stress [MPa],σ max – maximum normal stress [MPa],τ max – maximum tangential stress [MPa],σ D – maximum possible stress [MPa],F – axial force applied to the worm [N],S – Cross‐section worm [mm 2 ],M O – bending moment [N.mm],W O – selectional module for bend [mm 3 ],M Kmax – maximum torque [N.mm],W K – sectional module for torsion [mm 3 ]The maximum deflection at the end of the worm iscalculated from the relationship:4qLy max = ;8EJ44πD⎡ ⎛ d ⎞ ⎤J = ⎢1− ⎜ ⎟ ⎥64 ⎢⎣⎝ 4 ⎠ ⎥⎦where:y max – maximum deflection [mm],q – continuous load [N.mm ‐1 ],L – worm length [mm],E – Modulus of elasticity [MPa],J – moment of inertia of the cross section of the worm[mm 4 ],D – maximum diameter of the worm [mm],d – minimum diameter of the worm [mm]For reliable operation of these machines is alsoimportant to twist the worm. Twisting the wormshould not exceed 1.5 to 3° degrees [7]. For the truesize of the torsion:K1082012. Fascicule 3 [July–September]
ACTA TECHNICA CORVINIENSIS – Bulletin of Engineering° MKL180ϕ max = ⋅ ≤ϕDGJ πwhere:φ ° max – maximum tortion [°],M K – torque [N.mm ‐1 ],L – worm length [mm],G – modulus of elasticity [MPa],φ D – the maximum possible tortion[°]CONCLUSIONSDesign and calculation of components of themachinery is a creative activity using theoretical andpractical experience. This activity must be gearedmainly to meet the requirements. At present, virtuallyall areas of design activities supported by computertechnology that can be effectively used in the designof machinery components particularly in theconstruction of technical documentation and fieldstrength calculations.REFERENCES[1.] Gašpár, Š.: Implementácia programu AutodeskInventor 2009 pri riešení rovinne zaťažených, statickyurčitých priamych konštrukcií. ERIN 2009: 3. ročníkmedzinárodní konference, Ostrava, VŠB‐TU, 2009,ISBN 978‐80‐248‐1982‐2[2.] Batešková, E. – Maščenik, J. – Haľko, J. – Gašpár, Š:Device for measurement of clamped joints frictiontorque. In: Technological Developments inNetworking, Education and Automation. ‐ Dordrecht:Springer, 2010, p. 417 – 419, ISBN 978‐90‐481‐9150‐5[3.] Horvát, T. – Pavlenko, S. – Palko, A.: Použitieprogramu Autodesk Inventor pri vytváraní adimenzovaní hriadeľov, 2010. In: Vzdelávanie učiteľovstredných odborných škôl v nových európskychnormách : zborník referátov informačno‐tématickéhoseminára : 21. október 2010, Prešov FVT TU, s. 110‐114.,ISBN 978‐80‐553‐0549‐3[4.] Liptáková, T. – Alexy, P. – Gondár, E. – Khunová, V.:Polymérne technické materiály, ŽU Žilina, 2009, 182 s.[5.] Maščenik, J. – Haľko, J.: Proposal and calculation ofworm gear with PC upport /Návrh a výpočet závitovkys podporou PC /, In: ERIN 2009. ‐ Ostrava : VŠB‐TU, ‐ISBN 9788024819822[6.] Pavlenko, S. – Haľko, J. – Maščenik, J. – Nováková,M.:Navrhovanie súčastí strojov s podporou PC, 1. vyd.– Prešov : FVT TU, 2008, 347 s.,ISBN 978‐80‐553‐0166‐2[7.] Ragan, E. a kol.: Vstrekovanie plastických hmôt, FVTTU Prešov, 2008, 548 s., ISBN 978‐80‐553‐0102‐0ACTA TECHNICA CORVINIENSIS – BULLETIN of ENGINEERINGACTA TECHNICA CORVINIENSIS – BULLETIN of ENGINEERINGISSN: 2067‐3809 [CD‐Rom, online]ISSN: 2067‐3809 [CD‐Rom, online]copyright © UNIVERSITY POLITEHNICA TIMISOARA,FACULTY OF ENGINEERING HUNEDOARA,5, REVOLUTIEI, 331128, HUNEDOARA, ROMANIAhttp://acta.fih.upt.ro2012. Fascicule 3 [July–September] 109
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Regional Editors from MALAYSIAAbdel
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Imre TIMÁRUniversity of Pannonia,
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Ioan MILOŞANTransilvania Universit
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REFERENCES[1.] Bhavyesh Divecha, Aj
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compressor, the now hot and highly
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Figure 7. Pressure ratio of evapora
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Physical data model (MFD) is obtain
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The new project which now includes
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Figure 3. Materials evolutionThe pr
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