The design computation result of drive of flute profile catenary
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Big sprocket of Z1=17 of number of 53 chainlet teeth of a cogwheel counts Z2=43 catenary number: C095, pitch P=15.
875mm chainlet teeth of a cogwheel counts coefficient Kz= .
N2=395 of rotate speed of 77 large chain wheel.
P0= of 35r/min rated power.
27kw/mm guides a form: Guide inside 2.
Catenary drive computation designs power PdPd=KA.
P/KzPd=7.
Pd/P0b ≥ of ≥ of Bb of 79kw chain width 28.
86 recommend B=34.
50mm chain division counts LL=LppL=2 of LpLp=2aop+(z1+z2)/2+c/aopLp=144 chain length, 286.
MM=L of 00mm chain quality.
QM=4, 663.
44kg, q=2.
Aa=p(2Lp-z1-z2)Kaa=902 of span of 04kg/mm academic axis.
A=(0 of △ of A; of △ of Aa=a- of span of 48mm actual axis.
002 ~ 0.
004)aa=899.
Vv=z1n1p/60000v=4 of 77mm linear velocity of chain.
50m/s is effective and circumferential force FF=1000P/vF=1, 333.
95N action is in the ≈ of QF of tensile QF level on the axis (1.
15 ~ 1.
≈ of 20)KAF; perpendicular QF 1.
05KAFQF=1, 560.
72N (level) Or 1, 400.
65N(is perpendicular) 3.
Chain wheel is main π of Dd=p/sin(of diameter of reference circle of dimension chain wheel / Z)d1=86.
39mm;d2=217.
48mm sprocket spends π of round diameter Dada=p/tg(/ Z)da1=84.
92mm;da2=216.
Dfdf=p(1 of round diameter of 90mm sprocket root.
296328+(ctg(π / Z)-1.
26)2)1/2df1=67.
39mm;df2=197.
Contact of 72mm little chain wheel stops round diameter Djdj=p(1.
515213+(ctg(π / Z)-1.
1)2)1/2dj1=70.
23mm;dj2=200.
° of =60 of α of α of horn of 39mm tooth nail - ° of 30 α =60 - ° of =360 of φ of φ of 30 graduation horn / Z φ 1=21.
2=8 of φ of 176 ° ; .
° of =30 of β of β of 372 ° alveolar horn - 180 ° / Z β 1=19.
2=25 of β of 412 ° ; .
Rdrd=0 of round radius of fixed position of root of 814 ° tine.
375prd=5.
95mm nadir is apart from Hh=0 to pitch line.
55ph=8.
Clearance of 73mm tine root (H direction) Ee=0.
08pe=1.
27mm guides a thick δ , guide =1 of δ of δ of groovy wide Aa=2.
5mm, a=3mm chain wheel is wide BB=b-3 δ (outside guide) ; B=b+2 δ (inside guide) outside B=30mm, b=37.
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