PROJEKTOWANIE PRZEKŁADNI PASOWEJ |
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Z PASAMI KLINOWYMI |
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1. Dane wejściowe |
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400 |
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560 |
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710 |
800 |
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1120 |
1250 |
1400 |
1600 |
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2240 |
2500 |
2800 |
3150 |
3550 |
4000 |
4500 |
5000 |
5600 |
6300 |
7100 |
8000 |
9000 |
10000 |
11200 |
12500 |
14000 |
16000 |
18000 |
Moc przenoszona przez przekładnię N [kW] |
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Tu wpisz swoje dane
0 |
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Prędkość obrotowa koła napędzającego n1 [obr/min] |
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Tu wpisz swoje dane
0 |
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Przełożenie przekładni i (geometryczne) |
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Tu wpisz swoje dane
0 |
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63 |
71 |
80 |
90 |
100 |
112 |
125 |
140 |
160 |
180 |
200 |
224 |
250 |
280 |
315 |
355 |
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450 |
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560 |
630 |
710 |
800 |
900 |
1000 |
1120 |
1250 |
1400 |
1600 |
1800 |
2000 |
2240 |
2500 |
Rozstaw osi kół a [mm] (przyjęte) |
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Wpisz przewidywany rozstaw osi kół
0 |
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#DIV/0! |
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2. Warunki pracy urządzeń napędzających |
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#DIV/0! |
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Rozstaw osi kół a [mm] (obliczone) |
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Oblicza rzeczywisty rozstaw osi kół dla podanego przypadku
#DIV/0! |
Uwaga: |
#DIV/0! |
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Średnica skuteczna koła czynnego dp1 [mm] |
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Dobrać z tablicy 3.7
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0,55 |
0,83 |
0,95 |
1,05 |
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Współczynnik zależny od przełożenia Ci |
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Dobiera się automatycznie na podstawie danych z tablicy 3.12
dla przełożenia rzeczywistego MNIEJSZEGO od 1,06
#DIV/0! |
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#DIV/0! |
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Przełożenie przekładni irz |
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Obliczone rzeczywiste przełożenie przekładni dla wybranych średnic
#DIV/0! |
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Błąd przełożenia w % |
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Błąd wartości przełożenia rzeczywistego
Im mniejszy tym lepiej !!
Powyżej 9% zmienić rozmiar małego koła!!
#DIV/0! |
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3. Dobór typu pasa klinowego na podstawie średnicy zrównoważonej |
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Średnica równoważona De [mm] |
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Średnica skuteczna zostanie sama obliczona i jest podstawą do określenia typu pasa
#DIV/0! |
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Typ (wielkość) pasa klinowego |
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Należy wybrać jaki typ pasa będziemy stosowali.
Typ Z, A, B, C, D lub E
B |
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4.Obliczone wymiary przekładni pasowej |
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Średnica skuteczna koła biernego dp2 [mm] |
Kąt g [o] |
Kąt opasania a [o] |
Długość pasa teoretyczna L [mm] |
Długość pasa znormali-zowana Lp [mm] |
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Obliczona średnica skuteczna napędzanego koła
#DIV/0! |
#DIV/0! |
Kąt opasania powinien mieścić się w granicach od 70 do 180 stopni.
#DIV/0! |
Obliczona długość pasa
#DIV/0! |
Na podstawie długości obliczonej automatycznie dobierana jest zalecana długość znormalizowana z tablicy 3.6
#DIV/0! |
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Średnica skuteczna koła biernego dp2 [mm] |
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Na podstawie średnicy obliczonej automatycznie dobierana jest średnica znormalizowana z tablicy 3.7
#DIV/0! |
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#DIV/0! |
Uwaga: |
#DIV/0! |
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6. Obliczenie liczby pasów do przeniesienia założonej mocy |
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Dobór współczynnika żywotności pasa CL |
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Dobrać z tablicy 3.10 dla Lp
0 |
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Współczynnik uwzgl. warunki pracy Ct |
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Dobrać z tablicy 3.9
0 |
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Dobór współczynnika kąta opasania Ca |
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Dla wyliczonego kąta a dobór automatyczny na podstawie danych z tablicy 3.11
#DIV/0! |
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Moc przenoszona przez jeden pas N1 [kW] |
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Na podstawie wyliczonej prędkości V i średnicy równoważnej De dobieramy z tablicy 3.8 wartość
0 |
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Obliczona liczba pasów j |
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UWAGA!!!!
w praktyce przyjmuje się liczbę pasów z=1-5 (maksymalnie 8); im większa liczba pasów tym wymagany mniejszy przekrój pojedynczego paska-tym większa zwartość przekładni-mniejszy rozstaw kół; im większa ilość pasów tym większe prawdopodobieństwo nierównomiernego przenoszenia obciążenia tym większe prawdopodobieństwo uszkodzenia przekładni.
#DIV/0! |
Uwaga: |
#DIV/0! |
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Prędkość obwodowa pasa u [m/s] |
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0,00 |
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#DIV/0! |
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7. Oznaczenia i wymiary zaprojektowanych pasów klinowych oraz kół rowkowych |
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#DIV/0! |
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Liczba pasów
#DIV/0! |
Typ (wielkość) pasa
B |
Długość pasa
#DIV/0! |
PN-86/M-85200/06 |
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WIENIEC ROWKOWY 1 |
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Koła czynnego
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Liczba rowków
#DIV/0! |
B |
Średnica skuteczna
0 |
PN-66/M-85202 |
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WIENIEC ROWKOWY 2 |
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Koła biernego
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#DIV/0! |
B |
#DIV/0! |
PN-66/M-85202 |
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#DIV/0! |
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8. Obliczenie szerokości koła |
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Współczynnik e |
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Dobrać z tablicy 3.7 dla odpowiedniego typu pasa
19 |
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Współczynnik f |
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Dobrać z tablicy 3.7 dla odpowiedniego typu pasa
12,5 |
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Szerokość wieńca koła rowkowego B [mm] |
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#DIV/0! |
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9. Obliczenie siły cięgna |
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Siła użyteczna Su [N] |
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#DIV/0! |
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Kąt rozwarcia rowka na kole a [o] |
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Kąt ten przyjmuje wartość 34, 36, 38 stopni według tabeli 3.7
34 |
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Pozorny współczynnik tarcia m' |
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0,684 |
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Siła bierna Sb [N] |
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#DIV/0! |
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Siła czynna Sc [N] |
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#DIV/0! |
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Siła wypadkowa Q [N] |
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#DIV/0! |
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10. Sprawdzenie warunków wytrzymałościowych przekładni |
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Prędkość obrotowa n2 [obr/min] |
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#DIV/0! |
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Prędkość kątowa w2 [rad/s] |
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#DIV/0! |
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Moment skręcający Ms [Nmm] |
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#DIV/0! |
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Odległość między łożyskiem a środkiem koła l [mm] |
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Przyjęta wartość to 70 [mm]
Jeśli ktoś ma ochotę może wybrać własny rozstaw
0 |
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Moment gnący Mg [Nmm] |
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#DIV/0! |
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Moment zastępczy Mz1 [Nmm] |
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#DIV/0! |
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Średnica wałka dw1 [mm] dla I przypadku |
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Średnica wałka pod kołem przekładni
#DIV/0! |
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Wg [mm3] |
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#DIV/0! |
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Naprężenie d [N/mm2] |
<= |
Dopuszczalna wartość naprężenia kg [N/mm2] |
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#DIV/0! |
#DIV/0! |
60 |
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#DIV/0! |
Uwaga: |
#DIV/0! |
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Ws [mm3] |
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#DIV/0! |
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Naprężenie t [N/mm2] |
<= |
Dopuszczalna wartość naprężenia ks [N/mm2] |
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#DIV/0! |
#DIV/0! |
40 |
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#DIV/0! |
Uwaga: |
#DIV/0! |
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Średnica wałka dw2 [mm] dla II przypadku |
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Średnica wałka pod łożyskiem
#DIV/0! |
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Przyjęta średnica wałka dw1 [mm] |
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Dobór średnicy na podstawie wyników obliczeń
0 |
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Przyjęta średnica wałka dw2 [mm] |
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Dobór średnicy na podstawie wyników obliczeń
0 |
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11. Dobór łożysk |
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Zastępcze obciążenie dynamiczne łożyska P [N] |
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#DIV/0! |
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Czas pracy łożyska T [h] |
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Dobrać na podstawie tabeli 2.2
(ta na samym dole w arkuszu Tabele)
0 |
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Trwałość łożyska Lh [mln obr] |
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#DIV/0! |
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Nośność dynamiczna łożyska C [N] |
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#DIV/0! |
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Współczynnik potęgowy q |
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Dla łożysk kulkowych q=3
Dla łożysk wałeczkowych i igiełkowych q=4
3 |
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Trwałość łożyska L [mln obr] (liczone z uwzględnieniem rodzaju łożyska) |
= |
Trwałość łożyska Lh [mln obr] |
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#DIV/0! |
Wartości trwałości łożysk muszą spałniać warunek
L=Lh
#DIV/0! |
#DIV/0! |
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#DIV/0! |
Uwaga: |
#DIV/0! |
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