机械必威体育网址

标题:蜗轮蜗杆传动---请教 [打印本页]

作者:风起狂浪 时间:2008-11-29 11:46
标题:蜗轮蜗杆传动---请教
选用模数5,头数2,齿数31,蜗杆分度圆直径50,变位系数-0.5 设计手册的中心距是100,可我做出的图纸是102.5,
2 M$ Y# S* {6 k! w$ g \8 \不知道这2.5的问题出在哪里,请必威体育网址的高手给解答下 先谢了
作者:风起狂浪 时间:2008-11-30 13:39
等待着诸位大侠的到来ING....
作者:风起狂浪 时间:2008-12-1 15:55
是问题太过简单?可我还是不了解 还是在等待
作者:风起狂浪 时间:2008-12-3 15:41
问题没解决之前不想让帖子下沉 自己顶一下
, e1 Y. c2 b# J* I斑竹海涵
作者:willian 时间:2008-12-3 22:29
传动比多少啊,自己对着手册再算一遍吧
作者:风起狂浪 时间:2008-12-4 10:34
传动比不是齿数:头数=15.5么 计算了N回了 还是解决不了
作者:轩芳 时间:2008-12-4 23:55
注意变位系数。
作者:风起狂浪 时间:2008-12-5 18:10
原帖由 轩芳于 2008-12-4 23:55 发表 - N$ n' y1 i4 ^5 c# [
注意变位系数。
- E! d4 q& O: a9 q: T5 H2 Z
这个也算在里面了 就是不对
作者:风起狂浪 时间:2008-12-9 17:37
原帖由 klmn857于 2008-12-7 09:40 发表 + Y" m- M0 m8 @% n
一种理想就是一种力量!在这一人航海的人生浩瀚大海中水宜生健康杯,理想是罗盘针,热情是疾风。目标愈高,志向就愈可贵。生活好比旅行,理想是旅行的路线,失去了路线,只好停止前进。人有了物质才能生存水宜生保健杯 ...
. q2 }" d7 a4 {% q
好容易来了一个 一看还是广告 郁闷呢
作者:wpc 时间:2008-12-9 20:43
由于蜗轮变位导致分度圆与节圆不相等。变位后蜗轮与蜗杆实际是节圆相啮合。
; w: D" }/ T, u6 e1 e& U; @下面是我设计的蜗轮蜗杆:(参照第2版机械设计手册35-206)
2 O$ n1 ~! I5 O2 _" }. H# ]蜗轮、蜗杆中心距:41 9 B* y$ g8 H; n1 t9 ^6 |
蜗杆 7 ~8 n1 b- Y0 E
头数:2 、模数:2 、 分度圆直径:14 、节圆直径16 & Z p1 Q# O& {8 e9 U$ z3 V. p
蜗轮
2 I% Z5 f% y( f& ^' B9 z9 c模数:2 、齿数:33 、蜗轮变位系数:0.5 、分度圆直径:66 、节圆直径: 66
作者:wpc 时间:2008-12-9 21:12
不知什么原因刚才的帖子没发出去。重发。 [' k, d% h( D7 F& Z& E
0 U6 i7 [! r* L( b: F4 ~0 d4 \; w
正常情况下蜗轮、蜗杆是分度圆啮合,蜗轮变位后是节圆啮合。
- A5 }' k5 w" U0 q- J* M0 e9 ^下面是我设计的蜗轮、蜗杆(参照第2版机械设计手册35-207) 6 Z) r7 y+ A$ V7 }
蜗轮、蜗杆实际中心距:41 * p9 h! G, C4 y7 G7 K& b! _+ h6 u
蜗杆 - u: a6 k9 @$ p- O6 u8 B
模数:2 、 头数:2 、分度圆直径:14 、 节圆直径:16
7 c3 `8 r! F. w) E @2 m蜗轮 / s" W Q/ @/ |4 y" I2 ]! j
模数:2 、齿数:33 、蜗轮变位系数:0.5 、分度圆直径:66 、节圆直径:66 + d9 y N0 i1 N, @7 C

% D" {3 i9 R" |[ 本帖最后由 wpc 于 2008-12-9 21:14 编辑]
作者:风起狂浪 时间:2008-12-10 16:05
谢谢WPC的回答 先算算,再查查书。一会告诉您结果
作者:风起狂浪 时间:2008-12-11 09:42
可是中心距尾数一般取0或者是5,大侠这个好像不是的?这个有什么解释么?请教中。。。。
作者:wpc 时间:2008-12-11 22:12
尾数是0或5是为了标准化。变位系数就是为了调整中心距。 , M) f3 I& k4 r" }
如果有一天我们遇到中心距不是0或5的产品,我们不是也要做吗?
作者:风起狂浪 时间:2008-12-13 10:56
谢谢WPC大侠的指点 问题解决
作者:程程wah 时间:2008-12-13 15:03
不用那么复杂公式a=(d1+d2+2xm)/2
作者:风起狂浪 时间:2008-12-14 10:08
原帖由 程程wah于 2008-12-13 15:03 发表
! ?' x& _- f. V* X6 P$ D) H不用那么复杂公式a=(d1+d2+2xm)/2
6 m8 A1 b! c; h
这样的话变位系数不考虑了么?
作者:张鹏飞 时间:2008-12-19 10:30
标题:蜗轮我杆的计算公式
老兄,请把你的主要参数的计算公式在分析一下,往复演算以下,你算的多出来的2.5的数据主要出现在公式和数据上
作者:程程wah 时间:2008-12-19 10:59
变位系数不就是X吗?50+31*5+2*5*(-0.5)]/2
作者:风起狂浪 时间:2008-12-20 08:29
原帖由 程程wah于 2008-12-19 10:59 发表
0 A4 g% A* [ M: Z* O4 K+ U5 t变位系数不就是X吗?50+31*5+2*5*(-0.5)]/2
$ h) ^1 M* h0 j; k4 E. g& Y" c
谢谢 把变位系数看做乘号了 谢谢
作者:renhuiwen 时间:2012-5-31 11:59
WORMGEAR ANALYSIS
Drawing or article number:
worm: 0.000.0
Gear: 0.000.0
Calculation-method Only geometrycalculation
(Geometry: ISO 14521)
Geometry calculation from axial module
1. TOOTHGEOMETRY AND MATERIAL
Shape of flank: ZK
------- WORM---------------- WHEEL ----
Centre distance (mm) [a] 100.000
Centre distance tolerance ISO 286Measure js7
Axis angle (°) [Sigma] 90.0000
Transverse module (mm) [mt] 5.0000
Normal module (mm) [mn] 4.9029
Axial module (mm) [mx] 5.0000
Pressure angle at normal section (°) [alfn] 20.0000
Mean lead angle (°) [gamma] 11.3099
Helix left left
Number of teeth [z] 2 31
Facewidth (mm) [b1] 30.00
Wheel rim width b2R (mm) [b2R] 30.00
Wheel width b2H (mm) [b2H] 30.00
Facewidth for calcul. (mm) [b1, b2] 30.00 30.00
Accuracy grade (manufacturing) [Vqual] 6 7
Internal diameter gearbody (mm) [di] 0.00 0.00
Material
worm: 18CrNiMo7-6, Case-carburized steel, case-hardened
ISO6336-5 Figure 9/10 (MQ), core strength >=25HRC Jominy J=12mm
Gear: CuSn12-C-GZ, Bronze, untreated
------- WORM---------------- WHEEL ----
Surface hardness HRC 61 HBW 95
Yield point (N/mm?) [sigs] 850.00 150.00
Youngs modulus (N/mm?) [E] 206000 88300
Poisson's ratio [ny] 0.300 0.350
Fatigue str. tooth root tension (N/mm?) [tauFlim] 430.00 92.00
Fatigue str. Hertzian stress (N/mm?) [sigHlim] 1500.00 425.00
Average roughness, Ra, tooth flank (?m) [RAH] 0.60 1.30
Mean roughness height, Rz, flank (?m) [RZH] 4.80 0.00
Mean roughness height, Rz, root (?m) [RZF] 20.00 0.00
Material Coefficient YW [YW] 1.00
Material lubrication coefficient [WML_Min] 1.60
Tool or reference profile of gear 1 :
Reference Profile
1.25 / 0.38 / 1.0ISO 53.2 Profil A
Addendum factor [haP*] 1.000
Dedendum coefficient [hfP*] 1.250
Tip radius factor [rhoaP*] 0.000
Root radius factor [rhofP*] 0.380
Tip form height coefficient [hFaP*] 0.000
Protuberance height factor [hprP*] 0.000
Protuberance angle [alfprP] 0.000
Ramp angle [alfKP] 0.000
not topping
Tool or reference profile of gear 2 :
Reference Profile
1.25 / 0.38 / 1.0ISO 53.2 Profil A
Addendum factor [haP*] 1.000
Dedendum coefficient [hfP*] 1.250
Tip radius factor [rhoaP*] 0.000
Root radius factor [rhofP*] 0.380
Tip form height coefficient [hFaP*] 0.000
Protuberance height factor [hprP*] 0.000
Protuberance angle [alfprP] 0.000
Ramp angle [alfKP] 0.000
not topping
Sum of reference profile gears:
Dedendum reference profile (module) [hfP*] 1.250 1.250
Tooth root radius Refer. profile (module)
[rofP*] 0.380 0.380
Addendum Reference profile (module) [haP*] 1.000 1.000
Protuberance height (module) [hprP*] 0.000 0.000
Protuberance angle (°) [alfprP] 0.000 0.000
Buckling root flank height (module) [hFaP*] 0.000 0.000
Buckling root flank angle (°) [alfKP] 0.000 0.000
Generating angle (°) [alfa0] 20.000
Pressure angle at normal section (°) [alfn] 20.000
Indications forthe manufacture of the worm gear according to DIN3975:& L1 G' Q2 q) l7 k# I
(Only valid for worm gears which are manufactured with a hob similar to theworm)
Mean lead angle of the worm (°) [gamma] 11.3099
Transverse module (mm) [mt] 5.0000
Reference diameter (mm) [d] 155.000
Meancircle diameter (mm) [dm] 150.000
Outside diameter (mm)
Tipgroove mean radius (mm)
Profile shift coefficient [x-DIN3975] -0.5000
Pitch (mm) [p2] 15.708
Indications forthe manufacture of the worm gear as a cylindrical gear
4 L1 p3 q5 O) u(This specification is only asuggestion. It is necessary to do a calculation of the exact geometry using thecrossed-helical calculation!)
Pressure angle at Transverse section (°) [alft] (61.683) 20.452
Pressure angle at axial section (°) [alfx] (20.364) 59.091
Helix angle at reference diameter (°) [beta] (78.690) 12.586
Lead angle at pitch diameter (°) [gamma] (11.310) 77.414
Transverse module (mm) [mt] (25.000) 5.024
Axial module (mm) [mx] ( 5.000) 25.000
Helix angle at operating pitch diameter (°) [betas] (77.471) 12.529
Operating pitch diameter (mm) [dw] (45.000) 155.000
Profile shift coefficient [x-DIN3960] (0.0000) -0.5099
Gear ratio 15.500
Base helix angle (°) [betab] 10.620
Reference centre distance (mm) [ad] 102.500
Shape number q [q] 10.000
Sum of the Addendum modification [Summexi] -0.5000
Profile shift coefficient [x-DIN3975] 0.0000 -0.5000
Profile shift coefficient (x*m) (mm) [x*mx] 0.0000 -2.5000
(The addendum modification is related to the axial module of the wormsubject to DIN3975)
Modification of tip diam. (mm) [k] 0.000 0.000
Theoretical tip clearence (mm) [c] 1.250 1.250
Effective tip clearence (mm) [c.e/i] 1.512/ 1.405 1.340/ 1.233
Meancircle diameter (mm) [dm] 50.000 150.000
Reference diameter (mm) [d] 155.000
Base diameter (mm) [dB] 145.313
Tip diameter (mm) [da] 60.000 160.000
Tip chamfer/ tip rounding (mm) [hK] 0.000 0.000
Tip form circle (mm) [dFa] 60.000 160.000
(mm) [dFa.e/i] 60.000/59.990 160.000/159.990
Tip diameter allowances (mm) [Ada.e/i] 0.000/-0.010 0.000/-0.010
Root diameter (mm) [df] 37.500 137.500
Generating Profile shift coefficient [xE.e/i] -0.5450/-0.5588
Manufactured root diameter with xE (mm) [df.e/i] 37.500/37.364 137.155/137.021
Lead height (mm) [pz] 31.416
Axial pitch (mm) [px] 15.708
8. MEASURES FORTOOTH THICKNES
Tooth thickness tolerance
worm: Worm according Niemann
Gear: Wormwheel according Niemann
------- WORM---------------- WHEEL ----
Tooth thickness allowance (normal section) (mm)
[As.e/i] 0.000/-0.049 -0.161/-0.210
Axial Distance Without Backlash (mm) [aControl] 99.775/ 99.637
Backlash free centre-distance, Tolerances (mm) [jta] -0.225/-0.363
No of teeth over which to measure [k] 3.000
Base tangent length ('span') (no backlash) (mm)
[Wk] 36.759
Actual base tangent length ('span') (mm) [Wk.e/i] 36.608/36.562
Diameter of contact point (mm) [dMWk.m] 149.696
Base tangent length ('span'): Can only be measured, if the worm-wheel ismanufactured like a cylindrical gear
Theor. ball/roller diameter (mm) [dm] 8.211 8.045
Actual ball/roller diameter (mm) [DMeff] 9.000 8.000
Theor. dim. centre to ball (mm) [MrK] 80.060
Actual dimension centre to ball (mm) [MrK.e/i] 79.795/79.713
Diameter of contact point (mm) [dMMr.m] 51.899 149.473
Theor. dimension over two balls (mm) [MdK] 159.925
Actual dimension over balls (mm) [MdK.e/i] 159.396/159.231
Outer diameter of grinding wheel(mm) [daS] 500.000
Set angle of grinding wheel (°) [beta] 11.3099
Theoretical dim. over 3 wires (mm) [Md3R] 64.089
Actual dim. over 3 rolls (mm) [Md3R.e/i] 64.089/63.957
Tooth thickness (chordal) in pitch diameter (mm)
['sn] 7.701 5.880
Actual chordal tooth thickness (mm) ['sn.e/i] 7.701/7.652 5.720/5.671
Tooth thickness on axial cut (mm) [smx] 7.854
Actual tooth thickness (mm) [smx.e/i] 7.854/7.804
Tooth gap in axial cut (mm) [emx] 7.854
Actual tooth gap (mm) [emx.e/i] 7.854/7.904
Chordal height from da.m (mm) [ham1, ha2] 4.997 2.551
Centre distance deviation (mm) [Aa.e/i] 0.018/-0.018
Circumferential backlash (transverse section) (mm)
[jt] 0.277/0.151
Normal backlash (mm) [jn] 0.255/0.139
9. TOLERANCES
------- WORM----------------WHEEL ----
According DIN 3974:
Accuracy grade [Vqual] 6 7
Single normal pitch deviation (?m) [fpx, fp2] 8.50 13.00
Difference between adjacent pitches (?m) [fux, fu2] 11.00 16.00
Total deviation of the slope (?m) [Fpz] 11.00
Total cumulative pitch deviation (?m) [Fp2] 51.00
Profile angular deviation (?m) [fHa] 7.50 11.00
Profile deviation (?m) [ffa] 11.00 15.00
Profile total deviation (?m) [Fa] 13.00 19.00
Runout tolerance (?m) [Fr] 18.00 35.00
Total tangential composite deviation (?m) [Fi'] 29.00 56.00
Tooth-to-tooth tangential composite deviation (?m)
[fi'] 15.00 22.00

' h/ I' P% t F3 c- F/ q* h+ [




欢迎光临 机械必威体育网址 (//www.szfco.com/) Powered by Discuz! X3.4