圆带 round belt3 P1 o$ ~* m( d
圆带传动 round belt drive, Z7 H, M0 S& O- h4 V
圆弧齿厚 circular thickness
8 `8 C; n" L- k0 Z; O圆弧圆柱蜗杆 hollow flank worm2 [5 P, o" T1 v: ~
圆角半径 fillet radius2 b4 B9 W: q+ p6 Z
圆盘摩擦离合器 disc friction clutch2 K. h( K9 V9 D- j& f L* O7 R8 v
圆盘制动器 disc brake9 t7 l3 `. j# E0 I2 S
原动机 prime mover* q& Q& _. N) H3 E1 A
原始机构 original mechanism
! W1 E- P/ J. w& e! i0 Q/ ^! L圆形齿轮 circular gear' r/ a& _3 ~* _: G! i z
圆柱滚子 cylindrical roller
2 t6 a; l7 h4 b% d圆柱滚子轴承 cylindrical roller bearing9 D+ a: B: }' [; Y- }
圆柱副 cylindric pair
8 w( f- m, j6 b ]/ c圆柱式凸轮步进运动机构 barrel (cylindric) cam
, F4 B S1 P6 k9 x圆柱螺旋拉伸弹簧 cylindroid helical-coil extension spring
2 T/ e3 H: k5 X3 M圆柱螺旋扭转弹簧 cylindroid helical-coil torsion spring
5 _4 F& H- V* l0 z( R+ n圆柱螺旋压缩弹簧 cylindroid helical-coil compression spring
{& v q) v6 ^圆柱凸轮 cylindrical cam
: D7 ?# a# m/ s- ~( l圆柱蜗杆 cylindrical worm( z2 @5 r$ Q: M. ]: z
圆柱坐标操作器 cylindrical coordinate manipulator0 @+ T0 b# I9 o3 N& x0 O% |
圆锥螺旋扭转弹簧 conoid helical-coil compression spring$ i1 d4 D3 X0 O! X: C* Q, m8 b
圆锥滚子 tapered roller
$ o+ `7 |8 J- x% J* ~; u/ K4 a圆锥滚子轴承 tapered roller bearing
& _$ F; A* m9 p4 W6 t# y: R圆锥齿轮机构 bevel gears! q# o3 X: w9 r3 w: G
圆锥角 cone angle
7 {: f5 m( \; ^原动件 driving link
' s8 q% j& j" ^' |约束 constraint
- Z1 M/ i, w5 ]# \* Q约束条件 constraint condition7 R4 F! Z3 A! S& j6 P
约束反力 constraining force
. H4 Z, F1 X% D1 H0 h1 n( S跃度 jerk
1 q' u: ]' r! Q. E" E- h- D3 {6 P跃度曲线 jerk diagram% Z1 D {9 z5 ^' F4 ^' [4 q
运动倒置 kinematic inversion* R) y0 U, ?2 X. o- {2 G
运动方案设计 kinematic precept design/ y7 l0 Z) X( F, ?
运动分析 kinematic analysis
+ e/ @% g- w3 \3 T3 `) \6 l运动副 kinematic pair
6 X( r" O" I! z# d9 |" p' Q5 _运动构件 moving link
/ |$ ~5 b, v d2 N运动简图 kinematic sketch
# m! S1 R- X" N运动链 kinematic chain. U2 H3 b( C% J1 z
运动失真 undercutting
" k1 C: ]! s- x运动设计 kinematic design7 I! f3 c$ e2 H* y6 g) z
运动周期 cycle of motion w4 k: O* h7 C5 K% d: r- |( F
运动综合 kinematic synthesis
; {1 T+ @% t$ z运转不均匀系数 coefficient of velocity fluctuation
9 J" _) G: I7 n o2 m运动粘度 kenematic viscosity8 Z0 N5 d8 A9 r, G
载荷 load 6 r7 l8 A6 P K; W$ j
载荷 — 变形曲线 load—deformation curve
7 T: H% \ S6 k载荷 — 变形图 load—deformation diagram% c2 j6 l9 h7 I& h
窄 V 带 narrow V belt) f% i- |6 G+ \( D0 f/ s, |
毡圈密封 felt ring seal. K1 Q! t# n, l
展成法 generating
: ?6 ]+ o) b5 `$ y. o7 f6 M/ u张紧力 tension
5 U( i. b& b2 {6 g) x% _张紧轮 tension pulley% g0 P) e9 @+ e% W. q( t
振动 vibration* v, J! `5 U! v; B
振动力矩 shaking couple
+ K; t% i6 E0 B; k( P7 K0 D- }振动频率 frequency of vibration4 _$ L! N. M) Y4 [' Q; G; d# x
振幅 amplitude of vibration
! S+ M% @+ o8 ^ }& t; k- k正切机构 tangent mechanism
5 e" r. o( Z7 k$ ^* Z正向运动学 direct (forward) kinematics
- u& z _, g! r9 P6 K8 l- \正弦机构 sine generator, scotch yoke! S4 W6 |: M5 p2 b; ^& I
织布机 loom' Q, [! y0 b8 t- m4 t
正应力、法向应力 normal stress
. J8 n/ @* U+ h制动器 brake- | [/ B0 t2 S4 ^) l+ v
直齿圆柱齿轮 spur gear
2 i( g4 h( o8 R! S; a( q5 S直齿锥齿轮 straight bevel gear$ Y/ B6 P5 e+ y, U4 [$ D
直角三角形 right triangle- g% G* y# [, ^" g _# D; L
直角坐标操作器 Cartesian coordinate manipulator
; Q9 c" X: V; }; k$ R% r直径系数 diametral quotient
3 Z, D& \, y8 W- ^' q n! E直径系列 diameter series
4 u7 d8 L( k. l# \4 H2 \6 V7 F直廓环面蜗杆 hindley worm
/ t* f7 a" j3 C9 M, ^; l k直线运动 linear motion: U6 i8 A$ G# p( U" }5 f
直轴 straight shaft
7 B0 H$ \0 _) |! N2 V质量 mass
2 w0 e5 e; s% e质心 center of mass
; b. U. X- l7 }执行构件 executive link; working link
. v& }+ I+ k" g8 Q# ^+ {7 g/ |质径积 mass-radius product; H/ P% x/ p8 m/ Y* Y" v
智能化设计 intelligent design, ID1 H9 X9 J4 k5 S
中间平面 mid-plane1 r8 J( Y0 Q$ N6 T/ V
中心距 center distance6 p) c) h8 X( y
中心距变动 center distance change: z) Y) v, S9 X& P$ N" k* u Y0 {
中心轮 central gear% J. s% u9 V1 \2 m
中径 mean diameter2 W4 d' T5 b& |' v. Y
终止啮合点 final contact, end of contact
q) V0 c& N1 y! f' v周节 pitch8 k% p. L& ?' h3 p7 i
周期性速度波动 periodic speed fluctuation
" X+ H" {9 R. ?8 g8 t周转轮系 epicyclic gear train7 ^7 J, M y! j( Q! s
肘形机构 toggle mechanism
6 T( \* V: [$ _/ d+ Q2 T轴 shaft y% U% H$ [' R' g4 o
轴承盖 bearing cup
( L" @* |+ q0 v& ^" x轴承合金 bearing alloy7 w7 }; ~" C" m& T, z
轴承座 bearing block" e o# {1 r O v) l- n
轴承高度 bearing height* Q# ?: e# n& @8 B8 Q: y9 m
轴承宽度 bearing width
8 l6 W. V# @& {. j7 E轴承内径 bearing bore diameter
) E* c; a! O8 D! M, K- r轴承寿命 bearing life
8 ]4 `* v# x6 P) t8 i轴承套圈 bearing ring# s) u0 }4 ?& n7 i& V
轴承外径 bearing outside diameter
! S9 z3 x- Z; O. ^轴颈 journal( t7 D p* y5 b
轴瓦、轴承衬 bearing bush
: `' ?) @6 _, a" F轴端挡圈 shaft end ring
9 u. P: q J/ {) e轴环 shaft collar( @( n* g0 V! o. o
轴肩 shaft shoulder
7 H t/ N4 s. q. L* P' |轴角 shaft angle
" h4 [4 Y) `- G; o5 \: y3 t3 }轴向 axial direction6 n- p! Y- W% @* F" }+ ^* L
轴向齿廓 axial tooth profile
3 w2 Y( m# R1 I" z- A* V9 z轴向当量动载荷 dynamic equivalent axial load
) {) s8 u' a% Z& t! R0 W1 }6 R( }3 {轴向当量静载荷 static equivalent axial load
* s' b$ K; Q3 p轴向基本额定动载荷 basic dynamic axial load rating4 B: Z# ?8 W5 s4 o; W
轴向基本额定静载荷 basic static axial load rating8 H2 ~, \' O+ k/ x/ C9 M
轴向接触轴承 axial contact bearing
& k& c& O8 H, t5 S' O轴向平面 axial plane) K( i2 J: o c, j$ n$ C
轴向游隙 axial internal clearance
7 A( r: ?3 p* h* i! v9 k5 W- b轴向载荷 axial load
0 C! \. z! d% P! q9 w轴向载荷系数 axial load factor
4 P: l* X0 R: E& E* t1 E轴向分力 axial thrust load: I5 c$ {/ W9 Z! P+ G0 Q$ M# S
主动件 driving link
4 a- I; |. n4 f) Z) p0 n主动齿轮 driving gear
! N- c/ |" E7 D( H主动带轮 driving pulley2 R4 M( x A; \/ G b* L1 W
转动导杆机构 whitworth mechanism
, Q8 q m/ l+ A' L7 A2 x转动副 revolute (turning) pair
2 N a' _: f# t8 ^转速 swiveling speed rotating speed/ ^# w: J( w1 q5 g+ [* `1 d/ O! L
转动关节 revolute joint
* i2 _' y: d: R/ j& l' e3 n转轴 revolving shaft7 t' a. z6 O1 P8 K; T" a; b" _
转子 rotor
6 \5 n% l7 s% ^3 q转子平衡 balance of rotor
Y! n( f+ T$ }/ E: G; E装配条件 assembly condition
- N Y& ?$ {; ?8 O T5 ?锥齿轮 bevel gear
4 L: g( _# x/ E O- i7 W锥顶 common apex of cone
+ a+ j# t _; j6 {; {; e+ I% r4 l/ D锥距 cone distance
4 \$ E( r2 b/ v3 C& H锥轮 bevel pulley; bevel wheel
0 f$ f( ~8 J* {0 v锥齿轮的当量直齿轮 equivalent spur gear of the bevel gear3 [/ i3 U O$ V
锥面包络圆柱蜗杆 milled helicoids worm8 A' I( Z- B" x
准双曲面齿轮 hypoid gear
$ \# L" w/ X! m8 i( K子程序 subroutine
* I+ j/ j l! v子机构 sub-mechanism
8 ^9 F8 k1 ]1 p, K自动化 automation' Z! A O7 q2 Q, S8 j, s5 m
自锁 self-locking
, Q( @2 ^/ n% B; v, W自锁条件 condition of self-locking* g$ Z4 l/ L" h8 l: S- E' h
自由度 degree of freedom, mobility7 ]# K2 @2 N* L0 W U
总重合度 total contact ratio. L5 ~4 e# X( G) U* I; o
总反力 resultant force
/ O- a) o0 C! ?$ ]: {: b+ c总效率 combined efficiency; overall efficiency
, S* ^; j0 B# h0 \5 o1 X; k组成原理 theory of constitution
: e5 d: y1 {5 y% S0 M+ O组合齿形 composite tooth form7 V. Z" d6 _" ^+ G
组合安装 stack mounting# N4 C9 v( i7 C# P9 X/ f
组合机构 combined mechanism
& m9 F! J! w! A: c& q: r N! S* p) d阻抗力 resistance
. R8 N* ?+ E# m: V6 Q* i4 z, U最大盈亏功 maximum difference work between plus and minus work
7 O! r& V& h; O7 o" b/ Z纵向重合度 overlap contact ratio: m/ B) l; j. Y7 o3 f- u! L" O7 o
纵坐标 ordinate
0 S! f" a2 A- H( [, q组合机构 combined mechanism1 Z1 f* S; {! M, L- U
最少齿数 minimum teeth number9 N& ~6 S3 i! L4 q
最小向径 minimum radius
8 d, _, j$ h- @' j作用力 applied force
( z) S D: h, b( J坐标系 coordinate frame |
发表于 2008-2-21 11:45:15
