圆带 round belt# W! E- d% V( d7 `) C
圆带传动 round belt drive
2 \- e) X% ~: {3 r- d; J K圆弧齿厚 circular thickness
5 U% a5 Q A" m$ B! W. @: X- n. N圆弧圆柱蜗杆 hollow flank worm3 m, O8 y0 @( A6 G: c, e+ Z6 \
圆角半径 fillet radius
' l: j, _" ^7 r0 H. V E; J圆盘摩擦离合器 disc friction clutch) t: B2 d0 j3 n; }$ F9 Z
圆盘制动器 disc brake% t. X' f2 A( A; F$ X% {
原动机 prime mover' H( [" [7 Q' [0 H4 S
原始机构 original mechanism
0 J7 r5 `) \4 A3 v `圆形齿轮 circular gear: V# N: F6 y# P2 _. l- X
圆柱滚子 cylindrical roller
( q6 q+ _/ L9 X# u; C圆柱滚子轴承 cylindrical roller bearing1 T+ x) T8 X% S+ h9 J
圆柱副 cylindric pair
4 K$ `% S3 O ^5 d2 J圆柱式凸轮步进运动机构 barrel (cylindric) cam4 [1 q) v3 A, h
圆柱螺旋拉伸弹簧 cylindroid helical-coil extension spring# i# j' c) Z& x( ]9 n# U6 e
圆柱螺旋扭转弹簧 cylindroid helical-coil torsion spring4 Y8 \9 ~0 ^! q1 F5 I" g2 E
圆柱螺旋压缩弹簧 cylindroid helical-coil compression spring
9 X% M" P; m4 O$ ?6 S# K( ^: U- l圆柱凸轮 cylindrical cam
7 G" B8 C- X' N* q1 x1 I5 B; k; P* I圆柱蜗杆 cylindrical worm( p/ f6 F4 z, B& x
圆柱坐标操作器 cylindrical coordinate manipulator" n- E- G$ V5 J6 H2 ^4 J. c
圆锥螺旋扭转弹簧 conoid helical-coil compression spring
2 T$ c* D/ i* g0 X, W5 S+ z圆锥滚子 tapered roller2 l" q! |1 q$ ^( J. p7 e; ~* o5 C
圆锥滚子轴承 tapered roller bearing
- X8 |! J) V" A3 j, R% h圆锥齿轮机构 bevel gears
: w8 v3 Y k+ ?" g- q7 C圆锥角 cone angle
/ y! A; i+ a6 f& x( D原动件 driving link! c8 M; v1 M6 Q7 J2 _
约束 constraint% n3 T$ z$ n( \4 f( x* [/ p
约束条件 constraint condition1 }# E3 Z7 Y4 l L$ ^
约束反力 constraining force* m! f5 P6 e0 ]$ e
跃度 jerk; u- i1 P6 c; M0 W9 n3 P) m
跃度曲线 jerk diagram: v: C* ~( d8 F. j, ]
运动倒置 kinematic inversion
* {1 S' A: T2 G ?8 e% P% N9 ` n运动方案设计 kinematic precept design! H/ B$ W3 r- B0 v3 c
运动分析 kinematic analysis4 F/ K% Y' G. r- B+ u
运动副 kinematic pair
) S; o4 @. v! j- f运动构件 moving link
+ B( P* S( \4 x运动简图 kinematic sketch
7 v; ?8 t+ w, ^# Z- e运动链 kinematic chain
: l& ^5 c) ~3 o运动失真 undercutting
. h; F e% N- E! ^6 H! Q& n; |运动设计 kinematic design& g: O: v0 R* S! A& O" X4 }
运动周期 cycle of motion
" S, @5 X; O( T: H( L" H运动综合 kinematic synthesis* y) V( ^+ l' r7 b: I% i9 L
运转不均匀系数 coefficient of velocity fluctuation; d$ P @) O T- L8 @3 V
运动粘度 kenematic viscosity% H5 x' Q+ D% J2 u7 Z! I9 J
载荷 load
" x1 R9 m2 X* \8 c* r载荷 — 变形曲线 load—deformation curve
0 G: E! G7 Y6 i4 O; z载荷 — 变形图 load—deformation diagram! l+ z; A- Y9 ?# j1 k. R- x
窄 V 带 narrow V belt' H1 n0 e' C& N- m) w m
毡圈密封 felt ring seal
; e* L, b2 G0 C' k- A# M展成法 generating
6 Z% k1 y7 x4 A张紧力 tension
8 o3 a& G& T8 a. F! J H: r: \6 k张紧轮 tension pulley
0 e! p! x3 I; W6 U振动 vibration
( k0 v( w8 y/ v0 I% F) y A振动力矩 shaking couple( p, |0 ^3 E% {, u+ P4 Z
振动频率 frequency of vibration
6 T* k8 m1 Y& T+ A! G/ e振幅 amplitude of vibration8 z/ I. M! J# H& S( N3 a; Y
正切机构 tangent mechanism/ E* d( h: q4 L
正向运动学 direct (forward) kinematics% G9 L" p9 t: X; J& {
正弦机构 sine generator, scotch yoke1 l4 o& J- y: M, K
织布机 loom
' |- E6 V" s, w正应力、法向应力 normal stress
: Y5 }4 G% g2 S! B% K @制动器 brake- N% V+ v9 @* w! B& O8 |/ x; Y
直齿圆柱齿轮 spur gear
" N' |- u* \5 Y8 ?0 S" }$ ]直齿锥齿轮 straight bevel gear" Q# z: A# p7 c+ |$ z' F4 g3 U
直角三角形 right triangle3 T! j- @3 ]0 n! N
直角坐标操作器 Cartesian coordinate manipulator
/ i$ P8 e, N0 f直径系数 diametral quotient
1 j# ^7 x2 f5 w& C+ }" i' b( R直径系列 diameter series2 p9 b0 p7 L5 i3 i% m
直廓环面蜗杆 hindley worm
0 N9 u% G" L8 K7 h) g* U, f7 \1 p直线运动 linear motion
+ P6 h. ]) G. l3 O9 M: c/ N6 R: K直轴 straight shaft6 H8 V( k2 h4 G8 r8 Z+ O: m. n/ {% b
质量 mass B' N6 ?" x$ O* A, w
质心 center of mass' d2 f+ d8 k7 _7 S
执行构件 executive link; working link
) q3 S) S7 R' ?) o( l# v质径积 mass-radius product
/ l! j' i& \7 D8 w0 I" p智能化设计 intelligent design, ID- A% G6 v8 b3 {, r, S
中间平面 mid-plane
0 J) c v: W& V/ s; {中心距 center distance
) C5 h( G- a; H中心距变动 center distance change X7 Q0 ~2 I# L4 f+ C& Q
中心轮 central gear6 A% H9 ]4 ~& @- l1 v5 Y
中径 mean diameter
' @! j) r3 B/ s" K1 \终止啮合点 final contact, end of contact/ I- C, a' V9 f7 h' \4 A
周节 pitch
0 `& {2 M4 d* G1 O1 ^& A周期性速度波动 periodic speed fluctuation
$ z$ @: \ }4 H9 B0 U周转轮系 epicyclic gear train
- B! ~% G! C6 }% L8 L8 z+ K+ @肘形机构 toggle mechanism
8 [# r2 b5 m. S! w9 b" N5 B轴 shaft
+ k( [( N4 e0 C8 ^2 L1 k& P- d轴承盖 bearing cup- L- b* K: L3 P M
轴承合金 bearing alloy
; V9 K" R y4 d% i轴承座 bearing block, A& k% i: O4 l2 _8 N7 @* e
轴承高度 bearing height
( Y- E0 B. G; c0 E- b轴承宽度 bearing width
4 k3 {+ B7 K0 v- i2 R- j: B轴承内径 bearing bore diameter7 {1 z# P7 j) M$ a0 o
轴承寿命 bearing life
% _6 h" f& P2 x; `轴承套圈 bearing ring9 d! ?& c2 H f& u6 Y6 V
轴承外径 bearing outside diameter
# J7 a# `3 G. C- n$ d# r0 g轴颈 journal
$ e$ _% H8 P- y$ g$ u0 F轴瓦、轴承衬 bearing bush; k! S+ \& r8 C( x* o1 h
轴端挡圈 shaft end ring
# a# J- m+ R. s; P- z1 I' K& K轴环 shaft collar
; d1 q; F! A* k8 q+ e( U轴肩 shaft shoulder. V% s9 o% O- |
轴角 shaft angle* Z" D2 u9 v" N+ g' \* Q
轴向 axial direction
- F9 B/ N. O5 X2 N. x轴向齿廓 axial tooth profile$ G* \4 m: @. c+ ~; V0 P
轴向当量动载荷 dynamic equivalent axial load5 ?: @0 m" O1 D6 Q! z# N, g" c
轴向当量静载荷 static equivalent axial load
4 ?/ n# q ?, e/ Z: G3 h. U" D轴向基本额定动载荷 basic dynamic axial load rating
' R; S. R# M8 c+ W轴向基本额定静载荷 basic static axial load rating
# l: T6 |- y& Y4 B* v轴向接触轴承 axial contact bearing* c) i: ]" ~& v
轴向平面 axial plane4 I: {2 w3 ]4 t! d
轴向游隙 axial internal clearance+ q) V( h. y3 k: w% D6 f
轴向载荷 axial load
, r; O9 T) z f& c' ~5 V1 Z) f轴向载荷系数 axial load factor
, u+ I" D d: E( r2 [4 p+ C轴向分力 axial thrust load
7 O8 _3 V' Q3 t) t) C* C主动件 driving link
u L+ w- p3 v/ o1 ^1 i6 \主动齿轮 driving gear
8 a2 [+ } Y. F$ |; E7 x/ y主动带轮 driving pulley2 H. A$ `9 }* b/ q4 d$ N! u
转动导杆机构 whitworth mechanism
* n& ]. d v2 K* T, b+ e转动副 revolute (turning) pair! S' Q( m0 C0 O' o7 l
转速 swiveling speed rotating speed
( I0 w: P( K- a2 `0 ~转动关节 revolute joint
* m3 E- o) V$ c2 ^& d- ]. P转轴 revolving shaft
8 [4 T g2 T6 [! C2 G转子 rotor0 Q9 g7 [4 K: d* j' v+ X/ `
转子平衡 balance of rotor
5 R) g5 k8 z5 Y' N装配条件 assembly condition( M, l% V, g8 C1 P" G5 ^
锥齿轮 bevel gear
$ g& X9 T) g! `* N5 j锥顶 common apex of cone
5 Q. ^$ n: c6 l" R5 G3 Z6 R) x锥距 cone distance( I3 v1 m8 J p7 C, _7 ^& X
锥轮 bevel pulley; bevel wheel* ]! v) A. s) o% x# e
锥齿轮的当量直齿轮 equivalent spur gear of the bevel gear% z6 o+ W9 p& Y: w$ J
锥面包络圆柱蜗杆 milled helicoids worm% ^8 N4 f9 U- U5 `5 o2 s( ?9 E
准双曲面齿轮 hypoid gear
' D0 i# \7 r, y" R; F% _子程序 subroutine. M" N# z" ]& P. b
子机构 sub-mechanism8 A; o$ G( E8 b5 D6 t! J4 v
自动化 automation/ W+ A$ }: X. H O2 Q
自锁 self-locking
* s" k- k. Y1 N2 W1 \' P自锁条件 condition of self-locking
2 ]. x: ` n$ b4 Q自由度 degree of freedom, mobility
& [% U g( Z% x6 v# f总重合度 total contact ratio1 d& }; H0 a! @( y" G7 ^
总反力 resultant force, l3 j% M ?# o
总效率 combined efficiency; overall efficiency5 [+ g: P" R2 t$ u
组成原理 theory of constitution
+ s4 _6 z, I+ k/ t组合齿形 composite tooth form
+ K7 ~& M+ s2 D/ Z O% X9 p ]6 G组合安装 stack mounting3 s8 h4 w5 O8 K1 t
组合机构 combined mechanism( V( e7 t# T8 c6 N' v
阻抗力 resistance
, O* ]4 m1 u2 D最大盈亏功 maximum difference work between plus and minus work) I2 j7 [' m5 B/ l' o2 Q1 d8 }
纵向重合度 overlap contact ratio: l! L: T4 B# m3 x; @6 ^. R t, O* @
纵坐标 ordinate) Z2 _0 [" P$ _8 ^* L- B! ]* s
组合机构 combined mechanism
. K% u* a2 H& n最少齿数 minimum teeth number
( \( v1 A) r9 c9 q5 L最小向径 minimum radius
& a, d8 }9 |7 a6 Y3 Q作用力 applied force
" ?, c( H3 B4 j( u6 V4 d坐标系 coordinate frame |
发表于 2008-2-21 11:45:15
