圆带 round belt
' v1 A6 @0 C& h% r+ W/ T5 T圆带传动 round belt drive) }5 p2 ]6 d" E( h0 q. k; w
圆弧齿厚 circular thickness
) @7 B5 v& K2 b! j; d* y }' n圆弧圆柱蜗杆 hollow flank worm
4 A' q, [* U6 S- @圆角半径 fillet radius1 l# G- }& i# a' M0 Y' U# Y3 y4 t
圆盘摩擦离合器 disc friction clutch
2 B! w" j+ w) S( \圆盘制动器 disc brake
$ `) P5 ?3 B. ]* H) ]) S原动机 prime mover
4 G% W6 q: V* B7 F原始机构 original mechanism2 D& g( T/ e& q- e3 N9 ~5 j% x9 c
圆形齿轮 circular gear
# M: h! i! I5 \7 Z圆柱滚子 cylindrical roller
' D2 o5 W9 h: R7 x" k- i圆柱滚子轴承 cylindrical roller bearing$ g% p* }; c3 `7 X6 p
圆柱副 cylindric pair: q$ q. |' M' X7 f1 R, c' Z9 ]8 Q) W
圆柱式凸轮步进运动机构 barrel (cylindric) cam
3 _" y3 V @" q; i( W" `圆柱螺旋拉伸弹簧 cylindroid helical-coil extension spring; u7 m+ P0 |- y( ?7 S; l0 h# n6 u( ^' l
圆柱螺旋扭转弹簧 cylindroid helical-coil torsion spring' o: C5 r8 t$ p
圆柱螺旋压缩弹簧 cylindroid helical-coil compression spring* Y4 k4 H D3 S/ y: s* Y. ]+ ^
圆柱凸轮 cylindrical cam0 g$ b( i m' r- P9 R6 n' |
圆柱蜗杆 cylindrical worm9 v+ Z3 X; U7 g6 O+ f/ k0 Q
圆柱坐标操作器 cylindrical coordinate manipulator7 i/ A: L2 F5 q
圆锥螺旋扭转弹簧 conoid helical-coil compression spring
8 {3 R9 v) Q* W& P4 i/ c圆锥滚子 tapered roller9 B( M: `% K+ u) a. T4 Y# s: H
圆锥滚子轴承 tapered roller bearing
! ~' V( G, w1 R1 C圆锥齿轮机构 bevel gears
% f1 e7 L% v, F$ L圆锥角 cone angle
2 J* P' c4 e c, y/ z原动件 driving link
3 [" S; M3 `7 e$ r: E约束 constraint7 P9 L9 ?6 _* I' o; ~) x
约束条件 constraint condition v/ S! f, t2 r3 V
约束反力 constraining force* h( e% Q) W+ q
跃度 jerk
% I+ L2 l0 q' t( ^跃度曲线 jerk diagram9 u$ R/ H$ l6 o6 U# {' L/ `
运动倒置 kinematic inversion* V# ~" d1 T0 H/ W# t3 j
运动方案设计 kinematic precept design
. ^0 z+ b- K0 |) b8 l: A运动分析 kinematic analysis* s* Y# E+ I: G
运动副 kinematic pair' Q* S1 G; p/ a- A8 m, L2 u/ T( i W
运动构件 moving link# j5 [8 R, Q6 d1 Z$ X9 `2 d
运动简图 kinematic sketch D! I/ W( |$ D( a% m# y( Q' T
运动链 kinematic chain
g) G" \/ N9 U运动失真 undercutting
+ z6 s5 A; v0 m) Q8 ^运动设计 kinematic design: }% |3 |3 K' O8 P7 R+ ^
运动周期 cycle of motion
: |- O6 z$ I# ]( ^0 V$ e# w; m运动综合 kinematic synthesis- y8 w" k4 U# ?& i, E- U. E1 G7 _
运转不均匀系数 coefficient of velocity fluctuation
U1 v* `( p* X3 q6 V7 y运动粘度 kenematic viscosity
: k' l% }2 G' v3 |载荷 load
0 {0 E" A" G' y5 e0 D5 |, v载荷 — 变形曲线 load—deformation curve
& _8 v+ K, m. _0 B载荷 — 变形图 load—deformation diagram; C1 T6 K9 j1 g0 k
窄 V 带 narrow V belt- h$ v' P' K4 E: c
毡圈密封 felt ring seal
0 Z8 Q3 u* O: k; ?展成法 generating& b4 [% ~3 z, X. |$ D* ~7 w9 S3 B
张紧力 tension
8 M! v$ }6 x9 P" Q张紧轮 tension pulley" B! s$ I* B, h, K
振动 vibration" k- c+ U. T* Y3 |9 N+ g' z, R
振动力矩 shaking couple% [0 w* {' e/ \3 t# w8 X* X& i
振动频率 frequency of vibration
6 _) {+ z/ |+ _2 g1 J8 g) l0 ?$ U振幅 amplitude of vibration
4 D0 P# M2 \" Y2 _6 x正切机构 tangent mechanism. ]- r2 R3 b# v; ~- h$ c
正向运动学 direct (forward) kinematics
1 j2 q! W5 |. _8 R( O- J2 ?正弦机构 sine generator, scotch yoke
$ L' r, G( x+ y& v) T织布机 loom, c9 Z" ?' D. f" I( W
正应力、法向应力 normal stress
C# m* S4 }; q7 R Z制动器 brake8 o% J' p# @( u$ m
直齿圆柱齿轮 spur gear
8 r+ I# \6 ?. t直齿锥齿轮 straight bevel gear
2 q+ ?3 v# c2 d# W/ ]直角三角形 right triangle5 O& e: E8 a3 L! J6 F
直角坐标操作器 Cartesian coordinate manipulator
/ ~+ O. [" O) M( p0 [: p1 I直径系数 diametral quotient( N' A8 X' `) L: T# ?" q
直径系列 diameter series
9 m* x1 n) h) S" z直廓环面蜗杆 hindley worm# }! `. Z" A0 |' N4 a0 Q
直线运动 linear motion) j$ j& ^; T- i$ \
直轴 straight shaft1 I& m- ^: M/ u, [+ a# v! I2 J+ S
质量 mass9 e4 C& C1 u7 @4 S& M, r5 D3 q
质心 center of mass
3 d- I. \, X l5 m/ f1 A* t执行构件 executive link; working link
* k& E8 V U4 w& |# t6 U质径积 mass-radius product6 n# T X0 w$ u4 V& X
智能化设计 intelligent design, ID+ U: X' A5 Q% R# p2 M
中间平面 mid-plane% |! o6 p( z% w6 E
中心距 center distance
( f% v% W) z. R3 N- V中心距变动 center distance change8 u h' l" r+ U+ e
中心轮 central gear
- l; F a' g3 p( c. |$ u% M# S1 R中径 mean diameter" h7 f& W' { ?1 c/ c# u
终止啮合点 final contact, end of contact8 F" }7 G" ?6 }7 v
周节 pitch0 x+ [& `2 j4 A" C$ u [2 x
周期性速度波动 periodic speed fluctuation" s; M1 U* i" V0 k
周转轮系 epicyclic gear train7 ~2 l3 I( r3 q0 `' }- n
肘形机构 toggle mechanism* m4 C9 v r. b3 \/ `! w% Y% d
轴 shaft; B6 C; R4 G7 F5 {7 d. n; Y
轴承盖 bearing cup3 P) o; ? `, W
轴承合金 bearing alloy
: T" t9 B. f7 _2 [% O轴承座 bearing block
, o' Z- j( K' u' Z6 |) ~9 u) j轴承高度 bearing height- z* q, Z9 x4 E1 _* n7 `$ L/ r
轴承宽度 bearing width* }# ]1 x a1 N& c5 w: W8 `. v- h! k
轴承内径 bearing bore diameter: U$ h' {5 c% e q) E
轴承寿命 bearing life* r" d, b9 v3 U" Y! j
轴承套圈 bearing ring0 M( m; ]) R, S+ n
轴承外径 bearing outside diameter% m0 y% y: A* F0 B3 q- f/ E
轴颈 journal# F" l" y( o* t
轴瓦、轴承衬 bearing bush, O0 J0 }7 i6 v q: x/ @" R
轴端挡圈 shaft end ring( J1 V {& q# e2 |0 k" K
轴环 shaft collar8 Q; v. p1 _5 z7 x8 o
轴肩 shaft shoulder. [* K( \* ~/ }
轴角 shaft angle
! W' H% u5 l ]5 i" Y轴向 axial direction9 U9 [* e! a0 K, V! h
轴向齿廓 axial tooth profile8 g5 g# Y7 l8 t9 s
轴向当量动载荷 dynamic equivalent axial load
) W* c$ X% m- ^8 v' n* N: z( A轴向当量静载荷 static equivalent axial load
5 H U9 E7 y7 G- W轴向基本额定动载荷 basic dynamic axial load rating# g: C- c$ W8 a1 N5 _& D# J' f
轴向基本额定静载荷 basic static axial load rating+ d* O' V1 _. R' a( n( v) v
轴向接触轴承 axial contact bearing
$ E N1 G, Q, {$ ]6 s3 |! M轴向平面 axial plane3 J! x2 N# _, e
轴向游隙 axial internal clearance
7 }/ h& G+ S" o轴向载荷 axial load
! l! I. A! q2 ]! w4 w轴向载荷系数 axial load factor
! ^# j- t3 n4 D c ?, }& h, R" E. b轴向分力 axial thrust load- X6 F8 R0 c4 W1 g
主动件 driving link) F! X/ Z# n8 v' ^
主动齿轮 driving gear! Y4 Q+ P: S, T3 B& f0 k$ b R% k! h
主动带轮 driving pulley" X: K. z9 [- M- u J
转动导杆机构 whitworth mechanism, p$ a4 j! U+ f! U; K, ^7 v7 V @
转动副 revolute (turning) pair% U) `+ O7 \4 P) I) \
转速 swiveling speed rotating speed s8 V5 H5 j J: N* ^
转动关节 revolute joint
6 h% g7 U% j. N* h. {9 {转轴 revolving shaft2 ^& L5 h6 [6 x4 f2 J. v
转子 rotor( H! ]7 }3 f, ]7 q# U* w
转子平衡 balance of rotor
' @+ v2 Z1 B* m, \( B装配条件 assembly condition$ j9 w6 @+ d, l: K$ ]3 G+ P! a
锥齿轮 bevel gear
5 [( Q; L5 D# ?6 i3 m% L" R( S, B锥顶 common apex of cone Q |+ Q& P& G* T3 P* z% O# Y
锥距 cone distance
: N. x/ W; p9 C( N" B+ G锥轮 bevel pulley; bevel wheel9 C9 J/ W+ n7 A/ ]# b, b
锥齿轮的当量直齿轮 equivalent spur gear of the bevel gear! L$ s0 u4 [% P: X
锥面包络圆柱蜗杆 milled helicoids worm, N M1 x$ ?: t. F% d/ X
准双曲面齿轮 hypoid gear
$ A. J+ [- ]- Z# S @4 v0 I子程序 subroutine8 A, n7 ]9 W& f/ ^0 T2 K
子机构 sub-mechanism
4 h; n( {5 d) q# d! j# L; V自动化 automation
1 [0 {1 j# p+ z, A4 }9 x自锁 self-locking
+ y& v/ N9 f8 m自锁条件 condition of self-locking/ ^9 i. I3 J9 I4 a$ f! ?2 \
自由度 degree of freedom, mobility
. `8 b: _" I2 ]+ t总重合度 total contact ratio8 M7 c' f) w4 ]* ]
总反力 resultant force
3 f; _& V8 q* w) a9 A总效率 combined efficiency; overall efficiency' g, ?( r( r) B; q0 X
组成原理 theory of constitution1 l: A. Q3 ~+ ^$ ?
组合齿形 composite tooth form! l& b: E- P/ F3 f! }. B
组合安装 stack mounting( Q: q( _) v- S( [# i) v# l
组合机构 combined mechanism9 ^2 T' D. Q3 Z# w2 ]
阻抗力 resistance! S" t1 P0 P7 s3 W4 A8 Q
最大盈亏功 maximum difference work between plus and minus work
' W# X: g* ?2 c纵向重合度 overlap contact ratio- b1 |! t# U- \7 H
纵坐标 ordinate
$ c7 i% h6 h3 _( U7 N3 }组合机构 combined mechanism
8 o$ W/ A* {$ |- u6 r! ]- P最少齿数 minimum teeth number, V: W5 N6 I+ Y4 U4 M
最小向径 minimum radius# C* z* z2 F4 [3 d% ]5 q
作用力 applied force# c0 b% D8 t* x1 U8 p$ X
坐标系 coordinate frame |
发表于 2008-2-21 11:45:15
