圆带 round belt
8 j# O; w" F# T圆带传动 round belt drive! L; P, C; x r
圆弧齿厚 circular thickness
6 x6 b, K% X$ Y6 h, e圆弧圆柱蜗杆 hollow flank worm
: J/ \; m( |" y$ V圆角半径 fillet radius
/ k; X. o4 P, @6 z, I$ _ A圆盘摩擦离合器 disc friction clutch5 C, {. m$ n2 h7 _4 p5 R8 F3 w
圆盘制动器 disc brake9 ]: j- _& p6 ]( _/ y4 y* }7 T- k8 y
原动机 prime mover+ ~ S) b$ u( R: o5 ^
原始机构 original mechanism4 V& ]2 i' ?4 j! t3 h
圆形齿轮 circular gear
7 E2 c# d8 b `" F# U圆柱滚子 cylindrical roller4 R% k8 e9 O, M" K0 g' A
圆柱滚子轴承 cylindrical roller bearing
5 Z- i7 F% g" u8 O; e; T9 l+ Z圆柱副 cylindric pair
. ?% }9 J; V& n3 n) i( f. v圆柱式凸轮步进运动机构 barrel (cylindric) cam
1 ], n4 l, k0 o3 z6 Y5 Z1 `圆柱螺旋拉伸弹簧 cylindroid helical-coil extension spring2 d* [5 O- x7 s( s$ N# C' c' I. b
圆柱螺旋扭转弹簧 cylindroid helical-coil torsion spring
4 S& d3 X. J# w5 Q2 G% V圆柱螺旋压缩弹簧 cylindroid helical-coil compression spring
/ x2 C0 w8 m* Z1 f圆柱凸轮 cylindrical cam( q1 A, j- g. [2 z2 y/ z; A" N2 Y O
圆柱蜗杆 cylindrical worm
# y7 h! }6 ~+ ?9 D9 S- [; r6 R圆柱坐标操作器 cylindrical coordinate manipulator# {/ y8 m8 ?/ w) q( B8 v3 y
圆锥螺旋扭转弹簧 conoid helical-coil compression spring5 `, u& j3 H5 ^
圆锥滚子 tapered roller
: S7 |& V7 V( q: a! b圆锥滚子轴承 tapered roller bearing s. |+ y3 A3 D7 }: W
圆锥齿轮机构 bevel gears
5 B" v! ?8 ]4 q圆锥角 cone angle. L6 u0 ?" D0 H; Z& ]) \" t
原动件 driving link
! @3 [/ M% q* @/ N约束 constraint
7 i" U0 P* ]" t8 J约束条件 constraint condition0 x( Z5 A8 Y9 f
约束反力 constraining force
~9 B7 f7 |9 \% p e跃度 jerk
* d* n8 {3 d8 v E+ u4 s. C跃度曲线 jerk diagram- Q( n3 h7 F4 v+ C8 z
运动倒置 kinematic inversion4 \( d7 d/ c2 @! \1 e% B1 R
运动方案设计 kinematic precept design7 Q7 E7 k2 O" w1 i) g
运动分析 kinematic analysis
" q6 {* j7 i. u v/ U( B+ J U运动副 kinematic pair
. p3 x2 s0 z% o# z. N$ A运动构件 moving link) g# W+ ?% w4 ]! `# z2 t
运动简图 kinematic sketch
- b% I& w) m* F V1 G: s运动链 kinematic chain
~# p& a3 G) I' f; }$ Z7 _运动失真 undercutting
" p4 ?: i- ]5 T0 S% [. o1 F: |运动设计 kinematic design
9 N. d% x0 D0 ]6 ]8 r+ G运动周期 cycle of motion5 ?" F W/ K2 W5 z8 t9 `3 Q
运动综合 kinematic synthesis0 b5 ~6 u% t+ `# o
运转不均匀系数 coefficient of velocity fluctuation. R9 Z1 g* @2 S& x2 g/ h9 M
运动粘度 kenematic viscosity+ R4 w- E8 `' h$ P
载荷 load
1 R. N; \+ z* u) B' q+ b$ K a载荷 — 变形曲线 load—deformation curve
' y- t! R" m. q# ^载荷 — 变形图 load—deformation diagram @7 P5 b8 {. } b
窄 V 带 narrow V belt5 ^2 Y7 b* n2 ], ^/ l& B5 @5 R3 [
毡圈密封 felt ring seal
$ V( |; J% c3 ~9 v$ c. a3 w6 n展成法 generating5 e, M5 a1 [& ?+ T' K6 X& E
张紧力 tension
& c0 l; v! q, w* T张紧轮 tension pulley# a, j3 O; q0 o
振动 vibration& I6 r2 D, ~9 ^7 S
振动力矩 shaking couple1 P2 _, X! O7 d) }9 h4 h
振动频率 frequency of vibration
1 Y# a, N, c. d( L# F6 W振幅 amplitude of vibration
. p7 ^0 {3 v2 F C正切机构 tangent mechanism# C7 u! {. B- T% y
正向运动学 direct (forward) kinematics
, N" J" W, _8 s9 c$ \# J( W. a2 d正弦机构 sine generator, scotch yoke8 ]. J4 W- L9 D' n/ E6 }$ x. j
织布机 loom; a& i. X$ M% E0 F
正应力、法向应力 normal stress
: S8 S, _* s# R/ Q制动器 brake
/ f& a k* Q8 N, Q, a直齿圆柱齿轮 spur gear- J+ W; H+ E o, M: P9 g( v. V( N3 G
直齿锥齿轮 straight bevel gear
- y! M6 D& F3 s$ W" w直角三角形 right triangle+ l: R3 o& O& [ g C1 b% K
直角坐标操作器 Cartesian coordinate manipulator6 C) R# L) i. h6 S6 d
直径系数 diametral quotient. n; f* I( _2 u, m* V9 r7 K i$ E; W
直径系列 diameter series; a. J0 `; v" T5 U) G0 a( p
直廓环面蜗杆 hindley worm
! N6 I, }5 x+ h* d" O直线运动 linear motion
6 w9 u8 |6 o6 {9 r( J8 T直轴 straight shaft/ l% c7 M6 @5 X; x9 a
质量 mass
* S1 [+ h8 T+ k0 b8 v( K质心 center of mass- e* \ T- W4 U" @+ o& G
执行构件 executive link; working link
0 W; D5 S- Q$ v4 }4 f质径积 mass-radius product
3 n( j9 D) X4 I; R4 p9 q) a智能化设计 intelligent design, ID
( X: [4 {+ W4 H1 r中间平面 mid-plane2 m4 V# o" v+ t9 \ }
中心距 center distance9 T9 P8 ~7 ^$ x
中心距变动 center distance change
2 O& X& W3 i3 P5 v* ?5 M# M+ u- Q中心轮 central gear
5 o( q. {- j# k9 [中径 mean diameter2 ^" X. @! \1 Q0 R
终止啮合点 final contact, end of contact* }2 s4 |( n: w1 _/ `9 y7 L
周节 pitch% I* J6 C1 I( Y F$ O. f
周期性速度波动 periodic speed fluctuation( \$ d6 _6 q, p9 n! I
周转轮系 epicyclic gear train
$ ]3 P( Q) n! R肘形机构 toggle mechanism
6 ^. t' Z) Q4 X$ n: c5 n轴 shaft
0 i8 R) p' V4 b$ k0 t5 v0 v2 b轴承盖 bearing cup& s; n" c# ^/ d6 {5 f
轴承合金 bearing alloy. Q# b; M& ?* g
轴承座 bearing block" i% I6 N. ^4 F% W
轴承高度 bearing height
, o* q7 M# Q G/ H& `& A* K轴承宽度 bearing width! V- M+ t& G- M0 f b
轴承内径 bearing bore diameter! S/ ?, l. t7 r
轴承寿命 bearing life
2 m0 s* v& l/ v) o/ U轴承套圈 bearing ring5 t1 ~4 E9 R- e
轴承外径 bearing outside diameter
) a, e0 M+ o& z, Z轴颈 journal# t, `1 [1 W. S ?, ^
轴瓦、轴承衬 bearing bush
1 @) z8 R b3 A# v: ]轴端挡圈 shaft end ring
, j, P2 D0 a% _$ o2 Q s轴环 shaft collar1 B1 \+ X4 n8 V3 e8 h& I! C0 I: d/ u
轴肩 shaft shoulder
; J% c$ r! k% v; z轴角 shaft angle6 P c3 `1 `) s7 N
轴向 axial direction+ o/ U3 N2 N) L0 x$ b X* T3 O
轴向齿廓 axial tooth profile
?6 ~+ }& e' F7 v0 f4 K轴向当量动载荷 dynamic equivalent axial load2 ~4 \3 M2 I) J. Y1 U! b
轴向当量静载荷 static equivalent axial load/ V8 R4 a0 s$ R! e! G
轴向基本额定动载荷 basic dynamic axial load rating
3 }1 A) D* X1 i; C# D: E轴向基本额定静载荷 basic static axial load rating. T0 R+ y3 H; T z! }( r7 u. Z# m
轴向接触轴承 axial contact bearing0 d2 s: _; P) [& M( ^
轴向平面 axial plane4 q9 U3 k6 g6 P) A7 r7 H- ~
轴向游隙 axial internal clearance; w C6 J% |& ?) v8 U
轴向载荷 axial load
; k0 Q4 y5 N' m# z轴向载荷系数 axial load factor0 Y7 U9 L9 b* `
轴向分力 axial thrust load- ]7 b6 t2 Y$ A+ q* G, r$ D' ~
主动件 driving link+ [6 ~6 m P% u; y1 a
主动齿轮 driving gear
/ Y) n: s0 j6 `, v# Q, A' `6 U主动带轮 driving pulley+ u4 }1 p. q6 I% I" B) J% |- a
转动导杆机构 whitworth mechanism% h. Z* f& ^9 l1 N
转动副 revolute (turning) pair
Y" |" Q; p( n. T) w; F5 e/ f) c转速 swiveling speed rotating speed
0 S, n$ p4 O ?. N& |转动关节 revolute joint
0 v1 A, M' K4 A6 ~: @4 e, M转轴 revolving shaft
1 f# [0 ]) u Y) e2 u6 b转子 rotor
( D3 r/ Y( ^5 g" o转子平衡 balance of rotor
& J, R8 K7 J& \: u( O6 v装配条件 assembly condition
+ m) ?2 S, x$ F1 U# ]7 ]6 n锥齿轮 bevel gear
' Z. i: n$ t% J( `, \4 Z锥顶 common apex of cone
6 z4 g4 D" ~$ D. y* G7 I/ B' y锥距 cone distance
# Z) V- z6 w4 A3 `. @6 F- A锥轮 bevel pulley; bevel wheel/ {' M+ v% ?; }* x9 r. ~
锥齿轮的当量直齿轮 equivalent spur gear of the bevel gear; u& Q6 h# F6 ]6 H+ [
锥面包络圆柱蜗杆 milled helicoids worm
, v4 k; \% {. P% E准双曲面齿轮 hypoid gear$ v5 N6 @7 c, ^! h& Q
子程序 subroutine0 C( T% ?( n; h$ n% r# |
子机构 sub-mechanism; Y/ a/ Z: E, V/ U0 D/ {1 T( l
自动化 automation/ W! l; d* W1 J2 w: n+ D, T0 r- J
自锁 self-locking- b0 j; M! D& O/ s( B. A+ m$ B J
自锁条件 condition of self-locking
1 @6 [& S8 K& A S$ U) T+ o自由度 degree of freedom, mobility
& b* j. o& n, i; l2 d% M3 z* J总重合度 total contact ratio
% ]& |2 x# U4 u! r Q2 |总反力 resultant force
+ D2 b( }, z$ {) D) G4 |( ?总效率 combined efficiency; overall efficiency2 ?; k1 Y& S( F0 ?
组成原理 theory of constitution
) ?$ S9 c, J* }0 O2 p; ]5 Y组合齿形 composite tooth form
$ _7 _8 x( G& [# h6 Q( q组合安装 stack mounting; g; H& ~0 S8 p% g
组合机构 combined mechanism
i) w6 C3 z0 R, x, t阻抗力 resistance9 m i" x9 e$ O4 b0 b# G
最大盈亏功 maximum difference work between plus and minus work
, d. i% e9 M& d1 c6 x% n0 i纵向重合度 overlap contact ratio
0 G2 L4 q8 N& Y' E7 k" R, }. Z3 i- @* v纵坐标 ordinate5 h6 |& Z) m) g* v/ B0 V, r5 G
组合机构 combined mechanism) E6 m5 h2 C* i8 X5 v) d# M: x
最少齿数 minimum teeth number
9 [) y. R/ }1 a8 W最小向径 minimum radius
5 i0 W: @& w7 U7 V; {作用力 applied force
' U0 x4 I/ K4 {7 ]$ ?9 F坐标系 coordinate frame |
发表于 2008-2-21 11:45:15
