对称循环应力 symmetry circulating stress F% H$ J9 n2 e, R" Z# R" E' L3 D
对心滚子从动件 radial (or in-line ) roller follower4 J6 M1 K4 v: u* r
对心直动从动件 radial (or in-line ) translating follower4 n% `, s9 s* r; G% Y4 [& b N
对心移动从动件 radial reciprocating follower, |$ t4 G) \# |: @' o. `
对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism0 X3 _& J8 ^* l% I0 v& u, ?
多列轴承 multi-row bearing& x3 f( \* q1 D5 ?- G
多楔带 poly V-belt
4 w. j7 N5 Q( k4 [) y8 e# ]多项式运动规律 polynomial motion7 t, e0 Z6 ~- P* v0 v u
多质量转子 rotor with several masses6 P' f6 q4 R. X$ j( B- m! F$ o
惰轮 idle gear
2 v; W3 \& }% c4 D额定寿命 rating life7 X4 L; f" p& c* q" E: C
额定载荷 load rating- x# T4 Z& p+ P* P- r, a0 B# L( Q
II 级杆组 dyad: C& l7 J, y* B! S
发生线 generating line
/ C: X$ Y3 t* ?' V9 f5 O) e发生面 generating plane ' c7 ~0 z7 ?4 t
法面 normal plane1 e$ ~. {$ I: I% ^7 u Q
法面参数 normal parameters
1 L$ b% s3 S! y( R$ L4 m7 v3 a法面齿距 normal circular pitch6 ^; s" w' w4 O6 u+ t
法面模数 normal module
0 `8 F2 v Q/ K* j% j# C法面压力角 normal pressure angle
4 Y% m( f9 T7 x/ U/ u法向齿距 normal pitch' }, U$ q5 y, x. I8 [+ c
法向齿廓 normal tooth profile
- F. Z R9 d x7 N法向直廓蜗杆 straight sided normal worm/ Q; O( E9 q$ ~7 H
法向力 normal force
7 z1 @9 l1 t }( n7 E9 ]反馈式组合 feedback combining
, G6 [/ W) k+ C1 [2 g8 i7 H, K- d反向运动学 inverse ( or backward) kinematics
' w& F" v$ n3 C反转法 kinematic inversion
6 I# z$ W: J( S K3 r- ^; l反正切 Arctan
' E& ^* F9 {/ Z9 v/ M范成法 generating cutting6 L8 T6 k! ]6 P( i8 D
仿形法 form cutting5 @" g' N7 Y, z; z
方案设计、概念设计 concept design, CD7 V8 W$ }1 D0 ^6 W+ }3 ~% z; C
防振装置 shockproof device. c3 L1 [) n# C( H7 |2 _% k
飞轮 flywheel
' E$ }- j5 |8 N0 M- F飞轮矩 moment of flywheel* s8 s" B I. F1 D1 O$ N
非标准齿轮 nonstandard gear
0 q, a# j+ D8 f, _/ H+ c5 N非接触式密封 non-contact seal
" u9 k3 t. g$ Y非周期性速度波动 aperiodic speed fluctuation& [# M: @5 u. g4 g9 t
非圆齿轮 non-circular gear8 |4 K' X* _# K" H! X7 M
粉末合金 powder metallurgy2 y& |; L) e. S5 B0 L
分度线 reference line; standard pitch line
0 ]* m) U% R4 R$ E9 n分度圆 reference circle; standard (cutting) pitch circle
! V" U9 m0 Z1 Z" S" S分度圆柱导程角 lead angle at reference cylinder. y0 W4 `% n3 E+ b) j+ J
分度圆柱螺旋角 helix angle at reference cylinder
1 {3 r! y% D0 I, D8 K5 r% ~$ L/ f/ E分母 denominator
9 ~6 _7 ] S' ?8 |( o3 @ i分子 numerator2 U% O1 O6 U8 g5 F) E- ^; l
分度圆锥 reference cone; standard pitch cone
/ p5 C. L# b& o {" F分析法 analytical method# p# _! ]& z9 y4 _8 S; h' m* h/ J
封闭差动轮系 planetary differential
! L: @! A0 v3 \; v复合铰链 compound hinge
6 P4 i! U3 ?" z2 j( d( m& R# h复合式组合 compound combining
; n4 P9 _8 ~* b' ?0 u复合轮系 compound (or combined) gear train
2 Q. Q$ d- q2 ?! a' ?/ g复合平带 compound flat belt
' I) w7 D+ F2 N9 r N' f复合应力 combined stress: ^/ L: O4 o3 M% R# y% h% R" B
复式螺旋机构 Compound screw mechanism
7 g3 d; l3 c! v4 r$ V0 o$ V复杂机构 complex mechanism3 r% e& X. k$ b7 S1 r
杆组 Assur group W! d) `: A" F$ S
干涉 interference ( S* K1 J. v2 y
刚度系数 stiffness coefficient
$ w. B9 p+ M i+ \, _8 I' `3 M" H刚轮 rigid circular spline7 P2 K2 o2 o* v' e8 V: E
钢丝软轴 wire soft shaft' K; n2 e7 z1 v4 j5 U% H* d( h# E
刚体导引机构 body guidance mechanism4 n, W9 j0 P. l$ d2 E' ~
刚性冲击 rigid impulse (shock)1 a- W6 m7 E# P/ R
刚性转子 rigid rotor5 p7 z& _0 x6 Q& r3 K6 E7 {! Q4 ]
刚性轴承 rigid bearing
# v1 A! X4 Z4 q) x3 y' S刚性联轴器 rigid coupling( I5 h8 |+ _# y8 k: w }. Y
高度系列 height series
f& o' f: u0 k: F' b高速带 high speed belt
4 }. P, U4 |+ k1 Y7 n+ P( E8 a" m高副 higher pair& z" @9 y* a! d# H
格拉晓夫定理 Grashoff`s law/ v, W; q- F. |2 E
根切 undercutting
& t1 n0 o( ]( G4 `公称直径 nominal diameter
1 ^& a. W! x, q8 ~6 d K高度系列 height series' z6 ?0 Z7 h9 a2 p) j
功 work3 y g# z% e0 L* T7 F. @% d( V4 A
工况系数 application factor
% I4 k6 z# p O工艺设计 technological design
' D4 M1 S6 J! d工作循环图 working cycle diagram* Q% M# o2 X+ i' q! ^! l
工作机构 operation mechanism) h' I: v* F( N6 m9 I/ y4 A
工作载荷 external loads
9 n$ I# f, C2 D% a工作空间 working space, x6 ?6 Q& y/ R7 E
工作应力 working stress
M. q. J/ Y3 h( I: H工作阻力 effective resistance
) u0 O: X- t8 ^& e工作阻力矩 effective resistance moment
6 a6 S. a" ~+ @% @公法线 common normal line
) v+ J; ? d7 r1 ^# [- i/ W e% H公共约束 general constraint
6 Q1 x0 F2 }4 A公制齿轮 metric gears
, ]/ s( d% i7 @ ]; P6 J4 ?功率 power
" G' V) K6 Z. e8 p3 @2 W功能分析设计 function analyses design
0 ]5 {( R, r1 m" c9 L5 n共轭齿廓 conjugate profiles; j2 t# ^7 H* [8 A; c' V
共轭凸轮 conjugate cam) T3 j4 u+ c5 {) y
构件 link& K* J9 ~; z+ D) L. H, r
鼓风机 blower+ H X5 j: {+ s. ]5 m5 Q5 G9 p
固定构件 fixed link; frame) e R& }6 Y3 ?$ K1 h
固体润滑剂 solid lubricant1 W% I$ o. u+ s! D
关节型操作器 jointed manipulator Z5 \3 C5 n1 Y
惯性力 inertia force1 X. o$ R3 l, C; _& R
惯性力矩 moment of inertia ,shaking moment
3 v- l9 x, k& E2 m7 @/ b z惯性力平衡 balance of shaking force& E7 m# L# p5 X5 o1 t r
惯性力完全平衡 full balance of shaking force
' R/ E, k% W+ ]) ?惯性力部分平衡 partial balance of shaking force9 N2 w8 j Y9 ^; N- Q2 P9 B+ l1 F" t
惯性主矩 resultant moment of inertia! t5 n. y: D/ k- S/ |' Z, F
惯性主失 resultant vector of inertia% ~/ P$ m) o* Q! O
冠轮 crown gear
+ m& z5 ?: \) m6 H广义机构 generation mechanism
. ~- U/ o' h- M4 H# I广义坐标 generalized coordinate2 t; a% k! K+ s- M
轨迹生成 path generation
9 f( k4 e/ E* M5 P I轨迹发生器 path generator0 B6 {% ^* R$ e8 f A' Y& Q: ^
滚刀 hob
4 Y& y+ Q9 {/ ]+ {; W滚道 raceway$ U+ y/ D% F5 L7 j" P* c5 p
滚动体 rolling element
3 g5 c4 Z& `: c& x2 I滚动轴承 rolling bearing
" X/ p, Q: P5 c2 ?% o' N滚动轴承代号 rolling bearing identification code
- _* R9 ~" |) K! H0 ~滚针 needle roller
2 r, y# q! d8 U P滚针轴承 needle roller bearing
# R8 N m7 M1 B# |9 A, u滚子 roller
# E: U0 [) h; s3 p- u$ Z- x% K滚子轴承 roller bearing4 |% o& H6 ~" r X( N3 N% ~; n
滚子半径 radius of roller
# B8 `- K; ^9 c滚子从动件 roller follower
: q1 W$ C$ ^0 H! L滚子链 roller chain: F" q- ^: y) _5 N d3 M4 `
滚子链联轴器 double roller chain coupling
) U" c) X; c+ b" m滚珠丝杆 ball screw$ G. F4 N2 S4 s8 F. Z
滚柱式单向超越离合器 roller clutch
7 y% \1 c. c, X0 I& R( z过度切割 undercutting" W/ p+ C7 @! W
函数发生器 function generator / N, s% \2 \% |6 \# s+ w! }
函数生成 function generation $ c2 E6 E$ X$ e) C0 ]: l/ n) v5 q
含油轴承 oil bearing
2 A- k0 \: k/ M4 A耗油量 oil consumption
, T( r( U- F6 C% |耗油量系数 oil consumption factor
5 A5 `0 ]8 J0 }7 t$ \赫兹公式 H. Hertz equation, K/ b' ~) ~0 K M3 M8 v4 x7 }
合成弯矩 resultant bending moment. Y0 L; H, F5 R# j# f% E# N- c& f
合力 resultant force- v) s3 e+ M) J6 Z' u8 Q; }3 H, K
合力矩 resultant moment of force
6 H+ R0 \: @. T5 L1 n黑箱 black box
; X* j6 ?- m6 z! @- e横坐标 abscissa- W/ q; w- j, k0 g( P; B1 d
互换性齿轮 interchangeable gears
" R j# e# d. M" p! k花键 spline
& x" z, p( d- I3 V, u滑键、导键 feather key( l7 w5 C& n q. y6 F( R2 H+ O* R
滑动轴承 sliding bearing' j4 v2 C9 @: k- ^1 m
滑动率 sliding ratio
# D0 R1 C9 h) I( X7 e5 O6 S7 x滑块 slider8 {- b$ {& a- f- I% i9 A$ _
环面蜗杆 toroid helicoids worm {" ^& t5 K$ @- y/ }! O
环形弹簧 annular spring5 v3 N0 h$ r. T) B/ Q. B
缓冲装置 shocks; shock-absorber
5 z/ h7 I: S3 ^% q ~, y灰铸铁 grey cast iron
0 y, G( d8 l$ E. k! B回程 return+ p" q! F# g+ N* Z
回转体平衡 balance of rotors
* W( }! E0 V" {混合轮系 compound gear train
; x; A4 e' Q7 D, ~% l积分 integrate
4 @) ]7 X5 x: X+ j6 q {机电一体化系统设计 mechanical-electrical integration system design
9 J1 B3 v {; P' B' _机构 mechanism
4 K% `6 W$ z3 b E" _* |机构分析 analysis of mechanism
6 e" ~0 K' h$ p" v机构平衡 balance of mechanism! L$ T9 X1 N# c# b5 c: Z: D
机构学 mechanism* o4 o/ U9 N- Z$ f9 J# t
机构运动设计 kinematic design of mechanism/ d. I) i4 g" c0 [# E
机构运动简图 kinematic sketch of mechanism
; R! A r* Y }. R9 s; N" ]5 O7 O机构综合 synthesis of mechanism7 p( `5 x2 C/ @6 T2 ^' k
机构组成 constitution of mechanism A- u% I, [/ s$ L5 V5 Z
机架 frame, fixed link
4 J1 B3 n1 v! \6 u机架变换 kinematic inversion, i, |3 c: t$ g& q: U8 |
机器 machine+ j, u! B5 W/ u, y0 J9 b
机器人 robot- I3 Y; _3 `! b
机器人操作器 manipulator* H/ z3 Q# n7 ?: C0 ]. R" _ W$ q+ |
机器人学 robotics" J) l* A) J% A6 E
技术过程 technique process& ^$ c) C# L V- N; v$ {
技术经济评价 technical and economic evaluation
. Q7 k& W# ?" _1 n! k# x% w5 R+ [技术系统 technique system; o( Z( X8 r; s) s: E
机械 machinery
; A$ g% J* ^! N5 \$ V6 `机械创新设计 mechanical creation design, MCD7 w+ D* ^. [5 j7 f. |
机械系统设计 mechanical system design, MSD
" G- W! }* ^+ D9 W机械动力分析 dynamic analysis of machinery5 |7 `* `/ }% c9 I3 Z8 D
机械动力设计 dynamic design of machinery* a" H% l: ] w2 F, O
机械动力学 dynamics of machinery
- I0 }/ @% J7 k8 Z机械的现代设计 modern machine design
4 A8 z0 t$ D$ B+ ^' x机械系统 mechanical system; n; l& m3 C6 {- z
机械利益 mechanical advantage: L. u% P2 r& l+ n5 V) [+ n
机械平衡 balance of machinery
* T' K% D; h( r机械手 manipulator+ a1 {# F( N' m g9 j( Y8 Z% d
机械设计 machine design; mechanical design( L% e9 E9 e+ _! r
机械特性 mechanical behavior/ G) U: m Z6 t, C" J6 y% C
机械调速 mechanical speed governors" `: g0 L) v' p1 ^
机械效率 mechanical efficiency
) A" o B8 ~# g6 v' a9 B6 E机械原理 theory of machines and mechanisms9 k7 q0 b9 T e
机械运转不均匀系数 coefficient of speed fluctuation- U' F$ z3 ?: I) Y& F
机械无级变速 mechanical stepless speed changes( l) M% o. y- P) `3 F
基础机构 fundamental mechanism3 y! ^ G& k6 b2 v
基本额定寿命 basic rating life
+ v/ U3 j" w" r9 v, H; q基于实例设计 case-based design,CBD
, d7 ^( }! p0 r基圆 base circle) u5 H# `% l. x% D1 Q& n
基圆半径 radius of base circle* [4 q$ _, E0 _9 T ^
基圆齿距 base pitch' }" O3 n4 s0 f$ n* w
基圆压力角 pressure angle of base circle
0 \5 U% @! ^- [' b+ f0 z基圆柱 base cylinder
( ]) J3 v( h+ C+ Q* V/ S基圆锥 base cone4 t0 g6 _, q$ b8 P( J
急回机构 quick-return mechanism( f5 n, N& P7 r8 D0 A! y+ O
急回特性 quick-return characteristics
% u' E J3 `* V. a急回系数 advance-to return-time ratio
) ^6 G0 C) N+ W! m急回运动 quick-return motion/ u- }0 E- M* R0 I
棘轮 ratchet
% t9 H! F5 ~1 X% y# k2 r0 m9 k& P棘轮机构 ratchet mechanism
( t/ J+ D7 n: {棘爪 pawl
v7 f( J H Q- Y. ~: g极限位置 extreme (or limiting) position
- p9 M( V; E& g2 w" ?: B$ X6 f极位夹角 crank angle between extreme (or limiting) positions
9 p5 O* s+ C3 B( E计算机辅助设计 computer aided design, CAD9 F$ ?* p/ W/ u+ _% x
计算机辅助制造 computer aided manufacturing, CAM
: I9 L5 A7 T2 I8 N计算机集成制造系统 computer integrated manufacturing system, CIMS
4 Y$ V& J; _$ f* }. P; z) {! r2 v计算力矩 factored moment; calculation moment
( B% R, X( O* c计算弯矩 calculated bending moment/ L; q( c/ p+ l. \
加权系数 weighting efficient
& `- C: s! [0 ~% }. U' r* R加速度 acceleration
8 a5 G: ]$ T6 f1 o- v( V' K加速度分析 acceleration analysis
9 {3 q: X2 I# T加速度曲线 acceleration diagram
; @' F/ q7 P6 k5 p, \* M7 D* Q尖点 pointing; cusp
1 I1 K: g- Q u& n& q# @# B尖底从动件 knife-edge follower( s0 P( E) Z8 K* `7 p- v, x1 V
间隙 backlash
5 E4 X, w; i6 O. I0 M" m' t+ K) S; H间歇运动机构 intermittent motion mechanism/ m6 P% |( V( s& [, b- V
减速比 reduction ratio# l9 i; e1 j/ P& b
减速齿轮、减速装置 reduction gear
" `8 _; t7 d ^% V减速器 speed reducer
, k/ H+ _! A* h减摩性 anti-friction quality
2 p" D8 ]4 ^9 m! L渐开螺旋面 involute helicoid. n" \! x3 A8 J. Z# ~) k7 @
渐开线 involute) k% e7 Y( [1 C) |9 o4 Q! c) X" B1 m
渐开线齿廓 involute profile6 S2 Y0 j5 C& E7 I4 E
渐开线齿轮 involute gear
% g% @( Y) i6 S/ B" J' U渐开线发生线 generating line of involute
8 g. t& {$ ?0 h: U1 P. e渐开线方程 involute equation9 W) l! T8 ]5 O6 f, Z9 w$ A
渐开线函数 involute function( @% [8 ~) C" O+ B; `; q( x8 D
渐开线蜗杆 involute worm
5 @3 ?, Z2 C3 q, d4 y+ @渐开线压力角 pressure angle of involute5 v3 g; l' g9 M1 A
渐开线花键 involute spline
; `5 w9 `5 C; i5 t) K9 m简谐运动 simple harmonic motion2 y. g( U) X% B% Q
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发表于 2008-2-21 11:37:30
