对称循环应力 symmetry circulating stress/ B$ V3 k! C3 ?2 C1 L3 D7 j
对心滚子从动件 radial (or in-line ) roller follower
8 D* E, K4 g5 w对心直动从动件 radial (or in-line ) translating follower* P! X+ T# `8 i" H1 \5 |
对心移动从动件 radial reciprocating follower( j) a# b7 U6 \3 P
对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism; m8 H# a. }1 d' r3 t% g9 k
多列轴承 multi-row bearing
- D" {( Q3 I9 @! \多楔带 poly V-belt
) L& y! a! |4 c# }4 B# L5 }3 _6 S多项式运动规律 polynomial motion4 R: M1 e. ~" ?7 w9 `* V
多质量转子 rotor with several masses
, j I2 |# b# }0 W& k; B惰轮 idle gear9 @. _8 K, Y" i) Y
额定寿命 rating life
/ {& M% K3 y6 ?1 n3 s额定载荷 load rating
% }: E& a& ~1 ]# o/ U/ VII 级杆组 dyad
) j- z5 H' f$ O发生线 generating line
! g7 H" O: E+ j M! c发生面 generating plane + t+ p+ V. b$ b6 o
法面 normal plane+ I$ h$ d$ @, n. T, q) J! t& Z& h
法面参数 normal parameters
, Z" `/ Z2 o) | I法面齿距 normal circular pitch7 A' f5 L: x6 L0 \1 R/ u
法面模数 normal module
, X: k$ f+ S0 U2 w" H7 l法面压力角 normal pressure angle
5 S7 A) J- _. f( Q法向齿距 normal pitch
2 s% T* f# S7 [6 Y$ y& _" [法向齿廓 normal tooth profile1 U- U7 F4 k7 c: s. N1 V2 K4 x+ r# }
法向直廓蜗杆 straight sided normal worm! W' ?+ _! I: x5 |
法向力 normal force
h7 |% R% Z8 i. I" j/ @* l' _反馈式组合 feedback combining
; n- F5 d3 i- H$ I5 n% A0 z1 z反向运动学 inverse ( or backward) kinematics9 T# u# r! C5 ^# Y$ O
反转法 kinematic inversion& C5 c( k2 P9 A8 H$ g
反正切 Arctan( `. b8 M1 h7 D- S2 m
范成法 generating cutting% R2 e/ T/ p8 Q) E; S- S
仿形法 form cutting) G, S( L. ^# `
方案设计、概念设计 concept design, CD' O8 R8 D) p/ {' z1 Y) u7 C
防振装置 shockproof device* k H2 u" g6 {6 M6 m
飞轮 flywheel
5 d' v0 A! ]* K9 }7 p' u/ k7 w飞轮矩 moment of flywheel
* `; j5 m6 ~% f% F非标准齿轮 nonstandard gear$ p1 X& \0 N, V4 c3 Y L
非接触式密封 non-contact seal
- u2 i4 S9 x" g' K8 y& q {1 R非周期性速度波动 aperiodic speed fluctuation
h* @; R$ v# Z2 w$ E/ f$ j非圆齿轮 non-circular gear: J, b9 g: T) @5 }& b4 N8 o# u
粉末合金 powder metallurgy4 C, N7 j# |! g, y9 e& }
分度线 reference line; standard pitch line
y$ p' o- p, k! s; ]9 `分度圆 reference circle; standard (cutting) pitch circle0 B$ m3 Z* \: c) I6 J X4 ]& P3 `
分度圆柱导程角 lead angle at reference cylinder" G w0 G9 K/ W& n: ]4 M
分度圆柱螺旋角 helix angle at reference cylinder
& i. L+ `+ V( i% }分母 denominator* N, t" B4 ]* C7 ~0 y" d( @ }+ a
分子 numerator
1 z- N" E) W0 g7 u分度圆锥 reference cone; standard pitch cone
( c {- T# \" _# N! T' T4 S分析法 analytical method4 c1 s# m4 O7 R- R, U9 h
封闭差动轮系 planetary differential! c/ x' J% _* t$ _! H7 e1 q U
复合铰链 compound hinge. Z8 z: x, x' {# z& g: M
复合式组合 compound combining
2 D& x9 k# v" c0 k复合轮系 compound (or combined) gear train
# g8 |8 i9 k' O复合平带 compound flat belt: [ M$ o3 P( n( G( v8 U
复合应力 combined stress
& P' S5 [7 h' K. g& j$ x复式螺旋机构 Compound screw mechanism& N: x$ [$ B& V4 V m6 y# d" H3 m# n
复杂机构 complex mechanism" j, m/ e! u+ P# G/ i9 O
杆组 Assur group 6 F7 M# i/ {( W$ r0 x$ L {6 p
干涉 interference
; E0 `: q8 Z1 A; ~, u; u: C刚度系数 stiffness coefficient$ i; ]8 A" c7 E
刚轮 rigid circular spline* t4 l) \1 K- H! y
钢丝软轴 wire soft shaft
5 Y4 \" @; h4 w' [刚体导引机构 body guidance mechanism
: @, Y! l3 i; I; E刚性冲击 rigid impulse (shock)
. ~/ ?0 g" H4 F# k) i刚性转子 rigid rotor
: O K! o1 \; |1 e, X* N" K4 Z5 g刚性轴承 rigid bearing
5 x5 E/ f6 [ ?刚性联轴器 rigid coupling- v# O& V7 O' c' l0 Y1 {- {
高度系列 height series
/ e* q q8 N) `- H5 Y, l高速带 high speed belt
4 W: z9 {3 b5 m( T4 a高副 higher pair
5 Y. R* Z' |% M, X: Z格拉晓夫定理 Grashoff`s law K, u1 `0 y k$ s! q, `1 Y
根切 undercutting1 F: i+ g) A9 C
公称直径 nominal diameter' `& O3 W' c7 g5 m1 R
高度系列 height series- l# P) q; I, c( K$ q
功 work
8 L$ w" M D7 Y* x工况系数 application factor
4 N! U: h# A8 Q4 r( X2 E6 }工艺设计 technological design
% o& }6 H4 t# b7 l0 B& }8 ~工作循环图 working cycle diagram
) R/ h* N L8 m% G2 w工作机构 operation mechanism
% ^' k: ?# f" r: x _3 ], D工作载荷 external loads
. E- Y! s0 u K工作空间 working space/ f1 t; p: K3 y$ ]# u) B9 A7 I
工作应力 working stress; O2 f% n% x. y8 t( E
工作阻力 effective resistance/ P7 V. i/ N) u {" P2 U3 D c/ Q
工作阻力矩 effective resistance moment
c& l# E" [+ a* f u/ O0 \公法线 common normal line- h f" e6 n. V2 n3 y
公共约束 general constraint) ^) O. p" P, T$ s
公制齿轮 metric gears
6 r: E' a8 A/ M4 r5 Z& L k功率 power9 r3 s$ I/ h! k! j
功能分析设计 function analyses design
2 ~0 @8 {4 d! _: X0 @共轭齿廓 conjugate profiles
2 E* x2 E$ m3 H8 G2 f; a0 ?共轭凸轮 conjugate cam
$ w' d7 ]/ Q2 E7 T! ~构件 link. ^6 E' ?7 x7 P6 B8 _ P4 v
鼓风机 blower
2 x; J# _$ b! ~- z/ i4 i1 c) n# ~1 J固定构件 fixed link; frame8 Y6 E, M3 Q) v6 w m
固体润滑剂 solid lubricant* r6 y2 @2 g$ |" r
关节型操作器 jointed manipulator! ?5 b4 G+ w$ q: k" A* K
惯性力 inertia force y$ Z- O7 ?" u R5 ?
惯性力矩 moment of inertia ,shaking moment+ x+ r3 ^8 Y3 s) C4 c0 \) D
惯性力平衡 balance of shaking force
* o$ l6 h8 t/ D/ U$ n惯性力完全平衡 full balance of shaking force
( Y- s+ j4 q. b! @/ E惯性力部分平衡 partial balance of shaking force
4 p; M( ]/ R& V9 P惯性主矩 resultant moment of inertia, _' s% O, {5 I8 t
惯性主失 resultant vector of inertia
7 ?( W* p% V3 R3 L; ^$ w) V冠轮 crown gear( Z$ P* N8 j1 E7 w( j% A' l7 i
广义机构 generation mechanism. N9 j! F# F' P, _1 f9 o- H
广义坐标 generalized coordinate2 W/ J( Q& ~# G- I
轨迹生成 path generation8 Q7 e$ y7 ^2 ^5 |
轨迹发生器 path generator4 I+ b) `+ C: K; K
滚刀 hob3 u. j) `" H5 T, }: E
滚道 raceway
* k5 h/ a9 M1 j* _/ y& }滚动体 rolling element. t1 ~' x6 z8 y* q/ G! l
滚动轴承 rolling bearing: i4 @' J/ b# V4 Y! a9 D; t( }
滚动轴承代号 rolling bearing identification code5 @8 c/ s* v+ t3 s- s3 ^1 b) N
滚针 needle roller
+ ^+ z8 s5 _: ]滚针轴承 needle roller bearing/ _3 C9 j4 O! H$ v7 g9 H
滚子 roller9 K+ A) e2 Y" n' N3 B
滚子轴承 roller bearing
0 T7 ^9 ~5 v" q' }: p4 i滚子半径 radius of roller
* x+ M9 ~, _& h滚子从动件 roller follower' N F% y' _6 V J* x) H3 V
滚子链 roller chain
7 t) y! c" u# \1 j: \' c5 W滚子链联轴器 double roller chain coupling( a0 d" Q! i' C
滚珠丝杆 ball screw
- N) P1 t& B0 S [滚柱式单向超越离合器 roller clutch
2 M. Y2 w8 {- B+ e7 U5 K. W. g k过度切割 undercutting8 K9 D; Q& H* R/ H
函数发生器 function generator
" a& ^3 a |) [( H函数生成 function generation
* l8 G3 U3 ~ u7 ?, J. h含油轴承 oil bearing! I* q4 M- C9 J4 a& [/ t
耗油量 oil consumption
- P1 p9 [. i9 T$ ]7 H* m; a耗油量系数 oil consumption factor
; w" b- w8 V, f4 D/ h) z+ Q# I赫兹公式 H. Hertz equation/ }# Z( }2 M4 i- P, H! `4 E. B
合成弯矩 resultant bending moment" k8 O* M$ v+ _8 y. o
合力 resultant force
; g. t+ ?: O- f合力矩 resultant moment of force |2 `, \: f2 h5 k4 i- D
黑箱 black box2 |0 d5 W& |, `- v" S7 s
横坐标 abscissa* c% o3 B: ]6 }# _2 D& u0 C
互换性齿轮 interchangeable gears$ n0 m, ~- B9 i, Z: ~% p2 O( @* E
花键 spline; N4 V+ { k9 f$ z
滑键、导键 feather key
% a" Q+ Q1 C8 P5 C. H滑动轴承 sliding bearing
: u1 |+ _3 e$ l滑动率 sliding ratio" n# J2 Q2 ?( ~
滑块 slider0 K. p# ]" T: a1 l! m6 G y& @' C% b( v
环面蜗杆 toroid helicoids worm
+ y$ E7 W R |4 }) \+ F环形弹簧 annular spring
% _8 k/ j7 w. r& Y缓冲装置 shocks; shock-absorber5 Q" i: }" B' X' ]2 |) @
灰铸铁 grey cast iron
3 V- |) k+ T% f z r( H6 o回程 return1 Y, a! h0 j& U# n: G
回转体平衡 balance of rotors- y2 V0 g( ]& H1 Q" W4 w9 X! }# \
混合轮系 compound gear train
6 A; I5 ^% |: @" y" L9 A& k6 B积分 integrate / ]( n5 r2 }, w( s, l7 W* a
机电一体化系统设计 mechanical-electrical integration system design % `/ Z0 w8 X9 W' i( {7 Y
机构 mechanism" U* O: Y) Y. M, J( b
机构分析 analysis of mechanism
% e9 g0 r+ d/ n8 {9 Y1 R5 Q机构平衡 balance of mechanism
+ T7 n) L, X4 J+ p2 ^+ \机构学 mechanism
7 k2 g& [1 b. H$ {机构运动设计 kinematic design of mechanism
$ b. g, [0 ~9 X) p: p' d机构运动简图 kinematic sketch of mechanism0 g; q2 K' X5 O2 c# j* d* }! I
机构综合 synthesis of mechanism
: X2 q% ~/ [8 f# K5 M& j机构组成 constitution of mechanism
( K; E/ ?+ u/ R5 U! f机架 frame, fixed link8 h" f0 r$ X: I
机架变换 kinematic inversion) Y, C; G9 M$ M' @& K, b
机器 machine, ?1 \: P8 x s" i5 p4 v
机器人 robot
# U) K6 U' Y s# M& Z& |机器人操作器 manipulator
* z) j8 }& J% D: _7 C" z机器人学 robotics
S+ N9 c; ]8 A4 C技术过程 technique process! k' f( h9 E3 L3 [7 v
技术经济评价 technical and economic evaluation e! d# ?; f0 \+ B
技术系统 technique system: l; Q$ ?- I7 t: A
机械 machinery* Y6 `- a, }# e8 o1 X, g
机械创新设计 mechanical creation design, MCD
) z9 ?3 ?. p6 k" z机械系统设计 mechanical system design, MSD o- L* w2 A9 {/ {( e" ?6 I1 }4 a
机械动力分析 dynamic analysis of machinery& }3 x2 C6 r/ J+ s+ T
机械动力设计 dynamic design of machinery
7 l: g) a4 ~$ `; @0 i机械动力学 dynamics of machinery- N# l8 K+ ^; S. N, ~9 F- `
机械的现代设计 modern machine design
5 \. B* Q+ k! _2 f. q3 {- [7 [机械系统 mechanical system
4 q* ~5 b6 H- n9 k9 t" k3 s n机械利益 mechanical advantage# X3 C5 `# r* G6 ~$ K
机械平衡 balance of machinery3 S- m: Y% x( u. M4 U5 d8 m
机械手 manipulator
4 x8 ]6 X1 ]# y+ S/ A机械设计 machine design; mechanical design2 y+ O' G9 M% z6 Q. ~" l. W
机械特性 mechanical behavior" @, a& t* R L( G
机械调速 mechanical speed governors/ O5 A" j: ~, E- o6 o
机械效率 mechanical efficiency
3 Z5 z* {4 W Y4 J- ?机械原理 theory of machines and mechanisms
3 {, R5 m" | {7 @机械运转不均匀系数 coefficient of speed fluctuation
. g% t# a T& u& q* l& e机械无级变速 mechanical stepless speed changes
0 x. a- d+ R4 C1 c1 w基础机构 fundamental mechanism
9 | l8 G6 K+ B' b8 G基本额定寿命 basic rating life
9 K' V7 o& s1 U- f) B# o基于实例设计 case-based design,CBD3 G. |* x1 u A$ ]* L
基圆 base circle
. n& |! o$ S; z5 k) l; |基圆半径 radius of base circle
. [' Z* T0 s* l基圆齿距 base pitch/ x& d6 x4 s' K+ x5 T* j! q
基圆压力角 pressure angle of base circle
, [7 d% Y" x3 o+ T: s) a基圆柱 base cylinder* H7 ]! E- p; z! V- Y0 D
基圆锥 base cone8 `( m, i/ X' I" i- `3 e/ @0 a
急回机构 quick-return mechanism
+ b& [# @) r' d: ~急回特性 quick-return characteristics
0 z* O$ a2 {8 B2 ~急回系数 advance-to return-time ratio
3 }; J. r' j5 d+ A; V+ P) E急回运动 quick-return motion
5 @* K6 J( }& \9 ?' h' s# K棘轮 ratchet
; s, V3 T/ e3 ?2 a& k棘轮机构 ratchet mechanism
l# Q8 _8 F* _8 S5 ^6 s棘爪 pawl
1 ?% K9 q+ d$ f3 h8 ]& Y极限位置 extreme (or limiting) position2 V4 i/ g% A& k
极位夹角 crank angle between extreme (or limiting) positions
! I. W7 N; p% S! ]! n计算机辅助设计 computer aided design, CAD; W2 v. Y2 k( j( j( Y! T6 w
计算机辅助制造 computer aided manufacturing, CAM
' ~7 ]4 P" Z( p& m/ W计算机集成制造系统 computer integrated manufacturing system, CIMS
1 Z' ]# c. d5 _& K$ f, r$ }5 \计算力矩 factored moment; calculation moment& J! ?+ @% I) L
计算弯矩 calculated bending moment
2 E" o; |/ s `; H: p5 x, }加权系数 weighting efficient
& i4 W; U6 x7 K! N- _' r加速度 acceleration! i, Q$ F; D, a0 R7 ~ G/ A
加速度分析 acceleration analysis. Q v# }) P, x. k" K4 Y# d1 n
加速度曲线 acceleration diagram: N/ O, K+ t3 W1 {" u8 N
尖点 pointing; cusp* v6 @2 G0 }+ g, j' |/ P2 C
尖底从动件 knife-edge follower
& g0 D% }+ y' \- m$ ?间隙 backlash
3 H; g- V8 w |, ^间歇运动机构 intermittent motion mechanism
) T, v4 u/ l4 j7 Y% }减速比 reduction ratio0 c J6 k4 t+ T) G8 T
减速齿轮、减速装置 reduction gear
' T9 C! o! k8 N/ p/ I减速器 speed reducer/ n3 ` {4 M5 H) n6 Z6 l
减摩性 anti-friction quality
: g6 i4 n+ c: ~* L渐开螺旋面 involute helicoid
( O8 G0 F5 ^( w5 y0 _渐开线 involute
- v- Z$ v7 t- B* M6 W9 ]8 N渐开线齿廓 involute profile- h; I& p1 o7 ] O0 ]5 f& E
渐开线齿轮 involute gear& `1 X/ p8 ]6 D1 A/ X% x+ Z
渐开线发生线 generating line of involute/ f+ I5 s/ `. e3 O8 N
渐开线方程 involute equation$ q# U3 e4 J9 v- F: X
渐开线函数 involute function
2 u1 d$ w& L* _4 d+ B6 S& a渐开线蜗杆 involute worm
: z& m& Y* ^( a; w$ K7 D渐开线压力角 pressure angle of involute$ i7 k6 u9 `- G a! K
渐开线花键 involute spline" J& ? ]/ b' ^2 O, v+ L
简谐运动 simple harmonic motion' A3 N" a f& A( S }( A- J( G
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发表于 2008-2-21 11:37:30
