对称循环应力 symmetry circulating stress
* x! _8 O9 e: Q- ^0 [2 d7 F对心滚子从动件 radial (or in-line ) roller follower
( U2 O6 U& k2 x- Q+ u5 H. O1 l对心直动从动件 radial (or in-line ) translating follower
( y7 [/ I2 k5 |+ f! K对心移动从动件 radial reciprocating follower* K2 e; Y C; e, O
对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism/ c5 D4 W; Y8 U' ^! s5 R
多列轴承 multi-row bearing
& _7 G% B$ |/ u' g2 Z$ a* d% k4 H多楔带 poly V-belt
+ B2 R8 d3 k/ F0 I: o8 V, z0 a6 l# }多项式运动规律 polynomial motion
7 q/ l; f4 U; }/ w! [多质量转子 rotor with several masses- c6 L( F2 L1 k" ]# q8 C, l/ _5 p) a
惰轮 idle gear
' N. i0 p2 R _6 U5 X: x额定寿命 rating life* D# `$ D3 Y2 B Z
额定载荷 load rating
4 ]# \2 y; U0 p) C6 j' i% ^II 级杆组 dyad
# n! X4 t% k2 d9 j U发生线 generating line 0 g& q2 x9 c' q
发生面 generating plane
/ `% e. a, s3 F1 i" V/ d# P法面 normal plane6 m: Q& e, K% ]+ U% j
法面参数 normal parameters% K9 R, t1 E7 R
法面齿距 normal circular pitch, S4 ~$ e! ?7 z4 b1 w
法面模数 normal module9 R( s4 U4 F% q1 }) e8 U
法面压力角 normal pressure angle! }/ x# C3 h7 c
法向齿距 normal pitch' T& ]' a6 r! n5 S' `4 L5 [+ x
法向齿廓 normal tooth profile& x7 l5 v6 F$ [1 \. h
法向直廓蜗杆 straight sided normal worm- y! Y3 d5 s1 [0 b5 A8 H& n4 @
法向力 normal force
/ } T7 A" v, U! d" N反馈式组合 feedback combining* \: x; X7 d" u; j$ S6 ^: c/ y& ~
反向运动学 inverse ( or backward) kinematics
; Q9 W% {( o! F- @8 r o反转法 kinematic inversion
/ ^; y6 _7 B* J/ j反正切 Arctan7 d8 R6 R3 [& _" U* d
范成法 generating cutting( H. ~; w, T7 i; d0 [4 f3 p
仿形法 form cutting
5 X4 ^$ M5 T; i1 V+ H0 M8 o9 z方案设计、概念设计 concept design, CD
0 \& L! y0 o* ]( r防振装置 shockproof device
& K: J- _2 B" e& I. D飞轮 flywheel
; R3 h6 I0 V4 h6 D飞轮矩 moment of flywheel
3 h" f9 ]. ^; R' N8 F' @4 T非标准齿轮 nonstandard gear" V" D) P2 O1 {4 U) B
非接触式密封 non-contact seal
! s: w0 ?# c0 r, [! e0 X非周期性速度波动 aperiodic speed fluctuation
# Y- K/ U% A& O- i非圆齿轮 non-circular gear# D; h1 T5 f& U8 E9 m) G3 X
粉末合金 powder metallurgy
" z+ `/ b3 K! }+ ~ d分度线 reference line; standard pitch line/ ^$ j2 s' I) g3 M) ^; [
分度圆 reference circle; standard (cutting) pitch circle7 D v, y( ?: X" x$ _- H2 R$ u
分度圆柱导程角 lead angle at reference cylinder
4 [; R* E5 Y2 h& Y% R& P$ D* e分度圆柱螺旋角 helix angle at reference cylinder4 o( i M" A! m% `) J
分母 denominator+ U6 `8 p7 G+ z1 q3 G: Q5 k
分子 numerator% j$ H& H U/ M) T6 y% O( j
分度圆锥 reference cone; standard pitch cone
" r; a& v& m P8 @分析法 analytical method! X9 F" Q5 r \( U1 k7 Q7 f" x
封闭差动轮系 planetary differential4 l4 v3 N: H( F# M1 d
复合铰链 compound hinge
* x4 f, ^' F. ?复合式组合 compound combining* s- }! e( j( c# a% A6 k2 g
复合轮系 compound (or combined) gear train& m4 F/ d, y% [1 m
复合平带 compound flat belt
7 c" b* k, g7 o# K) w8 M7 B复合应力 combined stress
+ P# ? M7 i1 H6 @复式螺旋机构 Compound screw mechanism
' G( \ p1 J, R$ \4 l复杂机构 complex mechanism6 ~ K6 Z; | l1 s7 a7 E
杆组 Assur group - y( l8 d- G) Q% X+ |
干涉 interference 5 K8 H& Y1 G1 k A4 w
刚度系数 stiffness coefficient% o1 v- a7 a" n: K
刚轮 rigid circular spline
0 _6 `8 w9 I* D0 |# `钢丝软轴 wire soft shaft/ r2 B4 ?3 |0 G2 }' I- h
刚体导引机构 body guidance mechanism
# q& s; {# u! o8 C5 u! [8 l5 M: M5 e1 F刚性冲击 rigid impulse (shock)
7 c* T S, E; J2 \刚性转子 rigid rotor
4 A V( k6 a: P4 g3 R刚性轴承 rigid bearing
/ L5 W- N; u6 j ?/ h. e刚性联轴器 rigid coupling
* d# ]* t [! b9 i" y) W6 d( S高度系列 height series! j/ D1 O: ]5 w: F/ Z
高速带 high speed belt
! R/ W5 V7 D, L3 C! G高副 higher pair
) b6 { E- i( T格拉晓夫定理 Grashoff`s law |; a* f( W0 \
根切 undercutting
1 R( b9 z d+ \% _6 {+ L8 w公称直径 nominal diameter# y( z" E$ o/ I- w# d
高度系列 height series
0 h: U( b6 y' t功 work& K, |# }- I& y4 ]
工况系数 application factor- {6 U7 o" U# i: u: W
工艺设计 technological design
# E9 C+ L# |) p$ H5 D) h0 Q2 y) n工作循环图 working cycle diagram! \6 I( h$ U' O; P: Z( B
工作机构 operation mechanism
3 B- z. q/ [( ]- a工作载荷 external loads
+ X8 F& o* u' n) f工作空间 working space
* b8 o: }! W7 _- R- a$ F工作应力 working stress
/ C( ^ t ]% L5 P工作阻力 effective resistance
. }8 v% w$ y! B% U: M/ d6 z: y) [工作阻力矩 effective resistance moment( ] V+ l6 c" T0 a' z
公法线 common normal line
; Y. t" F: U/ O0 q8 P/ }公共约束 general constraint) [, i, i, ~& [0 u5 \( H- ~" c& d
公制齿轮 metric gears
; A, ]5 z& u1 Z功率 power) y" t+ L, d0 b# w5 w
功能分析设计 function analyses design& T4 d0 x# y) a& C; z( K
共轭齿廓 conjugate profiles M5 {8 v9 x' ]2 z
共轭凸轮 conjugate cam6 y9 D9 |. Q' _$ L+ L: Z
构件 link
0 o$ V+ N5 ~% F! N鼓风机 blower
, w/ `! N0 T7 i$ a# u9 w固定构件 fixed link; frame
# E$ W x( g; t) f+ |固体润滑剂 solid lubricant
U) e, |6 I& E( l4 x关节型操作器 jointed manipulator
# \ T; `& {& L$ x+ d* E h1 {惯性力 inertia force
9 Y1 k9 S/ _ T8 d" A( U惯性力矩 moment of inertia ,shaking moment
; M9 H/ N% L4 U0 Q% A( H9 x惯性力平衡 balance of shaking force/ i! S- k n- E4 n5 P
惯性力完全平衡 full balance of shaking force
; a; m! o' N- U0 s" ]- @* _惯性力部分平衡 partial balance of shaking force4 y2 c- f( h. _4 b& j1 |
惯性主矩 resultant moment of inertia$ q, f/ o1 [5 \, q8 B& f- {9 i, @
惯性主失 resultant vector of inertia
1 v2 r! x; a7 p8 w+ U9 Y) T+ P冠轮 crown gear
" b+ O4 ^! V& |+ t广义机构 generation mechanism0 L/ Z# L$ y6 u, L- l9 l" L9 Z
广义坐标 generalized coordinate% o7 }+ o& h) m$ G1 I4 i' l% F
轨迹生成 path generation( U: P' s( E5 v% K. t* Y
轨迹发生器 path generator
. U" S, o$ J& f- v4 m: t滚刀 hob4 {( x$ c3 \( P+ A9 ?
滚道 raceway
: a9 R( n# A0 e* o. k* W& Q, X8 n! _滚动体 rolling element. W* b! H% n5 x! b6 {
滚动轴承 rolling bearing
6 {# z( W2 P' P' r, p6 C滚动轴承代号 rolling bearing identification code# H u2 r" F4 D0 A/ w
滚针 needle roller) b7 N" A2 F0 @- f& R% I- J$ j' h
滚针轴承 needle roller bearing2 r8 I0 \ j$ F! p6 M4 }0 P
滚子 roller
5 b( O1 P4 {5 B' U6 X滚子轴承 roller bearing
! \; ~5 E' K ]' _4 S9 I! i滚子半径 radius of roller! O6 r7 \- [! F! G; R$ a: v
滚子从动件 roller follower
4 j1 e/ x) h. p8 S滚子链 roller chain
* G8 G- d2 l/ B6 U! ~* Y P. w滚子链联轴器 double roller chain coupling0 L: y% U5 L9 ^' `+ J
滚珠丝杆 ball screw, Q; ?4 [( S" V
滚柱式单向超越离合器 roller clutch
; S: { x3 L( n0 U过度切割 undercutting$ G- B& r# g- m q
函数发生器 function generator - L: R* }- Q* E
函数生成 function generation
4 F* }7 A5 K; f( y7 B" I0 f含油轴承 oil bearing3 b* J2 V# _* I D& x8 u2 g4 v. K
耗油量 oil consumption6 H6 D' n" U$ X; Q5 U
耗油量系数 oil consumption factor. O K$ A+ f( c) J8 b4 n. @
赫兹公式 H. Hertz equation' C5 b: U2 E! F* H7 g
合成弯矩 resultant bending moment2 z8 ]* Y( h0 \4 |7 X# ?
合力 resultant force
0 h! J7 c; t4 v7 u1 V, l合力矩 resultant moment of force9 I, z( E8 X% |2 G
黑箱 black box8 P$ _2 K' J; A- h' X' L
横坐标 abscissa
% P8 o0 y5 |$ k互换性齿轮 interchangeable gears' h0 h q5 N8 [+ X& ?1 }
花键 spline7 f. }5 R, j* V5 C( i! E: W" x1 O. ~
滑键、导键 feather key
* F% f4 z: \: _% `" u滑动轴承 sliding bearing
, j, {: R+ K" q1 d" }% ?! q滑动率 sliding ratio
% O3 {: K" [) C3 h, i滑块 slider
" F5 K9 O: I& W! O5 w# n环面蜗杆 toroid helicoids worm w+ U' B7 r5 M
环形弹簧 annular spring
# k' {% J' C v: o" Z5 ? M缓冲装置 shocks; shock-absorber: f! o/ ?% v& k) h
灰铸铁 grey cast iron$ A: ?% L3 D$ |
回程 return
( [, e8 u7 P4 f3 ^8 N回转体平衡 balance of rotors: |, O$ o& w: M5 ~. A7 j
混合轮系 compound gear train
, D% H% x1 E3 F, w" A, [积分 integrate
1 n. d) B! A' I( x7 R) M1 o机电一体化系统设计 mechanical-electrical integration system design 8 `# E" |) @- X( ?
机构 mechanism7 c5 C4 O+ P, b, l
机构分析 analysis of mechanism9 M2 P7 s' a) u& a3 F
机构平衡 balance of mechanism
* @! k0 Q/ V8 ~3 M" q) S5 J( q4 d* }机构学 mechanism
+ w" [- y) k1 `1 M! a- q1 _' [机构运动设计 kinematic design of mechanism! a [" z' U; V3 G5 G
机构运动简图 kinematic sketch of mechanism
& ]0 o% ~$ o/ v/ d8 f* {' n机构综合 synthesis of mechanism K' X& F: t+ d3 s, @, C* M
机构组成 constitution of mechanism
4 X& o. `/ a. s机架 frame, fixed link, d: ~" w9 g4 T
机架变换 kinematic inversion
$ J# _) h( H% G* A( Y( h! V% J机器 machine
; V N1 A$ i% v* B机器人 robot
2 J! V: v0 f/ W, e8 L f机器人操作器 manipulator1 q5 F* t* j% s% }
机器人学 robotics P3 G! z2 a( o7 \, q
技术过程 technique process
( `- E w; h/ G0 S8 c& ^( |技术经济评价 technical and economic evaluation/ Q/ P! ~1 j3 H* K& a
技术系统 technique system$ v6 v } V' `& F
机械 machinery2 M5 {/ T& U. k
机械创新设计 mechanical creation design, MCD
8 y/ u$ E# e9 `+ s机械系统设计 mechanical system design, MSD
. t! Z% |* |# g机械动力分析 dynamic analysis of machinery
- C1 g; s! Q' F& t! V1 t" U机械动力设计 dynamic design of machinery! ~% Q: ~) q6 L8 H
机械动力学 dynamics of machinery
( Y3 i/ k' ]8 v, @机械的现代设计 modern machine design
+ {- b) D/ }% {* Q! \机械系统 mechanical system
' t( Y0 a: e0 R J5 g8 l机械利益 mechanical advantage
" l" I: B2 h1 D4 v机械平衡 balance of machinery. R, G" o& B4 \0 @8 P4 u2 m8 O
机械手 manipulator
3 [# K8 D8 ?' s. _: n ~机械设计 machine design; mechanical design
, ^4 [! ]/ i, r; `) \% E% l' W; t0 f机械特性 mechanical behavior
- p- N( d( `: v4 Z) o4 y机械调速 mechanical speed governors/ u; v9 |, m8 S' h
机械效率 mechanical efficiency
+ R* M9 ^3 N- O机械原理 theory of machines and mechanisms
: Q8 _6 m" |! y2 J. c机械运转不均匀系数 coefficient of speed fluctuation7 O3 Z+ g* ^ ~9 O$ A4 O
机械无级变速 mechanical stepless speed changes) {# M& ~- y, m' ^
基础机构 fundamental mechanism7 _* t3 ?& a, z7 F
基本额定寿命 basic rating life6 k+ i9 F) N2 s% a
基于实例设计 case-based design,CBD
7 Z0 R: {8 r: Z3 _基圆 base circle% O2 O. {. {/ S2 B3 {% L% b1 p, s
基圆半径 radius of base circle
1 n. f. b" ?5 ~: g基圆齿距 base pitch3 t8 W! U4 E5 m+ s# F! n
基圆压力角 pressure angle of base circle! {; Q1 M* Q$ v8 ?& c
基圆柱 base cylinder, v$ I6 Q2 q! d2 @
基圆锥 base cone
6 r, G+ b6 f& H+ z2 w4 g% R+ T, T( p急回机构 quick-return mechanism- O! j9 {. Q( D: X
急回特性 quick-return characteristics5 I' Z1 l" Z% v: e0 j0 c
急回系数 advance-to return-time ratio
5 u+ N# j4 e& b4 Q2 ]+ H急回运动 quick-return motion
. L6 M7 Z& Y5 }. F1 t% w棘轮 ratchet
) L# t! [( z9 I1 A( T8 |2 A5 g# G" E棘轮机构 ratchet mechanism0 q4 q, ]; o5 i* N7 c0 ~
棘爪 pawl
# l; u2 a6 k3 G0 K; X! ~极限位置 extreme (or limiting) position
- o4 Z* X3 g1 n! z# n, {极位夹角 crank angle between extreme (or limiting) positions
8 t3 Y! j6 ~! o* b7 u! A* ^; J$ D7 e计算机辅助设计 computer aided design, CAD
) h1 G$ `2 @3 J5 J v计算机辅助制造 computer aided manufacturing, CAM) \: w! j) @4 S; _4 n! m$ {: U/ ]2 _0 O
计算机集成制造系统 computer integrated manufacturing system, CIMS& F& V9 D2 N9 U$ l) D+ a9 P1 Y
计算力矩 factored moment; calculation moment
+ ^6 r- M. z+ m. r; R计算弯矩 calculated bending moment' K* `( D8 C7 W% S% ?! z
加权系数 weighting efficient n$ @5 u( [- ^, {1 e$ h/ K
加速度 acceleration X' C1 y$ j" e& M4 o4 V" }7 y
加速度分析 acceleration analysis5 L; u/ W( O8 D s D: Z S
加速度曲线 acceleration diagram7 N" ]7 b8 P- S! Q& @
尖点 pointing; cusp
( y9 d. S' O+ R6 r% L尖底从动件 knife-edge follower
! f- B, p, R ?- h7 z5 \3 {% R1 W间隙 backlash
/ t# |" y: X7 P; M- q( E间歇运动机构 intermittent motion mechanism$ m: N0 X- }2 p- E& l
减速比 reduction ratio
# ~% Z* D( \! Y* |7 y* ?. w) Q8 ^1 c* X减速齿轮、减速装置 reduction gear
' f7 D: z. z8 a7 I+ z( ^减速器 speed reducer9 t$ O) Q+ C0 x$ r
减摩性 anti-friction quality
% j, l; ^: t# @, {: K3 C渐开螺旋面 involute helicoid, V M( `; ^$ \9 g$ ?) c
渐开线 involute4 P6 z9 K* ~3 o: o( r
渐开线齿廓 involute profile
5 Y1 h6 @9 \, ?渐开线齿轮 involute gear
+ n( i3 D3 m" Z- I8 M! w( }渐开线发生线 generating line of involute9 i3 G, R6 H0 d! `& k" A4 F6 x
渐开线方程 involute equation. U1 q% {7 G* L& M, F$ t6 ]
渐开线函数 involute function
8 w, M5 ]/ H* u+ B5 j8 _! `; ` V渐开线蜗杆 involute worm: S% m' V1 z$ u# W7 C( A" N
渐开线压力角 pressure angle of involute
& B3 X" D* T, H, T* x! U3 S' [渐开线花键 involute spline
; _9 D0 [9 y. z$ a6 u& ?4 n简谐运动 simple harmonic motion( g- B, y, G0 h5 y' q
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发表于 2008-2-21 11:37:30
