对称循环应力 symmetry circulating stress! @6 r1 N: W! G: p$ J
对心滚子从动件 radial (or in-line ) roller follower
& T5 `# L" b' w对心直动从动件 radial (or in-line ) translating follower+ s) E8 I: O0 D; |
对心移动从动件 radial reciprocating follower% f% j- b* ]2 C$ G. y, V8 K2 e: H! A: x
对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism: s/ W# a8 d# _& ?, {
多列轴承 multi-row bearing
# k* a1 B z. g/ e0 t4 j多楔带 poly V-belt' k/ ]2 c3 c0 ?) m7 K6 y
多项式运动规律 polynomial motion
; I, n7 _8 `4 K5 _6 X( |* t3 K; o多质量转子 rotor with several masses; O; D, F: D: n% j$ s) ~/ Z
惰轮 idle gear
# g7 @+ h7 }8 Y$ j额定寿命 rating life- M9 z! ~# G, c' R
额定载荷 load rating7 G$ z$ V; s6 x
II 级杆组 dyad
" d6 m6 E1 v( L' d发生线 generating line * v# e! @0 |. a+ Q9 }5 a
发生面 generating plane : L4 m/ b {6 Q K( ~
法面 normal plane" P9 G( z" [9 Y. x* ]
法面参数 normal parameters
l0 x5 X( J( e* \6 V' K法面齿距 normal circular pitch
# T" x4 B% d+ Z( l- ]4 T. n法面模数 normal module$ W( t' e, \& a3 X# x4 ]" ^
法面压力角 normal pressure angle
! \) w+ n: s2 }法向齿距 normal pitch
6 e: u5 Z. }. \0 D9 I/ e法向齿廓 normal tooth profile
y) k$ Y) W5 u# }法向直廓蜗杆 straight sided normal worm
: h4 v9 S' s( O0 Z) n) P$ j法向力 normal force
0 d; u; W9 R- @6 C! ^# V0 b) E, ^反馈式组合 feedback combining3 S, H* I% v9 A, I7 B) Z6 Z
反向运动学 inverse ( or backward) kinematics
4 D6 ^1 R& C: X2 [5 P4 C) R) n" }4 w0 L$ N反转法 kinematic inversion! A- ?; m1 ~' h$ A
反正切 Arctan
+ G0 W' ^- J# ? C( q范成法 generating cutting
- Q: R: u: T: Y! [& U9 y% J: T仿形法 form cutting0 Y Y: Q9 ~/ {6 }3 }
方案设计、概念设计 concept design, CD
8 m$ p$ h) j: t4 F防振装置 shockproof device
( h9 h$ o7 j1 L6 c# v% a$ ?( F5 v飞轮 flywheel
( z8 n. @5 X) [, g" R- d飞轮矩 moment of flywheel
% E% d; r& K4 t+ O非标准齿轮 nonstandard gear
; U6 g" G, B$ ]# W* S6 Q G非接触式密封 non-contact seal
9 u9 z: X% J |; d& v5 H非周期性速度波动 aperiodic speed fluctuation
7 C! ?) x5 s0 D$ v- J# a非圆齿轮 non-circular gear
( H5 d# T) t& x& E8 q4 z, L' p \: ~粉末合金 powder metallurgy
1 V" S% d- c# G4 X- W5 Z3 w分度线 reference line; standard pitch line H2 @- S1 S; q3 \- K! E
分度圆 reference circle; standard (cutting) pitch circle
) O$ C. W. `+ D" Q. ^( N! G, `, A分度圆柱导程角 lead angle at reference cylinder$ M" F# j' T) \0 V' T
分度圆柱螺旋角 helix angle at reference cylinder
! x# x/ P9 w$ M, K1 F( ^分母 denominator- U$ H; I4 v2 l+ u
分子 numerator
# W8 C4 s& x9 e+ ^2 l分度圆锥 reference cone; standard pitch cone
# x. O9 B. Z2 u分析法 analytical method5 ^. r" U% J* ]. f7 L- m0 F! G7 q
封闭差动轮系 planetary differential# f0 v, d* ?2 \) P1 H
复合铰链 compound hinge1 K1 a- n4 Y5 ^6 a: O" `/ o( Y
复合式组合 compound combining& }' @( U7 J8 S% @
复合轮系 compound (or combined) gear train( x+ @2 O0 _9 w
复合平带 compound flat belt$ }# {; Y( |/ d- c
复合应力 combined stress& k% L9 [4 h: C$ o+ f, m* c0 ^8 k
复式螺旋机构 Compound screw mechanism2 F( E& Z2 o9 ?' b `- r# y, ^
复杂机构 complex mechanism
6 c4 W" q0 `, X" i杆组 Assur group 8 e* |. C% F3 F2 m
干涉 interference
5 y1 V' w1 Z, r) R; D. U% n9 X刚度系数 stiffness coefficient1 G/ q S' e9 u, S- t7 ^
刚轮 rigid circular spline
. R0 W2 K" f2 a0 m* g" U* B, R. X钢丝软轴 wire soft shaft$ y8 E8 G! ^+ @, }4 b3 j+ y% i& k& [* L
刚体导引机构 body guidance mechanism
# O! ?9 I8 R9 n1 w, T( C' o刚性冲击 rigid impulse (shock)
! `& D8 E* e" m" r刚性转子 rigid rotor, `% G' z! ^. _. I; Z' R5 T+ C
刚性轴承 rigid bearing! h5 Z! o& _! x, _: |
刚性联轴器 rigid coupling J" v1 Z# T* d/ T8 t
高度系列 height series+ F$ H6 i3 t+ B1 h( ?
高速带 high speed belt
5 ]% g# B% P* b6 H! E, u高副 higher pair6 D- F5 o, {/ C! ?+ f4 N- i
格拉晓夫定理 Grashoff`s law
. z& O% K# A) d+ ?' w根切 undercutting3 G8 X+ ^9 ~8 D$ Z5 r( }
公称直径 nominal diameter- k; p& z, C9 s0 d J: V% J) U: n& F" @. m
高度系列 height series- x4 [& o3 [# \9 P
功 work' z( C+ e& y7 D
工况系数 application factor
4 ]! `9 Y* Q+ m) u工艺设计 technological design2 ]+ q2 ^- n# d# `. ^1 q1 j
工作循环图 working cycle diagram
4 ~6 h, f3 k" D工作机构 operation mechanism4 [. A: I8 N/ k5 M
工作载荷 external loads
1 f! K' j- Q- f/ l8 }工作空间 working space" |( X5 C, C& E4 z7 L# `7 @
工作应力 working stress
* i3 U% l( p$ ?5 a( M2 R! ^工作阻力 effective resistance a0 Q- K4 x1 Q$ C2 E ~
工作阻力矩 effective resistance moment
; G) v' ?8 k) y. D9 Z7 F- h% W. J公法线 common normal line: u C# s* X5 z+ M; m
公共约束 general constraint
1 o! i: H, Y0 I! D公制齿轮 metric gears
( u" o: c) z" n& _9 {* _" b# j6 q9 }功率 power3 g. f2 {9 m0 h7 W7 `, X
功能分析设计 function analyses design
' n+ ?4 ~7 |9 D5 R8 k4 w共轭齿廓 conjugate profiles
3 ?( ?1 R8 U% g$ B共轭凸轮 conjugate cam
. ]) U0 K- S' j7 Q构件 link: c, t7 M7 C! C6 H
鼓风机 blower
! _, v* @" @$ }3 m7 W& f, _$ _$ f固定构件 fixed link; frame& t& I" y5 }4 O3 u% D
固体润滑剂 solid lubricant
8 c7 S( `6 @5 h% v5 X& V- {, o M关节型操作器 jointed manipulator+ W7 r5 s) n! V
惯性力 inertia force
* L/ C# i, a9 a6 m' t6 y5 ?惯性力矩 moment of inertia ,shaking moment
- \' r7 C1 l! e: D+ p- q6 @, r. G惯性力平衡 balance of shaking force; c( A5 Z0 l2 j# m8 H5 f
惯性力完全平衡 full balance of shaking force: B" r& Z5 m% {: x6 J
惯性力部分平衡 partial balance of shaking force6 X! L& J% t2 Q, u" ?2 b
惯性主矩 resultant moment of inertia
9 v3 L8 L g1 x, J1 ]$ w; z惯性主失 resultant vector of inertia* \3 f, A% n) I; r, r/ D8 k' [5 H
冠轮 crown gear, k7 ~1 J) \9 X U K
广义机构 generation mechanism
; }# E- J7 y) L' A广义坐标 generalized coordinate
1 ?3 c* F+ U8 I轨迹生成 path generation! o3 b0 c% l K- P- V" I7 x+ h' Y
轨迹发生器 path generator' ?" m) x5 e4 e8 }4 U: o$ D
滚刀 hob2 a6 X8 z+ g6 O: y8 _) Z2 \* `
滚道 raceway
- l0 T4 M* F# ]0 U$ A3 y滚动体 rolling element3 r+ [; p7 L9 [: ^
滚动轴承 rolling bearing
4 d8 R2 L3 a3 `$ |滚动轴承代号 rolling bearing identification code2 a& C( l- t* y- S$ V
滚针 needle roller) k/ ?3 a* U3 u% }
滚针轴承 needle roller bearing
( _: S4 P; O9 `+ P6 ~. }* j2 g滚子 roller
& [" D* z) i9 G/ X滚子轴承 roller bearing7 N3 I6 g: q. T- C0 [. e% s
滚子半径 radius of roller
5 O2 Y4 `* A4 Z$ x4 _" m滚子从动件 roller follower5 G2 p4 y0 U [% b
滚子链 roller chain# I F% y2 M3 l; G+ d- L
滚子链联轴器 double roller chain coupling& n. @+ \4 n+ @$ N- U- G* ^
滚珠丝杆 ball screw5 l* J. w6 ^) O# ~
滚柱式单向超越离合器 roller clutch
7 i% E$ ~7 x' w3 N, ~4 A7 D% E过度切割 undercutting7 x5 ^8 U) P* @) C
函数发生器 function generator
4 y! v$ S3 t) B. K3 M函数生成 function generation . l1 z# M! e) A$ w0 d4 L! H& e
含油轴承 oil bearing; `. x5 R5 Q1 ~) F+ G/ \+ r& O* B
耗油量 oil consumption
* c: g8 U; N. |1 Z1 x" O N# c9 P耗油量系数 oil consumption factor
7 ?3 j6 h# G+ {; G! p5 E赫兹公式 H. Hertz equation
1 f6 n2 n% p/ b& u# Y2 B8 w- f合成弯矩 resultant bending moment- V( R; C6 q+ c% H6 T
合力 resultant force
3 W d' x0 R P% r2 j) V: G合力矩 resultant moment of force
8 O% m- Y$ F* D黑箱 black box: ^6 c4 U/ c0 W$ c) p% u# Z: b
横坐标 abscissa2 {' w$ T8 ?( Y+ Z8 C7 M9 p2 f
互换性齿轮 interchangeable gears
: r/ l3 n# E) s& x' u花键 spline4 Y" c1 O; w- ]5 V; o8 p4 [% Y
滑键、导键 feather key
5 x8 F% b t) b% M2 U2 G滑动轴承 sliding bearing; U' P7 u, `- w% ?8 M
滑动率 sliding ratio
! \* D% {! M6 L& P滑块 slider; P# W2 ^* R# F5 ` r1 @7 F
环面蜗杆 toroid helicoids worm+ q4 }8 i! J4 _- N& B" Q
环形弹簧 annular spring0 t3 X- n2 R) P9 G ?
缓冲装置 shocks; shock-absorber( d- ^% z+ c& E# O5 n! |. c+ i
灰铸铁 grey cast iron& P' r, [9 c& P! g4 I4 S
回程 return
, I3 b1 J( ]3 ]0 `2 M回转体平衡 balance of rotors
* c3 e4 N; e+ [混合轮系 compound gear train% [" t3 t+ p* ^' f: o
积分 integrate : T! O# n# d5 S/ v
机电一体化系统设计 mechanical-electrical integration system design
0 b# L- ^2 c6 {1 n机构 mechanism
$ Y8 |2 s9 `9 w机构分析 analysis of mechanism" x; ]+ r$ R& W# r' ~3 ]& v' {
机构平衡 balance of mechanism+ V( E$ H# q8 U, X3 U' Q: j
机构学 mechanism
4 T9 n' h3 w6 g7 t机构运动设计 kinematic design of mechanism' N2 K0 B( N9 K* n3 Z' D" n5 X- ~& h
机构运动简图 kinematic sketch of mechanism r1 ?9 {& u2 P1 Y1 ^: r2 i5 K
机构综合 synthesis of mechanism
$ [: ~' R) g) ^* s机构组成 constitution of mechanism
+ x$ h2 w5 U/ Q) S) x) m3 P5 l机架 frame, fixed link
7 q' Q7 Q, C) x3 Z机架变换 kinematic inversion
- d$ {$ v, s& w3 B- ?% g7 O. X& v% Y7 w机器 machine" ?: `* M5 C4 x8 O- M/ m/ O9 e8 S
机器人 robot
0 b6 t8 o! W% Q6 L% L机器人操作器 manipulator
$ R9 k4 i; _# G: f机器人学 robotics
2 s3 |+ U2 b7 p: H$ m. d技术过程 technique process
, T/ q3 S+ H' I3 P) F8 @2 W8 r4 x技术经济评价 technical and economic evaluation0 J+ f. Z& ]* H9 r% d
技术系统 technique system. V/ L- ? b- M1 ]$ A
机械 machinery* k+ I3 z/ u" b9 X" h
机械创新设计 mechanical creation design, MCD. {2 M# m# a5 \0 K" }
机械系统设计 mechanical system design, MSD
1 @: M; {; E6 ?, }1 A) E机械动力分析 dynamic analysis of machinery! W% X+ M' Z. }# y+ _/ N5 |" |
机械动力设计 dynamic design of machinery8 p& c6 Q( P2 A7 a; ]7 l8 l% M" w& z
机械动力学 dynamics of machinery* Y( J& _3 ?0 ^8 s8 n+ z) p& F
机械的现代设计 modern machine design, G: K( c/ T* V3 j- Q7 |4 J0 v
机械系统 mechanical system
5 v3 t$ W3 F6 H7 [* }* H机械利益 mechanical advantage% A! d$ Z, F7 Z' Q0 i6 f
机械平衡 balance of machinery
+ B% ?6 U% F" ~. \0 C/ B机械手 manipulator
1 j: G. |6 l5 G- n机械设计 machine design; mechanical design) R4 U: f: q& T8 L
机械特性 mechanical behavior
# Z S+ Q6 d [- T机械调速 mechanical speed governors
% L' z6 G: ?8 i2 g) \5 [9 T机械效率 mechanical efficiency
1 X0 n3 O2 E5 n3 G M, d( G机械原理 theory of machines and mechanisms
# T0 x; P# n3 ?9 K机械运转不均匀系数 coefficient of speed fluctuation
/ O6 O2 q8 N: `) V8 s$ N机械无级变速 mechanical stepless speed changes
! ^( K% O8 C; q4 t' Z( d% D' i, f基础机构 fundamental mechanism" }( ~0 h1 W/ m; I4 i! q
基本额定寿命 basic rating life1 C& \, s# J" K8 `. r$ [
基于实例设计 case-based design,CBD: Z \8 U K# F- @; e
基圆 base circle
$ f2 ~/ f+ \# O& B+ E t基圆半径 radius of base circle
. n( n8 f D9 S* O2 G+ k* Z基圆齿距 base pitch
! Y) C; Y6 ~! B( i, c/ U基圆压力角 pressure angle of base circle
& }" E* H3 A! f6 P: ~0 U基圆柱 base cylinder6 u/ f% A, k0 i, P# X4 n4 { Z7 C
基圆锥 base cone( O" e0 z( x' Z6 L! L8 w2 @: ^( Z
急回机构 quick-return mechanism
) M$ u4 y7 j+ l# o k: Q7 P- T! c急回特性 quick-return characteristics
# r# v2 G# \- c) u& h( h2 M& c- Y急回系数 advance-to return-time ratio
3 u1 i) i$ c) |. W7 P! w$ L, N急回运动 quick-return motion
i8 c8 o7 E: B7 T6 T棘轮 ratchet+ P: T1 F* f `2 }
棘轮机构 ratchet mechanism# u5 m. v$ U' w' X! f
棘爪 pawl
- v7 X) z8 C+ R: G极限位置 extreme (or limiting) position
; m" T8 X5 l3 d& J: Y# k极位夹角 crank angle between extreme (or limiting) positions) i: j k' i* |) s
计算机辅助设计 computer aided design, CAD7 ~" A/ u: ]/ K ^; `% F2 C
计算机辅助制造 computer aided manufacturing, CAM) [$ B5 V% {" |% w% j
计算机集成制造系统 computer integrated manufacturing system, CIMS# L; `0 A7 W1 l, o+ Z9 p9 ]
计算力矩 factored moment; calculation moment7 I4 V1 K1 x0 W; d( f
计算弯矩 calculated bending moment
: K0 x. m% u0 u/ s, c加权系数 weighting efficient
' z8 l7 ?! C# H# m7 J加速度 acceleration5 Z9 r" C/ u/ l& H6 {/ x: K
加速度分析 acceleration analysis
% f8 v# Q/ U' S2 @% ^% H加速度曲线 acceleration diagram
+ y" w: u2 z+ T- k5 ^' t尖点 pointing; cusp- V- p$ H5 ]" u0 W7 f- f. m
尖底从动件 knife-edge follower' V2 j' n0 X, p0 I- V8 l
间隙 backlash
# `$ v& s( A& I6 J( u间歇运动机构 intermittent motion mechanism
, P3 v8 E+ f. L9 E# Q减速比 reduction ratio5 g s7 y2 O* Y. O3 E" |
减速齿轮、减速装置 reduction gear" V3 ?! |# E' F1 v& j# x3 A& O2 X
减速器 speed reducer) v- E/ Q/ c+ r" @' F
减摩性 anti-friction quality0 J2 \# D! K; Q1 y0 Q ~9 K
渐开螺旋面 involute helicoid: | m( L" }# W' h% q" ~8 y
渐开线 involute
7 _1 y: I+ o- o6 [$ \5 V; E渐开线齿廓 involute profile0 K v0 D( h( Z" Y! {5 L1 j
渐开线齿轮 involute gear1 @9 p6 r1 P( e% Q5 N
渐开线发生线 generating line of involute+ r0 T* @. J' V7 n0 {
渐开线方程 involute equation
$ z' W. Y$ Z4 k, W ~渐开线函数 involute function3 o$ G) c6 A9 x/ O; \9 Z/ [ P) h
渐开线蜗杆 involute worm
( r# R$ I0 G/ R+ I/ @/ a渐开线压力角 pressure angle of involute9 @8 `0 d2 L' E+ U, a5 W) x: l
渐开线花键 involute spline1 B" O% j: ^- q C! }3 n1 M
简谐运动 simple harmonic motion ~* L! u/ H0 \. ?
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发表于 2008-2-21 11:37:30
