对称循环应力 symmetry circulating stress! [ o9 @- C0 r( n4 @2 U' d
对心滚子从动件 radial (or in-line ) roller follower% e& T, b) @) ], } }1 m
对心直动从动件 radial (or in-line ) translating follower. Y1 v5 m4 ^3 A) Z8 W+ F
对心移动从动件 radial reciprocating follower
, v* {0 P) I' K7 Z! e0 U6 Q9 S对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism; X( D) ^3 _" f* q. J
多列轴承 multi-row bearing* K9 p# f$ M6 _/ H8 C& ~% T
多楔带 poly V-belt5 c5 A4 O0 x1 I6 _& z) b$ Q
多项式运动规律 polynomial motion
/ ^ Z$ |- a) C& f4 P, ^1 W多质量转子 rotor with several masses
$ _+ ]9 v: ^/ n5 h. A惰轮 idle gear3 |2 Q( \/ A* F' u V/ x
额定寿命 rating life* A9 ~9 V6 I9 B9 p8 U6 C( j
额定载荷 load rating1 P3 K6 }. v4 Z$ o0 O
II 级杆组 dyad& L: g7 |; S' O* |% R
发生线 generating line ) O6 p) } V+ q# O! L- g2 ]
发生面 generating plane * C Z6 Z) @1 p+ g- D! e
法面 normal plane
0 {" m1 {7 ^- y; K; ]. B2 c! ~法面参数 normal parameters
o9 N4 X7 t! r2 h; e, |法面齿距 normal circular pitch
7 i" A- P0 R9 R0 r# S; z4 [0 P法面模数 normal module
. I! M7 U" C' u" B) e. J1 a/ }2 T法面压力角 normal pressure angle7 `4 T. `" c6 c6 Y
法向齿距 normal pitch
/ l" i0 F \: A- p: b法向齿廓 normal tooth profile0 q1 g: x- l/ M6 Q4 J! i
法向直廓蜗杆 straight sided normal worm
/ J4 N0 `0 @' h$ T2 c: }2 C# V法向力 normal force
R9 Z7 h4 @6 j# X反馈式组合 feedback combining n2 c( y" D0 e x/ l+ g
反向运动学 inverse ( or backward) kinematics
0 {& k! W8 G/ q) q& L9 p反转法 kinematic inversion
. g3 _, }' q1 [% m反正切 Arctan
2 f) X8 l7 T% N1 d! d7 m" B/ C* H7 ~范成法 generating cutting i" C- |* x* f8 T+ p
仿形法 form cutting5 }+ d/ Q; ]% P& I( N) h. j9 K8 q P
方案设计、概念设计 concept design, CD
, r4 A7 J; ^% Y/ M0 \* C2 o6 K防振装置 shockproof device
! X+ W0 ~- v8 c, b- | u飞轮 flywheel9 r7 @6 e+ p. V d2 g
飞轮矩 moment of flywheel* t% {& z- u* i7 D9 [
非标准齿轮 nonstandard gear
2 c7 M1 i" n8 A非接触式密封 non-contact seal) N) ^* T( {# ?) w
非周期性速度波动 aperiodic speed fluctuation/ y' @1 [4 y& x# P! K
非圆齿轮 non-circular gear! y" G) {6 c$ ~
粉末合金 powder metallurgy
6 }4 ~* c/ B) B分度线 reference line; standard pitch line2 ~+ s9 l9 j- u# b' x: u- K
分度圆 reference circle; standard (cutting) pitch circle
0 h& ~- w" U9 Z' _分度圆柱导程角 lead angle at reference cylinder" U3 e4 m/ S- o
分度圆柱螺旋角 helix angle at reference cylinder
' ?( v, C* K+ U9 Q分母 denominator
% v! Y8 A" S$ j4 ~" P分子 numerator# H. R5 t; z1 `9 i: I& a. y: R
分度圆锥 reference cone; standard pitch cone
& A) [$ |# [5 I, _+ d分析法 analytical method# I9 Q4 C3 p! j/ t. U1 F
封闭差动轮系 planetary differential
: g8 ~6 F$ O5 g! y- A' Z8 s复合铰链 compound hinge
A! d; A, e5 f复合式组合 compound combining/ g' P: |: ^: l m( E( L
复合轮系 compound (or combined) gear train
6 d0 _2 r( i) m; A" A复合平带 compound flat belt1 i! Y+ X/ P8 D) U( X7 }+ x5 v
复合应力 combined stress
+ s% K; W" c4 E. W) K* s复式螺旋机构 Compound screw mechanism
, |2 z, l, P- ]# S# w: n复杂机构 complex mechanism
4 i' s; |# \2 W# m8 h0 ]! w4 k" A杆组 Assur group
$ ? |- |5 s$ g7 V干涉 interference
6 b) a# Q7 l, s* k' I刚度系数 stiffness coefficient# ?6 h' J) X& l# e4 O
刚轮 rigid circular spline
( Q# ~: S6 x1 L; S& J. p1 H' s: t钢丝软轴 wire soft shaft0 _' n; @ q1 j) A7 p0 S$ ]9 D" D
刚体导引机构 body guidance mechanism- t5 t( N6 X: }$ h8 @: p
刚性冲击 rigid impulse (shock)! v" B. E% s( G8 I6 C+ {* Q: k Y
刚性转子 rigid rotor
8 P8 B; p, H# y( N刚性轴承 rigid bearing! H4 u6 }$ u6 W( }3 L) a; \- H: C
刚性联轴器 rigid coupling. L8 i2 R4 q1 m* A0 \3 D
高度系列 height series" Z+ j7 k: [% t/ z
高速带 high speed belt
7 _$ N2 N$ L* a/ ~5 L' F9 X9 [高副 higher pair
- Q( F4 U; V' n3 q格拉晓夫定理 Grashoff`s law
( V6 l2 q% o; X) L- J. P( E根切 undercutting4 ~' h3 P. }2 f, z, o6 f2 z
公称直径 nominal diameter
/ J' h# \2 d8 A3 ?高度系列 height series
6 L4 v( ?8 L1 s7 K' N7 Z5 l& g7 i功 work& s; ~ _: u( X" \. C, z7 \' ~
工况系数 application factor+ j8 S+ ]2 h# Q9 r. y5 l
工艺设计 technological design) z7 I- Y; J8 v: F/ T
工作循环图 working cycle diagram$ [) G, _* Y9 q5 ]& x% j
工作机构 operation mechanism
9 ^" O- A! D, J% H2 M- _' z工作载荷 external loads& ]. U- c. [# g0 J
工作空间 working space
# q/ b# b. p: J- \工作应力 working stress
* r" V2 F/ N9 p! x% w" ?: c* X& j工作阻力 effective resistance2 V2 t* O3 m' X
工作阻力矩 effective resistance moment
7 `# ?/ u6 r- U) V# x公法线 common normal line
) f% s3 V( G3 G' C公共约束 general constraint) n$ s9 R. b2 b2 E
公制齿轮 metric gears
! W* m6 E5 H- b0 J, T功率 power
. I0 \( g" [4 ~" P功能分析设计 function analyses design& U+ ^6 X5 C g( B
共轭齿廓 conjugate profiles) i, t5 p. q! x+ j
共轭凸轮 conjugate cam9 Q0 \1 M! H0 _" Z5 [
构件 link
. x/ r% |4 O& i" z. t* V, ?鼓风机 blower5 Y# f2 v6 O" @" u
固定构件 fixed link; frame
# K/ X, j1 ^8 g2 e) l$ U! n1 G/ y8 p2 e固体润滑剂 solid lubricant
8 j/ ]: E7 d: m2 w/ D, a关节型操作器 jointed manipulator
/ n8 T3 u0 A7 e( e' U% l惯性力 inertia force
0 X+ {! }" ~! q" ?. X6 z惯性力矩 moment of inertia ,shaking moment
& F2 |5 ^7 |/ b q* J6 \ g惯性力平衡 balance of shaking force
" T: x Q0 x" P7 W' t% J惯性力完全平衡 full balance of shaking force
7 L( b8 [' ] B4 I) V; S, A$ d* z惯性力部分平衡 partial balance of shaking force
0 S/ O/ n6 T8 F4 `4 S' S惯性主矩 resultant moment of inertia! P' ?8 |. Q7 N+ N" s Q
惯性主失 resultant vector of inertia1 K& U' B6 y v2 J& {3 j0 F
冠轮 crown gear/ \2 k0 Z1 i, q
广义机构 generation mechanism0 z9 G$ |/ Z" w4 a7 w: I; u$ o0 }
广义坐标 generalized coordinate
# K* r: Z I7 J! Q V: ?+ a轨迹生成 path generation: f$ ]8 t2 }& O& V2 J) Q- \4 h
轨迹发生器 path generator9 j/ V' A# S& s' Y9 i
滚刀 hob. {: R5 D/ D% s3 A& F! \3 t0 F: [
滚道 raceway f& n, P/ Q, c4 W( ^: @
滚动体 rolling element
) B3 w S( I3 t8 k# ]! G滚动轴承 rolling bearing
; y2 F5 F1 w. j2 E滚动轴承代号 rolling bearing identification code" J7 | U* W( X
滚针 needle roller
. h9 _- V7 H+ S( y" K7 J2 c1 v; a滚针轴承 needle roller bearing g4 F% D: x7 r! p' G2 D f, I
滚子 roller0 T8 x {& x$ x
滚子轴承 roller bearing
( j& W7 Z9 o$ W( e滚子半径 radius of roller
3 L* X9 y% ~' g1 V滚子从动件 roller follower
+ u& H0 f7 d5 @' j& ?滚子链 roller chain! }5 g' ~2 O& B+ }: A1 `3 n
滚子链联轴器 double roller chain coupling
- i4 w5 s1 ` D$ {1 R滚珠丝杆 ball screw
3 |* V! Q# q+ g8 i4 U滚柱式单向超越离合器 roller clutch
3 K1 B9 P% \6 }) B* o9 s# }过度切割 undercutting
+ o/ {' w- t0 t$ {% P/ p函数发生器 function generator
! U3 C# t9 d. l9 T函数生成 function generation
! M7 j8 S6 X: B含油轴承 oil bearing4 f+ q; R( Y1 @0 j
耗油量 oil consumption% D _! `5 x. O" _' K/ }
耗油量系数 oil consumption factor; I; I1 K/ Y8 U: f* P. w! A
赫兹公式 H. Hertz equation( m( p" s! H) z$ Y$ m
合成弯矩 resultant bending moment. U' r% _3 a$ a& O. `2 G( ]
合力 resultant force8 ]" ]6 C; H a- o
合力矩 resultant moment of force# X, l3 k- S A! j; i
黑箱 black box
& p5 v7 O" W6 v" d$ ^: J1 B$ x横坐标 abscissa
( P- N; [0 M0 D- ?7 V! }互换性齿轮 interchangeable gears6 x1 M' }. i$ c; b! {
花键 spline5 [1 f, P' Q' r) }$ A1 u2 F; ]
滑键、导键 feather key. h" {, h* U" b; Y0 ]7 Z
滑动轴承 sliding bearing
2 {* U) j0 U# d滑动率 sliding ratio
( |+ L( m7 j7 G. Z" I2 t滑块 slider
( e$ \ J1 J3 |: |1 R环面蜗杆 toroid helicoids worm& x! _1 c, n3 K1 u, g8 U
环形弹簧 annular spring" _4 W' K! B' ^- v6 m
缓冲装置 shocks; shock-absorber% I, c& z: @1 z# @/ Q3 K3 {
灰铸铁 grey cast iron
% o' \9 u, a5 U. I6 L2 E/ M回程 return
5 k0 H5 E# b) E) t回转体平衡 balance of rotors
1 w& K: M9 @( J$ @混合轮系 compound gear train
% \$ s+ t' i. c5 O/ f" x积分 integrate : G8 s! u7 `7 j1 c" o) z b( [9 Y
机电一体化系统设计 mechanical-electrical integration system design * i' J, @$ A C3 o
机构 mechanism
6 ^* k. c$ |' J: R3 C* s' Y! a& C机构分析 analysis of mechanism" V o5 y: S; Y0 f
机构平衡 balance of mechanism. r% o0 P) u6 K
机构学 mechanism+ H. G1 w. Z! }4 }# k
机构运动设计 kinematic design of mechanism
# I* s$ O9 d8 D& }6 W1 F机构运动简图 kinematic sketch of mechanism- R$ o+ c/ s! p6 s1 c& ?3 Y2 k
机构综合 synthesis of mechanism
. |/ w* ~4 w9 a @" v1 \" [3 j机构组成 constitution of mechanism0 b% h4 f5 [9 y1 r. F# r9 x
机架 frame, fixed link
: X! o5 H6 o0 S/ c* A/ U机架变换 kinematic inversion, u% s! x4 @+ Z9 l! z% I+ r, x
机器 machine- C$ y3 m; B; F' s+ k w" M
机器人 robot
' @% t2 j1 N9 i, E, o6 r机器人操作器 manipulator2 E0 C5 \' R' C7 _
机器人学 robotics9 U0 n V, D1 i: s0 c$ P! {! ^; t
技术过程 technique process- u. {+ x* ~( F5 j$ z
技术经济评价 technical and economic evaluation
% [1 h ?, s6 r' N7 r技术系统 technique system
4 z7 G/ q/ N# t0 ~; e机械 machinery
9 B" _: x8 H B( }9 v机械创新设计 mechanical creation design, MCD
8 }8 [/ m# `1 n机械系统设计 mechanical system design, MSD
; Y' S. K: p: g. c7 L1 N/ E) p! }机械动力分析 dynamic analysis of machinery
6 r# V, ?+ A' V5 x! n机械动力设计 dynamic design of machinery2 U; v7 w) X3 e( Q
机械动力学 dynamics of machinery6 ]& P' v. W+ Z7 |; i7 D3 d- K
机械的现代设计 modern machine design/ ]0 L) K+ x6 S6 G% j: p
机械系统 mechanical system* b8 H3 U5 C3 d: j* x, F+ e5 e6 X0 j" m
机械利益 mechanical advantage O+ o9 k& t# _9 D' P
机械平衡 balance of machinery: E; o2 r7 a6 j8 k! b. H
机械手 manipulator
1 ^5 {1 |# e2 m机械设计 machine design; mechanical design: @( o* R& j K6 z! S
机械特性 mechanical behavior
0 N7 f: _% l% i$ o1 ]- Y, ]9 l( n机械调速 mechanical speed governors
' \) E( n4 j* ]7 B机械效率 mechanical efficiency# r! u! B/ q' X2 l( p
机械原理 theory of machines and mechanisms6 z& s* v {9 j
机械运转不均匀系数 coefficient of speed fluctuation2 r% c9 O# N2 ?/ V. b
机械无级变速 mechanical stepless speed changes
- W+ w; e5 h! s基础机构 fundamental mechanism# m: q% F& j+ B
基本额定寿命 basic rating life
9 p! a! n1 L2 s# H- S基于实例设计 case-based design,CBD- H3 Q* r% A8 d4 j! A: f, O
基圆 base circle
; n- V" W2 |% |# X& D$ ?基圆半径 radius of base circle/ d- \ `9 `6 g e' ~
基圆齿距 base pitch
) J. |2 P, `# h3 W基圆压力角 pressure angle of base circle/ k% t8 w1 C% G }
基圆柱 base cylinder
6 J$ y) J, b0 z% m+ X9 d/ x0 D基圆锥 base cone2 `. i; x. O7 K& F9 I. r, S1 q# h
急回机构 quick-return mechanism5 V4 f/ j9 g! J- {
急回特性 quick-return characteristics
9 T" k+ f8 R8 ^0 v1 n& H5 U" l$ @4 [急回系数 advance-to return-time ratio" |0 o6 R$ n; I1 H* g
急回运动 quick-return motion3 }6 Z% G0 v4 C9 y# Q7 F0 j, D
棘轮 ratchet
; ]! X6 G7 V0 W% b" I5 T/ f棘轮机构 ratchet mechanism r1 c; L' i8 f# c: j' j: a
棘爪 pawl4 b* C1 f* R6 @2 y* V8 \, u7 C
极限位置 extreme (or limiting) position+ \; J+ W" i7 J+ T. m
极位夹角 crank angle between extreme (or limiting) positions
5 ?9 i* X. j& K9 }( ?) ]计算机辅助设计 computer aided design, CAD
" g, u) d+ Q$ r5 A9 v5 M计算机辅助制造 computer aided manufacturing, CAM
3 i* U7 h0 H) E2 V计算机集成制造系统 computer integrated manufacturing system, CIMS4 ^' H. W* i8 f* a: O
计算力矩 factored moment; calculation moment
3 \5 `' m/ I& P/ q, h. ?: _计算弯矩 calculated bending moment/ P9 E9 t% l; S$ J a2 t
加权系数 weighting efficient
6 \5 v3 V3 i4 U( U/ N' v加速度 acceleration# A3 @, f$ s( }1 g' s
加速度分析 acceleration analysis
3 Y0 @- A7 [$ _; v: l5 A( E% M6 o% B! I加速度曲线 acceleration diagram7 R b8 }0 ^, F
尖点 pointing; cusp8 ^0 W \( K! g5 {9 n
尖底从动件 knife-edge follower
3 E6 j. B* u- p( `* k间隙 backlash+ B9 v) _/ x3 \) t" ~
间歇运动机构 intermittent motion mechanism' B+ `& K, X" M! r
减速比 reduction ratio
( [/ [( g1 J8 u3 Z8 i, u减速齿轮、减速装置 reduction gear& k* H! o& `; F: x0 Z2 _
减速器 speed reducer- J) A5 f6 h0 w, M3 \3 ~
减摩性 anti-friction quality
! Y+ I1 n, H. c; B: c: [4 |0 X4 \渐开螺旋面 involute helicoid4 b) z9 t) Z8 @
渐开线 involute
; W. U7 }5 s' l- M( D0 f渐开线齿廓 involute profile
+ I% o2 w. K v2 X渐开线齿轮 involute gear
& v ]( ^" u+ l, V5 ?渐开线发生线 generating line of involute
$ N7 ^/ c( Z2 Y% S7 x$ x* ^! z渐开线方程 involute equation
! W. S5 Q3 g7 S. ^6 x渐开线函数 involute function
$ |$ K% C: g2 ~+ w$ |8 M* W7 n6 P渐开线蜗杆 involute worm
. p' i4 F1 ?6 |) P渐开线压力角 pressure angle of involute
$ v1 G# ?% T# f. ~# t0 K3 x渐开线花键 involute spline
( S% v/ D0 Y% y) K" d简谐运动 simple harmonic motion
! w! v6 A0 i/ R" i3 W' T键 key |
发表于 2008-2-21 11:37:30
