对称循环应力 symmetry circulating stress
8 t4 K" X; e7 J( c, l) E& \9 A对心滚子从动件 radial (or in-line ) roller follower
0 P/ V- t6 \5 _% o对心直动从动件 radial (or in-line ) translating follower
6 q- _4 K5 I( a+ ^/ V( A Z对心移动从动件 radial reciprocating follower
) W4 q V2 b3 k对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism: H- U }% B& Y: [
多列轴承 multi-row bearing2 o- H7 [* H3 I8 \# ~" n% K
多楔带 poly V-belt
% K' D" |2 s3 W- H+ @多项式运动规律 polynomial motion
" s1 u' V+ y c$ O5 f. [ n多质量转子 rotor with several masses
/ `1 }3 L: U. t. N5 a惰轮 idle gear
{) Y1 m7 U2 T& v% l @额定寿命 rating life
+ c! S0 j8 ]! F1 ]& J1 y/ i3 n额定载荷 load rating
8 R4 k: G, R! _' kII 级杆组 dyad7 d8 m3 p. h2 l4 x5 \
发生线 generating line % y5 O. ^7 h- n& T' L0 b1 P# \3 t
发生面 generating plane 1 J% {" u0 P0 x* }6 O2 f
法面 normal plane
/ G# W; T0 c5 x$ l7 @法面参数 normal parameters
0 f5 E3 |: O3 c& E8 | L法面齿距 normal circular pitch
+ K! g2 V; A8 K' U# J- f法面模数 normal module
' Q+ W$ `* o# S法面压力角 normal pressure angle
# h: L. L2 ^* L4 n+ ^法向齿距 normal pitch
- ^( I; q% t* h, b K法向齿廓 normal tooth profile
) H2 Y9 N5 b6 {( \; M5 {% |法向直廓蜗杆 straight sided normal worm$ e" Y* H( Q- A# ~7 ^* U
法向力 normal force
" e/ s$ ?2 u: T4 o' P3 r反馈式组合 feedback combining
0 }. a. S- s3 j$ b反向运动学 inverse ( or backward) kinematics
1 r/ ]3 W) H4 n Z反转法 kinematic inversion& Z5 {: g( P. T3 f0 {$ ]4 w
反正切 Arctan+ J5 b; @ O; s! ^. G2 x: W
范成法 generating cutting
; Z: @- }4 @2 S5 q* M$ @仿形法 form cutting
# s* s% w0 F. Q, Z( `/ _1 N方案设计、概念设计 concept design, CD: ~5 ^+ j% o8 v' F$ e6 `/ n
防振装置 shockproof device# f: }" R% j% B9 A4 q
飞轮 flywheel
) {( c4 C2 q8 `0 D# e飞轮矩 moment of flywheel i0 {- ^* V- J& d, I
非标准齿轮 nonstandard gear
# B$ F- t+ o& C0 {0 P x非接触式密封 non-contact seal
% c: Q! s0 F) }, o" p0 f9 {4 k非周期性速度波动 aperiodic speed fluctuation
9 }; I+ `0 U" G) U0 Q非圆齿轮 non-circular gear; k* w; l7 F8 O$ }0 |7 k2 a
粉末合金 powder metallurgy
- I. P& D' z7 `: o4 N5 R1 f' C分度线 reference line; standard pitch line
+ O. x1 d9 i+ R1 `分度圆 reference circle; standard (cutting) pitch circle
3 G2 c3 h6 _0 h* b4 t3 G$ ~分度圆柱导程角 lead angle at reference cylinder8 I8 L$ O- i2 y2 r- f0 F
分度圆柱螺旋角 helix angle at reference cylinder2 }" ` h( S& e: V' ?
分母 denominator
- A7 I8 ^. g( o( G4 A$ F4 D分子 numerator
: {$ R; Y0 B. K* F2 n) Z$ b' X; c分度圆锥 reference cone; standard pitch cone. p3 M+ I# |% h# c2 m. F
分析法 analytical method1 I6 |) e$ | a- @% A L. d
封闭差动轮系 planetary differential
2 x1 B' b( E/ r复合铰链 compound hinge. V6 u) P8 U" u3 `6 f% ]9 W" i$ I
复合式组合 compound combining5 X. w4 ]* |4 d5 O ^+ P9 P
复合轮系 compound (or combined) gear train
/ R) O; z1 v5 Z2 b- d复合平带 compound flat belt
8 Z; ^+ h. X# d8 t, V Y复合应力 combined stress, i( I$ r/ K0 g; T3 y( P
复式螺旋机构 Compound screw mechanism. C. W: O. K$ ^
复杂机构 complex mechanism3 ]( E% `5 b- ?# P) \0 S/ U# S2 p
杆组 Assur group 6 ^2 ^; p' X2 R4 J) ], n* U2 x6 s
干涉 interference ; \# x1 j) L# Y, k) T1 ~- ?
刚度系数 stiffness coefficient; M8 Z$ D; g; M: b' J2 {5 R# A! t2 _$ |
刚轮 rigid circular spline
- j- T5 M" x' [: y y. B( y钢丝软轴 wire soft shaft
& d7 k: v1 Q, I; |8 u: @. L/ f刚体导引机构 body guidance mechanism
3 J0 R9 ^0 J& a- u' y3 u8 E, i刚性冲击 rigid impulse (shock)% H% a, ~/ A8 @2 {: R2 f
刚性转子 rigid rotor
9 k3 N" b$ f% l! `- x; w2 N( y刚性轴承 rigid bearing
/ [9 c) d0 H+ r z刚性联轴器 rigid coupling
1 T7 J3 n1 w% o& f( M5 P高度系列 height series! K% N5 m3 D) _! f# E
高速带 high speed belt2 }) M m: V. }) q; }. `
高副 higher pair- W' ?3 P# h, r6 S
格拉晓夫定理 Grashoff`s law
, V5 c# o& Q( A7 k4 C. D根切 undercutting
4 V b7 S+ U/ y/ U2 T公称直径 nominal diameter- s" w+ X2 v& c- p
高度系列 height series
! _- K5 U& p' F C# z% G0 `功 work
) r; E/ G9 {3 b* R工况系数 application factor
" e) R1 C* ]; ?% G0 j) j) g- q工艺设计 technological design
# @- w5 h( k7 ]+ Q% R; Q9 C工作循环图 working cycle diagram
0 H* ~2 m' S$ A. I工作机构 operation mechanism. e. T* `& y0 c, s1 h
工作载荷 external loads* T$ M' k3 y( I2 ?. }3 @
工作空间 working space9 O) Z! f# M; P+ O
工作应力 working stress: {& A3 x' U* k6 b8 p
工作阻力 effective resistance
3 s1 _8 ^8 b3 V2 p, E) K工作阻力矩 effective resistance moment
' p @" Q/ i9 _7 s6 v/ o7 ^ I公法线 common normal line
& c/ U% T3 c: O4 ?* R! J公共约束 general constraint
, h% o% K- w/ ]$ y公制齿轮 metric gears( ?" O7 w! r+ ~ T0 T) M0 c9 W
功率 power
; A# @! _- t+ o% }; g功能分析设计 function analyses design
% \( A8 F- l0 |1 p+ N$ f* y, T# X共轭齿廓 conjugate profiles. D" H( i* y4 Y" U) @0 ?
共轭凸轮 conjugate cam! W$ _2 }' ]3 r! A1 v& f- I
构件 link
w! y% W7 q& D) Y3 p; y0 M% N鼓风机 blower
6 v2 }% t! r6 z R( V2 U固定构件 fixed link; frame
0 r% E+ R% M6 W* @+ f固体润滑剂 solid lubricant* o( y% n$ V. r9 @" [/ T6 U* E d3 q
关节型操作器 jointed manipulator
% B7 A9 X: f) D( A1 M+ ?1 A% W( c惯性力 inertia force2 y$ Z3 U- T; [' w, H
惯性力矩 moment of inertia ,shaking moment
+ Q0 A2 m1 g' g5 R9 g惯性力平衡 balance of shaking force) y/ ?5 _( }; F' e. b! t' Q+ d# J
惯性力完全平衡 full balance of shaking force+ t: ?- C4 Z( }, L
惯性力部分平衡 partial balance of shaking force2 `" W. L/ s6 g A' A# y$ C
惯性主矩 resultant moment of inertia
; l H' v. Q+ h$ p8 y惯性主失 resultant vector of inertia3 y% g; `3 d, d8 n$ @- u* J
冠轮 crown gear- o# {( A; B! v5 d/ ]+ d7 H
广义机构 generation mechanism2 w9 w1 {* w2 d$ @- H
广义坐标 generalized coordinate4 B2 a" h9 Q( c0 B6 @
轨迹生成 path generation
* m0 i) f# B$ }! h& a" k轨迹发生器 path generator b S/ H% F/ m% c4 e
滚刀 hob
! X, |# G+ N2 }0 y' `1 Z滚道 raceway3 ^" D: o7 R$ ^0 l7 l4 V& N
滚动体 rolling element
3 G. u" _/ i9 e% ~) }8 R滚动轴承 rolling bearing
" N. E1 W4 Q) `. l; P$ N* Q7 a滚动轴承代号 rolling bearing identification code
! \' E) f5 F7 w" t! A5 }滚针 needle roller
& Y0 h8 w. T( y* D' s& u! m滚针轴承 needle roller bearing
: H( ^" [4 d9 j* w6 i8 k# {0 x滚子 roller! C& I C/ I- N- }1 i& [
滚子轴承 roller bearing9 h. q5 ~. e5 k, Z5 j/ x6 f
滚子半径 radius of roller
2 ?2 W2 P7 z- d- Q1 V滚子从动件 roller follower
8 n, I- U3 ^, S+ W: `( m" c/ v滚子链 roller chain% v$ g% n. N4 n+ v, Q7 P/ v8 k8 F
滚子链联轴器 double roller chain coupling
" }4 \: u! Y$ V; V' y, Z滚珠丝杆 ball screw
: V) f4 {* m# D/ D: Z滚柱式单向超越离合器 roller clutch
+ b! i% X+ E4 s" C过度切割 undercutting9 M0 P# o" u5 J$ }8 N
函数发生器 function generator ! H" s9 [2 Z% d: G
函数生成 function generation : |5 c) C3 B9 y2 a2 q6 {$ Y
含油轴承 oil bearing D5 ^/ a% E% s" Z7 S) e3 C6 O
耗油量 oil consumption
# @! y7 a$ _) S1 N% e% @6 z! @/ g耗油量系数 oil consumption factor
0 U; c, U' K: u, O( W( O赫兹公式 H. Hertz equation# X/ J5 v3 U# d. f8 J" g: y& s
合成弯矩 resultant bending moment8 B. t M1 U# r, S5 u" K
合力 resultant force. `* @' u$ h: \' A1 u0 i& X: t
合力矩 resultant moment of force( r1 P% o1 k) L+ [3 d+ H( z9 O
黑箱 black box2 P' C ]# _: m# k, D" {$ h
横坐标 abscissa% C6 T% i# t0 V6 H# h7 n( B
互换性齿轮 interchangeable gears. v: D# Z" d& M, _7 o( M7 h5 A
花键 spline
% D& L5 Y: ^* V6 N* Y; X滑键、导键 feather key
0 g: _* `; \7 q% n滑动轴承 sliding bearing
4 G5 r# d3 p$ F7 ~- t' B" U滑动率 sliding ratio, F6 H8 ~; r5 {& C' |
滑块 slider
) l* r; U0 i+ b& W( H, k环面蜗杆 toroid helicoids worm4 B+ A: u! j' i- w' e8 K2 w
环形弹簧 annular spring
6 x0 ?% t" {# f% i; a. J+ |+ v, D缓冲装置 shocks; shock-absorber
- k0 I* G, s& Z3 k8 _3 \灰铸铁 grey cast iron
; }' u8 y u1 N } \1 [回程 return
& M1 [2 v2 x" D1 b) t2 a5 V回转体平衡 balance of rotors) J& ^& s( m$ j# [* E0 k7 t
混合轮系 compound gear train. ?2 J, n" K$ x9 C0 C
积分 integrate
8 E1 X1 ~5 o$ b机电一体化系统设计 mechanical-electrical integration system design
4 G m' m0 a0 V8 T机构 mechanism
/ B% s5 U$ ]7 N, }2 e3 Z机构分析 analysis of mechanism( Z/ ~: E2 W j9 O$ H" V
机构平衡 balance of mechanism
6 ?1 } V) ~1 H$ @3 c3 V: ]机构学 mechanism
# x1 ]0 V m2 v机构运动设计 kinematic design of mechanism
4 X% q. i0 p: Z! j& t机构运动简图 kinematic sketch of mechanism
5 ]$ H3 k% L6 @3 @& _/ ?5 Y机构综合 synthesis of mechanism* ` ^4 z. _7 V1 t8 Y
机构组成 constitution of mechanism8 u+ }* J F( V6 c$ r. d
机架 frame, fixed link
8 x* }1 z- t J9 H8 w机架变换 kinematic inversion
: m$ a4 _% Y1 a# t6 x( ]机器 machine- W5 @- f* m7 S; h Q
机器人 robot
9 l% x6 {3 F$ X机器人操作器 manipulator
, _; c& A @7 c6 T# y6 E; D机器人学 robotics, t7 [6 I0 b. q% O; ~' ?
技术过程 technique process
* h1 |1 t: D6 ?* c4 j# f v技术经济评价 technical and economic evaluation
! ~" \* e! W8 b6 W5 J技术系统 technique system
7 R* ^7 E7 q) s6 N" ?* q5 f1 c机械 machinery
- i5 Q* P- d4 k; l机械创新设计 mechanical creation design, MCD& E# c7 w/ g5 ], K8 I" N
机械系统设计 mechanical system design, MSD
) ?5 ^7 v Q8 I2 T机械动力分析 dynamic analysis of machinery
) t+ J* Y) E7 m4 d* }机械动力设计 dynamic design of machinery
. l3 p% L1 \2 L. m" K机械动力学 dynamics of machinery0 f+ j6 W9 u7 v* k
机械的现代设计 modern machine design0 g& O6 d! d H5 A) K& h3 Z- p1 g
机械系统 mechanical system2 I5 E+ L8 d! |+ ]( Y$ N" ~
机械利益 mechanical advantage
+ M. I8 D0 N3 n, I* E& @ r机械平衡 balance of machinery
# A9 p$ m W! b0 e机械手 manipulator
; T) w8 Q# z. o5 T/ _/ N9 Q L; B) u机械设计 machine design; mechanical design3 J: i& g1 l# r! k# i8 d$ l: R
机械特性 mechanical behavior" ` C1 [2 S5 Q6 k0 p, x6 V; b
机械调速 mechanical speed governors
" F9 |% m4 o1 u! z H# G机械效率 mechanical efficiency9 o. Y* A7 C6 J" x
机械原理 theory of machines and mechanisms* @* z( Y9 l5 I, _
机械运转不均匀系数 coefficient of speed fluctuation
3 o: c/ x' c; t, e) I机械无级变速 mechanical stepless speed changes0 F- T1 g6 W" T5 p' M& J
基础机构 fundamental mechanism+ R7 p Q/ f* c, r0 s
基本额定寿命 basic rating life
, `/ K9 l1 k: M) ]* n3 y3 b基于实例设计 case-based design,CBD; l2 ^- n. Z' c6 V: L+ s8 N- @6 |# L7 X
基圆 base circle! `9 v- n9 [- Q! x6 x6 b: d( t
基圆半径 radius of base circle. V& {9 a' V+ \' B
基圆齿距 base pitch
# u0 I1 m" i% k$ m$ z [基圆压力角 pressure angle of base circle
! H6 a3 o# S2 _/ [6 Y基圆柱 base cylinder- _$ _. F1 [' f1 L8 h& Y
基圆锥 base cone
: a) f3 a0 f4 n6 b) A9 W& x急回机构 quick-return mechanism+ E8 J) Y/ \/ |' y% I
急回特性 quick-return characteristics/ F; J" e8 `7 c# Q9 t8 N5 E6 }
急回系数 advance-to return-time ratio
X6 B* k( Q) I- Y3 @2 U0 u/ y; U( d急回运动 quick-return motion
) W- g/ G/ g. J4 y) I1 d$ l棘轮 ratchet
3 H$ d2 d1 M7 c- ^, l棘轮机构 ratchet mechanism1 p, {4 e* v2 c* h
棘爪 pawl( a/ R3 w6 l3 w3 @$ K# ?
极限位置 extreme (or limiting) position" n) \& N1 i! {, Q
极位夹角 crank angle between extreme (or limiting) positions
" t. j" j5 t- o% z" N计算机辅助设计 computer aided design, CAD
# g7 h, d6 M5 C/ D A, A计算机辅助制造 computer aided manufacturing, CAM
; f# J; y- J! I& x6 G* r: E计算机集成制造系统 computer integrated manufacturing system, CIMS+ c/ ?. B4 W9 [2 y
计算力矩 factored moment; calculation moment
9 l3 o9 ]- `* d- _8 F+ k& L( p计算弯矩 calculated bending moment5 t- G% U; y5 }6 i1 u/ r- N7 {
加权系数 weighting efficient
L1 B' I* B8 w( O5 `, }; |加速度 acceleration0 o! C" V) x8 c4 n0 i" {
加速度分析 acceleration analysis% R7 m& U n t8 e6 ^4 K+ i
加速度曲线 acceleration diagram! U5 U) I Y% H0 W- Z4 Z1 X
尖点 pointing; cusp# J8 ~- F2 u/ j7 ]% \
尖底从动件 knife-edge follower: z0 ?* T! D- e' L
间隙 backlash
$ k' k8 b" y) H6 w, }3 Z' S间歇运动机构 intermittent motion mechanism
5 T9 H* _5 `8 z8 P8 k减速比 reduction ratio
5 s/ i. L; ]- D减速齿轮、减速装置 reduction gear6 b5 i( L, _- N1 ?$ Y# t' F% C1 |
减速器 speed reducer. q2 V! O- J, F! V z
减摩性 anti-friction quality
. R! L5 f+ i2 j3 g- z& I- W5 S渐开螺旋面 involute helicoid8 S7 x" p4 L( x5 d3 y
渐开线 involute+ x1 m$ P0 P3 Z( B1 U, e$ N
渐开线齿廓 involute profile b+ Y8 U, X$ ~6 ?3 R: V' M
渐开线齿轮 involute gear. q' `# L9 ]6 Z, R D
渐开线发生线 generating line of involute) j- ~$ d, P5 Q1 ]3 e, Y* v5 }
渐开线方程 involute equation
9 W% n8 o8 ?# L; d" t2 Y R4 e) T8 N渐开线函数 involute function
+ b+ G& g' r6 Q渐开线蜗杆 involute worm
' H% b0 u9 C1 s% Q9 j渐开线压力角 pressure angle of involute
2 |6 g# K, C T* R渐开线花键 involute spline
, P: p. [# |' ~, y: K; D简谐运动 simple harmonic motion
1 G/ K. N0 J9 R键 key |
发表于 2008-2-21 11:37:30
