对称循环应力 symmetry circulating stress9 R! b! e+ O: j3 M5 x! _$ u
对心滚子从动件 radial (or in-line ) roller follower% l1 }8 z# o* I. H0 G' X
对心直动从动件 radial (or in-line ) translating follower. t& Y5 b" A u2 D
对心移动从动件 radial reciprocating follower" u5 f& m4 V1 t( r0 o: C) b m
对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism- j, p9 k$ `# F; g5 N$ d
多列轴承 multi-row bearing$ d! M0 g: T7 m8 u# J9 Y$ Y) B+ s
多楔带 poly V-belt* V( y% X" ~. s- S7 s* {0 w" u
多项式运动规律 polynomial motion
! C S# `. \0 w6 j多质量转子 rotor with several masses# ^$ l; r* P5 T0 o V
惰轮 idle gear) }6 @: g |% C, ~2 v- q0 J
额定寿命 rating life
/ R( n/ c" J. ], k5 [额定载荷 load rating
2 _ o* J# r' W9 j. H5 rII 级杆组 dyad
& n( h {3 E6 T& F发生线 generating line
1 q& a$ D' S" O7 R' m& {# _发生面 generating plane
+ ?1 }. R* @# V法面 normal plane
3 Q1 Z) `" Z# F* a6 v2 ^$ V$ _3 ?法面参数 normal parameters1 P; l$ `! l0 ^3 U
法面齿距 normal circular pitch
( V( L/ J9 d$ S8 t( a/ I法面模数 normal module
( C0 d1 M9 e$ f法面压力角 normal pressure angle
: W* U# @. e( u8 |法向齿距 normal pitch
& N1 F0 w! ?3 _/ A S0 c; t法向齿廓 normal tooth profile0 _1 \( t9 ^2 T& C9 }
法向直廓蜗杆 straight sided normal worm/ D0 w5 N6 @% B) G5 n1 n9 |, l( a
法向力 normal force3 o. J( V6 l2 l1 X+ A8 q
反馈式组合 feedback combining
' b/ e* i- u" G反向运动学 inverse ( or backward) kinematics+ L# Y8 @# a" |
反转法 kinematic inversion
5 `$ {" Y; r7 ?& p" w M8 {) m反正切 Arctan! i" e1 ?& M: V1 K: C
范成法 generating cutting
* q( z# {9 J; t, d4 L仿形法 form cutting. U0 e( [ k: i$ ~% K& D) U% o
方案设计、概念设计 concept design, CD
9 j+ _& }& S" s. ]; k" }防振装置 shockproof device
( h. ]) @( ^7 f飞轮 flywheel! T6 f1 I% o9 V T. c1 V
飞轮矩 moment of flywheel
7 u, x W8 d w/ W6 ]; ]非标准齿轮 nonstandard gear7 M, H# c: [4 N6 b4 W V- A& M: z& x
非接触式密封 non-contact seal) M/ A) G% w+ u5 A9 E& f0 R! w
非周期性速度波动 aperiodic speed fluctuation
6 L+ v& F+ M6 m# z+ r: Z1 ^2 s非圆齿轮 non-circular gear k( b. |; i6 b, U8 @/ L) K m
粉末合金 powder metallurgy
6 _+ T. }9 Y8 F y1 r分度线 reference line; standard pitch line
# U" b# n2 E9 K; J# L: j分度圆 reference circle; standard (cutting) pitch circle2 u6 F* W" p% j+ N/ k
分度圆柱导程角 lead angle at reference cylinder
. B6 a5 C+ O, A, U分度圆柱螺旋角 helix angle at reference cylinder
+ E) X7 M4 S; [# T分母 denominator' m+ J5 n( Y, K7 T3 _0 J: a
分子 numerator
! P2 x7 i: ~ P4 a) ?分度圆锥 reference cone; standard pitch cone
3 Y) w9 D1 C4 o+ E分析法 analytical method. J5 C3 P4 M; B7 m- ?
封闭差动轮系 planetary differential
9 |3 X/ K" [7 [; r复合铰链 compound hinge# d) h- l" k+ {% N. o! N1 D
复合式组合 compound combining
! k4 j6 j1 p" a9 Z% ^7 b+ ~3 K3 z复合轮系 compound (or combined) gear train
7 R& ?. B/ t: A" U$ R. ~! Z5 d; K复合平带 compound flat belt
/ o+ v& k2 D! |1 f复合应力 combined stress5 W- x0 @/ |/ v
复式螺旋机构 Compound screw mechanism
, A" ~( z: ], ]8 R复杂机构 complex mechanism- @ V9 h# N; N
杆组 Assur group 2 m8 b h5 c# o/ O t$ U I) t5 l
干涉 interference
' T4 q" T+ ?1 O! M刚度系数 stiffness coefficient! B& U0 p- [1 E! |8 M8 y
刚轮 rigid circular spline
% h% R5 z# X) `, m& p钢丝软轴 wire soft shaft
( |0 Z: I# |+ n! r* ^ A刚体导引机构 body guidance mechanism
- l8 L- q3 G' R1 p6 Y9 ] n刚性冲击 rigid impulse (shock)5 b$ ^9 {- ~' O& g3 a# E' M6 o
刚性转子 rigid rotor
' b' j7 q' q) M) Q( L, ~" @( ~7 l, o刚性轴承 rigid bearing
5 | V& C( C- V5 R$ z& y! `刚性联轴器 rigid coupling5 h3 K' O) `( J, a: \0 g
高度系列 height series
0 s% g, S" m# b7 {高速带 high speed belt
4 l- b Z f1 R# k e5 Y& U高副 higher pair. l" N7 g' x5 W$ Z; w! E% W; l5 A& V; p
格拉晓夫定理 Grashoff`s law
1 A) W2 I( w2 |# w Q; u0 Q# [5 R根切 undercutting5 z' D* I' F& C0 p0 l1 A8 Z
公称直径 nominal diameter; d. A- ^( C' h6 l# w
高度系列 height series
3 S% r. z3 C% A6 I3 \; g功 work& C" N6 e/ {; E1 |& e5 x
工况系数 application factor( y' d' t- I$ S
工艺设计 technological design
, s' S. r1 v. d' {( I7 Y$ L* ^工作循环图 working cycle diagram( c/ W# T& Z1 `/ _, {
工作机构 operation mechanism
! k/ |- h0 v5 F3 H* O* C- y/ S0 o工作载荷 external loads; ^- g! `3 R& @, D4 r/ d
工作空间 working space- n/ {2 J* z7 i/ P# h
工作应力 working stress4 R3 s p7 b$ O
工作阻力 effective resistance' ]/ ~% c. P3 O
工作阻力矩 effective resistance moment& L, C5 ?' |) N
公法线 common normal line+ M# V; j. n7 L$ z& r1 q4 R1 h
公共约束 general constraint* ?% z# Y7 |- u" ~4 ]" S7 e
公制齿轮 metric gears
/ Z/ _: ^* l( r! h# p Z9 f- ?8 z功率 power
. l3 ^ l# t3 |! b- | Z6 g功能分析设计 function analyses design
2 L7 |; c3 I! z; k共轭齿廓 conjugate profiles
; l$ T! o+ E6 D) a共轭凸轮 conjugate cam
9 P( t2 `& i9 s7 |1 X构件 link$ i' [) u; n, S
鼓风机 blower" N$ b0 v9 L8 n; P/ R3 W
固定构件 fixed link; frame
( t6 R1 i2 Q+ r固体润滑剂 solid lubricant; Z0 J$ _! S( A1 B: c1 y
关节型操作器 jointed manipulator
8 }7 ` A. a1 L惯性力 inertia force, N# ?5 w9 H. l9 m/ `8 C- e' W: S
惯性力矩 moment of inertia ,shaking moment- V& V" O$ N2 Z4 l0 ~; Q, y5 d/ [2 t
惯性力平衡 balance of shaking force
2 I4 A+ @5 H, c2 Q惯性力完全平衡 full balance of shaking force
3 c* H) }6 x" G( D8 @惯性力部分平衡 partial balance of shaking force6 m' M6 P, @9 ~
惯性主矩 resultant moment of inertia# j4 R8 E1 t! R- e9 q+ J# b5 m
惯性主失 resultant vector of inertia
9 n( w" V& p% h& u( D7 h冠轮 crown gear
- [0 a7 e3 ~2 @6 Z广义机构 generation mechanism
7 Q% W. }: K$ d& `0 e广义坐标 generalized coordinate/ w9 M6 N* {) `- f m( I+ ?
轨迹生成 path generation
, u S% v. [) l' V4 Q轨迹发生器 path generator
* _/ q+ D/ a( [% v; q4 b# y8 Q6 |滚刀 hob& m( t9 ?2 L) k! T
滚道 raceway
d$ C* M T) _4 z$ y9 M滚动体 rolling element
8 F+ H. `" }8 I# Y! i* j滚动轴承 rolling bearing
' d4 k4 V0 `% m滚动轴承代号 rolling bearing identification code
* y4 g3 c. f* c5 S, z滚针 needle roller
3 m( i- [* O( `. V3 M! K' Z0 }滚针轴承 needle roller bearing' d" B0 K. `5 x4 |
滚子 roller+ r1 x o1 E3 M$ ^7 K( B% W
滚子轴承 roller bearing: a( ~2 G2 p* @
滚子半径 radius of roller6 ?# P" w6 N! Q8 C* h
滚子从动件 roller follower# D& ]" L( N* A) z
滚子链 roller chain9 _7 [; R3 i+ L1 n" k
滚子链联轴器 double roller chain coupling( D/ Y% }# w, ~' W$ a
滚珠丝杆 ball screw4 k: X: X6 b2 u
滚柱式单向超越离合器 roller clutch
0 G0 a9 w. a c过度切割 undercutting7 I* w$ l5 B) I9 W/ Q) K4 N
函数发生器 function generator
; m7 J: e: j" d( E函数生成 function generation ' M+ `1 q% Y; c# s; ]6 ]
含油轴承 oil bearing
, \9 _4 \) _4 \6 Y* E- W耗油量 oil consumption, k! ~8 i9 [5 Z" @4 E1 }$ u! ^
耗油量系数 oil consumption factor
( M) g5 |! W2 [. D& L; a赫兹公式 H. Hertz equation0 R; s5 u% F; a4 D" ?: J u" k
合成弯矩 resultant bending moment2 m6 x/ p0 l- E* B* V9 V
合力 resultant force" ^0 ]; u9 t h3 L
合力矩 resultant moment of force
& t v- i! L2 a黑箱 black box# [' W# m. ]- g. q% }* h
横坐标 abscissa U. i$ l( ^1 I1 W4 I
互换性齿轮 interchangeable gears1 e- ? E) v; s% y- T- h
花键 spline3 z+ l! X0 E) S
滑键、导键 feather key: J/ V, _' D8 a, t3 ?, l
滑动轴承 sliding bearing
2 x! ^6 ]& j' v滑动率 sliding ratio
* E5 [0 l: i! m9 H& |; n6 O滑块 slider- B# i; A, K4 a7 d
环面蜗杆 toroid helicoids worm5 n0 Z; h* {9 R
环形弹簧 annular spring
# k U, k% G D- O缓冲装置 shocks; shock-absorber
, U9 V4 s8 g& j! y$ Z灰铸铁 grey cast iron4 l/ H" H0 ^" c9 D% B" e# c
回程 return9 i. w9 E: M: G6 R! Z/ X8 B
回转体平衡 balance of rotors" R0 k# s- s. n2 o. k4 y
混合轮系 compound gear train- u% a. k# j# a" B
积分 integrate
/ B) m8 O G1 S' W机电一体化系统设计 mechanical-electrical integration system design $ D F. I& U; |, ]% E. a
机构 mechanism
8 I. ] V0 | S6 j8 x. u机构分析 analysis of mechanism( }1 V, I3 I5 N" k7 p8 O- m
机构平衡 balance of mechanism
- \5 A; X( V. \3 p机构学 mechanism
. q2 w/ o' W0 U- e7 x机构运动设计 kinematic design of mechanism) j- Q3 \9 C4 v0 R; o9 v/ ^5 `
机构运动简图 kinematic sketch of mechanism3 y& l: z" z$ T" r
机构综合 synthesis of mechanism
7 w/ v# D5 {! l% t& q机构组成 constitution of mechanism! ]$ a# [# j- z
机架 frame, fixed link H% n; P, r' P+ Q6 g! k
机架变换 kinematic inversion$ ]* b) L% \+ h' N3 T( S. s
机器 machine
9 v( N. t/ ]7 k6 g6 x机器人 robot9 T; B$ k* ?0 Z0 r5 n3 a
机器人操作器 manipulator
5 j( j$ @' x& v9 \+ M) r机器人学 robotics( A, n4 l; c$ G- s3 l
技术过程 technique process# Q; I* z4 C$ ^& b0 S
技术经济评价 technical and economic evaluation
1 Q- ^1 ?, K! d/ \) _# \技术系统 technique system
) k, T6 z/ V# R$ ~机械 machinery8 w y! M4 z" h% v) |& [+ Z, x
机械创新设计 mechanical creation design, MCD
1 ], l% f. T' w' x0 C, ^机械系统设计 mechanical system design, MSD1 K7 h! b, y( Q2 d7 s
机械动力分析 dynamic analysis of machinery
4 R# O: l* c. L2 L3 p! c机械动力设计 dynamic design of machinery
o) a0 T$ J( a) X' S! S机械动力学 dynamics of machinery
8 D0 H9 L& h1 I机械的现代设计 modern machine design6 Y% S0 ~4 p' f- t. e, M
机械系统 mechanical system
8 q9 r, H/ L& i2 T3 w$ H机械利益 mechanical advantage: }( P3 A# U4 _5 M3 W4 s4 K
机械平衡 balance of machinery, `# H2 V; S' L3 |& X; x
机械手 manipulator" b8 u' ^- |5 m
机械设计 machine design; mechanical design
' r5 T4 e1 ~5 l机械特性 mechanical behavior
; L9 \8 x$ R# Q8 j" R2 {/ s机械调速 mechanical speed governors9 H' |& b+ s% v( t! p. v# ]& {1 X0 S
机械效率 mechanical efficiency% ?3 K. x8 Y" J p# K
机械原理 theory of machines and mechanisms
5 z. p# y4 U4 Q1 t# b/ g( I机械运转不均匀系数 coefficient of speed fluctuation6 K m' E- x; ^
机械无级变速 mechanical stepless speed changes) {/ K6 I9 v0 I% b6 E' L
基础机构 fundamental mechanism
( b3 E6 h* _2 l6 ^& M- g3 M4 Y9 `1 H基本额定寿命 basic rating life
3 m% m: k0 p, O/ D' O0 {基于实例设计 case-based design,CBD" k6 B9 ~! }$ W& k1 I* r
基圆 base circle
7 e1 R/ U2 p0 q7 O- x! L基圆半径 radius of base circle
7 [: A( S) W9 O; T! d t基圆齿距 base pitch
* l' `# R8 f5 Q" y基圆压力角 pressure angle of base circle& ]$ \& c' O+ b
基圆柱 base cylinder2 ?. S5 ^+ L: a' L, T
基圆锥 base cone
# M W n0 F2 }: h! G. x急回机构 quick-return mechanism
% p- Q1 t5 o% Y# G# N& M8 b7 q* k急回特性 quick-return characteristics
5 ~; ~% W8 V/ b6 i" e5 ]急回系数 advance-to return-time ratio; h3 _& V6 }) e7 u( i
急回运动 quick-return motion
! h5 z% a2 E5 S) z+ M& g棘轮 ratchet
& N7 `9 Y( Q0 a% o: S! d棘轮机构 ratchet mechanism6 j- b$ _% j8 d9 C
棘爪 pawl( q. g: J: M! y. }& B
极限位置 extreme (or limiting) position
$ K4 \3 c+ C! }. X! b7 J: B极位夹角 crank angle between extreme (or limiting) positions
5 V( Z6 ?4 C, v5 C9 P计算机辅助设计 computer aided design, CAD
- a. p& F, @8 l2 Z2 J& E5 K& L计算机辅助制造 computer aided manufacturing, CAM
2 ?! M9 U* X( G计算机集成制造系统 computer integrated manufacturing system, CIMS1 p D: w" ?4 Z: J: u: W/ `# B
计算力矩 factored moment; calculation moment5 ~$ B# C/ z# P. z& `, D
计算弯矩 calculated bending moment ~' l! Z8 Y" \9 h
加权系数 weighting efficient
) q: q1 c+ H, \8 m加速度 acceleration! [7 a, S, p7 E
加速度分析 acceleration analysis
y' R" L4 U: @; a: F. D! t+ X3 {加速度曲线 acceleration diagram" O6 r5 t0 D& K: ?: S6 v" e
尖点 pointing; cusp
' N7 d6 ]' R( C* g8 P1 W尖底从动件 knife-edge follower1 f/ m6 q% R2 k) E+ Y1 ?
间隙 backlash2 s ~3 {( x t: z( Q) u; q2 D
间歇运动机构 intermittent motion mechanism
* n7 M) n2 Y! o7 o8 y7 s减速比 reduction ratio
9 p) K" @5 `& J9 U9 k- o3 j减速齿轮、减速装置 reduction gear3 u0 y% z5 y/ g- }" y8 z
减速器 speed reducer
- i2 P% K( m3 c r' x+ J7 v' R" }减摩性 anti-friction quality, W' @6 K. G" X
渐开螺旋面 involute helicoid; ]' O: G( ~4 G4 W* g1 \3 ?
渐开线 involute
7 K" f* [$ M1 M渐开线齿廓 involute profile
4 B4 d6 i- b, A+ J/ M# \# g渐开线齿轮 involute gear
( |' @7 T" Z' }- k8 O渐开线发生线 generating line of involute/ b" I, s) C8 c) Z/ n3 Z
渐开线方程 involute equation
' v% H- g: h5 b3 }8 e渐开线函数 involute function
2 b: }* F' i2 P( a渐开线蜗杆 involute worm
5 l2 S3 g3 j8 |/ `% W渐开线压力角 pressure angle of involute
3 D+ O9 j6 U0 j" k, ~渐开线花键 involute spline+ F& ^2 j. P" }- ^4 g& F
简谐运动 simple harmonic motion
& ^1 e. ?0 I r) W, o) ^, ~键 key |
发表于 2008-2-21 11:37:30
