对称循环应力 symmetry circulating stress$ |% b5 _; C$ \) D+ w& c( Q1 P
对心滚子从动件 radial (or in-line ) roller follower
0 a0 {/ y4 Z1 L9 H/ a( d/ x对心直动从动件 radial (or in-line ) translating follower8 \, v: V0 f' c! N* E; T
对心移动从动件 radial reciprocating follower; @* o( }$ k, A7 Y/ }& M
对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism
6 K# p4 o% j7 `# ?多列轴承 multi-row bearing
& T/ L0 {8 r7 _2 [. T4 L多楔带 poly V-belt$ H, W/ p: {# J
多项式运动规律 polynomial motion
0 N/ Y$ s8 A/ r( W多质量转子 rotor with several masses- w- d7 k( B; o5 f
惰轮 idle gear* m: C3 v; p8 m$ O9 q o
额定寿命 rating life& v( }- ?) }0 j% W) r; I
额定载荷 load rating" z! v) @6 i1 c# M: Z
II 级杆组 dyad' ?( X$ I" m' }% N4 ?- e4 }- }
发生线 generating line
! P) I6 {8 N. q( z发生面 generating plane , {! y5 }- {4 | r
法面 normal plane
) l8 }; Y1 g# ^- x" K0 ~) s' u c* G法面参数 normal parameters
( t6 Q' ]; d9 e法面齿距 normal circular pitch0 k- a. G: B, q* q+ e8 _; W/ E8 S
法面模数 normal module
) }% H6 p6 Y8 ^# m0 j, B法面压力角 normal pressure angle6 m" F0 b/ ^7 o2 h
法向齿距 normal pitch
3 A6 a, F- j( T9 E1 ? }% W法向齿廓 normal tooth profile
4 {' Z& _* f( `1 ]+ u q9 l1 E法向直廓蜗杆 straight sided normal worm ]. }* n' h4 N+ y9 P/ |
法向力 normal force
6 ~- I, \6 Y& y. k& q9 m, ~: p反馈式组合 feedback combining
1 O4 F0 C% W% S! @! Q6 A反向运动学 inverse ( or backward) kinematics, M! w* G1 A: L
反转法 kinematic inversion
! D: H4 l z8 P, ^- b+ p反正切 Arctan# O7 Q* j7 m/ M
范成法 generating cutting
% @: @" t2 q: l: x. G仿形法 form cutting& y( V$ L; |8 Y9 [9 ~
方案设计、概念设计 concept design, CD7 Z" \; d. C! e& S. p3 ?* _
防振装置 shockproof device+ E: v0 |' O5 b
飞轮 flywheel w, Q, T. \; x8 c+ ]
飞轮矩 moment of flywheel1 s2 L3 {6 [8 f4 a0 [
非标准齿轮 nonstandard gear
% @' @. `& T; a; n( ~% e+ b9 n非接触式密封 non-contact seal
9 \9 w+ c) m& J- } K& J非周期性速度波动 aperiodic speed fluctuation4 Z/ F, B- I$ @: k
非圆齿轮 non-circular gear% G, M& j8 T2 U
粉末合金 powder metallurgy
) m& \, w, C, p8 L; T+ d分度线 reference line; standard pitch line
% H1 {9 j: X) ?' o1 l* I$ ]$ O; i分度圆 reference circle; standard (cutting) pitch circle
* V# ^+ K# F2 N( I9 K8 }- i/ @分度圆柱导程角 lead angle at reference cylinder! f0 p+ B# s" f3 p$ G
分度圆柱螺旋角 helix angle at reference cylinder) r" m# X5 q5 R b' z% _) {5 u, O' s( R
分母 denominator0 V9 w' L/ U/ [; X0 p
分子 numerator( y/ k3 Z0 n3 k* _
分度圆锥 reference cone; standard pitch cone
9 _' m4 G' P+ I: {* C: Y' x+ |分析法 analytical method
# j( Q5 V; Z- u/ h! ], r. |封闭差动轮系 planetary differential
, S) c2 o9 ]& x& x2 ]0 r/ N7 d+ s复合铰链 compound hinge) j9 K3 k0 R' g* W+ S6 @
复合式组合 compound combining
' Y, J1 f* v4 D- L+ y8 `复合轮系 compound (or combined) gear train- x& h# M# K) W+ C. f0 r# F& M
复合平带 compound flat belt4 \2 z8 t" S3 e0 i. R; [
复合应力 combined stress
4 H9 q; V: r; w复式螺旋机构 Compound screw mechanism
7 h4 u) x7 _. R; m复杂机构 complex mechanism
9 y2 R+ G6 `6 `+ s, f杆组 Assur group
$ u8 a) L' @. b$ x干涉 interference 5 {5 e+ N5 R2 \" Z. |6 l3 u4 p
刚度系数 stiffness coefficient& d- h0 a4 W( x# J- b9 f- V
刚轮 rigid circular spline
: i& q3 ~# o; G1 T0 b钢丝软轴 wire soft shaft: c7 |/ j2 u$ M
刚体导引机构 body guidance mechanism8 _# X: N5 ]7 f& |+ n1 [
刚性冲击 rigid impulse (shock)0 x' |- ]( S c0 g) z6 h
刚性转子 rigid rotor. I5 l1 G& J! ~2 S. W
刚性轴承 rigid bearing# D+ s8 C% Z, C8 u
刚性联轴器 rigid coupling6 j6 |% s/ l6 q
高度系列 height series$ R8 d4 ?! d& e; p
高速带 high speed belt; {! K w2 X" J# X1 ^- `! Z
高副 higher pair
' f) L) d0 }6 a1 [ M* |- f格拉晓夫定理 Grashoff`s law' q9 t% \, _5 E: N
根切 undercutting- Y$ H+ I8 u3 ^* {9 d# Y7 ~4 o
公称直径 nominal diameter2 }/ N8 t; K: N* Y
高度系列 height series; B# v+ K8 z. ^9 s4 k
功 work
& N# V3 X; n, X7 a- D' x工况系数 application factor
* B1 x$ _8 f, t# Z5 f工艺设计 technological design
& e% I& F. a" d# }. w工作循环图 working cycle diagram
n0 }1 [ k+ H) f+ N工作机构 operation mechanism6 |8 z8 L: `4 u
工作载荷 external loads
; b% H! e' s# l9 t! G/ p ~工作空间 working space
) e( Z0 D+ |* L' L, D工作应力 working stress7 D+ D. r! w6 E; D" b- A" u D
工作阻力 effective resistance6 P* h8 P/ p, Z8 O) d; P3 N3 `
工作阻力矩 effective resistance moment
# `* A3 ?: |7 F: w9 N公法线 common normal line$ N; P% [" c; G1 e
公共约束 general constraint C9 M& E" [2 i/ E1 @5 p W
公制齿轮 metric gears# z1 Z8 T% ~: P1 b
功率 power
G! d* K& c3 ^8 ~$ q$ }功能分析设计 function analyses design' k5 n, T' E- ]+ a: t/ B: v1 B
共轭齿廓 conjugate profiles
6 r, ~# M+ k" p3 z+ c共轭凸轮 conjugate cam
0 r [6 }, I: L" s; N/ i' `: c构件 link0 R0 n% C, v1 C5 f8 m& a
鼓风机 blower4 r3 f) \) {: Z8 q* X
固定构件 fixed link; frame% Q; q4 \6 b f) U g
固体润滑剂 solid lubricant
6 P$ y1 j. T! |" H关节型操作器 jointed manipulator; x% P& y8 l8 _
惯性力 inertia force
7 F, t) [% \8 S: u: Z* ?7 D) K惯性力矩 moment of inertia ,shaking moment" y$ h9 r/ P1 `5 N2 W
惯性力平衡 balance of shaking force
' R& s$ E; N2 U I7 M$ X惯性力完全平衡 full balance of shaking force0 g6 p* T5 ]4 V+ b
惯性力部分平衡 partial balance of shaking force
& C; m1 N$ Q' d0 Q: X惯性主矩 resultant moment of inertia3 e" C# e! R0 T- h
惯性主失 resultant vector of inertia/ s( E% ?. j6 c: f/ W( A' _
冠轮 crown gear
% I8 u; I4 Z* [6 w7 E广义机构 generation mechanism
6 i2 C2 A6 d0 L: }' `8 V! |广义坐标 generalized coordinate3 K+ H" {) r6 c6 [
轨迹生成 path generation, Q2 _% v4 h; E3 E' r2 f% q0 [% Y
轨迹发生器 path generator I$ E. d+ h" c a% s1 b9 _" i5 l; I3 @
滚刀 hob
) d( U% W/ ]( T; v滚道 raceway1 ]- V% L8 a+ z4 H. J
滚动体 rolling element K! U6 \1 Y! y! o3 S7 K3 K
滚动轴承 rolling bearing7 I' H! ^$ ?) G. }
滚动轴承代号 rolling bearing identification code7 X& F' e2 D& S# V# C2 p5 t/ C
滚针 needle roller* z' M" X( [5 t, e
滚针轴承 needle roller bearing7 {1 d# @. q# t# a4 D1 D
滚子 roller
& ?) q( c: `. M) `; W4 s1 W* `滚子轴承 roller bearing8 u1 N5 _: s/ l2 k
滚子半径 radius of roller
/ S7 ~& H, I1 ~/ y/ R4 v' j滚子从动件 roller follower: t/ D9 n+ d$ G2 }3 k* u. i
滚子链 roller chain
/ d8 V/ _* P6 d" q& [( W+ ^滚子链联轴器 double roller chain coupling
$ n/ H: K u- j, F4 P" [, } O滚珠丝杆 ball screw% [1 r# z( F7 L# F) K% Y) M4 y
滚柱式单向超越离合器 roller clutch6 G9 J. J6 K$ x- L
过度切割 undercutting5 b b' j" d3 P+ v j' o
函数发生器 function generator # g, q5 u4 s+ k! |6 m
函数生成 function generation 7 A: ?) t0 o6 @; \9 @ N, s
含油轴承 oil bearing/ n4 |# a, W6 K
耗油量 oil consumption
+ ^: u$ B' v# V; ^; P* G耗油量系数 oil consumption factor
4 G3 f. M, R. [赫兹公式 H. Hertz equation( i$ W7 {) v. z% t! n" t9 @
合成弯矩 resultant bending moment" Y/ [4 f% i% n9 A' ^; E
合力 resultant force4 ], _3 y5 [9 r* J4 R, w7 \8 l+ h# h
合力矩 resultant moment of force
, K4 z8 `5 u' c L黑箱 black box, K1 U7 W3 U/ O0 q" d4 J4 n. c
横坐标 abscissa) h! V0 Q" `0 T
互换性齿轮 interchangeable gears
8 L+ g, V" s: _. M/ y# h花键 spline
" T/ D3 \0 ^% J3 L: @滑键、导键 feather key
. p% s8 c8 ? G. h9 x/ Q" R% b$ @滑动轴承 sliding bearing
, |& ], r+ `7 T ^. C7 b滑动率 sliding ratio
7 L' Z9 w0 v% J; ?3 C滑块 slider) Y$ I" s# y) H1 Y! x8 \6 h$ }" t
环面蜗杆 toroid helicoids worm
/ Y4 m# {, `) ~5 }% ^环形弹簧 annular spring
+ A' }7 c4 U3 d- U+ U缓冲装置 shocks; shock-absorber
0 f2 R$ o2 ?9 [% |0 a灰铸铁 grey cast iron
5 ` r0 B" D9 P9 c8 T- i回程 return
3 h$ [* E& H# S# B# f8 a0 }回转体平衡 balance of rotors
- x7 Y% K8 v9 U$ A! y混合轮系 compound gear train/ I' i3 k( ]8 Z9 N$ k" Y1 O
积分 integrate - c5 f4 t2 l2 S" @
机电一体化系统设计 mechanical-electrical integration system design - K5 v# q" X* l( v/ d% P. q# \
机构 mechanism
& X. H, h I- e! @. y. C, S机构分析 analysis of mechanism1 s, W( n0 w1 Y, d" O# v. ?' E3 ?
机构平衡 balance of mechanism
+ s& R6 I- d- }, Y. I7 w机构学 mechanism) t, `0 X8 q. ~+ v( `# v
机构运动设计 kinematic design of mechanism* J0 j# G. K% a V/ }2 _
机构运动简图 kinematic sketch of mechanism: [" z6 C/ q0 I# D2 P) |" }' U4 T4 k
机构综合 synthesis of mechanism/ D" U/ ^. u3 A+ ]3 f
机构组成 constitution of mechanism
# h7 v4 ]# E' O* ~机架 frame, fixed link
2 \+ l/ h9 |$ F6 ^3 y' e3 m+ s机架变换 kinematic inversion% C `4 z0 t& f/ d
机器 machine
, Q2 |# @! v1 u+ ]: e& W& }机器人 robot
9 t- J% Y% G" X. B; Q0 H( F3 A机器人操作器 manipulator
& b' G6 T$ J1 M5 L, t/ |机器人学 robotics+ }8 l; j2 K8 F! K. p' u7 v$ B+ |
技术过程 technique process
0 Y) D5 ~3 Z) b) R. I- x0 G技术经济评价 technical and economic evaluation
4 @% k# \9 }7 b$ \: l6 _9 M- [6 v技术系统 technique system
# E/ t: e+ o4 A5 S9 q4 }( \机械 machinery! o1 F7 m9 {, N1 U% o
机械创新设计 mechanical creation design, MCD
$ R* P5 \, H9 u机械系统设计 mechanical system design, MSD' H1 w6 t* @1 Z( V
机械动力分析 dynamic analysis of machinery
+ F7 z, n8 r1 [9 i; {机械动力设计 dynamic design of machinery
6 m1 D9 ~ f# y [( Z8 a7 ]- f机械动力学 dynamics of machinery) l+ G: T9 G7 l. m1 R4 x: I& u; v
机械的现代设计 modern machine design
- W( \; o; U7 \4 s机械系统 mechanical system' l1 b# S# |# _& k" T
机械利益 mechanical advantage
1 V R9 ~, R/ V/ r7 \* H机械平衡 balance of machinery
: r, O; q j7 q8 i. U, S+ z/ J* _机械手 manipulator1 r, A9 ?7 T. N5 V0 [. J
机械设计 machine design; mechanical design: [; J8 z7 i/ V% }3 @3 }
机械特性 mechanical behavior+ A u' P8 c. v: n, W5 ?9 s/ B
机械调速 mechanical speed governors
# K: _8 x( i! O: e& G1 V机械效率 mechanical efficiency
% a7 R0 a7 p: W x% @! N Y5 w7 @机械原理 theory of machines and mechanisms2 b3 P; t: M* g3 M0 B
机械运转不均匀系数 coefficient of speed fluctuation& e$ U5 G* Z) n$ I
机械无级变速 mechanical stepless speed changes' K& D* x+ |' M+ Q, T
基础机构 fundamental mechanism4 V% I& H3 z2 p& U3 Q( _
基本额定寿命 basic rating life& v4 Q, e) C! e* _7 U1 P
基于实例设计 case-based design,CBD
9 P1 Q+ |0 g, r& `6 h1 n基圆 base circle
4 r) I% p/ c. q基圆半径 radius of base circle
. ~& x, @6 p& b- c0 | S0 K! i! q基圆齿距 base pitch
) K& J7 q+ f% Y$ w* t; N基圆压力角 pressure angle of base circle
) C/ _6 p' Y2 v" i0 M基圆柱 base cylinder1 q1 _: y& q( q1 M4 L4 n. m+ U, X5 f2 }
基圆锥 base cone
2 J4 \ m2 c9 o急回机构 quick-return mechanism
0 y4 f5 w( {3 u( _急回特性 quick-return characteristics
, `6 r+ T9 N) G- ~% g3 K+ d急回系数 advance-to return-time ratio
& H: P8 ` @) ]6 N急回运动 quick-return motion4 F' N' x5 T$ E% L- l8 n) G5 I5 c
棘轮 ratchet
! F8 U& d$ [: f- o棘轮机构 ratchet mechanism. n& s% k2 U+ U+ D
棘爪 pawl1 _$ U0 I. F/ Z. W p9 z
极限位置 extreme (or limiting) position8 x, i1 M& b2 ~. W* ?- v, W* a
极位夹角 crank angle between extreme (or limiting) positions" | t1 y3 r3 F) }
计算机辅助设计 computer aided design, CAD. k0 [1 C4 J- F1 @! j* t( |
计算机辅助制造 computer aided manufacturing, CAM
+ h( S1 j' ~ f& A/ c" E6 v计算机集成制造系统 computer integrated manufacturing system, CIMS
$ }0 c% Y' j: q5 `: [( P计算力矩 factored moment; calculation moment5 S2 |* R d \& b
计算弯矩 calculated bending moment9 u4 Y8 j" y, i- f9 n
加权系数 weighting efficient
$ H; C0 [% o( m4 a8 e加速度 acceleration4 L) Z: l$ i3 u+ x0 v! f
加速度分析 acceleration analysis, ]" z7 q% E' b4 G) A& v
加速度曲线 acceleration diagram9 ? X5 V |: H; t
尖点 pointing; cusp( Q) M6 q& V) H) G* X
尖底从动件 knife-edge follower
6 d+ v. r7 R* ], Y0 j1 X9 x7 K间隙 backlash% y$ b9 W5 n5 z8 y* n' R; E
间歇运动机构 intermittent motion mechanism1 g$ c. ^7 Q! i6 U% Z
减速比 reduction ratio4 T- W1 k1 Y/ V: O% p! V2 r% M
减速齿轮、减速装置 reduction gear
/ T! v1 h$ M1 E% u减速器 speed reducer
& m0 q: v7 L3 v3 v9 C$ E9 U减摩性 anti-friction quality5 Z. |0 P+ M/ ^; z4 l
渐开螺旋面 involute helicoid* k& s. h! ~# ^ e8 K
渐开线 involute
, o6 a& X) \4 T! S. o C渐开线齿廓 involute profile4 z% g) K8 e8 E' ]; J
渐开线齿轮 involute gear
J( n ?+ d% O渐开线发生线 generating line of involute/ [ R9 b0 z7 f4 j- H: d
渐开线方程 involute equation( E! o4 E7 l" z* T; Y2 c
渐开线函数 involute function
/ z0 d6 `7 |. p1 v$ y3 _4 n渐开线蜗杆 involute worm
- U1 U$ M2 }; _& e渐开线压力角 pressure angle of involute
! \; b8 s/ o; }" @' v9 ~渐开线花键 involute spline, g" p! u# n$ r7 J* M% X1 _( o7 m
简谐运动 simple harmonic motion
, D/ v" {; A0 O$ H8 V键 key |
发表于 2008-2-21 11:37:30
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