对称循环应力 symmetry circulating stress$ O5 ]2 s5 {5 u* G0 s. K: }- s
对心滚子从动件 radial (or in-line ) roller follower" ]; f# e4 o3 x9 L
对心直动从动件 radial (or in-line ) translating follower
; x: ~- y) T+ r6 i对心移动从动件 radial reciprocating follower( a9 W& l8 ^0 @! [3 s
对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism; f" L3 G6 o5 ]
多列轴承 multi-row bearing9 f7 W3 m4 H$ a, i9 B
多楔带 poly V-belt
/ ^' F$ p- \! {) z g* O( A, n多项式运动规律 polynomial motion
7 _2 f4 u. b/ D' Z9 p0 K: M多质量转子 rotor with several masses8 J6 c5 N& o- E0 A
惰轮 idle gear
: o: A4 A0 ~+ i* |额定寿命 rating life2 M4 g* h' t+ d9 l4 V
额定载荷 load rating# p/ w; R1 W- G/ w- B
II 级杆组 dyad# J9 h% p3 e0 K" I; W) w
发生线 generating line
}5 l3 n1 p) a+ _+ ]发生面 generating plane 7 j" S7 a+ e4 K+ q# F' U
法面 normal plane- d1 i1 O! n" Y1 z
法面参数 normal parameters
4 ~+ K# i8 z2 j& o4 G9 N法面齿距 normal circular pitch6 w H [/ F H$ j, o |/ I
法面模数 normal module
3 `/ Q8 K" H! U" N( f" _* D法面压力角 normal pressure angle4 B/ U+ x, m* p: N4 s7 j. l# v, A
法向齿距 normal pitch
9 N4 J1 f' J3 P法向齿廓 normal tooth profile
, o! C/ \. ]/ |& j法向直廓蜗杆 straight sided normal worm7 G5 _0 u+ p9 K# J: U! a) ]
法向力 normal force; l" ?1 V" y% O8 v$ c) U' c
反馈式组合 feedback combining5 _+ d3 B4 l. [& \( X& d( }
反向运动学 inverse ( or backward) kinematics3 g: }% ]; e7 ?) l
反转法 kinematic inversion
" g p% x t$ l. [/ x- H反正切 Arctan1 |2 P1 a {3 T
范成法 generating cutting0 o2 r7 l* g) u2 F
仿形法 form cutting
, p1 ~' a0 ~$ v# h- x4 |+ ~: `方案设计、概念设计 concept design, CD& Y" C% C8 b7 g+ C5 P
防振装置 shockproof device6 t# B, Z- {' D
飞轮 flywheel
& r! X& s$ P' k) X飞轮矩 moment of flywheel: ^: ^/ R0 x6 A# _; O$ J! z
非标准齿轮 nonstandard gear
+ b9 q! r. Z: X1 d. ~( J8 x# t非接触式密封 non-contact seal
" K% Q2 Q/ ]8 V2 e% s! o非周期性速度波动 aperiodic speed fluctuation
% ]; e+ t" l2 C8 I" m非圆齿轮 non-circular gear
, b5 @7 U6 c. l! I0 {6 i粉末合金 powder metallurgy
9 m% ]4 H( ~7 E$ m分度线 reference line; standard pitch line f# L9 n6 E( G, l, n$ S# a6 w/ c
分度圆 reference circle; standard (cutting) pitch circle
) w- G9 K( M5 y# l! j* ~6 ] d分度圆柱导程角 lead angle at reference cylinder
# O6 A6 z6 W& \% \分度圆柱螺旋角 helix angle at reference cylinder
7 D- J5 T4 H& T. C3 p1 v9 s分母 denominator
$ r6 W$ U7 r- B Q& R分子 numerator
1 K" ]4 E2 p$ V% y2 w' C8 g6 k r分度圆锥 reference cone; standard pitch cone, L) l/ ?! T3 S: _0 q9 A& _
分析法 analytical method0 L& [* U O7 Q9 X4 z% g
封闭差动轮系 planetary differential f- g7 H5 N6 s) D* m; p7 w
复合铰链 compound hinge0 I/ @& q" O. M7 {8 ~
复合式组合 compound combining
, m( q# `0 v! u! {复合轮系 compound (or combined) gear train- K# E, J) F4 J J( X
复合平带 compound flat belt
7 a9 h$ `, K; h" z3 S# K6 Q3 E复合应力 combined stress. D+ r1 |! I" G4 P8 v# \
复式螺旋机构 Compound screw mechanism
1 [" d+ f7 H2 R( f# f9 y9 p! n复杂机构 complex mechanism
: B0 D7 y* q, X c杆组 Assur group
3 u6 o- D! @1 @' d+ p+ W% Q9 A) x干涉 interference
: U$ I& |% C9 M& V! h, q刚度系数 stiffness coefficient$ { D: K4 S) O/ Z
刚轮 rigid circular spline G% N# h/ l5 [- D1 h' G
钢丝软轴 wire soft shaft4 U' ?$ _) g6 [7 o
刚体导引机构 body guidance mechanism+ n9 a0 A8 w. y! `' ]! t
刚性冲击 rigid impulse (shock), Z2 A8 @& L% b/ B @$ a, e( n) H
刚性转子 rigid rotor
9 M/ u. x4 M& F' s" `: L: A刚性轴承 rigid bearing# a' d% E7 S: z& U
刚性联轴器 rigid coupling J3 o& W0 P+ }# ]; w) }1 T3 {
高度系列 height series
5 R4 `6 i& L2 U6 G+ q高速带 high speed belt
) w6 _# b) g7 M$ G高副 higher pair) [! ]; O3 H$ ]
格拉晓夫定理 Grashoff`s law
. I+ M) I8 f2 h0 k0 t# h, u, A根切 undercutting. b9 D4 v J+ d
公称直径 nominal diameter
7 l! a, q: l- O0 G; z高度系列 height series- u/ T! S- S! a$ T7 z
功 work' ?- Q- R9 Y! h4 z t, p
工况系数 application factor
- q0 B4 A3 `) J( @8 ?7 w工艺设计 technological design
2 D8 e0 j: K4 U% E+ W* M5 J工作循环图 working cycle diagram7 z8 O; d, h1 X2 Y7 c7 x: _
工作机构 operation mechanism' j6 E+ {* E8 g0 Y& r3 X
工作载荷 external loads
3 M. \+ _: j' e+ z4 A7 Y7 @, m工作空间 working space) ?- O8 ~7 n/ M+ D) _
工作应力 working stress' l4 K$ Z8 K0 R
工作阻力 effective resistance9 I. J2 r: T( U7 |5 Y
工作阻力矩 effective resistance moment
5 e9 P" i: C' y/ j公法线 common normal line5 _5 @ t2 t* w
公共约束 general constraint
: U' T0 I2 D- D- h% v; m) ]公制齿轮 metric gears# U3 \: P' z5 t/ |4 O& {
功率 power
0 D$ m$ U- v2 Z$ g功能分析设计 function analyses design
0 y) m8 {: u( a7 i共轭齿廓 conjugate profiles8 ` e- ]/ [% s& o- r! o
共轭凸轮 conjugate cam
6 B. N4 f) W }% v* N* ?! [0 A构件 link3 i- z9 J% y. l
鼓风机 blower N) ?' H( o$ Z% p
固定构件 fixed link; frame6 {' T5 o: {9 O! R/ L# y
固体润滑剂 solid lubricant) V& c' \/ d/ P+ g$ W a: U& L
关节型操作器 jointed manipulator
7 o8 c: L- {" ^9 i/ z& [: r2 `惯性力 inertia force- F% n' ^2 y: q% a% R9 W
惯性力矩 moment of inertia ,shaking moment
e. p2 i8 y. x惯性力平衡 balance of shaking force
5 k( M+ K' m+ }" D2 N惯性力完全平衡 full balance of shaking force9 G: M- e* O l. G0 V
惯性力部分平衡 partial balance of shaking force
6 _1 d/ O5 K% }# H惯性主矩 resultant moment of inertia7 { \7 A( E0 T
惯性主失 resultant vector of inertia
4 w& L D! S# v冠轮 crown gear
5 B2 ?! h' I* Y* L( E广义机构 generation mechanism. o3 ]& g7 v: D5 n
广义坐标 generalized coordinate
( Z) N; r) x# T6 Q# U2 A3 l. F轨迹生成 path generation1 I; }$ V! n* t9 {* _
轨迹发生器 path generator1 ?5 H# k' N8 r1 s
滚刀 hob+ \" D1 D1 F) T! h
滚道 raceway, u5 t+ I; ^; x3 K! |8 G- Y. c
滚动体 rolling element
}) n e; l. R9 d# N& l7 o, @滚动轴承 rolling bearing* n3 p% @5 n- ] o
滚动轴承代号 rolling bearing identification code% }; n8 q( `2 w0 S. k
滚针 needle roller) L' Y, T6 t$ j4 D1 r$ N% s- {( i3 `
滚针轴承 needle roller bearing
- d) s) g% h" Z( R$ z/ C0 [+ O滚子 roller
1 o" O( x) ?+ K7 `+ {5 y( f滚子轴承 roller bearing
# I, r; K! P6 o( M+ M滚子半径 radius of roller
0 }/ B1 |! {' k J9 r) t7 w" t滚子从动件 roller follower
& s" ^7 s, u. n/ [1 s滚子链 roller chain' y* _% k! C. h3 {" u/ d6 i! N
滚子链联轴器 double roller chain coupling
/ k N9 z" A7 s( ]* _3 p( b0 l; R滚珠丝杆 ball screw+ v8 E2 g: Z- ]: X$ s) t& ?" p
滚柱式单向超越离合器 roller clutch
) `. ]2 z) e. h9 E过度切割 undercutting
2 g% p; J y6 P1 c: h2 |! c* [函数发生器 function generator ; d [+ @1 d/ ^7 A
函数生成 function generation % c- a$ N: E7 C5 c+ H
含油轴承 oil bearing. f5 s4 t3 z( U2 |$ @& f; N
耗油量 oil consumption
! v! x* Q2 X2 V/ k耗油量系数 oil consumption factor8 p! c" ^$ U C
赫兹公式 H. Hertz equation
& k) x/ ?$ V% w0 U$ v/ d* F% f2 O合成弯矩 resultant bending moment
2 } f1 l `3 J6 E8 J9 g合力 resultant force& R2 x! e+ z: ] [. H4 V8 L
合力矩 resultant moment of force" ^4 s, a& }0 N3 X! M
黑箱 black box
4 }1 q1 x: u+ E5 W, J0 h# _横坐标 abscissa
' w6 r9 U$ H- y2 L, J0 O( s3 v: E0 u互换性齿轮 interchangeable gears0 }; T" c2 O. ]* \7 E
花键 spline
1 Y7 {1 j- e) d9 [滑键、导键 feather key4 s; {! P; ~! B9 ?9 o
滑动轴承 sliding bearing
2 y/ y( B6 }6 f% A滑动率 sliding ratio# a! O/ c: U) R4 o% `
滑块 slider
3 X% y/ w' X; C环面蜗杆 toroid helicoids worm5 q6 ~7 x* I f+ m& R; B
环形弹簧 annular spring2 N1 X0 U1 H/ ?; o$ I. M9 ^1 I) `: {8 ^
缓冲装置 shocks; shock-absorber, c* l/ Y, o$ o& a' \5 S
灰铸铁 grey cast iron
# J. ^4 P* _8 |: r回程 return) V" t x% ^/ F
回转体平衡 balance of rotors
+ N5 B. s; g: w" H6 P混合轮系 compound gear train( ~! C9 }; I, }0 b4 I% [ i- c; K
积分 integrate ; ^7 v8 j% q0 \& W" D
机电一体化系统设计 mechanical-electrical integration system design
. X# G3 K5 q( E: v0 b机构 mechanism$ s* j, z u8 E. v
机构分析 analysis of mechanism: V0 x% Z5 `/ [7 z9 ?; e4 k( G
机构平衡 balance of mechanism
0 M1 M! h0 E# _$ B/ v机构学 mechanism( q1 k' N4 w X: a5 O* C
机构运动设计 kinematic design of mechanism
$ n) G2 h4 |: c! K6 ] x机构运动简图 kinematic sketch of mechanism
! a5 h8 k- e. z, ^' Z2 B. K7 j8 Y机构综合 synthesis of mechanism g: F3 c _% d
机构组成 constitution of mechanism
% a) j& K* ~" y# m; ~机架 frame, fixed link
$ @/ W* b+ q1 ~机架变换 kinematic inversion
4 ?' D' {4 b% V( ^4 J6 H; k机器 machine
- } Q. t' v/ K F* ]. Q' J机器人 robot2 @) ?+ H# K+ j3 l" k8 Q( f
机器人操作器 manipulator. H5 P7 B& M1 ^ H; c
机器人学 robotics
) Z" a1 X1 E. H, ?$ \技术过程 technique process9 K, _, C9 j: n- I
技术经济评价 technical and economic evaluation
5 y* I1 m: l! P1 f技术系统 technique system) T4 S- o; t0 M- [! n0 e
机械 machinery' x4 i4 X( a3 n' R& s* S4 p
机械创新设计 mechanical creation design, MCD1 P: `+ r7 P. c [ Y1 b* Q! N
机械系统设计 mechanical system design, MSD$ d" r; ?7 z6 D- ^2 k8 i ^0 `
机械动力分析 dynamic analysis of machinery
7 ]3 d R. R- y5 c6 c; A0 A H机械动力设计 dynamic design of machinery
2 \/ a" S8 {5 e! _0 q& C机械动力学 dynamics of machinery" e. {3 ?3 ^2 \' o9 V8 i
机械的现代设计 modern machine design
: z% L9 m6 _6 p机械系统 mechanical system
) n" |' N9 [: J' Q+ Z" f机械利益 mechanical advantage E$ A, ~1 Y0 p
机械平衡 balance of machinery
% J9 z2 ?$ o5 K6 g% N机械手 manipulator
0 b' l9 I" O( b$ {- [% v: {! m机械设计 machine design; mechanical design8 R/ h" y. G4 [0 L" b E9 v
机械特性 mechanical behavior
, }$ o! \, B6 r8 e5 ]+ K* V机械调速 mechanical speed governors( d9 O* { }) S1 @3 Y/ D1 D
机械效率 mechanical efficiency( _; _3 m9 Y$ x
机械原理 theory of machines and mechanisms
$ L3 }4 a* ]- c机械运转不均匀系数 coefficient of speed fluctuation
. E0 N! n. F: @0 |( I: ]机械无级变速 mechanical stepless speed changes
0 J) B% T& F; \8 t! Y0 Y& ?基础机构 fundamental mechanism8 H# J" L8 p% H4 Y6 C0 K3 b
基本额定寿命 basic rating life% C+ x* `9 p) g7 C8 \, P- x
基于实例设计 case-based design,CBD
/ M1 X4 N; Y/ {2 {" ^# J基圆 base circle% Q) F. q! H* Y/ e
基圆半径 radius of base circle
( c) w1 k3 S; h: o基圆齿距 base pitch& k, y: K; ?/ E! u; O. u
基圆压力角 pressure angle of base circle3 n n: [0 n* O! e0 B1 I
基圆柱 base cylinder3 M" ~: U. r4 [
基圆锥 base cone! O% d# a" O$ U. L
急回机构 quick-return mechanism c, j; J2 L' B' O5 f) h1 x( V
急回特性 quick-return characteristics
$ |: S+ O$ O8 C7 l1 e# j; f急回系数 advance-to return-time ratio0 l, @4 Z5 T/ `0 `/ j o
急回运动 quick-return motion2 t; J5 l4 L, Z0 i5 d1 m* Q
棘轮 ratchet
. }* x" j8 J2 W3 p2 i% I棘轮机构 ratchet mechanism5 X# D1 Q$ U: ^% T
棘爪 pawl3 D7 a# j$ ]$ g, `* v% Q) [4 p
极限位置 extreme (or limiting) position/ w% [4 Y% a" H+ A9 h
极位夹角 crank angle between extreme (or limiting) positions
, c6 x. Z/ M$ }# I+ {# O5 G b计算机辅助设计 computer aided design, CAD. y$ u( {- v. C0 Z) v$ p6 b" P
计算机辅助制造 computer aided manufacturing, CAM
, e( T; y6 R9 K; }/ {* H9 F计算机集成制造系统 computer integrated manufacturing system, CIMS
/ [* ^7 S3 U5 W: D5 X0 x计算力矩 factored moment; calculation moment9 s, M% G0 }3 c0 o. V, T( g
计算弯矩 calculated bending moment
9 B& W% `7 Z% q* H6 l/ x加权系数 weighting efficient
' Q. g5 j: @$ {2 E" C# z) j加速度 acceleration
) |5 Y( i- u) j: X5 p+ F2 S8 t加速度分析 acceleration analysis
- L F' f8 `$ F# f2 \9 u/ z- A3 |加速度曲线 acceleration diagram0 f! G" `5 o* o
尖点 pointing; cusp6 ?! b/ b5 V4 j! `4 o+ \8 U* i
尖底从动件 knife-edge follower. N2 P/ m+ j1 u4 P$ D
间隙 backlash9 ]/ z6 [1 K0 W
间歇运动机构 intermittent motion mechanism- B9 E( |) b: i5 w% ^
减速比 reduction ratio& o7 {4 M0 x$ v3 Y2 f6 _' U
减速齿轮、减速装置 reduction gear' G4 V' q9 E4 j: o: V
减速器 speed reducer
' p; W) R7 o& I9 X: E) U3 g; x减摩性 anti-friction quality
$ r' x ]9 a& y( t. C+ h渐开螺旋面 involute helicoid
- {+ s |2 C5 }. @4 }4 F% L渐开线 involute4 G; h9 N8 Q/ F6 {
渐开线齿廓 involute profile
$ w$ z3 _ q! ~* E/ u渐开线齿轮 involute gear
8 z' y+ P; X( b% y0 Y! b渐开线发生线 generating line of involute
" m: \( c. E% M( e渐开线方程 involute equation
6 S8 i4 }+ b: T; W; N+ D渐开线函数 involute function
! {4 _ g: j1 X$ R! G6 y2 p渐开线蜗杆 involute worm- j# u5 ]7 r; b& v) e
渐开线压力角 pressure angle of involute% L3 O' N0 q' e; e3 \6 h6 k0 R
渐开线花键 involute spline
3 R. ^9 s* g' g' ~ [# i简谐运动 simple harmonic motion8 D9 g! V, w5 S
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发表于 2008-2-21 11:37:30
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