对称循环应力 symmetry circulating stress/ N. n, K ]* ? R
对心滚子从动件 radial (or in-line ) roller follower
1 I+ E: a- @! |7 ^对心直动从动件 radial (or in-line ) translating follower
5 Q' Z" d6 c5 ]* Y5 J. v对心移动从动件 radial reciprocating follower
" v% Q0 j+ F+ n% L9 q8 R对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism
4 K7 X# n7 u3 v; O多列轴承 multi-row bearing8 @1 ~- V0 W3 w5 W) N
多楔带 poly V-belt
' _5 d7 ]* d$ F多项式运动规律 polynomial motion
6 `5 p2 N0 k( K- o" J) _多质量转子 rotor with several masses2 U, s: p0 O# o! l; ]$ _
惰轮 idle gear
# G, o8 H& C3 |$ a% \* @额定寿命 rating life
" M: A- E3 @$ h% Z% ^; _, M) J& ~/ ?8 x' i额定载荷 load rating# s, L9 u: j o& V u
II 级杆组 dyad
5 b8 n ?0 ~6 ^7 \发生线 generating line ; z3 M' z7 f( k: w
发生面 generating plane ' t2 p0 p2 K1 K0 F7 \7 @# m
法面 normal plane7 Z2 t( j5 |. |6 s+ l# ]/ e
法面参数 normal parameters
' W: F* d5 Q$ Q法面齿距 normal circular pitch# f# l0 b5 P. M* G! H' g5 z
法面模数 normal module9 u! s: L0 B2 t6 a/ v K5 N% C
法面压力角 normal pressure angle8 s$ L6 w o% q& y( y7 I
法向齿距 normal pitch
! h' {# Q! r# U1 s' A J) a5 J. r法向齿廓 normal tooth profile4 ?) ^" m f9 P0 Z8 V
法向直廓蜗杆 straight sided normal worm, T; I& [. ], w3 x3 l, |
法向力 normal force7 v! E9 n% ~: L! Z5 J q1 Y
反馈式组合 feedback combining
- D+ @! _2 h9 Y反向运动学 inverse ( or backward) kinematics/ ^) c$ Q" E; L8 ^ v
反转法 kinematic inversion
2 u" B( j9 E1 B反正切 Arctan. u8 `4 t- {) S; ?2 `; L
范成法 generating cutting$ E' Y+ c [! }& g+ U3 D; X* J* S& ?
仿形法 form cutting6 c$ f1 S. L& C. S6 y* F, }
方案设计、概念设计 concept design, CD
. n' a7 d2 K8 T+ h- {. y9 E防振装置 shockproof device! E7 L8 e! t9 J }6 y8 \' W
飞轮 flywheel5 W; q7 e- {8 R9 N
飞轮矩 moment of flywheel
2 I, _9 U9 y- V9 f5 t非标准齿轮 nonstandard gear: s$ M% e# g# H8 f
非接触式密封 non-contact seal8 U& [* r3 r! O R
非周期性速度波动 aperiodic speed fluctuation3 B, u C _9 U, I& V
非圆齿轮 non-circular gear
4 w" F$ E+ K3 N1 H0 @粉末合金 powder metallurgy2 x' C Q( S+ x" ], |
分度线 reference line; standard pitch line) s. [# h7 E$ g0 r8 Z4 i9 o
分度圆 reference circle; standard (cutting) pitch circle
, Q5 r6 ~+ s6 I; G; S" E分度圆柱导程角 lead angle at reference cylinder7 w5 H7 w, n' W) X
分度圆柱螺旋角 helix angle at reference cylinder' t( A& I- J& C- _# i7 u% X
分母 denominator# c; r6 X" N4 X5 h. [* \7 w% s
分子 numerator6 r5 g, C8 m) K$ a. h6 _, T2 d
分度圆锥 reference cone; standard pitch cone9 E# h3 `3 S2 _" |$ ~. w1 l5 T( d5 A
分析法 analytical method: X% K# t9 T2 Z7 e; f) z6 Q
封闭差动轮系 planetary differential4 G3 l- H" ^# ]7 v' b. _
复合铰链 compound hinge8 w& R5 O, Q; U; `. Q$ R# q% e5 b
复合式组合 compound combining
, p' }9 T6 c: C; c复合轮系 compound (or combined) gear train7 b+ o7 w# N' V0 I1 r5 w2 \
复合平带 compound flat belt6 Q+ _* E9 X! {7 v/ Z: U
复合应力 combined stress
: q6 l" k" P5 P8 N5 B' k) T# ?复式螺旋机构 Compound screw mechanism5 n! `+ v) S: N2 U. q% R- `+ l4 y
复杂机构 complex mechanism
. A5 t# D$ X8 H) U- k1 O5 D* {! A& q杆组 Assur group & ]. j' ]# g% {0 ^6 O4 @7 m
干涉 interference
5 R# E% `* {3 u刚度系数 stiffness coefficient: P: L/ C$ l% z' C, Z X: i5 O
刚轮 rigid circular spline7 f- y. N: ~3 W
钢丝软轴 wire soft shaft
; {# J8 X* o% X2 \3 ]9 L刚体导引机构 body guidance mechanism
( }. b i& A+ @8 Y刚性冲击 rigid impulse (shock)8 w: }7 u; X8 D! b. _' R
刚性转子 rigid rotor% H: T+ K+ D0 q& J, K* _+ _
刚性轴承 rigid bearing
2 C, w! {+ X4 v+ Z8 A% p6 i7 Z刚性联轴器 rigid coupling
* W) G. K- }1 l3 y2 Q8 ?高度系列 height series" S4 e$ o+ J$ V) @7 I- o
高速带 high speed belt8 t: C2 s8 P( M7 p+ _
高副 higher pair% \: v3 l r. A0 X
格拉晓夫定理 Grashoff`s law
# q( l h- B& y- m4 X! Q( _" w根切 undercutting& Y& J5 C, P) [0 }2 ^6 @% v
公称直径 nominal diameter
9 i" z. F, Q, H* q高度系列 height series9 I @, Z1 t0 Y" `' U& L h
功 work
3 X5 a, U. m7 b0 x工况系数 application factor% @; a$ [: L$ q( f5 g7 f. t: z
工艺设计 technological design2 j' R/ Y1 T- T6 X6 |) o* F* y
工作循环图 working cycle diagram
6 p+ Z" g9 r1 n2 c! s工作机构 operation mechanism
- F8 Z( k5 V" M7 s( [1 t工作载荷 external loads' y5 T5 o$ `" g& |) I# z
工作空间 working space
0 {% T# D4 S0 l9 M. {: h& Z( R- A工作应力 working stress
. B6 _( p, e! I. H$ l" ]0 y工作阻力 effective resistance$ G5 n X% C: [/ W. E
工作阻力矩 effective resistance moment- l8 j5 N: M7 C; s
公法线 common normal line0 E" M7 z0 d q* ~: r! e$ r
公共约束 general constraint
* T" @( A; t2 \: I6 W/ B5 J公制齿轮 metric gears8 i3 F$ J, ~6 ~! w
功率 power" \6 p6 A8 H, j; \5 a" K5 U
功能分析设计 function analyses design. o, o# ^* D, U1 _* E
共轭齿廓 conjugate profiles( H- P1 s+ B. e" F
共轭凸轮 conjugate cam3 |3 w6 n6 `: }6 W
构件 link7 r- @% s" f+ u7 k* Z1 H
鼓风机 blower1 s' s# N) j$ v0 @" H1 o
固定构件 fixed link; frame' h4 T1 f4 Z$ I: x
固体润滑剂 solid lubricant
+ G6 o! ?3 W% {- x关节型操作器 jointed manipulator8 }9 C. Y% {" y' Z8 [
惯性力 inertia force! S7 _4 [, u8 g& R. [
惯性力矩 moment of inertia ,shaking moment
3 F$ A4 |* g4 [) w8 N* _- I惯性力平衡 balance of shaking force* K7 X" a# N+ n6 O% k
惯性力完全平衡 full balance of shaking force
1 G* {$ a* { q% Z/ F5 n$ o惯性力部分平衡 partial balance of shaking force
- E4 k! N3 N; f( o4 k0 k7 v" E& H n惯性主矩 resultant moment of inertia
( J( U# [. n) G8 s" l5 }惯性主失 resultant vector of inertia
- T% m( y" ]& r. A冠轮 crown gear
- l" j6 W1 A U1 A8 z广义机构 generation mechanism
! _, {5 k2 k: W, ?) x/ k' N广义坐标 generalized coordinate1 C+ D% W) M( k1 }8 W
轨迹生成 path generation/ R% a6 | _5 N; _' }# O
轨迹发生器 path generator/ i H3 J. D4 M' l- z" m/ X
滚刀 hob5 M( h7 L V* O$ }
滚道 raceway+ v/ T9 g- A' S, u7 `6 O# `
滚动体 rolling element4 F% f) _* [8 q
滚动轴承 rolling bearing; b* Z! G) u. N( ]5 ?' }
滚动轴承代号 rolling bearing identification code
1 h; V( \8 j- {# f k2 D- C; J滚针 needle roller
, E3 y$ Q$ u) C! V4 w滚针轴承 needle roller bearing% H( u9 Q) f6 s7 B* P* z
滚子 roller. A& r+ o/ c1 g$ Q( m) k; e; |
滚子轴承 roller bearing; O# C( {$ a8 S
滚子半径 radius of roller5 Z9 T k+ x$ m( u/ |) L
滚子从动件 roller follower
& ~5 e; }, G5 W- F0 ^ {, W2 O滚子链 roller chain
1 X9 Q5 C8 u; _; s5 Z3 P滚子链联轴器 double roller chain coupling
$ C6 U5 f+ y) B7 p; t4 ?+ R滚珠丝杆 ball screw
$ Z2 ^+ n1 A" I+ N; m4 v- C3 K5 M# x滚柱式单向超越离合器 roller clutch
3 {0 ]9 y) A/ \+ k过度切割 undercutting t3 A( G7 k7 E5 c
函数发生器 function generator - P8 a9 c: {+ N# ]
函数生成 function generation 8 } m: ] v; A% ^: G0 y
含油轴承 oil bearing' G. s* y+ s: G) M
耗油量 oil consumption: _2 ?( I8 n2 X
耗油量系数 oil consumption factor
0 k0 f6 I( E/ l0 k) d6 Q5 g赫兹公式 H. Hertz equation
. S v$ R7 m) T+ t9 W- h* t合成弯矩 resultant bending moment
" M; o7 p% N. D0 P6 [5 M$ H9 ~& n7 d合力 resultant force1 b1 f. A8 ^; r- ]+ G
合力矩 resultant moment of force
) W4 q; b* V, ?5 r, v4 @- s黑箱 black box
' C+ T( g! |% {) W# }横坐标 abscissa
8 V1 i$ Q0 ^+ ^8 N互换性齿轮 interchangeable gears3 T& l9 j+ f# h
花键 spline
, i1 l, v7 y7 q. c滑键、导键 feather key2 I1 t7 _: U* G: ?; ^3 j
滑动轴承 sliding bearing- f% J V7 z5 q9 O9 X# c* H A6 O/ G
滑动率 sliding ratio
8 K- `! B1 |1 A滑块 slider& d1 E$ k- [7 H( e T4 N0 v' w8 G
环面蜗杆 toroid helicoids worm
$ p$ _$ `# n9 Z" @+ I环形弹簧 annular spring
! Y3 ^2 ?/ O2 ]! c缓冲装置 shocks; shock-absorber6 E( e5 u2 y6 u. X: u
灰铸铁 grey cast iron
# q$ K* q+ j* r, b+ e( b" |回程 return
2 K7 [6 x0 T! L9 _7 ~回转体平衡 balance of rotors+ V# _5 G5 b0 V" N0 L/ S0 m$ H3 w- z
混合轮系 compound gear train
6 ~5 J- i. \* d9 C积分 integrate
/ }( L- F; `, e机电一体化系统设计 mechanical-electrical integration system design 3 [4 O x/ ], R% F0 E
机构 mechanism
8 h- k! [: v! B$ j1 T" W% Q机构分析 analysis of mechanism
' z; U# }- c' X4 W2 H- j7 J机构平衡 balance of mechanism2 n6 M" A: ^2 ^! [) d, ~$ A
机构学 mechanism% N# Z+ ~( m* M: ]% R* C* y
机构运动设计 kinematic design of mechanism
; \8 c( M- U" |机构运动简图 kinematic sketch of mechanism
" N1 t; t, |7 B1 s. ~机构综合 synthesis of mechanism
! \# h G3 U+ I/ [7 ~" R# A机构组成 constitution of mechanism
! Z7 Q5 ^( l$ v" U机架 frame, fixed link
4 N1 G- G9 b4 l4 {/ x* I机架变换 kinematic inversion
2 F3 S" F; _2 c7 L) {* q. C机器 machine
]8 }0 B, h6 R7 |机器人 robot; ~+ \1 `& T4 I
机器人操作器 manipulator+ O I' E' Y+ p5 d* ^
机器人学 robotics$ m5 W+ p; R8 I# w) J, v( G8 B
技术过程 technique process8 S3 d1 i4 @ v
技术经济评价 technical and economic evaluation
8 J$ d1 k) S) j4 [6 C( o) |技术系统 technique system/ V1 y! D7 z( C
机械 machinery
6 l9 m! j0 `; H" E: J( O! O4 u机械创新设计 mechanical creation design, MCD
4 n4 y0 V( ]; L; l1 e/ P机械系统设计 mechanical system design, MSD
9 Y7 Q8 f) Y7 f机械动力分析 dynamic analysis of machinery3 o+ e1 h' S$ c* V
机械动力设计 dynamic design of machinery$ V1 o& w0 l! D
机械动力学 dynamics of machinery
9 X. l* Y; }$ B7 L机械的现代设计 modern machine design
# F2 B6 d$ h7 {4 D! e. l/ @机械系统 mechanical system- P. h; C0 \5 Z* `; x3 b" n1 W
机械利益 mechanical advantage
# H5 T+ Q$ F4 J9 C机械平衡 balance of machinery
8 Z0 @, \# ~6 p L4 d0 h机械手 manipulator4 _7 V* h9 z& Z! s7 C! N
机械设计 machine design; mechanical design
7 x1 w @: b/ A4 A( s! K/ r# |, x( ~机械特性 mechanical behavior
w( w. Y, x! z( [6 O( C机械调速 mechanical speed governors0 S$ o- W: `/ n
机械效率 mechanical efficiency9 D, s: K/ R9 k* @
机械原理 theory of machines and mechanisms# u9 q$ y( k8 s$ B3 W7 n0 x4 x, p
机械运转不均匀系数 coefficient of speed fluctuation
/ [4 y4 O+ ~: g* T! }4 ]机械无级变速 mechanical stepless speed changes
' L, l/ L+ }0 |8 A. `基础机构 fundamental mechanism7 {& W1 @4 O5 H7 k/ |% L; |* A# O+ N
基本额定寿命 basic rating life" Q3 c5 \2 j0 l' I
基于实例设计 case-based design,CBD# u+ t0 q7 A, S
基圆 base circle8 m( N# L0 R4 ?1 Q
基圆半径 radius of base circle9 C2 n# B$ E* p' I* O$ ~+ r
基圆齿距 base pitch
* y' r5 }$ b Z$ z1 L0 b基圆压力角 pressure angle of base circle+ v1 h! n( X9 ?9 P7 N8 g" K3 `
基圆柱 base cylinder
8 V. H$ ?/ M: S基圆锥 base cone
O0 O4 W/ E2 f# F& }8 S# o急回机构 quick-return mechanism
; V0 {; w. M: S; W! D8 B急回特性 quick-return characteristics/ s) V, ?: b( t! y. O
急回系数 advance-to return-time ratio: v) ~5 w3 i g
急回运动 quick-return motion
. u' S+ x" ?2 E棘轮 ratchet
! ]9 L# C" {, U' T6 j+ t棘轮机构 ratchet mechanism$ j/ o: a/ P2 ?9 Z/ g7 V' d
棘爪 pawl
. }- I5 G& B( w* i极限位置 extreme (or limiting) position6 N2 y4 {5 a, s
极位夹角 crank angle between extreme (or limiting) positions8 q% r1 C' x+ T& \
计算机辅助设计 computer aided design, CAD
' Z! C; B: {: ?, q/ t" y' O计算机辅助制造 computer aided manufacturing, CAM
& Y/ S+ f1 l# d1 l计算机集成制造系统 computer integrated manufacturing system, CIMS; v: A( X# [5 {8 K% Z1 A! w# t5 _
计算力矩 factored moment; calculation moment$ Z( U3 ~9 W. A7 u0 K
计算弯矩 calculated bending moment
! h* {9 b; d4 \1 m加权系数 weighting efficient
# f7 c) [# k2 ]: `1 N4 J" e加速度 acceleration
( R* F! r: ^' y9 S' M, N# z加速度分析 acceleration analysis
2 W+ d% B ~% [加速度曲线 acceleration diagram
- @/ q0 Q; q1 e. M8 }" J3 s7 ~尖点 pointing; cusp. [9 F! N f. H
尖底从动件 knife-edge follower/ ]8 d+ ]7 n {, E, W) c
间隙 backlash
\( ^' N( y' r$ c间歇运动机构 intermittent motion mechanism
' F3 [/ }+ y; y0 t减速比 reduction ratio6 Y& M" U, [. W! e" l
减速齿轮、减速装置 reduction gear
2 O& k( |- j! ~+ O减速器 speed reducer
7 h/ O& { M5 U8 U/ I. b4 Z减摩性 anti-friction quality$ Z: @6 H0 A- ?) r* N' b1 s9 X' ]2 D
渐开螺旋面 involute helicoid
4 u7 r& w: f% O渐开线 involute4 S1 p% T& ?" g' k
渐开线齿廓 involute profile k7 ?1 R2 Y0 m
渐开线齿轮 involute gear, L! C! ~; j. k3 O& [
渐开线发生线 generating line of involute* O5 M% c+ `4 K5 z! }9 ?) j
渐开线方程 involute equation
: C1 w& Z8 d* P5 R渐开线函数 involute function
8 o' V3 ?. Q2 u. T8 K渐开线蜗杆 involute worm
1 E& R! Y9 F1 D; O' X渐开线压力角 pressure angle of involute' \: S/ v0 P( U8 r
渐开线花键 involute spline
L" _ \/ \* X& e L简谐运动 simple harmonic motion
& D2 O5 }2 L' K/ ~( Y0 c键 key |
发表于 2008-2-21 11:37:30
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