对称循环应力 symmetry circulating stress8 _$ ?0 D4 Y5 K* L
对心滚子从动件 radial (or in-line ) roller follower
* K3 O6 x# Q1 q5 `: q i% q对心直动从动件 radial (or in-line ) translating follower5 V9 l1 H4 D+ Q. H% Z4 b
对心移动从动件 radial reciprocating follower
_& `) g+ _) W) m3 u对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism
/ S" D! f; v5 m4 [; ` m4 S5 m多列轴承 multi-row bearing
( P) Q/ _- o" V7 h9 H( m6 w多楔带 poly V-belt
5 T; M" ], k' w1 }5 o9 K: ?多项式运动规律 polynomial motion
- f$ g. [! m& }5 Q% m多质量转子 rotor with several masses9 w( Y' n% g/ M7 E) N: ?# t' g4 T
惰轮 idle gear
) w1 j9 Q7 d H* |8 o x' r额定寿命 rating life0 @9 A; z/ B% r( C& q+ h- d
额定载荷 load rating9 l2 g% J* R: Q
II 级杆组 dyad
3 j1 u2 u7 V R) Z* R0 u9 n发生线 generating line 5 Y& I' m2 l" P" t) ~+ ]( {
发生面 generating plane 2 L* @# {8 p) o; X: c
法面 normal plane
% A! a7 O8 A" O1 \' N- s* j法面参数 normal parameters. @3 B& [, L" w" c+ J
法面齿距 normal circular pitch9 R8 A# h& O$ Y3 m/ C f* ?, o M
法面模数 normal module
9 ~3 d# B3 B) |5 ^法面压力角 normal pressure angle" h& @/ f+ g5 F. q
法向齿距 normal pitch) y0 N9 t3 @: L. M' S; K
法向齿廓 normal tooth profile
4 {; u$ U7 U8 g/ E' W4 `法向直廓蜗杆 straight sided normal worm
. q1 }, Z4 |# b& ]" ?6 \& `法向力 normal force4 D& q0 I* ^- H" Z' l- C( x. `
反馈式组合 feedback combining
7 f& N$ J; h) x; \( \反向运动学 inverse ( or backward) kinematics9 d/ b, n& ~) d& l
反转法 kinematic inversion
0 k0 P+ H( M5 d/ u8 b8 n反正切 Arctan8 Q9 N$ r' A" ^" y% I- w" N
范成法 generating cutting f6 r$ e5 |, y" U9 s9 N! ?
仿形法 form cutting
6 ~1 r! [4 t: G7 @1 [方案设计、概念设计 concept design, CD! T& V2 R& S, `% ?
防振装置 shockproof device
7 l0 R* B' w" `/ E" W飞轮 flywheel8 W1 ?1 B3 M$ a+ B
飞轮矩 moment of flywheel
4 N% F" r/ a: F* R# g( S; h非标准齿轮 nonstandard gear2 z1 h! E' [; D. F. ?1 c1 O
非接触式密封 non-contact seal
/ I5 ` K3 c; w2 T& o) u& J非周期性速度波动 aperiodic speed fluctuation {) U m4 U: F$ ^
非圆齿轮 non-circular gear& r. y) z+ K! p( m) Z ]$ b3 _ O
粉末合金 powder metallurgy4 X6 V+ S" N# G3 l6 C
分度线 reference line; standard pitch line. R. G/ T2 ^8 Y5 `. O" @# E
分度圆 reference circle; standard (cutting) pitch circle
" Z7 f$ [7 [( g' q分度圆柱导程角 lead angle at reference cylinder1 |, p) b& F% Y4 X6 v
分度圆柱螺旋角 helix angle at reference cylinder
4 |7 {* l/ v$ T ~分母 denominator; |1 Q1 g; ]3 x* q
分子 numerator
`8 r0 Z/ f6 m5 `# ^分度圆锥 reference cone; standard pitch cone
8 b- e. X% u7 j* m分析法 analytical method4 A( O0 S5 G- d+ o
封闭差动轮系 planetary differential
2 j3 G9 K9 \) [+ l复合铰链 compound hinge! k P. r+ X3 T) C7 ~6 e' h" i
复合式组合 compound combining1 o% D0 f* X; G0 n% g: s
复合轮系 compound (or combined) gear train
+ w5 d3 j- ]6 G( B& D复合平带 compound flat belt
: \8 O, e1 S/ ]6 l7 [复合应力 combined stress" R7 H. I* G2 H! \6 r7 s; }
复式螺旋机构 Compound screw mechanism4 X7 S& R1 |) j& \# \8 D
复杂机构 complex mechanism
8 h: A* \' E/ o. q' i, e杆组 Assur group # }8 ~/ n$ b* Z/ v) X% G2 I
干涉 interference - u S' N1 I9 A3 N
刚度系数 stiffness coefficient! \7 k# H+ a1 u( R2 y, Q b' k
刚轮 rigid circular spline
5 M( \1 s6 K- i* I: r钢丝软轴 wire soft shaft& y3 s/ E J. E. y
刚体导引机构 body guidance mechanism
; T, }5 W3 L/ D- q; e, C3 @. [刚性冲击 rigid impulse (shock)
9 k$ I" p& E# D3 [9 j# F$ h: l刚性转子 rigid rotor
5 u- H |/ G* K! W3 A y# t) Z刚性轴承 rigid bearing
. g. n* O2 Q, ^: p2 n刚性联轴器 rigid coupling
! B! m7 A; L3 G* {& @高度系列 height series
- s- H: P; S! f7 E v高速带 high speed belt) |4 F2 K0 {- j: k. s+ U/ v
高副 higher pair
7 X h2 ]+ I! m格拉晓夫定理 Grashoff`s law' }: `' b( A/ h7 }
根切 undercutting
+ d, n$ ~+ ^: |8 A公称直径 nominal diameter+ w: I4 }3 X0 u( R
高度系列 height series* s* y# Q- `: t# Q% t
功 work! N6 l) L5 G0 s, g! y$ {
工况系数 application factor# u/ H+ K0 b2 ~9 c: A
工艺设计 technological design7 b" Z) k; { b9 V& a; K
工作循环图 working cycle diagram
) Q& b& l0 j x, X$ e% ~2 v工作机构 operation mechanism
$ R1 F: n! `3 @3 z工作载荷 external loads' E5 V/ K3 X3 |3 L5 v" T; ~& g
工作空间 working space
( g7 N" g6 Q' k: _; l工作应力 working stress
4 e! d5 u$ e1 m& e; k) M工作阻力 effective resistance4 P8 ?! D- A# r, f
工作阻力矩 effective resistance moment1 p* R. K- _ I' [
公法线 common normal line) a9 n4 X7 F' c' k
公共约束 general constraint3 k- J0 C; @4 L2 n
公制齿轮 metric gears/ X: `( ?1 Z. F. V/ g2 n T+ d
功率 power
+ q5 S* B; E( Y7 m N* _. V# k功能分析设计 function analyses design* w! d4 B% w* ^' p# G
共轭齿廓 conjugate profiles
& Y/ B2 H( W5 [. S共轭凸轮 conjugate cam
, S9 e% s- Y# D' o0 G构件 link. J2 j3 g, A) U L
鼓风机 blower8 |/ a: \* w- Q( }0 q4 w
固定构件 fixed link; frame
( ?8 x% I6 K' A固体润滑剂 solid lubricant
- r$ x- V2 c( e# w9 }- K$ B关节型操作器 jointed manipulator
1 T' g# ?* u+ t1 Z惯性力 inertia force8 |$ {# R, y6 }6 D6 t9 m# r. f3 b
惯性力矩 moment of inertia ,shaking moment
3 U9 ?" @4 m% T. C E惯性力平衡 balance of shaking force2 p8 L4 C6 f, }/ ?% e X8 O
惯性力完全平衡 full balance of shaking force9 m1 [1 N0 F! q
惯性力部分平衡 partial balance of shaking force+ {7 z3 Q7 W3 [. `) s
惯性主矩 resultant moment of inertia1 ^3 `' U4 D9 f2 M8 m! [
惯性主失 resultant vector of inertia
3 z7 M8 U1 J0 D* a/ c/ H$ u冠轮 crown gear
' a6 E. F+ V( `/ B% [% Q广义机构 generation mechanism
* f5 R9 s6 Z9 X0 N) m4 u0 U广义坐标 generalized coordinate/ g0 ^$ h, ]1 P9 R4 i) R
轨迹生成 path generation# L- U! O+ ^2 i& X9 R
轨迹发生器 path generator
+ o$ x- s- f# D E" k0 Q$ M* D滚刀 hob: y$ s2 A$ U: O$ P# ~
滚道 raceway' [" Z$ v* F( l/ [& S
滚动体 rolling element3 I! X7 a4 C3 F) M
滚动轴承 rolling bearing5 o2 U$ _* A8 M3 e1 X% k; @6 I& j9 a% |
滚动轴承代号 rolling bearing identification code" j1 I ^' [; W, p$ L
滚针 needle roller
7 L" G7 h+ S0 B3 f滚针轴承 needle roller bearing* ~! s5 s% E$ p! C1 s& t. n; c
滚子 roller9 F- O2 r' Q* D: C$ y' H
滚子轴承 roller bearing
) J- y; p0 K, a滚子半径 radius of roller
" ^) `& Y9 q: Y+ a& D; m7 J滚子从动件 roller follower
% `$ A- A1 o5 [% ~' R. }滚子链 roller chain
3 A3 f% ]# _: u" J; u9 o滚子链联轴器 double roller chain coupling$ d. D; p0 Y* s4 b2 g; h# [7 M' X, G
滚珠丝杆 ball screw
4 S+ x" u; X# B2 A滚柱式单向超越离合器 roller clutch4 d0 J4 A+ i; M4 m& Z; j- h* k8 C
过度切割 undercutting. G1 Z3 o& ~+ R2 p& T! X
函数发生器 function generator
; f$ q- H: e) A$ W函数生成 function generation
: l9 \; H8 T! n' f含油轴承 oil bearing
" a5 s6 E* C2 `. R( z! j耗油量 oil consumption0 d2 V: t, N) Q% A" @/ Q7 b' }* N
耗油量系数 oil consumption factor
) v. V6 n# a8 C, ~+ M W赫兹公式 H. Hertz equation
$ Q" }8 v' c9 g5 ^8 \5 W5 D合成弯矩 resultant bending moment
% I% O, |; r4 A; C; x o# X* P合力 resultant force
Y$ W; e) ]2 |5 O. }" ^合力矩 resultant moment of force3 B. i" U! A: Y+ x0 x' l7 J4 O* ?
黑箱 black box
. D2 W- K! j$ f- c7 X横坐标 abscissa
1 I* d* a: _: C2 n5 K, S) m2 n互换性齿轮 interchangeable gears
, ?, R! J8 @$ l! g$ @9 o花键 spline
8 b8 l' ?# |+ l2 L滑键、导键 feather key
9 G: M2 K2 S$ x* `4 { r" j滑动轴承 sliding bearing R. E! z9 E& a0 k' W# Z9 K
滑动率 sliding ratio1 a) O2 j. e( ]0 q' H& o- g
滑块 slider
5 t; T' m, U0 _9 w2 u- r$ l环面蜗杆 toroid helicoids worm5 G5 y% z/ D6 F3 O( h. E
环形弹簧 annular spring
+ ?+ C; q9 [( d0 T7 ~; ^/ N/ w4 t; W缓冲装置 shocks; shock-absorber! M5 n0 m h- r. w
灰铸铁 grey cast iron) N5 f' s: i" O( j, H& O
回程 return) s* H6 ~# d& y' B$ B3 G0 h( R4 f) Z
回转体平衡 balance of rotors% I& e) b, s7 d0 J* k! ~8 N
混合轮系 compound gear train
. b% |1 a! c3 `* h7 T, o积分 integrate
% P4 z% M8 B4 k( B; `* `机电一体化系统设计 mechanical-electrical integration system design
0 [% L$ J7 E" ?( n9 d机构 mechanism8 p) B6 b- L5 y: I$ _; g
机构分析 analysis of mechanism6 v8 k$ Y# C; G, S7 [
机构平衡 balance of mechanism* y( N$ |5 I* ?. t
机构学 mechanism
6 i* j$ E7 J$ i( d机构运动设计 kinematic design of mechanism
+ k, f `$ H- a9 e机构运动简图 kinematic sketch of mechanism
6 B; K# B: d. _0 G$ Q机构综合 synthesis of mechanism. I/ C( |/ M2 i T) i* O
机构组成 constitution of mechanism7 E$ \- g$ [2 Z
机架 frame, fixed link" V! \! P, s3 z1 k( _& B
机架变换 kinematic inversion
" i+ \2 a$ X, m' d! {$ l机器 machine$ Q+ Z& S- }$ r0 p
机器人 robot
6 Z1 Q [: n8 h% K3 K ^, A$ ]机器人操作器 manipulator
2 o! g) B0 R P4 v9 \3 u/ k4 k机器人学 robotics0 g. o7 v) }9 O4 e+ p$ }) L# w6 i
技术过程 technique process3 M5 d# ~8 u& d7 t1 c( t- N3 ~/ G
技术经济评价 technical and economic evaluation7 o% ?- x w, p7 }( i) O% @! C
技术系统 technique system
2 {0 [) ~) G7 A7 j机械 machinery9 @! P3 y& `4 P; X4 P2 W) [- {5 K
机械创新设计 mechanical creation design, MCD
4 N, U6 p" q# |+ T; H机械系统设计 mechanical system design, MSD. B7 A# D/ c' Q2 ~1 D' q
机械动力分析 dynamic analysis of machinery
% m, i- x: f/ q+ v) W/ s机械动力设计 dynamic design of machinery
1 F [! v9 Q" g3 m机械动力学 dynamics of machinery
1 d0 v$ }# T5 J$ G8 _/ T/ p. m, f& F机械的现代设计 modern machine design
$ B' j: a* b9 I$ d, H机械系统 mechanical system* r% V: p* s+ U# f$ g! o- s6 O
机械利益 mechanical advantage
0 ?6 G) d. z1 m Y3 J$ H* o: R8 d机械平衡 balance of machinery, v* Y; V7 G) j8 B& J% o+ F
机械手 manipulator) l' f0 {5 U, P- E6 t* y/ j: ?$ r
机械设计 machine design; mechanical design
4 J( o4 s+ e4 U c; N* t- x- t机械特性 mechanical behavior
' m' |* j7 c" Q2 g9 @4 ^4 Q机械调速 mechanical speed governors0 A* w# r3 R, U9 {
机械效率 mechanical efficiency; N4 R! w) A( L8 a; w0 M% }0 o6 u: h
机械原理 theory of machines and mechanisms/ I7 @/ _/ {/ |# B; S5 Y/ Z
机械运转不均匀系数 coefficient of speed fluctuation
+ k1 }1 Y# G; @ M机械无级变速 mechanical stepless speed changes
7 ~5 o5 D5 z a' X基础机构 fundamental mechanism
, \0 k) J) Z4 B; I基本额定寿命 basic rating life ?; t3 y7 D6 E5 y9 H
基于实例设计 case-based design,CBD+ g9 p# S- u4 R. r) |1 Q
基圆 base circle5 C/ Y1 {' V6 g& |
基圆半径 radius of base circle8 a) _# r, E) J& ?2 d: v# z
基圆齿距 base pitch* D6 E ~: B( J- p. T- x- x
基圆压力角 pressure angle of base circle
@4 j Z) Y( d基圆柱 base cylinder
# b6 c4 z1 G" G! V基圆锥 base cone
9 j! ~7 s$ F- C, w. t! ]3 S; l- I急回机构 quick-return mechanism. O, m2 ]! I1 P$ Q$ f7 T! l
急回特性 quick-return characteristics
1 R8 Z. J: ?" G急回系数 advance-to return-time ratio
1 W. W2 q4 f! h; E* b急回运动 quick-return motion" E4 b* m4 i9 K3 I
棘轮 ratchet4 O6 x# ^5 j! [: R0 S1 C% F9 L
棘轮机构 ratchet mechanism
3 P2 I$ N; p' l5 R% A6 \棘爪 pawl5 X& y% U3 }8 R3 R, B$ r1 d
极限位置 extreme (or limiting) position: r8 t F& \5 l/ u1 j8 ~; Z( f
极位夹角 crank angle between extreme (or limiting) positions
% }2 a& I' {- f+ i0 |$ O: ^计算机辅助设计 computer aided design, CAD1 A+ e& Z1 y1 V- V8 l l8 v6 H! }0 B
计算机辅助制造 computer aided manufacturing, CAM. F- |! i* [* @, ~" @0 Z4 w. n
计算机集成制造系统 computer integrated manufacturing system, CIMS2 t( g$ }# ]% o K/ O
计算力矩 factored moment; calculation moment6 m$ R0 U' H" Y9 q
计算弯矩 calculated bending moment
/ O( y" n& P1 H0 Z" S! U/ D加权系数 weighting efficient
) h1 }" [7 h1 Z$ N加速度 acceleration8 q+ | |" x! D) z$ P( a, N
加速度分析 acceleration analysis0 C4 D) F; U6 L3 M
加速度曲线 acceleration diagram
) M2 R) c6 b& ?# D尖点 pointing; cusp6 N+ X4 b. c3 A) s9 O8 p; d: V
尖底从动件 knife-edge follower
' e2 `& m6 n* J间隙 backlash4 O7 z4 J# ]; c+ L; [1 n# l
间歇运动机构 intermittent motion mechanism4 H3 A( V3 M2 M: O
减速比 reduction ratio, J! n+ |1 g: @; v* S
减速齿轮、减速装置 reduction gear
0 @- r5 K1 [7 v# X$ l减速器 speed reducer
0 N, E! a# n, w% v; ?减摩性 anti-friction quality6 d) {3 S( W" @, ], y$ }+ {" L* ]
渐开螺旋面 involute helicoid' y: O& V5 h! C
渐开线 involute
2 R0 p, t M) Y渐开线齿廓 involute profile p5 _3 Q; Q$ [! g
渐开线齿轮 involute gear
/ ^4 a/ N/ R+ Z' D' i0 S渐开线发生线 generating line of involute& H( I& v" `" \5 a( J) l' [. R
渐开线方程 involute equation1 T4 ^7 H2 j7 z. S
渐开线函数 involute function* [ j {" f+ j* u/ ~3 k( ^
渐开线蜗杆 involute worm) c- a% ]/ ?& X3 l3 I
渐开线压力角 pressure angle of involute9 n7 f, W( g5 Q3 p
渐开线花键 involute spline
5 b0 L: x8 x8 M5 T简谐运动 simple harmonic motion
& o! ?& d, H: w3 B$ ? w. b3 `键 key |
发表于 2008-2-21 11:37:30
