对称循环应力 symmetry circulating stress9 @! e9 ]- J! O6 Q' i& H1 ?3 C0 |
对心滚子从动件 radial (or in-line ) roller follower
+ E0 g% |0 O% l9 U& F对心直动从动件 radial (or in-line ) translating follower O# @5 s6 `6 k& ~
对心移动从动件 radial reciprocating follower9 V& R8 V5 i- U4 \' t4 o0 e
对心曲柄滑块机构 in-line slider-crank (or crank-slider) mechanism
3 C" N4 g. ]2 I: m$ A% K3 ~多列轴承 multi-row bearing
5 _6 l# D5 A( m! h; O6 t多楔带 poly V-belt
2 B3 a6 K; P6 c3 X2 _0 B4 D u多项式运动规律 polynomial motion- K% ~$ ?, H3 g: g4 H+ |
多质量转子 rotor with several masses
( E7 X! z* P9 O5 {惰轮 idle gear
! O( V R2 k. v7 E# [( B# A额定寿命 rating life3 a! R7 a2 b* r. U
额定载荷 load rating d1 e) S2 I5 o k1 m
II 级杆组 dyad
5 r0 G3 w Q! c/ P发生线 generating line
) E+ R; r% |" s$ t: M发生面 generating plane
( b3 v1 H. Y7 K. c法面 normal plane; b# o, a$ S1 E2 X
法面参数 normal parameters- I( H# Q* b! N' V. G( r( D' k0 N
法面齿距 normal circular pitch
) s$ i% z" k# g4 b/ H3 \法面模数 normal module2 y$ Z7 R" d1 c/ C
法面压力角 normal pressure angle
! {7 [# D, ?4 X0 o$ J: l法向齿距 normal pitch
0 m2 ^, t! b( o' u+ U* ^: L) h法向齿廓 normal tooth profile
! s% v7 x& Y. s+ j/ B7 W$ p3 U8 h法向直廓蜗杆 straight sided normal worm* k8 j4 l+ L! k
法向力 normal force
- W3 e a" |9 O4 l" C6 I反馈式组合 feedback combining
) f1 l. V1 h; R7 G7 K8 B! @/ X" I1 x反向运动学 inverse ( or backward) kinematics4 u/ E/ N7 r. R' i/ v8 G F
反转法 kinematic inversion
: R) b* q: v% P7 J* E反正切 Arctan
" h4 G* J; |2 d; O# K范成法 generating cutting
$ {( h" d$ d9 J! ~, Z+ T: D仿形法 form cutting
! w7 ^8 k [1 e. c方案设计、概念设计 concept design, CD
$ s4 o+ T! @' B6 }防振装置 shockproof device
6 m0 @# i2 I8 {4 x- W l( h0 J' b+ r* F飞轮 flywheel
V! z7 y$ q1 _/ K3 P, G3 Q飞轮矩 moment of flywheel; X. I2 t: w% l; r* O ]( r
非标准齿轮 nonstandard gear. i$ V9 ^0 l. ^# G
非接触式密封 non-contact seal
Q7 {2 j. A" {" d非周期性速度波动 aperiodic speed fluctuation
6 V3 k2 o7 a3 L$ |4 f+ \, B3 p非圆齿轮 non-circular gear, E% s, D3 {5 Z; u- Z
粉末合金 powder metallurgy( i% m1 @% ]' F/ v6 ~& I' m
分度线 reference line; standard pitch line$ D$ F6 L. P2 X8 [
分度圆 reference circle; standard (cutting) pitch circle
7 Z# q' B6 M$ H# s分度圆柱导程角 lead angle at reference cylinder
; Y! h5 l2 a, C1 Q- `" `分度圆柱螺旋角 helix angle at reference cylinder/ V4 h- r7 y$ u, j
分母 denominator
2 I Q9 y' D- r+ X. h1 l3 w分子 numerator. P' t" j) f# Y) ] }* }$ z' U. B* m$ u
分度圆锥 reference cone; standard pitch cone9 m) r. |' f; t( |& G% O, h
分析法 analytical method
/ f! Z0 J+ F* ?$ F, |* l! ^5 T封闭差动轮系 planetary differential
" o) t5 q* X; F1 ~/ s* m0 m7 W# b复合铰链 compound hinge
% Z: d. [% i5 l- }4 B. l复合式组合 compound combining
8 k+ h& {3 c# z4 Q6 d5 b复合轮系 compound (or combined) gear train
) {& x8 a& a9 r! v8 K% p, O# A# F复合平带 compound flat belt$ P" @: c" Y* B) W( S
复合应力 combined stress2 m# Y3 A6 d# c
复式螺旋机构 Compound screw mechanism
3 m% Z7 J. N! F复杂机构 complex mechanism" o" d% `6 o0 P( `' ^' B4 n$ Y6 x
杆组 Assur group
6 z: ^* S& K' Y3 A6 ~$ [干涉 interference ' E# \) l1 c$ S- q/ c; {% c
刚度系数 stiffness coefficient
) b! }0 s ~; Q$ L& N刚轮 rigid circular spline
& l# d5 s2 n7 ~2 ~, s; a钢丝软轴 wire soft shaft( Y2 l) b+ g" B4 i- S1 H
刚体导引机构 body guidance mechanism
& v7 @. o9 R# ]0 c刚性冲击 rigid impulse (shock)
7 E5 ? B5 V+ A刚性转子 rigid rotor
: J9 e" v8 {3 ~; G4 l4 _, ~刚性轴承 rigid bearing
" _" b6 z/ h1 L. j$ f9 ?; l刚性联轴器 rigid coupling
* O0 ^$ O4 G. E% j! ?" s4 z高度系列 height series6 x$ X! I2 T, |( W6 n
高速带 high speed belt
: C+ X: }9 `7 N7 K! {7 Y- s0 w高副 higher pair- P( F! p& G9 e1 s' w, o& ^
格拉晓夫定理 Grashoff`s law/ N& U- m& ]) `7 c5 R0 R
根切 undercutting7 ^' c0 r; T" P- ?6 c7 X
公称直径 nominal diameter
8 L8 c; H3 ]9 Q; ?高度系列 height series
$ J5 A( n. t$ X) E( Y功 work
/ m& a @+ ^3 c. P' a6 Z9 a工况系数 application factor
1 j9 `! j! A6 f$ n* Q3 S工艺设计 technological design
7 a& r; e7 ~ H& S工作循环图 working cycle diagram
0 w g1 E- e, M7 \工作机构 operation mechanism
B4 n5 ]% D. }5 |6 R9 W% U9 V) H( D工作载荷 external loads
' Q& H" q2 B; V3 Y9 @( D! E3 h工作空间 working space) Z: k) t. ~7 E& k
工作应力 working stress
' ?/ I) |/ f: s' ^* t( p7 ~7 q( ^工作阻力 effective resistance# l6 [9 R- O. I
工作阻力矩 effective resistance moment
! U: W# v/ M0 C! M( X7 _6 }7 u5 }8 ]公法线 common normal line
3 l3 ~: n2 r. u3 Z+ K3 x+ r2 ^8 j) y公共约束 general constraint
0 F4 I# f( d( s& c1 i9 V! k: q公制齿轮 metric gears
$ t7 q! U! U# g3 k$ ]: {功率 power
0 Z; o' q0 w" l- q& n8 u功能分析设计 function analyses design
* g; L3 `0 V0 ~4 ~; P- O共轭齿廓 conjugate profiles
3 x2 k* R) b) p) z( q8 j共轭凸轮 conjugate cam
1 G& U$ B6 W6 e! i1 c: V# b& M构件 link
6 b9 M/ Z$ W, y! `鼓风机 blower
- v4 A% E: X7 J. V固定构件 fixed link; frame
: I: X* R5 D( K2 t1 }( C) a固体润滑剂 solid lubricant
7 ~3 K2 o @6 \2 I7 L0 L关节型操作器 jointed manipulator* N' G) w9 R, R
惯性力 inertia force
' N( D/ A7 q% c6 f; E- G% \惯性力矩 moment of inertia ,shaking moment
' n$ N$ ^! Z1 \+ ?; V# d3 I u8 ^惯性力平衡 balance of shaking force- j! t) p) q8 I4 D9 a( g
惯性力完全平衡 full balance of shaking force3 R) P$ U6 U; L5 i
惯性力部分平衡 partial balance of shaking force/ n5 S$ K' p* V! I
惯性主矩 resultant moment of inertia$ B4 l" O) f) }( }3 o* H
惯性主失 resultant vector of inertia$ j, k5 R$ T5 X4 ]7 @
冠轮 crown gear
& `; ~' x- \" z! t% Z2 l2 V8 ~广义机构 generation mechanism- C- a4 ~. ], c, x+ z8 w& m, \/ j
广义坐标 generalized coordinate3 V% H3 n) y8 Q" h, Y. g' F7 ~
轨迹生成 path generation! O0 w6 F+ A( L- A
轨迹发生器 path generator4 G$ e; i2 ]1 f/ o; N
滚刀 hob
( _8 {/ x* L' k% P% n1 M$ M滚道 raceway2 L$ n! X- a+ ~% d% @3 \. u+ e
滚动体 rolling element4 Y" }4 i9 }, b: f% S; s4 [
滚动轴承 rolling bearing
- b( \% F+ Q: x0 G0 R+ p7 D滚动轴承代号 rolling bearing identification code
, n7 z0 o C6 T7 J5 ^ a" x6 k9 L滚针 needle roller& r9 D9 h, F. b7 I
滚针轴承 needle roller bearing1 }0 N: Y8 u2 M$ ~( f
滚子 roller
9 q+ G& ^5 n6 z# j1 ~+ Y" {1 b滚子轴承 roller bearing# l, o4 B& X, z; b7 z% f- c) w
滚子半径 radius of roller
% `1 i/ Q* N$ y" L" ~; W滚子从动件 roller follower
" U; x" }4 ?) ?6 K* a- B) E滚子链 roller chain. H, v# o+ T3 x
滚子链联轴器 double roller chain coupling
, U4 u1 B( B9 ]0 M5 L滚珠丝杆 ball screw. E; L/ L) S4 q- O3 i+ i% y
滚柱式单向超越离合器 roller clutch
- u! n: w2 H6 `6 p0 a1 B4 O过度切割 undercutting
! N3 L( x# T0 d, f( j; h函数发生器 function generator ) E+ J' }# e) t
函数生成 function generation 3 V# g) U/ a5 W' g
含油轴承 oil bearing
3 e3 D% C$ O8 J: `% g/ W* N1 x4 H耗油量 oil consumption
: G9 |5 a, x& I% q0 U耗油量系数 oil consumption factor
8 U- G; B' G, Z7 Z; k赫兹公式 H. Hertz equation
" K6 K. ?! D: B# G合成弯矩 resultant bending moment% n5 s, I% h* ]7 B+ t
合力 resultant force: L/ A1 X7 L% k1 e/ @! _" J
合力矩 resultant moment of force1 L* y0 U- p. s4 o' K O( h6 d# d
黑箱 black box8 v! l) q9 w3 _
横坐标 abscissa
, E# H& s s6 c4 S; T5 P; m4 z互换性齿轮 interchangeable gears
V# X( {7 B" h4 F' o" |3 f& L0 ^1 z9 M1 a花键 spline- y1 a1 }% K. y5 s( x
滑键、导键 feather key7 s6 W; _( f. ]8 R% N' y9 t" p& D
滑动轴承 sliding bearing- D6 @ k" c- U. I) I& S' P" k
滑动率 sliding ratio
! p- f" i6 x5 E) R: L7 w; J4 R滑块 slider4 c; k) \( L$ R) K( \
环面蜗杆 toroid helicoids worm+ {/ }4 }( t( o5 P$ L2 z+ ], D
环形弹簧 annular spring
1 E& F+ C4 P- v8 C# c缓冲装置 shocks; shock-absorber
5 U2 B* a c, Y6 |; }" _灰铸铁 grey cast iron
& E7 `( [1 V e8 V% E回程 return
3 ~ j+ y" R' g" }: H' ^回转体平衡 balance of rotors
1 v$ B+ h9 Z8 l" d! e6 x; d% }混合轮系 compound gear train
* T0 q4 I% b" G! J$ ~/ k- X3 c积分 integrate
9 g9 A+ q' z! I+ U( S机电一体化系统设计 mechanical-electrical integration system design # |2 J2 t1 W: K% b! c$ k& K
机构 mechanism, k" c5 S3 m5 E/ }1 O
机构分析 analysis of mechanism& W; _" q! O" h$ d& I& K( n6 f
机构平衡 balance of mechanism
, f# k" O& |* T4 X$ c l机构学 mechanism
1 V; H, y2 F/ T, Y7 S机构运动设计 kinematic design of mechanism; u; J2 E! W8 N6 ~ ?
机构运动简图 kinematic sketch of mechanism* D. _! R! I, C
机构综合 synthesis of mechanism. `% m' h2 t! O( k1 m+ B. T. P, S
机构组成 constitution of mechanism+ P* x! R( W0 [5 q$ N
机架 frame, fixed link' L4 m# u8 C- Z8 G# `' u
机架变换 kinematic inversion( N2 o9 J+ S. w
机器 machine
S0 x2 f, b4 `( d机器人 robot/ o/ Z' ^8 @6 _) o7 O
机器人操作器 manipulator& L) X8 a4 y. Q6 M* J
机器人学 robotics
# D5 F. S2 K- B技术过程 technique process7 [' ]( Y# \ V
技术经济评价 technical and economic evaluation& T9 e) K3 y: v1 n0 J6 A
技术系统 technique system
" n* i( Y3 y3 L" l3 g机械 machinery" d( j, O, ?$ h+ |$ n' w
机械创新设计 mechanical creation design, MCD4 E+ y0 K/ t: `, y
机械系统设计 mechanical system design, MSD' l8 y3 P2 p! \9 q# v a/ U+ l
机械动力分析 dynamic analysis of machinery2 ~) C# P, S' E; ]6 U
机械动力设计 dynamic design of machinery
& N- Y" Z" T) d机械动力学 dynamics of machinery5 g! D2 s& A; {' L* i
机械的现代设计 modern machine design" z8 l& J2 e% v( D O
机械系统 mechanical system
9 D$ K4 ~+ r4 b# R/ H" l6 g# i机械利益 mechanical advantage* M+ A; r* E% V) H3 s) ?0 ^
机械平衡 balance of machinery
8 k( z! u. d2 H6 ~: B1 N机械手 manipulator
# t H8 d& T1 H% n1 G) [机械设计 machine design; mechanical design- n2 f1 r: v; O6 J
机械特性 mechanical behavior X" _2 W; e& z
机械调速 mechanical speed governors T- |! s: ~3 M Q _3 n
机械效率 mechanical efficiency$ P+ W% P' q5 C) ^7 ^
机械原理 theory of machines and mechanisms. z) i0 J/ u' w
机械运转不均匀系数 coefficient of speed fluctuation
8 b/ u6 x9 y3 q- ?' N2 B* O. k" z( ?机械无级变速 mechanical stepless speed changes
% z' ^! E: w+ ], s B0 g& T8 J基础机构 fundamental mechanism
( p! v) Y' H" }- H9 _ D5 X基本额定寿命 basic rating life+ N4 x, K p5 q# |) @* @
基于实例设计 case-based design,CBD
( m" y% `4 _: t" }# c0 a! h5 M& u基圆 base circle1 H" P% H* k& j ?$ ]
基圆半径 radius of base circle
( W0 Z( U) [7 Q! u基圆齿距 base pitch5 a- J6 J; z$ c7 N, t, H8 c
基圆压力角 pressure angle of base circle9 s# M) s% s6 Z. _! V. H3 \
基圆柱 base cylinder2 |1 Y! Q& z' i, V" P# g; x0 V
基圆锥 base cone
. X2 n) l7 S( o! t( ^& O m急回机构 quick-return mechanism& a4 }3 Q4 n0 l/ ?# b* x
急回特性 quick-return characteristics
( F0 A$ ?& D0 q$ B急回系数 advance-to return-time ratio, u" Z4 v* K2 e3 [# V
急回运动 quick-return motion- f+ D5 @& p2 _1 J& e
棘轮 ratchet
' A! j3 P; i* G: B2 ?棘轮机构 ratchet mechanism& A+ v9 b/ o; X# N
棘爪 pawl
8 T- j V! i( r0 l9 A2 J% F' m% R8 a极限位置 extreme (or limiting) position
% K# Y" x3 R/ M! |极位夹角 crank angle between extreme (or limiting) positions1 h0 u) j/ w4 Y2 W
计算机辅助设计 computer aided design, CAD' Z1 Y- s6 F- Y9 b
计算机辅助制造 computer aided manufacturing, CAM
2 C, s0 g4 r; e: u v- X* \# O计算机集成制造系统 computer integrated manufacturing system, CIMS
: p- [& |$ I4 c9 Q% Y( m5 f9 I计算力矩 factored moment; calculation moment1 q1 `/ P. v& k% J
计算弯矩 calculated bending moment h; D7 V0 O% ?$ I$ j5 ?& F9 g
加权系数 weighting efficient
: A) k4 Q+ s! i6 r/ N2 O; e$ d加速度 acceleration
w1 g- o3 |; u6 \. W加速度分析 acceleration analysis
8 V& k- s2 F; E* B$ b; s加速度曲线 acceleration diagram8 _) \5 p8 ^) p" u
尖点 pointing; cusp. }( b9 F: T" o9 w
尖底从动件 knife-edge follower
0 ?) R. u! L3 Q/ j间隙 backlash
' K8 C; S4 g3 b% E间歇运动机构 intermittent motion mechanism ]/ \% V$ Q% H/ X( P& ~
减速比 reduction ratio
1 E$ [& B7 _, N" j$ g/ f; E1 G( p减速齿轮、减速装置 reduction gear$ b. F9 X" h5 S: B3 T2 h
减速器 speed reducer
1 X! P$ R3 I' s7 G5 z减摩性 anti-friction quality; X1 z9 o _; ^, Y' d/ S p0 d
渐开螺旋面 involute helicoid
9 S1 {4 }. y1 n渐开线 involute0 K: X1 q+ Q `+ Q
渐开线齿廓 involute profile
) ?! ^, I- u3 |4 G渐开线齿轮 involute gear! G9 w& V1 ~; {0 d5 X; k
渐开线发生线 generating line of involute! U1 L ]# p9 Q4 O
渐开线方程 involute equation3 s* l* R5 ^+ `: q+ z2 U5 C
渐开线函数 involute function' W0 f: U. A" {+ C7 H! C
渐开线蜗杆 involute worm% Q. K1 C% Q, F4 h0 y9 y
渐开线压力角 pressure angle of involute
. F4 Q9 \' s( c4 f1 p* @渐开线花键 involute spline
2 j) W3 p' H4 j" Y1 Y8 L7 X简谐运动 simple harmonic motion
7 K7 V4 H% b) W5 c% M$ C键 key |
发表于 2008-2-21 11:37:30
