對稱循環應力 symmetry circulating stress9 k0 B) p& R5 _3 }" t/ h6 b8 U
對心滾子從動件 radial (or in-line ) roller follower
/ J, c p5 g# p- _& p! A對心直動從動件 radial (or in-line ) translating follower
7 z9 g2 [) ~ V對心移動從動件 radial reciprocating follower1 O# v+ C# x: f% i* S+ q g
對心曲柄滑塊機構 in-line slider-crank (or crank-slider) mechanism
- R% n6 }2 s& _" R多列軸承 multi-row bearing% d: e1 l F2 ]
多楔帶 poly V-belt
, k/ _( I, m4 N1 ], ~+ E多項式運動規律 polynomial motion1 b4 B/ L+ b# \- X) |- S9 {8 O
多質量轉子 rotor with several masses/ E# j. Y5 v# C* [1 f+ w8 S
惰輪 idle gear O1 I- s* T t1 D
額定壽命 rating life
! |4 L \% s$ J& d2 W: t9 n z8 X0 ]額定載荷 load rating
4 ?7 v& h* m7 P' CII 級桿組 dyad
- R. V* G: n( k發生線 generating line # z: z- j1 [" f) u Z
發生面 generating plane ! v8 V a8 t4 v
法面 normal plane
! c- \9 u% X3 _9 u, s法面參數 normal parameters# p8 L" ~2 Z# P: f
法面齒距 normal circular pitch% H" z, I: R3 M- h. f6 v
法面模數 normal module
) ]0 m/ [5 X, R5 ?/ f9 ^2 i* o法面壓力角 normal pressure angle& U+ M5 }& [4 n. F, V9 o# _
法向齒距 normal pitch9 P) ]7 I' T) H* _* }# {. n( J
法向齒廓 normal tooth profile N' f- I2 a! b: U& i
法向直廓蝸桿 straight sided normal worm
. o" p) C y5 X' d法向力 normal force
! j7 q! Y6 m9 i) s% u, Y) G0 L反饋式組合 feedback combining/ y' i3 O3 k& ]. e u6 A P
反向運動學 inverse ( or backward) kinematics' Q- \$ M8 A( ]5 t, c
反轉法 kinematic inversion$ E) j1 t0 `' N% s3 Y
反正切 Arctan- e# f" p0 U) G, f) A# U% a3 C
范成法 generating cutting
$ T9 n: x! R7 l( t! w8 o6 k仿形法 form cutting
8 V, F! C( w, R, K. R, l方案設計、概念設計 concept design, CD0 G5 l5 [. X* X
防振裝置 shockproof device
' A: @8 F4 o7 T4 |6 `飛輪 flywheel& V! ~1 z2 W4 n: z- u/ V
飛輪矩 moment of flywheel% Z2 v3 @8 `/ x3 E! k
非標準齒輪 nonstandard gear* P. o/ G! n# U. m/ G0 t+ b, m
非接觸式密封 non-contact seal1 _" s/ G( U! w! z/ G& P: m5 m
非周期性速度波動 aperiodic speed fluctuation
% Z; V# d, A* _" L/ u非圓齒輪 non-circular gear
! ~. h1 s& D" L+ n! Q粉末合金 powder metallurgy% A4 U% C$ Z0 k, v
分度線 reference line; standard pitch line; |/ P, F' J% v
分度圓 reference circle; standard (cutting) pitch circle4 f$ ^6 M+ V# _$ m* F
分度圓柱導程角 lead angle at reference cylinder
, t; P+ S7 p, d7 |分度圓柱螺旋角 helix angle at reference cylinder) {" [& H" O4 R6 q
分母 denominator
! ~9 z# d* u& H$ o分子 numerator% h3 S( L) ?3 g3 L- A
分度圓錐 reference cone; standard pitch cone0 B$ F z8 c9 J, y$ @$ m7 N
分析法 analytical method
& Y' Z: p0 @; i! J0 X封閉差動輪系 planetary differential
2 q, v y. r+ [! Q: F4 N, l復合鉸鏈 compound hinge
# I! R& d, E$ |; j9 R! G; P7 T復合式組合 compound combining
7 B, v' }3 z- z& y- J/ ?復合輪系 compound (or combined) gear train( {% F+ Z# R; f0 k( O, `7 N7 U
復合平帶 compound flat belt6 [/ u$ [( b' C% F+ M/ m
復合應力 combined stress( p% W$ }9 a5 n7 Z) a
復式螺旋機構 Compound screw mechanism
+ ]% w2 X" q h$ N8 }復雜機構 complex mechanism' a C7 K, y" f6 i1 B5 ]
桿組 Assur group 9 }0 t+ W; b/ E( o* C
干涉 interference 9 {: _9 E/ p- Z) \( H2 X5 U C& ?
剛度系數 stiffness coefficient/ o9 V8 @0 a+ d% a' q
剛輪 rigid circular spline
7 Z$ X) f$ S3 a鋼絲軟軸 wire soft shaft
; x. p f% y+ `6 ]1 j剛體導引機構 body guidance mechanism: L) U$ m5 y. L' Z! S
剛性沖擊 rigid impulse (shock); J) N- c( b& g- d3 d( P# ^) p. W* X
剛性轉子 rigid rotor
+ O: t7 i p' v9 b$ }" i剛性軸承 rigid bearing& s: h2 I& p* ~8 U, z
剛性聯軸器 rigid coupling8 q# }( i1 F, f/ q
高度系列 height series
+ v! P( S% A: ]! t9 C高速帶 high speed belt
- b4 O3 T8 a* h+ d9 A+ Z7 o7 c8 H高副 higher pair( w: C% ?, O: m* r0 \* V
格拉曉夫定理 Grashoff`s law, p) S! [5 P, C' Z, f* G
根切 undercutting+ e+ b- F/ W. j& h
公稱直徑 nominal diameter4 @$ e, Z/ n6 R- i0 _- `
高度系列 height series
" z& P, W [" u; u' Q/ e s9 u( q功 work
+ ?4 X# b! d( c! \5 R, G工況系數 application factor0 Z0 @9 _$ E X" N
工藝設計 technological design
: `) ]( d7 m# ]/ N$ |/ Q) c* q0 M工作循環圖 working cycle diagram
9 p) a% T9 `& S( o工作機構 operation mechanism
2 R( J! w& ~7 R! g工作載荷 external loads
7 o5 N% m" X6 k0 G工作空間 working space% l+ x+ D; V" H' Z* p2 |2 m7 Y4 ?
工作應力 working stress* A; y) B* G; r5 [( ~
工作阻力 effective resistance& d" S0 p+ ^4 u; S0 ^
工作阻力矩 effective resistance moment
% l0 v) |9 M& |8 G. o公法線 common normal line! `8 h/ o: h5 @& p9 T4 r% _
公共約束 general constraint6 j3 M J0 u c! s6 g( ^
公制齒輪 metric gears6 f) ?' D! b [0 e( ~
功率 power
f) k: Q( K7 r4 p; {功能分析設計 function analyses design, G% R; A9 U4 R6 L: S+ X8 o
共軛齒廓 conjugate profiles" u) I3 W5 p( w3 u9 h& A
共軛凸輪 conjugate cam, S0 R6 p* C7 }/ K
構件 link8 M( Z3 W. k$ H7 L& g, |1 ]: P
鼓風機 blower
- {7 ]+ B% c8 q1 l( v固定構件 fixed link; frame. C+ W6 S7 j* `& }, s
固體潤滑劑 solid lubricant# u/ H4 a& V7 ^( }- @9 L4 q0 R: u
關節型操作器 jointed manipulator! d; [ ~) S f+ a( A% U- K
慣性力 inertia force8 W5 `( p# `& v- c$ l8 x \6 [/ d. ~
慣性力矩 moment of inertia ,shaking moment
, l- S0 ~4 r8 `5 z慣性力平衡 balance of shaking force6 I- w! G0 w7 w: g$ p. a
慣性力完全平衡 full balance of shaking force8 c8 r* ] D% n4 r
慣性力部分平衡 partial balance of shaking force+ r3 A0 ^$ k+ k4 `! ?, l3 m
慣性主矩 resultant moment of inertia$ \8 T! g( m7 L
慣性主失 resultant vector of inertia1 w. L) m) l4 `& D/ U
冠輪 crown gear: V, z; ~; h, `& M; D; r
廣義機構 generation mechanism5 V: B- R5 @/ M3 |
廣義坐標 generalized coordinate0 P, U( ]; J; b1 y$ h) u
軌跡生成 path generation
! @/ [2 i4 T; r1 M5 j軌跡發生器 path generator
& l7 e4 `3 x1 G8 X6 H1 G滾刀 hob
. V; [; n. H: L0 ?- M. s/ l& ]滾道 raceway6 | E- S u" f6 j( U5 v
滾動體 rolling element/ y* R+ R% Y$ x. c% L/ f U( A
滾動軸承 rolling bearing7 @1 F7 P9 d- i! K
滾動軸承代號 rolling bearing identification code i3 F5 u! }* L0 ~% t y
滾針 needle roller
" a* n0 j# A. @6 {滾針軸承 needle roller bearing) o8 a" I$ w+ p
滾子 roller
1 e L0 a; j1 }" @滾子軸承 roller bearing+ V/ `5 j% e5 I( t
滾子半徑 radius of roller
$ H& |/ [7 Q! z0 i6 f滾子從動件 roller follower
+ _6 B5 |3 j. d- p* U滾子鏈 roller chain
' k. @0 y* F: P9 e1 c* J: E滾子鏈聯軸器 double roller chain coupling
2 h/ L. r7 A! ~# p6 @, E滾珠絲桿 ball screw! h. V c' F, w4 |& h
滾柱式單向超越離合器 roller clutch! L2 V$ Q7 a3 `* M G8 `5 x
過度切割 undercutting
4 a5 G p5 E" Z( n函數發生器 function generator
: a! [4 U$ h, I. p# e) Q5 t9 ~; O1 x函數生成 function generation ' }: t- R; A" Y- U& R+ p* M
含油軸承 oil bearing
1 Q/ P9 y: r4 Y- K7 ?! b+ m3 f耗油量 oil consumption& E, I' A8 j2 Z
耗油量系數 oil consumption factor
8 f0 ^% L9 v& d6 i3 ~% J! I赫茲公式 H. Hertz equation
2 _! I* G) W2 }3 w合成彎矩 resultant bending moment
$ P9 B4 y& I% ^! j合力 resultant force& z9 h) k6 J1 s4 Q/ `' o; |. ?! W( ^
合力矩 resultant moment of force- M2 b( n1 H. d5 g6 T2 @
黑箱 black box% ^; {# b& V1 ] i7 m2 c4 c
橫坐標 abscissa8 k0 ~! {- o5 C1 a4 i, g
互換性齒輪 interchangeable gears# S7 B. p& k4 ~7 z# o* f3 a# o
花鍵 spline+ Z; I+ W' [, m0 u
滑鍵、導鍵 feather key" R5 G8 J4 Y! c& D- P1 r, L( f
滑動軸承 sliding bearing( }" j6 L: i. ^# E0 L( U- x
滑動率 sliding ratio
% T0 {+ @3 C$ i0 @6 ~滑塊 slider1 W; f8 K% N+ K) Z4 s) a
環面蝸桿 toroid helicoids worm
# Z: @& {5 {9 T+ c% M+ C環形彈簧 annular spring; D. T4 Y6 A1 N) G3 [- Z I. X
緩沖裝置 shocks; shock-absorber
( z& s9 A; X5 W5 c! V灰鑄鐵 grey cast iron
# M0 v& Z6 N( w: k+ J回程 return
+ o2 l! O+ Q; Z/ a* h回轉體平衡 balance of rotors$ { _9 l8 z- Y, J
混合輪系 compound gear train
- \( p+ _2 |$ P1 `2 `, w積分 integrate ! X* N# @! R' K
機電一體化系統設計 mechanical-electrical integration system design : v# H( V! ?: N. q
機構 mechanism
1 I) B" n( k. x: Z l機構分析 analysis of mechanism
) f. z) a# Q2 D% q機構平衡 balance of mechanism
! x1 W9 Q% ~; ~4 R機構學 mechanism5 J8 K! N- C1 X, s9 D4 M/ b
機構運動設計 kinematic design of mechanism" O, i! w( t5 X5 ?
機構運動簡圖 kinematic sketch of mechanism6 U S" M& [. H9 p1 _$ _0 b
機構綜合 synthesis of mechanism/ y; D) `$ ^1 R, z/ I% S
機構組成 constitution of mechanism2 P3 C- r- R/ P `$ n9 ] E% t2 |
機架 frame, fixed link
. E7 E5 F) Z# w2 F& o機架變換 kinematic inversion
3 o; x) G# O- D, Z" I) O1 x& x機器 machine4 ?8 u# L1 h" S; y- `9 a
機器人 robot
% j6 _6 `& c& n$ g7 B: b: I5 g機器人操作器 manipulator
6 e4 P! X/ Z' k機器人學 robotics
- _( U: F6 d! |: q2 F3 E技術過程 technique process' e2 Z) i5 a8 g7 N: q' X
技術經濟評價 technical and economic evaluation! e& P$ U* o5 i' \, l8 a
技術系統 technique system- _$ @- W" T7 C4 p4 v
機械 machinery
_: c J* l6 f1 S( A機械創新設計 mechanical creation design, MCD
1 _, p; ~5 f* k k% j6 ]: U/ c; z機械系統設計 mechanical system design, MSD
: z& j1 a2 o! `7 Z! |機械動力分析 dynamic analysis of machinery0 Z8 a1 ^: Z9 B9 k+ R( a
機械動力設計 dynamic design of machinery
5 C3 u$ f+ a* k' P( o機械動力學 dynamics of machinery
% }/ G) s. I, r9 _- N' [機械的現代設計 modern machine design
1 a- O! S! n3 v8 P1 x4 F8 j* `8 E機械系統 mechanical system% f/ b8 X& o {4 M
機械利益 mechanical advantage
* X1 C' `* o2 H* d機械平衡 balance of machinery, g% d& N* k s R
機械手 manipulator
+ S, d' `4 F, L: B* M; ~ w機械設計 machine design; mechanical design( h. G7 N: n' u" M& G
機械特性 mechanical behavior
" s, u1 Y% U& n( y機械調速 mechanical speed governors' k8 R+ D* n% L' X: a1 I" H k
機械效率 mechanical efficiency+ L& C5 P. a3 z% d* W f
機械原理 theory of machines and mechanisms
) e( a( Z/ F( J8 C8 ?. v機械運轉不均勻系數 coefficient of speed fluctuation( ^: N6 H6 M' o" y; }2 G! k
機械無級變速 mechanical stepless speed changes
5 t, W. [" n; L9 x E. U/ a4 T基礎機構 fundamental mechanism
9 I' E* p+ v, c5 h" h/ p8 M基本額定壽命 basic rating life
( K S5 q; E. v& m# `3 s6 o: ]基于實例設計 case-based design,CBD1 ^1 G5 ~7 e! F5 a2 w, d6 b9 E
基圓 base circle6 s, r/ K7 _% A8 c- k, z) W( P
基圓半徑 radius of base circle
. L2 m3 S) s) t3 k6 `( L基圓齒距 base pitch
" k; a4 f% n! f9 R基圓壓力角 pressure angle of base circle
# [" N% ?: S. [' I* y$ m基圓柱 base cylinder
2 q9 I$ o+ n" b8 t基圓錐 base cone1 X# \" O" c. M2 m7 a
急回機構 quick-return mechanism
9 @1 F. B6 U9 J: m. \3 J! R急回特性 quick-return characteristics
2 ]+ \8 X3 @. n$ ^急回系數 advance-to return-time ratio
1 g0 k- {, p1 }" y* S# ]! C, u急回運動 quick-return motion
4 F6 q2 C- {+ X' T: a1 Q棘輪 ratchet
! p: [" v2 [$ ~" q+ o( [ L' m棘輪機構 ratchet mechanism: L7 |. E! }0 X& ~+ h: ~8 k
棘爪 pawl
* c/ A! G2 M* Y, ^8 u極限位置 extreme (or limiting) position0 K, w2 @ [! w
極位夾角 crank angle between extreme (or limiting) positions
/ |: x5 Q e. ~: V: V' I# C' x計算機輔助設計 computer aided design, CAD) q# i) @* a& w9 [! ~0 z) K
計算機輔助制造 computer aided manufacturing, CAM
) Z$ Y2 ~& [" r' A9 o" H計算機集成制造系統 computer integrated manufacturing system, CIMS
6 C; Z4 ?; ~: c' V; F2 x% w計算力矩 factored moment; calculation moment) T3 J& A- K& A; S
計算彎矩 calculated bending moment4 G2 i# ^1 f4 h5 ]4 y# y+ O
加權系數 weighting efficient
# \( k& z! ~5 q4 a加速度 acceleration w* F; ~ t+ X. b, y
加速度分析 acceleration analysis! }9 \& r6 X# o) s% L1 r% D7 P% _
加速度曲線 acceleration diagram7 A; s3 U9 u. `% E. m
尖點 pointing; cusp
: G2 g* \+ l/ a尖底從動件 knife-edge follower7 R6 f+ @2 f p- w
間隙 backlash8 w* a. L; }6 K. l, R/ M
間歇運動機構 intermittent motion mechanism* _: _% [( Y) \: u
減速比 reduction ratio
2 I. c! ?# q s7 V1 X; W: |6 s1 J; u! l減速齒輪、減速裝置 reduction gear; W S3 G* L" x" v
減速器 speed reducer. `* R, ^5 _9 y
減摩性 anti-friction quality
% i1 {8 ^; L% b; {漸開螺旋面 involute helicoid) E) D0 D8 ~1 ?! M
漸開線 involute2 c1 i( E* S, L" ?/ n8 |2 u- s" J
漸開線齒廓 involute profile
3 i3 }: V; `- ]+ |漸開線齒輪 involute gear) R! W! M! ]3 K, J! N/ {
漸開線發生線 generating line of involute
, w8 \# ~! Q. c; Q" i漸開線方程 involute equation
~: B% \' A' x/ L& y漸開線函數 involute function
9 O2 p- B' {% q( Q8 E3 t0 B# n2 L4 m4 M漸開線蝸桿 involute worm3 l6 l5 m; j0 y# D3 x; H' ~
漸開線壓力角 pressure angle of involute! j5 F0 P2 P$ h
漸開線花鍵 involute spline
# ~2 `2 H/ Y6 |1 F, z7 E6 C簡諧運動 simple harmonic motion4 I1 S4 N/ A" k6 m& {
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發表于 2008-2-21 11:37:30
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