對稱循環應力 symmetry circulating stress
2 v6 [" r- N. b3 _4 ?6 f% @2 f對心滾子從動件 radial (or in-line ) roller follower* E1 a4 S4 q* g8 Q0 L3 [ S
對心直動從動件 radial (or in-line ) translating follower
9 W4 Y1 T% ?% u. K! `對心移動從動件 radial reciprocating follower
]3 Y5 r0 g! C) [8 S w對心曲柄滑塊機構 in-line slider-crank (or crank-slider) mechanism" q p) V! x- Z- W+ w# T
多列軸承 multi-row bearing
) D; B) R' j) i. o2 M. x多楔帶 poly V-belt
3 C: a. v! B! n1 b' P多項式運動規律 polynomial motion
8 I5 v' L+ s# P3 t多質量轉子 rotor with several masses" t) A; z8 j# [, W* K
惰輪 idle gear
1 v, V( _( Y/ v" Y' P額定壽命 rating life
0 m( v7 t4 y. w1 C" O& _6 ^額定載荷 load rating! x$ e; X7 J9 } Y/ Q4 U }
II 級桿組 dyad* j# _/ s, ]3 r4 D$ q
發生線 generating line 1 k. _% x0 ~9 u1 L( l! c7 r
發生面 generating plane
; c* f' C, ~* p) U( e, w法面 normal plane8 L" [' Q( V6 E' s
法面參數 normal parameters0 I3 P) f3 b- @% R) D. S
法面齒距 normal circular pitch
0 v! R% y2 s$ Q6 f+ W: g8 @法面模數 normal module. X3 w) Z% k( s! Z) b9 E- q
法面壓力角 normal pressure angle1 D: r$ F0 W0 L) D
法向齒距 normal pitch
0 Y5 o: V, g$ \' d法向齒廓 normal tooth profile7 T, e8 a! W8 m+ O, E$ L; o
法向直廓蝸桿 straight sided normal worm w/ x- B, Z m8 q! c+ S+ `- ]8 r
法向力 normal force, ` s6 O" o* \) {: y5 Y+ W
反饋式組合 feedback combining
& }7 E5 D( g* @反向運動學 inverse ( or backward) kinematics8 ]9 g- I, @. _1 r" L4 y
反轉法 kinematic inversion
, o& M: L3 x% G! u# T2 |反正切 Arctan4 g5 S2 d! e& ?7 F# G1 L. a" v' O
范成法 generating cutting' n2 p' @5 t. y
仿形法 form cutting5 f2 Q/ C. e6 h# ], q
方案設計、概念設計 concept design, CD
6 s+ k P3 Y! v防振裝置 shockproof device
4 W4 L; W9 h) Q4 G8 ?# X2 _飛輪 flywheel
' z+ ^ o4 E, _% e5 a飛輪矩 moment of flywheel
% c* V: J% u& n. P2 W1 _3 d非標準齒輪 nonstandard gear* ?4 v1 Y; x0 I6 [" o) K* t9 x/ y
非接觸式密封 non-contact seal
% b) B- C+ W! g3 z5 I; i非周期性速度波動 aperiodic speed fluctuation y4 c: C2 p+ [2 P/ K/ m
非圓齒輪 non-circular gear
" Q# Y+ Q) g9 ?/ T( l+ e粉末合金 powder metallurgy Q5 t5 C" g7 i9 A- b
分度線 reference line; standard pitch line
) d+ }. K4 U9 w) f* ~3 z9 s1 Z分度圓 reference circle; standard (cutting) pitch circle: Z+ {- ^1 ^/ ]# h2 m' ~; F
分度圓柱導程角 lead angle at reference cylinder
1 y2 a& F* C7 V9 R# e分度圓柱螺旋角 helix angle at reference cylinder
4 S% \' X3 N* I分母 denominator9 k1 M* M# T; x: K7 {0 N
分子 numerator
0 h* l& j1 h& A' \ l" |1 x* A+ U) N4 m w分度圓錐 reference cone; standard pitch cone
/ L4 B* B# b6 D/ N6 l6 Q2 v分析法 analytical method2 F, N! F9 I4 w) _6 s
封閉差動輪系 planetary differential9 R7 X# b |* h
復合鉸鏈 compound hinge
& l& ]& i% R, l1 H1 A( A6 U復合式組合 compound combining
9 ^. R: J# M8 w8 @- X復合輪系 compound (or combined) gear train& x! K! |8 v: x j! f
復合平帶 compound flat belt( y; f" U& y2 d
復合應力 combined stress
+ L- }- y. I9 @) L& E* z7 k6 D$ E復式螺旋機構 Compound screw mechanism7 g8 u; n7 e+ i
復雜機構 complex mechanism# j5 [* w9 ], ]( R
桿組 Assur group
" i! C7 S7 Q* G2 i干涉 interference " i+ ~) I% q5 f, r& w( @& Y5 H/ V
剛度系數 stiffness coefficient& [) m4 W1 ?0 `/ `$ v3 K
剛輪 rigid circular spline, ^% e* E# U G& x$ k9 v
鋼絲軟軸 wire soft shaft/ e0 x+ V& o7 O' G
剛體導引機構 body guidance mechanism- w" F$ o, a' Q/ f0 l
剛性沖擊 rigid impulse (shock)* ^' l" Y; ?7 A9 n7 _# t
剛性轉子 rigid rotor
$ n( T! j. n6 L% l3 E1 ]/ f剛性軸承 rigid bearing" M" W6 R2 R D2 N! f W6 \* J
剛性聯軸器 rigid coupling+ y K) ?* e( T$ i; p9 K
高度系列 height series
9 h w r% t' k5 T' B1 Y- Z3 D高速帶 high speed belt
7 R! }4 S6 V0 {, X高副 higher pair# D/ X& D- V4 `% e
格拉曉夫定理 Grashoff`s law
, k5 [0 V. P9 B% q3 {3 h' [5 A根切 undercutting
9 F: ? N. C2 u: Z! E' o公稱直徑 nominal diameter
3 |7 y, G0 ?1 Y b# h1 v4 T& v1 l+ U高度系列 height series* d7 {1 U3 |2 G0 J2 q
功 work
: Q( x n& c' T工況系數 application factor7 [9 _, j5 D8 a4 l. g% ]
工藝設計 technological design5 D: s* V% |/ C$ O4 Y% o" F6 ]/ ]
工作循環圖 working cycle diagram
" y" L. f$ v1 q$ A" O2 j工作機構 operation mechanism
9 i% B4 @' S4 ]0 I6 t工作載荷 external loads* p; S& ?; g V$ M8 B7 N
工作空間 working space
& K3 F; c3 X( Z/ U+ w工作應力 working stress
6 I' a, ~( Z" N9 ~; G工作阻力 effective resistance
4 d0 o% ~* n# \ c工作阻力矩 effective resistance moment" Q4 A% s* z3 a( N+ w
公法線 common normal line
; w7 ~0 g% D# X% f2 o* T( t1 |公共約束 general constraint
) t. s2 B" y. ~4 x/ P公制齒輪 metric gears
; B. e: O u3 E( `. D! P功率 power
3 o+ w% Z1 [0 v. M9 _, B功能分析設計 function analyses design& ?7 k- u" S1 s# V4 K
共軛齒廓 conjugate profiles) O! F8 V# Z! s- b
共軛凸輪 conjugate cam
% S8 O" F1 S( q1 G& ~, w) X構件 link
9 u' O% [! l( w; m: ?% Q& e鼓風機 blower
# c3 A( _- F' C5 Q( ~7 ?固定構件 fixed link; frame
6 o: \# O% g; o4 x固體潤滑劑 solid lubricant
" D" M8 |; ?) p, m關節型操作器 jointed manipulator: Y! P$ n o8 j# f+ ~
慣性力 inertia force
. b! Q4 x+ O8 y7 M, w/ |( {慣性力矩 moment of inertia ,shaking moment
! J: s/ Y4 a- b! z" w( i慣性力平衡 balance of shaking force
2 u4 ?3 l- X# l; s8 R慣性力完全平衡 full balance of shaking force
/ S s# H3 n" ~# e# F慣性力部分平衡 partial balance of shaking force0 E. |3 {7 W, H$ c' W: j& E# A
慣性主矩 resultant moment of inertia- R9 z8 |/ U ]7 K4 }& }
慣性主失 resultant vector of inertia2 T: Q S- A5 w: P; z0 M0 ?
冠輪 crown gear
1 F& S4 F- B) o) N' `, j3 Y$ P/ }" T廣義機構 generation mechanism2 f, m2 q! j8 l6 \
廣義坐標 generalized coordinate
+ g- W G& C3 X {8 \0 ]. V軌跡生成 path generation
( N. W. |- H! Q軌跡發生器 path generator; j u6 k% R# I7 e' @9 R: u
滾刀 hob
+ k* }4 g, b/ a- I滾道 raceway
. E4 j+ h$ ~9 N滾動體 rolling element# _3 J1 H8 m% W2 B. Y3 _* Z5 Q
滾動軸承 rolling bearing. G% C# ~" x- e
滾動軸承代號 rolling bearing identification code
. N9 ?/ r" i6 g; o& r w8 Y# G2 X8 e$ s滾針 needle roller1 L3 ^6 \% z; P1 M$ F) t# s
滾針軸承 needle roller bearing
1 j7 U$ a8 h8 e# F' C6 M$ q# y滾子 roller
/ g% D- P: p: Q0 C9 n滾子軸承 roller bearing
" o1 z# n3 y \滾子半徑 radius of roller2 l& a- i/ O2 c6 d' S3 O% k% K7 ^* D
滾子從動件 roller follower* D0 Q8 F! t7 X! s9 }2 ^
滾子鏈 roller chain
3 l& F. g; A6 Q/ q) _3 O; {" R滾子鏈聯軸器 double roller chain coupling x. P# F0 v: v8 I0 s
滾珠絲桿 ball screw
9 a5 m9 N: ]- W; u+ a7 V滾柱式單向超越離合器 roller clutch: n/ P$ ]$ A- t7 `4 D" z- q" s
過度切割 undercutting0 S9 \8 Y9 V( S. O) Y; n
函數發生器 function generator
6 @# e8 x2 u; S0 r函數生成 function generation ( q7 L- H2 y3 V6 O5 O! q) K
含油軸承 oil bearing
1 z( t9 G/ g( w4 b7 Y4 b耗油量 oil consumption" M* i# M. P) L. G% J1 R2 Q A
耗油量系數 oil consumption factor: c- v) M7 R- E3 f6 R
赫茲公式 H. Hertz equation0 g% w w A) i( L$ A
合成彎矩 resultant bending moment
6 @- W% M9 I2 w* z% w' K2 o合力 resultant force
. n" w2 _) U+ ]& V' {+ P合力矩 resultant moment of force! c3 a1 q7 r6 S2 a
黑箱 black box
, f F) D" E6 m, b橫坐標 abscissa' b' l% y& o y7 J$ F
互換性齒輪 interchangeable gears
3 W, `. U6 b6 q2 y n S: ^5 r花鍵 spline
E9 \( m7 b; D3 z5 V滑鍵、導鍵 feather key4 t Y- U5 f0 D) [* n X
滑動軸承 sliding bearing8 D* d" S" e' J- |7 \3 i
滑動率 sliding ratio% a+ p2 L- x* x' ~2 I
滑塊 slider1 x; U/ V. v; e) \; }
環面蝸桿 toroid helicoids worm
! g- c1 M; j E* T( b% E環形彈簧 annular spring
+ _/ D4 n/ Z6 x! Q緩沖裝置 shocks; shock-absorber
0 ^* `; b5 n( [6 i% D; |灰鑄鐵 grey cast iron
& { C" C' p2 c回程 return
& p2 f q0 x2 d3 O) o; A回轉體平衡 balance of rotors
- q0 i+ u4 m( y混合輪系 compound gear train
, b; e3 N. c0 y' }* d& f! l積分 integrate
! S4 ]: D& ]0 X3 c機電一體化系統設計 mechanical-electrical integration system design
2 E) g0 s1 O$ g8 u2 Q& H機構 mechanism
4 V$ b4 X7 X( F& ?機構分析 analysis of mechanism
( W8 L7 j! R8 v% C1 s8 K機構平衡 balance of mechanism
* |* [5 h; t& Y9 F) i機構學 mechanism
; P4 B8 V# \$ o機構運動設計 kinematic design of mechanism$ T) @) c; e( R) T1 U' A, S
機構運動簡圖 kinematic sketch of mechanism
# U' a) _, N6 q, a" j- x. P% |9 f機構綜合 synthesis of mechanism3 `) J- b8 {7 a
機構組成 constitution of mechanism
5 y2 f% G) O4 d X% d' m機架 frame, fixed link
" f/ Z {* c; P9 w' E. G機架變換 kinematic inversion
/ \" |9 F$ }* o9 @機器 machine0 y6 C* |% S, ~: u) k a! G7 e
機器人 robot* E. y( a% @* [$ w' ?- U- [& c
機器人操作器 manipulator
W2 \* L8 u* B E3 h! L機器人學 robotics" O$ D4 |5 t+ U9 }' U/ u3 E4 Z
技術過程 technique process
6 o- Z% z3 h; j; H. |8 F2 t技術經濟評價 technical and economic evaluation" q: s* }$ K8 ]" S S$ s3 G% D
技術系統 technique system& _0 o2 p- ~3 U- U& \- \
機械 machinery7 ^' j: v2 \# |/ E- O6 c
機械創新設計 mechanical creation design, MCD9 G% V( y Z8 ]- ?
機械系統設計 mechanical system design, MSD
) ?6 X' w1 A3 c% V8 `7 K機械動力分析 dynamic analysis of machinery
, m2 d- J F- P+ d- {+ p6 {機械動力設計 dynamic design of machinery
6 @; a4 V# ]5 I" Z機械動力學 dynamics of machinery4 \9 o# i) E& V3 H' S
機械的現代設計 modern machine design/ V- Z7 z6 @ ~8 C1 F: B Q' k
機械系統 mechanical system7 w: b4 X |+ e4 Y
機械利益 mechanical advantage
+ q" ]8 l7 }+ g* p" D& p機械平衡 balance of machinery
0 E( h( t+ l7 }! T% X機械手 manipulator5 M2 c3 Q7 Q6 B) b
機械設計 machine design; mechanical design1 o0 f/ A- b- e
機械特性 mechanical behavior
4 c& T4 L; o9 b; I" k* J: i1 k9 `機械調速 mechanical speed governors% k0 |! C* B: M
機械效率 mechanical efficiency
9 U* u* [! s6 u) y4 ^: L3 {機械原理 theory of machines and mechanisms! T7 L8 b2 o: h' D9 h& P g
機械運轉不均勻系數 coefficient of speed fluctuation
6 J' p( u; I+ |# i& ]機械無級變速 mechanical stepless speed changes1 @' [, V" |# p: L- N# ^/ O
基礎機構 fundamental mechanism
: ^! u) e# e3 a( ^/ M; \基本額定壽命 basic rating life
/ A% A3 X# E. @: O1 }基于實例設計 case-based design,CBD
8 e6 D/ |8 [3 W( i) ^基圓 base circle
# F& ^# M( T/ v1 g- r5 o* d Q基圓半徑 radius of base circle9 e: P" T3 W0 u2 V+ p. t
基圓齒距 base pitch
5 L7 g) a$ ^0 U) T基圓壓力角 pressure angle of base circle
. S. w9 Z. k7 { w基圓柱 base cylinder
t% k' G ~- h& e/ V- x! S基圓錐 base cone$ c' m! t3 Z g+ R6 r+ Q$ w5 ?
急回機構 quick-return mechanism8 H' } z0 Y: B, ~* B$ G
急回特性 quick-return characteristics/ [/ H+ T7 M$ y0 g9 e
急回系數 advance-to return-time ratio+ Q9 j2 F: p& d- t% ^/ F) i& I
急回運動 quick-return motion
. l+ V0 h$ J0 _1 R1 `" k' I棘輪 ratchet
+ I/ R, Z! f* H棘輪機構 ratchet mechanism$ X$ n9 E' \+ W# B3 [: T0 k
棘爪 pawl+ A2 Q2 W9 E; `* R6 {! E; \9 b
極限位置 extreme (or limiting) position
" A1 ~, r) T. a& s& B3 J極位夾角 crank angle between extreme (or limiting) positions
& n4 ]1 O9 Y+ \$ P計算機輔助設計 computer aided design, CAD( C7 K1 o7 w8 Y0 |+ z6 w/ W
計算機輔助制造 computer aided manufacturing, CAM
q0 h& E5 y, f計算機集成制造系統 computer integrated manufacturing system, CIMS
7 J& g; D' e% p0 t% i計算力矩 factored moment; calculation moment% g* L) `) {1 b7 \
計算彎矩 calculated bending moment
9 ^$ \6 q1 o. Y0 n- b! P6 r加權系數 weighting efficient
0 |0 s' |9 |& U' `5 ^加速度 acceleration
, S5 H! Z; b4 A+ D& G" b) h F加速度分析 acceleration analysis
& B! G- @' L A+ V6 C5 W加速度曲線 acceleration diagram' a0 D# H# M2 `" [& _0 b( Q
尖點 pointing; cusp
8 K! I4 w2 o) c$ g; `& W s尖底從動件 knife-edge follower8 D; Z' M1 d; ^% T
間隙 backlash( U0 ~8 b1 ~$ @2 x, D4 Q5 n( p
間歇運動機構 intermittent motion mechanism6 E$ A, ~& B* H- y( p
減速比 reduction ratio3 E% T1 f3 ]0 F- p
減速齒輪、減速裝置 reduction gear
# G9 s: h8 V* @; J( j減速器 speed reducer6 ^. s. ~1 \! P! _' u
減摩性 anti-friction quality3 f# V: M/ W9 z' j' O
漸開螺旋面 involute helicoid
2 `2 h4 y4 k# e* a0 C+ C U$ j漸開線 involute
2 M. D! C6 q4 e: c1 p; P漸開線齒廓 involute profile& J% q4 j& C/ k, J9 P
漸開線齒輪 involute gear
. M4 C! L( d: E5 s漸開線發生線 generating line of involute
' w* G+ n4 X+ I漸開線方程 involute equation
* P4 T" x9 d: }9 c' ]- t% j _, k漸開線函數 involute function K+ r& Z0 R+ U* t* }, `0 M1 V
漸開線蝸桿 involute worm
8 T' v& s' D% e& }5 T. e+ Y漸開線壓力角 pressure angle of involute
8 f; G: |' b3 ]漸開線花鍵 involute spline+ c- o# u5 k# z1 E
簡諧運動 simple harmonic motion
, u" E# Z) n* P$ w$ l+ u鍵 key |
發表于 2008-2-21 11:37:30
QQ好友和群
QQ空間