曲柄滑塊機構 slider-crank (or crank-slider) mechanism# c4 K' f p6 w8 r) H# U+ s$ e3 N9 d
曲柄搖桿機構 crank-rocker mechanism' i) i# T& ? }, z! [
曲齒錐齒輪 spiral bevel gear
& T! P8 q9 a3 ^* B" A曲率 curvature
# @" F- @+ B! \9 M; h曲率半徑 radius of curvature
) f4 G. w/ `. k9 ]% Q3 A曲面從動件 curved-shoe follower4 K, B# }1 u" w3 [, z$ z
曲線拼接 curve matching9 A! L$ O+ o! d, l/ F$ M, r
曲線運動 curvilinear motion
( G- G* c8 Y0 s$ I* t- V曲軸 crank shaft6 B/ d+ j% q$ K( H; l$ K p
驅動力 driving force0 C% E) ]1 [0 e% ~# G# \" A% {2 k
驅動力矩 driving moment (torque) A) Y0 }& ]+ r1 c) Z
全齒高 whole depth
& g+ _* N- r+ x! ~權重集 weight sets
3 u* O) _/ W& J- {球 ball, S# j p' \: `/ s! a- k9 {
球面滾子 convex roller: g& v& l/ ~: f8 }! m1 N
球軸承 ball bearing9 i! z4 M" {* G" `5 H0 Z4 i% K6 A. S
球面副 spheric pair
9 B& b$ ~ J1 x+ P0 h球面漸開線 spherical involute. |# S8 k! Z: N; p2 m
球面運動 spherical motion
4 q/ A* g9 l" e" X! E! M, h球銷副 sphere-pin pair
/ }8 S% Q6 f; Y, V; S7 E: _球坐標操作器 polar coordinate manipulator! c( P0 }' Z/ Y
燃點 spontaneous ignition % z6 N7 \7 L) J& E) ]( z7 l
熱平衡 heat balance; thermal equilibrium ; j: N( m4 e8 S6 w. X
人字齒輪 herringbone gear
$ o$ [ w+ c: u; Q冗余自由度 redundant degree of freedom! R3 @1 C" k/ ^. q9 @+ W# o
柔輪 flexspline& F& G) H4 Z+ ]8 C' u! k
柔性沖擊 flexible impulse; soft shock s$ j( s) `+ `4 U: T
柔性制造系統 flexible manufacturing system; FMS8 a; o* d4 p3 H0 a$ v) p
柔性自動化 flexible automation
8 G4 a$ ?$ {/ v7 f& k潤滑油膜 lubricant film, V6 X7 q% g1 R
潤滑裝置 lubrication device
" s5 }* ^9 M2 D+ H+ R/ s0 v潤滑 lubrication6 `, M* Q: Y9 W- J0 N1 r8 [1 L
潤滑劑 lubricant2 J) |+ _8 [2 ^
三角形花鍵 serration spline
! {8 h; h+ J* H0 Q" w o! W$ \三角形螺紋 V thread screw
/ L2 j x1 a0 B7 H. E, e5 D* f三維凸輪 three-dimensional cam X+ I _% K6 h7 p6 w: V M
三心定理 Kennedy`s theorem9 x, H; m$ g; v5 i3 {
砂輪越程槽 grinding wheel groove
% \. [) f+ a- Z: C3 h. C砂漏 hour-glass
8 z- Z' W% N0 D/ g5 q+ z少齒差行星傳動 planetary drive with small teeth difference
x; y5 X+ u# Z8 [6 p設計方法學 design methodology
$ g9 x- j) |" l# t7 ]設計變量 design variable
" }0 J2 L) S& o$ ]! E設計約束 design constraints! p. _/ A1 j% t
深溝球軸承 deep groove ball bearing4 T2 L7 q4 _' j+ G2 c
生產阻力 productive resistance; X9 Y, d7 q/ k! C: i& B
升程 rise/ V; c& y& y! X+ q' r/ V1 @ G
升距 lift
2 N% G. y3 H, G! @實際廓線 cam profile, t* J o* A6 r1 |& `5 n
十字滑塊聯軸器 double slider coupling; Oldham‘s coupling8 Y1 d/ v ]# ?$ ~! y
矢量 vector
8 W- t. t4 ]& J% L; I. \, F輸出功 output work( d" j4 R. P$ b- T0 ^/ X: d
輸出構件 output link, }, g5 Q* K) T$ Y) L
輸出機構 output mechanism
# f8 c% a# J) W6 ?" A輸出力矩 output torque
- z% l* G: v( x, X7 j6 N輸出軸 output shaft8 G! ~; }6 x3 n" e8 U
輸入構件 input link
6 b2 Q3 ~0 `! t' Q, l6 I數學模型 mathematic model4 ~* o* a: R! f& M" F7 T$ N4 V( ?
實際嚙合線 actual line of action
& z) {; Q% t* ?( [雙滑塊機構 double-slider mechanism, ellipsograph
$ D& g" f3 U2 T! P8 Y雙曲柄機構 double crank mechanism
" A* U4 i% t5 R' h. _" k雙曲面齒輪 hyperboloid gear
. G% m% V9 P1 u7 M/ k9 G) W1 D% H! W u雙頭螺柱 studs; \9 ?5 V7 T5 Q4 X
雙萬向聯軸節 constant-velocity (or double) universal joint9 ]$ Z) N# g+ q/ S3 B
雙搖桿機構 double rocker mechanism
: F: V( N9 z' v0 Q8 @雙轉塊機構 Oldham coupling" [- G5 K" r0 B* S1 O- ^* S* c
雙列軸承 double row bearing# x# _. H5 o& [7 B6 R/ @, U: ?
雙向推力軸承 double-direction thrust bearing
, r5 H4 G1 ~; D, l. R松邊 slack-side
! n& X, q# e$ l6 M2 D順時針 clockwise6 m% j" q9 M" e6 U4 z# l1 z
瞬心 instantaneous center
' ]3 [4 o8 a) G6 ?2 A1 T# b$ D死點 dead point( M+ F9 c) ]2 y+ |* h1 l/ D
四桿機構 four-bar linkage7 V# P" A* R. z
速度 velocity- ]1 g& w3 Z1 l3 m- P5 v
速度不均勻 ( 波動 ) 系數 coefficient of speed fluctuation
% G3 c+ \1 M9 n# Q% W# v |. ~& t速度波動 speed fluctuation O, ?* E1 Y" P6 S
速度曲線 velocity diagram
) W) _! }3 P) y3 v |速度瞬心 instantaneous center of velocity
$ k/ h3 ?2 V/ L' |0 [, |塔輪 step pulley % a9 R* X8 I) d+ M1 h5 W) R
踏板 pedal
7 J- e# }: @& _( Z2 z7 p臺鉗、虎鉗 vice
. X6 ~8 Z1 [8 X V+ ?# [( _6 n5 D太陽輪 sun gear
# f$ p8 [% E; Z( ^6 E彈性滑動 elasticity sliding motion
' _# I' J0 c" d彈性聯軸器 elastic coupling flexible coupling C5 K& f R# ]6 b$ {
彈性套柱銷聯軸器 rubber-cushioned sleeve bearing coupling
* H6 G9 {% ?4 ~ n3 r" ]套筒 sleeve
! Q0 K# L0 D! m/ y) ^9 D梯形螺紋 acme thread form% ]& }/ ?- z% [9 X
特殊運動鏈 special kinematic chain
% ]8 Q) ^& k2 ?. M0 u; j+ Q, J% x特性 characteristics& L- d- S2 e/ o( f" x" X. m- K; _
替代機構 equivalent mechanism# D. s& i8 Z0 T4 o% V. z# i% c( z, H3 N
調節 modulation, regulation* X7 d4 r) A k( q6 b0 s4 H& t
調心滾子軸承 self-aligning roller bearing
! m( T4 _$ T y* j調心球軸承 self-aligning ball bearing* y2 K, N" t8 x6 \$ u' X( Z
調心軸承 self-aligning bearing9 a$ M0 r: F# o3 g1 d8 Y
調速 speed governing! r! `3 v$ Q7 o
調速電動機 adjustable speed motors7 Z6 p1 c8 G% i# j
調速系統 speed control system* F0 v7 `. }* H+ \3 _3 L
調壓調速 variable voltage control
/ N7 D% U" h# V% h. F調速器 regulator, governor8 B9 `+ _) ^7 R
鐵磁流體密封 ferrofluid seal
; N6 X8 d9 n# u4 u4 q# u停車階段 stopping phase) x, l7 P0 _ a9 v& [3 l
停歇 dwell
: E: \% P7 W$ q: F3 Q! ^ h9 ?+ p7 O同步帶 synchronous belt1 [! Z* ?* f: X4 k9 e% Y8 n
同步帶傳動 synchronous belt drive3 x8 n% _8 h% v5 X) P5 e! r
凸的，凸面體 convex% D+ z7 a7 t' v! q1 B4 m6 o' z
凸輪 cam
9 _" D/ m8 I' Y( u0 o凸輪倒置機構 inverse cam mechanism
1 E5 I# J$ ^, l. F' G' M凸輪機構 cam , cam mechanism
" q: C+ N! n1 P( z2 O) \( C% S凸輪廓線 cam profile* `; }+ w5 S' X5 S
凸輪廓線繪制 layout of cam profile$ Y, | {. F' o& b8 n# m+ J6 X3 t
凸輪理論廓線 pitch curve
" R/ n {- } |+ f \: R凸緣聯軸器 flange coupling
7 A3 G# p+ e) c4 I% A圖冊、圖譜 atlas; {; n7 h2 A6 Q* ~& s! z
圖解法 graphical method
4 i4 I' B% H! ]) U推程 rise
7 W% ~( O( c+ g推力球軸承 thrust ball bearing
, a: E+ w* u: b% ?2 \推力軸承 thrust bearing
7 b: S' @4 f& q6 \/ L$ H0 d退刀槽 tool withdrawal groove- x) I8 N6 g2 F0 M- C
退火 anneal' M) ?6 f" V, V6 K$ V+ u
陀螺儀 gyroscope2 ~) F; {6 m( M4 r% l: h4 Q
V 帶 V belt' `$ ~& Y( b. j
外力 external force
7 H9 y$ R% w) l* G- y外圈 outer ring
' X8 R/ |( v; X外形尺寸 boundary dimension1 \8 v! h7 N- u6 k1 X2 n
萬向聯軸器 Hooks coupling universal coupling+ D9 X# i4 d" r$ T# w
外齒輪 external gear
. ~# B) D0 n. ~! T, z彎曲應力 beading stress- W6 M7 l5 Z J' ~
彎矩 bending moment8 {6 Z+ J5 r6 [% ~* a/ X- A
腕部 wrist3 G8 W/ q" c8 x1 d
往復移動 reciprocating motion/ v1 q4 [$ d: o
往復式密封 reciprocating seal0 D. l m& x& A3 I# @% S5 i& Z
網上設計 on-net design, OND
5 g# F5 [! N8 E* Q5 s9 Y微動螺旋機構 differential screw mechanism
: l' ]6 k# ], m$ j* f位移 displacement
+ j" q+ l c& D8 Z位移曲線 displacement diagram* z" J7 R4 r, g; s# V
位姿 pose , position and orientation
6 Q+ m S2 ~- F# N3 @穩定運轉階段 steady motion period
! \! U5 L. Z% \. {& B- P穩健設計 robust design& j7 N; A' q' M7 J8 w! ]$ q
蝸桿 worm, `( n c/ N3 I$ T, g6 e- b
蝸桿傳動機構 worm gearing
+ p: k* h& }$ o4 ?% W8 ?; b$ e蝸桿頭數 number of threads
" i; Q% [" m+ K; ^7 U蝸桿直徑系數 diametral quotient
4 a$ W; g& I& `! E/ x, S蝸桿蝸輪機構 worm and worm gear
- A) a: o4 D; x+ \1 Z) [蝸桿形凸輪步進機構 worm cam interval mechanism0 r! t! D. Z7 H$ [6 e x& V8 J1 M
蝸桿旋向 hands of worm
4 Y, G1 L9 {2 o# Q蝸輪 worm gear! |+ v; Q! p4 g& N/ j) @; v3 Y
渦圈形盤簧 power spring* C5 t( g& |) ]
無級變速裝置 stepless speed changes devices- d% Y& F1 ^- K5 A, ]
無窮大 infinite: S7 S. M5 C D$ D* ~) I; k
系桿 crank arm, planet carrier
1 u0 [; ]- e$ B. d2 U3 K/ O h2 d6 t5 j/ Y現場平衡 field balancing 7 ^+ U) K& O$ [4 u; V; b( y5 U
向心軸承 radial bearing. u3 _* z, v+ \7 c( G! W% P- W/ O# o' ^
向心力 centrifugal force
1 | y" N5 |7 `( d- Q相對速度 relative velocity
1 P9 \9 h4 `5 O% Q1 k8 {相對運動 relative motion
& h# r4 E" |; |7 Z- K/ {相對間隙 relative gap' X& o7 V8 G4 q( C5 `& R. F
象限 quadrant1 p. h6 B; @% H
橡皮泥 plasticine
) y F. K' b0 k: P0 V" ]! ^細牙螺紋 fine threads
0 A. {7 `( ` N7 N5 T! x$ \銷 pin
/ O0 |& V g) `) K; p" O( Q8 F: l消耗 consumption
- U* K/ l, }( }' W9 w5 d小齒輪 pinion1 p5 h( I' J+ m+ A
小徑 minor diameter* o6 H: V* w% n! _8 E$ z: N, z8 w
橡膠彈簧 balata spring
; N& c1 Z+ j) x2 {; Z修正梯形加速度運動規律 modified trapezoidal acceleration motion K( r/ T- W+ j$ r
修正正弦加速度運動規律 modified sine acceleration motion; q6 |0 g: m/ s" ~' h
斜齒圓柱齒輪 helical gear7 u+ a& c$ H% [+ u* h. Y. n
斜鍵、鉤頭楔鍵 taper key# @; R! |: c5 c3 ^8 r: M, b
泄漏 leakage
Q% m1 a1 O+ I: a. p- e t諧波齒輪 harmonic gear8 X' k+ ?& G0 }
諧波傳動 harmonic driving1 }. w2 h4 X, h% ]
諧波發生器 harmonic generator4 i' j3 V5 W* U9 B0 Y; ^8 E: I
斜齒輪的當量直齒輪 equivalent spur gear of the helical gear
# Y4 z6 y" z, g' ~心軸 spindle2 U/ j: \1 o0 T# t8 L6 l; O
行程速度變化系數 coefficient of travel speed variation+ p: r n" ]5 E! N! Q/ ^( X
行程速比系數 advance-to return-time ratio
* L" I9 |- g8 N. G& L行星齒輪裝置 planetary transmission4 J4 `! A$ y# a( L. ~
行星輪 planet gear
# ?4 h3 [& y* \5 e& b) v9 T行星輪變速裝置 planetary speed changing devices! O _) D% K6 F: F8 R8 \
行星輪系 planetary gear train+ z6 O3 D+ U/ |% z: k$ @0 w
形封閉凸輪機構 positive-drive (or form-closed) cam mechanism/ e. d" r$ _3 u0 Q( v2 ^
虛擬現實 virtual reality
" X, U3 {9 p$ [! S3 O& v3 G虛擬現實技術 virtual reality technology, VRT
+ a/ {% r8 ~5 Y2 q虛擬現實設計 virtual reality design, VRD
* D7 v" O+ M$ _虛約束 redundant (or passive) constraint
" a/ i h5 d& k0 F" E6 z許用不平衡量 allowable amount of unbalance/ X) I# b9 b6 h( P2 O; m& H
許用壓力角 allowable pressure angle5 m+ i4 b$ a3 P. d& d
許用應力 allowable stress; permissible stress- B% e2 M% _/ f: I/ H2 B3 A6 W
懸臂結構 cantilever structure
- N" j) Q# j/ F% d# K) e- A) a4 o7 }懸臂梁 cantilever beam/ [! L, R& Y. P/ |) I u/ f; {
循環功率流 circulating power load2 A+ H7 ~9 G7 f4 k1 ?
旋轉力矩 running torque# r8 H6 l5 ~2 E8 P- I Q4 r" @
旋轉式密封 rotating seal- { s9 x. `$ N6 z" q/ u
旋轉運動 rotary motion+ q/ g5 u$ h5 j( Y" }
選型 type selection# I: |* ]9 k' J* V7 K% J1 I2 r$ h
壓力 pressure
- X x2 w* V# m1 z; ~) h+ \, Z2 N壓力中心 center of pressure 7 `& j: P0 h2 X& ^* O! g- L
壓縮機 compressor
& @! Q. s) o$ M9 {+ B2 B壓應力 compressive stress2 s& @8 b! ~4 j! f9 r
壓力角 pressure angle
8 S- F* O1 b2 [& w6 U0 d6 P! f, I牙嵌式聯軸器 jaw (teeth) positive-contact coupling
! D' V% X: L, h2 {% `雅可比矩陣 Jacobi matrix
7 Y9 G. [. W3 u+ r; `5 b' l4 i搖桿 rocker' A$ c' I4 v: m" b D% m' K( G: c
液力傳動 hydrodynamic drive5 |' m5 p4 I' S! K
液力耦合器 hydraulic couplers
# W1 }1 v3 s1 ^' n: c. T- a液體彈簧 liquid spring* y8 {6 Z, O! k$ i1 i3 ?
液壓無級變速 hydraulic stepless speed changes; b6 h/ \% i7 l; n
液壓機構 hydraulic mechanism6 p3 y" A$ Q! ^5 A4 D# R7 n, c
一般化運動鏈 generalized kinematic chain
* _5 t0 a( S: j, Y* p移動從動件 reciprocating follower
: i" m) K2 Z3 F$ Y5 T& | T移動副 prismatic pair, sliding pair
' R- `" I* t( a0 R* V移動關節 prismatic joint
4 q5 G+ O8 B* s4 n* a8 b2 t移動凸輪 wedge cam
) y" h+ s1 f( r, m! Q% {' @盈虧功 increment or decrement work( [6 i# U4 y7 \" ]
應力幅 stress amplitude, w. u2 _1 k' u* F
應力集中 stress concentration
# B. |: k; u( l7 f( k! q7 y應力集中系數 factor of stress concentration3 p% m0 n" V0 o' q* L! W! i
應力圖 stress diagram
( U2 [$ c# v0 [0 v8 n/ F ^應力 — 應變圖 stress-strain diagram
. Y* w. {. Y) B8 y優化設計 optimal design
+ f9 I/ D/ v2 p( n( I& b$ H: d油杯 oil bottle$ N# H3 T, @/ ^0 d9 P
油壺 oil can! w6 _* I" A W/ W5 Z5 l4 e
油溝密封 oily ditch seal
0 ^0 b7 `' G( d有害阻力 useless resistance3 {& ~0 d) m; ~
有益阻力 useful resistance
- c7 `* w. z5 i; S& o$ q有效拉力 effective tension, L1 a1 e K% _' O
有效圓周力 effective circle force9 n$ P; Z- h5 t8 K1 J" C
有害阻力 detrimental resistance
: @7 g! l: W. L B" q+ A% U余弦加速度運動 cosine acceleration (or simple harmonic) motion
: R9 k3 G ]* L6 k6 X# B預緊力 preload
8 Q; Q9 ]$ h4 D8 X0 S原動機 primer mover |
發表于 2008-2-21 11:42:15
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