曲柄滑塊機構 slider-crank (or crank-slider) mechanism/ U7 D' T1 P2 A
曲柄搖桿機構 crank-rocker mechanism
" F2 J+ Q1 s$ E3 D* A2 O曲齒錐齒輪 spiral bevel gear1 P) [1 x" t& K: S, t: J' Q" U4 R
曲率 curvature. j1 t4 u& F, r$ i( F5 ^
曲率半徑 radius of curvature
+ Q( b7 P2 ]$ ?) ]4 ?! r, s& o曲面從動件 curved-shoe follower* u, S& X \% g& n$ u: r
曲線拼接 curve matching+ R5 N5 G" Q0 H! q2 Y
曲線運動 curvilinear motion$ @ @6 i. p6 W! ?. E4 ~5 h
曲軸 crank shaft& f" S1 B8 v/ o5 X0 b
驅動力 driving force
% o, i. z5 F7 C0 r! Q! a驅動力矩 driving moment (torque)/ T) c6 U1 ?* F3 F
全齒高 whole depth0 X. O7 V7 ?* e9 k2 g4 O7 P
權重集 weight sets: t; ^. m) O- b: ?9 Z8 j
球 ball. e1 z: r7 o/ i _1 X2 O
球面滾子 convex roller
+ r, b- h: i% x) {球軸承 ball bearing
4 q# Y' L# H% E1 [! |球面副 spheric pair
* S0 f% f) x8 Q4 \" b球面漸開線 spherical involute
" ]+ i0 B* m2 h6 R2 l% m3 l球面運動 spherical motion
+ ]2 i \; U3 ]9 I* o! P2 w球銷副 sphere-pin pair
5 Q! y7 w4 \: u球坐標操作器 polar coordinate manipulator
# P" R, x% l1 b/ ~燃點 spontaneous ignition
, h4 y( _# f, {/ Q6 h1 @" h5 g熱平衡 heat balance; thermal equilibrium
8 @4 f5 B0 k3 s! n, a, b* o人字齒輪 herringbone gear' c' t5 g- ]0 M! B. L* }: S( y
冗余自由度 redundant degree of freedom5 p0 N' L" x7 e* k+ _$ D4 y
柔輪 flexspline
5 x# l `2 x( I j8 J柔性沖擊 flexible impulse; soft shock1 O3 z' P3 ?) |2 S9 L
柔性制造系統 flexible manufacturing system; FMS
) |- u0 `2 p7 o- U柔性自動化 flexible automation/ n0 U8 }" V! _) O
潤滑油膜 lubricant film
% Q: n! c9 i8 L D4 h1 N4 I& v潤滑裝置 lubrication device, l* @1 c. b( g' R& Q8 H; e
潤滑 lubrication
! p/ k! a8 A1 b5 }7 q5 O潤滑劑 lubricant
, \8 y. }: {5 x/ ?4 J$ O' K# y三角形花鍵 serration spline 7 E* P* ]5 ]& [( l
三角形螺紋 V thread screw
: F- t4 x4 ]6 K/ H" d三維凸輪 three-dimensional cam
3 X# ?" T, J' Q& \8 r三心定理 Kennedy`s theorem* [8 b& s/ F, Z2 o G
砂輪越程槽 grinding wheel groove! e, E" |8 [ z3 ?5 x m
砂漏 hour-glass2 G- Z% J* p" I& r& C. ^1 m
少齒差行星傳動 planetary drive with small teeth difference
; g9 Q( f o" o/ `2 R設計方法學 design methodology
! t- n5 K. `) }9 C; c' ?' o設計變量 design variable
4 _, C( R" G9 H' f, l設計約束 design constraints, V; s, x2 g3 M; N9 u
深溝球軸承 deep groove ball bearing
) y- O5 O# c7 c, p" e7 @# x6 H生產阻力 productive resistance
; p$ z' X' a& u' H# n& L升程 rise3 y/ y1 K' }9 A: H5 t; d- `
升距 lift
" P' I& H5 ?" n- w實際廓線 cam profile- b# V5 ~( c9 j% y. @& k
十字滑塊聯軸器 double slider coupling; Oldham‘s coupling- X6 o8 Z" d0 M5 x2 r5 M
矢量 vector4 }$ ?. e6 e8 a( M' K6 Z* U, A
輸出功 output work
" ]! ^9 K0 }. z' z& j2 e) a$ H輸出構件 output link
0 u. R0 k+ S. \7 r9 Z輸出機構 output mechanism/ u1 D" [8 m I
輸出力矩 output torque! \8 D: n+ v% H- N
輸出軸 output shaft
& ]: R2 R2 b2 H* J2 [6 H/ r輸入構件 input link
$ g1 p( G S, _2 C0 y2 G4 i" h6 _數學模型 mathematic model& l9 `- z; X. k# `( J) c3 C
實際嚙合線 actual line of action
, @4 u* u5 F5 L: p雙滑塊機構 double-slider mechanism, ellipsograph. m2 [# P6 e8 y1 I5 R
雙曲柄機構 double crank mechanism
+ N2 z, f5 l" @) i- a/ |雙曲面齒輪 hyperboloid gear$ y1 s5 h& Z; [; l+ D! Q& V& T
雙頭螺柱 studs8 q* J. E! ]& p7 j
雙萬向聯軸節 constant-velocity (or double) universal joint
3 m+ j2 t v; y _" J$ c4 O D雙搖桿機構 double rocker mechanism9 R0 T K, d3 Y% G, ]+ G1 [
雙轉塊機構 Oldham coupling+ r& {3 d' @7 e4 L G% {' S; o6 P0 [$ l0 a
雙列軸承 double row bearing+ y% }, j+ h7 u, s
雙向推力軸承 double-direction thrust bearing" \ t1 n0 E v/ L l
松邊 slack-side0 Q: c, W) @( J7 W( c" |+ S% H
順時針 clockwise8 f+ Q0 w* Y+ B) ~( g5 T
瞬心 instantaneous center
5 o6 _' u2 V, l' {0 ] _死點 dead point
* ?. ^& S% r+ Q5 a1 m四桿機構 four-bar linkage
+ T5 q% x; u1 W: c* U v速度 velocity- ?) g$ C7 J9 x, R+ }
速度不均勻 ( 波動 ) 系數 coefficient of speed fluctuation0 k5 e$ |/ |6 W- B$ p; l R1 Y
速度波動 speed fluctuation6 D: N; L, k/ j- }$ B& |: v, \4 f
速度曲線 velocity diagram ?8 J: K/ k/ W4 M b8 G* l
速度瞬心 instantaneous center of velocity3 x) m0 p2 H9 E& f& i
塔輪 step pulley 7 |) \" _' ?8 z* a6 b7 X. O
踏板 pedal
$ m" I1 N" T6 _) |; N0 A臺鉗、虎鉗 vice
$ k0 S( e2 Z' {3 E9 B# C太陽輪 sun gear
4 Q. l; e& u5 C6 u! }* V彈性滑動 elasticity sliding motion* v; m& }; c) s# I9 L
彈性聯軸器 elastic coupling flexible coupling
1 V+ T+ k8 c0 x) s; D3 V彈性套柱銷聯軸器 rubber-cushioned sleeve bearing coupling
0 Y3 z" B- U( k' d) j- ^; C套筒 sleeve
) q( z9 O4 P% G0 R6 G! V梯形螺紋 acme thread form
& s9 n% [+ m6 v3 ~, _: u. M特殊運動鏈 special kinematic chain6 a. @9 z7 H# J. V
特性 characteristics
1 R) i3 C+ o! L' e& p替代機構 equivalent mechanism
) y# b, E7 _2 q$ g% u& Z/ \) V; W調節 modulation, regulation" ]4 o1 ~$ T8 Y) F" s8 \+ ^
調心滾子軸承 self-aligning roller bearing: @2 i& E! N$ W. U- g- l, Q+ |6 v
調心球軸承 self-aligning ball bearing
9 }2 B. k( p) S: K8 {調心軸承 self-aligning bearing4 E& X% {: S& u( }3 L
調速 speed governing
3 I/ i4 T+ ^ L% U調速電動機 adjustable speed motors6 u* f7 |, ~+ t) M
調速系統 speed control system! p8 t |3 M3 n" ?% _6 V6 j [3 n
調壓調速 variable voltage control
. D. y4 n% O0 E7 ~, @7 p( s* Y調速器 regulator, governor# W/ u7 N: G" i% G: R5 E; |0 {9 o
鐵磁流體密封 ferrofluid seal
) U" S( h: ?; C @2 f$ _停車階段 stopping phase4 J6 T, E0 F# G8 G* t6 M; C
停歇 dwell
. a- o5 W7 k% v$ G7 F同步帶 synchronous belt7 a6 }* u$ @( `/ [; s4 t1 M9 L
同步帶傳動 synchronous belt drive+ |% M; X+ {5 j( T
凸的,凸面體 convex
8 X# k% ], ]) V: m5 F- ]# z) L凸輪 cam
9 c5 H5 R8 L# o' D( o' B: E凸輪倒置機構 inverse cam mechanism* @% t# K2 F2 u8 M* E6 G* y
凸輪機構 cam , cam mechanism1 E6 Y% ?/ L/ ~
凸輪廓線 cam profile: i5 G. D3 ~; E* G: q' p5 {
凸輪廓線繪制 layout of cam profile( F. t' U9 y A ?$ ~
凸輪理論廓線 pitch curve1 p; S) w+ i8 ]. a% |0 B# @
凸緣聯軸器 flange coupling. x$ w; ~+ r) A- g
圖冊、圖譜 atlas9 N& P2 O5 q9 Z7 a& L- B4 V
圖解法 graphical method3 f/ D/ E7 b- ^+ L' g
推程 rise O5 b: C7 }& N- `4 }
推力球軸承 thrust ball bearing: _* y# T0 M0 L6 ?+ x1 i, ]! s
推力軸承 thrust bearing
' B% o+ |1 w7 {; v6 N退刀槽 tool withdrawal groove
" [# B. [4 F: t9 Z8 O' S退火 anneal3 ?9 r, I; v1 u8 E$ k5 h- [" p# z& o
陀螺儀 gyroscope; z; ^8 j% j+ F$ k; \$ Q7 Y
V 帶 V belt6 y7 Q+ N& S: o z/ d
外力 external force
* K0 n# G7 Q( p' y6 u外圈 outer ring
, Y' K7 m- J! A; ^* S" k u外形尺寸 boundary dimension" [4 W" {8 H' I- \) E
萬向聯軸器 Hooks coupling universal coupling- F; {, l( Q. X" ^+ Y1 v+ Q
外齒輪 external gear) B/ O& P. ~# T; t! E) {. W
彎曲應力 beading stress
) j0 z' i0 V+ t" }; {: s, C7 F彎矩 bending moment$ A1 z0 V! a3 g/ G9 e8 H9 V
腕部 wrist v. k1 N/ x! e6 X/ L. h
往復移動 reciprocating motion
7 T+ F4 B/ p* c$ F A# F; P往復式密封 reciprocating seal
8 z/ J; @% c1 w網上設計 on-net design, OND
7 c! y- x4 B- p. D微動螺旋機構 differential screw mechanism
) Q1 i2 Q4 R! E1 H% l& x4 r位移 displacement
$ G! Q0 {$ g! X% I位移曲線 displacement diagram
$ ~$ @( U1 x6 H位姿 pose , position and orientation
+ F9 }8 y4 @) V穩定運轉階段 steady motion period
c" K+ u# ]+ H9 w穩健設計 robust design9 w5 D7 X, ?' H4 ]. U3 i
蝸桿 worm k" a/ r3 H9 l8 W# O7 R1 b, F
蝸桿傳動機構 worm gearing9 k% N" x1 V% S4 Q$ w5 g2 D
蝸桿頭數 number of threads$ A- R* S0 d* D5 T% X
蝸桿直徑系數 diametral quotient5 q+ I4 M) v1 C. t) R3 X) d4 B& `
蝸桿蝸輪機構 worm and worm gear2 R9 @* D" D, q" Z9 B4 W, q
蝸桿形凸輪步進機構 worm cam interval mechanism
" R( b& [$ X2 o/ _ r蝸桿旋向 hands of worm
2 j8 n! a6 u4 w* e y3 l蝸輪 worm gear
1 ~0 z% J2 F1 N渦圈形盤簧 power spring8 E" I8 g) B/ ~9 z1 b4 p& U9 p# a
無級變速裝置 stepless speed changes devices
: Q! j# }+ q1 N6 J' \6 G3 J; E- s無窮大 infinite
* d, c( E& s# Q6 A2 x. V系桿 crank arm, planet carrier 3 V, a9 e# k) _) H+ T4 l
現場平衡 field balancing % c) v p3 p9 ?6 u% N! F7 |% s
向心軸承 radial bearing2 d/ M$ Z7 s" r) [) ?- F) x- z
向心力 centrifugal force; n0 ]2 O7 r2 ?- `# X; ^
相對速度 relative velocity
0 y3 m8 `9 R5 @相對運動 relative motion
6 d$ C# D/ b" h% T# Z9 z相對間隙 relative gap1 m+ o f2 e( \
象限 quadrant
& ]1 a- }! U, D; }" p橡皮泥 plasticine8 F9 Y/ Q) m$ y$ K
細牙螺紋 fine threads
7 \* N9 D( f: s銷 pin: |. S6 [0 A- _4 Y
消耗 consumption
6 [) d! h2 h+ G2 P/ X小齒輪 pinion- D: Z6 F( Z" n
小徑 minor diameter
+ i3 H7 ]* B4 k8 h/ f$ d: u/ V橡膠彈簧 balata spring' y$ z3 L/ C/ h$ l
修正梯形加速度運動規律 modified trapezoidal acceleration motion. k6 ~7 p; J! D9 T! J* g
修正正弦加速度運動規律 modified sine acceleration motion+ i/ s- R8 F9 B6 M/ e3 ]4 [0 F: S' m
斜齒圓柱齒輪 helical gear
3 y# ]" C) m" H: ^) l E" R斜鍵、鉤頭楔鍵 taper key9 X* Y" O* E6 d& U& m: ~
泄漏 leakage2 f* [' M0 w1 T3 f' f' [
諧波齒輪 harmonic gear' y, T3 m% Z9 H3 O
諧波傳動 harmonic driving
% U: A) _1 W* `3 M6 f諧波發生器 harmonic generator
7 R% n7 Z" x3 q9 G1 F% g: \斜齒輪的當量直齒輪 equivalent spur gear of the helical gear
+ {% i3 E3 x! ?7 n7 k1 Z! J心軸 spindle8 ]: B/ }) c: M# E5 ]0 q
行程速度變化系數 coefficient of travel speed variation/ z' K) N# j8 _) u
行程速比系數 advance-to return-time ratio' V. _% b R4 O$ w: h, n& Y1 a
行星齒輪裝置 planetary transmission
6 |: h+ M4 I* i$ {3 o5 X行星輪 planet gear" n) p) @ T3 j% j
行星輪變速裝置 planetary speed changing devices1 T1 b6 f! H3 s6 q
行星輪系 planetary gear train
0 Z! Y | Q" X: r形封閉凸輪機構 positive-drive (or form-closed) cam mechanism# W" s! u9 _: R, s4 `( O8 U
虛擬現實 virtual reality. V4 T' l) f1 c \% E
虛擬現實技術 virtual reality technology, VRT5 V: e* V! M5 ]" ?/ E6 H
虛擬現實設計 virtual reality design, VRD4 L3 P: R' F6 Z. @
虛約束 redundant (or passive) constraint
" s; o( L% |; e許用不平衡量 allowable amount of unbalance' i( E0 U, X; W& E
許用壓力角 allowable pressure angle, {9 M0 {+ k# Q Y
許用應力 allowable stress; permissible stress
' h3 ]& a1 I4 Y懸臂結構 cantilever structure
% U7 t, t# \ ]# y懸臂梁 cantilever beam
% X( u) i; D3 o5 Q y循環功率流 circulating power load
, O* W# s/ R- z |% c9 C3 d M旋轉力矩 running torque, h6 d8 W6 `0 o8 q
旋轉式密封 rotating seal
6 ~4 p1 ~- n' X- L- R旋轉運動 rotary motion
7 ?) n5 o! x2 {選型 type selection
% [2 }, Y* l+ M* a3 _壓力 pressure
$ E7 ~0 N' s' |: ?9 K壓力中心 center of pressure
1 I8 P5 ~1 L. M壓縮機 compressor
- u* v/ S! q1 f! h, E/ ^壓應力 compressive stress4 O0 p( S$ e% K6 e5 R0 H/ T
壓力角 pressure angle
0 x' M+ |4 v8 ?8 X牙嵌式聯軸器 jaw (teeth) positive-contact coupling+ G+ W& {( J! `" h1 l" P9 F0 {
雅可比矩陣 Jacobi matrix3 x# ?; o6 i) \8 E3 @1 o
搖桿 rocker! s5 S! i- l8 F" X
液力傳動 hydrodynamic drive
, i- X+ j# F& A ~# n7 R液力耦合器 hydraulic couplers
- a. t: W7 P0 M液體彈簧 liquid spring
$ {7 |& g) H6 b, b. T' t, b液壓無級變速 hydraulic stepless speed changes/ e* @: n' }: Y! z9 D* O/ C2 Y2 y y
液壓機構 hydraulic mechanism' s0 z1 [- b& t* w: i6 m
一般化運動鏈 generalized kinematic chain4 `6 w2 B, W& {7 ~- {* B" @
移動從動件 reciprocating follower
, v4 t( o& L$ f5 w; x移動副 prismatic pair, sliding pair
! d1 p8 Q8 i6 L2 P移動關節 prismatic joint
0 x7 b x6 e) D, j D移動凸輪 wedge cam
. S' T9 a/ ?5 `0 v3 g0 r盈虧功 increment or decrement work
4 ^6 u8 v t; ^6 ~% o: N應力幅 stress amplitude
. Q* Y7 g( {- K* Z$ g3 M% w應力集中 stress concentration F8 F0 K0 J1 ]) c. R' P$ b
應力集中系數 factor of stress concentration! j) @# |0 u. Z( k( g) r" x( [
應力圖 stress diagram; A- }" J- R1 X3 Q$ [ u# A
應力 — 應變圖 stress-strain diagram2 T o( D: t' O" _3 Q1 O
優化設計 optimal design
7 N# B0 W8 z4 |# c油杯 oil bottle) E3 |: A7 F0 P) ]
油壺 oil can
' J+ g+ q" h J油溝密封 oily ditch seal2 E, X- k# z% g) D' u/ S: A
有害阻力 useless resistance% s8 F1 y8 E8 G+ ?; ] P
有益阻力 useful resistance
" {2 R6 W2 A$ ~; c# M4 e有效拉力 effective tension# W0 s( n. W3 @. u
有效圓周力 effective circle force
2 w) h! L& r' E1 M1 t有害阻力 detrimental resistance
3 |& G" W5 j/ i* \; j$ s余弦加速度運動 cosine acceleration (or simple harmonic) motion/ z' }( Y7 n( c1 |$ `5 F3 D) _: Y
預緊力 preload
1 R- l- e# g" s7 F1 I$ X0 v; r原動機 primer mover |