键槽 keyway+ M/ \) I" T- p' s
交变应力 repeated stress0 H/ Y5 M5 u" F. n& ~' O" R' U
交变载荷 repeated fluctuating load
' W1 d) ? O) P: x( G7 ?交叉带传动 cross-belt drive
, y' b' E t% k* {交错轴斜齿轮 crossed helical gears
- k2 E ]4 _0 @7 X胶合 scoring
* l- X% B$ }& L% ~2 h角加速度 angular acceleration8 [. w9 |8 Z: O+ _4 Y* p
角速度 angular velocity' e% A5 T8 I8 v: t b/ b
角速比 angular velocity ratio
! d4 v! V1 j5 `1 F' ^角接触球轴承 angular contact ball bearing
; ~' @2 `: w( x, V2 t% h角接触推力轴承 angular contact thrust bearing$ n. c3 w+ R K8 r" `) q
角接触向心轴承 angular contact radial bearing c- A$ P; T4 U8 o$ U
角接触轴承 angular contact bearing2 v" z# m5 j" M, D+ ?' k
铰链、枢纽 hinge' M7 |6 X7 H& L2 m' o4 G" `
校正平面 correcting plane, D( s, Y1 D |+ v4 f, R1 H
接触应力 contact stress2 X8 o) F8 l: ?6 [" L p( c
接触式密封 contact seal4 g: q+ G' m5 N
阶梯轴 multi-diameter shaft
( V. ~, D& ~0 [结构 structure$ }1 X7 A7 {! ?: E' a5 S+ s
结构设计 structural design4 v# L- J& o) e0 y* I8 k, H ^
截面 section
& G2 a' d6 ?; g0 P- z节点 pitch point( F$ l# u# @! z! Z! E4 F0 z" ^
节距 circular pitch; pitch of teeth. l: ]1 e9 E: U+ F3 j( E
节线 pitch line3 E) g7 t& N. E2 f
节圆 pitch circle
5 K' S, q# d( l, N# k0 l节圆齿厚 thickness on pitch circle/ B3 X8 x0 N+ W6 z0 G
节圆直径 pitch diameter% X h( Q5 v; i
节圆锥 pitch cone
, m+ S: c% Q3 `2 ?节圆锥角 pitch cone angle
% G8 w5 s" j# @: U; s; B解析设计 analytical design
) P6 O7 W4 r2 F, w2 h5 A紧边 tight-side
) v0 f: @8 p: S* C8 r6 L紧固件 fastener
; T1 u4 @) r1 i' t4 }) D; G6 r' ?径节 diametral pitch1 b4 [- m6 A5 r) F8 X: k* \: S
径向 radial direction% v8 Q8 s( i4 _7 S7 ^: Z, N, K+ E& c
径向当量动载荷 dynamic equivalent radial load3 |; ?1 T& N/ d, u5 D: v) y
径向当量静载荷 static equivalent radial load- k& f% ~' H- l" m& x
径向基本额定动载荷 basic dynamic radial load rating
& N8 \ r# v7 g* {/ u径向基本额定静载荷 basic static radial load tating8 x7 }! a z$ D8 e- K- S2 _8 }
径向接触轴承 radial contact bearing# i! |1 ~6 B) E) g# G3 w, o% Q0 M' N
径向平面 radial plane
0 }0 A6 J6 L% U7 Z2 d8 O径向游隙 radial internal clearance! |( ]8 f3 l; V
径向载荷 radial load. b) V% X( [5 E V u
径向载荷系数 radial load factor
& u. `. c5 T* {& n/ W径向间隙 clearance
& x6 B2 O% U0 X* y. G静力 static force+ o y! x) @+ B& m7 s
静平衡 static balance
4 l% L2 w& ?2 I" ]; u0 ^9 S7 M) s静载荷 static load) F9 E; p) P3 N; Y# q
静密封 static seal
' n# B1 C: m4 o* ~* s' m0 D& d局部自由度 passive degree of freedom
* H2 i d0 O/ M& S7 n/ S0 w x矩阵 matrix$ G8 d! W' s: V) t3 X7 [
矩形螺纹 square threaded form
1 A5 E. I M2 {( \& t锯齿形螺纹 buttress thread form
7 S4 o/ t$ c1 P% k$ c矩形牙嵌式离合器 square-jaw positive-contact clutch: S: m% d4 H" @/ e- F2 c
绝对尺寸系数 absolute dimensional factor
T f7 x" |# m绝对运动 absolute motion
5 D9 I+ D5 j! I# f d( d/ L: }1 y绝对速度 absolute velocity
) W, e9 d) X, k% U( o% S均衡装置 load balancing mechanism
0 W/ ~* G! w$ o; U) U- ?* c抗压强度 compression strength
# [ V7 [) ]4 m# \6 W8 T2 S6 j& N" C开口传动 open-belt drive # z+ p. o9 n: W* s9 v2 o
开式链 open kinematic chain8 s; ^; g8 c% f: g$ R
开链机构 open chain mechanism# R5 D& J7 G" i* p/ }9 W+ |
可靠度 degree of reliability% u# E" r3 p1 R7 x, _
可靠性 reliability ~+ w5 P9 H: s5 G% n" }
可靠性设计 reliability design, RD0 }* T. O" g" F. P% L9 M$ u
空气弹簧 air spring0 p p* f* ?' U, p
空间机构 spatial mechanism1 o: ?2 i% C3 i) C' M
空间连杆机构 spatial linkage h, e! ]. J# q) E7 j6 e! ]9 Q
空间凸轮机构 spatial cam
A5 ]/ ~5 z! @' O4 i; V' R- [/ Q空间运动副 spatial kinematic pair1 E! d6 @* S6 `* T n
空间运动链 spatial kinematic chain
* |% ?2 {' o l' b L+ O- p) A空转 idle
9 l6 f9 ^' W8 G+ L9 H6 {宽度系列 width series: p; A2 J' w3 \9 t" M
框图 block diagram% k. X& m8 {2 M7 x7 T! j+ O5 P) P
雷诺方程 Reynolds‘s equation
' A- l! I1 S9 p9 l% ?离心力 centrifugal force ) v% ^0 f) p6 @5 W
离心应力 centrifugal stress2 e' Y; Z; f4 G3 Y# {. F" w- b
离合器 clutch
( a. r) y2 Z f3 N9 I离心密封 centrifugal seal6 C& K9 i- e. {) T7 C
理论廓线 pitch curve
7 A4 K: F/ R$ I" z理论啮合线 theoretical line of action
* y3 i3 V2 W9 `) o9 O- u1 n隶属度 membership( _7 E7 K+ g( N: e6 j2 V0 e- \
力 force
9 Z$ ^+ A4 O, [" C力多边形 force polygon
`; f8 w P* t; Z力封闭型凸轮机构 force-drive (or force-closed) cam mechanism0 D; H7 ^9 G/ T. K
力矩 moment
* `% ]& S$ W0 p* p) ]2 V5 b2 f力平衡 equilibrium
- T7 Y# h4 t1 C$ M& d8 m0 Q' S力偶 couple# F$ [0 i: q! Q$ {- Y
力偶矩 moment of couple
1 U( L* p4 X& S) ]4 |8 d连杆 connecting rod, coupler
1 f" `: q" }6 C$ E连杆机构 linkage
, F8 o% d# J. P' ~连杆曲线 coupler-curve% p$ T ^8 [! p2 ^( e4 f' r# n
连心线 line of centers
4 F b2 f$ A2 H链 chain9 E4 Q, p% {0 }3 W" `6 Z
链传动装置 chain gearing
* L) w+ [6 Z, e链轮 sprocket sprocket-wheel sprocket gear chain wheel
* }& @) |' ~) i0 I# B, |' D联组 V 带 tight-up V belt
) m" v' w" R/ x i p联轴器 coupling shaft coupling/ R! f4 y7 j; O- G. O! D
两维凸轮 two-dimensional cam
) R- I' @! q2 D' l e* t% {9 z2 N s临界转速 critical speed
8 e* Y* B( G' M* ^2 E/ | F六杆机构 six-bar linkage; ~ w0 x9 M+ _0 t; l
龙门刨床 double Haas planer/ M) c& B7 D) D! S2 \3 D
轮坯 blank& g b) m- H" L/ E3 F
轮系 gear train
& ?+ b7 b; I% c) I! n螺杆 screw2 p" L* p) \! Z' k! x" N
螺距 thread pitch- X/ K* W1 q9 j2 A7 K
螺母 screw nut
/ r# v7 ?) f1 y8 d: ]: l9 m螺旋锥齿轮 helical bevel gear, B" P$ o3 q% P7 \ C( z
螺钉 screws
8 l) y4 s9 @3 x1 G, ?. ?; f7 D) X1 ~螺栓 bolts
8 U; J( v' h z螺纹导程 lead
/ K/ t6 r4 C0 H% p4 V; ]- G螺纹效率 screw efficiency, `1 k0 a4 A7 M
螺旋传动 power screw
" G$ C2 M& O+ e C5 J- u8 n! @/ H螺旋密封 spiral seal7 l' l4 M; F; C8 T4 V+ c+ [
螺纹 thread (of a screw)7 }# B- X4 x7 i* M
螺旋副 helical pair
) K$ H0 q2 ^9 C; ^; y$ k+ Z; H螺旋机构 screw mechanism
9 A9 N' C2 o2 e; @% G) L9 C; q螺旋角 helix angle
. U; v0 o& \" D; z: F: x螺旋线 helix ,helical line( q. N' {, Q% b! V9 a6 r
绿色设计 green design design for environment7 k$ k8 \$ V: ^7 k. k' q+ p
马耳他机构 Geneva wheel Geneva gear : _; v E7 D; J; K6 W' X) K0 Z
马耳他十字 Maltese cross
5 @7 r& D/ n) L6 u# Y脉动无级变速 pulsating stepless speed changes y0 Z( B8 R9 e
脉动循环应力 fluctuating circulating stress- R: A9 j& e0 D* F
脉动载荷 fluctuating load9 N% ]" R: U% H) R
铆钉 rivet
9 i2 ~1 E' e& u+ h- D q迷宫密封 labyrinth seal
; M# }9 i( p' K2 x4 P密封 seal+ f& B ^: i" e6 g
密封带 seal belt5 z4 e( o2 O/ H/ d6 T" e, J# J
密封胶 seal gum
/ o* r2 q. A0 n# E密封元件 potted component
t9 G$ |6 E5 S8 c! S6 O! V+ a密封装置 sealing arrangement, O. l7 F: v8 m3 o
面对面安装 face-to-face arrangement3 q/ @" k1 R6 }4 h
面向产品生命周期设计 design for product`s life cycle, DPLC
+ F+ T7 L& V7 r, V! R2 [& _名义应力、公称应力 nominal stress; K- ~4 p. ~( g# S, R
模块化设计 modular design, MD% L- Z3 z. V* A3 n* S! g& x
模块式传动系统 modular system$ a3 [3 K, o/ e' d9 l, W! P, b
模幅箱 morphology box6 k9 I+ H% |; o4 @/ e
模糊集 fuzzy set
8 s- Q6 O# ?* u0 K' }模糊评价 fuzzy evaluation- P h+ {$ \1 E# s* B1 k
模数 module! r w: V# V3 z6 `% c8 W, L
摩擦 friction# f4 v8 P& G4 `# J% W: x; e; _% f' X6 A
摩擦角 friction angle
% K3 D0 u% K% r9 o+ C摩擦力 friction force
% Y3 U# l0 g# \1 j7 X摩擦学设计 tribology design, TD) y6 u8 i2 ]: P5 U4 w( O' k) u, |" J
摩擦阻力 frictional resistance+ B0 P$ k. Y( V6 e( z4 r e
摩擦力矩 friction moment+ J% J Q2 m9 S6 S; y0 x
摩擦系数 coefficient of friction6 X$ q0 B" N8 ] h/ e( [' o- d2 D, k( }
摩擦圆 friction circle- }2 s' l. L0 l" R0 j& [
磨损 abrasion wear; scratching
! m: u r" \, t' T1 E w末端执行器 end-effector
- `2 Z& {$ G" @4 }目标函数 objective function
4 I. l2 ~4 u+ S% M耐腐蚀性 corrosion resistance
$ _7 K U6 ?- W+ E. `耐磨性 wear resistance 1 m( W) o; f% R/ N, G+ }9 [% R
挠性机构 mechanism with flexible elements) K' |# z: Q3 |) A
挠性转子 flexible rotor
' v4 h t% j' V$ T! e- z内齿轮 internal gear2 N3 c* |0 Z' b. {' G+ V- N1 n
内齿圈 ring gear
( p0 s$ o7 | K r! t内力 internal force
- r) t( k ]' [9 ^ D& g内圈 inner ring
" e. _, ] x/ p" D( O能量 energy2 u% T% Y0 J* V/ y# H8 N3 M
能量指示图 viscosity! {% g: s2 P6 S) X( q5 H
逆时针 counterclockwise (or anticlockwise)
0 r3 r' D) s3 ~& X; y& R啮出 engaging-out8 E( n3 W1 W- y1 h; W# m' F
啮合 engagement, mesh, gearing, Y# C3 u0 @1 `% b3 [0 u2 w
啮合点 contact points$ R( |! \; k; f, k' K
啮合角 working pressure angle' v: L) T# P4 K) K
啮合线 line of action7 x- f7 Q h$ Z3 B
啮合线长度 length of line of action
! ], J7 M& O0 P2 q啮入 engaging-in
: ]- L0 U1 H% i8 `牛头刨床 shaper
! A& H6 O# {- D5 }" Q( V4 Y) N凝固点 freezing point; solidifying point
2 i* F( ^/ l0 c4 Z6 P扭转应力 torsion stress
7 F8 h1 _3 \; t' c2 v扭矩 moment of torque
4 X9 Z7 \, s$ H! b; ]; Z扭簧 helical torsion spring
9 k' A! H; |& D: { ^8 g诺模图 Nomogram8 D7 k6 d6 Y6 Y6 u" R8 [ F
O 形密封圈密封 O ring seal0 z) Y. E3 ^( b2 O
盘形凸轮 disk cam
# _% N4 m8 V$ Y8 f0 m8 y6 l盘形转子 disk-like rotor 4 l% L' e: F$ a! n; p7 ?/ Z1 ~( C
抛物线运动 parabolic motion/ \6 t" U5 y/ l5 }& V
疲劳极限 fatigue limit- k. p. e9 D5 i+ m: v4 W
疲劳强度 fatigue strength8 K& P4 k" _/ G2 e
偏置式 offset- ? v9 q+ {$ E( Z8 l2 f
偏 ( 心 ) 距 offset distance* O/ q4 ^- h; N8 a
偏心率 eccentricity ratio; B0 x, C. X% ] O) n! Z
偏心质量 eccentric mass
. t. M$ |9 k7 q偏距圆 offset circle
J! r. y- d/ e" _偏心盘 eccentric
( U# A- T; @7 Y! D) ^! ~偏置滚子从动件 offset roller follower+ u; a6 ~# [3 ^* K* m
偏置尖底从动件 offset knife-edge follower+ t, L' O* E% F) ^
偏置曲柄滑块机构 offset slider-crank mechanism
0 p) _4 |0 x( B9 b拼接 matching, v, Q& m4 d8 p! i7 x
评价与决策 evaluation and decision
3 k5 O/ U- Q0 n; o7 t$ J& E1 f0 S频率 frequency
" R4 X6 e2 E. `3 t* d平带 flat belt
2 n1 B* }8 c$ \( K平带传动 flat belt driving
) m1 q2 p) l# z4 Z& |$ @( _$ p2 s平底从动件 flat-face follower0 b7 g8 w7 x3 b! |' _% K& _
平底宽度 face width
( T6 n H: H4 n9 X平分线 bisector
/ G5 g$ u: Y7 D8 Y- I) y平均应力 average stress" S& P! j" o, m: o! R6 E$ }' L
平均中径 mean screw diameter. t8 ]) P$ [1 E4 g1 N2 N/ F9 f
平均速度 average velocity3 P) ]0 t$ L+ J+ t: F
平衡 balance @8 j5 U% W4 U, T
平衡机 balancing machine/ J/ z1 o! _: o K
平衡品质 balancing quality, C3 ^" C ?' ~' ~6 I% w
平衡平面 correcting plane
+ K7 h: B% V7 m- L+ B. C- Q. @9 _平衡质量 balancing mass# U8 T# n/ q% @& n! _6 H) m
平衡重 counterweight& h4 P$ V) n$ {2 l9 P6 p
平衡转速 balancing speed% f9 E1 v$ h/ y# U
平面副 planar pair, flat pair
' K D5 P/ h9 p$ a% W2 U5 s平面机构 planar mechanism
# H4 Q! T* }0 |1 R6 p( S平面运动副 planar kinematic pair0 `- o$ G. g( M' ~( y, b
平面连杆机构 planar linkage* r" l6 D9 s% q7 Q) T
平面凸轮 planar cam
! t3 O# ~+ Q8 {平面凸轮机构 planar cam mechanism% }/ l0 k! w8 H7 U/ B) Y5 n. P- y
平面轴斜齿轮 parallel helical gears
( j4 s2 n7 R3 d7 W, c普通平键 parallel key5 S8 y* Z: |5 x1 {
其他常用机构 other mechanism in common use 9 O& I4 f$ o% O2 x- h$ H4 f
起动阶段 starting period
4 V" y0 v9 ~4 ~+ I3 V/ p启动力矩 starting torque9 Y! Q4 M# e) n" l5 ^4 {' h+ ^$ O& M3 [
气动机构 pneumatic mechanism
5 w6 o( ?$ ~$ [9 b- y* `奇异位置 singular position; \+ D4 E, h4 e+ C
起始啮合点 initial contact , beginning of contact; J/ ^$ f g8 h; X c1 E t
气体轴承 gas bearing( N2 J' X& V0 e0 c7 @
千斤顶 jack# n) M% o2 u& i5 }" c. E# u
嵌入键 sunk key
. v% F# d& e8 m$ b+ l8 Q) ?- U强迫振动 forced vibration
, [) C8 ?0 R8 d/ t+ t% X切齿深度 depth of cut6 _" k& i' P0 ~7 t& e+ N
曲柄 crank
7 O% t* h- c1 t) ]* h曲柄存在条件 Grashoff`s law
9 I8 i+ w& T( a. Z7 k曲柄导杆机构 crank shaper (guide-bar) mechanism |
发表于 2008-2-21 11:39:46