键槽 keyway
S# z% ^! k, g" P# o" h" l交变应力 repeated stress- d" V+ W& [! r! u m
交变载荷 repeated fluctuating load3 V7 R1 h8 A6 J; K% R; L" t/ {6 s
交叉带传动 cross-belt drive% u* H) R0 }7 O7 I( _, |# e
交错轴斜齿轮 crossed helical gears
* ?1 P, ^! g2 A0 F胶合 scoring3 E& r# e: J- ~$ b! t. r" L, t6 W
角加速度 angular acceleration
) P* i! i0 a% n4 t9 r p角速度 angular velocity6 q H- H" }0 m c0 i; s3 _/ W
角速比 angular velocity ratio" K3 \+ {- z' _2 g' @
角接触球轴承 angular contact ball bearing6 I6 r+ ~; n3 [" A0 X( x0 z
角接触推力轴承 angular contact thrust bearing
! W: G- \& l+ q0 n" I9 b角接触向心轴承 angular contact radial bearing
( d% U2 p: @) N, A5 a& R) g) z# o角接触轴承 angular contact bearing) a7 ?7 R W9 E6 ~* P* }9 g( P
铰链、枢纽 hinge2 W+ b8 V0 d/ k3 c+ g+ W: }
校正平面 correcting plane2 I0 Z' y* \" _: c3 q$ F( k7 @
接触应力 contact stress( W" z8 Y) Q/ z: O& B4 d; }& H: R
接触式密封 contact seal" G7 C0 U' Q# p5 h0 e! m
阶梯轴 multi-diameter shaft2 M$ w. e6 o* ?. g' w
结构 structure
. K8 N' m/ M! R8 z, C% a结构设计 structural design3 ~- M3 B# O- \3 o1 R
截面 section
3 f: C" F& F+ ^. n4 @5 n V! e: A9 W节点 pitch point% z# `! o" e; r1 I
节距 circular pitch; pitch of teeth( @4 B4 N& e, A$ H# ?. N
节线 pitch line& Q6 F; k H7 Q# j9 Z
节圆 pitch circle7 Y- a* n% V- w7 _3 T4 x+ H5 y
节圆齿厚 thickness on pitch circle
+ v" ~, B' V" C( K7 F" a/ D6 ?" S节圆直径 pitch diameter1 G4 m4 _( [3 q# {1 J# o: ?1 k
节圆锥 pitch cone
% _( Z" w, g3 _7 Y节圆锥角 pitch cone angle4 W; D8 C2 q3 L* Y/ v
解析设计 analytical design
( e% Y5 Y( x- q! k紧边 tight-side
' h- D, p+ @0 S: v0 I3 {4 H' w& h5 t紧固件 fastener2 I4 a5 J$ R: x# y3 _
径节 diametral pitch: O. b6 d) H0 ~5 }
径向 radial direction; j. l1 [. ?6 E) @4 j
径向当量动载荷 dynamic equivalent radial load e8 {' l3 Q( ~
径向当量静载荷 static equivalent radial load/ j) E% a* r6 x
径向基本额定动载荷 basic dynamic radial load rating6 o; I* Q, {$ ~& n: U- a7 T
径向基本额定静载荷 basic static radial load tating$ ]. B. `/ W- I* ?% ]; w
径向接触轴承 radial contact bearing
- j% x" _: ^7 Y# u# [; p径向平面 radial plane0 N5 a( c* K: B
径向游隙 radial internal clearance
! T3 G6 ]6 a% ~1 E, T0 h4 E6 v径向载荷 radial load
$ O( `! c' p1 V. F径向载荷系数 radial load factor% c$ ?% @3 o5 ^2 m" n5 e
径向间隙 clearance; V0 N, C) q, K* J) B/ Z! g
静力 static force8 C) r8 ]/ L* H, p
静平衡 static balance8 B8 H$ l, l3 D" P! ]5 w. _
静载荷 static load% W5 B2 ^# r5 _$ W
静密封 static seal
- w& v+ u. Z9 W, M# N局部自由度 passive degree of freedom6 c, U3 B- d' P3 @& C3 u
矩阵 matrix- U. Z* _# O6 q
矩形螺纹 square threaded form# d# n1 b4 G6 I# ~
锯齿形螺纹 buttress thread form' d# P ~/ N( `
矩形牙嵌式离合器 square-jaw positive-contact clutch! Z/ t& l& H( r; U% E/ _# T6 l
绝对尺寸系数 absolute dimensional factor: n5 G* _" i5 `5 P" K0 v0 O
绝对运动 absolute motion& g2 q v* Q) V6 j
绝对速度 absolute velocity
0 Q4 h/ e u+ v0 k8 S& L均衡装置 load balancing mechanism
9 f2 q: R4 z& n! e- m抗压强度 compression strength ) z7 f% U3 Z5 r9 Z6 B6 C) v
开口传动 open-belt drive
6 f' M! f" T1 Z' v5 O* }. N开式链 open kinematic chain% U2 u8 l7 \& `
开链机构 open chain mechanism# A* e/ E) R8 b- X
可靠度 degree of reliability- Y& F6 i3 c- K0 |, X
可靠性 reliability0 l6 T3 y* C" t9 a& z q5 O
可靠性设计 reliability design, RD
! _/ W8 D0 `! K空气弹簧 air spring
/ Q/ H E3 v1 V; |4 |空间机构 spatial mechanism( p4 f1 ^% P' u; V
空间连杆机构 spatial linkage8 S, [; Y8 R, R) E4 Z1 l
空间凸轮机构 spatial cam* P, I3 g. A- o
空间运动副 spatial kinematic pair6 f" \4 d0 A1 P9 M
空间运动链 spatial kinematic chain+ g+ F% x) e- C4 R
空转 idle5 i R, D$ k- M( j* V$ C \
宽度系列 width series5 k, ~2 O- }; s2 \9 o" K
框图 block diagram1 c: S* P* X! Q* ?
雷诺方程 Reynolds‘s equation 2 ^& M5 J7 J- _0 q' K" D
离心力 centrifugal force - O+ ^, y8 v4 _% V; d
离心应力 centrifugal stress( f+ l8 U4 ]% B( n5 H! j
离合器 clutch. i: U6 R* F: Z* N7 {( A5 T: ]; O
离心密封 centrifugal seal, g! X! T' O( u3 c0 m/ c9 Q2 ^
理论廓线 pitch curve7 }5 z8 n1 V9 M* U) e8 o
理论啮合线 theoretical line of action
9 I9 P/ N+ g4 X) k3 \# h隶属度 membership/ x% ^" z# B2 d% Q& b/ f) T2 r
力 force, W# R) E. i' _0 }( ~8 ^4 ^
力多边形 force polygon
9 ]* p$ }9 q5 R! s% x; b0 }力封闭型凸轮机构 force-drive (or force-closed) cam mechanism
/ G+ }# H a& H/ j& |) e2 Q1 D6 \力矩 moment
f0 k% G; J2 h" W( a力平衡 equilibrium
+ B" P; e* k3 `3 K; L力偶 couple2 L" ?+ c& m' r# B Q- g& x- T
力偶矩 moment of couple
. M' H6 h4 T& Q ` Z# R5 y6 C连杆 connecting rod, coupler
1 i* S( i7 H% |" c# X连杆机构 linkage: y3 Q- ^. B2 [( o# ~" l2 b6 n
连杆曲线 coupler-curve
) p' k7 b, g9 e3 \: j& R* t* v9 E连心线 line of centers
/ Q8 }& h0 i! z) P# P( U链 chain
5 R1 P" a7 q/ H& L) M0 _链传动装置 chain gearing( o! F; L& E6 r8 X/ Z$ H m1 u& T
链轮 sprocket sprocket-wheel sprocket gear chain wheel# Z* @" i4 v* J* L6 T
联组 V 带 tight-up V belt! }5 b, @' U" h6 Z1 j9 V0 ?
联轴器 coupling shaft coupling
& ?- z) T( y' f9 a% j4 d% P两维凸轮 two-dimensional cam* k0 s2 a3 H) F% \: ~7 r( S
临界转速 critical speed0 N2 Q' d9 @# d" c4 h& {
六杆机构 six-bar linkage
; Q) ]& y% g5 u# v1 y3 J; s龙门刨床 double Haas planer
8 I5 D% G; }) ?! p1 g* ]; d轮坯 blank
6 J& [/ ]/ A l" F0 }" |6 u轮系 gear train
* a. V. ?8 k/ e3 c, |* @/ N螺杆 screw6 U/ Z; Q$ L9 Z+ y- D7 R& D
螺距 thread pitch1 L+ \- j: a) q. T
螺母 screw nut
3 a1 E! j+ V! O$ ~9 t. }螺旋锥齿轮 helical bevel gear
' J a- J8 j' M$ G# \螺钉 screws
2 _4 N# d2 z5 v4 \" o6 }螺栓 bolts3 f3 d8 A4 g& a0 T" U3 y2 T8 D
螺纹导程 lead% u. M( G+ T5 g0 _9 z; u/ ]
螺纹效率 screw efficiency
# x- d ]7 v4 b# Y螺旋传动 power screw! j' V G# q& P" N. g3 Q5 [
螺旋密封 spiral seal5 H- }' V3 I5 T7 D% h
螺纹 thread (of a screw)7 I* G3 ]; s& y' W. A/ i
螺旋副 helical pair. {* p: i! o6 P9 m) v
螺旋机构 screw mechanism# V5 d1 r8 S, m9 j
螺旋角 helix angle' x/ m4 }+ \! z
螺旋线 helix ,helical line2 d5 H. M( }3 Z
绿色设计 green design design for environment' k% @9 b/ Q7 Y. Z5 E! @! }
马耳他机构 Geneva wheel Geneva gear
: F g; g Q) {1 S4 h马耳他十字 Maltese cross ( H# t5 J D9 a* ]2 o% i& t8 e
脉动无级变速 pulsating stepless speed changes
4 l: I9 u" n/ A7 r3 {7 F6 Q i# r+ }脉动循环应力 fluctuating circulating stress
* E7 N5 l4 V# Y脉动载荷 fluctuating load/ U J% H. }1 f) B1 e' e
铆钉 rivet5 M8 {. a9 L% ]9 _* m
迷宫密封 labyrinth seal+ p6 u, d. K# f" Q9 L
密封 seal7 s7 P) Q1 x+ P) X1 _
密封带 seal belt! Z3 r4 I1 s: l# M. `
密封胶 seal gum
% _3 N+ K0 h8 l8 D' U+ ?( P密封元件 potted component
6 g( m! ^( {* q' a, |密封装置 sealing arrangement
5 {2 y2 N' j: h' c G面对面安装 face-to-face arrangement) H% g- ]$ U4 i+ U7 N- F
面向产品生命周期设计 design for product`s life cycle, DPLC
) \% U' z/ t, e名义应力、公称应力 nominal stress
: f& h: B( j' e4 n9 ]- \模块化设计 modular design, MD! d7 y: u* _4 p S6 ?- L/ Q" n* _5 b
模块式传动系统 modular system
) |1 y/ u. m8 {+ K模幅箱 morphology box" |$ n8 u$ f- }
模糊集 fuzzy set
8 K5 Q' q% B" p& D模糊评价 fuzzy evaluation, @ S" h G3 @0 f" s5 m# s
模数 module% W4 E' { g' B0 U" o8 C5 P: c' B
摩擦 friction
2 p r, r, _0 v6 n: G2 m5 s摩擦角 friction angle
. F. V$ A. R+ V# Q6 J3 U& c摩擦力 friction force
- Z5 h! e4 ?# y( H$ \) q摩擦学设计 tribology design, TD' q2 R2 v. u$ p5 S
摩擦阻力 frictional resistance7 N- \6 S" X" s% I/ I" W
摩擦力矩 friction moment
+ t: M- T3 N7 a- D+ `$ R) i# M摩擦系数 coefficient of friction
' l% ?' U( t* C+ K$ n4 D摩擦圆 friction circle* R* S5 i2 q: u0 C6 p( w) w
磨损 abrasion wear; scratching
' b! g7 N1 ]. `0 t4 _9 s* k1 R末端执行器 end-effector& k# H$ s! H4 K$ o7 f+ @# Z
目标函数 objective function
3 n1 C; \2 L8 @8 g$ c耐腐蚀性 corrosion resistance 9 O# s6 E' x- g2 l
耐磨性 wear resistance
- u4 O( n1 v Q$ N) s挠性机构 mechanism with flexible elements
u: `4 e5 d+ }8 M) J挠性转子 flexible rotor6 L- I; M2 Y& X0 p+ w3 Q8 _
内齿轮 internal gear+ i$ Y' M* q' f: B' \. W, d# `8 w
内齿圈 ring gear
7 d C0 A* P Y7 O% J内力 internal force
9 d9 o3 ?. P6 M内圈 inner ring6 \, J2 q g+ U( h- b9 F
能量 energy
# u+ [7 ?7 f" P5 _能量指示图 viscosity
6 j0 I& m2 I7 H0 J& ~* H% h3 p+ |2 T" [逆时针 counterclockwise (or anticlockwise)2 g" d& Q2 f T8 _- E1 @
啮出 engaging-out
7 z5 W0 M$ x8 v0 `2 ~啮合 engagement, mesh, gearing
+ O8 s6 i4 p! \; P啮合点 contact points. o$ h* u. ]1 l2 |6 i
啮合角 working pressure angle! w b A8 I: I& A7 c) m
啮合线 line of action% \! E' w) r: m3 A
啮合线长度 length of line of action0 q6 F* v5 g* Q" Y$ o/ X5 w4 q
啮入 engaging-in
" v) v1 W$ ~3 g. Q+ @- D' b牛头刨床 shaper8 Z$ P: T2 a1 q9 r5 [
凝固点 freezing point; solidifying point
; v2 g" _! V0 r3 w0 @扭转应力 torsion stress! y Z3 {! ?$ x. ]% t8 b @
扭矩 moment of torque
& m4 a5 E- @* {4 |扭簧 helical torsion spring
% y# G( J `! J% L诺模图 Nomogram- d6 M2 _- S F* G3 v
O 形密封圈密封 O ring seal- t4 i! d: g, [$ ]& I( B$ m3 d
盘形凸轮 disk cam $ ]4 j: a0 b! o# C0 b
盘形转子 disk-like rotor
9 E3 A! m: ]. h7 l- W抛物线运动 parabolic motion, G6 y$ @9 \: N2 x/ n, z. B9 u
疲劳极限 fatigue limit
! X7 I; q! P9 z6 j* t9 F疲劳强度 fatigue strength# ]2 E( H2 A& y* O$ b: J1 g% C2 I
偏置式 offset$ D, G3 w( K. }2 k, u0 V2 b ]3 m
偏 ( 心 ) 距 offset distance
$ x @# G3 A0 x( Q+ }偏心率 eccentricity ratio
' k, m8 D) E3 S" x6 ?$ c! Z偏心质量 eccentric mass
# M/ E) h7 a. ~8 x4 [/ S: g2 V偏距圆 offset circle
3 R( L# M7 |1 R+ E0 P% L! {偏心盘 eccentric
8 R! g2 g8 l( d& Z% R, i3 q偏置滚子从动件 offset roller follower
% Z! S. y9 G8 A& c$ e, I- }( y偏置尖底从动件 offset knife-edge follower
- v) x7 r8 G) @0 A- k* Q偏置曲柄滑块机构 offset slider-crank mechanism, w* ^# N2 t) b- r% d3 L
拼接 matching2 f" h4 h4 P1 ?9 K
评价与决策 evaluation and decision/ L. u- S2 c" \ E& P
频率 frequency/ Z; I! f2 h2 B" } ~ P b2 O: V# r6 ]
平带 flat belt V& A6 U2 B- V a1 W5 ^: Z: B5 U
平带传动 flat belt driving
) E' H/ T9 D% O1 l5 p) h平底从动件 flat-face follower
2 d I& }0 C( K. x) @/ ?平底宽度 face width
5 B( x# D2 U/ ?4 O5 } ^+ S" w平分线 bisector7 `4 X* j6 S2 N$ h5 U- D1 `
平均应力 average stress' ?2 O: q2 k- R/ d4 {# a: R
平均中径 mean screw diameter
. ~$ O5 J$ y9 x2 v; r平均速度 average velocity' D5 J6 V6 v9 I
平衡 balance
A' {9 V% t8 ?/ t& O$ l' g/ K平衡机 balancing machine6 C" ?' E; a. o$ d
平衡品质 balancing quality
1 ?% [# F* `- @* u0 Q$ h$ w! z% p2 a平衡平面 correcting plane
$ J5 @+ y" i7 y0 y5 r0 w% @' ?/ L平衡质量 balancing mass% O7 r4 w1 }2 n
平衡重 counterweight Z9 E8 b% [ o1 O
平衡转速 balancing speed
( B+ d& f! m }7 I4 R平面副 planar pair, flat pair6 t: @9 H% d# b% f
平面机构 planar mechanism# U4 ]8 ^ }; T$ z4 E" _8 `8 h
平面运动副 planar kinematic pair
$ Y( S2 | s% N5 @2 {9 a v7 L2 N0 U平面连杆机构 planar linkage
0 o1 ^* u. d9 R$ h平面凸轮 planar cam# K. K4 n/ [; E- C9 o0 Q/ Y# ]
平面凸轮机构 planar cam mechanism6 |3 p) v9 S! p7 w# }/ Z! A
平面轴斜齿轮 parallel helical gears
4 T0 ~% }3 S5 }1 A' `, H3 c普通平键 parallel key# x ?0 E' A! M$ f
其他常用机构 other mechanism in common use , M' P$ r P, ~8 ]
起动阶段 starting period , `" N% u" F( [/ r- k2 p8 {
启动力矩 starting torque7 w2 ?% C5 a. s3 T9 a
气动机构 pneumatic mechanism
) Z' h9 [! I1 H8 o Y( ~* ^奇异位置 singular position2 p1 J+ A# k" H3 {4 \* W7 Z
起始啮合点 initial contact , beginning of contact
# _0 I. [0 K" f& m6 v0 F) Y气体轴承 gas bearing
# e( C/ \7 z) j2 `2 e' G千斤顶 jack
6 v3 V- Z# l! S/ p嵌入键 sunk key
$ ~6 j( M2 s: H: o& g- f# m0 K( P强迫振动 forced vibration C2 x4 J& b: F8 R
切齿深度 depth of cut M" n, M; \) {
曲柄 crank
+ A5 ]. T3 n. ~/ v8 g+ a曲柄存在条件 Grashoff`s law3 `' c# D: Q' {& c9 [* |( p. e2 O
曲柄导杆机构 crank shaper (guide-bar) mechanism |
发表于 2008-2-21 11:39:46