键槽 keyway1 V2 |3 r6 @# e6 ]8 Y' b
交变应力 repeated stress1 D* ]2 k7 y% |, W
交变载荷 repeated fluctuating load
; [" D' M4 I% D! h交叉带传动 cross-belt drive) o0 S ^# \, p$ T6 Y2 }! o
交错轴斜齿轮 crossed helical gears5 n6 \4 t- h5 O, x
胶合 scoring- p, l+ r, ^% ]; k
角加速度 angular acceleration
, U8 t ^' C( \( w+ H角速度 angular velocity4 c$ P8 ^# r1 X' e( y# {7 E
角速比 angular velocity ratio
: G9 {- z4 a n" l1 d/ \角接触球轴承 angular contact ball bearing
7 L _# S9 i( E* Q2 {7 K4 S角接触推力轴承 angular contact thrust bearing
% s# i: e& Q) {" D; m8 D& Q角接触向心轴承 angular contact radial bearing! p3 e6 R4 b2 |% G
角接触轴承 angular contact bearing4 @. G4 `- x2 M- |5 W5 O. Z
铰链、枢纽 hinge
8 B3 }: e" m" j- _. {校正平面 correcting plane
0 H! p# o) D6 ~; t接触应力 contact stress" _2 \/ Y4 l: J0 S/ u
接触式密封 contact seal% N" _1 t' z, e6 W
阶梯轴 multi-diameter shaft. Z6 `$ r1 Y9 [
结构 structure1 ]* F& V4 h# d% _/ }2 ~' N
结构设计 structural design
% X3 y% |) ] d: y6 c" F" C( N截面 section
$ ^+ S: a2 ?' _0 D节点 pitch point
0 t2 ]1 \: v! p% ^3 i, G3 `节距 circular pitch; pitch of teeth d% j5 Q: } d, ]. ?4 z7 X
节线 pitch line
, A" {/ K8 B) m Y节圆 pitch circle
' t5 d d& t0 f B! j% P- u9 `- O节圆齿厚 thickness on pitch circle
# A1 U1 Y3 H% G7 t | K节圆直径 pitch diameter) g# H4 J' x4 p } {2 u# O
节圆锥 pitch cone
1 K, e9 v( b4 A6 h2 G节圆锥角 pitch cone angle
. ?: Z- I3 {9 R" T解析设计 analytical design. D+ \7 y, Q9 N" k/ m
紧边 tight-side9 W$ B" L# l7 l7 O6 f# A
紧固件 fastener
8 Z- P3 G h- o" R; H1 x! d' i径节 diametral pitch3 G' x# g2 r& L! V4 H
径向 radial direction
1 X& m# }2 _, {; c' M/ _径向当量动载荷 dynamic equivalent radial load {; U7 G" E) r( w
径向当量静载荷 static equivalent radial load
' q0 f. L" L/ c5 L径向基本额定动载荷 basic dynamic radial load rating# W% ?/ Q' C. _& l U2 @ V0 E
径向基本额定静载荷 basic static radial load tating4 b$ h# Y* j) \8 U& i9 l
径向接触轴承 radial contact bearing( S! i. }8 w0 h0 M
径向平面 radial plane* h* B6 B! z5 h. ?# V
径向游隙 radial internal clearance2 s7 R- J: E0 I0 m
径向载荷 radial load& c$ C0 t% B9 m
径向载荷系数 radial load factor3 R2 w. o" k# w0 m
径向间隙 clearance/ e2 b5 z1 g9 j4 B
静力 static force% `( s# }" t$ a' H+ l6 `4 T1 B' N: M
静平衡 static balance
" {7 w" H2 b S8 T3 A, S静载荷 static load2 Z2 N# q0 H' M& i+ k% j$ \
静密封 static seal% ?( R- u; B: z) s8 \
局部自由度 passive degree of freedom# M% l g! B4 i$ h0 g
矩阵 matrix k( M8 m. l# \9 T3 f* O5 h& j9 s
矩形螺纹 square threaded form
8 o3 K: K* G' }; _$ G' a锯齿形螺纹 buttress thread form
u/ R, E5 x9 q& C: i8 V6 c. U矩形牙嵌式离合器 square-jaw positive-contact clutch& ~2 {& S _, g j K
绝对尺寸系数 absolute dimensional factor
; v# q ?! w" T% h绝对运动 absolute motion, A# H5 Y- E7 b0 V1 p1 B& O7 z
绝对速度 absolute velocity6 V6 U; k4 G# P6 W# s% c# F
均衡装置 load balancing mechanism+ \" O( I# ^! _4 N
抗压强度 compression strength
2 ~+ P. M! d9 N; i4 K5 _( K开口传动 open-belt drive $ S( T3 {/ I0 h/ J5 A9 R+ c
开式链 open kinematic chain
! B: |* Y+ R8 \- @% K$ ?开链机构 open chain mechanism
8 N% a. x% T& g可靠度 degree of reliability% R: ?! z" _! X: }! \# X5 [
可靠性 reliability' L; e' l5 |1 y# L }. x# W
可靠性设计 reliability design, RD
+ C9 K1 p" y; a; a; k空气弹簧 air spring
- t1 ^4 j- R8 M3 |( h空间机构 spatial mechanism0 I, H }" w0 U3 `
空间连杆机构 spatial linkage7 x3 N7 O1 J1 C5 e* v
空间凸轮机构 spatial cam
7 V* }. l v, ]( Z, c空间运动副 spatial kinematic pair
, d% Z6 ]8 K7 l5 P空间运动链 spatial kinematic chain- j# l1 U- e4 B) u! v; G, H
空转 idle( k2 e1 K7 x; H% I7 I
宽度系列 width series$ D7 W8 D* B# c
框图 block diagram
5 R- A `4 O" c, Z0 c) e, _雷诺方程 Reynolds‘s equation
1 E0 C) z, L6 x8 Q0 ^1 E9 k离心力 centrifugal force # Q3 `4 ~7 L3 {$ B* R/ A/ U( k
离心应力 centrifugal stress5 P$ ?+ W& @+ R* r, L7 x3 ?3 h) {" c1 a
离合器 clutch- I8 C+ Y, j8 A2 c3 ` {
离心密封 centrifugal seal$ w3 n% E* \# m# |5 } v
理论廓线 pitch curve
8 ^1 B! V4 O9 l2 R$ c理论啮合线 theoretical line of action# W4 T3 |+ u8 r* N
隶属度 membership1 L. _. v* ^+ `# i
力 force
) C4 e! v: ~2 D! N" n- }, p* R6 _力多边形 force polygon' u0 j M' G" z ~1 g! f. U
力封闭型凸轮机构 force-drive (or force-closed) cam mechanism
. I9 o2 M$ _' W/ `- O( J力矩 moment
' S& I) P+ r' g3 a: ]力平衡 equilibrium
+ R4 w- Q5 k' i1 l- f* |3 n( J力偶 couple
: [2 _2 R3 [9 F* w+ B力偶矩 moment of couple
7 X) S0 `4 |/ f! g& `" B连杆 connecting rod, coupler
: y2 g& }, D- q, K连杆机构 linkage
% m. S5 D" S( d6 ^5 V6 K2 c连杆曲线 coupler-curve
0 O" f) N5 T* q6 ?* | a! D/ x连心线 line of centers5 f) {$ x/ m+ _7 y- ?, ~4 i
链 chain. h+ a$ s2 t9 v3 K/ y/ J$ o& K
链传动装置 chain gearing. e/ _; } d' }* u, W
链轮 sprocket sprocket-wheel sprocket gear chain wheel
: e) w6 N: Y l. z$ z2 j% I联组 V 带 tight-up V belt
8 _7 W0 ]' s6 j' T# n# s7 |联轴器 coupling shaft coupling1 Y" d" c- h5 w. p
两维凸轮 two-dimensional cam& e X$ |, [# y- ]
临界转速 critical speed
- x, x$ Y) g; B- ]六杆机构 six-bar linkage
- L2 P/ ]5 a% A, v! J龙门刨床 double Haas planer9 A8 i& \# P. C& K2 f% T" g
轮坯 blank
8 |1 j* y, x7 U9 b8 t轮系 gear train
3 t, E+ k9 o \3 S- s: x' n螺杆 screw9 S- W& C# H5 ], c6 w q) W
螺距 thread pitch
0 h5 B" M: @* h) |螺母 screw nut
; ]8 p/ p, ^% A# K& N( C3 s螺旋锥齿轮 helical bevel gear
+ f' T0 c* L* S2 A; d螺钉 screws, x2 n' U" ?& b# t( q
螺栓 bolts" ]. w6 [( k* z( j8 f. g
螺纹导程 lead/ E7 C* I0 H/ N' s6 `5 B
螺纹效率 screw efficiency) N5 Q9 [' R% n! K4 k+ R# `
螺旋传动 power screw I# O6 L. e, i: B! Q
螺旋密封 spiral seal
7 p# v n ^( p# F螺纹 thread (of a screw)# Q- T: V9 m* X% f' j/ T2 T6 J, i
螺旋副 helical pair
% i/ T7 q: i" H7 j' x6 z' Y螺旋机构 screw mechanism' }; y0 O- `6 L
螺旋角 helix angle, s" K/ ]4 O3 }7 ?1 J* i
螺旋线 helix ,helical line
* f S9 w1 ^" \* O3 ]绿色设计 green design design for environment0 j' _& q2 T& S6 p/ O1 a; V
马耳他机构 Geneva wheel Geneva gear % j5 T; S# W' p
马耳他十字 Maltese cross / P. m9 n- V5 C* K! h
脉动无级变速 pulsating stepless speed changes
5 X, X5 ^! z6 [脉动循环应力 fluctuating circulating stress
/ l0 d9 Y% h T6 x9 t \0 }' K脉动载荷 fluctuating load
: f2 Y. L3 n0 ~) [6 g* Q铆钉 rivet/ T ~; i* ]$ S
迷宫密封 labyrinth seal( t3 K" I; ]$ x5 A1 x6 ]& m
密封 seal
! S. a! }* K. ^/ {密封带 seal belt5 f, b. E6 s" ?$ ?3 D4 p% ]: g
密封胶 seal gum
, t* \( {0 s+ G M: U密封元件 potted component; u& f1 M2 v3 v
密封装置 sealing arrangement6 A1 A; P) L: F3 O/ d6 W+ V# ]
面对面安装 face-to-face arrangement
- z7 O! p" v& X5 z9 ^0 i& |面向产品生命周期设计 design for product`s life cycle, DPLC
5 ?% g0 r3 U* @# A0 H) a( o: D名义应力、公称应力 nominal stress
3 u( P" @' ~- W7 Y% Q* I& {* Y模块化设计 modular design, MD
$ Q$ X: b! V. F/ L2 C6 T模块式传动系统 modular system/ ]- f7 w. s/ \- a: c' k
模幅箱 morphology box
( g8 R' W6 D) }( N6 |) D5 h) t. R模糊集 fuzzy set
& F: f" b6 V4 T9 K模糊评价 fuzzy evaluation+ c+ p/ ~! c' k' ~
模数 module
: l" v3 A# @/ W/ M摩擦 friction
6 p( u( ?# e5 _3 d# _/ u摩擦角 friction angle
$ ~1 |7 ?& q$ h) S! }5 c摩擦力 friction force
6 Q' G9 F- g" R摩擦学设计 tribology design, TD' F+ I% M& L9 ]0 N( V
摩擦阻力 frictional resistance
! k8 q5 w: F2 J& D+ w0 R$ Y4 d/ E摩擦力矩 friction moment
& F) Y3 \0 `0 j H摩擦系数 coefficient of friction
9 W* x$ j; m5 x8 B3 b- D摩擦圆 friction circle
3 w6 H! C& Z1 K$ S3 l# t磨损 abrasion wear; scratching
. C' C4 Y# |- o5 f& |末端执行器 end-effector7 u; s5 e$ h u% E
目标函数 objective function
2 N( z* A; k) D2 R8 q# t; L* S耐腐蚀性 corrosion resistance ; Y6 |) F$ |0 c3 v# F" {3 ~
耐磨性 wear resistance / n* \1 z9 o7 J. B( J% d
挠性机构 mechanism with flexible elements
6 b; R! w2 O( b6 x3 G挠性转子 flexible rotor9 ?& h6 e4 O& w8 [0 _- g3 B7 }
内齿轮 internal gear# _/ L. b X% p2 u; ?4 W. T
内齿圈 ring gear+ X% [& ~; f! i/ h2 v! b
内力 internal force
O* t* k& O3 s7 k( P; W内圈 inner ring
) n- j H% H$ i/ v g% Z' W能量 energy
2 |% v8 h% P+ J: `4 |0 A1 {8 ?5 Y能量指示图 viscosity
; l" n& _: }7 ?6 U0 M* Z逆时针 counterclockwise (or anticlockwise)9 }8 {, ~: c0 w4 k% ?3 X* ^; _" Q! b
啮出 engaging-out
! Q) U |2 k* T& d啮合 engagement, mesh, gearing% G# g ^4 u0 H1 k% w b+ {" D
啮合点 contact points+ d' B1 c4 M1 ~1 N- m4 @
啮合角 working pressure angle
, `* Z0 }! ]: e7 L" H啮合线 line of action
7 Y' O" ]5 W$ n' R啮合线长度 length of line of action! ^0 w' H) w6 Q7 X: e! [
啮入 engaging-in
6 A! f' w4 K7 t: Z) a牛头刨床 shaper. {1 a A$ R3 J* Q4 @
凝固点 freezing point; solidifying point% T9 S& q0 S( _: h
扭转应力 torsion stress
0 v! j, r; z* A) g% s7 ]6 [5 w扭矩 moment of torque
9 A( C, ^2 q2 O! O5 R j, S扭簧 helical torsion spring
; M2 k) n+ D1 u7 D* @% V/ b诺模图 Nomogram
1 {6 E/ b, p; f1 @% B! zO 形密封圈密封 O ring seal
3 n$ O- K$ b3 R, t; W+ L" K% P3 R盘形凸轮 disk cam 8 S6 f, v! ]- h0 _0 x
盘形转子 disk-like rotor ' c% g9 Q4 s# J& o: B# o: Z* Q
抛物线运动 parabolic motion7 y$ [4 |; F# v
疲劳极限 fatigue limit
1 X- i) g! ], v疲劳强度 fatigue strength/ }7 E2 K( k+ i7 g F1 `8 \
偏置式 offset
0 c: S8 o# c( z1 Q# m" Z偏 ( 心 ) 距 offset distance: Q7 N6 C1 }) l1 Y! m
偏心率 eccentricity ratio
0 F2 \5 E* C3 h( r; O偏心质量 eccentric mass
M( W! q5 \1 y# a L偏距圆 offset circle9 c, s( }: p4 I, b/ s
偏心盘 eccentric7 a1 P, p/ q" l9 A: Y' k, Q
偏置滚子从动件 offset roller follower7 c" A* P" \0 w0 D7 \; o
偏置尖底从动件 offset knife-edge follower/ S8 m* q, @; _4 K% J9 i& ~+ d# \
偏置曲柄滑块机构 offset slider-crank mechanism
" T$ A, e: z+ G1 X- C1 d% w拼接 matching r( O7 L: J+ `$ T
评价与决策 evaluation and decision
6 Y u4 N; t/ }) K" q2 `& Y1 I频率 frequency
, r4 R0 g* a4 F, [" ~平带 flat belt/ x) H9 u) C5 m' h2 ]) w
平带传动 flat belt driving" u9 E6 E+ x' R- o
平底从动件 flat-face follower& b( y' i2 d4 r: A7 N" d" g6 x
平底宽度 face width0 D; X- j0 y# \. x8 r( l' T
平分线 bisector- n' q, t9 p3 e1 R$ N# r- w" p
平均应力 average stress
+ E3 ^$ ]. `9 p6 W0 S$ x! f6 e) m平均中径 mean screw diameter
9 I) Q8 V% G0 ^: x1 J. {平均速度 average velocity- y; V2 L* M9 b* _- y
平衡 balance
% p+ {. |. w d! G平衡机 balancing machine
- |6 n: D: K* X9 |2 k平衡品质 balancing quality
: \2 [! R8 _/ a8 s平衡平面 correcting plane4 ^7 A/ y/ m6 i q3 v3 H' e7 @4 J
平衡质量 balancing mass% z# u2 b( j+ h) D& U/ T0 C# [
平衡重 counterweight( d0 W' ^& ~1 J+ m
平衡转速 balancing speed
) q) `7 g7 i) O平面副 planar pair, flat pair- S2 R, a. J4 x
平面机构 planar mechanism
1 A4 r" q' k8 g3 S [& x+ i平面运动副 planar kinematic pair
4 M" r" o5 @. b( E% N n* M平面连杆机构 planar linkage7 g3 n2 Z- U; ~. H. y2 m
平面凸轮 planar cam
/ |" ]- p$ i. s* P1 B5 W3 G3 D, Z平面凸轮机构 planar cam mechanism/ K: y- t* r% X2 z' k' {" m
平面轴斜齿轮 parallel helical gears" ~: [. i2 W8 i1 d
普通平键 parallel key; e& l% h' g8 A, G' I- W- Z+ q
其他常用机构 other mechanism in common use
/ ? W' t! k. ~ r- _8 k- v起动阶段 starting period 8 ]3 Z8 _" V' ]$ p; G# {$ M
启动力矩 starting torque
( r2 L4 [$ u; G气动机构 pneumatic mechanism
% F9 Q" Z% R/ z" G" _; e p奇异位置 singular position5 l1 n; Y7 l. }2 G# e
起始啮合点 initial contact , beginning of contact
; k! p; N* U+ Z6 l% h/ z1 g气体轴承 gas bearing
0 Z S e% M. z+ X; D2 G千斤顶 jack
: Y( Y- ~, R5 {. k! z2 [嵌入键 sunk key
( c1 E. \! C. i7 w& r强迫振动 forced vibration7 p7 l, Q0 w& Q3 ~8 j, ?6 b
切齿深度 depth of cut& Z: a9 S" B( ~. z2 Q4 H+ Q
曲柄 crank
# R1 B2 E6 f+ j0 T曲柄存在条件 Grashoff`s law
$ L$ j& H8 b" o曲柄导杆机构 crank shaper (guide-bar) mechanism |
发表于 2008-2-21 11:39:46