键槽 keyway
0 b% @9 ]7 ~/ Y7 U交变应力 repeated stress
# w" U& r$ ]" ~5 S6 W- f$ K交变载荷 repeated fluctuating load7 t: T: O* T- v) E5 _: k! W
交叉带传动 cross-belt drive. v4 g0 W' r. v, T( o
交错轴斜齿轮 crossed helical gears
% q- t, o$ w- R$ L胶合 scoring4 J! I& i( H( j# Q
角加速度 angular acceleration' k- k( C1 \/ q: G, C
角速度 angular velocity6 W- E$ a) x% Y4 A5 r
角速比 angular velocity ratio$ z+ I. Q$ m9 y9 |8 I2 s. }
角接触球轴承 angular contact ball bearing7 T1 A% [% C) r7 e
角接触推力轴承 angular contact thrust bearing
# z, _, F0 x% i1 n角接触向心轴承 angular contact radial bearing
, R' L1 s; q7 v: ]* m角接触轴承 angular contact bearing
7 E8 E$ |! t) e# ~" Z* [" Z铰链、枢纽 hinge& u+ i5 h: j0 @3 ]- d. ?. J4 b
校正平面 correcting plane2 @% T( F$ c: d9 k7 `: K$ w
接触应力 contact stress0 l' M1 j3 J, z+ a* Y2 }
接触式密封 contact seal
% Z3 r6 P; q R0 C8 N阶梯轴 multi-diameter shaft9 ]% P$ }4 D5 }
结构 structure9 D, ?; q1 G- |+ i
结构设计 structural design
; j! }# M1 r8 s' K4 t5 K截面 section( E' b H) D* p2 Q
节点 pitch point
" e" S: ?9 n/ o" E, x% R9 G节距 circular pitch; pitch of teeth
2 r/ F& U% _# x; E- h节线 pitch line
c1 G! ^* x0 B. A% i节圆 pitch circle2 g; F' g) q! ?* M
节圆齿厚 thickness on pitch circle( g! m1 p7 l& \2 s4 V% a6 W
节圆直径 pitch diameter
* M# T+ N3 M" t, w' C/ s节圆锥 pitch cone8 o1 e0 S; U9 a, [; K' O; C
节圆锥角 pitch cone angle
# D9 `7 S) V' r2 h( H( B; Z3 F解析设计 analytical design
* a) C( j) y. s* l紧边 tight-side
) n" \# H4 K: k0 H$ l( Y, v紧固件 fastener
' D( p) O9 Q" z' Q0 ~9 D% P# x径节 diametral pitch3 l. _& w% L" U2 b4 k9 R& ^
径向 radial direction1 [" J1 F: }5 X) H* a
径向当量动载荷 dynamic equivalent radial load
% w) [$ j) s: ]! V' f: l1 a径向当量静载荷 static equivalent radial load# k1 ? E, }" M' j
径向基本额定动载荷 basic dynamic radial load rating& G4 g' N' B; k1 h! ]8 z
径向基本额定静载荷 basic static radial load tating6 P z) U' v2 c, f# K! N. B7 x% g" x
径向接触轴承 radial contact bearing
/ y6 W* J1 |' x' Q& r% |径向平面 radial plane
6 g5 _. L% b( q f径向游隙 radial internal clearance+ G! X9 T. P$ a" E' a
径向载荷 radial load
) y0 h& j$ w5 W6 k: N径向载荷系数 radial load factor9 x2 Q( q F$ U1 z' {1 A% k
径向间隙 clearance+ [& F4 ^7 [" X/ i3 P# G
静力 static force$ x1 I1 Z* K! v- P, f; B/ ^
静平衡 static balance
; }; U. a; ?1 o% H8 {# Y静载荷 static load
$ u% {, s; L* w2 a静密封 static seal" u, m4 E* E4 E/ c; u
局部自由度 passive degree of freedom
1 W: R$ Q4 _, z- z矩阵 matrix
+ \: k) k1 T, R) {1 c矩形螺纹 square threaded form
! l0 ^5 H3 ?! z; n* p锯齿形螺纹 buttress thread form
, ]8 s4 e$ z% Y% g; w& G( x5 f矩形牙嵌式离合器 square-jaw positive-contact clutch
# f* R* ^. d- Z3 _) ^# {' F; ?绝对尺寸系数 absolute dimensional factor
& k$ a+ T6 V3 V; H9 p6 h绝对运动 absolute motion
. v* r- x# h. v( F- O, r绝对速度 absolute velocity
, ]6 l! i9 v, X! b0 q均衡装置 load balancing mechanism
) c1 f8 n* d2 a! v抗压强度 compression strength & b2 l$ v4 k7 t( M4 ^
开口传动 open-belt drive
& e* X9 F- T! R) Y4 F4 T开式链 open kinematic chain7 Q% i( p; A' k$ N5 y4 e: i
开链机构 open chain mechanism7 | S) m" {8 @' F& G: J
可靠度 degree of reliability
$ Z! f1 ?2 p9 p6 w/ ?/ S+ {/ o, _可靠性 reliability" B: s# n- q1 h& Y4 `2 o4 @2 O/ F
可靠性设计 reliability design, RD: |9 `8 u* f& W; J o
空气弹簧 air spring
0 g7 P+ I& ` v" Q1 G; o. ]: ]空间机构 spatial mechanism" m! ]! P0 {4 Y1 n
空间连杆机构 spatial linkage
8 B5 i7 N! {/ R" N. J1 K空间凸轮机构 spatial cam j* {$ \6 @" J) |* x: M
空间运动副 spatial kinematic pair
9 ^; S! d- k* O4 @4 Z/ e7 E空间运动链 spatial kinematic chain- I- A1 w! Z) B9 d3 i
空转 idle$ }3 q6 @) M: ~& v" n5 L
宽度系列 width series* n% k1 P: ~( ^1 p h
框图 block diagram
) x% Q* C3 C: d- r雷诺方程 Reynolds‘s equation 5 ]0 E( ^, E) c8 \/ t7 i
离心力 centrifugal force ) Q5 m# v- ~( _0 b5 A/ ^ A! ^
离心应力 centrifugal stress
2 O3 o+ n1 w# Q/ L: x离合器 clutch& a/ `3 l9 Z1 N. ^$ A2 }! k# d8 {3 ]
离心密封 centrifugal seal# N4 M% f8 o. ]4 t
理论廓线 pitch curve
* C$ g2 F7 P, ~9 [- u9 m8 N理论啮合线 theoretical line of action7 f# J% H8 o% C2 |) f8 u( R
隶属度 membership
9 x! P* C7 f. ?力 force
( P; D6 J' u* x" |) U2 E q力多边形 force polygon9 v! h" Z4 i' a0 `( L9 s5 k: w6 z
力封闭型凸轮机构 force-drive (or force-closed) cam mechanism2 h; E& ?' R$ _5 ?' Y; S) \
力矩 moment
4 P# s& ^8 {9 Z8 I力平衡 equilibrium3 Q" I3 d( [6 n" C
力偶 couple
0 r! s3 u. z2 i& m/ _力偶矩 moment of couple2 o6 ?0 H2 |* R5 G- ~
连杆 connecting rod, coupler# ^# {* y* ~" o/ G
连杆机构 linkage1 F* h! S3 [. M I' I6 }- v' y
连杆曲线 coupler-curve
, T" s: V) `8 d连心线 line of centers+ |' K1 e: C" [1 |8 g4 I9 F6 }
链 chain
+ x/ F+ J( p) v链传动装置 chain gearing1 B* l w5 E) X2 {- N3 ~2 a
链轮 sprocket sprocket-wheel sprocket gear chain wheel
7 t/ W! {0 J; A% H联组 V 带 tight-up V belt
4 z0 ]) n6 {2 H+ j4 v联轴器 coupling shaft coupling- ]$ Q" X: f1 e0 T* l
两维凸轮 two-dimensional cam+ ^% x: b! ?! y, }% p
临界转速 critical speed
3 j1 P) ^/ ~5 K六杆机构 six-bar linkage
) s4 Y2 o( v3 e8 C% h7 d: K龙门刨床 double Haas planer$ E X, X5 F. a8 @& y0 J
轮坯 blank
* }' ]$ u) o- e3 Q0 y3 p轮系 gear train& w$ ^+ T e: U
螺杆 screw
8 Q* g7 O6 G* ^+ r7 Z& Y [- H螺距 thread pitch1 |& x0 f6 c! m* C
螺母 screw nut
. ] h% u, p! Y9 k0 N' q: `螺旋锥齿轮 helical bevel gear
. A9 z; M( u6 k: {3 ^螺钉 screws
- ? X" h3 H q2 @3 Y8 X螺栓 bolts* u; D8 N- \' t2 x0 s2 @
螺纹导程 lead, F1 d6 r( Z$ r+ U) }
螺纹效率 screw efficiency/ U9 H' J3 c$ X0 e- }3 w4 o8 X
螺旋传动 power screw
. g- A( t" W1 L3 ^. W; J& v9 d, _螺旋密封 spiral seal; p8 {* Q' ? F5 y) ?4 h
螺纹 thread (of a screw)
% z H( q1 M2 A% e0 r; g螺旋副 helical pair, p3 I% S' G9 P" y# C
螺旋机构 screw mechanism
- ?+ V. d: q9 r: z螺旋角 helix angle8 l* o! W# ~/ m+ v$ \2 B
螺旋线 helix ,helical line
& s4 X( q0 s9 V: R" `+ P3 g C- @绿色设计 green design design for environment& I& c' w! E; G2 D% q
马耳他机构 Geneva wheel Geneva gear
' N9 x6 Q F6 Z; k! s马耳他十字 Maltese cross 2 I2 U& i+ ]! w! j. g
脉动无级变速 pulsating stepless speed changes
7 u# y) ]- S% l脉动循环应力 fluctuating circulating stress
v% t3 x4 U& \4 P/ e8 m; s6 V脉动载荷 fluctuating load" z( J s' Y! ?! V
铆钉 rivet. M+ B2 A7 O6 U: {) Y n' k
迷宫密封 labyrinth seal3 R' u; J$ J( L5 b
密封 seal' I2 r0 N) ]8 s+ Q# O+ w
密封带 seal belt
, B1 O1 d' }8 z, [, G# W密封胶 seal gum" F) ~( Z- @( U" Y) z, g" l* X0 j
密封元件 potted component
- \$ {4 S& `6 ^& M* K. L# i密封装置 sealing arrangement
5 H0 V t( {3 ^1 Y4 [5 W9 _9 I9 D面对面安装 face-to-face arrangement$ q! ]2 t) F, l4 H7 S+ S
面向产品生命周期设计 design for product`s life cycle, DPLC. Z7 g6 [4 k% r/ B( z# ]
名义应力、公称应力 nominal stress
, `0 s! e* l) l, {) \% B模块化设计 modular design, MD
( X0 r9 x& }! D模块式传动系统 modular system5 [1 @6 m4 r* R
模幅箱 morphology box
: t, b3 l( e0 ~8 e# f7 c; x模糊集 fuzzy set, q) R* g/ N% m* l4 y! c& f( R1 Q
模糊评价 fuzzy evaluation
8 [) w( {$ v }: i% M3 n% J模数 module1 [' x* s- b* m) Y; Y' ?
摩擦 friction: O& J6 L# ^' t b
摩擦角 friction angle
3 U# q. E, _& o' z% ?) v摩擦力 friction force+ h$ h1 A" e0 t0 ?; \
摩擦学设计 tribology design, TD
# l0 z& a' D: C& k- j1 p摩擦阻力 frictional resistance/ g! q7 I# X' U" H* ?4 ^) }
摩擦力矩 friction moment
$ Z9 s. ?) a% ?, c摩擦系数 coefficient of friction- Y1 x# M0 e5 m# x, \
摩擦圆 friction circle
% g! ^: U8 f2 s ^磨损 abrasion wear; scratching
9 k1 ?9 I0 W1 a5 T/ Q6 \$ a末端执行器 end-effector
9 f7 D4 J) e( U目标函数 objective function
3 a# Y% K+ s2 ]/ {耐腐蚀性 corrosion resistance
. y& t+ N# n1 @; F# H) h5 N U4 ?, [耐磨性 wear resistance , F# Z; H& w6 m( _1 e; r3 V
挠性机构 mechanism with flexible elements7 g% w$ i* ] a" {
挠性转子 flexible rotor
( A6 A; N$ {0 ~内齿轮 internal gear+ O% M9 b$ v( L/ t0 s# y" z2 @4 s
内齿圈 ring gear1 D, N4 U6 X5 V5 T. Q& l1 f2 i) J
内力 internal force
$ U% c1 A. L- ?2 m% W内圈 inner ring; Y0 r" z- e, Z: V: r0 ?0 g4 l
能量 energy
+ X" R$ R; m0 v5 B8 q" g7 S能量指示图 viscosity
% t8 K5 ?4 w( i+ r; p# r$ E+ \3 \逆时针 counterclockwise (or anticlockwise)
9 ^- }& P7 B# w9 _, v# g! U# b* J啮出 engaging-out, q2 Y% k r$ ^) s
啮合 engagement, mesh, gearing
& e- A" C1 e" f啮合点 contact points' V( d) D2 x% ]8 v0 I7 N
啮合角 working pressure angle' |9 y0 H' X1 @/ A; H& I
啮合线 line of action
8 L$ l6 ~3 L5 h( D1 u [啮合线长度 length of line of action
5 _" Q5 W" v2 _( `, O3 ?啮入 engaging-in
- I8 F. `$ Y5 n% t" z牛头刨床 shaper9 g$ t- h# T' P0 t
凝固点 freezing point; solidifying point& Z. J) V2 j) t# H; v; |
扭转应力 torsion stress
2 y, {7 \+ k; s# b3 y+ d% r; B扭矩 moment of torque! o/ A7 a6 Y# |
扭簧 helical torsion spring
, B; v0 \$ E% U$ @+ W- P诺模图 Nomogram- r6 f/ D: t$ ?* v3 P' H# x0 c
O 形密封圈密封 O ring seal
$ T; \) C: y0 c9 @! B/ |6 U盘形凸轮 disk cam . e# `5 N8 c9 L2 I6 n( ~( Z6 N$ z, W
盘形转子 disk-like rotor
9 y. U- ?" b/ E; l0 ~1 o5 c抛物线运动 parabolic motion) _' o4 T% \2 p" G- ~; n; ~
疲劳极限 fatigue limit
0 K8 {8 P0 \) V* {疲劳强度 fatigue strength( _$ Q- B0 K# @ H9 z- J: J( N
偏置式 offset
, ]* \: G- g: M+ [0 Q+ f偏 ( 心 ) 距 offset distance
: i4 g3 T3 h- `2 r2 k4 ^, g! }偏心率 eccentricity ratio
5 i! T4 y- P) c {( y9 w, X' N& j5 y偏心质量 eccentric mass- [- z* T1 l# R
偏距圆 offset circle
* U! o+ e! d: W# g/ U* S偏心盘 eccentric
, q* C2 l0 \6 F- x8 B" h p偏置滚子从动件 offset roller follower b5 {/ U0 ?1 w/ |, n
偏置尖底从动件 offset knife-edge follower; f5 f9 v+ _, P4 V/ _
偏置曲柄滑块机构 offset slider-crank mechanism9 N" a+ R1 l8 P4 m4 T( K6 R; J
拼接 matching
* |3 I, F t4 B+ Q; [评价与决策 evaluation and decision
" r/ _) v7 ]; N7 u# P- U频率 frequency
' h9 J' I# G0 D1 W平带 flat belt" a% O2 E* }; T* v& R! p# E5 ~! a
平带传动 flat belt driving
- x" @ Z- F7 W: G平底从动件 flat-face follower
8 R% f- x- D2 T* Q, t9 @平底宽度 face width0 D/ v; `% F4 W2 H; M/ m
平分线 bisector; d5 _/ s* d7 H. j
平均应力 average stress
. L- i2 s/ s- Z5 M2 R" j, K平均中径 mean screw diameter1 g9 d; u3 d7 e! B) v, J
平均速度 average velocity& @% ^" s: D- ~( g9 L1 C, Q# g
平衡 balance
: s" P4 B' ]5 Y+ M2 L$ I平衡机 balancing machine
; k2 H, E) r8 s# @/ C6 Z平衡品质 balancing quality
* U% X- S8 e+ O平衡平面 correcting plane
) d9 Y; n# w" `) d. _1 X平衡质量 balancing mass
5 `" r' L4 z2 u# i* K8 S平衡重 counterweight
7 ]% n4 _! @1 A* y5 r平衡转速 balancing speed, s& I! W1 {' Y7 U
平面副 planar pair, flat pair3 b6 M% B+ H7 l% n
平面机构 planar mechanism" l3 I9 [# a( _; f
平面运动副 planar kinematic pair5 p) Z5 K$ B" Q% p$ M" e; y
平面连杆机构 planar linkage4 |5 g8 u% S, i I5 s
平面凸轮 planar cam
# D1 p# y) T$ }8 t. y# O2 Y平面凸轮机构 planar cam mechanism
0 @+ N. B7 K* S+ V+ E5 S7 {6 J平面轴斜齿轮 parallel helical gears3 Q# c2 h8 d$ k2 O
普通平键 parallel key
% y1 Y- b8 t8 S6 G& i; m f其他常用机构 other mechanism in common use
! U4 i9 S% {, M. O2 H起动阶段 starting period
4 n9 B) t, x* }, Z; q启动力矩 starting torque
/ K" `. v; m% a3 P气动机构 pneumatic mechanism
+ o; p; L" \% J- K7 i奇异位置 singular position6 `0 l+ r1 I/ v1 O8 J# [
起始啮合点 initial contact , beginning of contact+ q- g. g% r$ n6 M" v
气体轴承 gas bearing
' j3 |' R1 @0 \0 X2 I( D K千斤顶 jack
7 s& @; l: A/ E5 b: p* s3 u3 O嵌入键 sunk key
2 m5 s c H$ V; W- D$ G) B, G强迫振动 forced vibration$ ]9 Y9 j" j! A5 X) K* J, J& a
切齿深度 depth of cut
0 Q, H1 q, M3 t9 f1 @曲柄 crank* ?* N8 d. t9 v: r8 m( ?% U- Y1 v
曲柄存在条件 Grashoff`s law
# s. m/ ]+ E9 @曲柄导杆机构 crank shaper (guide-bar) mechanism |
发表于 2008-2-21 11:39:46