键槽 keyway. _- V8 V i2 Q8 _5 c# F3 W9 I0 Z
交变应力 repeated stress
* C; K8 w# T( O8 B& V交变载荷 repeated fluctuating load+ T( h# W. @2 i" ]2 T' U& e
交叉带传动 cross-belt drive1 x D% e% t* q; t3 M
交错轴斜齿轮 crossed helical gears. g/ c, X2 F1 ]. i* h1 Z
胶合 scoring
" |+ k T. g# l) M! [- r, H角加速度 angular acceleration
9 T7 I! P8 z& r% [% A角速度 angular velocity! A- I! x3 y1 N6 \( O1 b3 x
角速比 angular velocity ratio0 E- b7 Q4 O) M% U, D, G
角接触球轴承 angular contact ball bearing
& A: S, S. Y( {# y角接触推力轴承 angular contact thrust bearing
% V- N; r% M4 }/ m7 a角接触向心轴承 angular contact radial bearing
v* {, O( s4 z7 ^$ z; [角接触轴承 angular contact bearing+ W0 X- Q+ {# N$ C2 c. G7 t# U
铰链、枢纽 hinge
0 z b Y8 v" T校正平面 correcting plane
2 L: [5 b0 E1 B) |$ e' S8 h5 y接触应力 contact stress( H, ]: ]' P" Z* C
接触式密封 contact seal. i) I7 d8 I7 w1 G% P k% s
阶梯轴 multi-diameter shaft! h+ \4 y( Z+ ~! ~% [; `
结构 structure
9 |9 V) R8 v1 M' N) a+ V8 E结构设计 structural design
8 {5 k8 ^9 E0 l. z* O3 V截面 section
) T) ?; Y3 E% T节点 pitch point! K- i7 L& E9 @. |3 s
节距 circular pitch; pitch of teeth
* P4 [0 V) ]+ w节线 pitch line
* P. _2 V. B# }9 u& r节圆 pitch circle. k9 w/ j6 J3 b. U5 ~) H
节圆齿厚 thickness on pitch circle- s/ C( y4 @' E% j2 Y) K
节圆直径 pitch diameter# D c6 Y+ h% E6 ?
节圆锥 pitch cone
8 R+ v: L& S& l% L2 t! d- c* r节圆锥角 pitch cone angle
5 {; ^+ t& M2 z: i& l$ `0 S解析设计 analytical design6 d2 @1 k+ s* X& H9 f2 B
紧边 tight-side
8 f+ H" ]1 ?$ E% S紧固件 fastener5 h7 `9 v( [- Z& r& p) X4 [
径节 diametral pitch( Q6 {" W+ z a" V! M
径向 radial direction4 t1 ?% c) U! n% T
径向当量动载荷 dynamic equivalent radial load0 B* C, ?: p5 p+ ?$ Y
径向当量静载荷 static equivalent radial load+ f" T6 M) g7 m% {0 G
径向基本额定动载荷 basic dynamic radial load rating) k, j$ Q$ H) i1 B
径向基本额定静载荷 basic static radial load tating
0 Z/ M% B: L! l7 n' p& e% ]径向接触轴承 radial contact bearing; _8 y4 f1 l# J. M7 ?2 ~4 A
径向平面 radial plane! z1 H' k) h' P* e( x7 Z
径向游隙 radial internal clearance
1 G; D6 v9 Y$ |) r径向载荷 radial load
! b6 c! b3 c2 O0 x7 Y径向载荷系数 radial load factor5 n. l z( a) A2 E( q' K7 W
径向间隙 clearance
, |2 l4 x; @6 I ]0 h' U静力 static force& B* G# S2 D- t
静平衡 static balance
0 Q9 M0 X& v" J5 f静载荷 static load
+ N; a$ G( q1 c静密封 static seal
" ]% C! u$ G, m: [# t' p局部自由度 passive degree of freedom& q9 o$ m- J3 V9 N. |/ A# |" n; Z
矩阵 matrix" u; R" b W$ n5 D& P
矩形螺纹 square threaded form
5 v1 _. G# W$ C6 w4 |* i锯齿形螺纹 buttress thread form
/ H6 K; t. }0 c5 l矩形牙嵌式离合器 square-jaw positive-contact clutch
2 O3 H3 R8 R- f0 `' G绝对尺寸系数 absolute dimensional factor1 F# A. m; r% d. C( c) y$ R6 Y
绝对运动 absolute motion8 V: {% ?( D' W0 t
绝对速度 absolute velocity( h/ N* n( f; _- ?: I, T
均衡装置 load balancing mechanism
- v: d c4 ]5 s3 H. N抗压强度 compression strength
8 m8 w$ X% k4 u9 V% ^6 l( d, @0 F开口传动 open-belt drive , T& n0 U' O5 Q
开式链 open kinematic chain2 K& g) t( y5 }; _4 D
开链机构 open chain mechanism
$ l! E9 ]& w1 g3 f可靠度 degree of reliability( u K* x, @( u
可靠性 reliability
8 C/ \ T/ X0 i/ S, I# ? x. j r# v可靠性设计 reliability design, RD# f3 u' T" s0 c
空气弹簧 air spring
; ~* c7 P+ ^, p6 A, v) ?8 n# w空间机构 spatial mechanism, ]$ O/ a- J* I/ @4 n
空间连杆机构 spatial linkage4 H2 ]1 Q6 n* K! Q8 ]; A6 _2 O2 `
空间凸轮机构 spatial cam
; Z5 ]" D, A5 P/ k空间运动副 spatial kinematic pair
( T8 Y. S( s6 R. x5 U空间运动链 spatial kinematic chain
1 u% }0 y: A% o. w2 w2 f9 l空转 idle
8 W, k- C w( V& K宽度系列 width series2 s9 t. b7 O/ B; E& |
框图 block diagram; T/ a% U: }7 D: _
雷诺方程 Reynolds‘s equation / E$ ]% E1 a' X2 Q
离心力 centrifugal force & f/ G! V' n) {, N8 ~4 r
离心应力 centrifugal stress
. L" b4 P: A! q/ M. s4 z离合器 clutch6 k, M+ V6 z' [% T# \
离心密封 centrifugal seal
& `8 K& n; N) J( A% K# d$ y, Q理论廓线 pitch curve
3 O8 Q/ Q! x, o理论啮合线 theoretical line of action
5 Z5 i' j" p# q, L' I u/ S% L/ G/ B隶属度 membership
" N% B6 N' a# X6 g& m0 M) U7 }1 X力 force
+ O! N0 V8 Q& Z; G0 M力多边形 force polygon( e; U6 Z& d5 H# H& z1 P6 Y
力封闭型凸轮机构 force-drive (or force-closed) cam mechanism
3 }' W: M2 k6 D力矩 moment
; R% f& W8 W7 e7 ~; q$ v: J力平衡 equilibrium. }/ _% D4 h9 w" j. d
力偶 couple
" v0 I8 _! C; ]. m. b% w力偶矩 moment of couple
; \ F" f! c$ H5 f: K6 S连杆 connecting rod, coupler
! D/ h8 ]! w* J; L2 R连杆机构 linkage
5 [9 ^5 Q* x5 `, z7 |$ n: Y连杆曲线 coupler-curve) N9 m ?; `9 s$ f9 r% H+ w, K
连心线 line of centers
; D% {- W: C, v* B6 W5 `链 chain
* V1 ]& c6 J( t+ p3 Q d链传动装置 chain gearing
3 a7 T! Z* |6 c& @1 t$ ]) y1 ^链轮 sprocket sprocket-wheel sprocket gear chain wheel
+ P. j$ z. d+ w9 {! M联组 V 带 tight-up V belt
& M- d8 Z- J, t4 d联轴器 coupling shaft coupling
1 g9 c. z/ O8 F. l/ M: ]" w两维凸轮 two-dimensional cam- t3 E/ Z4 `: z
临界转速 critical speed
$ F6 o9 C1 G7 {/ [5 a0 B% e I六杆机构 six-bar linkage/ v( l& k( s5 S
龙门刨床 double Haas planer U& B" f: H( I' w2 b' ]+ |
轮坯 blank7 M$ W8 @9 q) |2 R+ I& C( F: s
轮系 gear train3 D1 l3 B4 Z# g ?# Z5 p* _
螺杆 screw7 B6 m* P3 ^; e/ x+ H/ b
螺距 thread pitch
% H; O% j1 y7 ^2 Y: R2 j螺母 screw nut
- c3 T. l" y5 E1 A I螺旋锥齿轮 helical bevel gear
% |2 C- W: Y0 X螺钉 screws
! R ], G5 v& G+ s1 e! T螺栓 bolts
: d4 J( D; U& L' ], o' |9 g螺纹导程 lead9 U Z- L) Y* Q4 f/ h
螺纹效率 screw efficiency7 U( X8 d* I7 _- @1 r
螺旋传动 power screw+ |) n# W" q+ O+ D5 M$ e8 @
螺旋密封 spiral seal4 C/ ]( A0 H# T4 G# u9 ?# k+ ]
螺纹 thread (of a screw)9 J/ H7 u, i% e- B F$ N
螺旋副 helical pair
2 z+ M( `: T" M2 e5 h) S螺旋机构 screw mechanism$ X! [) ?. l% \& l$ a W# Z
螺旋角 helix angle
2 }- L' p3 ?, p螺旋线 helix ,helical line# [2 S: M5 B2 ^% o M
绿色设计 green design design for environment7 ~) h" T2 I3 i$ s
马耳他机构 Geneva wheel Geneva gear # O1 ^/ B% [, q' q* T
马耳他十字 Maltese cross 3 Q- B! q) @# T9 c
脉动无级变速 pulsating stepless speed changes
* ]2 U: f' ]/ s7 @/ U: z脉动循环应力 fluctuating circulating stress
: X$ C+ e! \" F3 x% ~' W5 c3 o脉动载荷 fluctuating load
7 x! l7 P) \5 O# O7 P: f铆钉 rivet( H- c4 N8 m; A! S% k! Y9 m( j# ^
迷宫密封 labyrinth seal
4 ?8 ^7 Y0 b9 R) C' |) ?( O$ p2 o密封 seal
9 K5 K5 o' I. J9 T* m! q; c密封带 seal belt. N, H7 H. l' u5 [+ h$ ]
密封胶 seal gum
6 s' ?% u5 i4 H; ]$ G密封元件 potted component; ]6 W5 c# Y5 k0 A7 ]5 T1 P N
密封装置 sealing arrangement! C" S8 ^, R* @/ Y+ H) j# x* G0 p% s
面对面安装 face-to-face arrangement w1 P+ `" B) B
面向产品生命周期设计 design for product`s life cycle, DPLC
0 }, a4 B* d% }名义应力、公称应力 nominal stress2 L/ V; z3 \! B8 a( o
模块化设计 modular design, MD
8 m! y, y9 |+ ~. q- r9 Y* l4 N模块式传动系统 modular system& D) [! m4 E* ~* K
模幅箱 morphology box7 b5 S" q. R) {: K
模糊集 fuzzy set2 v( y$ @* U$ Q
模糊评价 fuzzy evaluation' ^; \5 ^* H9 s) k: a- o
模数 module# ]2 N6 ^# Y1 O& K C1 F# I2 L
摩擦 friction
9 m2 s1 q1 s9 x" C9 v* l+ b摩擦角 friction angle
0 k2 X6 @ l3 g! _% q摩擦力 friction force
~) b7 L! H- b8 t6 G Q摩擦学设计 tribology design, TD
0 f* X0 I! n9 C7 b: i摩擦阻力 frictional resistance6 I8 _+ O$ `9 w- a* I
摩擦力矩 friction moment) ?' o$ }) U$ \& r5 g: M0 [. Y
摩擦系数 coefficient of friction; D; h3 i; q: ~" i8 c2 j( b7 X0 I- b
摩擦圆 friction circle
9 B! D% [0 `8 f0 c* K磨损 abrasion wear; scratching
$ i0 l) A% l: d, c4 T末端执行器 end-effector
3 \; r& I! ?( X1 Y目标函数 objective function
% A% [; V1 V% |0 o! u4 y& |3 J* W耐腐蚀性 corrosion resistance
( R; P3 k; g. W0 [* Z5 ]8 \耐磨性 wear resistance 1 H0 M9 Z* |4 E
挠性机构 mechanism with flexible elements
q& T5 _! y6 F3 z挠性转子 flexible rotor
1 p9 @. I; v1 Y7 v* N) {内齿轮 internal gear
: C; K3 {; L/ N. \+ T内齿圈 ring gear
- Z# W, N& _8 b" ]6 d5 Q8 G内力 internal force
; ^3 {$ V/ m y" h6 m) z0 T内圈 inner ring) f2 P2 r) G* ?2 D! } e; _# R
能量 energy
4 Y/ Y3 D/ A- F5 }) _) `3 u能量指示图 viscosity
- b# M, S, | Z6 Y5 S; x! i# `/ r逆时针 counterclockwise (or anticlockwise)
4 X0 _, }- D) O$ _' D啮出 engaging-out0 [" t* c7 v; y. q; r; m
啮合 engagement, mesh, gearing
6 \8 z* C3 R/ U! c1 H( z% o啮合点 contact points0 }8 {# Q9 r m* f
啮合角 working pressure angle M# Q4 ?! p, C& Q3 Z3 f; [
啮合线 line of action
/ {8 @5 ]7 ^( n1 J* K1 w啮合线长度 length of line of action2 n& p; |, ^# {* v9 g4 |2 q
啮入 engaging-in
- n$ t3 K' y0 R+ m$ q9 t/ z+ [5 P4 V牛头刨床 shaper
5 N6 M( i0 p2 T: o凝固点 freezing point; solidifying point9 N! k$ s* d' N
扭转应力 torsion stress
0 q7 x5 N- R; B4 D+ ^+ d扭矩 moment of torque; h V" g" @3 Z1 B
扭簧 helical torsion spring- U" f. q" H( ?3 _* B( a
诺模图 Nomogram
9 F1 {, c+ _- i }" |O 形密封圈密封 O ring seal
! H8 E% U% U& o2 O* T盘形凸轮 disk cam / F! I7 C# ^4 H9 h m
盘形转子 disk-like rotor
% B5 _! Z3 @" \; L) F% u0 s' S; ?抛物线运动 parabolic motion
! p( p7 [3 ?2 {2 O. ~/ a0 S疲劳极限 fatigue limit
, H: R* C5 y# j, L疲劳强度 fatigue strength2 E1 P+ p/ |" \% f/ t1 P4 ~ |
偏置式 offset
/ C7 ^( K' V# v* W偏 ( 心 ) 距 offset distance
4 J2 e0 m( u9 T, q; i, w% }) ~偏心率 eccentricity ratio
" S0 h( h$ O7 _. @" x/ }8 U4 [' v偏心质量 eccentric mass1 P l1 ^8 v8 C. Q2 T& M
偏距圆 offset circle' E$ o, _- ?) r, g6 ^
偏心盘 eccentric
6 x+ Z6 ]: S$ \) I& r2 K/ |偏置滚子从动件 offset roller follower
* F, t1 P3 D' c* q$ a8 W偏置尖底从动件 offset knife-edge follower
4 j2 V5 e8 E# x+ u5 J" Z& V& e偏置曲柄滑块机构 offset slider-crank mechanism
]' q. a# h% t Z拼接 matching0 P% l$ {3 R6 p$ c7 u
评价与决策 evaluation and decision
9 W- k8 N/ r& T& Z频率 frequency
5 k9 P4 J1 D5 R. D' @平带 flat belt
% ?' Q4 i. q% Z+ M1 P平带传动 flat belt driving8 @# m; B7 `; V6 e7 f) r K
平底从动件 flat-face follower
" g* w) V0 H7 y1 T9 c平底宽度 face width
- A3 ?/ k9 R" Q5 b平分线 bisector
2 g6 x$ b0 ~8 f' |+ Q- J平均应力 average stress
0 |! x- X1 f' b2 Z4 d8 b平均中径 mean screw diameter8 a$ _( x# y4 J7 I
平均速度 average velocity a `% A! w; ^* ]- v: R
平衡 balance$ C8 O$ D1 h5 s: |/ w
平衡机 balancing machine
6 w/ _5 Y8 G; g9 X0 [, J平衡品质 balancing quality
4 [, z% d4 z( \! t) i' B# N平衡平面 correcting plane
/ t P) s3 }% u4 }# D) A2 E平衡质量 balancing mass3 D, A8 y3 p3 o: ]! j
平衡重 counterweight
) k/ n5 L, `7 v& [! r, {( ~. u平衡转速 balancing speed
. b. U4 L4 i) W+ N* ?& L1 |平面副 planar pair, flat pair
) `- O0 V. e- g8 x0 e& n平面机构 planar mechanism G" ^- ^% M! W: S F1 D
平面运动副 planar kinematic pair
% Y* S5 I/ Y, d4 h4 |' @6 l# x平面连杆机构 planar linkage0 b6 B1 q- x" a8 e
平面凸轮 planar cam
' p. a& S0 Q: r' p平面凸轮机构 planar cam mechanism
0 t! Y. o9 k; Y平面轴斜齿轮 parallel helical gears
0 T. D5 q$ `2 y& v普通平键 parallel key6 G$ A% D- c5 H6 }: U9 F: j" z
其他常用机构 other mechanism in common use ) ^5 H; W. @# F* H! f4 w
起动阶段 starting period / d7 I: n3 \1 O# K) }. y9 y
启动力矩 starting torque
; ?/ Q/ z" L8 c- e! ?气动机构 pneumatic mechanism) R$ u5 i* a7 K( E6 j/ @
奇异位置 singular position
0 S8 p3 I' D8 ^0 }起始啮合点 initial contact , beginning of contact
+ E! q, K7 v& g6 y- g气体轴承 gas bearing6 Z5 ?4 J3 e' v4 l/ r5 b6 L0 X2 n5 {
千斤顶 jack/ Y! g, z- S h8 X% S8 o+ ~5 F
嵌入键 sunk key
% p3 g9 ~7 {4 I- @: Y* C8 l9 z! b强迫振动 forced vibration' o5 v& A1 Y3 k4 Q4 f, r
切齿深度 depth of cut
! q$ ~! [; m) x) k" X曲柄 crank
2 U3 l3 o- e9 A( `; R% E% i曲柄存在条件 Grashoff`s law8 h. f) }) L$ p# R) P/ T
曲柄导杆机构 crank shaper (guide-bar) mechanism |
发表于 2008-2-21 11:39:46