键槽 keyway+ R! h. I, _' X
交变应力 repeated stress
! c; E9 U) T$ C, X$ `2 O交变载荷 repeated fluctuating load
+ a: L6 X/ B5 Y! b8 L. ?& `交叉带传动 cross-belt drive
! C5 M( j1 U z% v交错轴斜齿轮 crossed helical gears
" U6 B& u$ b; e( Q: F胶合 scoring
1 T2 K) H$ l: }; G7 \& B4 P角加速度 angular acceleration1 T! U" K! B2 ^) L
角速度 angular velocity6 i' M! g/ N4 b/ |1 G
角速比 angular velocity ratio
, g' X" N5 h% f9 F6 F角接触球轴承 angular contact ball bearing
0 S( S. b# |( X9 i8 n$ U* Y6 f角接触推力轴承 angular contact thrust bearing8 q1 [5 ^" S+ k; g
角接触向心轴承 angular contact radial bearing
9 z0 u, g6 s2 [* J! T. s1 i$ S角接触轴承 angular contact bearing& P( J |6 T+ W, E$ y4 d# G6 |
铰链、枢纽 hinge
3 _$ @% a7 i+ [) p0 U# Y2 r5 Z校正平面 correcting plane# Y5 N2 H) z$ o; C' \# c J
接触应力 contact stress/ I h p0 ^" p0 V" Z# U
接触式密封 contact seal
]+ |) s- c" [ b8 k9 t% ^ Z阶梯轴 multi-diameter shaft. H/ q# S2 J8 ?* r" T& X
结构 structure- }6 b- Y0 D0 }
结构设计 structural design
B, r" u- z3 r2 @# y- P! ~3 b截面 section
3 p$ B& S1 O; H& Y节点 pitch point
( Y0 `2 b2 x4 _2 q- O节距 circular pitch; pitch of teeth; H( l8 `) B* G( f. W
节线 pitch line
0 h. y' D8 A# Y+ C节圆 pitch circle* L+ _ C3 u( D; _# h
节圆齿厚 thickness on pitch circle* n5 l, Q- K6 i/ R5 d& C
节圆直径 pitch diameter% s+ O" L) l- `6 f4 F1 |6 r: O1 c
节圆锥 pitch cone
* I/ _' D2 J# I节圆锥角 pitch cone angle
% ?& K0 w9 k& ^解析设计 analytical design3 ]. H6 Q9 H' d8 X" k* y4 @2 a
紧边 tight-side1 p. {/ o# E0 x& z; J: ^. J
紧固件 fastener: p) s2 ~" g0 x' v/ u) ]/ f) f) }
径节 diametral pitch; Z9 M. F) l7 p& p: h& E! M8 F
径向 radial direction
4 G! A% e6 d+ R径向当量动载荷 dynamic equivalent radial load
" D4 |2 |% v1 V0 N, ` Y- x径向当量静载荷 static equivalent radial load2 f1 M% }! U( y
径向基本额定动载荷 basic dynamic radial load rating8 r K; Q% ]/ e: Z) f# e
径向基本额定静载荷 basic static radial load tating* U4 [& {& s6 N, A H
径向接触轴承 radial contact bearing
' Z: T$ Q0 i1 a径向平面 radial plane
3 q+ w( f* h$ C- e& ]% I7 P径向游隙 radial internal clearance4 I0 l! t+ d! \; f% e' y1 f8 Z. D% H
径向载荷 radial load& N+ c$ f0 }7 L( b5 e) V/ l
径向载荷系数 radial load factor& E7 O9 U, U" g! x( c. q
径向间隙 clearance1 {% L8 K. A) Y
静力 static force
. x+ M: D. k$ K) t* O9 C" I/ z/ e静平衡 static balance$ C( I$ g, a, n. Y! I$ ]
静载荷 static load2 j! c3 C( m1 s
静密封 static seal
3 }2 i# w1 |7 S( a局部自由度 passive degree of freedom3 ]4 u# `; G+ `; @& ?: ~+ @
矩阵 matrix' U: R7 y; t* W
矩形螺纹 square threaded form t" W4 E: w2 p' L% ^# x+ U
锯齿形螺纹 buttress thread form- Z. B. H+ z2 s! ]4 ^4 ^
矩形牙嵌式离合器 square-jaw positive-contact clutch
6 z! J; B* Q& `# i+ E x9 J; n5 ^绝对尺寸系数 absolute dimensional factor
8 d, }' ^9 p5 W7 @/ |. m绝对运动 absolute motion- g/ E. R B# W! m
绝对速度 absolute velocity8 V8 ^8 E' }* w8 }8 K7 t
均衡装置 load balancing mechanism
* |- o8 z, M1 L抗压强度 compression strength # s0 ]& U+ t) n+ j, a' P
开口传动 open-belt drive # E! C5 ^7 \; j0 p% q& [# a7 Q
开式链 open kinematic chain1 ?- T* H- M; H. I0 |' V: n
开链机构 open chain mechanism
* d/ |6 X. _! }' ]1 V( l! U可靠度 degree of reliability
( B% n6 G$ S0 U' O% L. l3 F可靠性 reliability4 J% k' l" M+ P3 Q
可靠性设计 reliability design, RD! x6 T3 a8 D s0 A6 \
空气弹簧 air spring8 r3 |: |. f0 a9 V# ]0 [$ `
空间机构 spatial mechanism
# r+ L% s+ b% J$ _5 E2 R空间连杆机构 spatial linkage
x! U9 q' z! l空间凸轮机构 spatial cam9 `) n7 `% n f. R" s4 i- j- U
空间运动副 spatial kinematic pair! \8 ]4 d" y" I' P8 s
空间运动链 spatial kinematic chain
3 |! m/ P4 \, W空转 idle& s: s" Z, z: w' }0 |) f% s
宽度系列 width series
. U4 P9 v2 B1 ^$ b框图 block diagram, e% ~ Q0 t8 }" r; f3 @/ K* m
雷诺方程 Reynolds‘s equation
|' o A$ B1 q- M8 d( q离心力 centrifugal force 8 ?# R+ N5 V0 d; t; \4 v f
离心应力 centrifugal stress
- [1 H0 a; A9 ~; f0 i离合器 clutch
. d# [& n. ^( q) U, Y# X8 D/ t离心密封 centrifugal seal5 L1 Z N$ _/ [3 Y$ i& A
理论廓线 pitch curve& c( F- ]5 x0 b3 D# J
理论啮合线 theoretical line of action
. v* g$ Y* `, ]隶属度 membership
) B- ~" ]1 |# z, | F力 force8 W7 Z% e' w) x# i4 n' e6 k
力多边形 force polygon9 v6 E% q9 C4 E5 v% a9 }
力封闭型凸轮机构 force-drive (or force-closed) cam mechanism/ Q( c& ^+ h3 V/ o7 R1 M: C
力矩 moment
" y% {; V$ T- L: ^2 M0 f力平衡 equilibrium
9 H# v; o5 ?& I7 l2 n- B0 |力偶 couple
, D( E3 @- S! g# r力偶矩 moment of couple8 y3 D3 j0 v7 ^2 U! L
连杆 connecting rod, coupler
' O8 P$ M2 ?" I2 ` @连杆机构 linkage
4 x, v2 L7 R9 k% q8 g% }' o# |连杆曲线 coupler-curve0 m6 Q* G3 @; I; q
连心线 line of centers
O- z* ~) J) o2 {! j, C1 k) v, m链 chain
0 Q3 Y5 {$ i% T4 O! o链传动装置 chain gearing) H+ K4 `! W! F6 B
链轮 sprocket sprocket-wheel sprocket gear chain wheel2 Q2 Q' h* o6 g& y& m
联组 V 带 tight-up V belt
6 k+ q) { f6 @联轴器 coupling shaft coupling. V7 g' r$ T; O3 L J4 r. T- c6 W
两维凸轮 two-dimensional cam
: @3 H0 e" W1 v% M$ F临界转速 critical speed! H# e- j% \0 @
六杆机构 six-bar linkage
5 @/ O l9 _, [1 K龙门刨床 double Haas planer
! a L) Y( }# Q. |- N轮坯 blank
6 @5 n( j7 Y3 b; `( s4 N+ j轮系 gear train
" p& ~# _- Q9 ?( \3 m8 R& i螺杆 screw
$ Y5 \* C! Y2 _) U2 B5 L3 B0 {螺距 thread pitch l" r8 P+ @6 T0 G
螺母 screw nut
7 O0 W9 J% r4 V; V) m螺旋锥齿轮 helical bevel gear( I+ Q$ C* G+ i
螺钉 screws
+ l% ~( p" z+ Z2 }) |0 I) v$ _螺栓 bolts, ^7 B: x% @( k2 @; V6 [
螺纹导程 lead G- [& B! D9 C8 O7 {% O O( ~
螺纹效率 screw efficiency+ G3 D! x" I' }0 E3 c" C
螺旋传动 power screw- v; x% @, H8 z* y8 V* Z
螺旋密封 spiral seal
9 B9 K0 ^. \) c4 P螺纹 thread (of a screw)8 u5 A9 k7 T" U/ L( [1 E' y
螺旋副 helical pair, W+ ?+ f1 ?( D
螺旋机构 screw mechanism7 y: j% |2 E6 m" Y
螺旋角 helix angle1 a( V- Z0 F+ G- a+ \
螺旋线 helix ,helical line m' m) b3 J7 R$ B# N# S( U+ }
绿色设计 green design design for environment& @6 v9 o9 ^5 Q. j4 O- j5 m6 i
马耳他机构 Geneva wheel Geneva gear 6 w* Z# K6 r- B
马耳他十字 Maltese cross
( q% b Z- l+ l% g7 _' C, z! Q脉动无级变速 pulsating stepless speed changes
( Q: M# J" ?; Z% U3 i4 g0 |: R脉动循环应力 fluctuating circulating stress( C; s. g) I- p- G) u& x& ?
脉动载荷 fluctuating load
: D/ X. E5 o( w% D% o- ?& s铆钉 rivet) a" @1 z. B1 R4 R0 j
迷宫密封 labyrinth seal; b+ G. g- b/ E3 n5 S p% T7 Y5 O
密封 seal8 v9 A, a9 g1 Y# M* ~% z# c
密封带 seal belt: u$ O3 J1 ~! R3 D
密封胶 seal gum9 i7 Z$ b U$ V4 X0 g6 C5 }2 c3 o
密封元件 potted component
: S' V- D) O" X1 l密封装置 sealing arrangement
& B9 ^8 v- |# Y* R面对面安装 face-to-face arrangement, X5 Q0 b7 R; q" b1 |
面向产品生命周期设计 design for product`s life cycle, DPLC
' H& F1 I/ U4 `4 d名义应力、公称应力 nominal stress
6 Y/ x! T. n6 T) G1 Q9 i2 k. I模块化设计 modular design, MD6 S3 N% z9 g; O: I" a2 F
模块式传动系统 modular system
6 l- ], G6 ]2 }" c模幅箱 morphology box
( x) @7 C7 |* o9 g0 b模糊集 fuzzy set
5 n5 h, `4 Z3 q3 _0 s4 {模糊评价 fuzzy evaluation
0 J+ w( |! o h/ U# c3 j模数 module. y6 f, f5 z2 s/ ^& @
摩擦 friction4 G% q( ^8 Y4 f; M
摩擦角 friction angle
, R( @9 q( ~" z/ a" [摩擦力 friction force
$ K" r, r, S8 t0 m4 y摩擦学设计 tribology design, TD6 h9 I' M6 ?# ~
摩擦阻力 frictional resistance$ J9 m4 B$ }: _6 P+ P7 `
摩擦力矩 friction moment
( L, r( ~9 g! H3 M/ z, C! ]摩擦系数 coefficient of friction+ |' F0 @1 |( P
摩擦圆 friction circle
# s/ V8 }; X9 I6 X2 } ]磨损 abrasion wear; scratching
# P0 ~: i2 e" V: V f末端执行器 end-effector
% K1 j3 J8 s3 P9 p% Y0 ~ l目标函数 objective function! m P" H0 s# n1 e
耐腐蚀性 corrosion resistance
1 x. x- `8 e% a' p耐磨性 wear resistance
6 Z1 R" k! {; k' t/ v4 L$ H挠性机构 mechanism with flexible elements0 x- Y4 u v' R( Q& l+ {. [$ U
挠性转子 flexible rotor
- W" D; ]. N( z& f4 O* i# o; z内齿轮 internal gear3 k1 C" x$ m+ }% f8 t+ d* G; Q
内齿圈 ring gear. V& `5 z# j, l8 T: V
内力 internal force
, U; K) M: P0 {, p+ n$ }0 S% |6 f内圈 inner ring! a# }8 {+ \ @1 y1 l2 }! J1 W
能量 energy) Y" s4 l! J5 p% O- T0 S/ ^
能量指示图 viscosity
$ ?5 ^9 A4 j" ?2 `( }) `逆时针 counterclockwise (or anticlockwise)$ c6 h$ f* S/ L, F1 B5 j$ \
啮出 engaging-out
% J# Q: q4 q S+ t& U啮合 engagement, mesh, gearing- W- f; J% ]- `
啮合点 contact points' X, {: z* M1 O& u4 U" Y
啮合角 working pressure angle/ I" L7 f6 m q' X& B* S
啮合线 line of action
8 e$ o: Z/ Z5 N) l. a. o啮合线长度 length of line of action
6 w3 x- G- {9 ?) C8 z7 n+ b啮入 engaging-in9 g% C$ E( R+ Q: Q+ M& L1 P/ q
牛头刨床 shaper- | U6 {# h! G% i# M2 B( F9 X2 r
凝固点 freezing point; solidifying point& Q: T9 ?$ W, g4 c3 t" E
扭转应力 torsion stress
A6 K* X s: c/ B扭矩 moment of torque8 j0 c3 a/ p6 G* ~. k+ i/ Q7 k
扭簧 helical torsion spring2 i( E1 s/ D# J# n* u( ~
诺模图 Nomogram
! g& d' r: V) K: EO 形密封圈密封 O ring seal+ I9 U' k4 n g5 X
盘形凸轮 disk cam ; E6 f% J/ N: l6 B" X- c" y1 y( N, \5 f
盘形转子 disk-like rotor $ G; N' h- e& O2 ?! V" U: g
抛物线运动 parabolic motion0 O/ X) ^5 W2 }- C
疲劳极限 fatigue limit+ d: b7 i$ N- ?: ?
疲劳强度 fatigue strength
: U( R1 G' b; \, O& k# o偏置式 offset+ J8 w1 ]$ W, D |- Q4 T
偏 ( 心 ) 距 offset distance' w$ ]$ R. e# a) M/ O3 J
偏心率 eccentricity ratio/ {; f. d6 j) a/ _1 L0 {
偏心质量 eccentric mass
2 _) G8 J( y2 o* D- X6 b9 \, B6 k偏距圆 offset circle8 j U) p3 C- u
偏心盘 eccentric
9 S. [$ x# W( z% c1 y- c3 e偏置滚子从动件 offset roller follower
+ u6 T+ o' [0 ]6 F @, O7 F偏置尖底从动件 offset knife-edge follower
1 w, T, U2 h& ?6 G偏置曲柄滑块机构 offset slider-crank mechanism
+ y$ m8 z+ L# W0 @( e# ~拼接 matching
+ `3 ] q' G; k6 l/ G评价与决策 evaluation and decision
& B" R. I- f0 ^7 S8 @5 U: M# z频率 frequency
- u" T7 j& h- I. M8 D- S7 E平带 flat belt
1 O0 V+ ^. q2 y5 Z; f A平带传动 flat belt driving
4 l. a5 f9 P' @. H7 o平底从动件 flat-face follower' K! ?9 S, V4 q) c; i+ b
平底宽度 face width2 o5 }8 ?. P- T7 u% u
平分线 bisector+ j% Q1 q f! _5 z
平均应力 average stress
5 l- O, j9 i. `* h1 r平均中径 mean screw diameter4 Y6 ]* ]. U$ g8 d. p; c4 `
平均速度 average velocity3 P7 Z; B4 C" s$ @9 }0 e/ B
平衡 balance
. Q- X% c' t$ E p4 y平衡机 balancing machine
3 M0 ^" i7 p G: i8 p; L) M平衡品质 balancing quality
$ _7 q: q( f% _7 g: ^平衡平面 correcting plane% G' Q' Y' S4 t$ f
平衡质量 balancing mass' f- Y6 G+ ]7 r% T4 a( O- _- [, q
平衡重 counterweight
; K5 K0 U! L# R8 u* Y1 U8 E平衡转速 balancing speed
" @2 F/ |0 r5 g平面副 planar pair, flat pair9 Y# ?8 u, R9 v( a3 _
平面机构 planar mechanism
7 E) H3 l6 w% e2 X平面运动副 planar kinematic pair( \! D! w; X H7 Y9 F- O
平面连杆机构 planar linkage# G+ D" O& y7 F8 O# s0 a
平面凸轮 planar cam6 u& J2 Z8 F# m- z* h
平面凸轮机构 planar cam mechanism- T3 C2 Y _* v1 _: y
平面轴斜齿轮 parallel helical gears/ o% l6 j; U5 ]1 H( t
普通平键 parallel key
/ ]5 C" U# |5 ?. I其他常用机构 other mechanism in common use
[. I: V4 S6 Z$ G8 h9 a起动阶段 starting period
v; W/ ^- d$ k Q启动力矩 starting torque* f0 {. J5 R8 o0 J7 ~- t! U" E
气动机构 pneumatic mechanism/ ]3 ?* _, C2 v' P! D
奇异位置 singular position
# L( K& h: S( S+ W起始啮合点 initial contact , beginning of contact/ B1 g+ X% X; Q& N
气体轴承 gas bearing# }8 }, K- x% \
千斤顶 jack. o( K( H3 P) R6 T# u7 Y; d5 @
嵌入键 sunk key8 b& E4 `& n* t/ r* n$ c0 l
强迫振动 forced vibration
5 }* d) V) q4 ]' f5 O7 ]% l6 V切齿深度 depth of cut
" D* Y/ d4 o6 Z, N9 _曲柄 crank+ @& \7 s7 F5 @: M2 u
曲柄存在条件 Grashoff`s law9 }8 W8 r; c8 H* k# G3 b- {, R
曲柄导杆机构 crank shaper (guide-bar) mechanism |
发表于 2008-2-21 11:39:46