键槽 keyway, z8 `1 ~1 }# j* L2 }* E) }
交变应力 repeated stress K. V. E N9 a. m2 o
交变载荷 repeated fluctuating load/ N; |. J) L' a2 r* Q4 u
交叉带传动 cross-belt drive' j% }/ q# A6 g
交错轴斜齿轮 crossed helical gears# k; B$ K' B# d, n- q+ |# u! j
胶合 scoring) F1 B* v1 M* O4 S& J" Q
角加速度 angular acceleration- ]% T* V: x- r9 B3 V' N8 n( p' G
角速度 angular velocity/ S' N+ v) E5 D0 t
角速比 angular velocity ratio
. E& P) B/ t4 P7 n) f3 ^' Q角接触球轴承 angular contact ball bearing
; G( v" k: o' e5 z! b: n角接触推力轴承 angular contact thrust bearing4 T7 z; b( p$ U( N) [; G
角接触向心轴承 angular contact radial bearing
9 H) Q) q! f* q7 K+ ^角接触轴承 angular contact bearing
/ d, ]& W" A+ t& f9 r x铰链、枢纽 hinge' ~2 C2 Y, O# M1 U2 V
校正平面 correcting plane a C. q2 t( C; L- q
接触应力 contact stress7 k4 Y: ~. a4 {. U3 J' i. g
接触式密封 contact seal: q4 v/ Z/ [$ P
阶梯轴 multi-diameter shaft
1 T. |1 D& E8 v" r4 b }结构 structure" v; l# F! h- r1 t* U
结构设计 structural design- e2 h: L1 K6 l+ G) k4 H y( ]
截面 section
& I: I! z r& b3 o$ n- b9 g节点 pitch point
% d+ J! H8 V1 N节距 circular pitch; pitch of teeth/ d& I9 `) g8 Q! @. X
节线 pitch line& K# c! L* g Z. ]
节圆 pitch circle% I% [/ E' B5 `7 t* w
节圆齿厚 thickness on pitch circle
- K' J0 X" P# s R6 s1 F节圆直径 pitch diameter+ P7 L! m+ A$ U. J
节圆锥 pitch cone1 H2 ?6 H" T4 F/ `4 }
节圆锥角 pitch cone angle
& m) b' t4 E. H' m) ^, Q解析设计 analytical design2 i0 u' n7 n7 m& h2 k
紧边 tight-side
3 ]. {' K0 r0 f' t8 C紧固件 fastener
. L. I0 n+ P9 f' G7 g; V径节 diametral pitch* ~) ?. ]7 J! U, p
径向 radial direction+ M1 o8 ]$ v! N- P1 [9 n
径向当量动载荷 dynamic equivalent radial load* @! W7 q, S$ F& e0 O& E6 h$ S
径向当量静载荷 static equivalent radial load8 d F/ d$ x7 A
径向基本额定动载荷 basic dynamic radial load rating
' w/ c. W7 z |" e3 A( P径向基本额定静载荷 basic static radial load tating1 J3 d9 A# o+ f; I& i
径向接触轴承 radial contact bearing
, \( c! d/ B2 [2 j& J径向平面 radial plane* S5 Z4 M) g) N# e3 T7 l* n
径向游隙 radial internal clearance
5 |3 ~9 q" a& i Q径向载荷 radial load- L" J/ j0 J- e8 _2 o5 M
径向载荷系数 radial load factor9 l4 E" e; _/ P2 M
径向间隙 clearance
7 y& N- S& z8 h5 E: p" |: Q静力 static force
. i$ {1 h X! o0 r8 S4 }静平衡 static balance
* @! R. f* O7 m! s% X& G静载荷 static load
; @9 h9 ^0 @, n u7 `0 {8 N& @1 s静密封 static seal
9 T4 y# u4 `5 Q8 {1 _2 ^5 D局部自由度 passive degree of freedom" ^: j3 D* m3 \' H& \
矩阵 matrix
; x/ w! {- s1 @- b( P0 ]% J3 L矩形螺纹 square threaded form
2 j% N9 j6 c6 |- o! W锯齿形螺纹 buttress thread form9 X; p( t) T' W- s: _! j+ h. c; ~
矩形牙嵌式离合器 square-jaw positive-contact clutch
' O [( S- H7 B# W$ r绝对尺寸系数 absolute dimensional factor# e. ?+ G, X( I, X: C
绝对运动 absolute motion
) q$ r8 {5 g& w; b+ h绝对速度 absolute velocity3 x- ^, N/ _+ R q9 L8 T
均衡装置 load balancing mechanism
4 X+ g1 w3 o( @; {8 u4 I9 ]抗压强度 compression strength . M# T' f2 _% e* O' H
开口传动 open-belt drive 2 d# U- |! z! ?3 M! C0 ]: G# l
开式链 open kinematic chain8 k4 \$ @* Z# i( [) B9 Y
开链机构 open chain mechanism5 k% }8 ?8 u" q4 s3 a& ]
可靠度 degree of reliability
# j2 q- u' O: |% A7 o2 F( s可靠性 reliability% x6 B; `. E7 J
可靠性设计 reliability design, RD
7 y7 X" ~1 l$ J. u5 |" o: h0 `空气弹簧 air spring
7 c1 h$ y7 e n4 B/ B空间机构 spatial mechanism
5 [/ u. S+ v. l) V5 W8 Z# G9 ]+ n空间连杆机构 spatial linkage
" _: V( V" C2 B+ S空间凸轮机构 spatial cam5 L% r1 I4 g3 A% y
空间运动副 spatial kinematic pair6 @ e1 ` x: Z/ m) D! O% K2 k
空间运动链 spatial kinematic chain
3 P" [5 R& n- E$ N5 \, H空转 idle# M+ Y9 q, M& R
宽度系列 width series( R; K+ g" Y7 P0 F- w% ?4 y) G0 Q
框图 block diagram" w, t& M* W3 ^8 @
雷诺方程 Reynolds‘s equation
4 `$ a- F# {6 R) J) n, v离心力 centrifugal force * q, v ~7 ]! q0 N$ N9 |
离心应力 centrifugal stress
. }, H0 W9 k/ g5 c离合器 clutch
& O( j1 b: A& ]3 ]6 t- m+ J2 A3 g离心密封 centrifugal seal/ `. [, D( s' W/ [1 h7 z9 }6 m( `
理论廓线 pitch curve. x- Z1 a, |( ]( M3 l
理论啮合线 theoretical line of action
+ C/ d3 e! _/ W! E5 Z5 J隶属度 membership
" F' h% R$ M& W+ f( D力 force c1 M+ W( V( L' g9 B; D0 e
力多边形 force polygon
3 K3 L! J+ D8 F力封闭型凸轮机构 force-drive (or force-closed) cam mechanism
' r' m' S: ?0 b; B- }力矩 moment
& z0 ~" Y8 h$ }4 _力平衡 equilibrium& [7 U- u! n) _& ?
力偶 couple
4 b% c# M2 V7 }# y ]. Q力偶矩 moment of couple* t; h1 m. S) {& }
连杆 connecting rod, coupler' [! f# G; P, X" g2 S
连杆机构 linkage2 O0 a' @3 O2 i( r3 j( m" a* L
连杆曲线 coupler-curve; \1 ?" A' Z2 Z% I" {1 K# g/ V! U
连心线 line of centers
- I+ v6 D# W* h: W# ?' |链 chain
2 T2 s! }2 y$ `# O链传动装置 chain gearing2 p# _- e# s, D4 Z7 U+ T
链轮 sprocket sprocket-wheel sprocket gear chain wheel$ D& E4 \$ T( [4 t5 B
联组 V 带 tight-up V belt) W3 i! n( L/ U3 n+ N, x% `' v- C
联轴器 coupling shaft coupling
8 y0 q" `: ^$ W: J两维凸轮 two-dimensional cam
' j4 ?$ X; H1 ?& q+ ]8 C" u! @临界转速 critical speed
' S2 T! Z; @2 x i9 H六杆机构 six-bar linkage+ W: a7 I- Q/ c
龙门刨床 double Haas planer" `' i5 H* l! N) W
轮坯 blank4 Z2 s. u" n2 g* `9 C5 w( i; s
轮系 gear train" o" [- a* B+ j" P+ J1 K
螺杆 screw# ], R6 t+ @! ^" \0 g
螺距 thread pitch! O7 Q0 q& W8 A2 C: S3 o
螺母 screw nut" a8 \. K" T' z( x4 |% p4 a& S) Z
螺旋锥齿轮 helical bevel gear
& j$ ?) r0 @" c. ?4 {6 S螺钉 screws
; q' U" Z, h- K+ D螺栓 bolts L% u! ?2 M2 F! {! {: J
螺纹导程 lead5 S% f v3 V4 u% I. M7 q
螺纹效率 screw efficiency1 Y2 g- l- J5 \ i5 [4 B, w6 f
螺旋传动 power screw3 c, G. d3 b7 k. j
螺旋密封 spiral seal1 `0 \4 c m7 y" [) S5 Q
螺纹 thread (of a screw)' `( h2 a+ V" s4 K2 @; i4 h
螺旋副 helical pair# J: y7 z" x' K! z7 |3 D
螺旋机构 screw mechanism5 b) X7 x4 Z/ s, d
螺旋角 helix angle" ]7 F) d8 {; [; K
螺旋线 helix ,helical line* \) P# }3 c/ V b6 P
绿色设计 green design design for environment" K, b% S9 X+ e
马耳他机构 Geneva wheel Geneva gear
$ B5 @1 C; h+ |/ V马耳他十字 Maltese cross
0 e& _ {/ F% _8 F' I* a; H9 ]1 {脉动无级变速 pulsating stepless speed changes
% H0 T8 t# y" Y2 G脉动循环应力 fluctuating circulating stress+ I- t) U8 I3 o0 R
脉动载荷 fluctuating load0 @* X" t- f1 V) r
铆钉 rivet
# Q- U. D( I$ d# l. W8 j& ^迷宫密封 labyrinth seal
: P1 G- A/ u4 V密封 seal; ~* ~- u( _8 u8 C$ {. [, O
密封带 seal belt
, t! H, y( P, J# u1 ]! z, B/ l& p密封胶 seal gum
! G3 g8 [5 F) M1 _5 ]& R: @密封元件 potted component6 t1 S# @# g$ A1 i
密封装置 sealing arrangement: ^1 r: @0 Q# ?6 Y* a0 v! _
面对面安装 face-to-face arrangement! a$ _- T7 K2 ?: [4 @
面向产品生命周期设计 design for product`s life cycle, DPLC# f% Q6 n3 |2 x' R% e
名义应力、公称应力 nominal stress' ^9 c. a1 u+ r2 H; H
模块化设计 modular design, MD9 K5 U, n3 O) q) d2 X7 h8 P7 `
模块式传动系统 modular system
. x4 q+ Q2 G5 A6 k& I- y) Y& i) |模幅箱 morphology box
2 L2 j6 i7 s! |, _% R模糊集 fuzzy set; h# o% t5 H( Y' S0 M
模糊评价 fuzzy evaluation
, k! _( W, e$ O* ]; {) J# V: F; m模数 module
+ ]3 ^* }7 }. B摩擦 friction
$ p$ v+ K* q. k摩擦角 friction angle
4 s3 a- d# q d2 c& w z摩擦力 friction force
# a+ b& {; y. A8 P* H+ _ j摩擦学设计 tribology design, TD
]+ |. g' n7 {摩擦阻力 frictional resistance9 r6 O6 l& i$ a' g9 u( X) f/ F! s
摩擦力矩 friction moment5 q, m" [" H9 A* D5 k
摩擦系数 coefficient of friction
" Y7 e- f' e/ @7 p摩擦圆 friction circle
/ _1 B1 p8 v4 ]7 P X磨损 abrasion wear; scratching
* h$ w2 Y1 L+ S末端执行器 end-effector
6 i' ~. Y; Y( m5 \8 u" L目标函数 objective function
9 K) x( B6 D$ ] U耐腐蚀性 corrosion resistance
+ w1 X" v/ \3 K耐磨性 wear resistance
/ X* {( M6 w" h1 l9 P挠性机构 mechanism with flexible elements
, F' B0 F( \: }" ]" U挠性转子 flexible rotor( {1 j: i( N+ ^
内齿轮 internal gear
8 X0 Q' [! f0 Q1 _! o# u内齿圈 ring gear
% B5 I/ d1 ^; l' h$ _4 ~9 b. n内力 internal force
% f. |5 d# j7 A' J0 \( }! n内圈 inner ring
6 {$ p Q9 ~: J |能量 energy
7 ^# C! {* @: N" ?# l* e! F- S1 O能量指示图 viscosity
/ y7 y) N6 @9 D- v0 X# A逆时针 counterclockwise (or anticlockwise)
+ x% _! }, N8 M% y7 I啮出 engaging-out
6 a$ x8 |2 A# D2 w, i" `9 N! H5 \) o& l啮合 engagement, mesh, gearing
, X p7 u5 S3 K+ s啮合点 contact points3 w7 b7 q n! ]' L. u& c
啮合角 working pressure angle
7 F! B B) H2 ^. w- h, L# ]啮合线 line of action# a9 r8 F$ G3 H2 A! z' q/ r7 r
啮合线长度 length of line of action
7 r# v9 `7 k! `' U/ f8 o+ F3 w啮入 engaging-in' s1 @9 O' q6 {& P7 [1 D% T
牛头刨床 shaper
3 w# K% f X3 p. g凝固点 freezing point; solidifying point
; S1 |& C, a2 Y5 S扭转应力 torsion stress
- y$ t2 t: E: [+ ~' v扭矩 moment of torque
6 {( e1 Q8 p. i! u" |扭簧 helical torsion spring* q4 |. S8 i. r ]
诺模图 Nomogram v8 B8 o, m2 Y# y; {! L5 t7 X
O 形密封圈密封 O ring seal
6 f a/ u7 \. [5 w: ^* t盘形凸轮 disk cam
, e. l4 [" e/ E- J7 l盘形转子 disk-like rotor , E* s3 G7 Y7 P/ ~
抛物线运动 parabolic motion
{9 `8 X4 k+ ?' W8 h; Z疲劳极限 fatigue limit4 z1 e2 d5 u+ L% M' E/ t1 f
疲劳强度 fatigue strength
! Y9 F/ O- c! N) n9 |5 K( z偏置式 offset- x& b; ?0 }& J1 o, q+ N
偏 ( 心 ) 距 offset distance4 ^, }0 J7 f; k
偏心率 eccentricity ratio
4 i! c5 ~! s& n q偏心质量 eccentric mass6 ]! U% w6 u7 ~9 ~* S$ ]' B' o
偏距圆 offset circle
0 A% U6 u3 L2 \- k, X$ b7 x偏心盘 eccentric- N# v2 e% d) K, K" L
偏置滚子从动件 offset roller follower
8 l8 X/ W% c4 b8 R1 B" q8 ~偏置尖底从动件 offset knife-edge follower
. _4 f5 Z( @9 f+ N偏置曲柄滑块机构 offset slider-crank mechanism
0 ~) T: t" e( _* X' \" z9 r( V拼接 matching+ g3 R# o* o1 r
评价与决策 evaluation and decision3 E/ b$ S: G g! |( n
频率 frequency
: l; b2 n# M5 _/ U8 N8 G平带 flat belt0 B0 A# N" Z, ~8 S( g) }3 X
平带传动 flat belt driving
- U0 T+ E3 k P. K& e平底从动件 flat-face follower& x9 `7 {- x! k0 J* m- w
平底宽度 face width: E/ L7 _. v- Y% e3 d3 L
平分线 bisector" v9 o5 l& \2 L @: V) @) f
平均应力 average stress" y5 k7 B. [% P4 x
平均中径 mean screw diameter
5 g5 f, e2 X/ A8 t平均速度 average velocity {+ N' o k! x
平衡 balance
3 v! n0 M/ A" \! k: }平衡机 balancing machine
. r" A7 R: Z& p' _5 S- h平衡品质 balancing quality
7 s: ~9 J" t C8 S/ K' r6 Q$ m平衡平面 correcting plane
2 r/ M' W. G+ k5 a* _3 T平衡质量 balancing mass9 @% h" m: H7 A U
平衡重 counterweight
- e# h- U3 _: y- g平衡转速 balancing speed# r2 Z) |* B; Z8 G" H
平面副 planar pair, flat pair
. O8 R' p; ?) R: b: f0 C) y) }$ a+ f平面机构 planar mechanism
, v! M: E& S0 |; f" r. V平面运动副 planar kinematic pair" s/ B; N1 r% c$ ]
平面连杆机构 planar linkage; B+ c: C) y4 A9 V8 F) ]7 B
平面凸轮 planar cam6 ~* D# G% q& E% h2 D6 ?0 Z
平面凸轮机构 planar cam mechanism
% Z9 S# Q [3 I& t9 O2 D6 X平面轴斜齿轮 parallel helical gears" x/ U, ]: n( [. q% B8 L
普通平键 parallel key- [3 l. z8 e; _ P' h# Q
其他常用机构 other mechanism in common use 9 @2 T8 j I. M& h
起动阶段 starting period + _* r' M3 R2 M/ w; A7 t9 @+ {
启动力矩 starting torque
% r8 |8 `7 K+ C' ~- K; M) v7 L+ b气动机构 pneumatic mechanism
1 w" k% A/ I( C% H奇异位置 singular position
, l1 h& V" b1 ]; d( A起始啮合点 initial contact , beginning of contact- z+ v U3 s% e6 r% }& Y% w
气体轴承 gas bearing" L9 n5 K: F6 A: X. h
千斤顶 jack& n" J5 x; L" {
嵌入键 sunk key
- B3 X' ^8 R4 t% ~强迫振动 forced vibration
0 n0 l. `% l( }; j7 N/ ]8 e8 Y9 N切齿深度 depth of cut
) Z* A7 K' z, C! f' p' d) W曲柄 crank
# \7 z2 e1 z0 S1 s! ~曲柄存在条件 Grashoff`s law
$ M; u0 p* I8 h# c+ q+ B* s曲柄导杆机构 crank shaper (guide-bar) mechanism |
发表于 2008-2-21 11:39:46