CN1016525B - Conversion mechanism of rotation to rectilinear motion - Google Patents
Conversion mechanism of rotation to rectilinear motionInfo
- Publication number
- CN1016525B CN1016525B CN 86104622 CN86104622A CN1016525B CN 1016525 B CN1016525 B CN 1016525B CN 86104622 CN86104622 CN 86104622 CN 86104622 A CN86104622 A CN 86104622A CN 1016525 B CN1016525 B CN 1016525B
- Authority
- CN
- China
- Prior art keywords
- centering block
- straight
- teeth
- tooth
- chain
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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- Retarders (AREA)
Abstract
The present invention relates to a new mechanism for converting rotation into rectilinear motion which has the structure that a W mechanism which is provided with a swing block with teeth on the straight side surface of the swing block is combined with a straight rod with teeth, or a chain so that the mechanism not only has the characteristics of multi-teeth stress bearing and load bearing with good speed reducing capacity but also has high mechanical efficiency. The mechanism can input torque by means of an eccentric shaft and drives the swing block with teeth in the W mechanism, and the swing block drives the straight rod with teeth or the chain to make straight reciprocating motion by means of the engagement of conjugation teeth. The mechanism can be widely used in a pressing machine of an elevating machine.
Description
The invention belongs to a kind of mechanical transmission.
At present, no matter browse " mechanical design handbook " unite " mechanical design handbook " of writing Beijing 3 times printing in June nineteen eighty-three that group writes, still retrieve the international monopoly document, all can draw: not by any medium, by certain gear ratio, directly becoming continuous straight line motion by continuous rotation, and have the various mechanisms of very big stroke, is nothing but following several combination:
(1) screw rod and nut;
(2) screw rod and tooth bar;
(3) roller and screw rod;
(4) wheel and rack;
(5) wheel and flexible element.
They have his own strong points, and shortage is also respectively arranged.The characteristics of former three transmission are the continuous slippage or the rolling of helicoid, and the peripheral velocity direction of driving link is perpendicular to the straight line movement direction of driven member.Their total deceleration force amplifier and small and exquisite advantages of compact structure, but (1), (2) two combinations make their transmission efficiency very low because the helicoid sliding rate of load is big, and it is comparatively violent to wear and tear; (3) combination is except that above-mentioned total advantage, because the helicoid of load and roller roll mutually and add that accuracy of manufacturing is very high, thereby also have the high and meticulous advantage of moving of efficient concurrently, but thing followed fragile structure, technology capability difference and price are more expensive, then are its inevitable shortcomings; (4), the transport characteristics of (5) two kinds of combinations is that the peripheral velocity of driving wheel cylindrical (or pitch circle of driving wheel) is consistent with the translational velocity of driven member, so a tangible advantage is arranged: transmission efficiency is very high, and the life-span is longer.But the function of no deceleration force amplifier with regard to its combination itself.In the occasion of low-speed heave-load, they all need be equipped with the huge retarder of structure, thereby the volume of complete machine is increased, and cost also rises thereupon significantly.
From the mechanism of above various combinations as seen, compact structure whether or the manufacture cost size just be the implacable contradiction of seeming of a pair of obvious existence with transmission efficiency.
The present invention's purpose provides the scheme that a kind of W dentulous mechanism of straight sided by eccentric shaft, centering block and straight-bar dentulous or chain etc. are formed driving mechanism.This change is rotated to straight-line force transmission mechanism had not only had multiple tooth stressed (contact ratio is big), decelerability is good and the advantage of compact structure but also can have lower flank of tooth slip velocity and higher transmission efficiency.
The present invention is achieved in that
(1) mainly forms and the motion skeleton diagram.
Main composition is: eccentric shaft, centering block front are worn W mechanism and the straight-bar dentulous or the chain of tooth.
(2) various W mechanism in the present invention with the relation of " centering block ":
(Shanghai science tech publishing house publishes for BH Ke Telve person husband work, Chinese translation, the 1st printing April in 1962 in " planetary pinion transmission ".) in the literary composition the 5th page putting down in writing passage like this: " we discuss K-H-V transmission (Fig. 6) now.Between parallel axes, realize velocity ratio equal+mechanism's (abbreviating the W of mechanism later on as) of 1 is the inalienable part of this transmission.In W mechanism, do not adopt gear engagement ..." in the present invention W mechanism be inalienable part too, this is because it has the cause of unique motion: establish two-parallel axis and be respectively A, B.When arbitrary axle A among them and frame fixedly the time, under the drive of eccentric shaft, another root axle B will do translation, and any point track on it will be that some same eccentric arms with eccentric shaft are the circle of radius.The present invention as plate-like, and makes tooth abundant and that have same flank profil in its straight sided with this B axle, is named " centering block ".From last summary as can be known: the tooth on " centering block " based on " same track " this point, under band tooth straight-bar or the external force effect on the chain from conjugation with it, will produce almost same stress.Why the present invention that Here it is has the basic place of very big contact ratio.
According to the definition of " planetary pinion transmission " literary composition, the scope of the W mechanism of indication has been included following several mechanisms at least, and by above design, any among them all can produce " centering block " among the present invention:
(1) parallel-crank mechanism (accompanying drawing 4):
In the fourbar linkage " ABCD ", crank AD and crank CB are isometric, and connecting rod CD and frame AB are isometric, are called as parallel-crank mechanism.When as eccentric shaft and with isometric another crank EF of AD during with angular velocity+W rotation, the last any point of connecting rod DC will produce E and order the same the circle that track-radius equals EF, but itself with regard to connecting rod, it only does translation, the same with frame, its angular velocity of rotation is zero, thereby it is a kind of of W mechanism, if make tooth, promptly become and of the present inventionly " centering block " at the upper side of such connecting rod.
(2) output mechanism in few tooth poor (N type) planetary pinion transmission-comprise pin axle type and slide block type (see in " mechanical design handbook " the 674th page of volume second edition-" mechanical design handbook " unite write group write).
(3) Green's shaft coupling [cross rolling shaft coupling-" planetary pinion transmission " (BH Ke Telve person husband work.Chen Dejian etc. translate, and Shanghai science tech publishing house publishes.The first impression in April, 1962) the 5th page of note.]
As with making " straight sided has tooth " with part that planet wheel is connected mutually in (2), (3) mechanism, also just become " centering block " among the present invention.
(3) relation between eccentric shaft, centering block and toothed straight-bar or the chain (accompanying drawing 2, accompanying drawing 3);
Modern is that " circle " (being named this " circle " is pinwheel or roller with the tooth flank profil on straight-bar or the chain, corresponding straight-bar is a shank, corresponding chain is a roller chain), tooth flank profil on the centering block is that this situation of equidistant curve of cycloid is an example, make an explanation following (situation of the conjugation tooth of other type therewith roughly the same);
Fig. 2 represents the structural principle of an example of the present invention.
Centering block (11), (12), (13) that Fig. 3 a, 3b, 3c and 3d express in certain ifm diagram 2 reach the relation between (14), pinwheel (4) and each eccentric disc (6).Among Fig. 300
1, 00
2, 00
3And 00
4Be respectively and the eccentric arm of corresponding each eccentric disc of centering block, their size is e, and with horizontal angle promptly " phase place " φ be respectively 0,1/2 π, π and 3/4 π.Their phase difference △ φ=1/2 π.Fig. 3 also express adjacent centering block side teeth groove (EFG of Fig. 3 a "." the E of Fig. 3 d
1F
1G
1") center line is with respect to the horizontal position relation of center of circle O1, O2, O3 and O4 by each centering block hole:
Both overlap Fig. 3 a; Fig. 3 d, 3c and 3b are then respectively at a distance of c, 2c and 3c.Wherein c is " straight line potential difference ", its value:
C＝ 1/4 ×2πe＝ 1/2 πe
In addition:
(1) when the centering block number is m.Phase difference △ φ=(2 π)/(m); Straight line potential difference c=(2 π e)/(m).
(2) pinwheel pitch (or straight-bar tooth pitch)=centering block tooth pitch=T=2 π e.The distance of passing by in turn in the center of circle in this value and centering block hole matches.In this pitch, can settle n tooth (n=1,2,3,4) on demand again, the distance of adjacent teeth homonymy flank profil on the nodel line at this moment is called tooth apart from Tn, its value:
Tn＝ (T)/(n+1)
Suppose to make the eccentric arm among Fig. 3 do counterclockwise to rotate when the eccentric shaft of being made up of driving shaft (5) and eccentric disc (6) rotation among Fig. 2, in diagram moment, centering block (11) has been in the position finally of one-period, is about to break away from pinwheel; Centering block (14) just enters engagement; Centering block (13) and (12) all are in disengaging configuration.Change if eccentric shaft turns over 1/4th, just eccentric arm is by counterclockwise turning over 1/2 π, and then transposition will be distinguished in the center of circle in each centering block hole:
Phase of living in after the center of circle transposition in centering block hole
O
4→O
O
3→ 3/4 π
O
2→π
O
1→ 1/2 π
Consequently: centering block (14) finishes engagement, and centering block (13) enters engagement, and all the other then are in disengaged position.The rest may be inferred, moves in endless cycles.The operating angle of each centering block is 1/2 π-from 3/2 π to 2 π in the middle of this, and promotes toothed straight-bar or chain displacement distance 1/2 π e successively.After eccentric shaft rotated a turn over, it was 2 π e that the accumulative total of straight-bar or chain is moved distance.
From as can be known above-mentioned, desire to make the continuous motion of straight-bar or chain energy, the quantity of centering block must be more than two.
(4) at the shaped tooth of the straight sided of " centering block ".
The driven member that the present invention is directly carried is the straight-bar or the chain of band tooth.The tooth of centering block is conjugation with it, and promptly its tooth profile equation should be a condition with the characteristics of motion and the driven member flank profil of demand.With basic engagement theorem serves as according to deriving.As an example, list below and the centering block tooth profile equation of pinwheel conjugation following (accompanying drawing 5):
If the characteristics of motion of the straight-bar of demand or chain is S=e ω t.:
y（t）＝e（1-Cosωt）+aSin 1/2 ωt……（A）
In the formula:
S is the distance of moving of straight-bar or chain; T is a time parameter; E is the throw of eccentric of eccentric shaft; A is the pinwheel outer radius; ω is the angular velocity of rotation of eccentric shaft." xoy " shown in Figure 5 is a bit being initial point on the nodel line, and the rectangular coordinate system that is connected with centering block.
Equation (A) representative be the equidistant curve b of a cycloid a.It draws like this:
Make centering block with respect to the shank stop motion with the conversion of motion method, and translation opposite with centering block moving direction of the extra acquisition of shank.At this moment, the track of the some O process on the centering block plane that fixes with shank, when the round as a ball d that will be equivalent to radius among Fig. 5 and be e rolls on nodel line ox, the track of the O point process on motionless plane that fixes with it.(spacing is the curve b that a) is equation (A) representative to the equidistant curve of this track.According to same reason, when on the centering block pinwheel being set, the conjugate profiles on the straight-bar that moves also will be the equidistant curve that is formed cycloid n by round as a ball m.In addition, as flank profil,,, curve b can be replaced with approximate circular arc in the less demanding use occasion of kinematic accuracy for the actual demand on using and processing.
When eccentric distance e is big, also be feasible with straight-tooth-involute fully as conjugate profiles of the present invention, in a word, as long as meet characteristics of motion S=e ω t, the flank profil of mutual conjugation all can be used as the flank profil of wanting required for the present invention again.
Flank of tooth contact ratio of the present invention is very big at first as can be known from above-mentioned, and this is one of its characteristics.According to formula:
S=e ω t; When ω t=2 π, S=2 π e=T
As can be known when eccentric distance e hour, initiatively eccentric shaft is whenever goed around, the moving of the straight-bar of band tooth or chain, thereby the present invention has decelerability preferably apart from also less, this is two of its characteristics.When adopting four " centering block ", deriving according to theory draws: if the conjugate profiles among the present invention adopts " circle " to reach the equidistant curve of " cycloid ", their loss coefficient φ in transmission process are about 8.5%.And be that 2.5 °, friction factor are that 0.1 common spiral motion is in fact secondary for helix angle, its loss coefficient is then up to 70%.This shows that the present invention also has higher transmission efficiency and long life-span, this is three of its characteristics.
Based on these characteristics, under the suitable situation of transferring power, volume and weight of the present invention has only 1/3～1/2 of rack and pinion drive mechanism; The complete machine transmission efficiency then is 2.5～3 times of bolt and nut mechanism.It can be widely used in handling machinery and the press.
Accompanying drawing 1 is the schematic perspective view of an example of the present invention.
Accompanying drawing 2 is the structure principle chart of same instance.
Accompanying drawing 3 is kinematic relation figure of eccentric disc, centering block and shank.(4) be pinwheel; (6) be eccentric disc; (11), (12), (13) and (14) are centering blocks; O is the center of driving shaft; O
1, O
2, O
3And O
4It is the center of circle in centering block hole; E is the eccentric arm of eccentric disc; T is the pitch of shank or tooth.
Accompanying drawing 4 is schematic representation of parallelogram lindage.
Accompanying drawing 5 is cycloid figure.A and n are cycloids; D and m are round as a ball.Their radius is e; C is a pinwheel; B is the equidistant curve of cycloid a.[x(t), y(t)] be the coordinate of putting on this equidistant curve; Xoy is a bit being initial point on the nodel line and rectangular coordinate system that be connected with centering block.
Below in conjunction with accompanying drawing narration one embodiment of the present of invention, a small-sized hand-operated Hoisting Machinery shown in attached Fig. 1 and 2.Left sideboard (1) is fixed on the basis with right sideboard (10).Driving shaft (5) is supported on the left and right side plate by lining; Four eccentric discs (6) are connected by flat key and driving shaft with 90 ° of phase angles, space; Four copper sheathings (7) sliding sleeve is passed through on four eccentric discs (6) in four centering blocks (11), (12), (13) and (14), three restriction bearing pins (9) parallel with driving shaft interfix left and right side plate by screw, nut, are interspersed in above-mentioned four centering blocks three holes separately by three restriction covers (8) again simultaneously.Like this, W mechanism-pin axle type output mechanism of having formed this example by (1), (8), (9), (10) and (11), (12), (13) and (14).The right flank of four centering blocks is made cycloid (or near cycloid) tooth, and can be meshed with pinwheel (4), though its pitch of these teeth is all consistent, has between the tooth on the different centering blocks " straight line potential difference "; Pinwheel (4) by pin bearing in shank (3); Shank (3) is supported on the centering block right flank that is engaged with by above-mentioned cycloid tooth on the one hand, leans against again on the other hand on the disc of constraint roller (2); Constraint roller (2) is supported on again on the left and right side plate by bearing pin.
When active torque was imported into by driving shaft right side axle head, driving shaft just had been with eccentric disc to rotate, because the effect of pin axle type output mechanism, every centering block is all done translation, and all to make the throw of eccentric with eccentric disc be the circular motion of radius to each point on it.By the engaging-in of cycloid tooth on it and pinwheel with nibble out, each centering block constantly forces shank to rise in turn or descends, thereby makes shank finish the lifting mission of top (or drawing) end placed on it (or lying in its a lower end) goods.
Claims (3)
1, a kind of rotation becomes straight-line mechanism, it is characterized in that this mechanism worn the W mechanism of tooth and form with straight-bar dentulous or chain by eccentric shaft, centering block front.
2,, it is characterized in that being provided with in the W mechanism straight sided centering block dentulous more than two according to the described mechanism of claim 1.
3, according to claim 1,2 described mechanisms, it is characterized in that on centering block and straight-bar or the chain the mutual conjugation of tooth flank profil or near conjugation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86104622 CN1016525B (en) | 1986-06-27 | 1986-06-27 | Conversion mechanism of rotation to rectilinear motion |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86104622 CN1016525B (en) | 1986-06-27 | 1986-06-27 | Conversion mechanism of rotation to rectilinear motion |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN86104622A CN86104622A (en) | 1987-01-14 |
| CN1016525B true CN1016525B (en) | 1992-05-06 |
Family
ID=4802541
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 86104622 Expired CN1016525B (en) | 1986-06-27 | 1986-06-27 | Conversion mechanism of rotation to rectilinear motion |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1016525B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103764894A (en) * | 2011-06-30 | 2014-04-30 | 伊莱克斯家用产品股份有限公司 | Laundry washing machine |
-
1986
- 1986-06-27 CN CN 86104622 patent/CN1016525B/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103764894A (en) * | 2011-06-30 | 2014-04-30 | 伊莱克斯家用产品股份有限公司 | Laundry washing machine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN86104622A (en) | 1987-01-14 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| CI01 | Correction of invention patent gazette |
Correct: Shao Xiaomiao False: Zou Xiaomiao Number: 3 Page: 52 Volume: 3 |
|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| ERR | Gazette correction |
Free format text: CORRECT FROM: ZOU XIAOMIAO TO: SHAO XIAOSEN |
|
| C13 | Decision | ||
| GR02 | Examined patent application | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |