CN101016945B - Wide tooth form relay transmission gear - Google Patents

Abstract

The invention relates to a method for producing wide-tooth gear used in power gear, which can be divided into wide tooth layer gear, wide tooth combine planet gear and wide tooth incline gear via different gear methods. The inventive tooth width is 1.2 times than present gear, while the torque of single tooth is 1.5 times of present one, with low cost and long service life, while the invention can save more than 40% material.

Description

Wide tooth form relay transmission gear

Technical field

The power speed changing driving gear of various machinery inside.

Background technique

Existing domestic and international gear industry design, the form of gear tooth of making, its profile line mainly contains involute, circular arc and Novikov gears with double circular arc tooth profiles.In recent years overlikon spiral bevel gear and the hypoid gear introduced from the America and Europe of China, the harmonic gear that also has the former Soviet Union once to design.Check the gear part of recent import and homemade high-grade automobile,, all belonged to the gear of above-mentioned profile line profile of tooth from the invention and the utility model patent bulletin of interconnected internet retrieval China F16H class since 1985.

The gear of above-mentioned all kinds of profiles of tooth all has following deficiency:

(1) profile of tooth is narrower, and the moment strength that gear can be born is difficult to significantly improve again.

(2) precise design of toothed wheel profile and manufacturing process are all complicated.

(3) during the between cog transmission, the wearing and tearing of the flank of tooth are unavoidable, especially near the wearing and tearing of tooth root portion more so.

Since gear came out hundreds of years, a large amount of research experiments was once done to the design and the accurate processing aspect of tooth-formation of gear profile line by scientific and technological circle both at home and abroad, though transmission properties is improved constantly, and be tending towards ideal limit, all do not obtain important breakthrough again.

Summary of the invention

At the deficiency that prior art exists, overlapped gear with wide teeth of the present invention, wide tooth shaped combined planetary gear and wide-tooth bevel gear have following feature and practical effect:

(1) satisfying automatically under the prerequisite of continuously steady transmission, the profile of tooth width of wide tooth-profile of gear is existing more than 1.2 times of various gears.The stress point of contact is all between two basic circles, so just can estimate from the correlation formula of the mechanics of materials: the moment strength that the gear teeth of wide tooth-profile of gear can bear is existing more than 1.5 times of gear.Make gear help miniaturization and slimming, this is especially to the high-power power transmission gear of big moment of extensive use at present, even more important to powerdriven gear, sees specification and accompanying drawing 1～10 for details.

(2) the toothed wheel profile of wide tooth-profile of gear is spliced by radius, broken line and circular arc line segment.The corner point joint is running-in wearing and tearing camber automatically, and also cutting and grinding becomes smooth camber line shape in advance.It is concavo-convex not remarkable that it has design convenience, the simple tooth ends of profile and tooth root portion, low to the required precision of toothed wheel profile, adopts forging and pressing-trimming-surface-treated continuous processing flow process manufacturing just easier.

(3) the between cog transmission surface of contact of wide tooth-profile of gear is all approaching vertical with the stress direction major part, and tangential speed and the stroke that slides of the node on the surface of contact is all very little, and the wearing and tearing between the flank of tooth are little.And the profile of tooth width is existing more than 1.2 times (as situation lower toothed width be existing 2～4 times), so it is also unimportant suitable wearing and tearing to occur, so just can prolong the working life of gear greatly.

(4) gear is the inside driving parts of modern and following most of machinery, and especially powerdriven gearbox mainly is made up of gear.Because the low production cost of wide tooth-profile of gear helps miniaturization and slimming, in light weight, wear-resistant, the life-span is long, can save material more than 40% again, so application is wide, and the macroeconomic Considerable effect.

(5) must carry out the characteristics of endless relay engagement driving in order to satisfy wide tooth-profile of gear, the author has invented respectively along the overlapped gear with wide teeth of stationary axle engagement driving, sees Fig. 1.All, see Fig. 7 by the wide tooth shaped combined planetary gear of the wide tooth-profile of gear combination of monolithic.Wide-tooth bevel gear is seen Fig. 8.That the following world has almost been monopolized in these 3 inventions is big～in～all original innovation technical fields of little～miniature gears industry.Below, the drive characteristics by wide tooth-profile of gear begins explanation earlier.

Description of drawings

Fig. 1 is overlapped gear with wide teeth profile of tooth and superimposed mode schematic representation;

Fig. 2 is wide tooth-profile of gear toothed wheel profile design principle schematic representation;

Node change in location schematic representation when Fig. 3 is wide tooth-profile of gear engagement driving;

Fig. 4 is not node change in location schematic representation during engagement driving of wide tooth-profile of gear;

Tooth force change in location figure when Fig. 5 is wide tooth-profile of gear engagement driving;

Fig. 6 is wide profile of tooth planetary pinion toothed wheel profile design principle schematic representation;

Fig. 7 is a wide tooth shaped combined planetary gear combination principle schematic representation;

Fig. 8 is a wide-tooth bevel gear design principle schematic representation;

Fig. 9 is the ring gear tooth ends profile of tooth characteristic pattern of wide tooth shaped combined planetary gear;

Figure 10 is the high strength alloy steel wheel chip architecture principle schematic of between the overlapped gear with wide teeth toothed surface flank of tooth trimming of processing dead angle area being ground.

Among the figure: 1. tooth ends, 2. tooth root portion, 3. the gear teeth angle of rotation of registration sprocketed wheel, 4. top circle, 5. root circle, 6. tooth ends increases part outward, 7. stay part in the tooth root portion, 8. sense of rotation, 9. driving wheel, 10. follower, 11. engaging stress time point starting point, 12. node terminal point during engaging stress, 13. node location during engaging stress not, 14. sun gear, 15. planet wheel, 16. ring gear, 17. the oblique angle that gear teeth rotation is tilted, 18. the axial length of short cylinder angular gear, 19. high strength alloy steel wheel sheet, 20. rotatingshaft, 21. the abrasive material of the sticking plating in alloy steel wheel sheet both sides.

Embodiment

Below in conjunction with accompanying drawing the specific embodiment of the invention is described:

(1),, determines two gear number of teeth z earlier according to gear diameter size estimation and velocity ratio referring to Fig. 2 ₁, z ₂And the radius R of driving wheel or follower top circle 4 _D1Or R _D2Value.

(2) by number of teeth z ₁, z ₂Directly calculating tooth ends 1 or tooth root portion 2 pairing central angles 3, promptly respectively is the angle of rotation θ that the coaxial gear teeth when superimposed of two plate gears should stagger in the overlapped gear with wide teeth ₁, θ ₂Or the maximum central angle that planetary pinion should stagger during the continuous engagement driving of planetary pinion relay.The gear teeth that also are wide-tooth bevel gear must rotate the minimum central angle of inclination.

(3) by top circle 4 radius Rs of driving wheel 9 or follower 10 _D1Or R _D2Value, derive the chord length AB that two top circles 4 intersect:

By Fig. 2, (1.1) formula, can obtain another top circle 4 radius Rs _D2Be respectively with the spacing CD of node maximum:

(4), determine the tooth ends 1 outer one-tenth-value thickness 1/10 △ H that stays part 7 in part 6 and the tooth root portion 2 that increases according to the requirement of meshed transmission gear continous-stable.

(5) can find out that by Fig. 2 each parameter of gear is respectively:

Whole depth: II=CD+2 △ II

Profile of tooth width biggest place: $\frac{\mathrm{<figure-callout\; id="2"\; label="P"\; filenames="DEST\_PATH\_H200610106730501E00011.png,S061A6730520060809E000011.png"\; state="\{\{state\}\}">P</figure-callout>}}{2}=\mathrm{AB}$

The real radius of gear outer contour: $\left\{\begin{array}{c}{\mathrm{<figure-callout\; id="1"\; label="R"\; filenames="S061A6730520060809E000051.png"\; state="\{\{state\}\}">R</figure-callout>}}_1={\mathrm{<figure-callout\; id="1"\; label="R\; d"\; filenames="S061A6730520060809E000051.png"\; state="\{\{state\}\}">R</figure-callout>}}_d+\mathrm{\&Delta;H}\\ {\mathrm{<figure-callout\; id="2"\; label="R"\; filenames="DEST\_PATH\_H200610106730501E00011.png,S061A6730520060809E000011.png"\; state="\{\{state\}\}">R</figure-callout>}}_2={\mathrm{<figure-callout\; id="2"\; label="R\; d"\; filenames="DEST\_PATH\_H200610106730501E00011.png,S061A6730520060809E000011.png"\; state="\{\{state\}\}">R</figure-callout>}}_d+\mathrm{\&Delta;H}\end{array}\right.$

Because the profile line of profile of tooth both sides all is the radius line segment, tooth ends 1 and tooth root portion 2 are the circular arc line segment and are spliced.Connect the corner and can directly cut into little circular arc.The A of Fig. 2, Fig. 3, Fig. 4, B position and whole tooth root portion 2 all should slightly enlarge, and the appropriate gap that stays engagement driving gets final product.The design of toothed wheel profile and node movement locus determines that by the Outside radius that number of teeth z and bucket intersect the toothed wheel profile directly is formed by connecting by radius line segment and circular arc line segment, the node movement locus be exactly the circular arc line segment that intersects of two top circles each half.Increase part outside tooth ends has, stay part in tooth root portion has, cut in advance and wear into smooth camber line shape at the corner point place, and to increase the stability of gear endless relay engagement driving, tooth root portion is slightly larger than tooth ends, leaves certain clearance in engagement driving.

(6) found out by Fig. 3, Fig. 4, Fig. 5: in engagement driving, have only driving wheel 9 for tooth root portion 2, when follower 10 is tooth ends 1,4 circular arc line AD and CB track are to node 12 places from node 11 along top circle, and engagement driving could be set up; When driving wheel 9 is a tooth ends 1, follower 10 during for tooth root portion 2, node 12 places have been that the terminal point of engagement driving will be in the not sliding mode of engagement driving with backgear.So to the stationary axle overlapped gear with wide teeth, the gear teeth stagger coaxial superimposed to cog by 2 or 2, carrying out the continuous engagement driving of relay is necessary selection.To wide tooth shaped combined planetary gear, just can utilize the engagement driving relation that staggers between 2～6 planetary pinions and sun gear and the ring gear could realize the endless relay engagement driving.To wide-tooth bevel gear, the gear teeth certain angle that should tilt to stagger could realize the endless relay engagement driving.

(7) to planetary pinion, the nodal pitch CD in (1.3) formula sees Fig. 6, should change into:

It will make flank of tooth sliding distance and wearing and tearing on the node littler

(8) existing profile of tooth is involute, circular arc and two circular arcs ... each type gear, must have plural gear teeth meshing point of contact simultaneously at each engagement driving section, transmission could be continuously.Keep unequal angular velocity when making plural joggle(d) joint contact along orbiting motion

, reach the purpose of steady transmission, just very high to the required precision of the design of toothed wheel profile, processing.By Fig. 1 of the present invention～9 as can be seen: the continuous engagement driving overall process of overlapped gear with wide teeth, wide tooth shaped combined planetary gear and wide-tooth bevel gear, each engagement driving section has only a stress point of contact all the time, (at the integration face of centerline for radius line segment composition).This stress point of contact is separately fixed at the tooth ends 1 corner point A place of two gears, and along the whole side slip of opposite side tooth ends.Hence one can see that: there is not plural engagement stress point of contact simultaneously in it, because of angular velocity

Fine difference interfere with each other phenomenon, the error that the Design and Machining precision of toothed wheel profile and wearing and tearing produce does not influence the original stationary performance of this meshed transmission gear yet.

Be optimized selection with specific embodiment below:

Overlapped gear with wide teeth

(1) earlier by the radius predicted value of velocity ratio and driving wheel, brings (1.1), (1.2), (1.3) formula respectively into, can calculate tooth radius, central angle, nodal pitch value.Again by tooth ends outer increase part and tooth root portion in stay part Δ H value, just can determine whole parameter values of gear.

(2) to overlapped gear with wide teeth, though can be superimposed together with fastenings by two gears that process, the benefit of doing like this is that the monolithic gear is processed easily, does not have " dead angle " of cutting, is not optimal selection again.Should advocate and adopt as far as possible that hot rolling-cold rolling continuous processing is disposable finishes two registration sprocketed wheel solid forgings, carry out necessary trimming and surface treatment again, such manufacturing process flow can further improve the bulk strength of gear.

(3) superimposed forging forms the trimming and the abrasive machining of the processing dead angle area between the flank of tooth, and tooth root portion 2 is as shown in Figure 1 put to death the flank of tooth trimming of angular region, the technical matters of grinding.We can adopt method as shown in figure 10: the flank of tooth gap that stays when utilizing tooth root portion to be slightly larger than tooth ends, design a high-intensity alloy steel wheel sheet, and wheel sheet both sides are sticking to plate abrasive material and makes thin emery wheel (cutting blade).High speed rotating approaches emery wheel (cutting blade), cuts the both sides trimming and the abrasive machining of expanssion type along flank of tooth gap, rebuilds and grind the processing dead angle area of the flank of tooth simultaneously.

Wide tooth shaped combined planetary gear

(1) establishes center solar wheeling tooth tip circle radius R _Da=5cm, number of teeth z _a=5, planet wheel is 2, number of teeth z _c=3.Stay in sun gear and planet wheel concavo-convex and increase part Δ H outward _Ac=0.1cm, the outer default Δ H of part that increases of ring gear tooth tip _b=0.3cm stays part also to be Δ H in the tooth root portion recess _Acb=0.1cm.

(please note: in order to realize the endless relay engagement driving, the central angle of the gear teeth meshing transmission between 2 planet wheels and sun gear and the ring gear should suitably stagger.The number of teeth of sun gear and ring gear is not equal to the multiple of planet wheel number 2, and the number of teeth of planet wheel should be got odd number, like this could be between sun gear and ring gear endless relay engagement carry-over moment effectively.)

(2) can get the Outside radius R of planet wheel and ring gear by (1.2) (1.3) formula and accompanying drawing 7 _Dc, R _Db, the nodal pitch CD of sun gear and planet wheel _AcBe respectively:

By shown in Figure 7, at Δ AO ₁O ₂In, O ₁O ₂=R _Da+ R _Dc-CD _Ac=7.4315 (cm), by the arbitrary triangle cosine law:

Related data substitution (1.5) formula is got: R _Db=10.2251 (cm).

(3) by (1.2), (1.4) formula, the number of teeth z of ring gear _b, planet wheel and ring gear nodal pitch CD _Cb, the pairing central angle θ of each internal tooth of ring gear _bBe respectively:

z _b=90 ° of ÷ (arcsin0.1511)=10.356, (z _bRound numbers=11)

Because nodal pitch CD _Ac＞CD _Cb, we can get CD _Ac+ Δ H _Ac〉=CD _Cb+ Δ H _b, can improve the stability of planetary pinion engagement driving like this.

By the aforementioned calculation result as can be seen, Outside radius R _Db=10.2251 (cm), the central angle θ of tooth root portion of ring gear _b=17.381 ° all is definite value, and we can't change.To ring gear, the number of teeth must be a natural number, so, z _bShould get big value 11, θ _b=16.364 ° (also being definite value).For the engagement driving between planet wheel and the sun gear can be carried out, see Fig. 9, we must suitably relax the tooth root portion of ring gear, corresponding central angle θ _bValue is relaxed to 17.381 ° by 16.364 °.In like manner, the central angle of the tooth ends width correspondence of ring gear just must be contracted to 16.364 ° * 2-17.381 °=15.347 ° by 16.364 °.So must make the root radius R of adjusted ring gear again _Dbg=R _Db, the radius R of top circle _DbdFor:

R _dbd＝R _dbg-CD _ac＝10.2251-0.6587＝9.5664(cm)

Cancellation ring gear tooth ends increases part Δ H outward _b=0.3cm sees Fig. 9, and at this moment, the ring gear top circle can occupy the maximum value Δ H at planetary gear internal concave at root place on center line _AcbFor:

Obviously, Δ H _AcbDesign load set up.According to the meshing relation of planet wheel tooth root circle with the ring gear top circle, see Fig. 9, by (1.1) formula, can derive the central angle θ of ring gear top circle correspondence _BdFor:

${\mathrm{\&theta;}}_{\mathrm{bd}}=2\arcsin \left(\frac{R_{\mathrm{dcd}}-{\mathrm{CD}}_{\mathrm{ac}}}{R_{\mathrm{db}d}}\sin \frac{{\mathrm{\&theta;}}_c}{2}\right)---\left(1.6\right)$

(1.6) formula that related data is brought into gets: θ _Bd=14.602 °.By Fig. 9, we can also further derive ring gear tooth ends side profile of tooth oblique angle β and are:

By the aforementioned calculation result, draw wide tooth shaped combined planetary gear and see Fig. 7.By shown in Figure 9, in case of necessity, we can also avoid the corner angle of ring gear tooth ends blunt in advance to be stuck in planet wheel tooth root portion in the engagement driving.As seen from Figure 7: suppose that sun gear 14 is driving wheel, ring gear 16 is a follower, and planet carrier is fixed, and then lower planetary gear 15 is in engagement driving moment state, and upper planet wheel 15 is then returned moment to sun gear 14 by ring gear 16.As long as the planet wheel more than 2 or 2 is arranged, just can between sun gear and ring gear, realize endless relay engagement carry-over moment effectively.

Wide-tooth bevel gear

(1) sees accompanying drawing 8, establish axial length (the two gear disk S just of wide-tooth bevel gear ₁, S ₂Between perpendicular distance) be L, L 〉=2A ₁B ₁

(2) if when wide tooth-profile of gear is single straight-tooth, node S shown in Figure 8 ₁A on the disk ₁Point and S ₂B on the circle demifacet ₄The connection straight line of point should be parallel with the gear medial axis of short cylinder.Be follower 10, A if make this gear be positioned at the below ₁B ₁Belong to the tooth ends position.Driving wheel is positioned at the top, just belongs to tooth root portion position.Then can find out by the wide tooth-profile of gear engagement driving principle of Fig. 2～4: this moment A ₁B ₄Straightway just is in the starting point of engaging stress transmission.When gear rotates θ ₁Behind the central angle to B ₁A ₃During node location, then whole driving gear arrives the terminal point of engaging stress transmission, just begins to change over to sliding mode subsequently.Engagement relay transmission just can't realize continuously.

(3) when we with the gear teeth rotation θ that tilts ₂During angle, see the S of Fig. 8 ₂Disk.Wherein: A ₁B ₁Be the profile of tooth width, L is the axial length that gear (profile of tooth) rotates.Helix angle of tooth γ value is:

$\mathrm{\&gamma;}=\mathrm{arctg}\frac{A_1{B}_1}{L}---\left(1.7\right)$

If L=2A ₁B ₁, γ=26.565 ° then.

At this moment, be follower, S if also make this gear be positioned at the below ₁A on the disk ₁Node has the initiative and takes turns on the starting point of engaging stress transmission S ₂A on the disk ₃The node place then is a terminating point.Along A ₁A ₃The whole piece arc is the stressed Line of contact of node, and along with the rotation θ of gear ₁Angle, S ₁A on the disk ₁Node arrives terminating point.A ₁A ₃The stressed conductor rail trace of whole piece arc node is gradually to A ₁Point shrinks, by line contact a becoming contact.And at this moment, S ₂Tooth ends A on the disk ₄B ₄Point then rotates to B forward ₄A ₃Point, driving wheel again can be continuously from B ₄Point begins follower 10 has been carried out the endless relay engagement driving.

(4) as can be seen: if when the tilt angle γ value of the gear teeth is determined by (1.7) formula, though the stressed conductor rail trace of node A from the analysis of the endless relay engagement driving process of wide-tooth bevel gear ₁A ₃Camber line can reach maximum value, but at S ₁, S ₂Engaging stress starting point and terminating point, all be some contact.So in order to increase half stability of the continuous engagement driving of wide-tooth bevel gear, the γ angle of inclination in (1.7) formula should suitably increase, and generally should enlarge 1.25～2 times.For ease of the processing cutting, can in OK range, round number of degrees value.

Certainly, to the wide tooth shaped combined planetary gear that I invent in earlier stage, adopt the suitable helix angle of tooth equally also to have the effect that increases steady relay engagement driving.

Claims (3)

1. wide tooth form relay transmission gear that is used for mechanical actuating unit, the gear that is involute, circular arc, Gothic with existing toothed wheel profile compares, it is characterized in that: the profile of tooth width is existing more than 1.2 times of gear, according to the different relay kinds of drive, be divided into two subclass of wide tooth shaped combined planetary gear and wide-tooth bevel gear, wide tooth shaped combined planetary gear subclass wherein, by the planet wheel more than 2 or 2, the gear teeth suitably stagger, and form the endless relay mesh gear jointly with sun gear and ring gear.

2. the wide tooth shaped combined planetary gear subclass of wide tooth form relay transmission gear as claimed in claim 1, it is characterized in that: the number of teeth of planet wheel must be an odd number, the number of teeth of sun gear and ring gear all is the multiple that is not equal to the planet wheel number.

3. the wide tooth shaped combined planetary gear subclass of wide tooth form relay transmission gear as claimed in claim 1, it is characterized in that: if the combination of the planet wheel more than 2, the gear teeth meshing position of relative sun gear of each planet wheel and ring gear then, the central angle θ that should stagger, multiple choices can be arranged, if planet wheel is an odd number, then gear teeth central angle θ can evenly stagger; If even number, then gear teeth central angle θ can evenly stagger, and also can stagger with suitable central angle θ value in pairs.

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