CN100543344C - High-speed transmission correcting gear - Google Patents

Abstract

The invention discloses a kind of high-speed transmission correcting gear that in the occasion of big speed ratio, uses, can improve the number of teeth that the gear meshing condition also can reduce small gear simultaneously.Its small gear adopts (Z ₁+ K) calculating and the processing of the flank profil degree of depth to be revised, gearwheel adopts (Z ₂+ (Z ₂/ Z ₁) K) calculating and the processing of the flank profil degree of depth are revised, COEFFICIENT K is 0.5～1, small gear and gearwheel all carry out calibration processing by number of actual teeth.Revise by calculating and processing the flank profil degree of depth of large and small gear, not only can reduce the number of teeth of small gear, the linear velocity of falling end gear reaches the purpose that improves rotating speed, also can improve the gear meshing condition simultaneously, reduce the wearing and tearing of gear, increase the operating life of gear, can also improve the intensity and the transmission efficiency of gear.Method for correcting provided by the present invention and processing method are all fairly simple, have brought convenience for design, processing, are particularly suitable for using in the occasion of high speed transmission.

Description

High-speed transmission correcting gear

Technical field

The present invention relates to a kind of gear, especially the high-speed transmission correcting gear that in the occasion of big speed ratio, uses.

Background technique

Involute master gear designing and calculating is simple, and interchangeability is good.But the master gear transmission still exists some narrow limitation: (1) is limited by undercut, and the number of teeth must not be less than Z _Min, make drive mechanism compact inadequately; (2) be not suitable for mounting center is not equal to reference center distance a apart from a ' occasion.When a '＜a, can't install, as a ' during a, though can install, can produce excessive sideshake and cause impact shock, influence the stationarity of transmission; (3) during a pair of master gear transmission, the thickness at root of tooth of small gear is little and the engagement number of times is more, and so the intensity of small gear is lower, it is also more serious that tooth root partly weares and teares, so small gear damages easily, and the while has also been limited the bearing capacity of gearwheel.

At present, in order to improve gear-driven performance, modified gear has appearred.When the tooth bar slotting tool addendum line contact points that oversteps the extreme limit, the gear generation undercut that cuts out.If away from core wheel one segment distance, addendum line no longer oversteps the extreme limit a little with the tooth bar slotting tool, undercut can not take place in the gear that then cuts out, but the standard pitch circle of the reticule of this hour rack and gear is no longer tangent.The gear that cutting is come out behind this change cutter and the tooth base relative position is called modified gear and is also referred to as corrected gear, and what cutter moved is called addendum modification apart from xm, and x is called modification coefficient, and m is the modulus of gear.Cutter is called normal shift away from the displacement of core wheel, at this moment x〉0; The displacement that cutter shifts near core wheel is called negative addendum modification, at this moment x＜0.Master gear is exactly the gear of modification coefficient x=0.

The transmission type of existing modified gear is divided into height change gear and angle correcting gear.

1, zero transmission

Zero transmission is meant that the modification coefficient of two gears satisfies X ₁+ X ₂=0, comprise two kinds of situations.

(1) X ₁=X ₂=0, master gear can be considered the special case of modified gear.

(2) X ₁=-X ₂≠ 0, be called the height change gear.Working pressure angle during two gear transmissions is still the standard pressure angle.The height change gear transmission can improve the bearing capacity of small gear, improves the abrasion condition of gear, and centre distance is still the centre distance of master gear.

2, positive drive, X ₁+ X ₂0, working pressure angle overgauge pressure angle is referred to as the angular deflection transmission.Positive drive can improve the strength of gear teeth, improves the gear wear situation, and centre distance and master gear are than increasing.

3, negative transmission, X ₁+ X ₂＜0, working pressure angle also is referred to as the angular deflection transmission less than the standard pressure angle.Negative transmission can make contact ratio increase to some extent, but the strength of gear teeth descends, and centre distance and master gear are than reducing.

As from the foregoing, master gear and corrected gear equally all are subjected to minimum teeth number Z _MinRestriction, generally, the minimum tooth number Z of its gear _MinBe 14～17.Like this, need the occasion of the big speed ratio of high speed transmission, just must increase the number of teeth of gearwheel, so just strengthened the size and the weight of driving gear pair in order to obtain big speed ratio at some.And in the modern machine, total hope reduces the size and the weight of gear as far as possible when improving gear capacity.

Summary of the invention

Technical problem to be solved by this invention provides a kind of high-speed transmission correcting gear that the gear meshing condition also can reduce the number of teeth of small gear simultaneously that improves.

The technical solution adopted for the present invention to solve the technical problems is: high-speed transmission correcting gear, the pressure angle a of selection original section _o=20 °, addendum coefficient f ₁=1, dedendum of the tooth coefficient f ₂=1.25, Z ₁Be the number of teeth of small gear, Z ₂The number of teeth for gearwheel is characterized in that: small gear adopts (Z ₁+ K) calculating and the processing of the flank profil degree of depth to be revised, gearwheel adopts Calculating and processing to the flank profil degree of depth are revised, and COEFFICIENT K is 0.5～1, and small gear and gearwheel all carry out calibration processing by number of actual teeth.

The invention has the beneficial effects as follows: revise by calculating and processing to the flank profil degree of depth of large and small gear, not only can reduce the number of teeth of small gear, the linear velocity of falling end gear reaches the purpose that improves rotating speed, also can improve the gear meshing condition simultaneously, reduce the wearing and tearing of gear, increase the operating life of gear, can also improve the intensity and the transmission efficiency of gear.Method for correcting provided by the present invention and processing method are all fairly simple, have brought convenience for design, processing, are particularly suitable for using in the occasion of high speed transmission.

Embodiment

Below the present invention is further specified.

High-speed transmission correcting gear of the present invention, the pressure angle a of selection original section _o=20 °, addendum coefficient f ₁=1, dedendum of the tooth coefficient f ₂=1.25, Z ₁Be the number of teeth of small gear, Z ₂Be the number of teeth of gearwheel, Z ₁And Z ₂Size determine by velocity ratio.Small gear adopts (Z ₁+ K) calculating and the processing of the flank profil degree of depth to be revised, gearwheel adopts

Calculating and processing to the flank profil degree of depth are revised, and COEFFICIENT K is 0.5～1, and small gear and gearwheel all carry out calibration processing by number of actual teeth.Adopt the gear of this method for correcting processing to be called high-speed transmission correcting gear, not only simplified each CALCULATION OF PARAMETERS of gear, also bring great convenience, use the general standard gear cutting tool, with regard to this corrected gear that processes that can be very well to processing.

Adopt this method for correcting, the minimum number of teeth of small gear can be 8, the number of teeth that generally can select small gear is 8～14, working pressure angle during working gear be 33 ° 21 ', be equivalent to about correction factor ξ=0.6, improved the intensity (having improved 30%) of gear, lubricating condition when having improved engagement, having reduced the wearing and tearing of tooth, improved the transmission efficiency of gear, is very desirable as driving gear.

Embodiment:

When choosing K=1, promptly small gear adopts the number of teeth to add 1 method for correcting, and its geometric element is as follows:

1.1 standard pitch diameter d ₁=mZ ₁

1.2 pitch diameter d _T1=m (Z ₁+ 1)

1.3 base circle diameter (BCD) d ₀₁=mZ ₁20 ° of cos

1.4 base pitch t ₀20 ° of=m π cos

1.5 outside diameter circle d _E1=m (Z ₁+ 3)

1.6 Z ₁, Z ₂The actual meshingangle of two gears,

1.7 Z ₁, Z ₂When two gear backlash were 0.03m, the correction factor of small gear, gearwheel was

1.8 pinion gear teeth overall height (gearwheel whole depth) h ₁(h ₂)=m[2.25-(ξ ₁-0.5)]

1.9 small gear Root diameter d _I1=(z ₁+ 2 ξ ₁-2.5) m

1.10 chordal thickness $s_1=m(Z_1+1)\sin (\frac{\mathrm{\π}}{2Z_1}-\frac{0.015}{Z_1+1})$

1.11 constant cord height $h_{c1}=m+\frac{d_{t1}}{Z}[1-\cos (\frac{\mathrm{\π}}{2Z_1}-\frac{0.015}{Z+1})]$

1.12 block the base tangent length of two teeth, equal base pitch and add transverse tooth thickness on the basic circle

1.13 tooth top pressure angle

1.14 addendum thickness $S_{e1}=d_{e1}(\frac{\mathrm{\π}}{2Z_1}-\frac{0.015}{Z_1+1}+\mathrm{inva}-{\mathrm{inva}}_{e1})$

During the processing small gear, the top circle diameter d _E1Calculate Root diameter di by (1.5) ₁Calculate by (1.9), calibration is pressed number of actual teeth Z ₁Its essence is exactly by (Z ₁+ 1) calculates the blank of gear, the degree of depth of rolling cut gear.Press number of actual teeth Z ₁Come calibration.The design of gear and processing are all very convenient like this.

Gearwheel adopts

Method for correcting the time, the geometric element of gearwheel is as follows:

2.1 gearwheel standard pitch diameter d ₂=mZ ₂

2.2 gearwheel pitch diameter $d_{t2}=m(Z_2+\frac{Z_2}{Z_1})$

2.3 gearwheel base circle diameter (BCD) d ₀₂=mZ ₂20 ° of cos

2.4 gearwheel base pitch t ₀20 ° of=m π cos

2.5 gearwheel outside diameter circle $d_{e2}=m(Z_2+\frac{Z_2}{Z_1}+2)$

2.6 gearwheel Root diameter d _I2=d _E2-2h ₂

2.7 gearwheel chordal thickness $S_2=m(Z_2+\frac{Z_2}{Z_1})\sin [\frac{\mathrm{\π}}{2Z_2}-\frac{0.015}{(Z_2+\frac{Z_2}{Z_1})}]$

2.8 gearwheel constant cord height $h_{c2}=m+\frac{d_{t2}}{2}\{1-\cos [\frac{\mathrm{\π}}{2Z_2}-\frac{0.015}{(Z_2+\frac{Z_2}{Z_1})}]\}$

2.9 the gearwheel common normal line is striden number of teeth K

Round up round numbers.

2.10 the base tangent length of K tooth of card

2.11 gearwheel tooth top pressure angle

2.12 gearwheel addendum thickness $s_{e2}=d_{e2}\{\frac{\mathrm{\π}}{2Z_2}-\frac{0.015}{Z_2+\frac{Z_2}{Z_1}}+\mathrm{inva}-{\mathrm{inva}}_{e2}\}$

During the processing gearwheel, the top circle diameter d _E1Calculate Root diameter d by (2.5) _I2Calculate by (2.6), calibration is pressed number of actual teeth Z ₂Its essence is pressed exactly

Calculate the blank of gear, the degree of depth of rolling cut gear is pressed number of actual teeth Z ₂Come calibration.The design of gear and processing are all very convenient like this.

2.13 large and small Gear center distance $A=\frac{(d_{t1}+d_{t2})}{2}$

2.14 the contact ratio ε during large and small gear engagement

$\mathrm{\ϵ}=\frac{1}{2\mathrm{\π}}[Z_1({\mathrm{tga}}_{e1}-\mathrm{tga})+Z_2({\mathrm{tga}}_{e2}-\mathrm{tga})]$

The calculating of helical gear (herringbone gear) is the same with general helical gear computational methods with processing method, at first determines to calculate transverse module according to the β angle by helixangle $m_t=\frac{m}{\cos \mathrm{\β}},$ When small gear adopts the number of teeth to add 1 method for correcting, small gear as the m in the helical gear geometric element with m _tSubstitution gets final product.

When gearwheel adopts

Method for correcting the time, gearwheel as the m in the helical gear geometric element with m _tSubstitution gets final product.

Total contact ratio ε during the engagement of a pair of helical gear _rEqual transverse contact ratio ε _aWith Face contact ratio ε _βSum, i.e. ε _r=ε _a+ ε _β, ε wherein _aCalculating by 2.14 is ε _a=ε, ε _β=btg β/π m _t, b is the helical gear facewidth.

Get Z ₁=8, Z ₂=36, a ₀=20 °, m=6, f ₁=1, f ₂=1.25, when K=1, it is as follows to calculate each parameter of large and small gear:

The small gear parameter

Standard pitch diameter d ₁=mZ ₁=6 * 8=48mm

Pitch diameter d _T1=m (Z ₁+ 1)=6 * 9=54mm

Base circle diameter (BCD) d ₀₁=mZ ₁20 °=45.1052458mm of 20 °=6 * 8cos of cos

Base pitch t ₀20 °=17.712788mm of=m π cos 20 °=6 π cos

Outside diameter circle d _E1=m (Z ₁+ 3)=6 * (8+3)=66mm

Working pressure angle

When the back lash is 0.3m=0.3 * 6=0.18mm, the correction factor of small gear (correction factor of gearwheel) ξ ₁

Pinion gear teeth overall height (gearwheel whole depth)

h ₁(h ₂)＝m[2.25-(ξ ₁-0.5)]＝6×[2.25-(0.65-0.5)]＝12.6mm

The small gear Root diameter

d _i1＝(z ₁+2ξ ₁-2.5)m＝(8+2×0.65-2.5)×6＝40.8mm

Perhaps d _I1=d _E1-2h ₁=66-2 * 12.6=40.8mm

Chordal thickness

$s_1=m(z_1+1)\sin (\frac{\mathrm{\π}}{2z_1}-\frac{0.015}{z_1+1})=6(8+1)\sin (\frac{\mathrm{\π}}{2\×8}-\frac{0.015}{8+1})$

$=6\×9\×\sin (0.19634954-0.0016666)=10.44659\mathrm{mm}$

Constant cord height

$h_{c1}=m+\frac{d_{t1}}{2}[1-\cos (\frac{\mathrm{\π}}{2z_1}-\frac{0.015}{z_1+1})]=6+\frac{54}{2}[1-\cos (\frac{\mathrm{\π}}{2\×8}-\frac{0.015}{8+1})]$

$=6.51\mathrm{mm}$

The tooth top pressure angle

Addendum thickness

$s_{e1}=d_{e1}(\frac{\mathrm{\π}}{2z_1}-\frac{0.015}{z_1+1}+\mathrm{inva}-{\mathrm{inva}}_{e1})=66(\frac{\mathrm{\π}}{2\×8}-\frac{0.015}{8+1}+0.07606-0.249736)$

$=1.386\mathrm{mm}$

The base tangent length of two teeth of card

$=28.2469\mathrm{mm}$

The gearwheel parameter

Standard pitch diameter d ₂=mz ₂=6 * 36=216mm

Pitch diameter $d_{t2}=m(Z_2+\frac{Z_2}{Z_1})=6\×(36+\frac{36}{8})=243\mathrm{mm}$

Gearwheel base circle diameter (BCD) d ₀₂=mZ ₂20 °=202.9736mm of 20 °=216cos of cos

Gearwheel base pitch t ₀20 °=17.712788mm of=m π cos 20 °=6 π cos

The gearwheel outside diameter circle $d_{e2}=m(Z_1+\frac{Z_2}{Z_1}+2)=d_{t2}+2\×6=255\mathrm{mm}$

The gearwheel Root diameter

d _i2＝d _e2-2h ₂＝255-2×12.6＝229.8mm

The gearwheel chordal thickness

$s_2=m(z_2+\frac{z_2}{z_1})\sin [\frac{\mathrm{\π}}{2z_2}-\frac{0.015}{(z_2+\frac{z_2}{z_1})}]=6(36+4.5)\sin (\frac{\mathrm{\π}}{2\×36}-\frac{0.015}{36+4.5})$

$=10.5095959\mathrm{mm}$

The gearwheel constant cord height

$h_{c2}=m+\frac{d_{t2}}{2}[1-\cos (\frac{\mathrm{\π}}{2z_2}-\frac{0.015}{z_2+\frac{z_2}{z_1}})]=6+\frac{243}{2}[1-\cos (\frac{\mathrm{\π}}{2\×36}-\frac{0.015}{36+4.5})]$

$=6.113687\mathrm{mm}$

The tooth top pressure angle

Addendum thickness

$s_{e2}=d_{e2}(\frac{\mathrm{\π}}{2z_2}-\frac{0.015}{z_2+\frac{z_2}{z_1}}+\mathrm{inva}-{\mathrm{inva}}_{e2})=255(\frac{\mathrm{\π}}{2\×36}-\frac{0.015}{40.5}+0.07606-0.11028)$

$=2.3059\mathrm{mm}$

The gearwheel common normal line is striden the number of teeth

The base tangent length of 7 teeth of card

$=123.989516+16.53778=104.527\mathrm{mm}$

Large and small Gear center distance

$A=\frac{d_{t1}+d_{t2}}{2}=\frac{54+243}{2}=148.5\mathrm{mm}$

Overlap coefficient during large and small gear engagement

$\mathrm{\ϵ}=\frac{1}{2\mathrm{\π}}[z_1({\mathrm{tga}}_{e1}-\mathrm{tga})+z_2({\mathrm{tga}}_{e2}-\mathrm{tga})]$

$=\frac{1}{2\mathrm{\π}}[8(1.068215466-0.658246015)+36(0.760488269-0.658246015)]$

$=\frac{1}{2\mathrm{\π}}[8\×0.409969-36\×0.102242254]=1.10779$

Claims (1)

1, high-speed transmission correcting gear, the pressure angle a of selection original section ₀=20 °, addendum coefficient f ₁=1, dedendum of the tooth coefficient f ₂=1.25, Z ₁Be the number of teeth of small gear, Z ₂The number of teeth for gearwheel is characterized in that: small gear adopts (Z ₁+ K) calculating and the processing of the flank profil degree of depth to be revised, gearwheel adopts

Calculating and processing to the flank profil degree of depth are revised,

Small gear and gearwheel all carry out calibration processing by number of actual teeth;

The correction of described large and small gear is undertaken by following processing formula, and wherein, m is the modulus of gear, K=1:

(1) geometric element of small gear:

Small gear standard pitch diameter: d ₁=mZ ₁

Small gear pitch diameter: d _T1=m (Z ₁+ K)

Small gear base circle diameter (BCD): d ₀₁=mZ ₁20 ° of cos

Small gear base pitch: t ₀Cos20 ° of=m π

Small gear outside diameter circle: d _E1=m (Z ₁+ 3)

z ₁, Z ₂The actual meshingangle of two gears:

Work as Z ₁, Z ₂When two gear backlash were 0.03m, the correction factor of small gear, gearwheel was:

Pinion gear teeth overall height (gearwheel whole depth): h ₁(h ₂)=m[2.25-(ξ ₁-0.5)]

Small gear Root diameter d _I1=(Z ₁+ 2 ξ ₁-2.5) m

Chordal thickness $s_1=m(Z_1+K)\sin (\frac{\mathrm{\π}}{2Z_1}-\frac{0.015}{Z_1+K})$

Constant cord height $h_{c1}=m+\frac{d_{t1}}{2}[1-\cos (\frac{\mathrm{\π}}{2Z_1}-\frac{0.015}{Z_1+K})]$

The base tangent length of two teeth of card equals base pitch and adds transverse tooth thickness on the basic circle

The tooth top pressure angle

Addendum thickness $S_{e1}=d_{e1}(\frac{\mathrm{\π}}{2Z_1}-\frac{0.015}{Z_1+K}+\mathrm{inva}-{\mathrm{inva}}_{e1})$

(2) geometric element of gearwheel:

Gearwheel standard pitch diameter d ₂=mZ ₂

The gearwheel pitch diameter $d_{t2}=m(Z_2+\frac{Z_2}{Z_1}K)$

Gearwheel base circle diameter (BCD) d ₀₂=mZ ₂Cos20 °

Gearwheel base pitch t ₀20 ° of=m π cos

The gearwheel outside diameter circle $d_{e2}=m(Z_2+\frac{Z_2}{Z_1}K+2)$

Gearwheel Root diameter d _I2=d _E2-2h ₂

The gearwheel chordal thickness

$S_2=m(Z_2+\frac{Z_2}{Z_1}K)\sin [\frac{\mathrm{\π}}{2Z_2}-\frac{0.015}{(Z_2+\frac{Z_2}{Z_1}K)}]$

The gearwheel constant cord height

$h_{e2}=m+\frac{d_{t2}}{2}\{1-\cos [\frac{\mathrm{\π}}{2Z_2}-\frac{0.015}{(Z_2+\frac{Z_2}{Z_1}K)}\left]\right\}$

The gearwheel common normal line is striden the number of teeth

Round up round numbers;

The base tangent length of n tooth of card:

Gearwheel tooth top pressure angle:

The gearwheel addendum thickness $s_{e2}=d_{e2}\{\frac{\mathrm{\π}}{2Z_2}-\frac{0.015}{Z_2+\frac{Z_2}{Z_1}K}+\mathrm{inva}-{\mathrm{inva}}_{e2}\}$

Centre distance between the above-mentioned large and small gear

$A=\frac{(d_{t1}+d_{t2})}{2}$

Contact ratio ε during large and small gear engagement

$\mathrm{\ϵ}=\frac{1}{2\mathrm{\π}}[Z_1({\mathrm{tga}}_{e1}-\mathrm{tga})+Z_2(\mathrm{tg}{a}_{e2}-\mathrm{tga})].$