CN1067152C - Double point-line meshing gear - Google Patents

Abstract

The present invention relates to a double-point line meshing gear whose tooth profile curve convex tooth forms involute. The concave tooth forms a transition curve, namely that one half of the tooth height forms involute, and the other half forms a transition curve. When the two double-point line meshing gears A, B are mutually meshed, the involute tooth profile of the gear A and the transition curve tooth profile of the gear B are mutually meshed, and the involute tooth profile of the gear B and the transition curve tooth profile of the other tooth of the gear A are mutually meshed to form double-point contact. In the process of operation, when the involute tooth profiles of the gears A, B are mutually in contact, line mesh is also formed. The present invention has the advantages of easy processing, low noise, small transmission size, high contact strength, high bending strength, etc. and is suitable for power transmission devices and universal speed reducers.

Description

Double point-line meshing gear

The present invention relates to a kind of new meshing gear of transferring power, be applicable to actuating unit and universal speed reducer.

Chinese patent 88107595.7 discloses Hovekov toothed gearing, it is a kind of Novikov gears with double circular arc tooth profiles, keep and developed the big characteristics of contact strength of the concavo-convex flank profil of single-circular-arc gear, and the work arc surface of making becomes the tooth top part and partly has antisymmetric two circular arc working surfaces with tooth root.In the engagement process of bidentate face contact at least the gear teeth have two-part to be in the state of transferring power, load is split on two contact point of gear surface, thereby has improved flexural strength.But it also exists deficiency, and at first Novikov gears with double circular arc tooth profiles must use special-purpose Novikov gear hob to process, and does not have separability, will descend greatly if be processed with the error bearing capacity.Secondly, this gear does not have transverse contact ratio, thereby must make helical teeth, makes engaging-in end produce very big impact like this in engagement process, and noise is bigger.

The purpose of this invention is to provide a kind ofly have transverse contact ratio and separability, bearing capacity is big, noise is low, the double point-line meshing gear that size is little, can use involute gear hob processing.

The object of the present invention is achieved like this:

The tooth curve double wedge of double point-line meshing gear is an involute, and recessed tooth is a transition curve, and promptly half of tooth depth is involute, and second half is a transition curve.Two double point-line meshing gear A, when B is meshing with each other, the involute profile of gear A is meshed with the transition curve flank profil of gear B, and the involute profile of gear B is meshed with the transition curve flank profil of another tooth of gear A, be that the tooth top part partly has antisymmetric two working surfaces with tooth root, form the two point contact; In operation process, when the involute profile of gear A, B is in contact with one another, form the line engagement again.

The recessed flank profil of the wide and transition curve of involute double wedge of the present invention respectively by under establish an equation determine:

The wide equation of involute double wedge: y ₀=(0.7854+0.3639x _n) m _n/ cos β

Wherein: r-reference radius, φ-roll angle, α _t-transverse pressure angle, β-helix angle

The recessed tooth profile equation of transition curve:

$x_1=x_c+\cos \mathrm{\β}\sqrt{{({\mathrm{\ρ}}_f/\cos \mathrm{\β})}^2-{(y_c-y_1)}^2}$ tgr=(x ₁-x _c)(y _c-y ₁)/[(p _f/cosβ) ²-(y _c-y ₁) ²]x _c=0.87m _n-m _nx _ny _c=1.5064m _n/cosβp _f=0.38m _ny ₁=1.149m _n/cosβ～1.5064m _n/cosβ

As centre distance a, little, gearwheel number of teeth z ₁, z ₂, normal module m _n, normal pressure angle α _nAfter given, its helixangle between 10 °～30 °, little, gearwheel modification coefficient x _N1, x _N2Between-0.3～-1.5.

Because its existing transverse contact ratio Face contact ratio is arranged again, thereby the present invention can also be made helical teeth or straight-tooth.

Major advantage of the present invention is:

1, owing to replace dome curved tooth exterior feature, replaces the concave circular arc flank profil,, can use common involute gear hob to process, have the factory of gear hobbing machine all can produce so Gear Processing is easy with the transition curve flank profil with involute profile;

2, because its existing transverse contact ratio Face contact ratio is arranged again, thereby when making helical gear, its contact ratio is big, the impact in the time of can reducing axial the engagement, so the noise ratio Novikov gears with double circular arc tooth profiles is low;

3, because it has transverse contact ratio, thereby the present invention can also make straight-tooth;

4, its transmission size is little, and contact strength and flexural strength are all than involute gear height.

Fig. 1 is the flank profil schematic representation of double point-line meshing gear;

Fig. 2 is the end face mesh schematic representation of a pair of double point-line meshing gear.

Embodiment 1:

a=150、z ₁=z ₂=36、m _n=4、α _n=20°、B=60、β=23.5°、x _n1=x _n2=-0.73、d _a1=d _a2=155、h ₁=h ₂=6.9；

Embodiment 2:

a=120、z ₁=z ₂=30、m _n=4、α _n=20°、B=48、β=14°55′42″、x _n1=x _n2=-0.453、d _a1=d _a2=128、h ₁=h ₂=8.71；

Embodiment 3:

a=150、z ₁=26、z ₂=76、m _n=3、α _n=20°、B=60、β=12°20′6″、x _n1=-0.323、x _n2=-1.48、d _a1=80.4、d _a2=227.6、h ₁=5、h ₂=53。

Wherein: a-centre distance, z ₁, z ₂-little, the gearwheel number of teeth, m _n-normal module, α _n-normal pressure angle, the B-facewidth, β-helix angle, x _N1, x _N2-little, gearwheel modification coefficient, d _A1, d _A2-little, gearwheel outside diameter circle, h ₁, h ₂-little, gearwheel tooth depth

Claims (3)

1, a kind of engaging gear is characterized in that: its double wedge tooth curve is an involute, and recessed tooth tooth curve is a transition curve, and promptly half of tooth depth is involute, and second half is a transition curve; Its engagement system is the double dotted line engagement, and promptly gear (A), (B) are when being meshing with each other, and the involute of gear (A) is meshed with the transition curve of gear (B), and the involute of gear (B) is meshed with the transition curve of another tooth of gear (A); Involute at operation process middle gear (A), (B) intermeshes again.

2, engaging gear according to claim 1 is characterized in that: the involute curve of its double wedge exterior feature and the transition curve of recessed flank profil respectively by under establish an equation determine:

The wide equation of involute double wedge:

y ₀=(0.7854+0.3639x _n)m _n/cosβ

Wherein: r-reference radius, φ-roll angle, α _t-transverse pressure angle, β-helix angle

The recessed tooth profile equation of transition curve:

$x_1=x_c+\cos \mathrm{\β}\sqrt{{({\mathrm{\ρ}}_f/\cos \mathrm{\β})}^2-{(y_c-y_1)}^2}$

tgγ=(x ₁-x _c)(y _c-y ₁)/[(p _f/cosβ) ²-(y _c-y ₁) ²]

x _c=0.87m _n-m _nx _n

y _c=1.5064m _n/cosβ

p _f=0.38m _n

y ₁=1.149m _n/cosβ～1.5064m _n/cosβ

3, engaging gear according to claim 1 and 2 is characterized in that: as centre distance (a), and little, the gearwheel number of teeth (z ₁, z ₂), normal module (m _n), normal pressure angle (α _n) given after, its helixangle between 10 °～30 °, little, gearwheel modification coefficient x _N1, x _N2Between-0.3～-1.5.

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