CN102979855A - Involute tooth-thickness variable non-circular gear transmission - Google Patents

Abstract

The invention discloses involute tooth-thickness variable non-circular gear transmission. The device comprises an involute tooth-thickness variable non-circular gear I and an involute tooth-thickness variable non-circular gear II, which are meshed with each other, wherein the axes of the involute tooth-thickness variable non-circular gear I and the involute tooth-thickness variable non-circular gear II are parallel in a plane or intersected in the plane, or the axes of the involute tooth-thickness variable non-circular gear I and the involute tooth-thickness variable non-circular gear II are spatially crossed. As the axes of the involute tooth-thickness variable non-circular gear I and the involute tooth-thickness variable non-circular gear II are parallel or intersected in the plane or spatially crossed, the involute tooth-thickness variable non-circular gear transmission can be utilized to realize spatial transmission, which not only inherits the advantages of high strength, good rigidity, convenience for manufacturing and processing and high reliability of involute tooth-thickness variable gear transmission of spatial parallel axes, concurrent axes and alternating axes, but also meets the requirement of gear ratio transmission.

Description

Involute becomes the transverse tooth thickness non-circular gear drive

Technical field

The present invention relates to a kind of gear transmission, concrete is that a kind of involute becomes the transverse tooth thickness non-circular gear drive.

Background technique

Can the gear-driven mode in inclination angle, implementation space mainly contain Worm Wheel System, face gear transmission, Spiral Bevel Gear Transmission and Hypoid Gear Drives etc. at present.Although it is large that these gear transmissions have a velocity ratio, the bearing capacity advantages of higher, and in the transmission situation of large crossed axis angle (near 90 °), shown preferably meshing performance, but under the operating mode for the transmission condition of little crossed axis angle (less than 45 °) and high-speed drive, Worm Wheel System, face gear transmission, Spiral Bevel Gear Transmission and Hypoid Gear Drives have in the actual transmission process that contact ratio is little, noise is large, to the shortcoming of foozle and assembly error sensitivity, and said gear all needs special purpose machine tool processing, process parameter adjustment and complexity thereof.

The involute beveloid gear is the general type of involute cylindrical gear, it is arbitrarily angled that the axis of two gears can become in theory, can between parallel axes, concurrent aces and alternating axis, realize the transmission of motion and power, especially meshing performance is better than other unparallel shaft kind of drive under small angle transmission of power condition, it is large to have intensity, good rigidly, convenient processing and manufacture, reliability high.

Noncircular gear can be used for transmitting the gear ratio motion, realizes special motion and functional operation, and its pitch curve shape is definite by given velocity ratio Changing Pattern, and is very favourable to the kinetic characteristic of mechanism, can improve the performance of mechanism, improves the moving condition of mechanism.

In view of this, the present invention is intended to explore a kind of involute and becomes the transverse tooth thickness non-circular gear drive, this involute becomes the gear ratio transmission that the transverse tooth thickness non-circular gear drive can be realized the arbitrary axis angle of cut, and have that intensity is large, good rigidly, convenient processing and manufacture and the high advantage of reliability, and under small inclination gear ratio transmission condition, have better transmission performance.

Summary of the invention

The technical problem to be solved in the present invention is to propose a kind of involute to become the transverse tooth thickness non-circular gear drive, this involute becomes transverse tooth thickness non-circular gear drive can realize the gear ratio transmission of the arbitrary axis angle of cut, and have that intensity is large, good rigidly, convenient processing and manufacture and the high advantage of reliability.

Realize above-mentioned technical purpose, involute of the present invention becomes the transverse tooth thickness non-circular gear drive, comprises that intermeshing involute becomes transverse tooth thickness noncircular gear I and involute becomes transverse tooth thickness noncircular gear II;

Described involute becomes the axis of transverse tooth thickness noncircular gear I and axis plane parallel or the Plane intersects that involute becomes transverse tooth thickness noncircular gear II, or described involute becomes the axis of transverse tooth thickness noncircular gear I and the axial space of involute change transverse tooth thickness noncircular gear II interlocks.

Further, when described involute becomes the axis of transverse tooth thickness noncircular gear I and axis plane parallel that involute becomes transverse tooth thickness noncircular gear II or Plane intersects:

∑＝δ _w1+δ _w2

β _w1＝-β _w2；

When described involute becomes the axis of transverse tooth thickness noncircular gear I and axial space that involute becomes transverse tooth thickness noncircular gear II when staggered:

$\cos ({\mathrm{\β}}_{w1}+{\mathrm{\β}}_{w2})=\tan {\mathrm{\δ}}_{w1}\tan {\mathrm{\δ}}_{w2}+\frac{\cos \mathrm{\Σ}}{\cos {\mathrm{\δ}}_{w1}\cos {\mathrm{\δ}}_{w2}}$

Wherein, δ _W1Become the work pitch cone cone angle of transverse tooth thickness noncircular gear I for involute;

δ _W2Become the work pitch cone cone angle of transverse tooth thickness noncircular gear II for involute;

β _W1Be the helix angle on the involute change transverse tooth thickness noncircular gear I pitch plane;

β _W2Be the helix angle on the involute change transverse tooth thickness noncircular gear II pitch plane;

β _W1, β _W2Get dextrorotation for just, left-handed for negative;

∑ is that involute becomes the crossed axis angle between transverse tooth thickness noncircular gear I and the involute change transverse tooth thickness noncircular gear II.

Further, the crossed axis angle between described involute change transverse tooth thickness noncircular gear I and the involute change transverse tooth thickness noncircular gear II is less than 45 °.

Further, the axis Plane intersects of the axis of described involute variable tooth thickness gear I and involute variable tooth thickness gear II, then:

d ₁＝-r _pw1cotδ _w1+r _pw2sin∑+r _pw2cotδ _w2cos∑+cot∑(r _pw1+r _pw2cos∑-r _pw2cotδ _w2sin∑)

${\mathrm{<figure-callout\; id="2"\; label="d"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">d</figure-callout>}}_2=\frac{{\mathrm{<figure-callout\; id="1"\; label="r\; pw"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{pw}}+{\mathrm{<figure-callout\; id="2"\; label="r\; pw"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{pw}}\cos \mathrm{\&Sigma;}-{\mathrm{<figure-callout\; id="2"\; label="r\; pw"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{pw}}\cot {\mathrm{\&delta;}}_{w2}\sin \mathrm{\&Sigma;}}{\sin \mathrm{\&Sigma;}}$

Wherein, d ₁Become the mounting distance of transverse tooth thickness noncircular gear I for involute;

d ₂Become the mounting distance of transverse tooth thickness noncircular gear II for involute;

r _Pw1Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear I axis;

r _Pw2Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear II axis.

Further, described involute becomes the axis of transverse tooth thickness noncircular gear I and the axis plane of involute change transverse tooth thickness noncircular gear II interlocks, then:

${\mathrm{<figure-callout\; id="1"\; label="d"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">d</figure-callout>}}_1=-\frac{{\mathrm{<figure-callout\; id="2"\; label="r\; Pw"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{Pw}}}{\sin {\mathrm{\&delta;}}_{w1}\cos {\mathrm{\&delta;}}_{w2}}+\frac{E({\sin }^2\mathrm{\&Sigma;}-{\sin }^2{\mathrm{\&delta;}}_{w1}-\sin {\mathrm{\&delta;}}_{w1}\sin {\mathrm{\&delta;}}_{w2}\cos \mathrm{\&Sigma;})}{\sin {\mathrm{\&delta;}}_{w1}\sin \mathrm{\&Sigma;}\sqrt{{\sin }^2\mathrm{\&Sigma;}-{\sin }^2{\mathrm{\&delta;}}_{w1}-{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2{\mathrm{\&delta;}}_{w2}-2\sin {\mathrm{\&delta;}}_{w1}\sin {\mathrm{\&delta;}}_{w2}\cos \mathrm{\&Sigma;}}}$

${\mathrm{<figure-callout\; id="2"\; label="d"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">d</figure-callout>}}_2=\frac{{\mathrm{<figure-callout\; id="2"\; label="r\; Pw"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{Pw}}}{\sin {\mathrm{\&delta;}}_{w2}\cos {\mathrm{\&delta;}}_{w2}}-\frac{E({\sin \mathrm{\&delta;}}_{w1}\cos \mathrm{\&Sigma;}+\sin {\mathrm{\&delta;}}_{w2})}{\sin \mathrm{\&Sigma;}\sqrt{{\sin }^2\mathrm{\&Sigma;}-{\sin }^2{\mathrm{\&delta;}}_{w1}-{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2{\mathrm{\&delta;}}_{w2}-2\sin {\mathrm{\&delta;}}_{w1}\sin {\mathrm{\&delta;}}_{w2}\cos \mathrm{\&Sigma;}}}$

$E=\frac{({\mathrm{<figure-callout\; id="1"\; label="r\; Pw"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{Pw}}\cos {\mathrm{\&delta;}}_{w2}+{\mathrm{<figure-callout\; id="1"\; label="r\; Pw"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{Pw}}\cos {\mathrm{\&delta;}}_{w2})\sin ({\mathrm{\&beta;}}_{w1}+{\mathrm{\&beta;}}_{w2})}{\sin \mathrm{\&Sigma;}}$

Wherein, d ₁Become the mounting distance of transverse tooth thickness noncircular gear I for involute;

d ₂Become the mounting distance of transverse tooth thickness noncircular gear II for involute;

r _Pw1Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear I axis;

r _Pw2Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear II axis;

E is that involute becomes the beeline between the axis of transverse tooth thickness noncircular gear I and the axis that involute becomes transverse tooth thickness noncircular gear II.

Beneficial effect of the present invention is:

Involute of the present invention becomes the transverse tooth thickness non-circular gear drive, become the axis that the axis of transverse tooth thickness noncircular gear I and involute become transverse tooth thickness noncircular gear II by involute and be set to plane parallel or Plane intersects or spatial intersecting, and involute become the axis of transverse tooth thickness noncircular gear I and the helix angle that involute becomes transverse tooth thickness noncircular gear II, relation between crossed axis angle and the pitch cone angle limits, can utilize involute to become the implementation space transmission of transverse tooth thickness non-circular gear drive, and this involute becomes the transverse tooth thickness non-circular gear drive and has not only inherited the space parallel axle, concurrent aces and alternating axis involute variable tooth thickness gear transmission intensity are large, good rigidly, the advantage that convenient processing and manufacture and reliability are high, but also obtained the requirement that non-circular gear drive satisfies the gear ratio transmission, can be applicable to the angled gear ratio transmission in space and require occasion.

Become crossed axis angle between the transverse tooth thickness noncircular gear II less than 45 ° by involute being become transverse tooth thickness noncircular gear I and involute, be about to involute change transverse tooth thickness non-circular gear drive and be set to little crossed axis angle transmission, can utilize the characteristics of involute variable tooth thickness gear transmission, overcome that the gear transmission of existing space inclination angle is little at the contact ratio of little crossed axis angle and high-speed drive condition, noise large, to the shortcoming of foozle and assembly error sensitivity.

Description of drawings

Fig. 1 is the work pitch cone schematic representation that involute of the present invention becomes transverse tooth thickness non-circular gear drive the first embodiment;

The involute of Fig. 2 present embodiment becomes the transverse tooth thickness non-circular gear drive at place, work pitch cone point of contact and the relative velocity schematic representation in the identical situation of two involute variable tooth thickness gear rotation directions;

Fig. 3 is that embodiment's involute becomes the transverse tooth thickness non-circular gear drive at place, work pitch cone point of contact and the relative velocity schematic representation in the opposite situation of two involute variable tooth thickness gear rotation directions;

Fig. 4 is the work pitch cone schematic representation that involute of the present invention becomes transverse tooth thickness non-circular gear drive the second embodiment.

Embodiment

Below in conjunction with accompanying drawing the specific embodiment of the present invention is elaborated.

The first embodiment

As shown in Figure 1, become transverse tooth thickness non-circular gear drive the first embodiment's work pitch cone schematic representation for involute of the present invention.The involute of present embodiment becomes the transverse tooth thickness non-circular gear drive, comprise that intermeshing involute becomes transverse tooth thickness noncircular gear I1 and involute becomes transverse tooth thickness noncircular gear II2, involute becomes the axis of transverse tooth thickness noncircular gear I1 and axis plane parallel or the Plane intersects that involute becomes transverse tooth thickness noncircular gear II2, and:

∑＝δ _w1+δ _w2

β _w1＝-β _w2；

Wherein, δ _W1Become the work pitch cone cone angle of transverse tooth thickness noncircular gear I for involute;

δ _W2Become the work pitch cone cone angle of transverse tooth thickness noncircular gear II for involute;

β _W1Be the helix angle on the involute change transverse tooth thickness noncircular gear I pitch plane;

β _W2Be the helix angle on the involute change transverse tooth thickness noncircular gear II pitch plane;

β _W1, β _W2Get dextrorotation for just, left-handed for negative;

∑ is that involute becomes the crossed axis angle between transverse tooth thickness noncircular gear I and the involute change transverse tooth thickness noncircular gear II.

The involute of present embodiment becomes the axis of transverse tooth thickness noncircular gear I1 and the axis Plane intersects that involute becomes transverse tooth thickness noncircular gear II2, and involute change transverse tooth thickness non-circular gear drive also satisfies following relationship:

d ₁＝-r _pw1cotδ _w1+r _pw2sin∑+r _pw2cotδ _w2cos∑+cot∑(r _pw1+r _pw2cos∑-r _pw2cotδ _w2sin∑)

${\mathrm{<figure-callout\; id="2"\; label="d"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">d</figure-callout>}}_2=\frac{{\mathrm{<figure-callout\; id="1"\; label="r\; pw"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{pw}}+{\mathrm{<figure-callout\; id="2"\; label="r\; pw"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{pw}}\cos \mathrm{\&Sigma;}-{\mathrm{<figure-callout\; id="2"\; label="r\; pw"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{pw}}\cot {\mathrm{\&delta;}}_{w2}\sin \mathrm{\&Sigma;}}{\sin \mathrm{\&Sigma;}}$

Wherein, d ₁Become the mounting distance of transverse tooth thickness noncircular gear I for involute;

d ₂Become the mounting distance of transverse tooth thickness noncircular gear II for involute;

r _Pw1Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear I axis;

r _Pw2Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear II axis.

The involute of present embodiment becomes the transverse tooth thickness non-circular gear drive, become the axis that the axis of transverse tooth thickness noncircular gear I1 and involute become transverse tooth thickness noncircular gear II2 by involute and be set to plane parallel or Plane intersects, and to the helix angle of involute variable tooth thickness gear I and involute variable tooth thickness gear II2, relation between crossed axis angle and the pitch cone angle limits, can utilize involute to become transverse tooth thickness non-circular gear drive implementation space concurrent aces inclination angle gear ratio transmission, and this involute becomes, and the transverse tooth thickness non-circular gear drive has not only been inherited the space parallel axle or concurrent aces involute variable tooth thickness gear transmission intensity is large, good rigidly, the advantage that convenient processing and manufacture and reliability are high, but also obtained the requirement that non-circular gear drive satisfies the gear ratio transmission.

Further, the crossed axis angle between involute change transverse tooth thickness noncircular gear I1 and the involute change transverse tooth thickness noncircular gear II2 is less than 45 °.Become crossed axis angle between the transverse tooth thickness noncircular gear II2 less than 45 ° by involute being become transverse tooth thickness noncircular gear I1 and involute, be about to involute change transverse tooth thickness non-circular gear drive and be set to the transmission of little crossed axis angle concurrent aces, can utilize the characteristics of involute variable tooth thickness gear transmission, overcome that the gear transmission of existing space inclination angle is little at the contact ratio of little crossed axis angle and high-speed drive condition, noise large, to the shortcoming of foozle and assembly error sensitivity, have better meshing performance.

Further, involute becomes the transverse tooth thickness non-circular gear drive and is non-round variable ratio transmission, and involute becomes transverse tooth thickness noncircular gear I1 and involute change transverse tooth thickness noncircular gear II2 is intermeshing noncircular gear.Can realize the variable ratio transmission by involute being become the transverse tooth thickness non-circular gear drive into non-round variable ratio transmission.

The involute that involute becomes the transverse tooth thickness non-circular gear drive becomes transverse tooth thickness noncircular gear I1 and the transmission of involute change transverse tooth thickness noncircular gear II2 composition space intersection axle gear ratio, can be used in the small inclination marine gearbox, this gear-box can be applicable to the high speed naval vessels, in the transmission device on the speedboat, realize small inclination gear ratio transmission under the ahead running operating mode.When ship power transmission system level was installed, the propeller cavitation that links to each other with small inclination marine gearbox output shaft namely can obtain the immersion angle of several angle.Two gears have the pitch curve shape of being determined by given transmission ratio function simultaneously, can realize desired velocity ratio Changing Pattern.

The second embodiment

As shown in Figure 4, become transverse tooth thickness non-circular gear drive the second embodiment's work pitch cone schematic representation for involute of the present invention.The involute of present embodiment becomes the transverse tooth thickness non-circular gear drive, comprises that intermeshing involute becomes transverse tooth thickness noncircular gear I1 and involute becomes transverse tooth thickness noncircular gear II2.The involute of present embodiment becomes the axis of transverse tooth thickness noncircular gear I1 and the axial space of involute change transverse tooth thickness noncircular gear II2 interlocks, and:

$\cos ({\mathrm{\&beta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}+{\mathrm{\&beta;}}_{w2})=\tan {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}\tan {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="2"\; label="w"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">w</figure-callout>}2}+\frac{\cos \mathrm{\&Sigma;}}{\cos {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}\cos {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="2"\; label="w"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">w</figure-callout>}2}}$

Wherein, δ _W1Become the work pitch cone cone angle of transverse tooth thickness noncircular gear I for involute;

δ _W2Become the work pitch cone cone angle of transverse tooth thickness noncircular gear II for involute;

β _W1Be the helix angle on the involute change transverse tooth thickness noncircular gear I pitch plane;

β _W2Be the helix angle on the involute change transverse tooth thickness noncircular gear II pitch plane;

β _W1, β _W2Get dextrorotation for just, left-handed for negative;

∑ is that involute becomes the crossed axis angle between transverse tooth thickness noncircular gear I and the involute change transverse tooth thickness noncircular gear II.

And the involute of present embodiment becomes the transverse tooth thickness non-circular gear drive and satisfies following relation:

${\mathrm{<figure-callout\; id="1"\; label="d"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">d</figure-callout>}}_1=-\frac{{\mathrm{<figure-callout\; id="2"\; label="r\; Pw"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{Pw}}}{\sin {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}\cos {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="2"\; label="w"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">w</figure-callout>}2}}+\frac{E({\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&Sigma;}-{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2{\mathrm{\&delta;}}_{w1}-\sin {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}\sin {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="2"\; label="w"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">w</figure-callout>}2}\cos \mathrm{\&Sigma;})}{\sin {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}\sin \mathrm{\&Sigma;}\sqrt{{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&Sigma;}-{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2{\mathrm{\&delta;}}_{w1}-{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2{\mathrm{\&delta;}}_{w2}-2\sin {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}\sin {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="2"\; label="w"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">w</figure-callout>}2}\cos \mathrm{\&Sigma;}}}$

${\mathrm{<figure-callout\; id="2"\; label="d"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">d</figure-callout>}}_2=\frac{{\mathrm{<figure-callout\; id="2"\; label="r\; Pw"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{Pw}}}{\sin {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="2"\; label="w"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">w</figure-callout>}2}\cos {\mathrm{\&delta;}}_{w2}}-\frac{E({\sin \mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}\cos \mathrm{\&Sigma;}+\sin {\mathrm{\&delta;}}_{w2})}{\sin \mathrm{\&Sigma;}\sqrt{{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2\mathrm{\&Sigma;}-{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2{\mathrm{\&delta;}}_{w1}-{\mathrm{<figure-callout\; id="2"\; label="sin"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">sin</figure-callout>}}^2{\mathrm{\&delta;}}_{w2}-2\sin {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}\sin {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="2"\; label="w"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">w</figure-callout>}2}\cos \mathrm{\&Sigma;}}}$

$E=\frac{({\mathrm{<figure-callout\; id="1"\; label="r\; Pw"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{Pw}}\cos {\mathrm{\&delta;}}_{\mathrm{<figure-callout\; id="2"\; label="w"\; filenames="HDA00002616908100011.png,HDA00002616908100012.png"\; state="\{\{state\}\}">w</figure-callout>}2}+{\mathrm{<figure-callout\; id="1"\; label="r\; Pw"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">r</figure-callout>}}_{\mathrm{Pw}}\cos {\mathrm{\&delta;}}_{w2})\sin ({\mathrm{\&beta;}}_{\mathrm{<figure-callout\; id="1"\; label="w"\; filenames="HDA00002616908100011.png"\; state="\{\{state\}\}">w</figure-callout>}1}+{\mathrm{\&beta;}}_{w2})}{\sin \mathrm{\&Sigma;}}$

Wherein, d ₁Become the mounting distance of transverse tooth thickness noncircular gear I for involute;

d ₂Become the mounting distance of transverse tooth thickness noncircular gear II for involute;

r _Pw1Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear I axis;

r _Pw2Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear II axis;

E is that involute becomes the beeline between the axis of transverse tooth thickness noncircular gear I and the axis that involute becomes transverse tooth thickness noncircular gear II.

The involute of present embodiment becomes the transverse tooth thickness non-circular gear drive, becoming the axis that the axis of transverse tooth thickness noncircular gear I1 and involute become transverse tooth thickness noncircular gear II by involute is set to interlock, and involute become the helix angle that transverse tooth thickness noncircular gear I and involute become transverse tooth thickness noncircular gear II2, relation between crossed axis angle and the pitch cone angle limits, can utilize involute to become transverse tooth thickness non-circular gear drive implementation space alternating axis inclination angle gear ratio transmission, and it is large that this involute change transverse tooth thickness non-circular gear drive has not only been inherited spatial intersecting axle involute variable tooth thickness gear transmission intensity, good rigidly, the advantage that convenient processing and manufacture and reliability are high, but also obtained the requirement that non-circular gear drive satisfies the gear ratio transmission.

Further, the crossed axis angle between involute change transverse tooth thickness noncircular gear I1 and the involute change transverse tooth thickness noncircular gear II2 is less than 45 °.Become crossed axis angle between the transverse tooth thickness noncircular gear II2 less than 45 ° by involute being become transverse tooth thickness noncircular gear I1 and involute, be about to involute change transverse tooth thickness non-circular gear drive and be set to the transmission of little crossed axis angle alternating axis, can utilize the characteristics of involute variable tooth thickness gear transmission, overcome that the gear transmission of existing space inclination angle is little at the contact ratio of little crossed axis angle and high-speed drive condition, noise large, to the shortcoming of foozle and assembly error sensitivity, have better meshing performance.

Further, involute becomes the transverse tooth thickness non-circular gear drive and is non-round variable ratio transmission, involute becomes transverse tooth thickness noncircular gear I1 and involute change transverse tooth thickness noncircular gear II2 is intermeshing noncircular gear, and involute becomes the end face pitch curve shape of transverse tooth thickness noncircular gear I1 and involute change transverse tooth thickness noncircular gear II2 and jointly determined by gear pair correct engagement condition and given velocity ratio Changing Pattern.Can realize the variable ratio transmission by involute being become the transverse tooth thickness non-circular gear drive into non-round variable ratio transmission.

The involute that involute becomes the transverse tooth thickness non-circular gear drive becomes transverse tooth thickness noncircular gear I1 and the transmission of involute change transverse tooth thickness noncircular gear II2 composition spatial intersecting axle gear ratio, can be used in the small inclination marine gearbox, this gear-box can be applicable to the high speed naval vessels, in the transmission device on the speedboat, realize small inclination gear ratio transmission under the astern condition.When ship power transmission system level was installed, the propeller cavitation that links to each other with small inclination marine gearbox output shaft namely can obtain the immersion angle of several angle.Two gears have the pitch curve shape of being determined by given transmission ratio function simultaneously, can realize desired velocity ratio Changing Pattern.

Explanation is at last, above embodiment is only unrestricted in order to technological scheme of the present invention to be described, although with reference to preferred embodiment the present invention is had been described in detail, those of ordinary skill in the art is to be understood that, can make amendment or be equal to replacement technological scheme of the present invention, and not breaking away from aim and the scope of technical solution of the present invention, it all should be encompassed in the middle of the claim scope of the present invention.

Claims (5)

1. an involute becomes the transverse tooth thickness non-circular gear drive, it is characterized in that: comprise that intermeshing involute becomes transverse tooth thickness noncircular gear I and involute becomes transverse tooth thickness noncircular gear II;

Described involute becomes the axis of transverse tooth thickness noncircular gear I and axis plane parallel or the Plane intersects that involute becomes transverse tooth thickness noncircular gear II, or described involute becomes the axis of transverse tooth thickness noncircular gear I and the axial space of involute change transverse tooth thickness noncircular gear II interlocks.

2. according to claim 1ly gradually open

Line becomes the transverse tooth thickness non-circular gear drive, it is characterized in that: when described involute becomes the axis of transverse tooth thickness noncircular gear I and axis plane parallel that involute becomes transverse tooth thickness noncircular gear II or Plane intersects:

∑＝δ _w1+δ _w2

β _w1＝-β _w2；

When described involute becomes the axis of transverse tooth thickness noncircular gear I and axial space that involute becomes transverse tooth thickness noncircular gear II when staggered:

$\cos ({\mathrm{\&beta;}}_{w1}+{\mathrm{\&beta;}}_{w2})=\tan {\mathrm{\&delta;}}_{w1}\tan {\mathrm{\&delta;}}_{w2}+\frac{\cos \mathrm{\&Sigma;}}{\cos {\mathrm{\&delta;}}_{w1}\cos {\mathrm{\&delta;}}_{w2}}$

Wherein, δ _W1Become the work pitch cone cone angle of transverse tooth thickness noncircular gear I for involute;

δ _W2Become the work pitch cone cone angle of transverse tooth thickness noncircular gear II for involute;

β _W1Be the helix angle on the involute change transverse tooth thickness noncircular gear I pitch plane;

β _W2Be the helix angle on the involute change transverse tooth thickness noncircular gear II pitch plane;

β _W1, β _W2Get dextrorotation for just, left-handed for negative;

∑ is that involute becomes the crossed axis angle between transverse tooth thickness noncircular gear I and the involute change transverse tooth thickness noncircular gear II.

3. involute according to claim 2 becomes the transverse tooth thickness non-circular gear drive, it is characterized in that: the crossed axis angle between described involute change transverse tooth thickness noncircular gear I and the involute change transverse tooth thickness noncircular gear II is less than 45 °.

According to claim 2 or 3 each described involutes become transverse tooth thickness non-circular gear drives, it is characterized in that: described involute becomes the axis of transverse tooth thickness noncircular gear I and the axis Plane intersects that involute becomes transverse tooth thickness noncircular gear II, has following relation:

d ₁＝-r _pw1cotδ _w1+r _pw2sin∑+r _pw2cotδ _w2cos∑+cot∑(r _pw1+r _pw2cos∑-r _pw2cotδ _w2sin∑)

$d_2=\frac{r_{\mathrm{pw}1}+r_{\mathrm{pw}2}\cos \mathrm{\&Sigma;}-r_{\mathrm{pw}2}\cot {\mathrm{\&delta;}}_{w2}\sin \mathrm{\&Sigma;}}{\sin \mathrm{\&Sigma;}}$

Wherein, d ₁Become the mounting distance of transverse tooth thickness noncircular gear I for involute;

d ₂Become the mounting distance of transverse tooth thickness noncircular gear II for involute;

r _Pw1Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear I axis;

r _Pw2Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear II axis.

According to claim 2 or 3 each described involutes become transverse tooth thickness non-circular gear drives, it is characterized in that: described involute become the axis of transverse tooth thickness noncircular gear I and axial space that involute becomes transverse tooth thickness noncircular gear II staggered, have following relation:

$d_1=-\frac{r_{\mathrm{Pw}2}}{\sin {\mathrm{\&delta;}}_{w1}\cos {\mathrm{\&delta;}}_{w2}}+\frac{E({\sin }^2\mathrm{\&Sigma;}-{\sin }^2{\mathrm{\&delta;}}_{w1}-\sin {\mathrm{\&delta;}}_{w1}\sin {\mathrm{\&delta;}}_{w2}\cos \mathrm{\&Sigma;})}{\sin {\mathrm{\&delta;}}_{w1}\sin \mathrm{\&Sigma;}\sqrt{{\sin }^2\mathrm{\&Sigma;}-{\sin }^2{\mathrm{\&delta;}}_{w1}-{\sin }^2{\mathrm{\&delta;}}_{w2}-2\sin {\mathrm{\&delta;}}_{w1}\sin {\mathrm{\&delta;}}_{w2}\cos \mathrm{\&Sigma;}}}$

$d_2=\frac{r_{\mathrm{Pw}2}}{\sin {\mathrm{\&delta;}}_{w2}\cos {\mathrm{\&delta;}}_{w2}}-\frac{E({\sin \mathrm{\&delta;}}_{w1}\cos \mathrm{\&Sigma;}+\sin {\mathrm{\&delta;}}_{w2})}{\sin \mathrm{\&Sigma;}\sqrt{{\sin }^2\mathrm{\&Sigma;}-{\sin }^2{\mathrm{\&delta;}}_{w1}-{\sin }^2{\mathrm{\&delta;}}_{w2}-2\sin {\mathrm{\&delta;}}_{w1}\sin {\mathrm{\&delta;}}_{w2}\cos \mathrm{\&Sigma;}}}$

$E=\frac{(r_{\mathrm{Pw}1}\cos {\mathrm{\&delta;}}_{w2}+r_{\mathrm{Pw}1}\cos {\mathrm{\&delta;}}_{w2})\sin ({\mathrm{\&beta;}}_{w1}+{\mathrm{\&beta;}}_{w2})}{\sin \mathrm{\&Sigma;}}$

Wherein, d ₁Become the mounting distance of transverse tooth thickness noncircular gear I for involute;

d ₂Become the mounting distance of transverse tooth thickness noncircular gear II for involute;

r _Pw1Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear I axis;

r _Pw2Pitch cone point of contact to the involute that becomes the transverse tooth thickness non-circular gear drive for involute becomes the distance of transverse tooth thickness noncircular gear II axis;

E is that involute becomes the beeline between the axis of transverse tooth thickness noncircular gear I and the axis that involute becomes transverse tooth thickness noncircular gear II.

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