CN102979855B - 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

It is secondary that involute becomes 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 transverse tooth thickness non-circular gear drive pair.

Background technique

The gear-driven mode in inclination angle, implementation space can 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 velocity ratio, bearing capacity advantages of higher, and in the transmission situation of large crossed axis angle (close to 90 °), show good meshing performance, but under the transmission condition of little crossed axis angle (being less than 45 °) and the operating mode of high-speed drive, Worm Wheel System, face gear transmission, it is little that Spiral Bevel Gear Transmission and Hypoid Gear Drives have contact ratio in actual transmission process, noise is large, to the shortcoming of foozle and assembly error sensitivity, and said gear all needs special purpose machine tool to process, technical arrangement plan and complexity thereof.

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

Noncircular gear can be used for transmitting gear ratio motion, and realize special motion sum functions computing, its pitch curve shape is determined by given velocity ratio Changing Pattern, very favourable to the kinetic characteristic of mechanism, can improve the performance of mechanism, improve the moving condition of mechanism.

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

Summary of the invention

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

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

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

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

Σ＝δ _w1+δ _w2

β _w1＝-β _w2；

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

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

Wherein, δ _w1for involute becomes the work pitch cone cone angle of transverse tooth thickness noncircular gear I;

δ _w2for involute becomes the work pitch cone cone angle of transverse tooth thickness noncircular gear II;

β _w1for involute becomes the helix angle on transverse tooth thickness noncircular gear I pitch plane;

β _w2for involute becomes the helix angle on transverse tooth thickness noncircular gear II pitch plane;

β _w1, β _w2getting dextrorotation is that just left-handed is negative;

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

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

Further, the axis of described involute variable tooth thickness gear I and the axial plane of involute variable tooth thickness gear II intersect, then:

d ₁＝-r _pw1cotδ _w1+r _pw2sinΣ+r _pw2cotδ _w2cosΣ+cotΣ(r _pw1+r _pw2cosΣ-r _pw2cotδ _w2sinΣ)

$d_2=\frac{r_{\mathrm{pw}1}+r_{\mathrm{pw}2}\cos \mathrm{\Σ}-r_{\mathrm{pw}2}\cot {\mathrm{\δ}}_{w2}\sin \mathrm{\Σ}}{\sin \mathrm{\Σ}}$

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

D ₂for involute becomes the mounting distance of transverse tooth thickness noncircular gear II;

R _pw1for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear I axis of transverse tooth thickness non-circular gear drive pair;

R _pw2for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear II axis of transverse tooth thickness non-circular gear drive pair.

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

$d_1=-\frac{r_{\mathrm{Pw}2}}{\sin {\mathrm{\δ}}_{w1}\cos {\mathrm{\δ}}_{w2}}+\frac{E({\sin }^2\mathrm{\Σ}-{\sin }^2{\mathrm{\δ}}_{w1}-\sin {\mathrm{\δ}}_{w1}\sin {\mathrm{\δ}}_{w2}\cos \mathrm{\Σ})}{\sin {\mathrm{\δ}}_{w1}\sin \mathrm{\Σ}\sqrt{{\sin }^2\mathrm{\Σ}-{\sin }^2{\mathrm{\δ}}_{w1}-{\sin }^2{\mathrm{\δ}}_{w2}-2\sin {\mathrm{\δ}}_{w1}\sin {\mathrm{\δ}}_{w2}\cos \mathrm{\Σ}}}$

$d_2=\frac{r_{\mathrm{Pw}2}}{\sin {\mathrm{\δ}}_{w2}\cos {\mathrm{\δ}}_{w2}}-\frac{E(\sin {\mathrm{\δ}}_{w1}\cos \mathrm{\Σ}+\sin {\mathrm{\δ}}_{w2})}{\sin \mathrm{\Σ}\sqrt{{\sin }^2\mathrm{\Σ}-{\sin }^2{\mathrm{\δ}}_{w1}-{\sin }^2{\mathrm{\δ}}_{w2}-2\sin {\mathrm{\δ}}_{w1}\sin {\mathrm{\δ}}_{w2}\cos \mathrm{\Σ}}}$

$E=\frac{(r_{\mathrm{Pw}1}\cos {\mathrm{\δ}}_{w2}+r_{\mathrm{Pw}1}\cos {\mathrm{\δ}}_{w2})\sin ({\mathrm{\β}}_{w1}+{\mathrm{\β}}_{w2})}{\sin \mathrm{\Σ}}$

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

D ₂for involute becomes the mounting distance of transverse tooth thickness noncircular gear II;

R _pw1for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear I axis of transverse tooth thickness non-circular gear drive pair;

R _pw2for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear II axis of transverse tooth thickness non-circular gear drive pair;

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

Beneficial effect of the present invention is:

It is secondary that involute of the present invention becomes transverse tooth thickness non-circular gear drive, the axis becoming transverse tooth thickness noncircular gear II by involute being become the axis of transverse tooth thickness noncircular gear I and involute is set to plane parallel or Plane intersects or spatial intersecting, and the axis of transverse tooth thickness noncircular gear I and the helix angle of involute change transverse tooth thickness noncircular gear II are become to involute, relation between crossed axis angle and pitch cone angle limits, involute can be utilized to become the secondary implementation space transmission of transverse tooth thickness non-circular gear drive, and this involute change transverse tooth thickness non-circular gear drive pair not only inherits space parallel axes, concurrent aces and alternating axis involute variable tooth thickness gear transmission intensity large, good rigidly, convenient processing and manufacture and the high advantage of reliability, but also achieve the requirement that non-circular gear drive meets variable ratio transmission, the variable ratio transmission that can be applicable to space angled requires occasion.

45 ° are less than by the crossed axis angle become by involute between transverse tooth thickness noncircular gear I and involute change transverse tooth thickness noncircular gear II, become transverse tooth thickness non-circular gear drive pair by involute and be set to little crossed axis angle transmission, the feature of involute variable tooth thickness gear transmission can be utilized, 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, shortcoming to foozle and assembly error sensitivity.

Accompanying drawing explanation

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

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

Fig. 3 is that the involute of embodiment becomes the secondary relative velocity schematic diagram at work pitch cone point of contact place and when two involute variable tooth thickness gear rotation directions are contrary of transverse tooth thickness non-circular gear drive;

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

Embodiment

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

First embodiment

As shown in Figure 1, for involute of the present invention becomes the work pitch cone schematic diagram of secondary first embodiment of transverse tooth thickness non-circular gear drive.The involute of the present embodiment becomes transverse tooth thickness non-circular gear drive pair, comprise intermeshing involute and become transverse tooth thickness noncircular gear I 1 and involute change transverse tooth thickness noncircular gear II 2, involute becomes the axis of transverse tooth thickness noncircular gear I 1 and involute and becomes the parallel or Plane intersects of the axial plane of transverse tooth thickness noncircular gear II 2, and:

Σ＝δ _w1+δ _w2

β _w1＝-β _w2；

Wherein, δ _w1for involute becomes the work pitch cone cone angle of transverse tooth thickness noncircular gear I;

δ _w2for involute becomes the work pitch cone cone angle of transverse tooth thickness noncircular gear II;

β _w1for involute becomes the helix angle on transverse tooth thickness noncircular gear I pitch plane;

β _w2for involute becomes the helix angle on transverse tooth thickness noncircular gear II pitch plane;

β _w1, β _w2getting dextrorotation is that just left-handed is negative;

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

The axial plane that the axis of the involute change transverse tooth thickness noncircular gear I 1 of the present embodiment and involute become transverse tooth thickness noncircular gear II 2 intersects, and involute change transverse tooth thickness non-circular gear drive pair also meets following relationship:

d ₁＝-r _pw1cotδ _w1+r _pw2sinΣ+r _pw2cotδ _w2cosΣ+cotΣ(r _pw1+r _pw2cosΣ-r _pw2cotδ _w2sinΣ)

$d_2=\frac{r_{\mathrm{pw}1}+r_{\mathrm{pw}2}\cos \mathrm{\Σ}-r_{\mathrm{pw}2}\cot {\mathrm{\δ}}_{w2}\sin \mathrm{\Σ}}{\sin \mathrm{\Σ}}$

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

D ₂for involute becomes the mounting distance of transverse tooth thickness noncircular gear II;

R _pw1for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear I axis of transverse tooth thickness non-circular gear drive pair;

R _pw2for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear II axis of transverse tooth thickness non-circular gear drive pair.

The involute of the present embodiment becomes transverse tooth thickness non-circular gear drive pair, the axis being become transverse tooth thickness noncircular gear II 2 by the axis and involute involute being become transverse tooth thickness noncircular gear I 1 is set to plane parallel or Plane intersects, and the helix angle to involute variable tooth thickness gear I and involute variable tooth thickness gear II 2, relation between crossed axis angle and pitch cone angle limits, involute can be utilized to become transverse tooth thickness non-circular gear drive secondary concurrent aces inclination angle, implementation space variable ratio transmission, and this involute change transverse tooth thickness non-circular gear drive pair not only inherits space parallel axes or concurrent aces involute variable tooth thickness gear transmission intensity is large, good rigidly, convenient processing and manufacture and the high advantage of reliability, but also achieve the requirement that non-circular gear drive meets variable ratio transmission.

Further, the crossed axis angle that involute becomes between transverse tooth thickness noncircular gear I 1 and involute change transverse tooth thickness noncircular gear II 2 is less than 45 °.45 ° are less than by the crossed axis angle become by involute between transverse tooth thickness noncircular gear I 1 and involute change transverse tooth thickness noncircular gear II 2, become transverse tooth thickness non-circular gear drive pair by involute and be set to little crossed axis angle driving of intersecting axes, the feature of involute variable tooth thickness gear transmission can be utilized, 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, shortcoming to foozle and assembly error sensitivity, there is better meshing performance.

Further, it is the transmission of not rounded variable ratio that involute becomes transverse tooth thickness non-circular gear drive pair, and involute becomes transverse tooth thickness noncircular gear I1 and involute change transverse tooth thickness noncircular gear II 2 is intermeshing noncircular gear.By being become by involute, transverse tooth thickness non-circular gear drive is secondary can realize variable ratio transmission into the transmission of not rounded variable ratio.

The involute that involute becomes transverse tooth thickness non-circular gear drive pair becomes transverse tooth thickness noncircular gear I 1 and involute change transverse tooth thickness noncircular gear II2 composition space intersection axle variable ratio transmission, can be used in small inclination marine gearbox, this gear-box can be applicable to high speed naval vessels, in transmission device on speedboat, small inclination variable ratio transmission under realization ahead running operating mode.When ship power transmission system level is installed, namely the propeller cavitation be connected with small inclination marine gearbox output shaft can obtain the immersion angle of several angle.Two gears have the pitch curve shape determined by given transmission ratio function simultaneously, can realize required velocity ratio Changing Pattern.

Second embodiment

As shown in Figure 4, for involute of the present invention becomes the work pitch cone schematic diagram of secondary second embodiment of transverse tooth thickness non-circular gear drive.The involute of the present embodiment becomes transverse tooth thickness non-circular gear drive pair, comprises intermeshing involute and becomes transverse tooth thickness noncircular gear I 1 and involute change transverse tooth thickness noncircular gear II 2.The axial space that the axis of the involute change transverse tooth thickness noncircular gear I 1 of the present embodiment and involute become transverse tooth thickness noncircular gear II 2 interlocks, and:

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

Wherein, δ _w1for involute becomes the work pitch cone cone angle of transverse tooth thickness noncircular gear I;

δ _w2for involute becomes the work pitch cone cone angle of transverse tooth thickness noncircular gear II;

β _w1for involute becomes the helix angle on transverse tooth thickness noncircular gear I pitch plane;

β _w2for involute becomes the helix angle on transverse tooth thickness noncircular gear II pitch plane;

β _w1, β _w2getting dextrorotation is that just left-handed is negative;

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

And the involute of the present embodiment change transverse tooth thickness non-circular gear drive pair meets following relation:

$d_1=-\frac{r_{\mathrm{Pw}2}}{\sin {\mathrm{\δ}}_{w1}\cos {\mathrm{\δ}}_{w2}}+\frac{E({\sin }^2\mathrm{\Σ}-{\sin }^2{\mathrm{\δ}}_{w1}-\sin {\mathrm{\δ}}_{w1}\sin {\mathrm{\δ}}_{w2}\cos \mathrm{\Σ})}{\sin {\mathrm{\δ}}_{w1}\sin \mathrm{\Σ}\sqrt{{\sin }^2\mathrm{\Σ}-{\sin }^2{\mathrm{\δ}}_{w1}-{\sin }^2{\mathrm{\δ}}_{w2}-2\sin {\mathrm{\δ}}_{w1}\sin {\mathrm{\δ}}_{w2}\cos \mathrm{\Σ}}}$

$d_2=\frac{r_{\mathrm{Pw}2}}{\sin {\mathrm{\δ}}_{w2}\cos {\mathrm{\δ}}_{w2}}-\frac{E(\sin {\mathrm{\δ}}_{w1}\cos \mathrm{\Σ}+\sin {\mathrm{\δ}}_{w2})}{\sin \mathrm{\Σ}\sqrt{{\sin }^2\mathrm{\Σ}-{\sin }^2{\mathrm{\δ}}_{w1}-{\sin }^2{\mathrm{\δ}}_{w2}-2\sin {\mathrm{\δ}}_{w1}\sin {\mathrm{\δ}}_{w2}\cos \mathrm{\Σ}}}$

$E=\frac{(r_{\mathrm{Pw}1}\cos {\mathrm{\δ}}_{w2}+r_{\mathrm{Pw}1}\cos {\mathrm{\δ}}_{w2})\sin ({\mathrm{\β}}_{w1}+{\mathrm{\β}}_{w2})}{\sin \mathrm{\Σ}}$

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

D ₂for involute becomes the mounting distance of transverse tooth thickness noncircular gear II;

R _pw1for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear I axis of transverse tooth thickness non-circular gear drive pair;

R _pw2for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear II axis of transverse tooth thickness non-circular gear drive pair;

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

The involute of the present embodiment becomes transverse tooth thickness non-circular gear drive pair, the axis being become transverse tooth thickness noncircular gear II by the axis and involute involute being become transverse tooth thickness noncircular gear I 1 is set to interlock, and involute is become to the helix angle of transverse tooth thickness noncircular gear I and involute change transverse tooth thickness noncircular gear II 2, relation between crossed axis angle and pitch cone angle limits, involute can be utilized to become transverse tooth thickness non-circular gear drive secondary alternating axis inclination angle, implementation space variable ratio transmission, and this involute becomes transverse tooth thickness non-circular gear drive pair, and not only to inherit spatial intersecting axle involute variable tooth thickness gear transmission intensity large, good rigidly, convenient processing and manufacture and the high advantage of reliability, but also achieve the requirement that non-circular gear drive meets variable ratio transmission.

Further, the crossed axis angle that involute becomes between transverse tooth thickness noncircular gear I 1 and involute change transverse tooth thickness noncircular gear II 2 is less than 45 °.45 ° are less than by the crossed axis angle become by involute between transverse tooth thickness noncircular gear I 1 and involute change transverse tooth thickness noncircular gear II 2, become transverse tooth thickness non-circular gear drive pair by involute and be set to little crossed axis angle crossed-axes gear drive, the feature of involute variable tooth thickness gear transmission can be utilized, 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, shortcoming to foozle and assembly error sensitivity, there is better meshing performance.

Further, it is the transmission of not rounded variable ratio that involute becomes transverse tooth thickness non-circular gear drive pair, involute becomes transverse tooth thickness noncircular gear I1 and involute change transverse tooth thickness noncircular gear II 2 is intermeshing noncircular gear, and the end face pitch curve shape that involute becomes transverse tooth thickness noncircular gear I 1 and involute change transverse tooth thickness noncircular gear II 2 is determined jointly by gear pair correct engagement condition and given velocity ratio Changing Pattern.By being become by involute, transverse tooth thickness non-circular gear drive is secondary can realize variable ratio transmission into the transmission of not rounded variable ratio.

The involute that involute becomes transverse tooth thickness non-circular gear drive pair becomes transverse tooth thickness noncircular gear I 1 and involute change transverse tooth thickness noncircular gear II2 composition spatial intersecting axle variable ratio transmission, can be used in small inclination marine gearbox, this gear-box can be applicable to high speed naval vessels, in transmission device on speedboat, realize small inclination variable ratio transmission under astern condition.When ship power transmission system level is installed, namely the propeller cavitation be connected with small inclination marine gearbox output shaft can obtain the immersion angle of several angle.Two gears have the pitch curve shape determined by given transmission ratio function simultaneously, can realize required velocity ratio Changing Pattern.

What finally illustrate is, above embodiment is only in order to illustrate technological scheme of the present invention and unrestricted, although with reference to preferred embodiment to invention has been detailed description, those of ordinary skill in the art is to be understood that, can modify to technological scheme of the present invention or equivalent replacement, and not departing from aim and the scope of technical solution of the present invention, it all should be encompassed in the middle of right of the present invention.

Claims (4)

1. an involute becomes transverse tooth thickness non-circular gear drive pair, comprises intermeshing involute and becomes transverse tooth thickness noncircular gear I and involute change transverse tooth thickness noncircular gear II; Described involute becomes the axis of transverse tooth thickness noncircular gear I and involute and becomes the parallel or Plane intersects of the axial plane of transverse tooth thickness noncircular gear II, or described involute becomes the axial space that the axis of transverse tooth thickness noncircular gear I and involute become transverse tooth thickness noncircular gear II and interlocks; It is characterized in that: when described involute become the axis of transverse tooth thickness noncircular gear I and involute become the axial plane of transverse tooth thickness noncircular gear II parallel or Plane intersects time:

Σ＝δ _w1+δ _w2

β _w1＝-β _w2；

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

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

Wherein, δ _w1for involute becomes the work pitch cone cone angle of transverse tooth thickness noncircular gear I;

δ _w2for involute becomes the work pitch cone cone angle of transverse tooth thickness noncircular gear II;

β _w1for involute becomes the helix angle on transverse tooth thickness noncircular gear I pitch plane;

β _w2for involute becomes the helix angle on transverse tooth thickness noncircular gear II pitch plane;

β _w1, β _w2getting dextrorotation is that just left-handed is negative;

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

2. involute according to claim 1 becomes transverse tooth thickness non-circular gear drive pair, it is characterized in that: the crossed axis angle that described involute becomes between transverse tooth thickness noncircular gear I and involute change transverse tooth thickness noncircular gear II is less than 45 °.

3. it is secondary that the involute according to any one of claim 1 or 2 becomes transverse tooth thickness non-circular gear drive, it is characterized in that: the axial plane of axis and involute change transverse tooth thickness noncircular gear II that described involute becomes transverse tooth thickness noncircular gear I intersects, and there is following relation:

d ₁＝-r _pw1cotδ _w1+r _pw2sinΣ+r _pw2cotδ _w2cosΣ+cotΣ(r _pw1+r _pw2cosΣ-r _pw2cotδ _w2sinΣ)

$d_2=\frac{r_{\mathrm{pw}1}+r_{\mathrm{pw}2}\cos \mathrm{\Σ}-r_{\mathrm{pw}2}\cot {\mathrm{\δ}}_{w2}\sin \mathrm{\Σ}}{\sin \mathrm{\Σ}}$

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

D ₂for involute becomes the mounting distance of transverse tooth thickness noncircular gear II;

R _pw1for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear I axis of transverse tooth thickness non-circular gear drive pair;

R _pw2for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear II axis of transverse tooth thickness non-circular gear drive pair.

4. it is secondary that the involute according to any one of claim 1 or 2 becomes transverse tooth thickness non-circular gear drive, it is characterized in that: the axial space of axis and involute change transverse tooth thickness noncircular gear II that described involute becomes transverse tooth thickness noncircular gear I interlocks, and there is following relation:

$d_1=-\frac{r_{\mathrm{Pw}2}}{\sin {\mathrm{\δ}}_{w1}\cos {\mathrm{\δ}}_{w2}}+\frac{E({\sin }^2\mathrm{\Σ}-{\sin }^2{\mathrm{\δ}}_{w1}-\sin {\mathrm{\δ}}_{w1}\sin {\mathrm{\δ}}_{w2}\cos \mathrm{\Σ})}{\sin {\mathrm{\δ}}_{w1}\sin \mathrm{\Σ}\sqrt{{\sin }^2\mathrm{\Σ}-{\sin }^2{\mathrm{\δ}}_{w1}-{\sin }^2{\mathrm{\δ}}_{w2}-2\sin {\mathrm{\δ}}_{w1}\sin {\mathrm{\δ}}_{w2}\cos \mathrm{\Σ}}}$

$d_2=\frac{r_{\mathrm{Pw}2}}{\sin {\mathrm{\δ}}_{w2}\cos {\mathrm{\δ}}_{w2}}-\frac{E(\sin {\mathrm{\δ}}_{w1}\cos \mathrm{\Σ}+\sin {\mathrm{\δ}}_{w2})}{\sin \mathrm{\Σ}\sqrt{{\sin }^2\mathrm{\Σ}-{\sin }^2{\mathrm{\δ}}_{w1}-{\sin }^2{\mathrm{\δ}}_{w2}-2\sin {\mathrm{\δ}}_{w1}\sin {\mathrm{\δ}}_{w2}\cos \mathrm{\Σ}}}$

$E=\frac{(r_{\mathrm{Pw}1}\cos {\mathrm{\δ}}_{w2}+r_{\mathrm{Pw}1}\cos {\mathrm{\δ}}_{w2})\sin ({\mathrm{\β}}_{w1}+{\mathrm{\β}}_{w2})}{\sin \mathrm{\Σ}}$

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

D ₂for involute becomes the mounting distance of transverse tooth thickness noncircular gear II;

R _pw1for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear I axis of transverse tooth thickness non-circular gear drive pair;

R _pw2for involute becomes the distance of pitch cone point of contact to involute change transverse tooth thickness noncircular gear II axis of transverse tooth thickness non-circular gear drive pair;

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