CN86104871A - The comprehensive displacement of pitch cone and be the spiral bevel gear pair of negative value - Google Patents
The comprehensive displacement of pitch cone and be the spiral bevel gear pair of negative value Download PDFInfo
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- CN86104871A CN86104871A CN86104871.7A CN86104871A CN86104871A CN 86104871 A CN86104871 A CN 86104871A CN 86104871 A CN86104871 A CN 86104871A CN 86104871 A CN86104871 A CN 86104871A
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- bevel gear
- pitch cone
- design
- cone
- gear pair
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Abstract
The comprehensive displacement of pitch cone and be the spiral bevel gear pair of negative value the invention belongs to mechanical transmission mechanism.Secondary its comprehensive modification coefficient sum of existing spiral bevel gear is zero, causes the large helix angle transmission to have only monodentate to engagement in node area.Pitting corrosion resistant performance is low, and the intensity of low pitch angle transmission is lower, and noise is bigger.The present invention adopts the comprehensive displacement of pitch cone and is the principle design of negative value.Node area can have bidentate to engagement, can optimal design radially, the tangent modification coefficient forms novel tooth form and selects for use with different damage types for various operating conditions, satisfying under the strength condition, not only stable drive, noise are low, and just can make very easily popularization with existing machine tool.
Description
The present invention is used for mechanical transmission fields, the spiral bevel gear ancillary equipment of transmission between two turning axlees that intersect.
The spiral bevel gear pair that existing countries in the world are industrial, most with rack cutter processing, they all are that employing modification coefficient sum is that zero principle designs.With West Germany's Cyclo-Paliold-System KN3028/ssue No.2 gear is example, and it comprises two kinds of situations:
(1) when the bevel gear pair gear ratio is 1, adopts no displacement (x
1=x
2=0) design;
(2) when the bevel gear pair gear ratio greater than 1 the time, often adopt high displacement (x
1+ x
2=0) design.Promptly adopt the modification coefficient sum to be all zero principle and design, this spiral bevel gear pair can be described as " zero " deflection curve bevel gear pair.When this spiral bevel gear pair was designed, pitch cone angle δ ' overlapped with calibration cone angle δ, and meshingangle ' equal the pressure angle α on the pitch cone does not change so that guarantee two crossed axis angles of bevel gear pair.Shortcomings such as " zero " displacement design exists bevel pinion bigger, more easy to wear than sliding, and bevel pinion is more weak relatively.And, can not realize that bidentate is to engagement driving as helixangle m during less than 30 °.Cause steady transmission poor, noise is higher.
Task of the present invention is a kind of novel spiral bevel gear pair that has low noise, steady transmission and high bearing capacity and just can produce with the existing cutting equipment in various countries of design.
Solution of the present invention is: adopt the comprehensive displacement pitch cone of negative value principle design to make novel spiral bevel gear pair, making its comprehensive modification coefficient sum Xc on end face virtual gear pair is negative value.
Xc＝X
1+X
2+0.5（X
t1+X
t2）ctgα＜0
X in the formula
1, X
2Be respectively the overlap arc of bevel pinion and bevel gear wheel,
X
T1, X
T2Be respectively the tangent modification coefficient of bevel pinion and bevel gear wheel.
α is upward pressure angle, Equivalent number of teeth calibration garden
Also want the meshingangle of envoy garden awl ' less than pitch cone upward pressure angle α.Simultaneously, pitch cone angle δ ' is constant, and it is big that reference cone angle δ becomes, and reference cone separates with pitch cone after the displacement, forms △ δ＜0, but crossed axis angle sum ∑=δ
1'+δ
2' still remain unchanged.δ
1' be the bevel pinion pitch cone angle, δ
2' be the bevel gear wheel pitch cone angle.
The variation △ δ of cone angle is reflected on the end face virtual gear and is: the joint garden is constant, and the calibration garden changes, this and traditional angle correcting principle-Jie garden variation, and the calibration garden is constant to be to completely contradict.But still keep common negative drive characteristics: joint garden radius r
v' less than calibration garden radius r
v
The composition form of novel tooth form of the present invention has two kinds: radius increases (△ R) formula that contracts in (△ r) formula or the pitch cone radius.
The present invention will be illustrated more clearly in from the accompanying drawing of the following example.
The composition form of at first selected novel tooth form.Fig. 1 represents that radius increases (△ r) formula, Fig. 2 (△ R) formula of representing to contract in the pitch cone radius:
r
V1Be equivalent small gear calibration garden radius.
r
V1' be that the equivalent small gear saves the garden radius.
r
V2Be equivalent gearwheel calibration garden radius.
r
V2' be that the equivalent gearwheel saves the garden radius.
δ
1Be the bevel pinion reference cone angle.
δ
1' be the bevel pinion pitch cone angle.
δ
2Be the bevel gear wheel reference cone angle.
δ
2' be the bevel gear wheel pitch cone angle.
a
vBe no displacement centre distance, a
v=r
V1+ r
V2
a
v' be operating center distance, a
v'=r
V1'+r
V2'.
∑ is two crossed axis angles.
(1) (△ r) (radius increase) formula is when adopting negative value displacement, i.e. X
c, can increase calibration garden radius r at＜0 o'clock
v, and keep joint garden radius r
v' constant, its semidiameter is △ r=r
v'-r
v＜0.Correspondingly, joint garden awl meshingangle ' less than pitch cone upward pressure angle α.
invα′＝invα+2X
c（Z
v1+Z
v2）
-1·tgα
Z in the formula
V1Be the bevel pinion Equivalent number of teeth.
Z
V2Be the bevel gear wheel Equivalent number of teeth.
Simultaneously, it is big that reference cone angle δ becomes, and pitch cone angle δ ' is constant, and the relation of δ and δ ' is:
δ′-δ＝△δ＝arctg〔（1-Ka
-1）
tgδ〕＜0
Ka is the center distance change ratio in the formula, Ka=
=cos α/cos α '＜1
And crossed axis angle sum ∑=δ
1'+δ
2' still remain unchanged.
At this moment, the operating center distance a of virtual gear pair
v' constant.
a
v′＝r
v1′+r
v2′。Non-displacement centre distance a
v=r
V1+ r
V2Increase, then the difference of centre distance is △ a=a
v'-a
v＜0, calibration garden transverse module is corresponding slightly to be increased.
(2) (△ R) (contracting in the pitch cone radius) formula-be increases at radius on the basis of (△ r) formula, and two pairs of pitch cones and pitch cone are inwardly moved near the vertex of a cone 0 along the public tangent plane of pitch cone, and its amount of movement is △ R=R '-R
o'
△R＝△a·（tg△δ
1′+tg△δ
2′）
-1＜0
Then, on the basis of selected profile of tooth composition form, according to requirements such as various operating conditions and different gear teeth damage types, to four independent design parameter X
1, X
2, X
T1And X
T2Be optimized design.Engagement driving characteristic of the present invention is represented with Fig. 3,4:
Fig. 3 is the radial shift Closed Graph
The sliding curve of η-geometric ratio.
Curves of sliding such as u-.
Y-etc. bend strong curve.
1-does not have the undercut boundary.
2-does not have the interference boundary.
The 3-small gear does not have the pinnacle boundary.
4-transverse contact ratio ε
αBoundary.
Fig. 4 is the tangent modification Closed Graph
y
1=ky
2Be curved strong curves such as equivalent life
The 1-bevel pinion does not have pinnacle boundary Sa
1 *=0.25
The 2-bevel gear wheel does not have pinnacle boundary Sa
2 *=0.25
3-tangent modification and be zero boundary X
T1+ X
T2=0
The long tooth depth boundary of 4-
σ=-0.3～0.3 is the tooth depth coefficient of alteration
Again by Fig. 3,4 and figure in the series of characteristics curve can preferably form required low noise, high bearing capacity profile of tooth system application scheme.For example:
(1) bidentate is to transmission optimized design ε
r＞2
(2) curved strong optimal design y such as equivalent life
1=ky
2
(3) use X
t＞0 compensates because the transverse tooth thickness attenuate problem that X＜0 causes.
(4) little working pressure angle engagement design α '＜α
(5) according to one of preferred following feature of different gear teeth damage types:
The grade of a. anti-broken teeth ability is bent strong optimal design Y
FS1≈ Y
FS2
B. waiting of antiscuffing capacity slided than optimal design η
I1≈ η
I2
C. wearing and tearing such as the equivalent life of antiwear property optimal design U
1≈ U
2
D. the node place bidentate of pitting corrosion resistant performance is to the engagement optimal design
The characteristics that novel tooth form intensity is calculated are to use Z
BExpression novel tooth form and traditional profile of tooth strength ratio coefficient
Z
B＝φ（X
1·X
2）＝0.5～0.8
Cutting tooth process feature of the present invention is that its generating motion change gear ratio should be pressed reference cone angle δ and adjust, and pitch cone radius R is installed presses pitch cone apart from calculating with tooth bar (straight sword) cutter generate on pitch cone.
On the cutting equipment of existing processing " zero " deflection curve bevel gear, just can produce novel tooth form.
Advantage of the present invention is many (X of design variable independently1、X
2、X
t1And Xt2), but and have the profile of tooth application scheme processed that the multiple objective function optimal design satisfies low noise, high bearing capacity, stable working, select with different gear teeth damage types for various conditions of work. This is that existing paired bevel gears does not possess. The present invention can be applicable in the various accurate prior device of the industries such as automobile, lathe, instrument, can make with lathe and the cutter of existing processing zero deflection curve bevel gear pair, does not need to do in addition equipment frock, makes so be easy to promote.
Claims (8)
1, comprehensive displacement principle design and manufacturing are adopted in the comprehensive displacement of pitch cone and be the spiral bevel gear pair of negative value.Feature of the present invention is the comprehensive modification coefficient sum X on end face virtual gear pair
cBe negative value:
X
c=X
1+X
2+0.5(X
t1+X
t2)ctgα＜0
X in the formula
1, X
2Be respectively the overlap arc of bevel pinion and bevel gear wheel,
X
T1, X
T2Be respectively the tangent modification coefficient of bevel pinion and bevel gear wheel,
α is upward pressure angle, equivalent calibration garden.
2, spiral bevel gear pair according to claim 1 is characterized in that when carrying out the comprehensive displacement of negative value design, the meshingangle of joint garden awl ' and less than pitch cone upward pressure angle α
invα′＝invα+2X
c（Z
v1+Z
v2）
-1·tgα
Z in the formula
V1Be the bevel pinion Equivalent number of teeth;
Z
V2Be the bevel gear wheel Equivalent number of teeth.
Simultaneously, pitch cone angle δ ' is constant, and it is big that reference cone angle δ becomes, and the relation of δ ' and δ is:
δ′-δ＝△δ＝arctg〔（1-Ka
-1）tgδ〕＜0
Ka is that center distance change compares Ka=in the formula
=(cos α)/(cos α ')
Reference cone separates with pitch cone after the displacement, forms △ δ＜0
Crossed axis angle sum ∑=δ
1'+δ
2' still remain unchanged.
3, spiral bevel gear pair according to claim 1 and 2 is characterized in that the profile of tooth composition form can select radius and increase (△ R) formula that contracts in (△ r) formula or the pitch cone radius:
(△ r) Shi-Jie garden radius r
v' constant, calibration garden radius r
vIncrease, semidiameter is △ r=r
v'-r
v＜0.This moment the equivalent bevel gear pair operating center distance a
vConstant, a
v'=r
V1'+r
V2'.Non-displacement centre distance a
v=r
V1+ r
V2Increase, then the difference of centre distance is △ a=a
v'-a
v＜0, calibration garden transverse module is corresponding slightly to be increased.
(△ R) formula-on (△ r) formula basis two pairs of pitch cones and pitch cone are inwardly moved near vertex of a cone o along the public tangent plane of pitch cone, its amount of movement is △ R=R '-R
o'
△R＝△a（tg△δ
1′+tg△δ
2′）
-1＜0
4, spiral bevel gear pair according to claim 1 and 2 is characterized in that comprehensive modification coefficient and X
oIn comprise four independent design parameter X
1, X
2, X
T1And X
T2, can be optimized and design the profile of tooth system application scheme that satisfies low noise, high bearing capacity, select for use with different gear teeth damage types for various operating conditions.
ε when 1) bidentate is to transmission optimized design
r＞2
2) y during curved strong optimal design such as equivalent life
1=ky
2
3) use X
t＞0 compensates the transverse tooth thickness attenuate problem that X＜0 causes
α '＜α when 4) little working pressure angle engagement designs
5) according to one of preferred following feature of different damage types:
A) the curved strong optimal design Y of the grade of anti-broken teeth ability
FS1≈ Y
FS2
B) the sliding optimal design η of the geometric ratio of antiscuffing capacity
I1≈ η
I2
C) U such as optimal design such as equivalent life such as wearing and tearing such as grade of antiwear property
1≈ U
2
D) the node place bidentate of pitting corrosion resistant performance is to the engagement optimal design
5, spiral bevel gear pair according to claim 1 is characterized in that comprehensive modification coefficient and x
cIn comprise four independent design parameter x
1, x
2, x
T1And x
T2, can be optimized and design the profile of tooth system application scheme that satisfies low noise, high bearing capacity, select for use with different gear teeth damage types for various operating conditions.
ε when 1) bidentate is to transmission optimized design
r＞2
2) y during curved strong optimal design such as equivalent life
1=ky
2
3) use x
t＞0 compensates the transverse tooth thickness attenuate problem that X＜0 causes
α '＜α when 4) little working pressure angle engagement designs
5) according to one of preferred following feature of different damage types:
A) the curved strong optimal design Y of the grade of anti-broken teeth ability
FS1≈ Y
FS2
B) the sliding optimal design η of the geometric ratio of antiscuffing capacity
I1≈ η
I2
C) U such as optimal design such as equivalent life such as wearing and tearing such as grade of antiwear property
1≈ U
2
D) the node place bidentate of pitting corrosion resistant performance is to the engagement optimal design
6, spiral bevel gear pair according to claim 1 and 2 is characterized in that cutting tooth process is that its generating motion change gear ratio should be pressed reference cone angle δ and adjust, and pitch cone radius R is installed presses pitch cone apart from calculating with tooth bar (straight sword) cutter generate on pitch cone.
7, spiral bevel gear pair according to claim 3 is characterized in that cutting tooth process is that its generating motion change gear ratio should be pressed reference cone angle δ and adjust, and pitch cone radius R is installed presses pitch cone apart from calculating with tooth bar (straight sword) cutter generate on pitch cone.
8, spiral bevel gear pair according to claim 4 is characterized in that cutting tooth process is that its exhibition moves into the change gear ratio, should press reference cone angle δ and adjust, and pitch cone radius R is installed presses pitch cone apart from calculating with tooth bar (straight sword) cutter generate on pitch cone.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86104871 CN1009384B (en) | 1986-07-31 | 1986-07-31 | Conical gear pair with curved teeth with graduation cone synthetic position-changing coefficient sum being negative value |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86104871 CN1009384B (en) | 1986-07-31 | 1986-07-31 | Conical gear pair with curved teeth with graduation cone synthetic position-changing coefficient sum being negative value |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN86104871A true CN86104871A (en) | 1988-02-10 |
| CN1009384B CN1009384B (en) | 1990-08-29 |
Family
ID=4802632
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 86104871 Expired CN1009384B (en) | 1986-07-31 | 1986-07-31 | Conical gear pair with curved teeth with graduation cone synthetic position-changing coefficient sum being negative value |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1009384B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1073677C (en) * | 1997-05-30 | 2001-10-24 | 梁桂明 | Curve-bevel-teeth gear pair |
| CN100406781C (en) * | 2004-11-02 | 2008-07-30 | 梁桂明 | Durable noiseless pan-conic gear pair |
| CN101865272A (en) * | 2010-07-01 | 2010-10-20 | 西北工业大学 | Design method of spiral bevel gear |
-
1986
- 1986-07-31 CN CN 86104871 patent/CN1009384B/en not_active Expired
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1073677C (en) * | 1997-05-30 | 2001-10-24 | 梁桂明 | Curve-bevel-teeth gear pair |
| CN100406781C (en) * | 2004-11-02 | 2008-07-30 | 梁桂明 | Durable noiseless pan-conic gear pair |
| CN101865272A (en) * | 2010-07-01 | 2010-10-20 | 西北工业大学 | Design method of spiral bevel gear |
| CN101865272B (en) * | 2010-07-01 | 2013-02-20 | 西北工业大学 | Design method of spiral bevel gear |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1009384B (en) | 1990-08-29 |
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