CN1007003B - Paired bevel gears using the principle-positive sum of modifying coefficients - Google Patents
Paired bevel gears using the principle-positive sum of modifying coefficientsInfo
- Publication number
- CN1007003B CN1007003B CN 86104914 CN86104914A CN1007003B CN 1007003 B CN1007003 B CN 1007003B CN 86104914 CN86104914 CN 86104914 CN 86104914 A CN86104914 A CN 86104914A CN 1007003 B CN1007003 B CN 1007003B
- Authority
- CN
- China
- Prior art keywords
- cone
- pitch cone
- bevel gear
- radius
- formula
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
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- Gears, Cams (AREA)
- Gear Transmission (AREA)
Abstract
The present invention belongs to a mechanical transmission mechanism. The sum of the integrative displacement factors of the existing curve tooth cone gear pair is zero, so a small gear is weak, and the service life of the small gear is short. The gear pair of the present invention is designed by a principle that the sum of pitch cone integrative displacement factors is a positive value, the pitch cone is separated from a joint cone after displacement, an engaging angle is enlarged, and the gear pair can be manufactured by the existing machine tool. The present invention has the advantages of high strength, long service life, and easy popularization and manufacture. A radial displacement factor and a tangential displacement factor are optimally designed to form a new tooth shape system which is selected and used in various working conditions and different damage forms.
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 of the industrial rack cutter processing in existing countries in the world, the overwhelming majority are that employing modification coefficient sum is zero (x
1+ x
2=0) principle designs, " non-grade is moved apart from the equal strength spiral bevel gear " exception that the Soviet Union is only arranged, consult Н e р а в н о с м e щ e н н а я р а в н о п р о ч н а я к о н и ч e с к а я п e р e д а ч а с к р у г о в ы м и з у б ь я м й к а н д. т e х н. н а у к А. Б. О с и ц я н А В Т. п р о м. № 1,1977 г.Latter's radial shift sum x
1+ x
2＞0, tangent modification x
T1+ x
T2=0, as at the little or z of gear ratio u value
∑Value waits specified conditions under employing after a little while, can satisfy etc. to bend a strong requirement, and the number of teeth is less, but still restricted (z
1+ z
2〉=24).There are some shortcomings in the whole profile of tooth systems in above-mentioned various countries, and for example the gear pair volume is bigger, and small gear is sliding bigger, intensity relatively a little less than, more easy to wear.
When helixangle＜30 °, the bidentate that can not realize node area has influenced the further improvement of performances such as intensity, life-span to engagement driving or the like.
Task of the present invention is design a kind of high strength, the long lifetime, and the novel spiral bevel gear pair that just can produce with the existing cutting equipment in various countries.
Solution of the present invention is: adopt the comprehensive displacement of pitch cone and on the occasion of principle design make novel spiral bevel gear pair, make its comprehensive modification coefficient sum x on end face virtual gear pair
cFor on the occasion of.
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,
And x
1+ x
2＞0
x
T1, x
T2Be respectively the tangent modification coefficient of bevel pinion and bevel gear wheel, α is upward pressure angle, equivalent calibration garden.
Envoy garden awl meshingangle ' greater than upward pressure angle, calibration garden α, simultaneously, pitch cone angle σ ' is constant, reference cone angle σ diminishes, reference cone separates with pitch cone after the displacement, forms △ δ=δ '-δ＞0, and crossed axis angle sum ∑=δ
1'+δ
2' still remain unchanged.
The variation △ δ of cone angle is reflected on the end face virtual gear and is: the joint garden is constant, the calibration garden changes this and traditional angle correcting principle: the joint garden changes, the calibration garden is constant just opposite, but still is keeping common positive drive feature: joint garden radius r
v' greater than calibration garden radius r
v
The composition form of novel tooth form of the present invention has two kinds: radius reduces (△ r) formula or pitch cone radius extends out (△ R) formula.
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 reduces (△ r) formula, Fig. 2 represents that pitch cone radius extends out (△ R) formula:
r
v-calibration garden radius, r
v'-Jie garden radius,
δ-reference cone angle, δ '-pitch cone angle,
a
v-no displacement centre distance, a
v=r
V1+ r
V2,
a
v'-operating center distance, a
v'=r
V1'+r
V2',
∑-two crossed axis angle.
1) (△ r) (radius reduces) formula
When adopting on the occasion of displacement, i.e. x
c, can reduce 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, the meshingangle of joint garden awl ' greater than upward pressure angle, calibration garden α.
invα′＝invα+2x
c（z
v1+z
v2）
-1·tgα
Z in the formula
V1Be the small gear Equivalent number of teeth
z
V2Be the gearwheel Equivalent number of teeth
Simultaneously, reference cone angle δ diminishes, and pitch cone angle δ ' is constant, and the relation of δ ' and δ is:
δ′-δ＝△δ＝arctg〔（1-ka
-1）tgδ〕＞0
K is the center distance change ratio in the formula, k
a=(a
v')/(a
v)
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
V2Reduce, then the difference △ a=a of centre distance
v'-a
v＞0, calibration garden transverse module is corresponding slightly to be reduced.
2) (△ R) (pitch cone radius extends out) formula-
Be to reduce (△ at radius
r) on the basis of formula, with two pairs of pitch cones and pitch cone along the public tangent plane of pitch cone outwards (away from vertex of a cone o) move.Its amount of movement is △ R=R '-R
0'
△R＝△a·（tg△δ
1′+tg△δ
2′）
-1＞0
Then, on the basis of selected profile of tooth composition form, according to different requirements such as user job condition and gear destruction forms, to four displacement parameter x
1, x
2, x
T1, x
T2Be optimized design, its engagement driving characteristic is represented with Fig. 3, Fig. 4:
Fig. 3 is the radial shift Closed Graph.
η-wait to slide and compare curve
Curves of sliding such as v-
Y-etc. bend strong curve
δ
2-node area bidentate is to the meshing zone
1 with 4-do not have the interference boundary line
2-does not have the undercut boundary line
3-zero displacement and boundary line
The 5-small gear does not have the boundary line, pinnacle
6-transverse contact ratio ε
α=1.1 boundary lines
Fig. 4 is tangent modification Closed Graph y
1=ky
2Be curved strong curves such as equivalent life.
The 1-pinion gear teeth is risen s
* α 1=0.25 boundary
2-gearwheel addendum s
* α 2=0.25 boundary
3-tangent modification and be zero x
T1+ x
T2=0 boundary
The long tooth depth restriction of 4-tooth depth coefficient of alteration σ=-0.2～-0.3
Again by Fig. 3,4 and figure in the series of characteristics curve can form required profile of tooth system application scheme.
During anti-broken teeth optimal design, select the anti-broken teeth of Fig. 5 (y) to show Closed Graph.
y
FS1≈y
FS2
During anti-spot corrosion optimal design, select the anti-spot corrosion of Fig. 6 to show Closed Graph.
Node c district biconjugate tooth engagement (ε
α)
c＞2
During anti-bonding optimal design, select Fig. 7 anti-bonding (η) Closed Graph.
η
i1≈η
i2
When resistance to wearing optimal design, select Fig. 8 (u) Closed Graph of resistance to wearing.
u
1≈u
2
The characteristics that novel tooth form intensity is calculated are to use z
Expression 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 cutter of existing processing " zero " deflection curve bevel gear and lathe, just can produce novel tooth form.
The present invention is not limited to embodiment, and its protection domain is defined by the claims.
Advantage of the present invention is to have than each industrial spiral bevel gear of the existing world more to much more excellent engaged transmission performance, higher, the life of intensity. Can keep the gear pair crossed axis angle not change, the novel tooth form design variable is many, and has multiple objective function and can select for optimal design, realizes by computer or manual calculation. Under same volume conditions, the large and small gear of gear pair of the present invention is increasing tooth thickness simultaneously, and its bending strength and antiwear property are greatly strengthened. Under the equality strength condition, can reduce the volume of bevel gear pair, can also replace the high-quality steel with common iron. The angle of engagement can increase, and has improved the tooth root contact strength; Slip ratio reduces, and has improved antiwear property and antiscuffing capacity. The present invention can be applicable in the mechanical driving device of the industries such as heavy type, mine metallurgy, oil drilling, tank, rolling stock, sailing boat, engineering machinery. Owing to use the lathe of existing Processing Curve bevel gear and cutter just can make, do not need to do in addition equipment frock, can be easy to promote.
Claims (5)
1, the comprehensive displacement of pitch cone and be on the occasion of the spiral bevel gear pair, adopt comprehensive displacement principle design and manufacturing, feature of the present invention is the comprehensive modification coefficient sum X on end face virtual gear pair
oFor on the occasion of:
X
o=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, and X
1+ X
2＞0,
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 on the occasion of comprehensive displacement design, the meshingangle of joint garden awl ' greater than upward pressure angle, calibration garden 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,
Pitch cone angle δ ' is constant simultaneously, and reference cone angle δ diminishes, 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= (av′)/(av) = (cosα)/(cosα′)
Pitch cone separates with pitch cone after the displacement, forms △ δ＞0, crossed axis angle sum ∑=δ
1'+δ
2' still remain unchanged.
3,, it is characterized in that the profile of tooth composition form can select that radius reduces (△ r) formula or pitch cone radius extends out (△ R) formula according to claim 1 and 2 described spiral bevel gear pairs:
(△ r) Shi-Jie garden radius r
v' constant, calibration garden radius r
vReduce, semidiameter is △ r=r
v'-r
v＞0.At this moment, the operating center distance a of virtual gear pair
v' constant, a
v' by little, bevel gear wheel radius and (r
V1'+r
V2') constitute, by calibration garden radius and (r
1+ r
2) to constitute non-displacement centre distance be a
v, the difference △ a=a of centre distance then
v'-a
v＞0, calibration garden transverse module is corresponding slightly to be reduced;
(△ R) formula-on (△ r) formula basis, two pairs of pitch cones and pitch cone are moved a segment distance △ R=R '-R along the public tangent plane of pitch cone outside (away from the vertex of a cone 0)
0'
△R＝△a（tg△δ
1′+tg△δ
2′）
-1＞0
4, the manufacture method of claim 1 or 2 described spiral bevel gear pairs is characterized in that cutting tooth process is tooth bar (straight sword) cutter generate on pitch cone, and 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.
5, the manufacture method of the described spiral bevel gear pair of 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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86104914 CN1007003B (en) | 1986-07-31 | 1986-07-31 | Paired bevel gears using the principle-positive sum of modifying coefficients |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86104914 CN1007003B (en) | 1986-07-31 | 1986-07-31 | Paired bevel gears using the principle-positive sum of modifying coefficients |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN86104914A CN86104914A (en) | 1987-10-28 |
| CN1007003B true CN1007003B (en) | 1990-02-28 |
Family
ID=4802647
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 86104914 Expired CN1007003B (en) | 1986-07-31 | 1986-07-31 | Paired bevel gears using the principle-positive sum of modifying coefficients |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1007003B (en) |
Families Citing this family (2)
| 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 |
-
1986
- 1986-07-31 CN CN 86104914 patent/CN1007003B/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| CN86104914A (en) | 1987-10-28 |
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