GB/T 11367-1989 Calculation method for the gluing load capacity of bevel gears
Some standard content:
National Standard of the People's Republic of China
Methods for the calculation of scuffing loadcapacity for bevel gears
1 Subject content and scope of application
This standard specifies the calculation principle of the anti-scuffing capacity of bevel gears. This standard is applicable to the transmission of spur, helical and spiral bevel gears (including zero-degree bevel gears) made of steel. GB 11367—89
This standard is applicable to the scuffing damage (thermal scuffing) caused by the rupture of the lubricating oil film due to the high temperature of the tooth surface caused by the tooth surface load and sliding speed.
2 Reference standards
GB1006288 Calculation method of scuffing loadcapacity for bevel gearsSY2691—84 Determination method of lubricant load capacity 3 Reliability and safety factor
When designing gears, different use fields have different reliability requirements for gears. The reliability requirements of gear work are determined by comprehensive consideration of factors such as its importance, work requirements and maintenance difficulty. At present, reliability theory has begun to be used in mechanical design, and it is shown that only the safety factor does not fully reflect the reliability level. However, there is still a lack of necessary data to treat each design parameter as a random variable. Therefore, this standard still treats the design parameter as a determined value, and still uses the safety factor or tooth surface temperature as a criterion, and considers the reliability requirements when selecting the safety factor. When the reliability requirements of the product are high (such as aviation gears), the safety factor should be taken as a higher value, otherwise it should be taken as a lower value. In addition, when selecting the safety factor, the reliability of your calculation should also be considered. When the original parameters and additional variables used in the calculation (such as load conditions, manufacturing errors, material and surface treatment quality and performance, lubrication conditions, etc.) are more reliable, the safety factor can be obtained. On the contrary, it should be larger.
The determination of the safety factor should be based on user requirements or determined by the design and manufacturing department in consultation with the user. 4 Main codes
The codes, meanings and units of the main numbers in this standard are shown in Table 1 Table 1 Main codes, meanings and units
Equivalent cylindrical gear center distance
Effective tooth width for contact strength calculation
Effective tooth width for bonding load capacity calculation
Average value of total stiffness per unit tooth width of gear teeth (meshing stiffness) Maximum stiffness per unit tooth width of a pair of gear teeth (single pair of teeth stiffness) Approval by the State Administration of Technology Supervision on May 6, 1989
N/(mm 'μm)
N/(mm*μm)
Implementation on January 1, 1990
dei te
tmradra
dul da
outden
tahidwh2
d ii.dehn?
ctnidon?
S eani
tooth trimming amount
effective trimming amount
GB 11367-89
Continued Table 1
Diameter of the large end of the small wheel and the large wheel
Diameter of the pitch circle at the midpoint of the tooth width of the small wheel and the large wheelEquivalent cylindrical gear pitch circle diameter of the small wheel and the large wheelEquivalent cylindrical gear tooth tip circle diameter of the small wheel and the large wheelEquivalent circle of the gear normal cutting surfaceTrue diameter of the top circle of the tooth of the small wheel and the large wheelEquivalent circle of the gear normal cutting surfaceBase circle diameter of the small wheel and the large wheelEquivalent cylindrical gear normal wearing surface base circle diameter of the small wheel and the large wheelEquivalent cylindrical gear normal wearing surface pitch circle diameterElastic modulus
Comprehensive elastic modulus
Nominal tangential force on the pitch circle at the midpoint of the tooth widthEquivalent cylindrical gear end face beep line length
Use coefficient
Tooth load distribution coefficient for calculation of bonding load capacityCalculation of bonding load capacity Tooth load distribution coefficient
Arithmetic mean deviation of the wheel
Calculation safety factor of bonding load capacity
Minimum safety factor of bonding load capacity
Tooth ratio
Equivalent cylindrical gear tooth ratio
Tooth width midpoint indexing threshold Peripheral speed
Sum of the speeds of the two wheels along the tangent direction of the tooth profile at the meshing point Unit tooth width load
Geometric coefficient of the small wheel tooth E point
Tooth edge repair coefficient
Heat flash coefficient
Meshing impact coefficient
Lubrication coefficient
Material welding coefficient
Pressure angle coefficient
Overlap coefficient
KNc.75.s.3.mu.5 .mim
Besiat
Basic formula
Number of teeth of small wheel and man-wheel
GB 11367
Continued 1
Number of teeth of crown cylindrical gear of small wheel and man-wheelNumber of teeth of normal section of equivalent cylindrical gear of small wheel and man-wheelNormal tooth profile angle
Positive angle of end face of equivalent cylindrical gear
Helix angle of pitch circle at midpoint of tooth width
Helix angle of base circle of equivalent cylindrical gear
Tooth contact of equivalent cylindrical gear of small wheel
Tooth tip overlap of equivalent cylindrical gear of large wheel
End face overlap of equivalent cylindrical gear
End face overlap of equivalent cylindrical gear on normal sectionEquivalent cylindrical gear longitudinal overlap
Total overlap of equivalent cylindrical gear
Lubricating oil in working Dynamic viscosity at working temperature Instantaneous temperature rise at meshing point
Assuming that the load is all applied to the pinion tooth top E pointIntegral average temperature rise along the meshing line
Integral temperature
Bond temperature
Main body temperature
RunyoushanKinematic viscosity
Poisson's ratio
Average friction coefficient
Integrated radius of curvature at meshing point
The tooth surface temperature as a criterion can be determined by any appropriate method in principle, and then compared with the tooth surface temperature determined under the same conditions by the test results or statistical results when bonding occurs to evaluate the bonding load capacity of the designed gear. This standard uses the sum of the integral average value of the weighted instantaneous temperature rise of each meshing point as the calculated tooth surface temperature (integral temperature).
Taking into account the different materials and surface treatments of designed gears, this standard uses the modified specimen tooth surface integral temperature as the limiting tooth surface temperature (bonding temperature)
5. 1 Calculation criteria
The integral temperature 8ml should meet:
GB 11367-89
or the calculated safety factor S of the bonding load capacity. It should satisfy: Se a SBamin
In the above formula: mm-integral temperature, ℃, see Article 5.2: Ssunt
bonding temperature, ℃, see Article 5. 3;
Calculation safety factor of bonding bearing capacity, see Article 5.4; Sh
（2）
Minimum safety factor of bonding bearing capacity, selection principle see Chapter 3, when no data is available, refer to Appendix S puut
5.2 Integral temperature 6.
Integral temperature is determined by the following formula:
Om=Om+COin
In the formula: 2
（3）
The weighted number is the coefficient introduced to consider the different degrees of influence of the integrated average temperature rise and the body temperature u on the bonding damage. The test results show that the following is usually taken as approximation: C2 = 1. 5
6%——body temperature, see 5.2. 8——integral average temperature rise C, see 5.2.2. 5.2.1 Body humidity gm
The body temperature m refers to the tooth surface temperature when it is about to enter meshing. The body temperature 3M can be determined by any suitable accurate method (such as thermal network method, accurate measurement, etc.). The following approximation method can also ensure the necessary calculation accuracy.
Ou=(+Ciat)X
Wherein: 0-
-working oil temperature, ℃
coefficient, the average value is taken according to the test results: C, -0.7; c.
-integral average temperature rise, ℃, see 5.2.2; OHlain
X, —lubrication coefficient, is to consider the effect of lubrication mode on heat transfer, obtained from the test: oil bath lubrication: X=1.0;
oil injection lubrication: Xg-1.2,
5.2.2 The integral average temperature rise 8man
The integral average temperature rise 8m refers to the integral average value of the instantaneous temperature rise of 8% at each meshing point on the tooth surface along the meshing line, that is: Gnair
wherein a
equivalent cylindrical gear end face meshing line length, tni In this method, the integral average temperature rise 6nin can be calculated according to the following simplified formula, Bnain = CneXe
SE = pmXrXX
（4）
wherein: E—
CB 11367—89
Assuming that the load is all acting on the instantaneous temperature rise of point E of the pinion equivalent cylindrical gear tooth, C:X, overlap coefficient, see 6.9;
average friction coefficient, see 6.3!
- thermal flash coefficient, K·N-0.15, s.·n1-0.5mm, see 6.1; geometric coefficient of the tooth tip E point of the small wheel equivalent cylindrical gear, see 6.5; unit tooth width load, N/Im, see 6.1; Uui-circumferential speed of the dividing circle at the midpoint of the tooth width, m/s: a.
-center distance of the equivalent circular gear (at the midpoint of the tooth width), mm; X.-meshing impact coefficient, see 6.6; tooth tip trim coefficient, see 6.7;
-pressure angle coefficient, see 6.8.
5.3 Gluing temperature 8sml
Gluing temperature 6sn refers to the limit integral temperature when the tooth surface fails due to gluing, which is usually obtained based on test results. Tests have shown that for a "oil-material" combination, Bsin is a constant and does not change with operating conditions. The gluing temperature 6ut is calculated as follows:
Cu = Am+ C2.XwDln
Where: C——weighting factor, see explanation of formula (3); Xw
Material welding coefficient, see 6.10:
Body temperature and integral average temperature rise of the test gear, C℃, see 6.11. 5.4 Safety factor Se
.· (8)
Calculation of gluing load-bearing capacity Safety factor S: The ratio of gluing temperature to integral temperature, used to reflect the safety margin of the gear's anti-gluing capacity.
6 Related parameters and coefficients
6. 1 Unit tooth width load Wmr
Unit tooth width load W is calculated by the following formula:
Wam= KAKmKuK
Effective tooth width for calculation of bonding load capacity, take hR=bm, bm see GB10062: Wu Zhong b
Nominal tangential force on the pitch circle at the midpoint of the tooth width, N, see GB10062 Article 7.1 K;——Service factor, see GB 10062 Article 7.2; (9
（10）
Tooth load distribution coefficient for calculation of bonding load capacity, take KmKK see GB10062 Article 7.4; Kea
Tooth load distribution coefficient for calculation of bonding load capacity, take Km=Kl, K see GB10062 Article 7.5; Helix coefficient, see 6.2
6.2 Helix coefficient K
The helix coefficient K is a correction factor introduced to take into account the tendency of gluing to increase when the total overlap e increases. Its value is obtained from the test and can be obtained from Figure 1 drawn based on the test data. The curve in Figure 1 can be approximately expressed by the following formula: When E.2:
2 <, when e < 3.5:
When E 3.5:
6.3 Average friction coefficient
GB 11367-89
Ker = 1
Kur = 1 + 0.2 V(ey - 2)(5 - e..)KBy = 1. 3
Helix coefficient KBr
Average friction coefficient refers to the average friction coefficient at each meshing point of the tooth profile, and the friction coefficient at the node can be approximated. Ftm=0.045
Where: Xr=3. 8(R,/d.1)J.23
Roughness coefficient:
FKAKpKj 0.2
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Arithmetic mean deviation of tooth profile along the tooth profile direction, im, here take the average value of two wheels: R,=0.5(R, +Ra2)
Next—Dynamic viscosity of lubricating oil at working temperature, mPa·s; for ten commonly used gear oils, it can be approximately determined by the following formula: ng =p - U4a(40'C/0)2. s
Wherein: 0-10°N/mm2
The sum of the speeds of the two wheels along the tooth tangent direction at the node, m/s, is taken as: Vsc-2umsinan
The circumferential speed of the pitch circle at the midpoint of the tooth width, m/s; if m50m/s, then take V=50m/s
Equivalent cylindrical gear end face positive angle;
d—The comprehensive curvature radius of the two tooth corridors at the meshing point, mm, is taken as: Prel
Equivalent cylindrical gear tooth number ratio:
(u, + 1ya cosp.
:(12）
(17）
3.b——Equivalent cylindrical gear base circle helix angle). 6.4 Thermal flash coefficient XM
GB 1136789
The thermal flash coefficient X is a coefficient that takes into account the influence of material properties (elastic modulus E, Poisson's ratio u, thermal contact coefficient BM) and the speed of the two wheels along the tangent direction of the tooth profile at the meshing point.
Buiu5+BM2
When the elastic modulus, Poisson's ratio and thermal contact coefficient of the large and small wheels are the same, formula (19) can be simplified to the following formula: XM
Wherein: The thermal contact coefficient By is:
(1 - u°)u. 2 BM
. (20)
(21)
For martensitic steel, the thermal conductivity is in the range of 41 to 52 N/(K·s), the specific heat capacity C is about 4.87X10°J/(kg·K), and the density p is about 7.8×10kg/m. The average value of the thermal contact coefficient is: B = 13. 6 N/(mtm + sc.5. K) (22
For commonly used steel gear pairs, E=206000N/mm2, u=0.3, Bm=13.6N/(mm·sm.5.K), the thermal flash coefficient can be taken as:
Xm= 50.0K -NF.s0.5.m 0.5 -mm6.5Pinwheel tooth top geometry coefficient X
The He coefficient XB is a coefficient that considers the influence of the geometric parameters at the pinion equivalent cylindrical gear tooth top E point on the Hertz stress and sliding speed.
XBe = 0. 5 V u
Where: Pr=0.5 Vd.,-db
Pes =a, sinau——Pe:
det equivalent cylindrical gear tooth top circle diameter of small wheel, mm; dtt—equivalent cylindrical gear base circle diameter of small wheel, mm. 6.6 Engagement impact coefficient Xg
(pE·Pea)2E
（24)
（25）
（26)
engagement impact coefficient X. It is a coefficient that takes into account the influence of the engagement impact load of the driven wheel tooth top with a large sliding speed, and the value is taken according to Table 2. Drive mode
Small wheel drives large wheel
Large wheel drives small wheel
CB 11367-89
Table 2 Engagement impact coefficient X.
Tooth overlap &
Ey ssl, 5en)
1. 5e10:
Test gear body temperature and integrated average temperature rise, C℃, see 6.11. 5.4 Safety factor Se
.· (8)
Calculation of bonding load capacity Safety factor S: The ratio of bonding temperature to integrated temperature, used to reflect the safety margin of the gear's anti-bonding capacity.
6 Related parameters and coefficients
6.1 Unit tooth width load Wmr
Unit tooth width load W is calculated by the following formula:
Wam= KAKmKuK
Effective tooth width for bonding load capacity calculation, take hR=bm, bm see GB10062: Wu Zhong b
Nominal tangential force on the pitch circle at the midpoint of the tooth width, N, see GB10062 Article 7.1 K;——Service factor, see GB 10062 Article 7.2; (9
(10)
The tooth load distribution coefficient for the calculation of the bonding bearing capacity is KmKK, see Article 7.4 of GB10062; Kea
The tooth load distribution coefficient for the calculation of the bonding bearing capacity is Km=Kl, K see Article 7.5 of GB10062; helix coefficient, see Article 6.2.
6.2 Helix coefficient K
The helix coefficient K is a correction coefficient introduced to take into account the tendency of bonding to increase when the total overlap e increases. Its value is obtained from the test. It can be obtained from Figure 1 drawn based on the test data. The curve in Figure 1 can be approximately expressed by the following formula: When E.2:
2 <, e < 3.5:
E 3.5:
6.3 Average friction coefficient
GB 11367-89
Ker = 1
Kur = 1 + 0. 2 V(ey - 2)(5 - e..)KBy = 1. 3
Helical coefficient KBr
The average friction coefficient refers to the average value of the friction coefficient at each meshing point of the tooth profile, and the friction coefficient at the node can be approximated. Ftm=0.045
Where: Xr=3. 8(R,/d.1)J.23
Roughness coefficient:
FKAKpKj 0.2
Casa.baz:red!
The arithmetic mean deviation of the tooth profile along the tooth profile direction, im, here take the average value of the two wheels: R,=0.5(R, +Ra2)
next—dynamic viscosity of lubricating oil at working temperature, mPa·s; for ten commonly used gear oils, it can be approximately determined by the following formula: ng =p - U4a(40'C/0)2. s
where: 0-10°N/mm2
the sum of the speeds of the two wheels along the tooth tangent direction at the node, m/s, the value is: Vsc-2umsinan
circumferential speed of the dividing circle at the midpoint of the tooth width, m/s; if m50m/s, then V=50m/s
equivalent cylindrical gear end face positive angle;
d—the comprehensive curvature radius of the two tooth corridors at the meshing point, mm, the value at the node is: Prel
equivalent cylindrical gear tooth number ratio:
(u, + 1ya cosp.
:(12）
(17）
3.b——Equivalent cylindrical gear base circle helix angle). 6.4 Thermal flash coefficient XM
GB 1136789
The thermal flash coefficient X is a coefficient that takes into account the influence of material properties (elastic modulus E, Poisson's ratio u, thermal contact coefficient BM) and the speed of the two wheels along the tangent direction of the tooth profile at the meshing point.
Buiu5+BM2
When the elastic modulus, Poisson's ratio and thermal contact coefficient of the large and small wheels are the same, formula (19) can be simplified to the following formula: XM
Wherein: The thermal contact coefficient By is:
(1 - u°)u. 2 BM
. (20)
(21)
For martensitic steel, the thermal conductivity is in the range of 41 to 52 N/(K·s), the specific heat capacity C is about 4.87X10°J/(kg·K), and the density p is about 7.8×10kg/m. The average value of the thermal contact coefficient is: B = 13. 6 N/(mtm + sc.5. K) (22
For commonly used steel gear pairs, E=206000N/mm2, u=0.3, Bm=13.6N/(mm·sm.5.K), the thermal flash coefficient can be taken as:
Xm= 50.0K -NF.s0.5.m 0.5 -mm6.5Pinwheel tooth top geometry coefficient X
The He coefficient XB is a coefficient that considers the influence of the geometric parameters at the pinion equivalent cylindrical gear tooth top E point on the Hertz stress and sliding speed.
XBe = 0. 5 V u
Where: Pr=0.5 Vd.,-db
Pes =a, sinau——Pe:
det equivalent cylindrical gear tooth top circle diameter of small wheel, mm; dtt—equivalent cylindrical gear base circle diameter of small wheel, mm. 6.6 Engagement impact coefficient Xg
(pE·Pea)2E
（24)
（25）
（26)
engagement impact coefficient X. It is a coefficient that takes into account the influence of the engagement impact load of the driven wheel tooth top with a large sliding speed, and the value is taken according to Table 2. Drive mode
Small wheel drives large wheel
Large wheel drives small wheel
CB 11367-89
Table 2 Engagement impact coefficient X.
Tooth overlap &
Ey ssl, 5en)
1. 5e10:
Test gear body temperature and integrated average temperature rise, C℃, see 6.11. 5.4 Safety factor Se
.· (8)
Calculation of bonding load capacity Safety factor S: The ratio of bonding temperature to integrated temperature, used to reflect the safety margin of the gear's anti-bonding capacity.
6 Related parameters and coefficients
6.1 Unit tooth width load Wmr
Unit tooth width load W is calculated by the following formula:
Wam= KAKmKuK
Effective tooth width for bonding load capacity calculation, take hR=bm, bm see GB10062: Wu Zhong b
Nominal tangential force on the pitch circle at the midpoint of the tooth width, N, see GB10062 Article 7.1 K;——Service factor, see GB 10062 Article 7.2; (9
(10)
The tooth load distribution coefficient for the calculation of the bonding bearing capacity is KmKK, see Article 7.4 of GB10062; Kea
The tooth load distribution coefficient for the calculation of the bonding bearing capacity is Km=Kl, K see Article 7.5 of GB10062; helix coefficient, see Article 6.2.
6.2 Helix coefficient K
The helix coefficient K is a correction coefficient introduced to take into account the tendency of bonding to increase when the total overlap e increases. Its value is obtained from the test. It can be obtained from Figure 1 drawn based on the test data. The curve in Figure 1 can be approximately expressed by the following formula: When E.2:
2 <, e < 3.5:
E 3.5:
6.3 Average friction coefficient
GB 11367-89
Ker = 1
Kur = 1 + 0. 2 V(ey - 2)(5 - e..)KBy = 1. 3
Helical coefficient KBr
The average friction coefficient refers to the average value of the friction coefficient at each meshing point of the tooth profile, and the friction coefficient at the node can be approximated. Ftm=0.045
Where: Xr=3. 8(R,/d.1)J.23
Roughness coefficient:
FKAKpKj 0.2
Casa.baz:red!
The arithmetic mean deviation of the tooth profile along the tooth profile direction, im, here take the average value of the two wheels: R,=0.5(R, +Ra2)
next—dynamic viscosity of lubricating oil at working temperature, mPa·s; for ten commonly used gear oils, it can be approximately determined by the following formula: ng =p - U4a(40'C/0)2. s
where: 0-10°N/mm2
the sum of the speeds of the two wheels along the tooth tangent direction at the node, m/s, the value is: Vsc-2umsinan
circumferential speed of the dividing circle at the midpoint of the tooth width, m/s; if m50m/s, then V=50m/s
equivalent cylindrical gear end face positive angle;
d—the comprehensive curvature radius of the two tooth corridors at the meshing point, mm, the value at the node is: Prel
equivalent cylindrical gear tooth number ratio:
(u, + 1ya cosp.
:(12）
(17）
3.b——Equivalent cylindrical gear base circle helix angle). 6.4 Thermal flash coefficient XM
GB 1136789
The thermal flash coefficient X is a coefficient that takes into account the influence of material properties (elastic modulus E, Poisson's ratio u, thermal contact coefficient BM) and the speed of the two wheels along the tangent direction of the tooth profile at the meshing point.
Buiu5+BM2
When the elastic modulus, Poisson's ratio and thermal contact coefficient of the large and small wheels are the same, formula (19) can be simplified to the following formula: XM
Wherein: The thermal contact coefficient By is:
(1 - u°)u. 2 BM
. (20)
(21)
For martensitic steel, the thermal conductivity is in the range of 41 to 52 N/(K·s), the specific heat capacity C is about 4.87X10°J/(kg·K), and the density p is about 7.8×10kg/m. The average value of the thermal contact coefficient is: B = 13. 6 N/(mtm + sc.5. K) (22
For commonly used steel gear pairs, E=206000N/mm2, u=0.3, Bm=13.6N/(mm·sm.5.K), the thermal flash coefficient can be taken as:
Xm= 50.0K -NF.s0.5.m 0.5 -mm6.5Pinwheel tooth top geometry coefficient X
The He coefficient XB is a coefficient that considers the influence of the geometric parameters at the pinion equivalent cylindrical gear tooth top E point on the Hertz stress and sliding speed.
XBe = 0. 5 V u
Where: Pr=0.5 Vd.,-db
Pes =a, sinau——Pe:
det equivalent cylindrical gear tooth top circle diameter of small wheel, mm; dtt—equivalent cylindrical gear base circle diameter of small wheel, mm. 6.6 Engagement impact coefficient Xg
(pE·Pea)2E
（24)
（25）
（26)
engagement impact coefficient X. It is a coefficient that takes into account the influence of the engagement impact load of the driven wheel tooth top with a large sliding speed, and the value is taken according to Table 2. Drive mode
Small wheel drives large wheel
Large wheel drives small wheel
CB 11367-89
Table 2 Engagement impact coefficient X.
Tooth overlap &
Ey ssl, 5en)
1. 5e0-10°N/mm2
The sum of the speeds of the two wheels along the tooth tangent direction at the node, m/s, is taken as: Vsc-2umsinan
The circumferential speed of the pitch circle at the midpoint of the tooth width, m/s; if m50m/s, then take V=50m/s
Equivalent cylindrical gear end face positive angle;
d—The comprehensive curvature radius of the two tooth corridors at the meshing point, mm, at the node is taken as: Prel
Equivalent cylindrical gear tooth number ratio:
(u, + 1ya cosp.
:(12）
(17）
3.b——Equivalent cylindrical gear base circle helix angle). 6.4 Thermal flash coefficient XM
GB 1136789
The thermal flash coefficient X is a coefficient that takes into account the influence of material properties (elastic modulus E, Poisson's ratio u, thermal contact coefficient BM) and the speed of the two wheels along the tangent direction of the tooth profile at the meshing point.
Buiu5+BM2
When the elastic modulus, Poisson's ratio and thermal contact coefficient of the large and small wheels are the same, formula (19) can be simplified to the following formula: XM
Wherein: The thermal contact coefficient By is:
(1 - u°)u. 2 BM
. (20)
(21)
For martensitic steel, the thermal conductivity is in the range of 41 to 52 N/(K·s), the specific heat capacity C is about 4.87X10°J/(kg·K), and the density p is about 7.8×10kg/m. The average value of the thermal contact coefficient is: B = 13. 6 N/(mtm + sc.5. K) (22
For commonly used steel gear pairs, E=206000N/mm2, u=0.3, Bm=13.6N/(mm·sm.5.K), the thermal flash coefficient can be taken as:
Xm= 50.0K -NF.s0.5.m 0.5 -mm6.5Pinwheel tooth top geometry coefficient X
The He coefficient XB is a coefficient that considers the influence of the geometric parameters at the pinion equivalent cylindrical gear tooth top E point on the Hertz stress and sliding speed.
XBe = 0. 5 V u
Where: Pr=0.5 Vd.,-db
Pes =a, sinau——Pe:
det equivalent cylindrical gear tooth top circle diameter of small wheel, mm; dtt—equivalent cylindrical gear base circle diameter of small wheel, mm. 6.6 Engagement impact coefficient Xg
(pE·Pea)2E
（24)
（25）
（26)
engagement impact coefficient X. It is a coefficient that takes into account the influence of the engagement impact load of the driven wheel tooth top with a large sliding speed, and the value is taken according to Table 2. Drive mode
Small wheel drives large wheel
Large wheel drives small wheel
CB 11367-89
Table 2 Engagement impact coefficient X.
Tooth overlap &
Ey ssl, 5en)
1. 5e0-10°N/mm2
The sum of the speeds of the two wheels along the tooth tangent direction at the node, m/s, is taken as: Vsc-2umsinan
The circumferential speed of the pitch circle at the midpoint of the tooth width, m/s; if m50m/s, then take V=50m/s
Equivalent cylindrical gear end face positive angle;
d—The comprehensive curvature radius of the two tooth corridors at the meshing point, mm, at the node is taken as: Prel
Equivalent cylindrical gear tooth number ratio:
(u, + 1ya cosp.
:(12）
(17）
3.b——Equivalent cylindrical gear base circle helix angle). 6.4 Thermal flash coefficient XM
GB 1136789
The thermal flash coefficient X is a coefficient that takes into account the influence of material properties (elastic modulus E, Poisson's ratio u, thermal contact coefficient BM) and the speed of the two wheels along the tangent direction of the tooth profile at the meshing point.
Buiu5+BM2
When the elastic modulus, Poisson's ratio and thermal contact coefficient of the large and small wheels are the same, formula (19) can be simplified to the following formula: XM
Wherein: The thermal contact coefficient By is:
(1 - u°)u. 2 BM
. (20)
(21)
For martensitic steel, the thermal conductivity is in the range of 41 to 52 N/(K·s), the specific heat capacity C is about 4.87X10°J/(kg·K), and the density p is about 7.8×10kg/m. The average value of the thermal contact coefficient is: B = 13. 6 N/(mtm + sc.5. K) (22
For commonly used steel gear pairs, E=206000N/mm2, u=0.3, Bm=13.6N/(mm·sm.5.K), the thermal flash coefficient can be taken as:
Xm= 50.0K -NF.s0.5.m 0.5 -mm6.5Pinwheel tooth top geometry coefficient X
The He coefficient XB is a coefficient that considers the influence of the geometric parameters at the pinion equivalent cylindrical gear tooth top E point on the Hertz stress and sliding speed.
XBe = 0. 5 V u
Where: Pr=0.5 Vd.,-db
Pes =a, sinau——Pe:
det equivalent cylindrical gear tooth top circle diameter of small wheel, mm; dtt—equivalent cylindrical gear base circle diameter of small wheel, mm. 6.6 Engagement impact coefficient Xg
(pE·Pea)2E
（24)
（25）
（26)
engagement impact coefficient X. It is a coefficient that takes into account the influence of the engagement impact load of the driven wheel tooth top with a large sliding speed, and the value is taken according to Table 2. Drive mode
Small wheel drives large wheel
Large wheel drives small wheel
CB 11367-89
Table 2 Engagement impact coefficient X.
Tooth overlap &
Ey ssl, 5en)
1. 5eCeH
Ca>Cel
The actual trimming amount (normal value) of the small wheel and the large wheel.um, when the meshing gear teeth have root trimming, it should be taken as the sum of the trimming amount and the root trimming amount.
The effective trimming amount·um refers to the trimming amount required to just compensate for the elastic deformation of the gear teeth. It can be estimated as follows: When Bm= 0°:
0°,
Ce: =KA Fm/(hg+ccosa)
Cht: - KA +Fmt/(te +r,- cosuut) Where: F—nominal tangential force on the pitch circle at the midpoint of the tooth width, N; K.-service coefficient;
bh—effective tooth width for calculation of bonding load capacity, mmbu=bhc——single pair of teeth stiffness, c-14 N/(mm*μm); meshing stiffness, c20N/mm, μm); Www.bzxZ.net
When the above conditions are not met, take X=1. 0.
6. 8 Pressure angle coefficient Xp
（30）
...(31)
The pressure angle coefficient X is a coefficient used to consider the influence of pressure angle and helix angle on integral temperature. For non-displacement and zero-displacement bevel gear transmission, it can be calculated as follows:
1.22(sina,)c.2)
casau）75
6. 9 Overlap coefficient X,
The overlap coefficient X is a coefficient that converts the local instantaneous temperature rise 8 when the load is assumed to act entirely on the pinion tooth top into the integral average temperature along the meshing line; F-8mlmn.,
X, determined according to formulas (33) to (38).
When 1,
When 1≤2,1,1, (see Figure 3)
(e + )
+..+..+..+..++......( 33 )
[0. 7(e, + e2) — 0. 22e-. + 0. 52 — 0. 6e2]26E.1
When 1≤<2,≥1,E2<1, (see Figure 3)
( 34 )
GB 11367—89
[0.18 + 0.7+ 0.8261-0.52-0.38E2]28E
When 1≤%≤,2,1,21inch,(see Figure 3)
—[0.18+0.7+0.82—0.521—0.3515]2....
When 2<3,≥2,(see Figure 4)
-[0.44%+0.59e+0.30
0. 30E 0. 15EE,]
When 2E<3,Em<, (See Figure 1)
Wherein=+
［0.59+0.44—0.30+0.305—0.15se2]2EvE.
The above formula is established under the assumption that the load and temperature are linearly distributed along the meshing line (as shown in Figures 3 and 4). Load
Meshing line
（a）Load distribution along the meshing line
B）Temperature distribution along the meshing line
Figure 3 Schematic diagram of load and temperature distribution along the meshing line (12)
Meshing line
·（35）
（37）
（38)
GB 11367—89
(a) Load distribution along meshing line
riarofo
(b) Temperature distribution along meshing line
Figure 4. Schematic diagram of load and temperature distribution along meshing line (23)
Anji load distribution
Approximate load distribution
Meshing line
Ca-frnink
C,Bmaint
Harmonic line
6.10 Material welding coefficient Xw
Material welding coefficient X is the modification coefficient introduced to consider the different materials and surface treatments between the design gear and the test gear. It is a relative ratio. It is obtained by comparing the test gears with different materials and surface treatments with the standard test gears. Its value can be found in Table 4.
Austenitic steel (stainless steel)
Carburized crushed hard steel
Surface nitrided steel
Surface phosphating steel
Surface copper plating
Other cases (such as quenched and tempered steel)
Table 1 Material welding coefficient X
Material and surface treatment
Retained austenite content is higher than normal value
Retained austenite content is normal (about 20%)Retained austenite content is lower than normal value
6.11 Body temperature 0mr and integrated average temperature rise nainrT of the test gear The body temperature 3mt and integrated average temperature rise 6nainc of the test gear are calculated based on the gear test data using formula (4) and formula (6).
GB 1136789
When the load-bearing capacity of the oil is obtained by the A/8.3/90 test on the CL100 testing machine specified in SY2691: the relationship curve between 0mr and ul and load is shown in Figure 5. At this time, the values of B and Huint can be obtained from Figure 5 according to the viscosity u and the bonding load level of the lubricating oil selected for the designed gear. The bonding load level of the lubricating oil is taken as the performance indicator of the oil, which is provided by the oil manufacturer. The curve in Figure 5 can be approximately expressed by the following formula:
8mr = 0. 23T+ 80
gpinf - 0. 2T2r
Wherein: TT-
-the test gear pinion torque corresponding to the bonding load level, N·Ⅱ;-the nominal kinematic viscosity of the lubricating oil at 40℃, mm\/s. 35.3 60.8 94.1 135.8183.1
Fig.5 Body temperature 8r and integrated average temperature rise iainF of the test gear?
-(39）
** 40
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