CN100360803C - Big pressure angle negative profile shifted gear for hydraulic gear pump - Google Patents
Big pressure angle negative profile shifted gear for hydraulic gear pump Download PDFInfo
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- CN100360803C CN100360803C CNB2005100945191A CN200510094519A CN100360803C CN 100360803 C CN100360803 C CN 100360803C CN B2005100945191 A CNB2005100945191 A CN B2005100945191A CN 200510094519 A CN200510094519 A CN 200510094519A CN 100360803 C CN100360803 C CN 100360803C
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- gear pump
- pressure angle
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- pump
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Abstract
The present invention discloses an evolvent cylindrical gear used on a hydraulic gear pump, the tooth shape of which is a pressure angle of 30DEG negative addendum modification. The hydraulic gear pump with the tooth shape has the advantages of small volume, light weight, long service life, no root cutting and low noise. The discharge capacity, the rated pressure, the volumetric efficiency, the overall efficiency and the noise reach the requirements of international standards. Therefore, the present invention has good use value for application.
Description
Technical field
The present invention relates to a kind of gear, specifically, relate to the large pressure angle negative addendum modification tooth-profile of gear in a kind of hydraulic gear pump.
Background technique
Present widely used hydraulic gear pump, its gear mostly adopts the involute cylindrical gear of common standard, and in the design of hydraulic gear pump, discharge capacity is calculated and is generally all adopted formula q=2 π zm
2B*10
-3Carry out the parameter of discharge capacity calculating, in the formula with definite gear
Q-pump delivery unit/ml/r
The number of teeth of Z-gear
The mm of modulus unit of m-gear
The cm of width unit of B-gear
As can be known, the first power direct ratio of discharge capacity q and number of teeth z with square being directly proportional of modulus, is directly proportional with the gear width from above-mentioned formula.When need increase discharge capacity, if increase the number of teeth gear pump volume is increased, if increase the gear width, the volume of pump is increased, also can increase the gear pump bearing load, influence the gear pump life-span.
The pressure angle of national Specification involute cylindrical gear is
20 °, addendum coefficient ha=1, gear do not produce the minimum number of teeth Zmin=2 * 1/sin of undercut
220 °=17.The theoretical center that two gears are meshed, increases modulus m and the number of teeth z gear pump volume is increased in order to reach big discharge capacity apart from A=m * z, and the mounting teeth wheel pump need be than large space, and the space young pathbreaker can't use.
The present gear pump that uses, the shortcoming that the pulsation of ubiquity instantaneous flow is excessive has reduced the stationarity and the uniformity of element work in the hydraulic system, even can produce pressure pulse, thereby makes whole system produce vibration, and very strong noise pollution takes place.
Summary of the invention
It is few that the technical problem to be solved in the present invention provides a kind of number of teeth, the gear that modulus is big, and the hydraulic gear pump of manufacturing can not only satisfy the requirement of flow, can accomplish that again volume is little, and in light weight, the life-span is long, undercut not, noise is low.
In order to solve the problems of the technologies described above, the profile of tooth of the hydraulic gear pump involute cylindrical gear of the present invention's design is 30 ° of pressure angle profile of tooth negative addendum modifications.
Good effect of the present invention is: the hydraulic gear pump that adopts large pressure angle negative addendum modification profile of tooth involute cylindrical gear to make, volume is little, in light weight, the life-span is long, noise is low, gear does not produce undercut, its discharge capacity, rated pressure, volumetric efficiency, total efficiency and noise all reach the standard of GB Grade A.
Description of drawings
Fig. 1 is a standard cylinder gear outer gearing schematic representation;
Fig. 2 is the APPROXIMATE DISTRIBUTION curve of circumference of gear pressure.
Among the figure: d, standard pitch diameter, ha, addendum, hf, dedendum of the tooth, h, whole depth, da, tip diameter, d, standard pitch circle, df, root diameter, a, centre distance, α, top circle pressure angle, Fty, engaging force be at the axial component of y, Rb, rolling circle radius, Ra, Outside radius, R, gear compound graduation circle radius.
Embodiment
One, gear parameter and calculating case:
1, tooth profile parameter
(1) tooth number Z=10
(2) modulus m=5.75
(3) profile of tooth pressure angle α=30 °
2, design calculation formula
(1) theoretical center is apart from a=mz=57.5
(2) practical center is according to a '=55
(3) standard pitch diameter d=mz=57.5
(4) base circle diameter (BCD) db=mzcos α=49.8
(5) meshingangle ' by formula cos α '=a/a ' * cos α
α '=arcc (a/a ' * cos α)=arccos57.5/55*cos30 °=25.12 °
(6) modification coefficient x=z (ivn α '-ivn α)/2tg α=-0.202
(7) centre distance Separating factor y=(a '-a)/m=(55-57.5)/5.75=-0.435
(8) addendum coefficient of alteration Δ y=(x1+x2)-y=-0.404+0.435=0.031
(9) addendum ha=(ha*+x-Δ y) m=(1-0.202-0.031) * 5.75=4.41
(10) dedendum of the tooth hf=(ha*+cn*-x) m gets cn*=0.17
hf＝(1+0.17+0.202)×5.75＝7.89
(11) tip diameter da=d+2ha=57.5+4.441*2=66.32 gets 66.5
(12) root diameter df=d-2hf=57.5-7.89*2=41.72
(13) top circle pressure angle α is a=arccosdb/da=arccos49.8/66.5=41.5 °
(14) contact ratio ε=1/2 π * [2z (tg α a-tg α ')]=1.32
(15) K gets k=2 for overstating number of teeth K=30z/180+0.5=2.16 in base tangent length w=mzcos α [(k-0.5) π+zinv α]+2xmsin α formula
Then w=5.75*10*cos30 ° [(2-0.5) π+10inv30 °]-2*0.202*5.75sin30 °=24.998
Two, adopt the embodiment of large pressure angle negative addendum modification profile of tooth:
1, reduced the radial force that bearing bore:
Shown in Figure 2 as Fig. 1, act on the radial force F on the driven gear shaft
2Be to form along the radial force Fp of circumference of gear fluid pressure generation and the radial force Ft that is produced by gear engagement, wherein the component of radial force FT on the y axle that is produced by gear engagement is
Fty＝BΔP/Rb*(Ra-R)cosα
In the formula: Fty: engaging force is at the axial component of y
Rb: rolling circle radius
Ra: Outside radius
R: gear compound graduation circle radius
α: pressure angle
By the APPROXIMATE DISTRIBUTION plotted curve of following formula and circumference of gear pressure as can be seen: because pressure angle α increases, driven gear reduces in the radial force that the y axle direction is born, thereby has alleviated bearing load, has reduced mechanical loss.Help the mechanical efficiency of gear pump and the raising in working life.
2, avoided under cut:
By Der Grundsatz der Maschinen as can be known: the minimum teeth number that the involute cylindrical gear work in-process does not produce undercut is:
Zmin＝2ha*/Sin
2α
Wherein: Zmin: involute cylindrical gear does not produce the minimum teeth number of undercut
Ha*: addendum coefficient national Specification: ha*=1
α: pressure angle national Specification: α=20 °
By following formula as can be known: when addendum coefficient ha*=J α=20 °:
Do not produce the minimum number of teeth Zmin=2*1/Sin of undercut
220 °=17
And gear pump is because the restriction of volume can not be increased to 17 with the number of teeth.After we have adopted the tooth profile parameter of Z=10, m=5.75, α=30 °, do not produce the minimum number of teeth Zmin=2*1/Sin of undercut
230 °=8.Although we have taked negative addendum modification, by the minimum modification coefficient formula X 〉=ha*-zSin that does not produce undercut
2α/2=-0.25 as can be known, modification coefficient X=-0.202＞-0.25, proof at Z=10, can not produce undercut under the condition of correction factor X=-0.202 behind the pressure angle of employing α=30 ° thus, promptly guarantees the intensity of the gear teeth, and has reduced the volume of gear pump.
3, reduce the gear pump factor of non-uniform flow:
Hydraulic gear pump has advantages such as volume simple in structure is little, in light weight, the life-span is long, but also has the shortcoming of moment flow pulsation.If the flow pulsation conference reduces the stationarity and the uniformity of element work in the hydraulic system, even can produce pressure pulsation, thereby make whole system produce vibration, very strong noise takes place.
The gear pump factor of non-uniform flow is:
σQ＝3π
2Cos
2α/12(Z+1)π
2Cos
2α
In the formula: σ Q: factor of non-uniform flow
Z: the gear number of teeth
α: pressure angle
As can be seen from the above equation: adopt the large pressure angle profile of tooth can reduce the gear pump factor of non-uniform flow, thereby improve the stationarity of system element work, reduce the load of bearing, the integrated quality and the working life of improving gear pump.
In sum, adopt large pressure angle negative addendum modification profile of tooth can dwindle the volume of gear pump, alleviate bearing load, reduce factor of non-uniform flow and noise, thereby improve the mechanical efficiency and the working life of gear pump.The gear pump of recommending this gear parameter of use to manufacture and design, its important technological parameters:
Discharge capacity: q=20-110ml/r
Rated pressure: P=20MPa
Maximum pressure: P
Max=25MPa
Rated speed: n=2000r/min
Maximum speed n
Max=2500r/min
Volumetric efficiency: η v 〉=92%
Total efficiency: η always 〉=83%
Noise: dB (A)≤85
Claims (1)
1, a kind of involute cylindrical gear that is used for hydraulic gear pump is characterized in that: tooth-formation of gear is 30 ° of pressure angles, and modification coefficient is-0.202 profile of tooth, and the number of teeth is 10, and modulus is 5.75.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100945191A CN100360803C (en) | 2005-09-22 | 2005-09-22 | Big pressure angle negative profile shifted gear for hydraulic gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100945191A CN100360803C (en) | 2005-09-22 | 2005-09-22 | Big pressure angle negative profile shifted gear for hydraulic gear pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1743673A CN1743673A (en) | 2006-03-08 |
| CN100360803C true CN100360803C (en) | 2008-01-09 |
Family
ID=36139167
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005100945191A Expired - Fee Related CN100360803C (en) | 2005-09-22 | 2005-09-22 | Big pressure angle negative profile shifted gear for hydraulic gear pump |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104389682A (en) * | 2014-11-17 | 2015-03-04 | 哈尔滨广瀚燃气轮机有限公司 | Electric lubricating oil supply pump of gas turbine |
| CN104675957A (en) * | 2015-03-06 | 2015-06-03 | 佛山市汇禧建筑五金制品有限公司 | Special gear for sliding door and window |
| US20200095991A1 (en) * | 2016-12-22 | 2020-03-26 | Pumps Aps | A beverage dispensing machine and a gear pump therefor |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1031214C (en) * | 1992-10-26 | 1996-03-06 | 中国人民解放军第二炮兵工程学院 | Hydraulic motor for non-circular epicyclic train |
| US5676617A (en) * | 1995-07-12 | 1997-10-14 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission for vehicles |
| CN2298371Y (en) * | 1996-12-24 | 1998-11-25 | 中国纺织大学 | Convex-concave, convex-plane tooth face meshed gear pair |
-
2005
- 2005-09-22 CN CNB2005100945191A patent/CN100360803C/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1031214C (en) * | 1992-10-26 | 1996-03-06 | 中国人民解放军第二炮兵工程学院 | Hydraulic motor for non-circular epicyclic train |
| US5676617A (en) * | 1995-07-12 | 1997-10-14 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission for vehicles |
| CN2298371Y (en) * | 1996-12-24 | 1998-11-25 | 中国纺织大学 | Convex-concave, convex-plane tooth face meshed gear pair |
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|---|---|
| CN1743673A (en) | 2006-03-08 |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee |
Owner name: XUZHOU KEYUAN HYDRAULICS CO., LTD. Free format text: FORMER NAME: XUZHOU KEYUAN HYDRAULIC CO., LTD. |
|
| CP03 | Change of name, title or address |
Address after: Ganjiang road Copper Mt. District 221116 Jiangsu city of Xuzhou province No. 6 Patentee after: Xuzhou Keyuan Hydraulics Co., Ltd. Address before: 221006 No. 6 East mining road, Jiangsu, Xuzhou Patentee before: Xuzhou Keyuan Hydraulic Co., Ltd. |
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080109 Termination date: 20150922 |
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| EXPY | Termination of patent right or utility model |