CN102029442A - Method for improving lubrication performance of spiral taper gear - Google Patents

Abstract

The invention discloses a method for improving the lubrication performance of a spiral taper gear, belonging to a design method of gears, and breaking through the limitation that only the intensity performance of the gear is considered, but not the lubrication performance in the formation process of the present spiral taper gear. The method comprises the following steps of: (1) calculating curvature radius, entrainment speed and load of a spiral taper gear contact point according to regulation parameters of a spiral taper gear machine tool; (2) solving the thickness of an oil film on the spiral taper gear contact point by an elasto-hydrodynamic lubrication fundamental equation according to the curvature radius, the entrainment speed, the load and lubricant performance parameters of the spiral taper gear contact point; and (3) changing machine tool rolling ratio of the regulation parameters of the spiral taper gear machine tool, repeating from the step (1) to the step (2), and selecting the machine tool rolling ratio which makes the thickness of the oil film of the spiral taper gear contact point maximum. The invention can achieve the improvement on the lubrication performance of the spiral taper gear on the premise of no needing of selecting a better lubricant and changing a lubricant feeding manner.

Description

A kind of method that improves the spiral bevel gear greasy property

Technical field

The present invention relates to a kind of method that improves the spiral bevel gear greasy property, belong to the design of gears technology, be particularly useful for the spiral bevel gear in aero-engine and the helicopter.

Background technology

Spiral bevel gear method for designing commonly used is at present mainly considered the strength character of gear, but for the spiral bevel gear under the high-speed working condition condition, as the spiral bevel gear in aero-engine and the helicopter, be easier to take place because tooth surface abrasion, the scuffing failure that the greasy property difference causes.Only consider that the spiral bevel gear method for designing of the strength character of gear can't improve the greasy property of spiral bevel gear.The method of raising spiral bevel gear greasy property commonly used is to select better lubricating oil for use and change the lubrication oil supply mode at present, selects for use better lubricating oil to raise the cost, and changes the structure that the lubrication oil supply mode need be revised the Helical Bevel Gear system.

Therefore, still lack a kind of method that under the prerequisite that need not select better lubricating oil and change lubrication oil supply mode for use, improves the spiral bevel gear greasy property at present both at home and abroad.

Summary of the invention

Technology of the present invention is dealt with problems: overcome the deficiencies in the prior art, a kind of method that improves the spiral bevel gear greasy property is provided, this method can need not selected better lubricating oil for use and change the greasy property that improves spiral bevel gear under the prerequisite of lubrication oil supply mode, and cost is lower and do not need to revise the structure of Helical Bevel Gear system.

Technical scheme of the present invention: a kind of method that improves the spiral bevel gear greasy property, performing step is as follows:

(1) calculates radius of curvature, Entrainment Velocity, the load of spiral bevel gear contact point according to the spiral bevel gear lathe adjusting parameter; Described spiral bevel gear lathe adjusting parameter comprises cutter diameter, cutterhead profile angle, radial, angle cutter spacing, workhead offset, axially position of wheel, berth, lathe roll ratio;

(2) according to radius of curvature, Entrainment Velocity, load and the lubricants performance parameter of spiral bevel gear contact point,, find the solution the oil film thickness of spiral bevel gear contact point by the elastohydrodynamic lubrication fundamental equation; Described lubricants performance parameter comprises lubricating oil viscosity, density under atmospheric pressure; Described elastohydrodynamic lubrication fundamental equation comprises Reynolds equation, oil film geometric equation, lubricating oil viscosity equation, lubricating oil density equation and counterweight balance equation;

(3) lathe that changes in the spiral bevel gear lathe adjusting parameter rolls ratio, and repeating step (1) is to step (2), and selection makes the lathe of the oil film thickness maximum of spiral bevel gear contact point roll ratio.

Reynolds equation in the described step (2) is:

$\frac{\∂}{\∂x}\left(\frac{{\mathrm{\ρh}}^3}{12\mathrm{\η}}\frac{\∂p}{\∂x}\right)+\frac{\∂}{\∂y}\left(\frac{{\mathrm{\ρh}}^3}{12\mathrm{\η}}\frac{\∂p}{\∂y}\right)-u_m\frac{\∂\left(\mathrm{\ρh}\right)}{\∂x}=0$

In the formula: p is the oil film pressure of spiral bevel gear contact point, and h is the oil film thickness of spiral bevel gear contact point, and ρ is the density of lubricating oil, and η is an oil body, u _mEntrainment Velocity for the spiral bevel gear contact point;

Oil film geometric equation in the described step (2) is:

$h=h_0+\frac{x^2}{{2R}_x}+\frac{y^2}{2R_y}+\frac{2}{{\mathrm{\πE}}^{\′}}{\∫}_{-\∞}^{+\∞}{\∫}_{-\∞}^{+\∞}\frac{p(x^{\′},y^{\′}){\mathrm{dx}}^{\′}{\mathrm{dy}}^{\′}}{\sqrt{{(x-x^{\′})}^2+{(y-y^{\′})}^2}}$

In the formula: R _x, R _yBe the radius of curvature of spiral bevel gear contact point, E ' is the elasticity modulus of materials of spiral bevel gear;

Lubricating oil viscosity equation in the described step (2) is:

$\mathrm{\η}={\mathrm{\η}}_0\exp (\ln \left({\mathrm{\η}}_0\right)+9.67)(-1{(1+\frac{p}{p_0})}^z)$

In the formula: η ₀Be lubricating oil viscosity under atmospheric pressure, z is 0.68, p ₀Be 196000000;

Lubricating oil density equation in the described step (2) is:

$\mathrm{\ρ}={\mathrm{\ρ}}_0\frac{5.9\×{10}^8+1.34p}{5.9\×{10}^8+p}$

In the formula: ρ ₀Be lubricating oil density under atmospheric pressure;

Counterweight balance equation in the described step (2) is:

$w={\∫}_{-\∞}^{+\∞}{\∫}_{-\∞}^{+\∞}p(x^{\′},y^{\′}){\mathrm{dx}}^{\′}{\mathrm{dy}}^{\′}$

In the formula: w is the load of spiral bevel gear contact point.

Lathe in the change spiral bevel gear lathe adjusting parameter in the described step (3) roll than method be: on the basis of original value, add 2% the 1st time, on the basis of original value, add 4% the 2nd time, on the basis of original value, add 6% the 3rd time, the 4th adds 8% on the basis of original value, the 5th adds 10% on the basis of original value, on the basis of original value, subtract 2% the 6th time, on the basis of original value, subtract 4% the 7th time, on the basis of original value, subtract 6% the 8th time, subtract 10% subtracting on the basis of original value on 8%, the 10 basis the 9th time at original value.

The present invention's beneficial effect compared with prior art is: the present invention calculates radius of curvature, Entrainment Velocity, the load of spiral bevel gear contact point according to the spiral bevel gear lathe adjusting parameter, radius of curvature, Entrainment Velocity, load and lubricants performance parameter according to the spiral bevel gear contact point, by the elastohydrodynamic lubrication fundamental equation, find the solution the oil film thickness of spiral bevel gear contact point, roll ratio by the lathe that changes in the spiral bevel gear lathe adjusting parameter, selection makes the lathe of the oil film thickness maximum of spiral bevel gear contact point roll ratio.The present invention is a kind of method for designing that can improve the spiral bevel gear greasy property, and using the present invention does not need to select better lubricating oil for use, and cost is lower.On the other hand, use the lubrication oil supply mode that the present invention does not change the Helical Bevel Gear system, do not need to revise the structure of Helical Bevel Gear system.

Description of drawings

Fig. 1 is a method flow diagram of the present invention;

Fig. 2 is the graphics of spiral bevel gear;

Fig. 3 for a change lathe rolls oil film thickness than rear screw bevel gear contact point.

The specific embodiment

The present invention improves the method for spiral bevel gear greasy property, as shown in Figure 1.Following embodiment is an example with the spiral bevel gear greasy property process that improves in certain model aero-engine, specifies implementation procedure of the present invention.As shown in Figure 2, the basic design parameters of spiral bevel gear is the gear wheel number of teeth 97, the pinion number of teeth 19, modulus 5.2mm, 20 ° of pressure angles, 35 ° of helical angles, 91.5 ° of crossed axis angles, face width of tooth 35mm.The working condition of spiral bevel gear is pinion moment of torsion 388Nm, 20900 rev/mins of pinion rotating speeds.The elasticity modulus of materials of spiral bevel gear is 206000MPa.But protection scope of the present invention is not limited to following embodiment:

Step (1): radius of curvature, Entrainment Velocity, the load of calculating the spiral bevel gear contact point according to the spiral bevel gear lathe adjusting parameter;

The original lathe adjusting parameter of spiral bevel gear is cutter diameter 304.8mm in the present embodiment, 18 ° of cutterhead profile angles, radial 175.31mm, 55.76 ° of angle cutter spacing, workhead offset 2.99mm, axially position of wheel 33.05mm, berth-7.96mm, lathe rolls than 4.74.

Wherein: cutter diameter refers to process the diameter of the used cutterhead of spiral bevel gear; The cutterhead profile angle refers to process the cutting edge and the angle of cutter axis on the cutter axis cross section of the used cutterhead of spiral bevel gear; The distance between the shape wheel axis was produced in cutter axis and processing when radial referred to process spiral bevel gear; The angle between the shape wheel axis was produced in cutter axis and processing when the angle cutter spacing referred to process spiral bevel gear; The distance between the shape wheel axis was produced in Gear axis and processing when workhead offset referred to process spiral bevel gear; Distance when axially the position of wheel refers to process spiral bevel gear between the intersection point of the intersection point of Gear axis and processing product shape wheel axis and a pair of spiral bevel gear axis; Berth refers to the adjusted value of the sliding bottom of hypoid generating machine; The ratio of shape rotating speed was produced in gear and processing when lathe rolled than finger processing spiral bevel gear.

Original lathe adjusting parameter and working condition according to spiral bevel gear, the operation spiral bevel gear loads the contact analysis program, and (this program is known, spiral bevel gear as U.S. Gleason company loads the contact analysis program), the radius of curvature that obtains the spiral bevel gear contact point is R _x=0.011mm, R _y=0.481mm, the Entrainment Velocity of spiral bevel gear contact point is u _m=18.5m/s, the load of spiral bevel gear contact point is w=8015.1N.

Wherein: the radius of curvature of spiral bevel gear contact point refers to the inverse of a pair of spiral bevel gear in the curvature of contacting points position; The Entrainment Velocity of spiral bevel gear contact point refers to the mean value of a pair of spiral bevel gear in the speed of contacting points position.

Step (2):,, find the solution the oil film thickness of spiral bevel gear contact point by the elastohydrodynamic lubrication fundamental equation according to radius of curvature, Entrainment Velocity, contact point load and the lubricants performance parameter of spiral bevel gear contact point;

The lubricants performance parameter is in the present embodiment:

Lubricating oil viscosity under atmospheric pressure is 0.1936Pas, and lubricating oil density under atmospheric pressure is 870kg/m ³

By the elastohydrodynamic lubrication fundamental equation, in radius of curvature, Entrainment Velocity, load and lubricants performance parameter substitution Reynolds equation, oil film geometric equation, lubricating oil viscosity equation, lubricating oil density equation and the counterweight balance equation with the spiral bevel gear contact point that obtains in the step (1), operation numerical computations program, the oil film thickness that obtains the spiral bevel gear contact point is 16.69 μ m.

Step (3): the lathe that changes in the spiral bevel gear lathe adjusting parameter rolls ratio, and repeating step (1) is to step (2), and selection makes the lathe of the oil film thickness maximum of spiral bevel gear contact point roll ratio.

Change for the 1st time: lathe is rolled than adding 2% on the basis of original value, and lathe rolls than being 4.83.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 19.03 μ m.

Change for the 2nd time: lathe is rolled than adding 4% on the basis of original value, and lathe rolls than being 4.92.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 20.05 μ m.

Change for the 3rd time: lathe is rolled than adding 6% on the basis of original value, and lathe rolls than being 5.01.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 21.04 μ m.

The 4th changes: lathe is rolled than adding 8% on the basis of original value, and lathe rolls than being 5.1.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 20.70 μ m.

The 5th changes: lathe is rolled than adding 10% on the basis of original value, and lathe rolls than being 5.19.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 20.52 μ m.

Change for the 6th time: lathe is rolled than subtracting 2% on the basis of original value, and lathe rolls than being 4.65.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 19.36 μ m.

Change for the 7th time: lathe is rolled than subtracting 4% on the basis of original value, and lathe rolls than being 4.56.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 17.86 μ m.

Change for the 8th time: lathe is rolled than subtracting 6% on the basis of original value, and lathe rolls than being 4.47.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 19.36 μ m.

Change for the 9th time: lathe is rolled than subtracting 8% on the basis of original value, and lathe rolls than being 4.38.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 20.37 μ m.

Change for the 10th time: lathe is rolled than subtract 10% on the basis of original value.Lathe rolls than being 4.29.Repeating step (1) is to step (2), and the oil film thickness that obtains the spiral bevel gear contact point is 20.19 μ m.

As shown in Figure 3, the lathe of the oil film thickness maximum of spiral bevel gear contact point is rolled than being 5.01.Roll than 4.74 with the lathe in the original spiral bevel gear lathe adjusting parameter of 5.01 replacements, make the oil film thickness maximum of spiral bevel gear contact point, improve the spiral bevel gear greasy property thereby finish.

Owing to the limitation of test method, can't directly record the oil film thickness of spiral bevel gear contact point, can only judge the spiral bevel gear greasy property by near the environment temperature the measurement spiral bevel gear contact point.To present embodiment, to adopting original spiral bevel gear lathe adjusting parameter (lathe roll than be 4.74) and adopt the spiral bevel gear of the spiral bevel gear lathe adjusting parameter that changes (lathe roll than be 5.01), near the environment temperature of measuring under the same experiment condition spiral bevel gear contact point.Adopting near the environment temperature of spiral bevel gear contact point of original spiral bevel gear lathe adjusting parameter is 64 ℃, near the spiral bevel gear contact point of the spiral bevel gear lathe adjusting parameter that adopt to change environment temperature is 61 ℃, illustrates that the method that the present invention improves the spiral bevel gear greasy property is effectively.

In a word, the present invention calculates radius of curvature, Entrainment Velocity, the contact point load of spiral bevel gear contact point according to the spiral bevel gear lathe adjusting parameter; According to radius of curvature, Entrainment Velocity, contact point load and the lubricants performance parameter of spiral bevel gear contact point,, find the solution the oil film thickness of spiral bevel gear contact point by the elastohydrodynamic lubrication fundamental equation; Roll ratio by the lathe that changes in the spiral bevel gear lathe adjusting parameter, make the oil film thickness maximum of spiral bevel gear contact point, thereby realize improving the spiral bevel gear greasy property.Use the present invention and need not select better lubricating oil for use, and do not change the lubrication oil supply mode of Helical Bevel Gear system.The present invention is applicable to the application of common engineering problem, for the spiral bevel gear of in the engineering application greasy property being had relatively high expectations provides a new design approach.

Claims (3)

1. method that improves the spiral bevel gear greasy property is characterized in that step is as follows:

(1) calculates radius of curvature, Entrainment Velocity, the load of spiral bevel gear contact point according to the spiral bevel gear lathe adjusting parameter; Described spiral bevel gear lathe adjusting parameter comprises cutter diameter, cutterhead profile angle, radial, angle cutter spacing, workhead offset, axially position of wheel, berth, lathe roll ratio;

(2) according to radius of curvature, Entrainment Velocity, load and the lubricants performance parameter of spiral bevel gear contact point,, find the solution the oil film thickness of spiral bevel gear contact point by the elastohydrodynamic lubrication fundamental equation; Described lubricants performance parameter comprises lubricating oil viscosity, density under atmospheric pressure; Described elastohydrodynamic lubrication fundamental equation comprises Reynolds equation, oil film geometric equation, lubricating oil viscosity equation, lubricating oil density equation and counterweight balance equation;

(3) lathe that changes in the spiral bevel gear lathe adjusting parameter rolls ratio, and repeating step (1) is to step (2), and selection makes the lathe of the oil film thickness maximum of spiral bevel gear contact point roll ratio.

2. a kind of method that improves the spiral bevel gear greasy property according to claim 1 is characterized in that: the Reynolds equation in the described step (2) is:

$\frac{\∂}{\∂x}\left(\frac{{\mathrm{\ρh}}^3}{12\mathrm{\η}}\frac{\∂p}{\∂x}\right)+\frac{\∂}{\∂y}\left(\frac{{\mathrm{\ρh}}^3}{12\mathrm{\η}}\frac{\∂p}{\∂y}\right)-u_m\frac{\∂\left(\mathrm{\ρh}\right)}{\∂x}=0$

In the formula: p is the oil film pressure of spiral bevel gear contact point, and h is the oil film thickness of spiral bevel gear contact point, and ρ is the density of lubricating oil, and η is an oil body, u _mEntrainment Velocity for the spiral bevel gear contact point;

Oil film geometric equation in the described step (2) is:

$h=h_0+\frac{x^2}{{2R}_x}+\frac{y^2}{2R_y}+\frac{2}{{\mathrm{\πE}}^{\′}}{\∫}_{-\∞}^{+\∞}{\∫}_{-\∞}^{+\∞}\frac{p(x^{\′},y^{\′}){\mathrm{dx}}^{\′}{\mathrm{dy}}^{\′}}{\sqrt{{(x-x^{\′})}^2+{(y-y^{\′})}^2}}$

In the formula: R _x, R _yBe the radius of curvature of spiral bevel gear contact point, E ' is the elasticity modulus of materials of spiral bevel gear;

Lubricating oil viscosity equation in the described step (2) is:

$\mathrm{\η}={\mathrm{\η}}_0\exp (\ln \left({\mathrm{\η}}_0\right)+9.67)(-1{(1+\frac{p}{p_0})}^z)$

In the formula: η ₀Be lubricating oil viscosity under atmospheric pressure, z is 0.68, p ₀Be 196000000;

Lubricating oil density equation in the described step (2) is:

$\mathrm{\ρ}={\mathrm{\ρ}}_0\frac{5.9\×{10}^8+1.34p}{5.9\×{10}^8+p}$

In the formula: ρ ₀Be lubricating oil density under atmospheric pressure;

Counterweight balance equation in the described step (2) is:

$w={\∫}_{-\∞}^{+\∞}{\∫}_{-\∞}^{+\∞}p(x^{\′},y^{\′}){\mathrm{dx}}^{\′}{\mathrm{dy}}^{\′}$

In the formula: w is the load of spiral bevel gear contact point.

3. a kind of method that improves the spiral bevel gear greasy property according to claim 1, it is characterized in that: the lathe in the change spiral bevel gear lathe adjusting parameter in the described step (3) roll than method be: on the basis of original value, add 2% the 1st time, on the basis of original value, add 4% the 2nd time, on the basis of original value, add 6% the 3rd time, the 4th adds 8% on the basis of original value, the 5th adds 10% on the basis of original value, on the basis of original value, subtract 2% the 6th time, on the basis of original value, subtract 4% the 7th time, on the basis of original value, subtract 6% the 8th time, subtract 10% subtracting on the basis of original value on 8%, the 10 basis the 9th time at original value.

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