CN111797361A - Long-life high temperature resistant textile motor bearing - Google Patents
Long-life high temperature resistant textile motor bearing Download PDFInfo
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- CN111797361A CN111797361A CN202010665241.3A CN202010665241A CN111797361A CN 111797361 A CN111797361 A CN 111797361A CN 202010665241 A CN202010665241 A CN 202010665241A CN 111797361 A CN111797361 A CN 111797361A
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- 239000004753 textile Substances 0.000 title claims abstract description 16
- 239000004519 grease Substances 0.000 claims abstract description 25
- 230000001050 lubricating effect Effects 0.000 claims abstract description 18
- 239000000463 material Substances 0.000 claims abstract description 17
- 238000004519 manufacturing process Methods 0.000 claims abstract description 15
- 230000005489 elastic deformation Effects 0.000 claims abstract description 9
- 238000005096 rolling process Methods 0.000 claims abstract description 8
- 238000012360 testing method Methods 0.000 claims description 49
- 229910000831 Steel Inorganic materials 0.000 claims description 33
- 239000010959 steel Substances 0.000 claims description 33
- 239000003921 oil Substances 0.000 claims description 13
- 238000013459 approach Methods 0.000 claims description 9
- 230000005540 biological transmission Effects 0.000 claims description 8
- 239000010687 lubricating oil Substances 0.000 claims description 8
- 239000004721 Polyphenylene oxide Substances 0.000 claims description 7
- 238000000137 annealing Methods 0.000 claims description 7
- 238000005097 cold rolling Methods 0.000 claims description 7
- 238000005516 engineering process Methods 0.000 claims description 7
- 150000002148 esters Chemical class 0.000 claims description 7
- 238000005461 lubrication Methods 0.000 claims description 7
- 229920000570 polyether Polymers 0.000 claims description 7
- 229920002396 Polyurea Polymers 0.000 claims description 6
- 230000009467 reduction Effects 0.000 claims description 6
- 239000002562 thickening agent Substances 0.000 claims description 6
- 238000004364 calculation method Methods 0.000 claims description 5
- 230000003068 static effect Effects 0.000 claims description 3
- 238000001816 cooling Methods 0.000 claims description 2
- 238000010438 heat treatment Methods 0.000 claims description 2
- 230000006698 induction Effects 0.000 claims description 2
- 238000001556 precipitation Methods 0.000 claims description 2
- WGYKZJWCGVVSQN-UHFFFAOYSA-N propylamine Chemical compound CCCN WGYKZJWCGVVSQN-UHFFFAOYSA-N 0.000 claims description 2
- 230000002787 reinforcement Effects 0.000 claims 1
- 238000013461 design Methods 0.000 abstract description 10
- 230000008859 change Effects 0.000 abstract description 8
- 238000009434 installation Methods 0.000 abstract description 2
- 230000002028 premature Effects 0.000 abstract description 2
- 229910052751 metal Inorganic materials 0.000 description 7
- 239000002184 metal Substances 0.000 description 7
- 238000005728 strengthening Methods 0.000 description 7
- 238000005242 forging Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 239000010410 layer Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 239000002199 base oil Substances 0.000 description 3
- 238000010791 quenching Methods 0.000 description 3
- 230000000171 quenching effect Effects 0.000 description 3
- 238000005496 tempering Methods 0.000 description 3
- 238000004458 analytical method Methods 0.000 description 2
- 229910052729 chemical element Inorganic materials 0.000 description 2
- 238000007405 data analysis Methods 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
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- 239000002344 surface layer Substances 0.000 description 2
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- RTAQQCXQSZGOHL-UHFFFAOYSA-N Titanium Chemical compound [Ti] RTAQQCXQSZGOHL-UHFFFAOYSA-N 0.000 description 1
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F17/00—Digital computing or data processing equipment or methods, specially adapted for specific functions
- G06F17/10—Complex mathematical operations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/62—Selection of substances
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/64—Special methods of manufacture
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6633—Grease properties or compositions, e.g. rheological properties
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6688—Lubricant compositions or properties, e.g. viscosity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2220/00—Shaping
- F16C2220/40—Shaping by deformation without removing material
- F16C2220/46—Shaping by deformation without removing material by forging
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2223/00—Surface treatments; Hardening; Coating
- F16C2223/10—Hardening, e.g. carburizing, carbo-nitriding
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
Abstract
The invention discloses a long-life high-temperature-resistant textile motor bearing, and belongs to the technical field of high-precision special bearing manufacturing. The invention improves the four aspects of technical design, manufacturing process, bearing lubricating grease selection and bearing manufacturing materials, and the improved bearing can obviously prolong the service life and is wear-resistant and high-temperature-resistant. The invention scientifically designs the working clearance Gr of the bearing, not only considers the installation clearance and the change clearance of the inner ring and the outer ring caused by the temperature change, but also mainly solves the problems of increasing the friction torque and the temperature rise caused by the change of the clearance caused by the elastic deformation when the maximum rolling element load of the bearing area of the bearing raceway is increased during the working operation, and causing the premature seizure or fatigue damage of the bearing, thereby greatly prolonging the service life of the bearing.
Description
Technical Field
The invention belongs to the technical field of high-precision special bearing manufacturing, and particularly relates to a long-life high-temperature-resistant textile motor bearing.
Background
In recent years, the environment and conditions suitable for rolling bearings have become increasingly strict, and the rolling bearings have become diversified. The operating conditions of the motors FYQ and FYQQ of the textile machinery are harsh, and the bearings matched with the motors for use must meet the use requirements of special operating conditions. Meanwhile, the common motor is arranged at a relatively closed position at the lower part of the machine tool, and only one exhaust window hole is arranged on the side surface. High internal temperature and high humidity. The radial load is large (four belts are tight and do not move), and the instant impact force is generated during starting. Because the operating condition and environment are harsh, the bearings of foreign imported products generally have fatigue damage within 5700-7200 h (the domestic bearings generally have the service life of 2160-4320 h). Under the continuous working condition of 24 hours without stopping the machine, the bearing with the long service life of more than or equal to 15000 hours is a key product for development.
After analysis of the bearing anatomical damage to the customer fatigue damage the following can be seen: (1) the outer ring channel is peeled off, and the color of the steel ball is changed at high temperature; (2) the inner ring channel is peeled off, and the steel ball is discolored at high temperature. The cause of this analysis was mainly damage due to life fatigue. Under high-temperature operation, the load is large, lubricating oil is separated out after long-time operation, grease is invalid, the lubrication-free operation is caused, meanwhile, the elastic deformation generated by instant impact force causes the fatigue damage of the bearing (the characteristic of fatigue damage is that the sliding surface in the channel is peeled off), although the bearing can rotate, the bearing is dry ground on a damaged raceway, and the jumping sound is large.
Especially, in some occasions such as permanent magnet motors, variable frequency speed regulating motors and the like which continuously operate for a long time under the working conditions of large load, high temperature and high humidity environment, the bearings cannot adapt to severe working environment in the use process, so that the bearings are fatigue damaged in advance, and the fatigue damage of the bearings is accelerated when instantaneous impact force exists in the operation.
The bearing is improved in four aspects of technical design, manufacturing process, bearing lubricating grease selection and bearing manufacturing materials, and the improved bearing can obviously prolong the service life and is wear-resistant and high-temperature-resistant.
Disclosure of Invention
In order to solve the technical problems, the applicant provides a long-life high-temperature-resistant textile motor bearing which is obviously prolonged in service life, resistant to wear and high temperature and excellent in performance.
The specific technical scheme of the invention is as follows:
the utility model provides a high temperature resistant textile motor bearing of long-life which characterized in that the work play Gr of bearing is selected according to the calculation of following step:
calculating the maximum contact stress according to the maximum load bearing:
in the formula: pmax-maximum Hertz contact stress;
ea-contact ellipse major axis coefficients;
eb-contact ellipse minor axis coefficients;
q is the maximum load of the rolling body;
sigma rho is the sum of main curvatures at the contact points of the steel ball and the roller path;
f (rho) -main curvature difference function of two contact bodies of the steel ball and the raceway;
ρ1Ⅰ-the curvature of the steel ball in the principal plane i;
ρ1Ⅱ-the curvature of the steel ball in the principal plane ii;
ρ2Ⅰ-the curvature of the raceway in the principal plane i;
ρ2Ⅱ-the curvature of the raceway in the principal plane ii;
② calculating elastic deformation
In the formula: i, elastic approach of the steel ball and the inner ring raceway;
e, elastic approach of the steel ball and the outer ring raceway;
e-elastic approach coefficient;
selecting the working clearance Gr of the bearing according to the elastic deformation:
in the formula: a Gr' bearing is provided with a radial clearance;
Δ ui — the amount of reduction in play caused by the temperature of the inner ring being higher than the temperature of the outer ring;
delta ue is the amount of reduction of the play caused by the temperature of the outer ring being higher than the temperature of the outer ring;
r-the amount of play increase caused by radial deformation of the bearing in the operating state.
Preferably, the inner ring and the outer ring of the bearing are manufactured and formed by adopting high-speed upsetting and cold rolling technology; (ii) a The high-speed upsetting ferrule adopts a medium-frequency induction heating technology, the temperature is controlled to be 1110-1170 ℃, complete austenitization is ensured, and secondary net-shaped carbide precipitation is inhibited through rapid cooling; meanwhile, the isothermal spheroidizing annealing is protected by the aminopropane atmosphere, so that the depth of the forged decarburized layer of the inner ring and the outer ring of the bearing is ensured to be 0.03 mm. The cold rolling and expanding processing technology makes the material plastically deformed and formed. The surface of a metal streamline connection workpiece in the ferrule is ensured to form extension, the internal tissue density is improved, the wear resistance is enhanced, and the service life of the ferrule is greatly prolonged.
Preferably, the lubricating oil adopted in the bearing consists of polyether + ester fully-synthetic oil and a polyurea thickening agent, and the mass ratio of the polyether + ester fully-synthetic oil to the polyurea thickening agent is 8: 2. preferably, the oil film lubrication parameter λ is calculated according to the following formula:
wherein: k is a radical ofλ-constants related to the type of bearing;
dm-pitch circle diameter;
ni-inner ring working speed, unit r/min;
P0bearing equivalent static load in N.
Substituting the relevant parameters of the bearing into the formula to calculate: lambda is more than or equal to 4.2.
Preferably, the lubricating grease is long-life grease Q954 selected from lubricating grease, and the kinematic viscosity of the grease is 98-CST。
Preferably, the steel material selected for manufacturing the bearing is SKF3 bearing steel material.
Preferably, the service life of the strengthening test of the bearing is calculated according to the following formula:
wherein: l10h — nominal life calculation test value (hours);
c, bearing rated dynamic load;
p-bearing test equivalent load:
n-test motor speed.
Preferably, the method for calculating the bearing equivalent test load P is as follows: according to the actual working condition, the motor is transmitted by a belt pulley, the belt pulley structure generates radial load, the load acting on the wheel shaft is a function of the resultant force of tension load, and the transmission force formula of the belt is as follows:
wherein: ft is the transmission force of the belt, unit N;
n-transmission power, unit KW;
n-the rotation speed of the belt pulley, unit r/min;
r-effective radius of the pulley in mm.
Load force acting on the bearing
Wherein: fb-Belt coefficient;
fw-impact load coefficient;
after each belt F is determined, the actual equivalent load P' acting on the bearing is:
the bearing equivalent test load P is:
wherein: tau-radial load test parameters of the lubricating grease life.
The invention has the beneficial effects that:
(1) the invention improves the four aspects of technical design, manufacturing process, bearing lubricating grease selection and bearing manufacturing materials, and the improved bearing can obviously prolong the service life and is wear-resistant and high-temperature-resistant. The invention scientifically designs the working clearance Gr of the bearing, not only considers the installation clearance and the change clearance of the inner ring and the outer ring caused by temperature change, but also mainly solves the problems of increasing friction torque and temperature rise caused by the change of the clearance caused by elastic deformation when the maximum rolling element load of a bearing area of a bearing raceway is increased during working operation, and causing the premature seizure or fatigue damage of the bearing, thereby greatly prolonging the service life of the bearing.
(2) According to the invention, the outer ring and the inner ring of the bearing are subjected to quenching and tempering by adopting a high-speed upsetting and cold rolling technology, so that the density of the surface layer and the inner structure is high, the depth of a forged decarburized layer is measured to be 0.03mm, and the performance of the surface layer structure and the inner structure after the forging is greatly improved compared with that after the ordinary hot forging. The metal streamline of the internal organization is parallel to the channel after cold rolling, the metal streamline in reprocessing can not be damaged, and the fatigue life of the bearing in operation is ensured.
(3) Long bearing operation may cause lubrication failure leading to fatigue failure in bearing life. In the trial production of the long-life bearing, polyether and ester long-life lubricating grease with special performance is adopted. The lubricating grease with special performance and long service life can improve the fatigue life by more than one time by changing the thickness of the lubricating grease film.
(4) The bearing provided by the invention is made of an SKF3 bearing steel material in a foreign standard, the content of harmful elements in the SKF3 material is much smaller than that of domestic bearing steel GCr15, and the bearing has excellent properties of good comprehensive performance, high and uniform hardness after quenching and tempering, good wear resistance, high contact fatigue strength and the like.
(5) The test run of the enhanced life tester was run smoothly at L10t for up to 825 hours. The K value is more than or equal to 15 times, and the test reaches the expectation. And test data analysis is carried out, and the design requirement of the long-life bearing is met. After the test operation is finished, the bearing is dissected and analyzed, and no damage is found. The grease appearance is normal, the channel and the steel ball are intact, and no fatigue damage point exists. The test life time reaches the expectation, the reliability is 99.8 percent, and the design requirement is met.
(6) Compared with the similar products, the service life of the bearing of the invention is as follows: the bearing strengthening life tester achieves a test value K = 15. The factory working condition is that the machine is actually installed and operated, and the continuous operation time exceeds two years. The service life of the bearing is 2.5 times of that of a bearing imported from abroad.
Drawings
FIG. 1 is a surface structure diagram (isothermal annealed surface structure 500X) of an inner ring and an outer ring of a high-speed upset bearing after annealing;
FIG. 2 is a diagram showing the internal structure of the bearing inner ring and outer ring after annealing (isothermal annealing surface structure 500X);
FIG. 3 is a surface structure diagram (isothermal annealing surface structure 500X) of an inner ring and an outer ring of a bearing after ordinary hot forging;
FIG. 4 is an internal structure diagram (isothermal annealing surface structure 500X) of an inner ring and an outer ring of a bearing after ordinary hot forging;
FIG. 5 is a schematic view showing the distribution direction of the metal flow lines of the outer ring of the bearing;
FIG. 6 is a graph comparing oil film thickness at a contact area of lubricating grease and base oil;
FIG. 7 is a graph of fatigue life of a bearing versus λ;
FIG. 8 is a diagram showing the stress condition of the bearing in the belt pulley transmission;
FIG. 9 is a graph showing a temperature change of a bearing in a life strengthening test;
FIG. 10 is a graph illustrating RMS, Peak, and kurtosis values for enhanced lifetime tests;
FIG. 11 is a comparative graph of life tests of similar bearing products.
Detailed Description
In order to better understand the invention, the following examples further illustrate the content of the invention, but the content of the invention is not limited to the following examples, and the examples should not be construed as limiting the scope of the invention.
The invention improves the four aspects of technical design, manufacturing process, bearing lubricating grease selection and bearing manufacturing materials, and the improved bearing can obviously prolong the service life and is wear-resistant and high-temperature-resistant.
The working clearance Gr of the bearing is calculated and selected according to the following steps:
calculating the maximum contact stress according to the maximum load bearing:
in the formula: pmax-maximum Hertz contact stress;
ea-contact ellipse major axis coefficients;
eb-contact ellipse minor axis coefficients;
q is the maximum load of the rolling body;
sigma rho is the sum of main curvatures at the contact points of the steel ball and the roller path;
f (rho) -main curvature difference function of two contact bodies of the steel ball and the raceway;
ρ1Ⅰ-the curvature of the steel ball in the principal plane i;
ρ1Ⅱ-the curvature of the steel ball in the principal plane ii;
ρ2Ⅰ-the curvature of the raceway in the principal plane i;
ρ2Ⅱ-the curvature of the raceway in the principal plane ii;
② calculating elastic deformation
In the formula: i, elastic approach of the steel ball and the inner ring raceway;
e, elastic approach of the steel ball and the outer ring raceway;
e-elastic approach coefficient;
selecting the working clearance Gr of the bearing according to the elastic deformation:
in the formula: a Gr' bearing is provided with a radial clearance;
Δ ui — the amount of reduction in play caused by the temperature of the inner ring being higher than the temperature of the outer ring;
delta ue is the amount of reduction of the play caused by the temperature of the outer ring being higher than the temperature of the outer ring;
r-the amount of play increase caused by radial deformation of the bearing during operation.
And (II) the inner ring and the outer ring of the bearing are manufactured and molded by adopting high-speed upsetting and cold rolling technology, the density of internal tissues is high, the surface tissues and the internal tissues of the annealed high-speed upset bearing inner ring and outer ring are shown in figures 1 and 2, and the depth of the forged decarburized layer of the inner ring and the outer ring of the bearing is 0.03 mm. The surface structures and the internal structures of the inner ring and the outer ring of the bearing after the common hot forging are shown in figures 3 and 4, and the depth of the forged decarburized layer of the bearing treated by the method is measured to be 0.115 mm.
In addition, the metal flow lines of the internal structure after cold rolling are parallel to the channel. As shown in FIG. 5, the distribution of the metal wire flow of the bearing outer ring can be seen, the position profile of the channel can be kept basically parallel to the forging wire flow, the metal wire flow in reprocessing can not be damaged, and the fatigue life of the bearing in operation is ensured.
And (III) the lubricating oil adopted in the bearing consists of polyether and ester fully-synthetic oil and a polyurea thickening agent, wherein the mass ratio of the polyether and ester fully-synthetic oil to the polyurea thickening agent is 8: 2.
the oil film lubrication parameter lambda is calculated according to the following formula:
wherein: k is a radical ofλ-constants related to the type of bearing;
dm-pitch circle diameter;
ni-inner ring workpiece rotational speed, unit r/min;
P0bearing equivalent static load in N.
Substituting the relevant parameters of the bearing into the formula to calculate: lambda is more than or equal to 4.2.
The lubricating grease is long-life lubricating grease Q954 with kinematic viscosity of 98CST. The comparison of the oil film thickness of the contact area of the lubricating grease and the base oil is shown in fig. 6, and as shown in the figure, when the long-life lubricating grease Q954 is selected, the oil film thickness is obviously higher than that of the common base oil contact area.
The oil film lubrication parameter λ is made to affect lubrication (see fig. 7), and it can be seen that the lubrication state has a significant effect on fatigue life. It is seen in fig. 7 that the fatigue life decreases sharply when λ is less than 1; and the fatigue life is doubled when the lambda is more than 4.
And fourthly, the steel material selected for manufacturing the bearing is SKF3 bearing steel material. Harmful chemical elements influencing the fatigue life in bearing manufacturing materials are mainly oxygen (O) and titanium (Ti), so that the invention selects the foreign standard SKF3 bearing steel material.
The content of harmful chemical element components influencing the fatigue life in SKF3 is compared with that of domestic steel:
as seen from the table, the content of harmful elements in the SKF3 material is much smaller than that of domestic bearing steel GCr15, and the SKF3 material has the excellent properties of good comprehensive performance, high and uniform hardness, good wear resistance and high contact fatigue strength after quenching and tempering.
(V) the service life of the strengthening test of the bearing is calculated according to the following formula:
in the formula: l10h — basic rated life test value (hours);
c, bearing rated dynamic load;
p-bearing equivalent test load:
n-test motor speed.
The method for calculating the bearing equivalent test load P is as follows: according to the actual working condition, the motor is transmitted by a belt pulley, the belt pulley structure generates radial load, the load acting on the wheel shaft is a function of the resultant force of tension load, and the transmission force formula of the belt is as follows:
wherein: ft is the transmission force of the belt, unit N;
n-transmission power, unit KW;
n-the rotation speed of the belt pulley, unit r/min;
r-effective radius of the pulley in mm.
Load force acting on the bearing:
wherein: fb-Belt factor, 2.5
fw-impact load coefficient, textile machinery fw is selected: 1.5.
Substituting into a formula:
F＝1.5×2.5×（105050000/75000）＝ 5252.5 （N）
after each belt F is determined, the actual equivalent load P' acting on the bearing is:
P′ ＝ 4 F
because the above equation calculates:
f-belt transmission bearing load 5252.5N
P′＝ 4×5252.5＝ 21.01 KN
Setting parameters of the life tester:
(1) setting P/C ratio coefficient
P/C is 24.06/40.75 is 0.59, NACKK (Japan) 6308 bearing strengthening life test parameters are met:
c-rated bearing load;
p-bearing equivalent test load:
P = P′+τ = 21.01+4.05=24.06（KN）;
tau-SKF lubricating grease life radial load test parameters: selecting 3.05KN for tau radial load
(2) Formula for calculating time of reinforced life test
(neglecting the temperature coefficient fT and the load coefficient fP in the test)
The rotating speed n of the motor is 1500 r/min under the selected working condition
Substituting the parameters into a formula: calculating time of the bearing life strengthening test:
L10h =6670/1500×（40.75/24.06）³ = 54 h
(3) weight of loading weight of testing machine
F ＝2P/9.8/100
＝2×24.06/9.8/100
＝48.12/9.8/100
＝49.1（Kg）
The tester actually loads a weight of 49.1KG (additional load for testing the life of lubricating oil). The test run is carried out under the heavy load state, if the test run L10t reaches 270 hours, the K (L10 t/L10 h) value is more than or equal to 5 times of the calculation time, the bearing is not damaged (the lubricating grease is normal), the service life fatigue reliability is met, and the proposed requirement condition can be met.
Test conclusion of enhanced Life test
(1) Determination by timing test
The timed trial ran smoothly with L10t for 825 hours. The K (L10 t/L10 h) value is more than or equal to 15 times, and the test reaches the expectation. And test data analysis is carried out, and the design requirement of the long-life bearing is met. The temperature change curve during the test is shown in FIG. 9. The plot of the root mean square, peak and kurtosis values in the experiment is shown in FIG. 10.
(2) Conclusion of the experiment
Calculating the service life: l10h 54h
Timing test time: l10t 825 h;
K（L10t/ L10h）= 825/54 ≥ 15
firstly, judging: the test is qualified, and the requirement of the bearing with long service life is met.
After the test operation is finished, the bearing is dissected and analyzed, and no damage is found. The grease appearance is normal, the channel and the steel ball are intact, and no fatigue damage point exists. The test life time reaches the expectation, and the reliability is 99.8%. Meets the design requirements.
Secondly, the service life of the bearing is compared with that of similar products: the service life of the bearing is 2.5 times of that of a bearing imported from abroad. The life ratio of the inventive bearing to the imported bearing and the domestic brand bearing (shown in fig. 11).
According to the high service life reliability indexes of rolling bearing products:
the value of a universal bearing (ball bearing) K (L10 t/L10 h) is more than or equal to 12
The bearing strengthening life tester achieves the test K (L10 t/L10 h) value of more than or equal to 15. The actual installed running time of the working condition of the factory exceeds two years.
Claims (8)
1. The utility model provides a high temperature resistant textile motor bearing of long-life which characterized in that the work play Gr of bearing is selected according to the calculation of following step:
calculating the maximum contact stress according to the maximum load bearing:
wherein: pmax-maximum Hertz contact stress;
ea-contact ellipse major axis coefficients;
eb-contact ellipse minor axis coefficients;
q is the maximum load of the rolling body;
sigma rho is the sum of main curvatures at the contact points of the steel ball and the roller path;
f (rho) -main curvature difference function of two contact bodies of the steel ball and the raceway;
ρ1Ⅰ-the curvature of the steel ball in the principal plane i;
ρ1Ⅱ-the curvature of the steel ball in the principal plane ii;
ρ2Ⅰ-the curvature of the raceway in the principal plane i;
ρ2Ⅱ-the curvature of the raceway in the principal plane ii;
② calculating elastic deformation r
Wherein: i, elastic approach of the steel ball and the inner ring raceway;
e, elastic approach of the steel ball and the outer ring raceway;
e-elastic approach coefficient;
selecting the working clearance Gr of the bearing according to the elastic deformation:
in the formula: a Gr' bearing is provided with a radial clearance;
Δ ui — the amount of reduction in play caused by the temperature of the inner ring being higher than the temperature of the outer ring;
delta ue is the amount of reduction of the play caused by the temperature of the outer ring being higher than the temperature of the outer ring;
r-the amount of play increase caused by radial deformation of the bearing.
2. The long-life high-temperature-resistant textile motor bearing of claim 1, wherein the inner ring and the outer ring of the bearing are manufactured and formed by high-speed upsetting ferrules and cold rolling technology; the high-speed upsetting ferrule adopts a medium-frequency induction heating technology, the temperature is controlled to be 1110-1170 ℃, complete austenitization is ensured, and secondary net-shaped carbide precipitation is inhibited through rapid cooling; meanwhile, the isothermal spheroidizing annealing is protected by the aminopropane atmosphere, so that the depth of the forged decarburized layer of the inner ring and the outer ring of the bearing is ensured to be 0.03 mm.
3. The long-life high-temperature-resistant textile motor bearing of claim 1, characterized in that the lubricating oil used in the bearing is composed of polyether + ester fully synthetic oil and polyurea thickener, the mass ratio of polyether + ester fully synthetic oil to polyurea thickener is 8: 2.
4. a long life high temperature resistant textile motor bearing according to claim 3, characterized in that the oil film lubrication parameter λ is calculated according to the following formula:
in the formula: k is a radical ofλ-constants related to the type of bearing;
dm-pitch circle diameter;
ni-inner ring working speed, unit r/min;
P0bearing equivalent static load in units N;
substituting the relevant parameters of the bearing into the formula to calculate: lambda is more than or equal to 4.2.
5. A long life high temperature resistant textile motor bearing as claimed in claim 4, characterized in that said grease is selected from long life grease Q954 with kinematic viscosity 98-CST。
6. The long-life high-temperature-resistant textile motor bearing of claim 1, characterized in that the steel material selected for manufacturing the bearing is SKF3 bearing steel material.
7. A long life high temperature resistant textile motor bearing according to claim 1, wherein said bearing is characterized by a reinforcement test life time calculated according to the formula:
in the formula: l10h — nominal life calculation test value, hours;
c, bearing rated dynamic load;
p-bearing test equivalent load:
n-test motor speed.
8. A long life high temperature resistant textile motor bearing according to claim 7, characterized in that the bearing equivalent test load P is calculated as follows:
according to the actual working condition, the motor is transmitted by a belt pulley, the belt pulley structure generates radial load, the load acting on the wheel shaft is a function of the resultant force of tension load, and the transmission force formula of the belt is as follows:
wherein: ft is the transmission force of the belt, unit N;
n-transmission power, unit KW;
n-the rotation speed of the belt pulley, unit r/min;
r-effective radius of belt pulley, unit mm;
load force acting on the bearing
Wherein: fb-Belt coefficient;
fw-impact load coefficient;
after each belt F is determined, the actual equivalent load P' acting on the bearing is:
the bearing equivalent test load P is:
wherein: tau-radial load test parameters of the lubricating grease life.
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| CN113357269A (en) * | 2021-07-05 | 2021-09-07 | 太原科技大学 | Method for manufacturing outer ring of rolling bearing |
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| CN113357269B (en) * | 2021-07-05 | 2022-08-12 | 太原科技大学 | Method for manufacturing outer ring of rolling bearing |
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