CN111709098B - Method for reducing friction coefficient of bearing by changing lubricating oil under variable load - Google Patents
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Abstract
The invention belongs to the technical field of sliding bearings, and particularly relates to a method for reducing the friction coefficient of a bearing by changing lubricating oil under variable load, which is realized based on an oil-lubricated sliding bearing with an oil row distributor, and comprises the following specific steps: measuring the maximum load fluctuation range of the sliding bearing during working and obtaining the known viscosity eta0The c-v/w curve of the lubricating oil is set, the low value fluctuation range L% of the friction coefficient is set, the viscosity values of the lubricating oil used in different load ranges are deduced one by one from the maximum load of the sliding bearing to the direction of the minimum load, the lubricating oil with different viscosities is supplied aiming at different load ranges through an oil row distributor, the bearing is ensured to run under a lower friction coefficient level, the friction power consumption of the bearing is reduced, the bearing abrasion is reduced, the service life and the running performance of the bearing are prolonged, and the calculation analysis of the system power loss and the like is facilitated; simple structure, ingenious design concept, low manufacturing cost, wide market prospect and environment-friendly application.
Description
The technical field is as follows:
the invention belongs to the technical field of sliding bearings, and particularly relates to a method for reducing the friction coefficient of a bearing by changing lubricating oil under variable load, which supplies lubricating oil with different viscosities aiming at different load ranges, controls the friction coefficient of the bearing within a low value range, and can quantitatively select the viscosity of the required lubricating oil.
Background art:
the bearing is widely applied to various fields of national economy and national defense affairs. In actual work, the load borne by the bearing is not constant, and the fluctuation range is large under a plurality of working conditions, such as high-end bearings used by electric equipment, high-power engineering machinery, mining machinery and the like, can face regular or irregular load changes. When bearing load fluctuation is large, lubrication state change is easily caused, friction coefficient is rapidly increased, abrasion is aggravated, and even bearing failure is caused.
In order to solve the problem, many researches are made on the aspects of bearing structures, materials, lubricating oil additives and the like, and the service performance of the bearing is improved to a certain extent. For example, chinese patent CN201020693026.6 discloses a multi-stage composite floating sleeve sliding bearing, which comprises a bearing outer ring, a journal and a floating sleeve, wherein the floating sleeve is installed between the journal and the bearing outer ring, and at least 2 stages of the floating sleeve are arranged between the bearing outer ring and the journal; the floating sleeves are arranged in parallel along the axial direction of the shaft neck, the structure is simple, the shaft neck, the shaft hole and the floating sleeves of the bearing are loaded more uniformly, the abrasion tends to be synchronous, the uneven abrasion is reduced, and the floating capacity of the floating sleeves and the lubricating condition of the bearing are improved; the load distribution of the bearing is improved, and the service life of the bearing is prolonged; the Chinese patent CN201010617014.X discloses a spiral floating sleeve sliding bearing, which comprises a bearing outer ring, a shaft neck and a floating sleeve, wherein the floating sleeve is arranged between the shaft neck and the bearing outer ring, and a spiral groove is formed in the floating sleeve and is communicated along the radial direction; the shaft neck, the shaft hole and the floating sleeve of the bearing can be loaded more uniformly, the abrasion tends to be synchronous, and the uneven abrasion is reduced; the floating capacity of the floating sleeve and the lubrication condition of the bearing are improved; the load distribution of the bearing is improved, and the service life of the bearing is prolonged; chinese patent CN201620591081.1 discloses a compressor, which comprises a crankshaft and an upper bearing, wherein the long shaft of the crankshaft is installed in the upper bearing, a flexible groove is formed on the lower end surface of the upper bearing, an annular groove is formed on the outer surface of the crankshaft or the inner hole wall of the upper bearing, and the annular groove and the flexible groove are matched with each other, so that the contact stress distribution of the lower end of the long shaft of the crankshaft and the lower end of the upper bearing can be improved, the load distribution of the upper bearing is more reasonable, the problem of abrasion between the long shaft and the upper bearing of the crankshaft of the large-displacement double-cylinder or multi-cylinder rotor compressor is solved, and the service life of the compressor is prolonged; these prior art techniques all structurally improve the service life of the bearing. However, under complex conditions, the ability of a single lubricating medium to maintain good lubrication is limited, and when the load fluctuation is large, the lubricating state can still be changed, so that the friction coefficient is increased, the wear is aggravated, and a series of conditions such as bearing failure are caused. Therefore, in order to achieve better and more stable antifriction and antifriction effects, improve bearing performance and reduce system friction power consumption, it is necessary to adjust the lubrication state when the load changes, so that the friction coefficient is always at a low level, which is also important for accurate prediction of the service life of the part, calculation and analysis of system power loss, and the like.
For a fixed friction pair, a Stribeck (Stribeck) curve, i.e., a relationship curve between a friction coefficient and a bearing characteristic number (η × V/W), can be obtained through experiments, where η is the lubricating oil environment viscosity, V is the sliding speed, and W is the load. Three lubrication states of the friction pair are judged by a Stribeck (Stribeck) curve: boundary lubrication, mixed lubrication, and hydrodynamic lubrication. With the increase of the characteristic number of the bearing, the lubricating state can be gradually changed, and the friction coefficient value shows a rule of firstly reducing and then increasing in the process from boundary lubrication, mixed lubrication and then fluid dynamic pressure lubrication. There will always be an optimum lubrication condition such that the bearing friction coefficient reaches a minimum. Therefore, it is highly desirable to design a method for reducing the friction coefficient of a bearing by changing the lubricating oil under a variable load, which supplies the lubricating oil with different viscosities for different load ranges, controls the friction coefficient of the bearing within a low value range, and can quantitatively select the viscosity of the required lubricating oil.
The invention content is as follows:
the invention aims to overcome the defects of the prior art, and aims to design a method for reducing the friction coefficient of a bearing by changing lubricating oil under variable load, so that the lubricating oil with different viscosities can be correspondingly supplied for different load ranges even under the condition that the load fluctuation during the operation of the bearing is large, the friction coefficient of the bearing can be controlled within a low value range, the bearing can be operated under low friction power consumption, and the viscosity of the required lubricating oil can be quantitatively selected.
In order to achieve the above purpose, the invention relates to a method for reducing the friction coefficient of a bearing by changing lubricating oil under variable load, which is realized on the basis of an oil-lubricated sliding bearing with an oil row distributor, and comprises the following specific steps:
s1, firstly, measuring the maximum load fluctuation range of the sliding bearing during working to be [ Wa，Wb]Wherein W isb>Wa；
S2, measuring and acquiring the known viscosity eta of the sliding bearing0The c-v/w curve of the lubricating oil of (1) is: a new function curve obtained by removing eta from the abscissa bearing characteristic number (eta multiplied by V/W) in a Stribeck (Stribeck) curve is named as a c-V/W curve, the abscissa of the c-V/W curve is V/W, the ordinate is a friction coefficient cof, wherein V is a sliding speed, and W is a load; the measurement method of the c-v/w curve is the same as that of the Stribeck (Stribeck) curve, and the measurement method is that on a common friction tester, a sliding bearing under the actual working condition forms a friction pair, and the lubricating medium is viscosity eta0The common lubricating oil takes the rotating speed of the bearing during working as a testing rotating speed, measures the friction coefficient of the bearing under different loads, draws a Stribeck curve of the bearing according to the measured data, and removes eta in a horizontal coordinate to obtain a c-v/w curve;
s3, setting a low value fluctuation range L% of the friction coefficient of the bearing, taking the lowest value of the friction coefficient in the c-v/w curve obtained in the step S2 as a reference value, and respectively representing the lower boundary line and the upper boundary line of the friction coefficient fluctuation range L% by two straight lines in the c-v/w curve; the upper boundary line of the friction coefficient fluctuation range is intersected with the c-v/w curve to obtain two intersection points, and the abscissa corresponding to the two intersection points is respectively
And
because V is a fixed value, the load value W corresponding to two intersection points is obtainedn>Wm，WnAnd WmAll at the maximum load [ W ] of the sliding bearinga，Wb]Within the range, the load of the sliding bearing is explained to be [ W ]m，Wn]When the friction coefficient of the sliding bearing fluctuates in the internal fluctuation, the fluctuation of the friction coefficient of the sliding bearing does not exceed L percent, and W can be obtained at the same timemAnd WnThe exact value of (d); for a fixed friction pair, the c-v/w curve shapes of lubricating oil with different viscosities are basically the same, but the positions in the coordinate system are relatively translated leftwards or rightwards, so that for the lubricating oil with different viscosities, the lubricating oil with different viscosities slidesThe load ranges corresponding to the low-value fluctuation range L% of the friction coefficient of the movable bearing are different;
s4 maximum load W from sliding bearingbTowards the minimum load WaThe same abscissa value can correspond to different ratios of viscosity to load according to the overlapping characteristic of the Stribeck curves of the lubricating oil with different viscosities when the rotating speed V is the same, namely the same abscissa value has an equality relationship of
It is then possible to derive the known viscosity η from the c-v/w diagram0And two corresponding load values WnAnd WmDeducing the fluctuation range [ W ] of the maximum loada，Wb]Several viscosity values of the lubricating oil can be used, and different load ranges with different viscosity values can be obtained; lubricating oil with corresponding viscosity value is used in corresponding load range, and the fluctuation range of the friction coefficient of the sliding bearing does not exceed L%;
s5, the viscosities of the lubricating oil obtained in the step S4 and the corresponding load parameters are input into a lubricating oil supply system, an oil row distributor on the bearing is provided with a plurality of passages, each passage is one-way, one passage is communicated during each work, each passage fixedly conveys lubricating oil with one viscosity, the lubricating oil supply system controls the communication or the closing of each passage of the oil row distributor according to different load ranges, the lubricating oil with the corresponding viscosity of the bearing is supplied through the communicated passages, and the effect of reducing the friction coefficient of the bearing through changing the lubricating oil under the variable load is achieved.
The specific derivation process of step S4 of deriving the viscosity values of the lubricating oil one by one according to the present invention is:
SS1, known viscosity η0Corresponding two load values WnAnd WmThe abscissa values in the Stribeck curve are respectively
And
then by an equality relationship
The corresponding viscosity can be calculated
Then passes through the horizontal coordinate value eta0×V/WmCorresponding equality relationship
To obtain the viscosity eta1Corresponding another load value W1The viscosity eta can be determined1The position of the c-v/W curve in coordinates is within the load range [ W ]1，Wb](Wb>W1) Internal use viscosity of eta1In the case of the lubricating oil of (1), the fluctuation of the friction coefficient of the sliding bearing does not exceed L%, and the load is W1And WbThe friction coefficient reaches the maximum fluctuation value; judging if Wa≥W1I.e. by
Illustrating the bearing in the maximum load fluctuation range Wa，Wb]The friction coefficient does not exceed the fluctuation range L% during internal work;
SS2 if Wa<W1I.e. maximum load fluctuation range [ Wa，Wb]Exceed [ W ]1，Wb]The maximum load fluctuation range [ W ] of the bearing is explaineda，Wb]Inner [ W ]a，W1]The friction coefficient can exceed the fluctuation range L% during operation, so when the bearing working load is less than W1Time-induced viscosity η2From the equation relationship
To obtain
By
To obtain
Description in the load range [ W2，W1](W1>W2) Internal use viscosity of eta2In the case of the lubricating oil of (1), the fluctuation of the friction coefficient of the sliding bearing does not exceed L%, and the load is W2And W1When the friction coefficient reaches the maximum value; judging if Wa≥W2I.e. by
Illustrating the bearing in the maximum load fluctuation range Wa，Wb]The friction coefficient does not exceed the fluctuation range L% during internal work;
SS3 if WaIs still less than W2I.e. maximum load fluctuation range [ Wa，Wb]Exceed [ W ]2，Wb]The maximum load fluctuation range [ W ] of the bearing is explaineda，Wb]Inner [ W ]a，W2]The friction coefficient can exceed the fluctuation range L%, so when the working load of the bearing is less than W2Time-introduced viscosity of η3Of lubricating oil of
To obtain
By
To obtain
Description in the load range [ W3，W2](W2>W3) Internal use viscosity of eta3In the case of the lubricating oil of (1),the friction coefficient fluctuation of the sliding bearing is not more than L percent, and the load is W3And W2When the friction coefficient reaches the maximum value; judging if Wa≥W3I.e. by
Illustrating the bearing in the maximum load fluctuation range Wa，Wb]The friction coefficient does not exceed the fluctuation range L% during internal work;
SS4, and so on, if WaIs still less than Wi-1I.e. maximum load fluctuation range [ Wa，Wb]Exceed [ W ]i-1，Wb]The maximum load fluctuation range [ W ] of the bearing is explaineda，Wb]Inner [ W ]a，Wi-1]The friction coefficient can exceed the fluctuation range L%, so when the working load of the bearing is less than Wi-1Time-induced viscosity ηiOf lubricating oil of
To obtain
By
To obtain
A load W can always be determinediSo that W isi≤WaI.e. by
When the load is Wi、Wi-1、Wi-2…W1，WbWhen using the respective viscosity etaiThe friction coefficient of the sliding bearing reaches the maximum value, and the sliding bearing fluctuates in the maximum load fluctuation range [ W ]a，Wb]The friction coefficient does not exceed the fluctuation range L% during internal work, and the lubricating oil viscosity values are deduced one by one.
In step S4, the viscosity values of the lubricating oil are derived one by one from the maximum load toward the minimum load, and the viscosity values of the lubricating oil can also be derived from the minimum load toward the maximum load, and the same principle applies.
The invention relates to load detection of an oil lubrication sliding bearing, which is obtained by adopting a mechanical control system or by installing a corresponding sensor.
In step S5, because the oil supply delay time of different lubricating oil supply systems is different and the change of the mixed viscosity of the lubricating oil in the bearing clearance is not transient and has a transition time in the process of replacing the lubricating oil with different viscosity, the replacement of the lubricating oil can ensure that the friction coefficient does not exceed the set fluctuation range by setting different load advance amounts according to different working conditions.
The viscosity of the lubricating oil according to the invention is influenced by the temperature at the contact area of the bearing, so that the viscosity value used for the calculation must be the viscosity value at the corresponding temperature.
The lubricating oils of different viscosities used in the sliding bearing according to the present invention may be the same type of lubricating oil or different types of lubricating oils or lubricating oil additives.
Compared with the prior art, the technical scheme of the invention has the advantages that by designing a plurality of oil supply passages, lubricating oil with different viscosities is supplied aiming at different load ranges, the bearing is ensured to run at a lower friction coefficient level, the friction power consumption of the bearing is reduced, the bearing abrasion is reduced, the service life and the running performance of the bearing are prolonged, and the calculation and analysis of the system power loss and the like are facilitated; simple structure, ingenious design concept, low manufacturing cost, wide market prospect and environment-friendly application.
Description of the drawings:
fig. 1 is a schematic structural diagram of an oil-lubricated sliding bearing according to the present invention.
Fig. 2 is a schematic cross-sectional structural view of a section a-a of a sliding bearing according to the present invention.
FIG. 3 is a graph of Stribeck (Stribeck) in which A represents boundary lubrication, according to the present invention; b represents mixed lubrication (partial elastohydrodynamic lubrication); c represents hydrodynamic lubrication (elastohydrodynamic lubrication); h represents a surface gap; r represents the average height of surface unevenness.
FIG. 4 is a schematic view of the c-v/w curve of lubricating oil of 2 viscosities under a defined friction pair according to the present invention.
FIG. 5 is a graph of the viscosity derivative of a c-v/w curve for a defined friction pair according to the present invention.
FIG. 6 is a c-v/w plot of a PAO10 lubricating oil at room temperature in accordance with the present invention.
FIG. 7 is a c-v/w curve viscosity derivative of a sliding bearing at room temperature according to the present invention.
The specific implementation mode is as follows:
the present invention will be described in detail below with reference to specific embodiments and accompanying drawings.
Example 1:
the method for reducing the friction coefficient of the bearing by changing the lubricating oil under the variable load according to the embodiment is realized by mounting an oil drain distributor 6 on a common commercially available sliding bearing to form an oil-lubricated sliding bearing, and the main structure of the oil-lubricated sliding bearing comprises the following steps: the oil pump comprises a bearing seat 1, a bush 2, an oil pool 3, an oil filling hole 4, a connecting piece 5, an oil row distributor 6 and a rotating shaft 7; the bearing seat 1 is used for fixing the bush 2; an oil filling hole 4 is formed in the bushing 2, the oil filling hole 4 is of an obliquely extending cylindrical structure, the upper end of the oil filling hole 4 is connected with an oil drain distributor 6 through a connecting piece 5, and the lower end of the oil filling hole 4 extends into the bushing 2; the oil pool 3 is positioned on the inner surface of the bush 2, the oil pool 3 is of a cavity structure and is used for storing oil, and the oil pool 3 is communicated with the oil injection hole 4; the rotating shaft 7 is arranged in the bush 2, and the rotating shaft 7 rotates relative to the bush 2; the oil discharge distributor 6 is externally connected with a lubricating oil supply system, so that lubricating oil in the lubricating oil supply system can be injected between the bush 2 and the rotating shaft 7 through the oil filling hole 4.
The lubrication mode of the sliding bearing used in the embodiment is oil lubrication, and the method for reducing the friction coefficient of the bearing by changing the lubricating oil under variable load is specifically carried out according to the following steps:
s1, measuring a bearing with the steel block and the glass as a friction pair by using a commercially available mechanical control system to obtain that the maximum load fluctuation range of the bearing when the bearing works under a certain occasion is 0.28-21 MPa;
s2, on the surface contact lubricating oil film measuring instrument, a friction pair is formed by a steel block and a glass disc, and the lubricating medium is selected from viscosity eta0The PAO10 lubricating oil with the viscosity of 104.3 mPas, the relative sliding speed V between the friction pairs is 20mm/s, the friction coefficients between the friction pairs under different loads are measured, the Stribeck curve is drawn according to the measured data, eta in the abscissa is removed, and a c-V/w curve can be obtained; as shown in FIG. 6, the abscissa of the c-V/W curve is V/W, and the ordinate is the friction coefficient cof, where V is the sliding velocity and W is the load;
s3, setting the upper limit value of the friction coefficient of the bearing to be 0.01, taking the lowest value of the friction coefficient in the c-v/w curve obtained in the step S2 as a reference value, and respectively representing the lower boundary line and the upper boundary line of the fluctuation range of the friction coefficient by two straight lines in the c-v/w curve; the upper boundary line of the fluctuation range of the friction coefficient intersects with the c-v/w curve to obtain two intersection points, and the abscissa corresponding to the two intersection points obtained from FIG. 6 is
And
namely obtain Wn＝2.67MPa,WmWhen the load is between 0.3 and 2.67MPa, the friction coefficient of the sliding bearing is not more than 0.01; for a fixed friction pair, the c-v/w curve shapes of lubricating oil with different viscosities are basically the same, but the positions in a coordinate system translate leftwards or rightwards relatively, so that the load ranges corresponding to the low-value fluctuation ranges of the friction coefficients of the sliding bearing are different for the lubricating oil with different viscosities;
s4 maximum load W from sliding bearingbTowards the minimum load WaThe viscosity values of the lubricating oil used in different load ranges are deduced one by one, and when the rotating speed V is the same, the same abscissa value can correspond to different viscosity-load ratios according to the overlapping characteristic of Stribeck curves of the lubricating oil with different viscositiesThe values, i.e. the same abscissa value, being related by an equality
It is then possible to derive the known viscosity η from the c-v/w diagram0And two corresponding load values WnAnd WmDeducing several viscosity values of the lubricating oil used in the maximum load fluctuation range of 0.28-21 MPa, and obtaining different load ranges used by different viscosity values; lubricating oil with corresponding viscosity value is used in corresponding load range, so that the friction coefficient of the sliding bearing does not exceed 0.01; the specific derivation process is as follows:
SS1, known viscosity η0Two load values W corresponding to 104.3mPa · snAnd WmThe abscissa values in the Stribeck curve are respectively
And
then pass the abscissa value
Corresponding equality relationship
The corresponding viscosity can be calculated
Then passes the horizontal coordinate value
Corresponding equality relationship
To obtain the viscosity eta1Corresponding another load value
The viscosity eta can be determined1The c-v/w curve of (a) is in the position of the coordinate, and the viscosity is eta within the load range of 2.3-21 MPa1When the lubricating oil is 819.4 mPas, the friction coefficient of the sliding bearing is not more than 0.01, and when the load is W12.3MPa and WbWhen the friction coefficient is 21MPa, the maximum fluctuation value is reached; the viscosity of the PAO40 at room temperature is 819.4mPa & s, which just meets the viscosity requirement;
SS2, the maximum load fluctuation range of the bearing is 0.28-21 MPa, the maximum load fluctuation range exceeds the range of 2.3-21 MPa obtained in SS1, the friction coefficient is higher than 0.01 when the bearing works in the load fluctuation range of 0.28-2.3 MPa, and therefore, the viscosity eta is introduced when the working load of the bearing is less than 2.3MPa2From the equation relationship
To obtain
By
To obtain
Indicating that the viscosity is eta in the range of 0.26-2.3MPa2The friction coefficient of the sliding bearing is not more than 0.01, and the maximum value of the friction coefficient is reached when the load is 0.26MPa and 2.3 MPa; the viscosity of the PAO8 lubricating oil at room temperature is 86.53mPa & s & lt 89.85mPa & s, and the lubricating oil can not be directly used, while the viscosity of the PAO10 lubricating oil at room temperature is 104.3mPa & s, and the lubricating oil with the viscosity of 89.85mPa & s can be mixed by the PAO8 and the PAO10 according to a certain proportion; the lubricating oil is matched with PAO40 to ensure that the friction coefficient of the bearing does not exceed 0.01 when the bearing works between 0.26MPa and 21 MPa;
the maximum load fluctuation range of the bearing is 028-21 MPa; supply viscosity eta when the load is between 0.28 and 2.3MPa2A PAO8+ PAO10 mixed oil of 89.85 mPas, and the viscosity eta is provided when the load is 2.3-21 MPa1PAO40 lubricating oil of 819.4 mPas ensures that the friction coefficient is not more than 0.01 all the time when the bearing works;
s5, inputting the viscosities of the 2 lubricating oils obtained in S4 and corresponding load parameters into a lubricating oil supply system, wherein an oil row distributor on a bearing is provided with 2 passages, each passage is unidirectional, one passage is conducted during each work, each passage fixedly conveys lubricating oil with one viscosity, aiming at different load ranges, the lubricating oil supply system controls the conduction or the closing of each passage of the oil row distributor, and the lubricating oil with the corresponding viscosity of the bearing is supplied through the conducted passages; the purpose of reducing the friction coefficient of the bearing by changing the lubricating oil under the variable load is achieved.
In S4 according to the present embodiment, the lubricating oil viscosity values are derived one by one from the maximum load toward the minimum load, or the lubricating oil viscosity values may be derived from the minimum load toward the maximum load, and the same principle applies.
The load detection of the oil lubrication sliding bearing related to the embodiment is obtained by a commercially available mechanical control system or by installing a corresponding sensor.
In step S5 according to this embodiment, the oil supply delay times of different lubricating oil supply systems are different, and in the process of replacing lubricating oil with different viscosities, the change of the mixed viscosity of the lubricating oil in the bearing gap is not transient, and there is a transition time.
The viscosity of the lubricating oil related to the embodiment is greatly influenced by the temperature of the contact area of the bearing, so the viscosity value used for calculation is determined to be the viscosity value at the corresponding temperature.
The lubricating oil used for the sliding bearing according to the present embodiment is commercially available lubricating oil.
The lubricating oils of different viscosities used in the sliding bearing according to the present embodiment are the same type of lubricating oil or different types of lubricating oil or lubricating oil additives.
Claims (6)
1. A method for reducing the friction coefficient of a bearing by changing lubricating oil under variable load is characterized in that the method is realized based on an oil-lubricated sliding bearing with an oil row distributor, and the specific steps comprise:
s1, firstly, measuring the maximum load fluctuation range of the sliding bearing during working to be [ Wa，Wb]Wherein W isb>Wa；
S2, measuring and acquiring the known viscosity eta of the sliding bearing0The c-v/w curve of the lubricating oil of (1) is: a new function curve obtained by removing eta from the abscissa bearing characteristic number (eta multiplied by V/W) in the Sterbek curve is named as a c-V/W curve, the abscissa of the c-V/W curve is V/W, the ordinate is a friction coefficient cof, wherein V is sliding speed, and W is load; the measuring method of the c-v/w curve is the same as that of the Strobeck curve, the measuring method is that on a common friction tester, a sliding bearing under the actual working condition forms a friction pair, and the lubricating medium is viscosity eta0The normal lubricating oil uses the rotating speed of the bearing during working as a testing rotating speed, measures the friction coefficient of the bearing under different loads, draws a Strobel curve of the bearing according to the measured data, and removes eta in the abscissa to obtain a c-v/w curve;
s3, setting a low value fluctuation range L% of the friction coefficient, taking the lowest value of the friction coefficient in the c-v/w curve obtained in the step S2 as a reference value, and respectively representing a lower boundary line and an upper boundary line of the friction coefficient fluctuation range L% by two straight lines in the c-v/w curve; the upper boundary line of the friction coefficient fluctuation range is intersected with the c-v/w curve to obtain two intersection points, and the abscissa corresponding to the two intersection points is respectively
And
because V is a fixed value, the load value W corresponding to two intersection points is obtainedn>Wm，WnAnd WmAll at the maximum load [ W ] of the sliding bearinga，Wb]Within the range, the load of the sliding bearing is explained to be [ W ]m，Wn]When the friction coefficient of the sliding bearing fluctuates in the internal fluctuation, the fluctuation of the friction coefficient of the sliding bearing does not exceed L percent, and W can be obtained at the same timemAnd WnThe exact value of (d); for a fixed friction pair, the c-v/w curve shapes of lubricating oil with different viscosities are the same, but the positions in a coordinate system are relatively translated leftwards or rightwards, so that the load ranges corresponding to the low-value fluctuation ranges L% of the friction coefficients of the sliding bearing are different for the lubricating oil with different viscosities;
s4 maximum load W from sliding bearingbTowards the minimum load WaThe same abscissa value can correspond to different ratios of viscosity to load according to the overlapping characteristic of the Sterbek curves of the lubricating oils with different viscosities when the rotating speeds V are the same, that is, the same abscissa value has an equality relationship of
It is then possible to derive the known viscosity η from the c-v/w diagram0And two corresponding load values WnAnd WmDeducing the fluctuation range [ W ] of the maximum loada，Wb]Several viscosity values of the lubricating oil can be used, and different load ranges with different viscosity values can be obtained; lubricating oil with corresponding viscosity value is used in corresponding load range, and the fluctuation range of the friction coefficient of the sliding bearing does not exceed L%;
s5, the viscosities of the lubricating oil obtained in the step S4 and the corresponding load parameters are input into a lubricating oil supply system, an oil row distributor on the bearing is provided with a plurality of passages, each passage is one-way, one passage is communicated during each work, each passage fixedly conveys lubricating oil with one viscosity, the lubricating oil supply system controls the communication or the closing of each passage of the oil row distributor according to different load ranges, the lubricating oil with the corresponding viscosity of the bearing is supplied through the communicated passages, and the effect of reducing the friction coefficient of the bearing through changing the lubricating oil under the variable load is achieved.
2. The method for reducing the friction coefficient of a bearing through changing lubricating oil under the variable load according to claim 1, wherein the step S4 relates to the specific derivation process of one-by-one derivation of the viscosity values of the lubricating oil as follows:
SS1, known viscosity η0Corresponding two load values WnAnd WmThe abscissa values in the strorbek curve are respectively
And
then by an equality relationship
The corresponding viscosity can be calculated
Then passes through the horizontal coordinate value eta0×V/WmCorresponding equality relationship
To obtain the viscosity eta1Corresponding another load value W1The viscosity eta can be determined1The position of the c-v/W curve in coordinates is within the load range [ W ]1，Wb](Wb>W1) Internal use viscosity of eta1In the case of the lubricating oil of (1), the fluctuation of the friction coefficient of the sliding bearing does not exceed L%, and the load is W1And WbThe friction coefficient reaches the maximum fluctuation value; judging if Wa≥W1I.e. by
Illustrating the bearing in the maximum load fluctuation range Wa，Wb]The friction coefficient does not exceed the fluctuation range L% during internal work;
SS2 if Wa<W1I.e. maximum load fluctuation range [ Wa，Wb]Exceed [ W ]1，Wb]The maximum load fluctuation range [ W ] of the bearing is explaineda，Wb]Inner [ W ]a，W1]The friction coefficient can exceed the fluctuation range L% during operation, so when the bearing working load is less than W1Time-induced viscosity η2From the equation relationship
To obtain
By
To obtain
Description in the load range [ W2，W1](W1>W2) Internal use viscosity of eta2In the case of the lubricating oil of (1), the fluctuation of the friction coefficient of the sliding bearing does not exceed L%, and the load is W2And W1When the friction coefficient reaches the maximum value; judging if Wa≥W2I.e. by
Illustrating the bearing in the maximum load fluctuation range Wa，Wb]The friction coefficient does not exceed the fluctuation range L% during internal work;
SS3 if WaIs still less than W2I.e. maximum load fluctuation range [ Wa，Wb]Exceed [ W ]2，Wb]The maximum load fluctuation range [ W ] of the bearing is explaineda，Wb]Inner [ W ]a，W2]The friction coefficient can exceed the fluctuation range L%, so when the working load of the bearing is less than W2Time-introduced viscosity of η3Of lubricating oil of
To obtain
By
To obtain
Description in the load range [ W3，W2](W2>W3) Internal use viscosity of eta3In the case of the lubricating oil of (1), the fluctuation of the friction coefficient of the sliding bearing does not exceed L%, and the load is W3And W2When the friction coefficient reaches the maximum value; judging if Wa≥W3I.e. by
Illustrating the bearing in the maximum load fluctuation range Wa，Wb]The friction coefficient does not exceed the fluctuation range L% during internal work;
SS4, and so on, if WaIs still less than Wi-1I.e. maximum load fluctuation range [ Wa，Wb]Exceed [ W ]i-1，Wb]The maximum load fluctuation range [ W ] of the bearing is explaineda，Wb]Inner [ W ]a，Wi-1]The friction coefficient can exceed the fluctuation range L%, so when the working load of the bearing is less than Wi-1Time-induced viscosity ηiOf lubricating oil of
To obtain
By
To obtain
A load W can always be determinediSo that W isi≤WaI.e. by
When the load is Wi、Wi-1、Wi-2…W1，WbWhen using the respective viscosity etaiThe friction coefficient of the sliding bearing reaches the maximum value, and the sliding bearing fluctuates in the maximum load fluctuation range [ W ]a，Wb]The friction coefficient does not exceed the fluctuation range L% during internal work, and the lubricating oil viscosity values are deduced one by one.
3. A method for reducing the friction coefficient of a bearing by changing lubricating oil under variable load according to claim 1, characterized in that the load detection of the oil-lubricated sliding bearing is obtained by a mechanical control system or by installing a corresponding sensor.
4. The method for reducing the friction coefficient of the bearing by changing the lubricating oil under the variable load according to claim 1, wherein in step S5, the change of the mixed viscosity of the lubricating oil in the bearing clearance is not transient due to different oil supply delay time of different lubricating oil supply systems and the change of the lubricating oil with different viscosity, so that the change of the lubricating oil can be ensured to not exceed the set fluctuation range by setting different load advance for different working conditions.
5. A method for reducing the friction coefficient of a bearing by transforming lubricating oil under varying load according to claim 1, characterized in that the viscosity of the lubricating oil is influenced by the temperature of the contact area of the bearing, whereby the viscosity value used for the calculation must be the viscosity value at the corresponding temperature.
6. A method of reducing the coefficient of friction of a bearing by changing the lubricating oil under varying loads as claimed in claim 1, wherein the lubricating oils of different viscosities used for the sliding bearing can be the same kind of lubricating oil or different kinds of lubricating oils.
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| JP2007333161A (en) * | 2006-06-16 | 2007-12-27 | Nsk Ltd | Manufacturing method of self-aligning roller bearing, and self-aligning roller bearing |
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| CN101893535A (en) * | 2010-06-30 | 2010-11-24 | 清华大学 | Method for testing limit operating temperature and high-temperature wear-resisting property of lubricating oil |
| CN110765617A (en) * | 2019-10-25 | 2020-02-07 | 常州市乾憬轴承科技有限公司 | Lubrication theory-based cylindrical roller bearing roller logarithmic modification design method |
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