CN112943805A - Lubricating grease supply device for space precision bearing and design method thereof - Google Patents

Lubricating grease supply device for space precision bearing and design method thereof Download PDF

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CN112943805A
CN112943805A CN202110417131.XA CN202110417131A CN112943805A CN 112943805 A CN112943805 A CN 112943805A CN 202110417131 A CN202110417131 A CN 202110417131A CN 112943805 A CN112943805 A CN 112943805A
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initial
inner sleeve
lubricating oil
lubricating
contact
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吴成伟
马建立
刘玉浩
武洪凯
张伟
马国军
韩啸
吕永涛
夏阳
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Dalian University of Technology
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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
    • 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
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • 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
    • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/08—Thermal analysis or thermal optimisation
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces

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  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
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  • Sliding-Contact Bearings (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

A lubricating grease supply device for a space precision bearing and a design method thereof belong to the technical field of automatic oil supply and long-acting lubrication of space miniature bearings. Comprises an inner sleeve and an outer sleeve, and lubricating oil is stored between the two sleeves. Wherein, the upper end and the lower end of the inner sleeve are respectively provided with an annular boss A, B outwards, and the outer surface of the boss A, B of the inner sleeve is tightly attached to the inner surface of the outer sleeve. And a through hole matched with the threaded rod is processed on the annular boss A of the inner sleeve, and an annular groove used for placing the rubber ring is arranged below the through hole. The oil seepage rate is adjusted by adjusting the interference magnitude, the surface roughness, the rotating speed and other factors, so that the aim of controlling the lubricating time according to the service time of the bearing and controlling the lubricating oil supply rate is fulfilled. The invention can fully utilize the internal space of the bearing device, improve the oil storage capacity, realize accurate long-time oil supply, and has simple structure and high reliability of the oil supply system.

Description

Lubricating grease supply device for space precision bearing and design method thereof
Technical Field
The invention belongs to the technical field of automatic oil supply and long-acting lubrication of space miniature bearings, and relates to a lubricating grease supply device for a space precision bearing and a design method thereof.
Background
The spacecraft such as a satellite generally flies in an outer space for years, an attitude control flywheel system is an important flight control device, an ultra-precise bearing is a core component of a flywheel rotor system, and the bearing is required to be low in friction power consumption and high in running precision and is required to be provided with lubricating oil or lubricating grease. However, vacuum and semi-vacuum environments are special working conditions, under the working conditions, the bearings are required to work for 3-7 years by carrying lubricating oil at one time, in addition, the pressure is reduced, and the evaporation capacity of the lubricating oil is increased, so that the lubricating oil/grease carried by the oil-containing bearing retainer cannot meet the use requirements, the lubricating oil/grease is required to be carried in a narrow space, and continuous oil supply can be realized in the aerospace environment, which puts severe requirements on the lubrication of the bearings.
Most of the existing oil storage devices for the precision bearings in the air space environment adopt two modes of porous materials or oil supply ropes to provide lubrication for the precision bearings. The porous material oil-retaining lubrication device gradually permeates the lubricating oil retained in the porous material into the lubricated part of the bearing by centrifugal force. However, there is a contradictory relationship between the oil storage capacity and the material strength of the device, and an increase in the designed oil storage capacity causes a decrease in the designed strength, which reduces the service life of the device. In addition, because the device adopts porous materials, the evaporation loss of the lubricating oil is serious in vacuum and semi-vacuum environments; in addition, due to the capillary force of the porous material, the lubricant remains in the device and cannot be fully utilized, which results in the device having an uncontrollable lubricant supply rate and a low lubricant utilization efficiency. The oil supply rope oil storage lubricating device is another common mode, the oil supply rope is in contact with a conical sleeve adjacent to an inner ring of a bearing under the slight compression of a spring, the friction generated by the contact causes the oil to continuously migrate along the larger end of the sleeve and enter the bearing under the action of centrifugal force, the oil rope absorbs the oil from an oil storage device and continuously supplies oil to the bearing under the action of capillary tube, and the device is influenced by machining precision, so that the oil supply speed of the oil supply rope is high, and the lubricating oil supply speed is uncontrollable.
According to the liquid sealing theory, as the liquid leakage rate has a functional relation with the surface roughness of the structure and the interference contact pressure, the invention designs a novel lubricating grease supply device for the space precision bearing. Compared with the conventional common air-to-sky environment ultra-precise bearing oil storage lubricating device, the invention can adjust the oil seepage rate by adjusting the interference magnitude, the surface roughness, the rotating speed and other factors, thereby achieving the purposes of controlling the lubricating time according to the bearing service time and controlling the lubricating oil supply rate. In addition, the internal space of the bearing device is fully utilized, so that the oil storage amount is greatly increased, compared with the conventional common oil storage lubricating device, the oil storage amount can be increased by 1-2 times, the accurate long-time oil supply is realized, and the oil supply system has a simple structure and high reliability.
Disclosure of Invention
The invention provides a novel aerospace environment precision bearing oil storage lubricating device and a design method thereof aiming at the defects of uncontrollable lubricating oil supply rate, low oil storage capacity and the like of the existing aerospace environment precision bearing lubricating device. The novel oil supply device realizes the purposes of controllable oil supply rate and high oil storage.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a lubricating grease supply device for a space precision bearing comprises an inner sleeve 1 and an outer sleeve 2, lubricating oil 3 is stored between the two sleeves, and a shaft 16 is arranged in the inner sleeve 1.
The upper end and the lower end of the inner sleeve 1 are respectively provided with an annular boss A4 and an annular boss B5, and the outer surfaces A6 and B7 of the bosses A4 and B5 are provided with certain roughness. The inner sleeve 1 and the outer sleeve 2 are assembled together in an interference fit mode, so that the outer surfaces A6 and B7 of bosses at the two ends of the inner sleeve 1 are tightly attached to the inner surface 8 of the outer sleeve 2, and a certain interference range is formed between 0.001 mm and 1 mm. And lubricating oil 3 is placed in a cavity formed after the inner sleeve 1 and the outer sleeve 2 are assembled.
A through hole 9 is processed on the annular boss A4 of the inner sleeve 1, and the through hole 9 consists of two parts. An annular groove 10 is processed towards the inner side of the annular boss A4 at the lower half part of the through hole 9, a rubber ring 11 is placed in the annular groove 10, the rubber ring 11 is matched with the inner wall of the groove 10, the rubber ring 11 protrudes out of the groove 10, and the diameter of the rubber ring 11 is larger than the depth of the annular groove 10. The upper half part of the through hole 9 is processed with a thread structure A12. After the lubricating oil 3 is injected into a cavity formed after the inner sleeve 1 and the outer sleeve 2 are assembled through the through hole 9, the threaded rod 13 is screwed into the through hole 9 to play a sealing role.
The threaded rod 13 consists of two parts: the lower half is smooth surface 14 and the upper half is provided with thread structure B15. The thread structure B15 is matched with the thread structure A12 of the through hole 9, so that the threaded rod 13 can be screwed into the through hole 9. The threaded rod 13 is provided with a part with a smooth surface 14, the outer diameter of the threaded rod is smaller than the inner diameter of the thread structure A12, but is larger than the inner diameter of the rubber ring 11 arranged in the groove 10, and after the threaded rod 13 is screwed into the through hole 9, the rubber ring 11 is extruded to achieve a sealing effect. When the shaft 16 rotates, the inner sleeve 1 and the outer sleeve 2 are driven to rotate together, the lubricating oil 3 stored in the inner sleeve 1 and the outer sleeve 2 can be extruded due to inertia, the outer surfaces A6 and B7 of the bosses 4 and 5 at the two ends of the inner sleeve 1 are tightly attached to the inner surface 8 of the outer sleeve 2, but the outer surfaces A6 and B7 are processed to have certain roughness, gaps can be formed at the positions where the outer surfaces A6 and B7 are contacted with the inner surface 8 of the outer sleeve 2, and the lubricating oil can be extruded from the gaps and enter the surrounding bearings, so that the lubricating oil plays a role of lubricating the bearings.
A design method of a lubricating grease supply device for a space precision bearing comprises the following steps:
in a first step, the total time t is determined according to the actual lubrication time required by the devicezGiven initial oil storage volume V0。
Secondly, determining a target initial leakage rate q of the lubricating grease supply device of the space precision bearingg1
The lubricating grease supply device for the space precision bearing generates pressure at the contact of the lubricating oil 3 inside through centrifugal action so as to realize the leakage of the lubricating oil 3 at the contact of the outer surfaces A6 and B7 of the bosses 4 and 5 and the inner surface 8 of the outer sleeve 2. However, as the lubricant 3 leaks, the pressure generated at the contact point is gradually reduced, and the leakage rate is also reduced. The leak rate is therefore a time-varying quantity expressed as:
Figure BDA0003026367280000031
wherein q is0Denotes an initial leak rate, V, when t is 00Representing the initial reservoir volume and t representing time.
As can be seen from equation (1), the function of the leak rate over time is only related to the initial leak rate q0And initial oil storage volume V0In connection therewith, an initial leakage rate q is determined0And initial oil storage volume V0The leak rate as a function of time can then be determined.
At a given total volume V of oil storage0Total time of use tzAnd after the desired leakage rate α in the use time, the target initial leakage rate of the structure can be obtained:
Figure BDA0003026367280000032
wherein alpha is a leakage ratio, namely the ratio of the leaked oil amount to the total oil amount, the value range is 0-1, the value is generally a fixed value in practice, and the value is determined according to the actual working condition; t is tzRepresenting the total time of operation of the device design.
Thus, the target initial leakage rate q of the structure is determinedg1。
Thirdly, according to the lubricating oil supply speed q required by the actual working condition of the bearingminCalculating the minimum initial leakage rate q satisfying the requirementg2；
It can be seen from equation (1) that the leak rate decreases monotonically over time, and is always greater than q if the operation is attemptedminThen t is required to be equal to tzWhen q (t) is satisfiedz)≥qminI.e. by
Figure BDA0003026367280000041
The minimum initial leak rate q that meets this requirementg2The following equation should be satisfied:
Figure BDA0003026367280000042
wherein q isminIndicating the required lubrication oil supply rate for the actual condition of the bearing.
The minimum initial leakage rate q can be obtained by solving the formula (3) through numerical solutiong2。
Fourthly, judging the target initial leakage rate qg1Whether or not it is equal to or greater than the minimum initial leak rate qg2: if the condition of being greater than or equal to is approximately satisfied, the target initial leak rate q in this caseg1Can be used; if the target initial leak rate qg1Less than the minimum initial leak rate qg2Many times, the structural parameters are readjusted to adjust the total oil storage volume V0And replace it back to the secondRecalculating target initial leak rate q in stepg1And a minimum initial leak rate q in the third stepg2And re-compared until the requirements are met.
Fifthly, setting the initial interference delta0And initial root mean square surface roughness σ0Determining the theoretical initial leakage rate q of the lubricating grease supply device of the space precision bearing under given parameters0；
1) According to the overall dimension parameters of the space precision bearing lubricating grease supply device and the given initial interference delta0The average value P of the contact pressure at the structural contact (the outer surfaces A6 and B7 of the bosses 4 and 5 and the inner surface 8 of the outer sleeve 2) is obtained by finite element calculationc。
2) For a total volume of V0The pressure P of the lubricating oil at the contact position is obtained through finite element calculationA。
3) By mean value of contact pressure P at the contactcAnd given initial root mean square surface roughness σ0The nominal film thickness h at the contact is found according to the following equation (4):
Figure BDA0003026367280000051
wherein K represents a constant value range of 0.0003-0.003; e' represents an equivalent elastic modulus; f is an intermediate variable; h represents the nominal film thickness at the contact; σ represents the root mean square surface roughness; e1Representing the modulus of elasticity of the inner sleeve; e2Representing the modulus of elasticity of the outer sleeve; mu.s1Representing the poisson's ratio of the inner sleeve; mu.s2Showing the poisson's ratio of the outer sleeve.
4) According to the obtained nominal film thickness h, the parameters of the lubricating grease supply device and the dynamic viscosity of the lubricating grease, the initial leakage rate q of the lubricating grease supply device under specific conditions is obtained0：
Figure BDA0003026367280000052
Wherein phixRepresenting a pressure flow factor; l is the length of the contact in the direction of leakage flow; b is the circumferential perimeter of the contact; pAIndicating the pressure of the lubricating oil at the contact; pBIndicating the pressure outside the device at the contact; μ represents the dynamic viscosity of the lubricating oil.
Sixthly, judging the theoretical initial leakage rate q0With the target initial leak rate q determined in the fourth stepg1Whether they are consistent: if the relative error is within 5%, the theoretical initial leakage rate q is considered to be consistent0The corresponding structure can meet the corresponding use requirement; if the difference exceeds 5 percent, the interference delta and the root mean square surface roughness sigma at the contact position need to be readjusted and are carried into the fifth step to replace the initial values of the interference delta and the root mean square surface roughness sigma to solve the theoretical initial leakage q again0Up to the target initial leak qg1The relative error is within 5%.
Compared with the prior art, the invention has the beneficial effects that:
compared with the conventional common oil storage lubricating device for the aerospace environment ultra-precise bearing, the bearing oil storage lubricating device has the advantages that the oil seepage rate can be adjusted by adjusting the interference, the surface roughness, the rotating speed and other factors, so that the lubricating time is controlled according to the service time of the bearing, and the lubricating oil supply rate is controlled.
Drawings
FIG. 1 is a schematic view of a space precision bearing assembly;
FIG. 2 is an enlarged view of a lubricating grease supply device for a space precision bearing;
FIG. 3 is a partially enlarged view of a lubricating grease supply device for a space precision bearing (region A in FIG. 2); FIG. 3(a) is a schematic view of a threaded rod structure, and FIG. 3(b) is a schematic view of a through hole and an annular groove structure;
FIG. 4 is a partially enlarged view of a lubricating grease supply device for a space precision bearing (region B in FIG. 2);
FIG. 5 is a flow chart showing the design of a lubricating grease supply device for a space precision bearing;
fig. 6 shows the geometry of the lubricating grease supply device for the space-precision bearing involved in the embodiment.
In the figure: 1, an inner sleeve; 2 an outer sleeve; 3, lubricating oil; 4, an annular boss A; 5, an annular boss B; 6, the outer surface of the boss A; 7, the outer surface of the boss B; 8 an inner surface of the outer sleeve; 9 through holes; 10 an annular groove; 11 a rubber ring; 12, a thread structure A; 13 a threaded rod; 14 smooth surface; 15, a thread structure B; 16 shafts.
Detailed Description
The present invention is further illustrated by the following specific examples.
A lubricating grease supply device for a space precision bearing comprises an inner sleeve 1 and an outer sleeve 2, lubricating oil 3 is stored between the two sleeves, and a shaft 16 is arranged in the inner sleeve 1.
The upper end and the lower end of the inner sleeve 1 are respectively provided with an annular boss A4 and an annular boss B5, and the machining roughness Ra of the outer surface A6 and the outer surface B7 of the boss A4 and the boss B5 is 0.1-1000 microns. The inner sleeve 1 and the outer sleeve 2 are assembled together in an interference fit mode, so that the outer surfaces A6 and B7 of the bosses at the two ends of the inner sleeve 1 are tightly attached to the inner surface 8 of the outer sleeve 2, and a certain interference is formed. And lubricating oil 3 is placed in a cavity formed after the inner sleeve 1 and the outer sleeve 2 are assembled.
A through hole 9 is processed on the annular boss A4 of the inner sleeve 1, and the through hole 9 consists of two parts. An annular groove 10 is processed on the inner side of the annular boss A4 below the through hole 9, a rubber ring 11 is placed in the annular groove 10, the rubber ring 11 is matched with the inner wall of the groove 10, the rubber ring 11 protrudes out of the groove 10, and the diameter of the rubber ring 11 is larger than the depth of the annular groove 10. The upper part of the through hole 9 is processed with a thread structure A12. After the lubricating oil 3 is injected into a cavity formed after the inner sleeve 1 and the outer sleeve 2 are assembled through the through hole 9, the threaded rod 13 is screwed into the through hole 9 to play a sealing role.
The threaded rod 13 consists of two parts: the lower part is a smooth surface 14 and the upper part is provided with a thread structure B15. The thread structure B15 is matched with the thread structure A12 of the through hole 9, so that the threaded rod 13 can be screwed into the through hole 9. The threaded rod 13 is provided with a part with a smooth surface 14, the outer diameter of the threaded rod is smaller than the inner diameter of the thread structure A12, but is larger than the inner diameter of the rubber ring 11 arranged in the groove 10, and after the threaded rod 13 is screwed into the through hole 9, the rubber ring 11 is extruded to achieve a sealing effect. The supply means may be rotated with the shaft 16 of the bearing or with the outer sleeve of the bearing, both of which may be centrifugally supplied.
A design method of a lubricating grease supply device for a space precision bearing comprises the following steps:
in the first step, the total time t is determined according to the lubrication time actually required by the device (under the actual working condition, just to give an example)z26280H, H denotes the time unit: and (4) hours. Given initial oil storage volume V0＝0.754mL。
Second, a target initial leak rate q of the structure is determinedg1
At a given total volume V of oil storage0Service time tzAnd when the desired leakage rate α becomes 0.9 during the use time, the target initial leakage rate of the structure can be determined:
Figure BDA0003026367280000071
thus, the target initial leakage rate q of the structure is determinedg1。
Thirdly, according to the lubricating oil supply speed q required by the actual working condition of the bearingmin＝3.7×10-6mL/H, calculating the minimum initial leakage rate q meeting the requirementg2：
Figure BDA0003026367280000072
The minimum initial leakage rate q can be obtainedg2＝3×10-5mL/h。
Fourth step, in this embodimentIn (1), comparing qg1And q isg2Discovery qg1>qg2So target initial leak rate qg1Can be used.
Fifthly, setting the initial interference delta0And initial root mean square surface roughness σ0Determining the theoretical initial leakage rate q of the structure under given parameters0
1) According to the overall dimensional parameters of the structure and a given initial interference delta0Obtaining the average value P of the contact pressure at the contact position of the structure through a finite element calculation method, wherein the average value P is 0.01mmc＝100MPa。
2) For a total volume of V0The pressure P of the lubricating oil at the contact position is obtained by finite element calculation when the lubricating oil is 0.754mLA＝6977Pa。
3) By mean value of contact pressure P at the contactcAnd given initial root mean square surface roughness σ0The nominal film thickness h at the contact is found according to the following equation, 0.36 μm:
Figure BDA0003026367280000081
wherein, K is 0.003, E1＝E2＝210GPa，μ1＝μ20.3. The nominal film thickness h was 0.2572 μm.
4) According to the obtained nominal film thickness h and the parameters and lubricating oil properties of the structure, the initial leakage rate q of the structure under specific conditions is obtained0：
Figure BDA0003026367280000082
Wherein phix0.32 denotes the pressure flow factor, PB0 denotes the pressure at the contact point outside the device, L1 mm is the length of the contact point in the leakage flow direction, B69.115 mm is the circumferential perimeter of the contact point, and μ 0.023Pa · s denotes the dynamic viscosity of the lubricating oil. Finally obtaining the theoretical initial leakage rate q0＝3.374×10-5mL/H。
Sixthly, judging the theoretical initial leakage rate q0With the target initial leak rate q determined in the fourth stepg1Whether they are consistent or not, if the relative error is within 5%, the two are considered to be consistent, in this embodiment, the relative error is
Figure BDA0003026367280000083
The theoretical initial leak rate q0Corresponding structure (interference delta at contact point)00.01mm and root mean square surface roughness σ00.36 μm) can meet the corresponding use requirements.
The above-mentioned embodiments only express the embodiments of the present invention, but not should be understood as the limitation of the scope of the invention patent, it should be noted that, for those skilled in the art, many variations and modifications can be made without departing from the concept of the present invention, and these all fall into the protection scope of the present invention.

Claims (4)

1. A lubricating grease supply device for a space precision bearing is characterized by comprising an inner sleeve (1) and an outer sleeve (2), wherein a shaft (16) is arranged in the inner sleeve (1);
the upper end and the lower end of the inner sleeve (1) are respectively provided with an annular boss A (4) and an annular boss B (5) in an outward processing mode, and the outer surfaces A (6) and B (7) of the bosses A (4) and B (5) are provided with roughness in a processing mode; the inner sleeve (1) and the outer sleeve (2) are assembled in an interference fit mode, so that the outer surface A (6) and the outer surface B (7) of bosses at two ends of the inner sleeve (1) are tightly attached to the inner surface (8) of the outer sleeve (2) to form a certain interference; lubricating oil (3) is placed in a cavity formed after the inner sleeve (1) and the outer sleeve (2) are assembled;
a through hole (9) is processed on the annular boss A (4) of the inner sleeve (1), and the through hole (9) consists of two parts; an annular groove (10) is formed in the inner side of the lower half portion of the through hole (9), a rubber ring (11) is placed in the annular groove (10), the rubber ring (11) is matched with the inner wall of the groove (10), and the diameter of the rubber ring (11) is larger than the depth of the annular groove (10); the upper half part of the through hole (9) is processed with a thread structure A (12); after the lubricating oil (3) is injected into a cavity formed after the inner sleeve (1) and the outer sleeve (2) are assembled through the through hole (9), the threaded rod (13) is screwed into the through hole (9) to play a role in sealing;
the threaded rod (13) consists of two parts: the lower half section is a smooth surface (14), and the upper half section is provided with a thread structure B (15); the thread structure B (15) is matched with the thread structure A (12) of the through hole (9) to ensure that the threaded rod (13) can be screwed into the through hole (9); the threaded rod (13) is provided with a part with a smooth surface (14), the outer diameter of the threaded rod is smaller than the inner diameter of the threaded structure A (12) but larger than the inner diameter of the rubber ring (11) arranged in the groove (10), and the rubber ring (11) is extruded after the threaded rod (13) is screwed into the through hole (9) to achieve a sealing effect;
when the shaft (16) rotates, the inner sleeve (1) and the outer sleeve (2) are driven to rotate, and the lubricating oil (3) is extruded out from a gap at the contact position of the inner sleeve (1) and the outer sleeve (2) and enters the bearing to play a role in lubricating the bearing.
2. A space precision bearing grease supply device as claimed in claim 1, characterized in that the interference at the close fitting of the inner sleeve (1) and the outer sleeve is 0.001-1 mm.
3. A method for designing a lubricating grease supply device for a space precision bearing as claimed in claim 1 or 2, characterized by comprising the steps of:
in a first step, the total time t is determined according to the actual lubrication time required by the devicezGiven initial oil storage volume V0；
Secondly, determining a target initial leakage rate q of the lubricating grease supply device of the space precision bearingg1
The supply device generates pressure at the contact part of the internal lubricating oil (3) through centrifugal action, and the lubricating oil (3) leaks from the contact part of the lug boss 4 and the lug boss 5 and the outer sleeve (2); along with lubricating oil (3) constantly leaks, its pressure that produces at the contact reduces gradually, leads to the leakage rate constantly to reduce, and its expression of leakage rate is:
Figure FDA0003026367270000021
wherein q is0Denotes an initial leak rate, V, when t is 00Represents the initial oil storage volume, and t represents time;
at a given total volume V of oil storage0Total time of use tzAnd after the desired leakage rate α in the use time, the target initial leakage rate of the structure can be obtained:
Figure FDA0003026367270000022
wherein alpha is a leakage ratio, namely a ratio of the leaked oil amount to the total oil amount, and is determined according to an actual working condition; t is tzRepresents the total time of operation of the device design;
finally, the target initial leakage rate q of the structure is determinedg1；
Thirdly, according to the lubricating oil supply speed q required by the actual working condition of the bearingminCalculating the minimum initial leakage rate q satisfying the requirementg2；
If the leakage rate is always greater than q during workingminThen t is required to be equal to tzWhen q (t) is satisfiedz)≥qminI.e. by
Figure FDA0003026367270000023
The minimum initial leak rate q that meets this requirementg2The following equation should be satisfied:
Figure FDA0003026367270000024
wherein q isminRepresenting the lubricating oil supply rate required by the actual working condition of the bearing;
solving the formula (3) through numerical solving to obtain the minimum initial leakage rate qg2；
The fourth step, judge the target initial leakageRate qg1Whether or not it is equal to or greater than the minimum initial leak rate qg2: if the condition of being greater than or equal to is approximately satisfied, the target initial leak rate q in this caseg1Can be used; if the target initial leak rate qg1Less than the minimum initial leak rate qg2Many times, the structural parameters are readjusted to adjust the total oil storage volume V0And replacing it back to the second step to recalculate the target initial leak rate qg1And a minimum initial leak rate q in the third stepg2And re-comparing until the requirements are met;
fifthly, setting the initial interference delta0And initial root mean square surface roughness σ0Determining the theoretical initial leakage rate q of the lubricating grease supply device of the space precision bearing under given parameters0；
1) According to the overall dimension parameters of the space precision bearing lubricating grease supply device and the given initial interference delta0Obtaining the average value P of the contact pressure at the contact position of the structure through finite element calculationc；
2) For a total volume of V0The pressure P of the lubricating oil at the contact position is obtained through finite element calculationA；
3) By mean value of contact pressure P at the contactcAnd given initial root mean square surface roughness σ0The nominal film thickness h at the contact is found according to the following equation (4):
Figure FDA0003026367270000031
wherein K represents a constant; e' represents an equivalent elastic modulus; f is an intermediate variable; h represents the nominal film thickness at the contact; σ represents the root mean square surface roughness; e1Representing the modulus of elasticity of the inner sleeve; e2Representing the modulus of elasticity of the outer sleeve; mu.s1Representing the poisson's ratio of the inner sleeve; mu.s2Representing the poisson's ratio of the outer sleeve;
4) determining the lubricating oil dynamic viscosity according to the determined nominal film thickness h and the parameters of the lubricating oil supply deviceInitial leakage rate q of lubricating grease supply device under specific conditions0：
Figure FDA0003026367270000032
Wherein phixRepresenting a pressure flow factor; l is the length of the contact in the direction of leakage flow; b is the circumferential perimeter of the contact; pAIndicating the pressure of the lubricating oil at the contact; pBIndicating the pressure outside the device at the contact; μ represents the dynamic viscosity of the lubricating oil;
sixthly, judging the theoretical initial leakage rate q0With the target initial leak rate q determined in the fourth stepg1Whether they are consistent: if the relative error is within 5%, the theoretical initial leakage rate q is considered to be consistent0The corresponding structure can meet the corresponding use requirement; if the difference exceeds 5 percent, the interference delta and the root mean square surface roughness sigma at the contact position need to be readjusted and are carried into the fifth step to replace the initial values of the interference delta and the root mean square surface roughness sigma to solve the theoretical initial leakage q again0Up to the target initial leak qg1The relative error is within 5%.
4. A design method of a lubricating grease supply device for a space precision bearing as claimed in claim 3, wherein the leakage ratio α ranges from 0 to 1.
CN202110417131.XA 2021-04-19 2021-04-19 Lubricating grease supply device for space precision bearing and design method thereof Pending CN112943805A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
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CN113595322A (en) * 2021-07-29 2021-11-02 中国科学院工程热物理研究所 Anti-disengagement flywheel structure and flywheel energy storage system
CN113669372A (en) * 2021-08-23 2021-11-19 北京微纳星空科技有限公司 Bearing and bearing oil supply device
CN114370456A (en) * 2021-12-13 2022-04-19 上海航天控制技术研究所 Microporous supplementary lubrication device for bearing with long space life
CN117072617A (en) * 2023-10-16 2023-11-17 平乡县工力飞轮有限公司 Dustproof, waterproof and noiseproof flywheel for vehicle and flywheel assembly

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113595322A (en) * 2021-07-29 2021-11-02 中国科学院工程热物理研究所 Anti-disengagement flywheel structure and flywheel energy storage system
CN113669372A (en) * 2021-08-23 2021-11-19 北京微纳星空科技有限公司 Bearing and bearing oil supply device
CN114370456A (en) * 2021-12-13 2022-04-19 上海航天控制技术研究所 Microporous supplementary lubrication device for bearing with long space life
CN117072617A (en) * 2023-10-16 2023-11-17 平乡县工力飞轮有限公司 Dustproof, waterproof and noiseproof flywheel for vehicle and flywheel assembly
CN117072617B (en) * 2023-10-16 2024-01-23 平乡县工力飞轮有限公司 Dustproof, waterproof and noiseproof flywheel for vehicle and flywheel assembly

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