CN104615801B - The heavy critical lubricating status tachometer value of hydrostatic bearing determines method - Google Patents
The heavy critical lubricating status tachometer value of hydrostatic bearing determines method Download PDFInfo
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- CN104615801B CN104615801B CN201410721177.0A CN201410721177A CN104615801B CN 104615801 B CN104615801 B CN 104615801B CN 201410721177 A CN201410721177 A CN 201410721177A CN 104615801 B CN104615801 B CN 104615801B
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Abstract
Hydrostatic bearing is effectively in carrying and the range of speeds, known conventional load finds out corresponding critical speed value when critical lubrication occurs, show that hydrostatic bearing often uses the critical lubrication corresponding relation of load and rotating speed, and supporting film lubrication critical condition mathematical modeling is verified by FLUENT softwares.Step A, by being derived from the critical lubricating status rotary rpm expression formula of workbench.Step B, according to carrying scope, rotating speed theoretical value corresponding to load is often used when calculating the critical lubrication of hydrostatic bearing oil film.Step C, simplified model is established by UG, recycles GAMBIT softwares to carry out mesh generation to initial oil film and export mesh files.Step D, with FLUENT softwares, numerical simulation is carried out to hydrostatic bearing critical speed.Step E, heavy hydrostatic bearing film lubrication critical condition mathematical modeling is verified according to this numerical method.The present invention determines technique study applied to the critical lubricating status tachometer value of heavy hydrostatic bearing.
Description
Technical field
The present invention relates to heavy hydrostatic bearing under conventional load oil film critical speed parameter study.
Background technology
When carrying out rotate counterclockwise in the processing of heavy hydrostatic bearing rotary table, all fluids to the right of single lubricating pad
Domain, it may occur however that pressure difference is identical with the flow value caused by shear flow and mobility status that flowing velocity is in opposite direction, now
Critical lubricating status can be caused.Critical profit under the more lubricating pad hydrostatic support concrete structures of series can be obtained by this research method
Sliding parameter, supporting is caused to be failed to avoid occurring the i.e. critical lubrication of zero lubricating status, so as to greatly improve heavy hydrostatic bearing fortune
Capable reliability provides theoretical foundation.
The content of the invention
Effectively carried the present invention is to solve hydrostatic support with the range of speeds, it is known that found out under the premise of load occur it is critical
Corresponding tachometer value during lubrication, when heavy hydrostatic bearing gap oil film is in critical lubricating status, draw hydrostatic support load
With the critical lubrication corresponding relation of rotating speed, and by FLUENT softwares, supporting film lubrication is faced using the method for numerical simulation
Boundary's state mathematical modeling is verified.
Heavy hydrostatic bearing critical speed parameter study is realized according to the following steps：
Step A, it is as follows by being derived from worktable rotary angular speed expression formula：
(rad/s) (1)
Wherein it is hydrostatic support structural parameters, is worktable rotary angular speed, be fluid kinematic viscosity, is oil film thickness,
For oil pocket and oil-recovery tank pressure differential；
Speed unit generally use rev/min in numerical simulation, therefore the rotating speed expression formula that formula (1) is converted to rev/min
It is as follows：
(r/min) (2)
Step B, according to the carrying scope of heavy hydrostatic bearing, table 1 list load be respectively 0t, 20t, 40t, 60t,
Corresponding oil pocket pressure and rotating speed during the critical lubrication of hydrostatic support oil film are theoretical when 80t, 100t, 120t, 140t, 160t
Value；
Rotating speed theoretical value during the hydrostatic support of table 1 critical lubrication
| W(t) | 0 | 20 | 40 | 60 | 80 | 100 | 120 | 140 | 160 |
| Oil pocket pressure (MPa) | 0.14 | 0.18 | 0.23 | 0.27 | 0.32 | 0.37 | 0.41 | 0.46 | 0.50 |
| Theoretical critical fire area rotating speed (r/min) | 0.95 | 1.32 | 1.86 | 2.21 | 2.60 | 3.14 | 3.25 | 4.06 | 4.42 |
Step C, hydrostatic support model simplification model is established by 3 d modeling software UG, then with GAMBIT softwares to initial
Oil film carries out mesh generation, obtains grid, given fluid domain boundary condition simultaneously exports zhuansu. mesh files；
Step D, with FLUENT softwares, numerical simulation is carried out to hydrostatic support critical speed；
Step E, shown that such a hydrostatic support often uses the critical corresponding relation of load and rotating speed, according to this numerical method pair
Heavy hydrostatic bearing film lubrication critical condition mathematical modeling is verified.
Invention effect
Single hydrostatic support oil film fluid domain is divided into four by the inventive method from heavy hydrostatic bearing lubrication mechanism
Individual region, when workbench rotate counterclockwise, select what is formed caused by worktable rotary between shear flow and oil pocket oil-recovery tank
Pressure difference stream region in opposite direction is object, and rotating speed when deriving the critical lubrication of heavy hydrostatic bearing oil film carrying oil film is theoretical
Value.Draw the increase with load value, the tachometer value under corresponding critical lubricating status also gradually increases, and the load value that compares increases
Big degree, corresponding critical speed increasing degree are simultaneously little.FLUENT softwares are recycled to realize the number in heavy hydrostatic bearing
Value simulation calculates, and draws and oil film fluid domain mobility status is corresponded under each operating mode, i.e., corresponding section face1 traffic conditions.Root
It can find that face1 volume computation is close to zero from lower limit according to oil film section flow curve figure, illustrate under such a operating mode
Heavy hydrostatic bearing gap oil film fluid domain lies substantially in critical lubrication state, and numerical simulation result demonstrates theoretical research
Correctness.According to the relation of Fuel film model and coordinate, can be inferred that it is now that differential pressure flow is less than shearing flow, i.e., it is theoretical
It is calculated that corresponding critical speed value is bigger than normal, compares face1 flow curves and find out heavy static pressure corresponding to idle condition
Bearing critical speed theoretical value error is slightly larger, and other operating mode theory of correspondences value errors are smaller, and error is mainly derived from theoretical formula
The simplified partial of moulded dimension is caused in calculating.The heavy hydrostatic bearing rotation under specific load is precomputed according to the method
Revolving worktable critical speed, improve hydrostatic support reliability service for Practical Project and provide theoretical foundation.
Brief description of the drawings
Fig. 1 is flow chart of the present invention,
Fig. 2 is the face1 locations drawing at the single lubricating pad sealing oil edge of the present invention,
Fig. 3 is step D of the present invention particular flow sheet,
Fig. 4 is critical flow simulation result of the present invention in conventional load with face1 under corresponding rotating speed.
Embodiment
Heavy hydrostatic bearing critical speed parameter study is realized according to the following steps：
Step A, it is as follows by being derived from worktable rotary angular speed expression formula：
(rad/s) (1)
Wherein it is hydrostatic support structural parameters, is worktable rotary angular speed, be fluid kinematic viscosity, is oil film thickness,
For oil pocket and oil-recovery tank pressure differential；
Speed unit generally use rev/min in numerical simulation, therefore the rotating speed expression formula that formula (1) is converted to rev/min
It is as follows：
(r/min) (2)
Step B, according to the carrying scope of heavy hydrostatic bearing, table 1 list load be respectively 0t, 20t, 40t, 60t,
Corresponding oil pocket pressure and rotating speed during the critical lubrication of hydrostatic support oil film are theoretical when 80t, 100t, 120t, 140t, 160t
Value；
Rotating speed theoretical value during the hydrostatic support of table 1 critical lubrication
| W(t) | 0 | 20 | 40 | 60 | 80 | 100 | 120 | 140 | 160 |
| Oil pocket pressure (MPa) | 0.14 | 0.18 | 0.23 | 0.27 | 0.32 | 0.37 | 0.41 | 0.46 | 0.50 |
| Theoretical critical fire area rotating speed (r/min) | 0.95 | 1.32 | 1.86 | 2.21 | 2.60 | 3.14 | 3.25 | 4.06 | 4.42 |
Step C, hydrostatic support model simplification model is established by 3 d modeling software UG, then with GAMBIT softwares to initial
Oil film carries out mesh generation, obtains grid, given fluid domain boundary condition simultaneously exports zhuansu. mesh files；
Step D, with FLUENT softwares, numerical simulation is carried out to hydrostatic support critical speed；
Step D1, FLUENT 6.3.26 softwares are opened, import ready-portioned geometrical model zhuansu. mesh files,
And grid is checked by check, it is ensured that the minimum volume of grid is not negative；
Step D2, solver parameter is set, click on Define-Solver, using the Pressure Base based on pressure and
Stable state calculates Steady, and other specification keeps acquiescence；
Step D3, material properties are set, click on density and viscosity that Define-Materials defines oil film；
Step D4, boundary condition is set, click on Define-Boundary Conditions options, defining entrance respectively is
Quality inflow entrance, export as pressure export, while define the cycle boundary of rotation and the rotating speed of rotation wall；
Step D5, stream field initialization Solve-Initialization, selects Compute From-all-zones, point
Hit Init and complete initialization；
Step D6, monitoring plane is set, Surface-Plane chooses three coordinate points and determines that plane is named as face1, will
This plane is as monitoring plane；
Step D7, set monitor Solve-Monitors-Residual to keep acquiescence, click on OK, selection monitoring plane
Monitors-Surface is monitored using mass flow, and is named as face-1.out；
Step D8, calculating is iterated, iterative steps are 800 steps, click on Iterate and are iterated, eventually through iteration
Draw simulation value；
Step E, the critical corresponding relation of such a hydrostatic support load and rotating speed has been drawn, and by numerical method to heavy type
Hydrostatic bearing film lubrication critical condition mathematical modeling is verified.
Present embodiment effect：
Single hydrostatic support oil film fluid domain is divided into four by the inventive method from heavy hydrostatic bearing lubrication mechanism
Individual region, when workbench rotate counterclockwise, select what is formed caused by worktable rotary between shear flow and oil pocket oil-recovery tank
Pressure difference stream region in opposite direction is object, and rotating speed when deriving the critical lubrication of heavy hydrostatic bearing oil film carrying oil film is theoretical
Value.Draw the increase with load value, the tachometer value under corresponding critical lubricating status also gradually increases, and the load value that compares increases
Big degree, corresponding critical speed increasing degree are simultaneously little.FLUENT softwares are recycled to realize the number in heavy hydrostatic bearing
Value simulation calculates, and draws and oil film fluid domain mobility status is corresponded under each operating mode, i.e., corresponding section face1 traffic conditions.Root
It can find that face1 volume computation is close to zero from lower limit according to oil film section flow curve figure, illustrate under such a operating mode
Heavy hydrostatic bearing gap oil film fluid domain lies substantially in critical lubrication state, and numerical simulation result demonstrates theoretical research
Correctness.According to the relation of Fuel film model and coordinate, can be inferred that it is now that differential pressure flow is less than shearing flow, i.e., it is theoretical
It is calculated that corresponding critical speed value is bigger than normal, compares face1 flow curves and find out heavy static pressure corresponding to idle condition
Bearing critical speed theoretical value error is slightly larger, and other operating mode theory of correspondences value errors are smaller, and error is mainly derived from theoretical formula
The simplified partial of moulded dimension is caused in calculating.The heavy hydrostatic bearing rotation under specific load is precomputed according to the method
Revolving worktable critical speed, improve hydrostatic support reliability service for Practical Project and provide theoretical foundation.
Claims (3)
- A kind of 1. heavy hydrostatic bearing critical speed parameter study method, it is characterised in that derive when hydrostatic bearing faces During boundary's lubrication circumstances, its rotary speed parameter and the relational expression of other each parameters, bearing film is lubricated by FLUENT softwares critical State mathematical modeling is verified, is realized according to the following steps：Step A, it is as follows by being derived from worktable rotary angular speed expression formula：(1)WhereinR 1For hydrostatic bearing lubricating pad inner circle radius,R 4For hydrostatic bearing lubricating pad exradius,R 2For hydrostatic bearing oil pocket inner circle Radius,φ 1For the half radian of the single oil pocket of hydrostatic bearing,φ 2For the half radian of the single lubricating pad of hydrostatic bearing,ωFor worktable rotary angular speed,μFor fluid kinematic viscosity,hFor oil film thickness, △pFor oil pocket and oil-recovery tank pressure differential；Speed unit generally use rev/min in numerical simulation, therefore the rotating speed expression formula that formula (1) is converted to rev/min is as follows：(2)Step B, according to the carrying scope of heavy hydrostatic bearing, table B list load be respectively 0t, 20t, 40t, 60t, 80t, Corresponding oil pocket pressure and rotating speed theoretical value during the critical lubrication of hydrostatic bearing oil film when 100t, 120t, 140t, 160t；Rotating speed theoretical value during table B hydrostatic bearings critical lubrication
W(t) 0 20 40 60 80 100 120 140 160 Oil pocket pressure (MPa) 0.14 0.18 0.23 0.27 0.32 0.37 0.41 0.46 0.50 Theoretical critical fire area rotating speed (r/min) 0.95 1.32 1.86 2.21 2.60 3.14 3.25 4.06 4.42 Step C, hydrostatic bearing model simplification model is established by 3 d modeling software UG, recycles GAMBIT softwares to initial oil Film carries out mesh generation, obtains grid, given fluid domain boundary condition simultaneously exports zhansu.mesh files；Step D, the inlet flow rate under above-mentioned load-up condition is calculated as simulated conditions, carries out FLUENT simulations；Step E, whether the flow in the monitoring face drawn according to simulation is zero, basis for estimation formula（1）Or formula（2）What is drawn is upper The reasonability of face list data. - 2. a kind of heavy hydrostatic bearing critical speed parameter study method according to claim 1, it is characterised in that described FLUENT softwares are used in step D, numerical simulation is carried out to hydrostatic bearing critical speed respectively.
- 3. a kind of heavy hydrostatic bearing critical speed parameter study method according to claim 1, it is characterised in that described Go to monitor whether zero flowing be present after inputting by simulating boundary condition data in step E, to heavy hydrostatic bearing film lubrication Critical condition mathematical modeling is verified.
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106021729A (en) * | 2015-11-16 | 2016-10-12 | 哈尔滨理工大学 | Method for solving hot oil carrying values of heavy hydrostatic bearing under different loads |
| CN106021775B (en) * | 2016-05-30 | 2019-04-12 | 广东电网有限责任公司电力科学研究院 | Oil film Meshing Method and system in a kind of minim gap |
| CN109002569A (en) * | 2018-01-12 | 2018-12-14 | 哈尔滨理工大学 | A method of establishing static pressure oil film motion layer boundary condition |
| CN111503153B (en) * | 2020-04-21 | 2021-09-07 | 南京工程学院 | Static-pressure sliding bearing oil film pressure loss compensation method |
| CN113158369B (en) * | 2021-04-19 | 2023-11-28 | 哈尔滨理工大学 | Oil film flow simulation monitoring method for oil sealing edge of oil pad of hydrostatic thrust bearing |
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| CN103593537A (en) * | 2013-11-27 | 2014-02-19 | 哈尔滨理工大学 | Method for building lubricating oil film model after thermal coupling deformation of static pressure center frame |
| CN104598666A (en) * | 2014-12-01 | 2015-05-06 | 哈尔滨理工大学 | Large-scale hydrostatic support critical load parameter acquiring method |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103593537A (en) * | 2013-11-27 | 2014-02-19 | 哈尔滨理工大学 | Method for building lubricating oil film model after thermal coupling deformation of static pressure center frame |
| CN104598666A (en) * | 2014-12-01 | 2015-05-06 | 哈尔滨理工大学 | Large-scale hydrostatic support critical load parameter acquiring method |
Non-Patent Citations (3)
| Title |
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| 基于FLUENT的动压滑动轴承油膜稳定性研究;涂林;《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》;20110815;第2011年卷(第08期);第C029-19页 * |
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