CN108591260A - A kind of ramp type double square lubricating pad bearing capacity computation method considering dynamic pressure effect - Google Patents
A kind of ramp type double square lubricating pad bearing capacity computation method considering dynamic pressure effect Download PDFInfo
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- CN108591260A CN108591260A CN201810413854.0A CN201810413854A CN108591260A CN 108591260 A CN108591260 A CN 108591260A CN 201810413854 A CN201810413854 A CN 201810413854A CN 108591260 A CN108591260 A CN 108591260A
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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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
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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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
- F16C32/0692—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for axial load only
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- 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
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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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/20—Application independent of particular apparatuses related to type of movement
- F16C2300/22—High-speed rotation
-
- 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
- F16C2322/00—Apparatus used in shaping articles
- F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Mechanical Engineering (AREA)
- General Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Pure & Applied Mathematics (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Mathematical Optimization (AREA)
- Mathematical Analysis (AREA)
- Computational Mathematics (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The invention discloses a kind of ramp type double square lubricating pad bearing capacity computation methods considering dynamic pressure effect, easily cause boundary lubrication in the extreme operating condition operation of high-speed overload to solve lathe, form the case where dry friction leads to tile kilning, the present invention is by analyzing the single pad lubrication mechanism of ramp type hydrostatic bearing, the computational methods of bearing load carrying capacity when ramp type hydrostatic bearing rotates clockwise are derived and establish, this method effectively combines the advantages of dynamic and static last item is held.Step A, the computational methods of ramp type double square chamber hydrostatic thrust bearing bearing capacity are determined；Step B, derived that single ramp type double square chamber hydrostatic thrust bearing is quiet, dynamic pressure bearing capacity respectively；Step C, the calculation formula of the total bearing capacity of ramp type double square chamber hydrostatic thrust bearing has been derived.The present invention is suitable for heavy digital control machine tool field.
Description
Technical field
The present invention relates to the computational methods of ramp type hydrostatic thrust bearing bearing capacity more particularly to a kind of consideration dynamic pressure effects
Ramp type double square chamber hydrostatic thrust bearing bearing capacity computational methods, belong to heavy machine tool technical field.
Background technology
Heavy wool pad hydrostatic thrust bearing is the core component greatly, in weight equipment field such as aerospace, military project, ship,
The optimum state of bearing operation is that the fluid film of Castor Oil is consistently formed between friction is secondary, but mostly in high speed when due to machine tooling
It is run under the extreme operating condition of heavy duty so that the case where being likely to be in boundary lubrication in operation, and then leading to tile kilning.Based on this,
The present invention determines ramp type hydrostatic bearing dynamic pressure effect by analyzing the single pad lubrication mechanism of ramp type hydrostatic bearing
The key area of generation derives and establishes the computational methods of the bearing capacity of bearing when ramp type hydrostatic bearing rotates clockwise,
The purpose of the invention is to probe into the bearing capacity of ramp type hydrostatic bearing, and solution carries caused by bearing hydrostatic pressures losses
Scarce capacity, easily cause lubrication failure formed dry friction the problem of.
Invention content
The present invention is to solve above-mentioned critical issue, for a kind of ramp type hydrostatic thrust bearing, it is proposed that a kind of to consider to move
The ramp type double square lubricating pad bearing capacity computation method for pressing effect, the dynamic pressure to efficiently use the formation of its wedge-shaped oil film compensate
The hydrostatic pressures losses of lubricating oil.
It is a kind of to consider that the ramp type double square lubricating pad bearing capacity computation method of dynamic pressure effect is realized according to the following steps：
Step A, ramp type double square chamber hydrostatic thrust bearing bearing capacity computation method is determined：
It is analyzed by the lubrication mechanism to lubricating pad, the calculating of the ramp type double square lubricating pad bearing capacity with dynamic pressure effect is answered
Consider that workbench starts and oil pocket static pressure bearing capacity and moved caused by wedge-shaped oil film when workbench high speed rotation when stable operation
Press bearing capacity two parts, formula as follows：
W=Wj+Wd (1)
In formula：W is the total bearing capacity of ramp type double square chamber hydrostatic thrust bearing；WjFor ramp type double square chamber hydrostatic thrust bearing
Static pressure bearing capacity；WdFor ramp type double square chamber hydrostatic thrust bearing dynamic pressure bearing capacity.
Step B, derive that single ramp type double square chamber hydrostatic thrust bearing is quiet, dynamic pressure bearing capacity is as follows respectively：
Single ramp type double square chamber hydrostatic thrust bearing static pressure bearing capacity equation is as follows：
Wherein
Ae=(L-l1)(B-b2-2b1)
In formula：λ is double square oil pad structure parameter；AeFor double square lubricating pad effective bearing area；μ is dynamic viscosity；H is minimum
Oil film thickness；Q is single lubricating pad double square chamber total flow, the input flow rate as pumped；
Single ramp type double square chamber hydrostatic thrust bearing dynamic pressure bearing capacity equation is as follows：
Wd=μ ω [A1(C1+C2)+A2C3] (3)
Wherein
A2=Lb1
In formula：C1、C2、C3For ramp type double square chamber hydrostatic bearing oil pad structure parameter；A1For each rectangle oil pocket of single lubricating pad
All sealing oil edge areas unilateral to the left and right；A2Single side sealing oil edge area is radially descended for each rectangle oil pocket of single lubricating pad；μ is hydraulic pressure
Oily dynamic viscosity；H is wedge-shaped oil film minimum thickness；ω is turntable angular velocity of rotation；θ is oil film wedge angle；r1=r3For lubricating pad
Oil pocket circumferential left and right sides sealing oil edge center in outside is to the distance of the static pressure centre of gyration, r2=r4To the left for oil pocket week on the inside of lubricating pad
Right both sides sealing oil edge center is to the distance of the static pressure centre of gyration, r5<r6<r7<r8Its numerical value is respectively two oil pockets radial direction inside and outside lubricating pad
Distance of the upper and lower both sides sealing oil edge center to the static pressure centre of gyration；
Step C, it is as follows to derive the total bearing capacity formula of ramp type double square chamber hydrostatic thrust bearing：
Wherein static pressure bearing capacity factor K1=λ Ae；Dynamic pressure bearing capacity factor K2=A1(C1+C2)+A2C3。
Invention effect
The key area that the present invention is mainly carried according to dynamic pressure on the single lubricating pad of ramp type hydrostatic bearing, is deduced difference
The bearing capacity equation of size inclined-plane lubricating pad inclines wherein playing flow, rotating speed of table and inclined-plane that main affecting parameters are pump
Angle.Dynamic pressure effect is mixed into hydrostatic thrust bearing by the invention, is released by calculating the influence of dynamic pressure effect of bearing
The bearing capacity of entire ramp type double square lubricating pad, the computational methods improve original calculating bearing load carrying capacity value so that oil
The hydrostatic pressures losses of pad are compensated, and improve the precision and stability of static pressure support operation, solve static pressure support process
In friction Problem of Failure, this method can effectively improve vertical numerical controlled lathe bearing capacity 50% or so through practical proof.
Description of the drawings
Attached drawing 1：Ramp type double square cavity configuration scale diagrams.
Attached drawing 2：The single lubricating pad 3 dimensional drawing of ramp type double square chamber hydrostatic thrust bearing.
Attached drawing 3：Ramp type double square lubricating pad is uniformly distributed schematic diagram along bearing base.
Specific implementation mode
It is a kind of to consider that the ramp type double square lubricating pad bearing capacity computation method of dynamic pressure effect is realized according to the following steps：
Step A, ramp type double square chamber hydrostatic thrust bearing bearing capacity computation method is determined：
It is analyzed by the lubrication mechanism to lubricating pad, the calculating of the ramp type double square lubricating pad bearing capacity with dynamic pressure effect is answered
Consider that workbench starts and oil pocket static pressure bearing capacity and moved caused by wedge-shaped oil film when workbench high speed rotation when stable operation
Press bearing capacity two parts, formula as follows：
W=Wj+Wd (1)
In formula：W is the total bearing capacity of ramp type double square chamber hydrostatic thrust bearing；WjFor ramp type double square chamber hydrostatic thrust bearing
Static pressure bearing capacity；WdFor ramp type double square chamber hydrostatic thrust bearing dynamic pressure bearing capacity.
Step B, derive that single ramp type double square chamber hydrostatic thrust bearing is quiet, dynamic pressure bearing capacity is as follows respectively：
Single ramp type double square chamber hydrostatic thrust bearing static pressure bearing capacity equation is as follows：
First, the double square chamber flow formula of static pressure carrying is derived for ramp type double square cavity configuration size as shown in Figure 1
It is as follows：
First, the flow for circumferentially flowing out rectangular cavity through left and right sides sealing oil edge is：
Second, the flow for radially flowing out rectangular cavity through upper and lower both sides sealing oil edge is：
Then total outflow flow formula of double square chamber is；
In formula：μ is dynamic viscosity, and Δ P is oil pocket and external pressure differential, and Q is double square chamber total flow, the input flow rate as pumped；
Secondly, thrust bearing static pressure bearing capacity formula is as follows：
Wherein
Ae=(L-l1)(B-b2-2b1)
In formula：λ is double square oil pad structure parameter；AeFor double square lubricating pad effective bearing area；μ is dynamic viscosity；H is minimum
Oil film thickness；Q is single lubricating pad double square chamber total flow, the input flow rate as pumped；
Single ramp type double square chamber hydrostatic thrust bearing dynamic pressure bearing capacity equation is as follows：
First, for the fluid of arbitrary wedge angle and wedge length, the bearing capacity formula for deriving arbitrary wedge-shaped fluid is as follows：
In formula：μ is dynamic viscosity, and h is wedge-shaped oil film minimum thickness, and v is turntable rotating speed, and L is wedge-shaped oil film length, and θ is oil film
Wedge angle；
Secondly, for the dimensional parameters of ramp type double square chamber hydrostatic thrust bearing lubricating pad as shown in Figure 1,3, ramp type is derived
Double square chamber hydrostatic thrust bearing dynamic pressure bearing capacity formula is as follows：
Wd=μ ω [A1(C1+C2)+A2C3] (7)
Wherein
A2=Lb1
In formula：C1、C2、C3For ramp type double square chamber hydrostatic bearing oil pad structure parameter；A1For each rectangle oil pocket of single lubricating pad
All sealing oil edge areas unilateral to the left and right；A2Single side sealing oil edge area is radially descended for each rectangle oil pocket of single lubricating pad；μ is hydraulic pressure
Oily dynamic viscosity；H is wedge-shaped oil film minimum thickness；ω is turntable angular velocity of rotation；θ is oil film wedge angle；r1=r3For lubricating pad
Oil pocket circumferential left and right sides sealing oil edge center in outside is to the distance of the static pressure centre of gyration, r2=r4To the left for oil pocket week on the inside of lubricating pad
Right both sides sealing oil edge center is to the distance of the static pressure centre of gyration, r5<r6<r7<r8Its numerical value is respectively two oil pockets radial direction inside and outside lubricating pad
Distance of the upper and lower both sides sealing oil edge center to the static pressure centre of gyration.
Step C, it is as follows to derive the total bearing capacity formula of ramp type double square chamber hydrostatic thrust bearing：
The heavy hydrostatic bearing that the present invention is studied belongs to heavy wool pad guide rail structure, for five-meter numerical control vertical lathe Q1-205 series
On, as shown in figure 3, hydrostatic slideway includes that circumferentially array arrangement, i.e., each lubricating pad oil film mobility status are also in 12 lubricating pads
Periodically.It can thus be appreciated that the total dynamic pressure bearing capacity of such ramp type hydrostatic thrust bearing is：
Wherein static pressure bearing capacity factor K1=λ Ae；Dynamic pressure bearing capacity factor K2=A1(C1+C2)+A2C3。
Present embodiment effect：The present invention is mainly to determine the emphasis that dynamic pressure carries on the single lubricating pad of ramp type hydrostatic bearing
Region, is deduced the bearing capacity equation of different size inclined-planes lubricating pad, wherein it is the flow of pump, work to play main affecting parameters
Make platform rotating speed and inclination angle of inclined plane.Dynamic pressure effect is mixed into hydrostatic thrust bearing by the invention, and the dynamic pressure by calculating bearing is imitated
The bearing capacity of entire ramp type double square lubricating pad is released in the influence answered in turn, which improves original calculating bearing and hold
Loading capability value so that the hydrostatic pressures losses of lubricating pad are compensated, and improve the precision and stability of static pressure support operation, are solved
Friction Problem of Failure during static pressure support, this method through practical proof can effectively improve vertical numerical controlled lathe bearing capacity
50% or so.
Claims (2)
1. a kind of ramp type double square lubricating pad bearing capacity computation method considering dynamic pressure effect, it is characterised in that be directed to different sizes
Double square inclined-plane lubricating pad, analyzed by the lubrication mechanism to the single lubricating pad of ramp type double square chamber hydrostatic thrust bearing,
It derives it to start and static pressure bearing capacity equation and the dynamic pressure bearing capacity equation when bearing high-speed cruising when stable operation, and then obtains
The total bearing capacity formula of hydrostatic bearing；
It is a kind of to consider that the ramp type double square lubricating pad bearing capacity computation method of dynamic pressure effect is realized according to the following steps：
Step A, ramp type double square chamber hydrostatic thrust bearing bearing capacity computation method is determined：
It is analyzed by the lubrication mechanism to lubricating pad, the calculating of the ramp type double square lubricating pad bearing capacity with dynamic pressure effect is answered
Consider that workbench starts and oil pocket static pressure bearing capacity and moved caused by wedge-shaped oil film when workbench high speed rotation when stable operation
Press bearing capacity two parts, formula as follows：
W=Wj+Wd (1)
In formula：W is the total bearing capacity of ramp type double square chamber hydrostatic thrust bearing；WjFor ramp type double square chamber hydrostatic thrust bearing
Static pressure bearing capacity；WdFor ramp type double square chamber hydrostatic thrust bearing dynamic pressure bearing capacity；
Step B, derive that single ramp type double square chamber hydrostatic thrust bearing is quiet, dynamic pressure bearing capacity is as follows respectively：
Single ramp type double square chamber hydrostatic thrust bearing static pressure bearing capacity equation is as follows：
Wherein
Ae=(L-l1)(B-b2-2b1)
In formula：λ is double square oil pad structure parameter；AeFor double square lubricating pad effective bearing area；μ is dynamic viscosity；H is minimum
Oil film thickness；Q is single lubricating pad double square chamber total flow, the input flow rate as pumped；
Single ramp type double square chamber hydrostatic thrust bearing dynamic pressure bearing capacity equation is as follows：
Wd=μ ω [A1(C1+C2)+A2C3] (3)
Wherein
A2=Lb1
In formula：C1、C2、C3For ramp type double square chamber hydrostatic bearing oil pad structure parameter；A1For each rectangle oil pocket of single lubricating pad
All sealing oil edge areas unilateral to the left and right；A2Single side sealing oil edge area is radially descended for each rectangle oil pocket of single lubricating pad；μ is hydraulic pressure
Oily dynamic viscosity；H is wedge-shaped oil film minimum thickness；ω is turntable angular velocity of rotation；θ is oil film wedge angle；r1=r3For lubricating pad
Oil pocket circumferential left and right sides sealing oil edge center in outside is to the distance of the static pressure centre of gyration, r2=r4To the left for oil pocket week on the inside of lubricating pad
Right both sides sealing oil edge center is to the distance of the static pressure centre of gyration, r5<r6<r7<r8Its numerical value is respectively two oil pockets radial direction inside and outside lubricating pad
Distance of the upper and lower both sides sealing oil edge center to the static pressure centre of gyration；
Step C, it is as follows to derive the total bearing capacity formula of ramp type double square chamber hydrostatic thrust bearing：
Wherein static pressure bearing capacity factor K1=λ Ae；Dynamic pressure bearing capacity factor K2=A1(C1+C2)+A2C3。
2. a kind of ramp type double square lubricating pad bearing capacity computation method considering dynamic pressure effect according to claim 1,
It is characterized in that the hydrostatic bearing is to quantify oil pump feed, workbench is clockwise direction high speed rotation, the oil in the step A
Membrane modle takes 1/12 Fuel film model of whole circumference to be analyzed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810413854.0A CN108591260B (en) | 2018-05-03 | 2018-05-03 | Calculation method for bearing capacity of inclined plane type double-rectangular oil pad considering dynamic pressure effect |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810413854.0A CN108591260B (en) | 2018-05-03 | 2018-05-03 | Calculation method for bearing capacity of inclined plane type double-rectangular oil pad considering dynamic pressure effect |
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| CN108591260A true CN108591260A (en) | 2018-09-28 |
| CN108591260B CN108591260B (en) | 2020-07-24 |
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Cited By (4)
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| CN110443000A (en) * | 2019-08-13 | 2019-11-12 | 哈尔滨理工大学 | A kind of Calculation of Oil Film Thickness method of lubricating pad tilting-type double square chamber hydrostatic thrust bearing |
| CN111322511A (en) * | 2020-02-27 | 2020-06-23 | 南京工程学院 | Method for detecting lubricating performance of oil film in constant linear velocity operation of static pressure rotary table |
| CN111503152A (en) * | 2020-04-21 | 2020-08-07 | 南京工程学院 | Temperature rise control method for hydrostatic circular guide rail inclined plane oil pad |
| CN113311710A (en) * | 2021-05-27 | 2021-08-27 | 东华大学 | Method and system for predicting and controlling working performance of vertical static pressure sliding table with variable oil film thickness |
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Cited By (5)
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| CN110443000A (en) * | 2019-08-13 | 2019-11-12 | 哈尔滨理工大学 | A kind of Calculation of Oil Film Thickness method of lubricating pad tilting-type double square chamber hydrostatic thrust bearing |
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| CN111322511A (en) * | 2020-02-27 | 2020-06-23 | 南京工程学院 | Method for detecting lubricating performance of oil film in constant linear velocity operation of static pressure rotary table |
| CN111503152A (en) * | 2020-04-21 | 2020-08-07 | 南京工程学院 | Temperature rise control method for hydrostatic circular guide rail inclined plane oil pad |
| CN113311710A (en) * | 2021-05-27 | 2021-08-27 | 东华大学 | Method and system for predicting and controlling working performance of vertical static pressure sliding table with variable oil film thickness |
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