CN2614287Y - A hydrostatic bearing variation constant-current oil supply system - Google Patents
A hydrostatic bearing variation constant-current oil supply system Download PDFInfo
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- CN2614287Y CN2614287Y CN 01280421 CN01280421U CN2614287Y CN 2614287 Y CN2614287 Y CN 2614287Y CN 01280421 CN01280421 CN 01280421 CN 01280421 U CN01280421 U CN 01280421U CN 2614287 Y CN2614287 Y CN 2614287Y
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- oil
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- pressure
- regulating valve
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Abstract
A hydrostatic bearing variable constant flow oil supply system of the utility model belongs to hydrostatic bearing technique field of mechanical engineering, the key point of the utility model lies in that an electro hydraulic proportional speed-regulating valve is used as a flow controller of the oil supply system, an oil outlet of a variable-flow pump is parallel connected with an oil inlet of an overflow valve, the oil inlet of the electro hydraulic proportional speed-regulating valve on each static pressure oil recess is parallel connected with the oil outlet of the variable-flow pump, the oil outlet of the electro hydraulic proportional speed-regulating valve is connected with the oil inlet of a flow sensor and the oil inlet of a pressure sensor, the oil outlet of the flow sensor is connected with the oil inlet of the static pressure oil recess, the flow sensor and the pressure sensor is respectively formed a flow closed-loop system and a pressure closed-loop system with a calculating control system to keep the design oil film thickness being invariable and to make the oil film hardness be close to infinity. According to the utility to design and produce hydrostatic bearings, the utility model has the advantages of simple design and calculation, convenient initialization and alteration of design parameters, stable bearing performance, not being influenced by oil viscosity due to temperature changing, not being influenced by pressure changing, the oil film hardness being close to infinity, and having the advantages of other hydrostatic bearing oil supply systems.
Description
The utility model belongs to the hydrodynamic journal liquid polymers field in the mechanical engineering.
At present, the hydrodynamic journal liquid polymers oil supply system mainly contains two classes both at home and abroad.One class is constant pressure oil supply system (accompanying drawing 1), normal concentrating with an oil pump respectively to each flow controller fuel feeding, send into each oil pocket again, regulate charge oil pressure by relief valve, pressure when relying on oil to flow through flow controller falls automatic adjusting flow to adapt to the variation of load, often select the flow controller of compensate function for use, as capillary restrictor, Slot Aperture Restrictor, orifice restriction device, guiding valve feedback flow controller, book film feedback flow controller etc.Another kind of is constant current amount oil supply system (accompanying drawing 2, Fig. 3), can regulate oil pocket pressure automatically to adapt to the variation of load with the variation of oil slick thickness, generally by multiplex pump respectively to each oil pocket fuel feeding, or behind proportional valve or shunt fuel feeding, deliver to each oil pocket more respectively by an oil pump because to the manufacturing of pump or valve have relatively high expectations use less.
The purpose of this utility model is to make a kind of working pressure height, adjusts the constant current value automatically, keeps the design oil slick thickness, makes the oil film rigidity approach infinity, is applicable to the hydrostatic bearing that various load and load change are big.
The utility model is made up of variable displacement pump 1, relief valve 2, electrohydraulic proportional velocity regulating valve 3, flow transducer 4, pressure transducer 5, static pressure oil pocket 6, calculating control system 7 shown in accompanying drawing 4,5.It is characterized in that with the flow controller of electrohydraulic proportional velocity regulating valve as the hydrostatic bearing oil supply system, the variable displacement pump oil outlet also connects the relief valve oiler, electrohydraulic proportional velocity regulating valve oiler on each static pressure oil pocket also is connected on the variable displacement pump oil outlet, the electrohydraulic proportional velocity regulating valve oil outlet connects flow transducer oiler and pressure transducer oiler, the flow transducer oil outlet connects static pressure oil pocket oiler, flow transducer and calculating control system form the flow closed-loop system, and it is constant to keep setting flow value qsd.Pressure transducer and calculating control system form pressure circle system, calculate through calculating control system, revise and set flow value q
Sd, keep the design oil slick thickness constant, make the oil film rigidity approach infinity.
Advantage of the present utility model, be that designed hydrostatic bearing calculates simply, it is convenient to change setting value, reliable operation, and bearing performance is stable, be not subjected to oil viscosity because of influence of temperature variation, the influence that is not stressed and changes, the flow control accuracy height is adjusted flow value automatically, the oil film rigidity approach infinity is optimal hydrodynamic journal liquid polymers oil supply system.
This description of drawings:
Fig. 1: constant pressure oil supply system
Fig. 2: constant current amount oil supply system
Fig. 3: constant current amount oil supply system
Fig. 4: become constant current amount oil supply system
Fig. 5: become constant current amount fuel feeding control system
Among the figure: 1. variable displacement pump 2. relief valves 3. electrohydraulic proportional velocity regulating valves 4. flow transducers
5. pressure transducer 6. static pressure oil pockets 7. calculating control systems
The utility model embodiment such as accompanying drawing 4, the system diagram of 5 signals, by variable displacement pump 1, relief valve 2, electrohydraulic proportional velocity regulating valve 3, flow transducer 4, pressure transducer 5, static pressure oil pocket 6, calculating control system 7 is formed, the variable displacement pump oil outlet also connects the relief valve oiler, make the variable displacement pump oil outlet form certain fuel supply flow rate Qs and pressure P s, fuel supply flow rate Qs is regulated by variable displacement pump, constant charge oil pressure Ps is regulated by relief valve, electrohydraulic proportional velocity regulating valve oiler on each static pressure oil pocket also is connected on the variable displacement pump oil outlet, the electrohydraulic proportional velocity regulating valve oil outlet connects flow transducer oiler and pressure transducer oiler, and the flow transducer oil outlet connects static pressure oil pocket oiler.Electrohydraulic proportional velocity regulating valve flow value q is flow through in setting
Sd, the variation along with load, temperature etc. changes the pressure of static pressure oil pocket and flow, and the pressure when relying on oil to flow through electrohydraulic proportional velocity regulating valve falls, and regulates static pressure oil pocket pressure adaptation load automatically.The flux signal that flow transducer is measured amplifies through amplifier, and the collection of calculating control system, calculating are compared, and the throttle opening of control electrohydraulic proportional velocity regulating valve keeps setting flow value q
SdBy the pressure of pressure transducer measurement static pressure oil pocket, the flow value when calculating the design oil slick thickness is revised and is set flow value q
Sd, keep the design oil slick thickness.Calculating control system is also finished input, the calculating of hydrostatic bearing parameter designing value, and output becomes constant current amount system testing result.Theoretical calculation is as follows:
Just decide the flow setting value q of electrohydraulic proportional velocity regulating valve
Sd0
Q in the formula
0Oil pocket design discharge p
0Oil pocket design pressure h
0Oil pocket design oil slick thickness
C
dThe oil pocket flow coefficient, relevant with the oil pocket shape and size
The η lubricating oil viscosity
The single oil pocket load of W W=P
0A
e
A
eThe effective bearing area of an oil pocket can distribute by the actual pressure of difformity oil pocket and try to achieve their effective bearing area A
eValue
Calculate the flow setting value q of electrohydraulic proportional velocity regulating valve according to the oil pocket pressure value P of measuring
Sd
If
Both
Q oil pocket flow p oil pocket pressure h oil pocket oil slick thickness in the formula
R
hThe resistance of the liquid of oil pocket, relevant input design load with oil pocket shape, size and lubricating oil viscosity: 1. C
dThe oil pocket flow coefficient is A 2.
eThe effective bearing area of an oil pocket
3. 4. h of η lubricating oil viscosity
0Oil pocket design oil slick thickness is the single oil pocket load of W oil film rigidity 5.: when oil pocket was subjected to external load function, the oil pocket pressure of hydrostatic bearing will cause variation, with balance external load.The liquid resistance R of this system's oil pocket
h=η/C
dh
3, C
dBe definite value, and h is a constant, i.e. the liquid of oil pocket resistance R
hBe constant, this system's oil pocket flow is with the variation in direct ratio of oil pocket pressure, and this shows that this system has the oil film rigidity of approach infinity.
Claims (1)
1. a hydrostatic bearing becomes constant current amount oil supply system, by variable displacement pump (1), relief valve (2), electrohydraulic proportional velocity regulating valve (3), flow transducer (4), pressure transducer (5), static pressure oil pocket (6), calculating control system (7) is formed, it is characterized in that with the flow controller of electrohydraulic proportional velocity regulating valve as the hydrostatic bearing oil supply system, the variable displacement pump oil outlet also connects the relief valve oiler, make the variable displacement pump oil outlet form certain fuel supply flow rate Qs and pressure P s, fuel supply flow rate Qs is regulated by variable displacement pump, constant charge oil pressure Ps is regulated by relief valve, electrohydraulic proportional velocity regulating valve oiler on each static pressure oil pocket also is connected on the variable displacement pump oil outlet, the electrohydraulic proportional velocity regulating valve oil outlet connects flow transducer oiler and pressure transducer oiler, the flow transducer oil outlet connects static pressure oil pocket oiler, flow transducer and calculating control system form the flow closed-loop system, keep setting flow value q
SdConstant, pressure transducer and calculating control system form pressure circle system, calculate through calculating control system, revise and set flow value q
Sd, keep the design oil slick thickness constant, make the oil film rigidity approach infinity.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01280421 CN2614287Y (en) | 2001-12-28 | 2001-12-28 | A hydrostatic bearing variation constant-current oil supply system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 01280421 CN2614287Y (en) | 2001-12-28 | 2001-12-28 | A hydrostatic bearing variation constant-current oil supply system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2614287Y true CN2614287Y (en) | 2004-05-05 |
Family
ID=34230944
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 01280421 Expired - Fee Related CN2614287Y (en) | 2001-12-28 | 2001-12-28 | A hydrostatic bearing variation constant-current oil supply system |
Country Status (1)
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| CN (1) | CN2614287Y (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100533103C (en) * | 2007-11-30 | 2009-08-26 | 洛阳轴研科技股份有限公司 | Long-life high-precision oil supply velocity testing method for bearing |
| CN101900163A (en) * | 2010-07-14 | 2010-12-01 | 武汉重型机床集团有限公司 | Frequency-conversion constant-current hydrostatic bearing |
| CN101581338B (en) * | 2009-06-17 | 2011-02-16 | 重庆大学 | Hydraulic servo-controlled throttle device |
| CN102009353A (en) * | 2010-10-19 | 2011-04-13 | 武汉重型机床集团有限公司 | Variable constant-current static pressure guide rail and control method |
| CN102141084A (en) * | 2011-03-30 | 2011-08-03 | 哈尔滨理工大学 | Numerical simulation method for temperature and thickness relation of static thrust bearing gap oil film based on film thickness variation |
| CN102680059A (en) * | 2012-05-24 | 2012-09-19 | 哈尔滨电机厂有限责任公司 | Method for reducing small-flow calibration error of test bed flow meter of hydraulic machine model |
| CN103383295A (en) * | 2012-05-03 | 2013-11-06 | 上海大众汽车有限公司 | All-dimensional secondary pressure monitoring device and method of static pressure supporting system |
| CN108627336A (en) * | 2018-07-19 | 2018-10-09 | 中国人民解放军陆军装甲兵学院 | Gear fatigue test flow of lubrication control system |
| CN108661903A (en) * | 2018-05-17 | 2018-10-16 | 安徽工程大学 | A kind of inside engaged gear grease pump end clearance axial force balance system and method |
| 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 |
-
2001
- 2001-12-28 CN CN 01280421 patent/CN2614287Y/en not_active Expired - Fee Related
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100533103C (en) * | 2007-11-30 | 2009-08-26 | 洛阳轴研科技股份有限公司 | Long-life high-precision oil supply velocity testing method for bearing |
| CN101581338B (en) * | 2009-06-17 | 2011-02-16 | 重庆大学 | Hydraulic servo-controlled throttle device |
| CN101900163A (en) * | 2010-07-14 | 2010-12-01 | 武汉重型机床集团有限公司 | Frequency-conversion constant-current hydrostatic bearing |
| CN102009353A (en) * | 2010-10-19 | 2011-04-13 | 武汉重型机床集团有限公司 | Variable constant-current static pressure guide rail and control method |
| CN102141084B (en) * | 2011-03-30 | 2012-11-21 | 哈尔滨理工大学 | Numerical simulation method for temperature and thickness relation of static thrust bearing gap oil film based on film thickness variation |
| CN102141084A (en) * | 2011-03-30 | 2011-08-03 | 哈尔滨理工大学 | Numerical simulation method for temperature and thickness relation of static thrust bearing gap oil film based on film thickness variation |
| CN103383295A (en) * | 2012-05-03 | 2013-11-06 | 上海大众汽车有限公司 | All-dimensional secondary pressure monitoring device and method of static pressure supporting system |
| WO2013163851A1 (en) * | 2012-05-03 | 2013-11-07 | 上海大众汽车有限公司 | Omnidirectional secondary pressure monitoring device and method for static supporting system |
| CN103383295B (en) * | 2012-05-03 | 2015-10-21 | 上海大众汽车有限公司 | The comprehensive second pressure supervising device of hydrostatic support system and method |
| CN102680059A (en) * | 2012-05-24 | 2012-09-19 | 哈尔滨电机厂有限责任公司 | Method for reducing small-flow calibration error of test bed flow meter of hydraulic machine model |
| CN108661903A (en) * | 2018-05-17 | 2018-10-16 | 安徽工程大学 | A kind of inside engaged gear grease pump end clearance axial force balance system and method |
| CN108661903B (en) * | 2018-05-17 | 2020-05-01 | 安徽工程大学 | System and method for balancing axial force of end face gap of internal gear lubrication grease pump |
| CN108627336A (en) * | 2018-07-19 | 2018-10-09 | 中国人民解放军陆军装甲兵学院 | Gear fatigue test flow of lubrication control system |
| 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 |
| CN113311710B (en) * | 2021-05-27 | 2022-08-02 | 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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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20040505 Termination date: 20101228 |