CN101737380A - Electro-hydraulic load simulator with low-pressure oil pump - Google Patents
Electro-hydraulic load simulator with low-pressure oil pump Download PDFInfo
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- CN101737380A CN101737380A CN 200910218027 CN200910218027A CN101737380A CN 101737380 A CN101737380 A CN 101737380A CN 200910218027 CN200910218027 CN 200910218027 CN 200910218027 A CN200910218027 A CN 200910218027A CN 101737380 A CN101737380 A CN 101737380A
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Abstract
The invention relates to an electro-hydraulic load simulator with a low-pressure oil pump, and belongs to the technical field of electro-hydraulic servo control. The conventional electro-hydraulic load simulator has frictional resisting moment, on one hand, the burden of a tested motor is increased, and on the other hand, a simulation test result of the moment is influenced. In the prior art, the vibration of a hydraulic motor is caused by negative pressure generated in a pipeline at an oil suction port of the hydraulic motor. In the electro-hydraulic load simulator, the low-pressure oil pump is arranged on the oil suction pipeline of the hydraulic motor; before the electro-hydraulic load simulator operates and in the operating process of the electro-hydraulic load simulator, the low-pressure oil pump generates a backpressure to offset static friction moment, and the negative pressure is prevented from being generated. The electro-hydraulic load simulator is used for simulating loads of servo systems.
Description
Technical field
The present invention relates to a kind of electro-hydraulic load simulator, adopt low pressure fuel pump to overcome the technological scheme of device self friction resisting moment in static and motion state in the hydraulic power system therein, belong to the electro-hydraulic servo control technical field with low pressure fuel pump.
Background technique
Electro-hydraulic load simulator is used for simulating the various resisting moment that followup system is born at the movement process motor, as moment of inertia, moment of wind resistance, unbalance moment etc.One piece of by name " the electro-hydraulic servo simulator of servo system load ", application number are that 200910066801.7 Chinese invention patent ublic specification of application discloses a kind of typical scenario that adopts the electro-hydraulic servo load mode to realize the simulation of various loads, see shown in Figure 1, electro-hydraulic load simulator is made of oil hydraulic motor 1, selector valve 2, servovalve 3, high pressure oil pump 4, torque transducer 5, encoder 6, main control computer 7 and oil groove 8, torque transducer 5 and encoder 6 are installed on the oil hydraulic motor 1 moment output shaft, and are electrically connected with main control computer 7 respectively; Main control computer 7 is electrically connected with the valve actuator of servovalve 3; Be that conventional hydraulic circuit connects between oil hydraulic motor 1, selector valve 2, servovalve 3 threes, used hydraulic oil recycles in oil groove 8.The moment that adopts torque transducer 5 test simulator to provide, and realize the simulation of various loads by the opening amount of control servovalve 3.Oil hydraulic motor 1 and tested motor 9 are connected by mechanical mechanisms such as coupling or speed changers, and the moment that electro-hydraulic load simulator is simulated is applied on the tested motor 9.
There is frictional resistance moment electro-hydraulic load simulator in self, mainly from wherein the connection oil hydraulic motor 1 and the mechanical mechanism and the oil hydraulic motor part of tested motor 9.Especially drive the process of electro-hydraulic load simulator from static to motion at tested motor 9, need overcome frictional resistance moment, promptly have only tested motor 9 to produce when equaling the driving moment of this frictional resistance moment, its rotating shaft just begins to rotate.For electro-hydraulic load simulator, this frictional resistance moment of himself that is present in will inevitably be caused the output of electro-hydraulic load simulator moment to have error if do not eliminate.Existing solution is to adopt software compensation, promptly determine the frictional resistance moment data by actual measurement, with these data as zero point, in the electro-hydraulic load simulator working procedure, the moment data of detected tested motor carrying are deducted this data, carry out subsequent treatment again.Though this method does not increase the parts in the electro-hydraulic load simulator, but, the moment of tested motor 9 carryings is increased, increase the burden of tested motor on the one hand, when the less and frictional resistance moment of tested motor 9 operation torques is big, the situation that tested motor 9 is difficult to drive electro-hydraulic load simulator can appear particularly; On the other hand, tested motor 9 need consume excessive torque for overcoming frictional resistance moment, makes that electro-hydraulic load simulator is difficult to carry out the moment simulation according to design, influences test result.
Reason owing to operating mode, noise aspect, oil hydraulic motor 1 in the electro-hydraulic load simulator be the hydraulic power system apart from each other of core with high pressure oil pump 4, and the suction capacity of oil hydraulic motor 1 is limited, can in the pipeline at its inlet port place, produce negative pressure, when reaching Oil-gas Separation pressure, air in the oil will be separated, and can make oil hydraulic motor 1 produce vibration after the hydraulic oil that has air enters oil hydraulic motor 1, to such an extent as to cisco unity malfunction.
Summary of the invention
In simulation process occur the problem of vibration to the influence of electro-hydraulic load simulator analog result and in the hydraulic oil pipeline because of thereby negative pressure generation air separation causes electro-hydraulic load simulator for solving frictional resistance moment, we have invented a kind of electro-hydraulic load simulator with low pressure fuel pump.
Its constituent element of the present invention's device comprises oil hydraulic motor 1, selector valve 2, servovalve 3, high pressure oil pump 4, torque transducer 5, encoder 6, main control computer 7 and oil groove 8, torque transducer 5 and encoder 6 are installed on the oil hydraulic motor 1 moment output shaft, and be electrically connected with main control computer 7 respectively, main control computer 7 is electrically connected with the valve actuator of servovalve 3, be that conventional hydraulic circuit connects between oil hydraulic motor 1, selector valve 2, servovalve 3 threes, it is characterized in that, on the oil-absorbing pipeline 10 of oil hydraulic motor 1, low pressure fuel pump 11 is installed also.
Its effect of the present invention is, adopts low pressure fuel pump 11 can solve the technical problem that prior art exists to oil hydraulic motor 1 fuel feeding.Before electro-hydraulic load simulator work, a back pressure that is produced by low pressure fuel pump 11 is applied to oil hydraulic motor 1, until the mechanical mechanism that connects oil hydraulic motor 1 and tested motor 9, make electro-hydraulic load simulator be in the threshold state that is about to running, promptly the moment that is formed by this back pressure equals described static friction torque, tested motor 9 is equivalent to be in the state near unloaded, and starting load is very little in other words.When electro-hydraulic load simulator is started working, only need to get final product according to tested motor 9 rotating speeds, given definite required simulation Torque Control servovalve 3 opening amounts that provide such as command signal.The moment that tested motor 9 rotating shafts are carried almost completely is the simulation moment that electro-hydraulic load simulator applied.In addition, be because the generation of negative pressure in oil hydraulic motor 1 oil-absorbing pipeline 10 has been avoided in the existence of this back pressure equally, just the phenomenon that the air in the hydraulic oil is therefrom separated can not take place, the vibration problem of oil hydraulic motor 1 solves thereupon.Torque transducer 5 detected numerical value extremely approach electro-hydraulic load simulator provides moment, and testing result is more true.In addition, the existence of back pressure is equivalent to increase electro-hydraulic load simulator rigidity for electro-hydraulic load simulator carries out pretension, makes the electro-hydraulic load simulator simulation precision improve.
Description of drawings
Fig. 1 is the electro-hydraulic servo simulator structural representation of existing servo system load.Fig. 2 is the present invention's the electro-hydraulic load simulator structural representation with low pressure fuel pump.Fig. 3 is the mobile direction schematic representation of the preceding hydraulic power system hydraulic oil of the present invention's device busy, and this figure double as is a Figure of abstract.Fig. 4 is the hydraulic oil direction schematic representation that the flows when oil hydraulic motor in the hydraulic power system is operated in the pump state behind the present invention's the device busy.Fig. 5 is the hydraulic oil direction schematic representation that the flows when oil hydraulic motor in the hydraulic power system is operated in the motor state behind the present invention's the device busy.
Embodiment
Its constituent element of the present invention's device comprises oil hydraulic motor 1, selector valve 2, servovalve 3, high pressure oil pump 4, torque transducer 5, encoder 6, main control computer 7 and oil groove 8.Torque transducer 5 and encoder 6 are installed on the oil hydraulic motor 1 moment output shaft, and are electrically connected with main control computer 7 respectively.Torque transducer 5 is a kind of torque sensors, detects the moment of torsion that tested motor 9 bears, and the moment of torsion data of acquisition are as the output of feedback signal control electro-hydraulic load simulator, to realize the closed loop control of electro-hydraulic load simulator.Encoder 6 is a kind of shaft-position encoders, with tested motor 9 rotations, detects tested motor 9 movement velocitys.Main control computer 7 is electrically connected with the valve actuator of servovalve 3.Be that conventional hydraulic circuit connects between oil hydraulic motor 1, selector valve 2, servovalve 3 threes.Selector valve 2 adopts meta function Y type electro-hydraulic reversing valve, when electro-hydraulic load simulator no-load running, is communicated with filler opening, the oil outlet of oil hydraulic motor 1, realizes the conversion that servovalve 3 oil outlets are connected with oil hydraulic motor 1 filler opening, oil outlet.Servovalve 3 bases are controlled its openings of sizes from the size and Orientation of the command signal of main control computer 7, realize the control to oil hydraulic motor 1 filler opening, oil outlet working pressure.Selector valve 2 cooperates with servovalve 3, and decision is the filler opening of control oil hydraulic motor 1 or the working pressure of oil outlet.This working pressure is converted to moment by oil hydraulic motor 1, affacts on the tested motor 9 by the moment output shaft.High pressure oil pump 4 is a Main Hydraulic Pump, adopts the Oil pump electrical machinery group of motor and pluger type hydraulic pump integrative-structure pattern.Regulate high pressure oil pump electromagnetic relief valve 12, determine the delivery pressure of high pressure oil pump 4.Provide power by servovalve 3 for oil hydraulic motor 1.On the oil-absorbing pipeline 10 of oil hydraulic motor 1, low pressure fuel pump 11 is installed also.Low pressure fuel pump 11 be installed in oil-absorbing pipeline 10 near 8 sections in oil groove, avoid to the oil pipe of oil groove 8, forming negative pressure at its filler opening.Low pressure fuel pump 11 is by forming a back pressure to oil hydraulic motor 1 fuel feeding in oil-absorbing pipeline 10.Low pressure fuel pump electromagnetic relief valve 13 is in parallel with low pressure fuel pump 11, under the control of main control computer 7, regulate the charge oil pressure of low pressure fuel pump 11, just described back pressure is adjusted to just and can supports described frictional resistance moment and to prevent that in oil-absorbing pipeline 10 formation is enough to cause the degree of the negative pressure of separating in the air self-hydraulic oil.
Further specify the present invention below by description to the present invention's device working procedure.
Before the electro-hydraulic load simulator work, low pressure fuel pump 11 work also produce a back pressure, this back pressure directly produces a moment on oil hydraulic motor 1, at this moment, selector valve 2 is in a working position, servovalve 3 is not worked, and the flow direction of hydraulic oil is: oil groove 8, low pressure fuel pump 11, oil-absorbing pipeline 10, just change one-way valve 14, oil hydraulic motor 1, selector valve 2, Twoway valves 15, oil groove 8, see shown in Figure 3.Regulate low pressure fuel pump electromagnetic relief valve 13, make the size of back pressure reach the state that makes electro-hydraulic load simulator be in motion soon and do not move.
After the electro-hydraulic load simulator work, tested motor 9 drives oil hydraulic motor 1 and rotates, and oil hydraulic motor 1 switches between pump or motor state according to the moment of electro-hydraulic load simulator needs simulation.
When oil hydraulic motor 1 was operated in the pump state, tested motor 9 imposed on 1 one moments of oil hydraulic motor, drives its rotation, as just changeing.Set up resisting moment by control servovalve 3 opening amounts and act on the oil hydraulic motor 1 this moment, and be delivered on the tested motor 9, realizes the resisting moment simulation.In this process, low pressure fuel pump 11 continues to provide back pressure, and the moment that this back pressure produces on oil hydraulic motor 1 is identical with the moment direction that tested motor 9 imposes on oil hydraulic motor 1.Hydraulic oil when oil hydraulic motor 1 is operated in the pump state direction that flows is: oil groove 8, low pressure fuel pump 11, oil-absorbing pipeline 10, just change one-way valve 14, oil hydraulic motor 1, selector valve 2, servovalve 3, return check valve 16, oil groove 8, see shown in Figure 4.
When oil hydraulic motor 1 was operated in the motor state, tested motor 9 imposed on 1 one moments of oil hydraulic motor, drives its rotation, as just changeing.High pressure oil pump 4 for oil hydraulic motor 1 provides power, drives its rotation by servovalve 3, as just changeing.Again by oil hydraulic motor 1 with this power-converting be one in the same way moment impose on tested motor 9.In this working state, set up certain braking torque by control servovalve 3 opening amounts and act on the oil hydraulic motor 1, and be delivered on the tested motor 9, realize the braking torque simulation.In this process, low pressure fuel pump 11 still continues to provide back pressure, and the moment that this back pressure produces on oil hydraulic motor 1 is identical with the moment direction that high pressure oil pump 4 imposes on oil hydraulic motor 1.When oil hydraulic motor 1 is operated in the motor state, in electro-hydraulic load simulator, there are two hydraulic oil circulations.Wherein the hydraulic oil that is ordered about by low pressure fuel pump 11 direction that flows is: oil groove 8, low pressure fuel pump 11, oil-absorbing pipeline 10, just change one-way valve 14, oil hydraulic motor 1, selector valve 2, Twoway valves 15, oil groove 8, see shown in Figure 5.Wherein the mobile direction of hydraulic oil of being ordered about by high pressure oil pump 4 is: oil groove 8, high pressure oil pump 4, servovalve 3, selector valve 2, hydraulic-pressure pump 1, selector valve 2, Twoway valves 14, oil groove 8, see shown in Figure 5.
After the electro-hydraulic load simulator work, tested motor 9 drives oil hydraulic motor 1 counter-rotating, and the flow path of the hydraulic oil in the hydraulic power system changes in the one-way valve link, flows by counter-rotating one-way valve 17, and other are constant.
Claims (2)
1. electro-hydraulic load simulator with low pressure fuel pump, its constituent element comprises oil hydraulic motor (1), selector valve (2), servovalve (3), high pressure oil pump (4), torque transducer (5), encoder (6), main control computer (7) and oil groove (8), torque transducer (5) and encoder (6) are installed on oil hydraulic motor (1) the moment output shaft, and be electrically connected with main control computer (7) respectively, main control computer (7) is electrically connected with the valve actuator of servovalve (3), oil hydraulic motor (1), selector valve (2), be that conventional hydraulic circuit connects between servovalve (3) three, it is characterized in that, on the oil-absorbing pipeline (10) of oil hydraulic motor (1), low pressure fuel pump (11) is installed also.
2. electro-hydraulic load simulator according to claim 1 is characterized in that, low pressure fuel pump (11) be installed in oil-absorbing pipeline (10) near oil groove (8) section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN 200910218027 CN101737380B (en) | 2009-12-17 | 2009-12-17 | Electro-hydraulic load simulator with low-pressure oil pump |
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| CN 200910218027 CN101737380B (en) | 2009-12-17 | 2009-12-17 | Electro-hydraulic load simulator with low-pressure oil pump |
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| CN101737380A true CN101737380A (en) | 2010-06-16 |
| CN101737380B CN101737380B (en) | 2013-02-20 |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102654754A (en) * | 2012-04-18 | 2012-09-05 | 中国工程物理研究院总体工程研究所 | Method for detecting vibration control dynamic range by using load simulator and load simulator |
| CN104155608A (en) * | 2014-09-04 | 2014-11-19 | 上海航天电子通讯设备研究所 | Rotating load simulation device |
| CN104198170A (en) * | 2014-08-26 | 2014-12-10 | 北京精密机电控制设备研究所 | Front-oscillation center spray pipe load simulating friction loading device |
| CN105045134A (en) * | 2015-05-25 | 2015-11-11 | 哈尔滨工业大学 | Double-friction-disk loading mechanism and bidirectional friction loading-type no-additional-torque electro-hydraulic load simulator employing same |
| CN105045133A (en) * | 2015-05-25 | 2015-11-11 | 哈尔滨工业大学 | Multi-friction-plate stacking loading mechanism and large-amplitude bidirectional friction loading-type electro-hydraulic load simulator employing same |
| CN106855466A (en) * | 2015-12-08 | 2017-06-16 | 上海宇航系统工程研究所 | A kind of big flexible load simulator of single-degree-of-freedom |
| CN107796644A (en) * | 2017-10-19 | 2018-03-13 | 中石化四机石油机械有限公司 | A kind of motor-driven load experimental rig of oil gas field Operating Pressure and test method |
| CN110907830A (en) * | 2019-12-13 | 2020-03-24 | 永昌控股集团有限公司 | Tubular motor life test machine |
| CN112983800A (en) * | 2021-03-19 | 2021-06-18 | 北京航空航天大学 | Pump environment simulation and test system for electro-hydrostatic actuator |
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| CN201013312Y (en) * | 2006-03-09 | 2008-01-30 | 西南石油学院 | Oil extraction load simulator |
| CN101532516B (en) * | 2009-04-10 | 2010-12-29 | 长春理工大学 | Device for simulating servo system load by electrohydraulic servo |
| CN101532517A (en) * | 2009-04-10 | 2009-09-16 | 长春理工大学 | Method for simulating servo system load by electrohydraulic servo |
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2009
- 2009-12-17 CN CN 200910218027 patent/CN101737380B/en not_active Expired - Fee Related
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102654754A (en) * | 2012-04-18 | 2012-09-05 | 中国工程物理研究院总体工程研究所 | Method for detecting vibration control dynamic range by using load simulator and load simulator |
| CN104198170B (en) * | 2014-08-26 | 2017-01-25 | 北京精密机电控制设备研究所 | Front-oscillation center spray pipe load simulating friction loading device |
| CN104198170A (en) * | 2014-08-26 | 2014-12-10 | 北京精密机电控制设备研究所 | Front-oscillation center spray pipe load simulating friction loading device |
| CN104155608A (en) * | 2014-09-04 | 2014-11-19 | 上海航天电子通讯设备研究所 | Rotating load simulation device |
| CN104155608B (en) * | 2014-09-04 | 2017-05-31 | 上海航天电子通讯设备研究所 | One kind rotates load simulating device |
| CN105045134A (en) * | 2015-05-25 | 2015-11-11 | 哈尔滨工业大学 | Double-friction-disk loading mechanism and bidirectional friction loading-type no-additional-torque electro-hydraulic load simulator employing same |
| CN105045133A (en) * | 2015-05-25 | 2015-11-11 | 哈尔滨工业大学 | Multi-friction-plate stacking loading mechanism and large-amplitude bidirectional friction loading-type electro-hydraulic load simulator employing same |
| CN105045134B (en) * | 2015-05-25 | 2017-08-25 | 哈尔滨工业大学 | The bi-directional friction loaded type of double frictional disk load maintainers and the use mechanism is without Surplus Moment electrohydraulic load simulator |
| CN105045133B (en) * | 2015-05-25 | 2017-11-17 | 哈尔滨工业大学 | More friction plate superposition load maintainers and the amplitude bi-directional friction loaded type electrohydraulic load simulator using the mechanism |
| CN106855466A (en) * | 2015-12-08 | 2017-06-16 | 上海宇航系统工程研究所 | A kind of big flexible load simulator of single-degree-of-freedom |
| CN106855466B (en) * | 2015-12-08 | 2019-08-23 | 上海宇航系统工程研究所 | A kind of big flexible load simulator of single-degree-of-freedom |
| CN107796644A (en) * | 2017-10-19 | 2018-03-13 | 中石化四机石油机械有限公司 | A kind of motor-driven load experimental rig of oil gas field Operating Pressure and test method |
| CN110907830A (en) * | 2019-12-13 | 2020-03-24 | 永昌控股集团有限公司 | Tubular motor life test machine |
| CN112983800A (en) * | 2021-03-19 | 2021-06-18 | 北京航空航天大学 | Pump environment simulation and test system for electro-hydrostatic actuator |
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| CN101737380B (en) | 2013-02-20 |
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