CN104359658A - Load test board with sail stress simulation function - Google Patents
Load test board with sail stress simulation function Download PDFInfo
- Publication number
- CN104359658A CN104359658A CN201410553125.7A CN201410553125A CN104359658A CN 104359658 A CN104359658 A CN 104359658A CN 201410553125 A CN201410553125 A CN 201410553125A CN 104359658 A CN104359658 A CN 104359658A
- Authority
- CN
- China
- Prior art keywords
- gear
- bearing
- motor
- sail
- shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Abstract
The invention discloses a load test board with a sail stress simulation function. Mechanical hardware of the load test board includes a base, an oil tank, a motor, a low-speed large-torque motor, a pinion, a main gear, a gear shaft, a bearing and bearing seat set, a reducer, a coupler, a magnetic powder brake, an encoder and a torque sensor. According to the arrangement, the rotating angle of main gear simulates that of the sail; the magnetic powder brake is used with the reducer to simulate resistance applied onto ship during sailing. A hydraulic system of the load test board comprises the oil tank, the motor, a gear pump, a speed-regulating reversing valve, the motor, a one-way valve, a relief valve, a pressure sensor, a flow sensor and the main gear. The main gear is used for driving a sail rotation simulating mechanism. The load test board has the advantages that under varied wind field conditions, the stress applied onto the sail can be simulated in the real-time manner, structure is simple, operation is reliable, functions are complete, stability is high, and response speed is high.
Description
Technical field
The present invention relates to a kind of load test equipment of Experiments of Machanics technical field, particularly relate to and a kind ofly simulate the stressed bracket loading test platform of sail.
Background technology
Oversea wind aboundresources, and wind energy has the plurality of advantages such as clean, renewable, rich reserves.Utilize wind energy to carry out navaid as power, not only can reach the object of saving fuel energy, and the discharge of greenhouse gases can be reduced.Therefore, ships sail adds packing technique and has important practical significance to energy-saving and emission-reduction and environmental protection.
But sea turn has polytrope to wind speed, and it not the navigation that any wind direction is all conducive to boats and ships.When course is determined, need, according to different wind direction, sail is adjusted to best Windward angle so that navaid, thus need to design a set of adaptive control system that can adjust sail Windward angle in real time.At present, this technology is also in the pilot development stage, and all has that experimental period is long, cost is high, the problem of poor real with ship test and wind tunnel test.Therefore, in order to shorten adaptive control system construction cycle, save research cost, needing that design is a kind of badly can sail is stressed under real time modelling changeable wind field condition load testing machine.
Summary of the invention
For above-mentioned Problems existing, the present invention aims to provide a kind ofly can shorten the control system's development cycle, save research cost and can sail is stressed under real time modelling changeable wind field condition bracket loading test platform.
In order to solve the technical matters of above-mentioned existence, the object of the invention is realized by following technical proposals:
Simulate the bracket loading test platform that sail is stressed, comprise mechanical hardware and hydraulic system;
Its mechanical hardware formation comprises testing table base, fuel tank, motor, low-speed big torque motor, pinion wheel, gear wheel, the first gear shaft, the second gear shaft, clutch shaft bearing and bearing seat, the second bearing and bearing seat, the 3rd bearing and bearing seat, the 4th bearing and bearing seat, reductor, the first shaft coupling, the second shaft coupling, the 3rd shaft coupling, the 4th shaft coupling, magnetic powder brake, scrambler and torque sensor; Fuel tank and motor are installed on testing table base, low-speed big torque motor is arranged on testing table base by motor bracket, pinion wheel is sleeved on the first gear shaft of clutch shaft bearing and bearing seat and the second bearing and bearing seat support, gear wheel is sleeved on the second gear shaft of the 3rd bearing and bearing seat and the 4th bearing and bearing seat support, engaged transmission between gear wheel and pinion wheel, first---the 4th bearing and bearing seat are installed on testing table base; Low-speed big torque motor output shaft connects first gear shaft one end by the first shaft coupling, and scrambler is arranged on the other end of the first gear shaft; Reductor is arranged on reductor support, and reductor support installing is on testing table base, and reductor input shaft is connected by the second shaft coupling with between gear wheel, and speed reducer output shaft connects the 3rd shaft coupling; Magnetic powder brake is arranged on magnetic powder brake support, and magnetic powder brake support installing is on testing table base, and magnetic powder brake is connected with the 4th shaft coupling; Torque sensor is placed between the 3rd shaft coupling and the 4th shaft coupling;
Its hydraulic system comprises fuel tank, motor, gear-type pump, timing reversal valve, low-speed big torque motor, the first retaining valve, the second retaining valve, the first surplus valve, the second surplus valve, the first pressure transducer, the second pressure transducer and flow sensor; Be connected by bell-jar between motor with gear-type pump, the inlet port of gear-type pump is connected by hydraulic oil pipe with between fuel tank, and the oil drain out of gear-type pump is connected by hydraulic oil pipe with between timing reversal valve; Be connected by hydraulic oil pipe between low-speed big torque motor with timing reversal valve; First pressure transducer and the second pressure transducer are arranged on low-speed big torque motor import and export oil circuit respectively; First retaining valve is connected with the second retaining valve and is connected across between low-speed big torque motor import and export, and the first surplus valve is connected with the second surplus valve and is connected across between low-speed big torque motor import and export, and two contacts are connected with fuel tank; Flow sensor is connected between low-speed big torque motor and the first retaining valve.
The conveniently movement of testing table, testing table base is provided with castor.
During test, utilize the angle that the angle of bull gear drive is rotated to simulate sail, so determined the angle of revolution of sail by the rotational angle measuring or calculate gear wheel in test.Magnetic powder brake is for generation of load torque, and simulate the resistances such as windage suffered in actual ship's navigation, the current signal that the Resistance Value that magnetic powder brake produces is provided by electric-control system controls.Laying a reductor between magnetic powder brake and gear wheel, for amplifying the torque value that magnetic powder brake produces pro rata, and then reacting windage suffered by actual sail more truly.
For hydraulic system, gear-type pump as hydraulic power supply for system provides hydraulic energy.Timing reversal valve is on reversal valve, be integrated with a flow speed control valve, and it has two functions: one is commutation, changes the flow direction of hydraulic oil, realizes the rotating of motor; Two is flows of regulating system, controls the rotating speed of motor.Low-speed big torque motor is used for driving pinion, and then drives the gear wheel of simulation sail slew gear.Two retaining valves and two surplus valves are arranged on two of motor between actuator port and fuel tank respectively, and composition brake valve group, can alleviate anxious stopping and the hydraulic shock produced during counter motion, can play again the effect of repairing, prevent motor to inhale empty damage.During test, motor driven gear pump rotates to be system provides hydraulic energy to drive low-speed big torque motor to rotate, and then drives the gear wheel of simulation sail slew gear to rotate by motor driving pinion wheel.Timing reversal valve changes the flow direction of hydraulic oil and the flow of regulating system by the current signal that electric-control system is given, to control the anglec of rotation of low-speed big torque motor, and then the gear wheel of simulation sail slew gear is made to forward the position being conducive to ship's navigation most to according to certain rule.
Scrambler is used for measuring the rotational angle of pinion wheel, and then can by calculating the rotational angle of gear wheel; Torque sensor is used for the torque value detecting magnetic powder brake output in real time; Pressure transducer and flow sensor are used for pressure and the flow of Real-Time Monitoring hydraulic system.During test, in host computer, experimentally demand works out control program in advance, sends signal control magnetic powder brake and timing reversal valve by controller.The control system developed in host computer by the pressure of pressure transducer and flow sensor real-time monitoring system and flow, to guarantee that system works is normal; By the torque value that torque sensor monitoring magnetic powder brake exports, by the angle that encoders monitor pinion wheel rotates, Real-time Feedback signal, and compare with Setting signal, form closed-loop control, and then make the given moment of torsion of the real-time output control system of magnetic powder brake, make the gear wheel of simulation sail slew gear arrive the position of specifying quickly and accurately.For under changeable wind field condition, if be applicable to using sail supplementary navigation, so for different wind directions and wind speed, then necessarily there is different best sail parallactic angles.Now, the control program developed in host computer carries out calculating according to the data that scrambler records and obtains current sail parallactic angle, then position deviation is drawn by the control program of establishment, send control signal and control timing reversal valve and magnetic powder brake, and then make gear wheel forward best sail parallactic angle to according to behaviour's sail rule of the best.
Beneficial effect of the present invention is as follows:
The mode that the present invention uses mechanical drive and hydrostatic transmission to combine simulates actual boats and ships windward sail stressing conditions, provide good test condition for developing and debug sail adaptive control system in laboratory conditions, greatly can shorten the construction cycle of control system, save research cost.
The present invention utilizes the angle of bull gear drive to simulate the angle of revolution of sail, the mode utilizing magnetic powder brake and reductor to combine produces load torque to simulate in actual ship's navigation suffered resistance, can sail stressing conditions under the changeable wind field condition of real time modelling.
The present invention utilizes low-speed big torque motor to carry out driven wheel slew gear, and it is simple that this type of drive has structure, is convenient to the feature of arranging.Hydraulic control system have employed electrohydraulic proportion technology simultaneously, and system response time is fast.
Testing table of the present invention is equipped with various sensor, can the various parameters of Real-Time Monitoring pilot system, make testing table function more complete.Can closed-loop control be formed simultaneously, make Systematical control precision higher.
As fully visible, the present invention effectively provides a kind ofly can shorten the control system's development cycle, save research cost and can sail is stressed under real time modelling changeable wind field condition bracket loading test platform, structure is simple, reliable operation, complete function, control accuracy is high, good stability, fast response time is a kind of range of application stressed load testing machine of sail more widely.
Accompanying drawing explanation
Fig. 1 is structural representation of the present invention.
Fig. 2 is the A direction view of Fig. 1.
Fig. 3 is hydraulic system principle figure of the present invention.
Fig. 4 is pilot system schematic diagram of the present invention.
In figure: 1-motor; 2-low-speed big torque motor; 3-motor bracket; 4-first shaft coupling; 5-clutch shaft bearing and bearing seat; 6-first gear shaft; 7-pinion wheel; 8-second bearing and bearing seat; 9-scrambler; 10-base; 11-magnetic powder brake support; 12-magnetic powder brake; 13-the 4th shaft coupling; 14-torque sensor; 15-the 3rd shaft coupling; 16-reductor; 17-reductor support; 18-second shaft coupling; 19-the 3rd bearing and bearing seat; 20-gear wheel; 21-second gear shaft; 22-the 4th bearing and bearing seat; 23-fuel tank; 24-gear-type pump; 25-bell-jar; 26-castor; 27-timing reversal valve; 28-first pressure transducer; 29-second pressure transducer; 30-flow sensor; 31-first retaining valve; 32-second retaining valve; 33-first surplus valve; 34-second surplus valve.
Embodiment
Below in conjunction with drawings and Examples, the present invention is further elaborated.
See Fig. 1 and Fig. 2, of the present inventionly a kind ofly simulate the stressed bracket loading test platform of sail, its mechanical hardware forms and comprises testing table base 10, fuel tank 23, motor 1, low-speed big torque motor 2, pinion wheel 7, gear wheel 20, first gear shaft 6, second gear shaft 21, clutch shaft bearing and bearing seat 5, second bearing and bearing seat 8, the 3rd bearing and bearing seat 19, the 4th bearing and bearing seat 22, reductor 16, first shaft coupling 4, second shaft coupling 18, the 3rd shaft coupling 15, the 4th shaft coupling 13, magnetic powder brake 12, scrambler 9 and torque sensor 14.Fuel tank 23 and motor 1 are installed on testing table base 10, low-speed big torque motor 2 is arranged on testing table base 10 by motor bracket 3, pinion wheel 7 is sleeved on the first gear shaft 6 of clutch shaft bearing and bearing seat 5 and the second bearing and bearing seat 8 support, gear wheel 20 is sleeved on the second gear shaft 21 of the 3rd bearing and bearing seat 19 and the 4th bearing and bearing seat 22 support, engaged transmission between gear wheel 20 and pinion wheel 7, bearing and clutch shaft bearing seat 5, second bearing seat 8, the 3rd bearing seat 19, the 4th bearing seat 22 are installed on testing table base 10; Low-speed big torque motor 2 output shaft connects first gear shaft 6 one end by the first shaft coupling 4, and scrambler 9 is arranged on the other end of the first gear shaft 6; Reductor 16 is arranged on reductor support 17, and reductor support 17 is arranged on testing table base 10, and reductor 16 input shaft is connected by the second shaft coupling 18 with between gear wheel 20, and reductor 16 output shaft connects the 3rd shaft coupling 15; Magnetic powder brake 12 is arranged on magnetic powder brake support 11, and magnetic powder brake support 11 is arranged on testing table base 10, and magnetic powder brake 12 is connected with the 4th shaft coupling 13; Torque sensor 14 is placed between the 3rd shaft coupling 15 and the 4th shaft coupling 13.
See Fig. 3, hydraulic system of the present invention is mainly used to the gear wheel 20 driving simulation sail slew gear, and it comprises fuel tank 23, motor 1, gear-type pump 24, timing reversal valve 27, low-speed big torque motor 2, first retaining valve 31, second retaining valve 32, first surplus valve 33, second surplus valve 34, first pressure transducer 28, second pressure transducer 29 and flow sensor 30.Be connected by bell-jar 25 between motor 1 with gear-type pump 24, the inlet port of gear-type pump 24 is connected by hydraulic oil pipe with between fuel tank 23, and the oil drain out of gear-type pump 24 is connected by hydraulic oil pipe with between timing reversal valve 27; Be connected by hydraulic oil pipe between low-speed big torque motor 2 with timing reversal valve 27; First pressure transducer 28 and the second pressure transducer 29 are arranged on low-speed big torque motor 2 import and export oil circuit respectively; First retaining valve 31 is connected with the second retaining valve 32 and is connected across between low-speed big torque motor 2 import and export, and the first surplus valve 33 is connected with the second surplus valve 34 and is connected across between low-speed big torque motor 2 import and export, and two contacts are connected with fuel tank 23; Flow sensor 30 is connected between low-speed big torque motor 2 and the first retaining valve 31.
The conveniently movement of testing table, the position of testing table base 10 symmetry is provided with 4 castors 26.
During test, the angle that the angle utilizing gear wheel 20 to rotate is rotated to simulate sail, so the angle of revolution being determined sail in test by the rotational angle measuring or calculate gear wheel 20.Magnetic powder brake 12 is for generation of load torque, and simulate the resistances such as windage suffered in actual ship's navigation, the current signal that the Resistance Value that magnetic powder brake 12 produces is provided by electric-control system controls.Because the resistance of sail in rotary course suffered by different angles is different, therefore the Changing Pattern pre-entering resistance suffered by sail and its anglec of rotation in host computer is needed, and then according to the change of gear wheel 20 anglec of rotation, the torque value that magnetic powder brake 12 exports can be changed in real time during test.Laying a reductor 16 between magnetic powder brake 12 and gear wheel 20, for amplifying the torque value that magnetic powder brake 12 produces pro rata, and then reacting windage suffered by actual sail more truly.
For hydraulic system, gear-type pump 24 as hydraulic power supply for system provides hydraulic energy.Timing reversal valve 27 is on reversal valve, be integrated with a flow speed control valve, and it has two functions: one is commutation, changes the flow direction of hydraulic oil, realizes the rotating of motor 2; Two is flows of regulating system, controls the rotating speed of motor 2.Low-speed big torque motor 2 is used for driving pinion 7, and then drives the gear wheel 20 of simulation sail slew gear.Two retaining valves (31,32) and two surplus valves (33,34) are arranged between two actuator ports of motor 2 and fuel tank 23 respectively, composition brake valve group, anxious stopping and the hydraulic shock produced during counter motion can be alleviated, the effect of repairing can be played again, prevent motor 2 to inhale empty damage.During test, motor 1 driven gear pump 24 rotates to be system provides hydraulic energy to drive low-speed big torque motor 2 to rotate, and then drives pinion wheel 7 to drive the gear wheel 20 of simulation sail slew gear to rotate by motor 2.Timing reversal valve 27 changes the flow direction of hydraulic oil and the flow of regulating system by the current signal that electric-control system is given, to control the anglec of rotation of low-speed big torque motor 2, and then the gear wheel 20 of simulation sail slew gear is made to forward according to certain rule the position being conducive to ship's navigation most to.
Scrambler 9 is used for measuring the rotational angle of pinion wheel 7, and then can by calculating the rotational angle of gear wheel 20; The torque value that torque sensor 14 exports for detecting magnetic powder brake 12 in real time; Pressure transducer (28,29) and flow sensor 30 are for the pressure of Real-Time Monitoring hydraulic system and flow.
See Fig. 1, Fig. 2, Fig. 3 and Fig. 4, during test, in host computer, experimentally demand works out control program in advance, sends signal control magnetic powder brake 12 and timing reversal valve 27 by controller.The control system developed in host computer by the pressure of pressure transducer (28,29) and flow sensor 30 real-time monitoring system and flow, to guarantee that system works is normal; The torque value of magnetic powder brake 12 output is monitored by torque sensor 14, the angle that pinion wheel 7 rotates is monitored by scrambler 9, Real-time Feedback signal, and compare with Setting signal, form closed-loop control, and then make magnetic powder brake 12 moment of torsion that in real time output control system is given, make the gear wheel 20 of simulation sail slew gear arrive the position of specifying quickly and accurately.For under changeable wind field condition, if be applicable to using sail supplementary navigation, so for different wind directions and wind speed, then necessarily there is different best sail parallactic angles.Now, the control program developed in host computer carries out calculating according to the data that scrambler 9 records and obtains current sail parallactic angle, then position deviation is drawn by the control program of establishment, send control signal and control timing reversal valve 27 and magnetic powder brake 12, and then make gear wheel 20 forward best sail parallactic angle to according to behaviour's sail rule of the best.
Claims (2)
1. simulate the bracket loading test platform that sail is stressed, it is characterized in that: it comprises mechanical hardware and hydraulic system;
Its mechanical hardware formation comprises testing table base, fuel tank, motor, low-speed big torque motor, pinion wheel, gear wheel, the first gear shaft, the second gear shaft, clutch shaft bearing and bearing seat, the second bearing and bearing seat, the 3rd bearing and bearing seat, the 4th bearing and bearing seat, reductor, the first shaft coupling, the second shaft coupling, the 3rd shaft coupling, the 4th shaft coupling, magnetic powder brake, scrambler and torque sensor; Fuel tank and motor are installed on testing table base, low-speed big torque motor is arranged on testing table base by motor bracket, pinion wheel is sleeved on the first gear shaft of clutch shaft bearing and bearing seat and the second bearing and bearing seat support, gear wheel is sleeved on the second gear shaft of the 3rd bearing and bearing seat and the 4th bearing and bearing seat support, engaged transmission between gear wheel and pinion wheel, first---the 4th bearing and bearing seat are installed on testing table base; Low-speed big torque motor output shaft connects first gear shaft one end by the first shaft coupling, and scrambler is arranged on the other end of the first gear shaft; Reductor is arranged on reductor support, and reductor support installing is on testing table base, and reductor input shaft is connected by the second shaft coupling with between gear wheel, and speed reducer output shaft connects the 3rd shaft coupling; Magnetic powder brake is arranged on magnetic powder brake support, and magnetic powder brake support installing is on testing table base, and magnetic powder brake is connected with the 4th shaft coupling; Torque sensor is placed between the 3rd shaft coupling and the 4th shaft coupling;
Its hydraulic system comprises fuel tank, motor, gear-type pump, timing reversal valve, low-speed big torque motor, the first retaining valve, the second retaining valve, the first surplus valve, the second surplus valve, the first pressure transducer, the second pressure transducer and flow sensor; Be connected by bell-jar between motor with gear-type pump, the inlet port of gear-type pump is connected by hydraulic oil pipe with between fuel tank, and the oil drain out of gear-type pump is connected by hydraulic oil pipe with between timing reversal valve; Be connected by hydraulic oil pipe between low-speed big torque motor with timing reversal valve; First pressure transducer and the second pressure transducer are arranged on low-speed big torque motor import and export oil circuit respectively; First retaining valve is connected with the second retaining valve and is connected across between low-speed big torque motor import and export, and the first surplus valve is connected with the second surplus valve and is connected across between low-speed big torque motor import and export, and two contacts are connected with fuel tank; Flow sensor is connected between low-speed big torque motor and the first retaining valve.
2. according to claim 1ly a kind ofly simulate the stressed bracket loading test platform of sail, it is characterized in that: on described testing table base, castor is installed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410553125.7A CN104359658A (en) | 2014-10-17 | 2014-10-17 | Load test board with sail stress simulation function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410553125.7A CN104359658A (en) | 2014-10-17 | 2014-10-17 | Load test board with sail stress simulation function |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104359658A true CN104359658A (en) | 2015-02-18 |
Family
ID=52526941
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410553125.7A Pending CN104359658A (en) | 2014-10-17 | 2014-10-17 | Load test board with sail stress simulation function |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN104359658A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105301756A (en) * | 2015-11-03 | 2016-02-03 | 芜湖戎征达伺服驱动技术有限公司 | Super low speed rotation bearing platform |
| CN106468605A (en) * | 2016-10-28 | 2017-03-01 | 湘潭大学 | A kind of torque limiter breakaway torque Calibrating experimental bench on wind driven generator coupler |
| CN107515162A (en) * | 2016-08-15 | 2017-12-26 | 襄阳博亚精工装备股份有限公司 | Mechanical Static torsion test machine |
| CN110779555A (en) * | 2019-11-06 | 2020-02-11 | 中国船舶科学研究中心（中国船舶重工集团公司第七0二研究所） | Deep sea is with gas pressure compensation magnetism formula rotary encoder |
| CN113458766A (en) * | 2020-03-30 | 2021-10-01 | 广州汽车集团股份有限公司 | Bolt tightening device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0749291A (en) * | 1993-04-13 | 1995-02-21 | Tomoe Giken:Kk | Hydraulic power circulating type abrasion testing device |
| KR20100132843A (en) * | 2009-06-10 | 2010-12-20 | (주)케이지엠 | Load test equipment of motor reduction gear with up and down part |
| CN102221461A (en) * | 2011-06-10 | 2011-10-19 | 武汉理工大学 | Ship propelling unit and coupling dynamics test stand of ship body |
| CN102359869A (en) * | 2011-08-11 | 2012-02-22 | 徐州徐工筑路机械有限公司 | Loading test device for milling wheel driving system |
| CN202166519U (en) * | 2011-08-24 | 2012-03-14 | 东北农业大学 | Ship steering engine loading device for ground test |
-
2014
- 2014-10-17 CN CN201410553125.7A patent/CN104359658A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0749291A (en) * | 1993-04-13 | 1995-02-21 | Tomoe Giken:Kk | Hydraulic power circulating type abrasion testing device |
| KR20100132843A (en) * | 2009-06-10 | 2010-12-20 | (주)케이지엠 | Load test equipment of motor reduction gear with up and down part |
| CN102221461A (en) * | 2011-06-10 | 2011-10-19 | 武汉理工大学 | Ship propelling unit and coupling dynamics test stand of ship body |
| CN102359869A (en) * | 2011-08-11 | 2012-02-22 | 徐州徐工筑路机械有限公司 | Loading test device for milling wheel driving system |
| CN202166519U (en) * | 2011-08-24 | 2012-03-14 | 东北农业大学 | Ship steering engine loading device for ground test |
Non-Patent Citations (2)
| Title |
|---|
| 刘绪儒: ""风翼回转液压系统特性研究"", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》 * |
| 赵志强 等: ""翼帆回转实验台液压系统实验特性研究"", 《液压与气动》 * |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105301756A (en) * | 2015-11-03 | 2016-02-03 | 芜湖戎征达伺服驱动技术有限公司 | Super low speed rotation bearing platform |
| CN107515162A (en) * | 2016-08-15 | 2017-12-26 | 襄阳博亚精工装备股份有限公司 | Mechanical Static torsion test machine |
| CN107515162B (en) * | 2016-08-15 | 2023-12-08 | 襄阳博亚精工装备股份有限公司 | Mechanical static torque testing machine |
| CN106468605A (en) * | 2016-10-28 | 2017-03-01 | 湘潭大学 | A kind of torque limiter breakaway torque Calibrating experimental bench on wind driven generator coupler |
| CN106468605B (en) * | 2016-10-28 | 2019-01-08 | 湘潭大学 | A kind of torque limiter breakaway torque Calibrating experimental bench on wind driven generator coupler |
| CN110779555A (en) * | 2019-11-06 | 2020-02-11 | 中国船舶科学研究中心（中国船舶重工集团公司第七0二研究所） | Deep sea is with gas pressure compensation magnetism formula rotary encoder |
| CN113458766A (en) * | 2020-03-30 | 2021-10-01 | 广州汽车集团股份有限公司 | Bolt tightening device |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104359658A (en) | Load test board with sail stress simulation function | |
| CN107203184B (en) | The dynamic control method of straight line steering engine Electric Loading System | |
| CN203858778U (en) | Steering engine load simulation device based on electric loading | |
| CN103353395B (en) | Hydraulic loading device for large marine propulsion shafting test bed | |
| CN201903440U (en) | High-speed wind tunnel angle attacking control system | |
| CN103593508A (en) | Universal simulation platform for large-sized pumped storage power stations | |
| CN103760777B (en) | Boat diesel engine governor test stand | |
| CN102507060A (en) | Torque calibration device used for passive motor-driven loading system | |
| CN201606352U (en) | Testing device for hydraulic motor | |
| CN103323250B (en) | Test system and method for simulating field operation of variable pitch system of wind generating set | |
| CN203616642U (en) | System for testing steering engine of underwater unmanned navigation device | |
| CN109269808A (en) | A kind of diesel engine speed regulator semi-physical simulation test platform | |
| CN205002963U (en) | Pressurized strut load analogue means and semi -physical simulation tester | |
| CN103064404B (en) | Power matching controlling simulation testing system of automobile crane | |
| CN208833510U (en) | A kind of diesel engine speed regulator semi-physical simulation test platform | |
| CN202255757U (en) | Torque calibrating device for passive electric loading system | |
| CN102486899A (en) | Load simulator for loading gradient following passive loading steering engine | |
| CN108089521A (en) | A kind of hydraulic machinery test stand electric control system based on WinCC and PLC | |
| CN203463045U (en) | Control device of automatic derrick worker rotating mechanism | |
| CN103711685A (en) | Hydraulic loading testing device | |
| CN103236218B (en) | Adjusting and testing experiment system and adjusting and testing method for power machinery | |
| CN102122135B (en) | Closed loop load rigidity changing device | |
| CN202159255U (en) | Simulation bench of engineering machinery monitoring system | |
| CN205910003U (en) | High accuracy transmission detecting system | |
| CN204359538U (en) | A kind of high capacity waggon fault detection system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20150218 |
|
| WD01 | Invention patent application deemed withdrawn after publication |