CN102221461A - Ship propelling unit and coupling dynamics test stand of ship body - Google Patents
Ship propelling unit and coupling dynamics test stand of ship body Download PDFInfo
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- 238000012360 testing method Methods 0.000 title claims abstract description 50
- 230000008878 coupling Effects 0.000 title claims abstract description 11
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- 238000005259 measurement Methods 0.000 claims abstract description 4
- 230000033001 locomotion Effects 0.000 claims description 10
- 238000004088 simulation Methods 0.000 claims description 10
- 239000010720 hydraulic oil Substances 0.000 claims description 7
- 230000008093 supporting effect Effects 0.000 claims description 7
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- 238000011161 development Methods 0.000 abstract description 14
- 238000013461 design Methods 0.000 abstract description 7
- 238000000034 method Methods 0.000 abstract description 5
- 238000009434 installation Methods 0.000 abstract description 2
- 230000005284 excitation Effects 0.000 abstract 3
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- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
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- 230000002045 lasting effect Effects 0.000 description 1
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- 238000005457 optimization Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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- 238000005728 strengthening Methods 0.000 description 1
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Abstract
本发明涉及一种船舶推进装置与船体的耦合动力学试验台。试验台主要由驱动电机、减速机、试件安装支架、激振器、力传感器、测控系统、摇摆系统组成；驱动电机经减速机减速，通过弹性联轴器带动被试件轴转动，被试件轴两端各设一个固定支承点，轴中多处安放浮动支承；试件安装支架下方放置摇摆台。本试验台针对船机轴试验开发设计，浮动支承设置了激振点，每个激振点可产生两个方向的激振，可测量外加载荷、轴承支承力、轴功率、轴系振动等数据，通过还原机轴在实际使用中因舱壁受外力作用而对其产生的影响，从而为轴的结构及安装方式的优化设计提供依据。
The invention relates to a coupling dynamics test bed for a ship propulsion device and a ship body. The test bench is mainly composed of a drive motor, a reducer, a test piece mounting bracket, a vibrator, a force sensor, a measurement and control system, and a swing system; A fixed support point is set at both ends of the specimen shaft, and floating supports are placed in multiple places in the shaft; a swing table is placed under the specimen mounting bracket. The test bench is designed for the development and design of the ship engine shaft test. The floating support is equipped with excitation points. Each excitation point can generate excitation vibration in two directions, and can measure data such as external load, bearing support force, shaft power, and shaft system vibration. , by restoring the influence of the crankshaft due to the external force on the bulkhead in actual use, it provides a basis for the optimal design of the shaft structure and installation method.
Description
Technical field:
The present invention relates to the Coupled Dynamics testing table of a kind of marine propulsion and hull.
Background technology:
Rich in natural resources is being contained in the ocean, and ocean resources are sources that the mankind depend on for existence.The exploitation ocean resources become the great strategic direction of countries in the world future development, and in order to carry out marine resources development better, the development marine technology is important techniques basis and condition.In recent years, big countries such as the U.S., Germany, Japan, Britain, India are in order to alleviate domestic shortage of resources problem, march marine resources development one after another, great attention marine resources development strategy, the high-new marine technology of develop actively, make large-scale and ultra-large type novel sea boats and ships and workbench, competitively fight for ocean resources.
In China, in order to promote boats and ships economy and shipping enterprise development, ensure territory, marine site, China southeast and ocean resources safety, press for the innovation of strengthening the boats and ships theory and technology.In recent years, development along with boats and ships, technical parameters large-scale and maximization boats and ships such as ultra large crude carrier, ocean resources exploitation accumulating boats and ships, scientific investigation boats and ships, aircraft carrier and large ship become increasing, its lasting running power reaches 60000 Thomas's power, boats and ships length surpasses 300m, and tonnage surpasses 3 * 10
5T and cardan shaft are that diameter is more than 500mm.Be accompanied by the power of marine propulsion, the maximization direction of technical parameters such as size develops, the functional reliability of marine propulsion, extremely Ship Design of new demand such as cabin integrated noise comfort level, build, the ship inspection, department such as port prison and shipping and crewman's great attention and concern, motion-promotion force to propulsion plant is learned characteristic and its centering of shafting, the bearing supporting, the deformation of hull, ship hull vibration, packoff, the main frame operating mode, coupled relation between base installation etc. are multifactor has proposed new technical matters, needs utilization more perfect, more accurate new theory carries out the performance demonstration and the design optimization of marine propulsion.If fault has appearred in large-scale and propulsion plant super large marine, just might cause tremendous loss, even become disaster, therefore, strengthen the Coupled Dynamics theoretical research between super large marine propulsion and the hull, existing important significance for theories has pressing for of engineerings such as boats and ships transportation, defence equipment and marine resources development strategy again, and its achievement in research will play a significant role to the development of country.
Because boats and ships maximize, many in recent years boats and ships produce the tail pipe abnormal noise under sail repeatedly, the tail tube bearing scorification, the host crankshaft fracture, faults such as hull and aircraft cabin noise are big, the Large crude-carrying vessel of check in nearly 3 years of the CCS Shanghai classification society only, liquefied gas ship, large ship such as container ship and bulk freighter this type of fault occurs up to tens of, have a strong impact on the safe handling of propulsion plant, go to search failure cause from existing ship specification and theory, can't find out the concrete mechanism that produces of fault, this fault that maximization boats and ships are described is to existing ship specification and the theoretical requirement that need to have proposed further perfect and development.
Marine propulsion is a yielding large scale of multi-support, big mass inertia dynamical system.In this system, main frame and angle of rake mass inertia are concentrated, be positioned at the two ends of cardan shaft system, transmission shaft is supported by the multiple tracks bearing, be positioned in the middle of the system, whole propulsion system is installed on the hull, and the distortion of hull, the displacement of each base is inharmonious and factors such as the loading of boats and ships and motion state all produce very important influence to the duty of propulsion plant, reliability and runnability.In marine propulsion and this complicated dynamical system of hull, coupling between each parameter and influence are not clearly to the influence of spitkit, have then become very important new theory problem for large-scale with large ships such as ultra large crude carrier, large ship, aircraft carriers.
The appearance of large ship, main frame in the propulsion plant and propulsion mode have had new development, marine main engine is except the low speed internal combustion engine, novel high-power gas turbine, electric propulsion apparatus, hybrid power and multimachine and car etc. are aboard ship especially actively used on the ship for civil use, the coupled relation of this novel high-power main frame and propulsion plant-hull thereof has become the new problem that must face in the boats and ships maximization process, in the marine shafting school, how vibration to have evaluated into a technical barrier with the comprehensive comfort level in cabin.
Simultaneously, large ship propulsion plant-hull dynamical system (as shown in Figure 1) has the dynamics singularity of self, the one, Ship Propeling propulsion system-Ship Structure has strong coupling, it is complicated big inertia, a large scale dynamical system that is composited by to-and-fro movement and gyration, the pulsating nature and the impact of motion are big, and general conventional rotor---the bearing system dynamics theory can't solve the dynamics problem in the marine propulsion; The 2nd, marine propulsion---hull system works have mobile waterborne or under water, Ship Structure distortion, loading and ship motion influence marine propulsion reliability of operation and stability by shafting alignment, the vibration generation coupling of base to marine propulsion.So the behavior of the Coupled Dynamics system between marine propulsion and hull is more complicated, the coupling influence factor is more, has the problem in science that needs further investigation.
In a word, large ship propulsion plant and hull coupled system dynamics research have important theoretical research and engineering application value for ship performance and shipping technical development.
Summary of the invention:
The Coupled Dynamics testing table that the purpose of this invention is to provide a kind of marine propulsion and hull.Simulation ship arbor in practical work process because of the influence of cabin wall distortion to its generation, for the structure of ship arbor and the optimal design of mounting means thereof provide foundation, this testing table is primarily aimed at the ship arbor and tests special development and Design, a plurality of exciting points can be set, each exciting point minute both direction, the practical working situation of energy real simulated ship arbor.
The present invention realizes by following technical scheme:
The Coupled Dynamics testing table of a kind of marine propulsion and hull (referring to Fig. 2 and Fig. 3), this testing table mainly is made up of drive motor, reductor, test specimen mounting bracket, vibrator, TT﹠C system and swing system; Described TT﹠C system is made up of industrial computer, force transducer, the data transmission system controller of unifying, force transducer is imported industrial computer with the data that collect by data transmission system, show in user interface, and by controller vibrator is operated according to user's input; Described swing system is made up of three servo-control systems and three-axis swinging platform, controls the motion of tilter by three servo-control systems; Described drive motor is connected on the reductor, link together by spring coupling and test specimen axle, a fixed supporting frame supporting is respectively established at test specimen axle two ends, floating support is laid in many places in the middle of the test specimen axle, tilter is placed in test specimen mounting bracket below, described vibrator has many groups, is installed on the test specimen mounting bracket.
In the technical scheme of the present invention, described vibrator comprises vertical vibrator and horizontal vibrator, each supporting-point is done two to exciting, join force transducer before each exciting head of described vertical vibrator and horizontal vibrator, form the exciting force ring and close TT﹠C system, and come control phase poor by user's requirement input.
In the technical scheme of the present invention, drive motor uses common commercial power, and supply voltage is AC380V, and frequency is 50Hz.The output shaft of drive motor enters reductor and slows down, and the output shaft of reductor drives arbor by spring coupling and rotates, and can add corresponding load on the tailing axle, obtains required vibration frequency by vibrator.
In the technical scheme of the present invention, vibrator provides energy by hydraulic oil source, the size of the controller passing ratio valve control output energy in the TT﹠C system, the force transducer that is installed in vibrator head front end front end detects the size of actual output energy, and controlled variable and real-time measurement values are shown by display device simultaneously.
The usage of testing table of the present invention, it is installed in vibrator on the test specimen mounting bracket, vibrator does not on the same group use simultaneously, or only select wherein several groups of uses for use, its exciting force size is by the controller passing ratio valve control of control hydraulic oil source, and each exciting point phase differential is by controlling each vibrator break-make.
The usage of testing table of the present invention, tilter and vibrator are controlled respectively, tilter is controlled by three servo-drive systems, vibrator provides energy by hydraulic oil source, control by controller passing ratio valve, the force transducer that is installed in vibrator head front end front end provides feedback, and tilter provides the simulation of ocean wave for the ship arbor, and vibrator is used to simulate the local pressure of arbor.
The usage of testing table of the present invention uses hyperchannel exciting TT﹠C system that the vibration frequency of test specimen axle is measured during observing and controlling.
In the technical scheme of the present invention, three servo-control systems by change the three-axis swinging platform interior, in, the corner of outer 3 frames finishes the simulation of ship rolling, pitching, yawing three-degree-of-freedom motion, inside casing rotates rolling (0 °～± 45 °) motion of simulation boats and ships, rotation simulation pitching (0 °～± 20 °) motion of center, rotation simulation yawing (0 °～± 15 °) motion of housing.The usage of testing table of the present invention, the load of test specimen axle obtains by charger.
The beneficial effect that the present invention reached:
(1) proofreaies and correct power, the moment of torsion that is transmitted by test specimen.
(2) centering of shafting.
(3) antiwear property of examination tailing axle, tail pipe.
(4) the examination axle is gone up the sealing ability of seal in the process of waving.
(5) the resistance to shock loads ability of ship arbor.
Description of drawings
Fig. 1 propulsion plant is installed model
Fig. 2 test platform structure master looks synoptic diagram
Fig. 3 test platform structure schematic top plan view
Among the figure: 1 drive motor, 2 reductors, 3 spring couplings, 4 axle head bearing supports, 5 vertical vibrators, 6 horizontal vibrators, 7 test specimen axles, 8 test specimen mounting brackets.
Embodiment
The ship arbor is installed on the supporting-point of cabin wall, when cabin is subjected to the external force effect, the bulkhead distortion, make the supporting-point of axle produce relative displacement or relative displacement trend, adopt the marine propulsion shown in the accompanying drawing 2,3 and the Coupled Dynamics table apparatus of hull to simulate above-mentioned operating mode, check the design rationality of test specimen axle under above-mentioned operating mode, reliability and its life-span is predicted.
Embodiment is as follows:
1) output shaft of drive motor 1 enters reductor 2 decelerations, the output shaft of reductor 2 drives test specimen axle 7 by spring coupling 3 and rotates, axle head bearing support 4 fixed bearings are respectively established at the two ends of test specimen axle 7, five place's floating supports (is example with five place's floating supports) have been laid in the axle, (a vertical vibrator 5 and a horizontal vibrator 6 are one group by five groups of vibrators, totally five groups) supporting and exciting, shown in Fig. 2,3, five groups of vibrators can use simultaneously, also can be only with wherein several groups, so that satisfy the demand that the different supportings of user are counted.
Vibrator provides energy by hydraulic oil source, control by controller passing ratio valve, the force transducer that is installed in vibrator head front end provides feedback, controlled variable and real-time measurement values are reflected on the display simultaneously intuitively, so just the stressing conditions of ship arbor under working condition be can reappear fully, and power, moment of torsion that correction is transmitted by the test specimen axle finished; Centering of shafting; The test of the antiwear property of tailing axle, tail watt.
2) equipment in the step 1) is fixed on the tilter, can realizes all intended function.Tilter and exciter system are controlled respectively, tilter provides the simulation of ocean wave for the ship arbor, the local pressure of vibrator simulation ship arbor, thereby the Coupled Dynamics testing table of this marine propulsion and the hull working environment of the tested test specimen axle of real simulated more.
Claims (8)
1. the Coupled Dynamics testing table of marine propulsion and hull, it is characterized in that: this testing table mainly is made up of drive motor (1), reductor (2), test specimen mounting bracket (8), vibrator, TT﹠C system and swing system; Described TT﹠C system is made up of the controller of being unified by industrial computer, force transducer, data transmission system, force transducer is imported industrial computer with the data that collect by data transmission system, show in user interface, and by controller vibrator is operated according to user's input; Described swing system is made up of three servo-control systems and three-axis swinging platform, controls the motion of tilter by three servo-control systems; Described drive motor (1) is connected on the reductor (2), link together by spring coupling (3) and test specimen axle (7), a fixed supporting frame (4) supporting is respectively established at test specimen axle (7) two ends, floating support is laid in many places in the middle of the test specimen axle, swing system is placed in test specimen mounting bracket (8) below, described vibrator has many groups, is installed on the test specimen mounting bracket (8).
2. the Coupled Dynamics testing table of marine propulsion according to claim 1 and hull, it is characterized in that: described vibrator comprises vertical vibrator (5) and horizontal vibrator (6), each supporting-point is done two to exciting, join force transducer before each exciting head of described vertical vibrator and horizontal vibrator, form the exciting force ring and close TT﹠C system, and come control phase poor by user's requirement input.
3. the Coupled Dynamics experiment table of marine propulsion according to claim 1 and hull is characterized in that: the supply voltage that drive motor uses is AC 380V, and frequency is 50Hz.
4. the Coupled Dynamics experiment table of marine propulsion according to claim 2 and hull, it is characterized in that: vibrator provides energy by hydraulic oil source, the size of the controller passing ratio valve control output energy in the TT﹠C system, the force transducer that is installed in vibrator head front end detects the size of actual output energy, and controlled variable and real-time measurement values are shown by display device simultaneously.
5. the application of the Coupled Dynamics testing table of marine propulsion according to claim 1 and 2 and hull, it is characterized in that: be installed in test specimen mounting bracket (8) and go up vibrator, its exciting force size is by the controller passing ratio valve control of control hydraulic oil source, each exciting point phase differential is by controlling the break-make of each group vibrator, vibrator does not on the same group use simultaneously, or only selects wherein several groups of uses for use.
6. the application of the Coupled Dynamics experiment table of claim 1 or 2 described marine propulsions and hull, it is characterized in that: tilter and vibrator are controlled respectively, tilter is controlled by three servo-drive systems, vibrator provides energy by hydraulic oil source, control by controller passing ratio valve, the force transducer that is installed in vibrator head front end provides feedback, and tilter provides the simulation of ocean wave for the ship arbor, the local pressure of vibrator simulation arbor.
7. the application of the Coupled Dynamics experiment table of marine propulsion according to claim 1 and 2 and hull is characterized in that: use hyperchannel exciting TT﹠C system that the vibration frequency of arbor is measured in real time.
8. according to the application of the Coupled Dynamics experiment table of described marine propulsion of claim and hull, it is characterized in that: the load of test specimen axle obtains by charger.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201110155123A CN102221461B (en) | 2011-06-10 | 2011-06-10 | Ship propelling unit and coupling dynamics test stand of ship body |
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| CN201110155123A CN102221461B (en) | 2011-06-10 | 2011-06-10 | Ship propelling unit and coupling dynamics test stand of ship body |
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| CN102221461B CN102221461B (en) | 2012-09-05 |
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Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102980765A (en) * | 2012-12-12 | 2013-03-20 | 武汉理工大学 | Comprehensive test platform for marine shafting |
| CN103323346A (en) * | 2013-07-16 | 2013-09-25 | 中国科学院地质与地球物理研究所 | One-dimensional stress wave rock test piece dynamic tester |
| CN103353395A (en) * | 2013-05-27 | 2013-10-16 | 武汉理工大学 | Hydraulic loading device for large marine propulsion shafting test bed |
| CN104215426A (en) * | 2014-09-22 | 2014-12-17 | 中国船舶工业集团公司第七〇八研究所 | Measuring device and measuring method of internal flow field and external characteristic of water-jet propeller |
| CN104266799A (en) * | 2014-10-17 | 2015-01-07 | 无锡市宏源弹性器材有限公司 | Test bench for ship shafting end face sealing device |
| CN104359658A (en) * | 2014-10-17 | 2015-02-18 | 燕山大学 | Load test board with sail stress simulation function |
| CN105021400A (en) * | 2015-07-07 | 2015-11-04 | 武汉理工大学 | Intermediate bearing with hydraulic loading device used for ship cardan shaft system test stand |
| CN106323594A (en) * | 2016-11-21 | 2017-01-11 | 董诗晨 | Ship shafting testing device under action of wave force |
| CN106969908A (en) * | 2017-04-07 | 2017-07-21 | 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） | Simulate the load testing machine of marine propeller |
| CN106996871A (en) * | 2017-04-07 | 2017-08-01 | 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） | Real yardstick marine propulsion shafting vibration transmissibility experimental rig |
| CN110243707A (en) * | 2019-04-19 | 2019-09-17 | 武汉理工大学 | Piston pin fatigue wear test device for marine diesel engine |
| CN110987251A (en) * | 2019-12-20 | 2020-04-10 | 武汉理工大学 | A dynamic load test method for ship bearings based on resistance strain gauges |
| CN111982511A (en) * | 2020-08-07 | 2020-11-24 | 武汉理工大学 | A fault simulation test bench for ship electric propulsion system |
| CN113267333A (en) * | 2021-07-19 | 2021-08-17 | 湖北东湖实验室 | Comprehensive performance testing device for shaftless pump jet propeller and using method thereof |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU582139A2 (en) * | 1976-06-18 | 1977-11-30 | Предприятие П/Я В-8662 | Ship model testing plant |
| SU1078409A1 (en) * | 1982-07-16 | 1984-03-07 | Всесоюзный заочный машиностроительный институт | Device for testing hydromechanical governor of rotational speed |
| CN1696631A (en) * | 2005-05-23 | 2005-11-16 | 苏州试验仪器总厂 | Triaxiality and six degrees of freedom test bench for airdriven vibration, transportation bump, and slant swing |
| CN101704403A (en) * | 2009-08-13 | 2010-05-12 | 上海海事大学 | Control and research/development platform for electric propulsion system of ships |
-
2011
- 2011-06-10 CN CN201110155123A patent/CN102221461B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU582139A2 (en) * | 1976-06-18 | 1977-11-30 | Предприятие П/Я В-8662 | Ship model testing plant |
| SU1078409A1 (en) * | 1982-07-16 | 1984-03-07 | Всесоюзный заочный машиностроительный институт | Device for testing hydromechanical governor of rotational speed |
| CN1696631A (en) * | 2005-05-23 | 2005-11-16 | 苏州试验仪器总厂 | Triaxiality and six degrees of freedom test bench for airdriven vibration, transportation bump, and slant swing |
| CN101704403A (en) * | 2009-08-13 | 2010-05-12 | 上海海事大学 | Control and research/development platform for electric propulsion system of ships |
Cited By (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102980765B (en) * | 2012-12-12 | 2014-03-26 | 武汉理工大学 | Comprehensive test platform for marine shafting |
| CN102980765A (en) * | 2012-12-12 | 2013-03-20 | 武汉理工大学 | Comprehensive test platform for marine shafting |
| CN103353395A (en) * | 2013-05-27 | 2013-10-16 | 武汉理工大学 | Hydraulic loading device for large marine propulsion shafting test bed |
| CN103353395B (en) * | 2013-05-27 | 2015-02-25 | 武汉理工大学 | Hydraulic loading device for large marine propulsion shafting test bed |
| CN103323346A (en) * | 2013-07-16 | 2013-09-25 | 中国科学院地质与地球物理研究所 | One-dimensional stress wave rock test piece dynamic tester |
| CN103323346B (en) * | 2013-07-16 | 2015-07-08 | 中国科学院地质与地球物理研究所 | One-dimensional stress wave rock mass specimen dynamic tester |
| CN104215426A (en) * | 2014-09-22 | 2014-12-17 | 中国船舶工业集团公司第七〇八研究所 | Measuring device and measuring method of internal flow field and external characteristic of water-jet propeller |
| CN104266799A (en) * | 2014-10-17 | 2015-01-07 | 无锡市宏源弹性器材有限公司 | Test bench for ship shafting end face sealing device |
| CN104359658A (en) * | 2014-10-17 | 2015-02-18 | 燕山大学 | Load test board with sail stress simulation function |
| CN105021400B (en) * | 2015-07-07 | 2018-03-16 | 武汉理工大学 | The intermediate bearing with hydraulic loading device system test-bed for ship propulsive shafting |
| CN105021400A (en) * | 2015-07-07 | 2015-11-04 | 武汉理工大学 | Intermediate bearing with hydraulic loading device used for ship cardan shaft system test stand |
| CN106323594A (en) * | 2016-11-21 | 2017-01-11 | 董诗晨 | Ship shafting testing device under action of wave force |
| CN106323594B (en) * | 2016-11-21 | 2018-08-31 | 董诗晨 | A kind of marine shafting experimental rig under action of wave force |
| CN106996871A (en) * | 2017-04-07 | 2017-08-01 | 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） | Real yardstick marine propulsion shafting vibration transmissibility experimental rig |
| CN106969908A (en) * | 2017-04-07 | 2017-07-21 | 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） | Simulate the load testing machine of marine propeller |
| CN106969908B (en) * | 2017-04-07 | 2019-05-28 | 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） | Simulate the load testing machine of marine propeller |
| CN106996871B (en) * | 2017-04-07 | 2019-05-31 | 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） | Real scale marine propulsion shafting vibration transmissibility experimental rig |
| CN110243707A (en) * | 2019-04-19 | 2019-09-17 | 武汉理工大学 | Piston pin fatigue wear test device for marine diesel engine |
| CN110987251A (en) * | 2019-12-20 | 2020-04-10 | 武汉理工大学 | A dynamic load test method for ship bearings based on resistance strain gauges |
| CN111982511A (en) * | 2020-08-07 | 2020-11-24 | 武汉理工大学 | A fault simulation test bench for ship electric propulsion system |
| CN113267333A (en) * | 2021-07-19 | 2021-08-17 | 湖北东湖实验室 | Comprehensive performance testing device for shaftless pump jet propeller and using method thereof |
| CN113267333B (en) * | 2021-07-19 | 2021-09-24 | 湖北东湖实验室 | Comprehensive performance testing device for shaftless pump jet propeller and using method thereof |
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