CN110389035B - Vibration characteristic test system of diesel engine propulsion system - Google Patents
Vibration characteristic test system of diesel engine propulsion system Download PDFInfo
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- CN110389035B CN110389035B CN201810349973.4A CN201810349973A CN110389035B CN 110389035 B CN110389035 B CN 110389035B CN 201810349973 A CN201810349973 A CN 201810349973A CN 110389035 B CN110389035 B CN 110389035B
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M15/00—Testing of engines
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M15/00—Testing of engines
- G01M15/04—Testing internal-combustion engines
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Abstract
The invention discloses a vibration characteristic test system of a diesel engine propulsion system, which comprises: the power output device, the thrust loading device and the transmission device are in transmission connection with the power output device and the thrust loading device at two ends respectively; the ship body simulation base, the power output device and the transmission device are arranged on the simulation base; and the air spring height control assembly is used for supporting the ship body simulation base to isolate external vibration. The air spring height control assembly of the test system can provide a boundary condition of soft support for the ship body simulation base, and further isolate external vibration.
Description
Technical Field
The invention relates to the field of test systems for ships, in particular to a vibration characteristic test system of a diesel engine propulsion system.
Background
The diesel engine is a main machine device commonly used for ships, the diesel engine can generate thrust after transmitting the power of the diesel engine to the propeller through the propulsion shafting, and the thrust acts on the ship body structure through the thrust bearing.
The thrust generated by the operation of diesel engines, gearboxes and propellers can induce vibrations in the hull or associated structures of the equipment and radiate noise. Structural vibrations caused by dynamic force excitation of the propeller are becoming more and more pronounced, even in the case of vibration-damping measures in diesel propulsion systems. Therefore, technicians need to study the contribution of the thrust of the diesel engine, the transmission and the propeller to the vibration response of the relevant structures, and accordingly, establish a vibration reduction and isolation measure for mutually coordinating the devices, so as to further improve the ship vibration control level.
In the prior art, various test devices for simulating ship propulsion systems for scientific research and teaching are established in domestic scientific research institutions and colleges. For example, a full-scale ship propulsion shafting vibration transmission characteristic test device (chinese patent CN106996871) developed by the chinese ship science research center adopts a motor to drive the whole horizontal shafting, and loads axial thrust dynamic force through an electromagnetic vibration exciter, and all the devices are rigidly mounted on the ground paved with a fine gravel layer after a concrete structure foundation platform. However, the mounting base of this device has a limited ability to isolate external vibrations, and the conventional test device has not been able to satisfy the test conditions for the reliability, vibration transmission characteristics, and vibration damping and isolating device performance of the diesel engine propulsion system that is elastically supported by a large axial thrust of a dummy propeller in the mounted state of the real-scale hull base.
Disclosure of Invention
It is an object of the present invention to provide a vibration characteristic testing system for a diesel propulsion system which obviates or mitigates the above-mentioned problems of the prior art.
The invention provides a simulated vibration characteristic test system, which comprises:
a diesel engine;
the thrust loading device is connected with the diesel engine and provides axial static thrust and axial dynamic force for the diesel engine;
the transmission device is connected between the diesel engine and the thrust loading device;
the diesel engine and the transmission device are both supported by the ship body simulation base;
a height control assembly supporting the hull-simulating base.
In an alternative embodiment, the transmission includes a gearbox, and both the gearbox and the diesel engine are supported by a vibration isolation unit.
In an alternative embodiment, the transmission comprises a transmission shaft, which is arranged obliquely.
In an alternative embodiment, the thrust loading means comprises:
the dynamic and static separation structure is connected with the transmission shaft;
the static loading device is connected with the dynamic and static separation structure and used for providing axial static thrust; and
and the dynamic force loading device is connected with the static force loading device and is used for providing axial dynamic force.
In an alternative embodiment, the static loading means comprises:
a static loading device mounting seat;
the air spring assembly is arranged on the static loading device mounting seat; and
and the thrust shaft penetrates through the air spring assembly and is connected with the dynamic and static separation structure.
In an optional embodiment, the moving and static separation structure includes:
a bearing seat; and
and the thrust bearing is arranged on the bearing seat and is connected with the transmission shaft.
In an alternative embodiment, the vibration isolation unit includes:
the first vibration isolation unit is arranged between the diesel engine and the ship body simulation base, and the first vibration isolation device comprises at least two layers of vibration isolation units;
and the second vibration isolation unit is arranged between the gear box and the ship body simulation base, and the second vibration isolation device comprises at least one layer of vibration isolation unit.
In an alternative embodiment, the height control assembly comprises:
a vertical air spring assembly for supporting the hull-simulating base;
the displacement sensor is positioned below the ship body simulation base and used for detecting the height change of the ship body simulation base; and
and the controller adjusts the vertical air spring assembly according to the value of the displacement sensor.
Drawings
The following drawings of the invention are included to provide a further understanding of the invention. The drawings illustrate embodiments of the invention and, together with the description, serve to explain the principles of the invention. In the drawings, there is shown in the drawings,
FIG. 1 is a schematic view of the overall configuration of a vibration characteristic testing system for a diesel engine propulsion system of the present invention;
FIG. 2 is a block diagram of the high spring coupling of the present invention;
FIG. 3 is a system schematic of an air spring height control assembly of the present invention;
FIG. 4 is a view showing the structure of dynamic and static separation according to the present invention;
fig. 5 is a structural view of the static loading apparatus of the present invention.
Detailed Description
In the following description, numerous specific details are set forth in order to provide a more thorough understanding of the present invention. It will be apparent, however, to one skilled in the art, that the present invention may be practiced without one or more of these specific details. In other instances, well-known features have not been described in order to avoid obscuring the invention.
Referring to fig. 1, an embodiment of the present invention discloses a vibration characteristic testing system of a diesel engine propulsion system, which includes a diesel engine 10, a thrust loading device 20, a transmission device 30 connected therebetween, a hull simulation base 40, and a height control assembly 50. The diesel engine 10 and the transmission 30 are disposed on the hull-simulating base 40, the hull-simulating base 40 is supported by the height control assembly 50 to isolate external vibration, and the hull-simulating base 40 approximates a boundary condition of floating in water.
The diesel engine 10 may be a V-type 8-cylinder diesel engine. Of course, the present application is not limited to a particular type of diesel engine 10, and it is contemplated that electric motors, gasoline engines, and the like may be used in accordance with the teachings of the present invention.
The diesel engine 10 may be mounted on the hull simulation base 40, and a first vibration isolation unit 61 may be provided between the diesel engine 10 and the hull simulation base 40. The first vibration isolating unit 61 includes at least two layers of vibration isolators 611 and 614. Intermediate rafts 612 may be disposed between isolators 611, 614. Vibration isolators 611, 614 may comprise elastomeric vibration isolators. The first vibration isolation unit 61 may function to reduce the transmission of the vibration of the diesel engine 10 to the hull simulation base 40, and facilitate the replacement of the vibration isolator to test and verify the performance of the vibration isolation unit. To facilitate mounting, the first vibration isolation unit 61 may further include a transition base and a mounting base to support the diesel engine and to be mounted to the hull simulation base 40.
Referring to fig. 1 and 2, the transmission 30 may include a high-elasticity coupling 31 (fig. 2), a gear box 32, and a shafting 33. A high-elasticity coupling 31 may be provided between the gearbox 32 and the diesel engine 10 and connected to the gearbox 32 and the diesel engine 10, respectively, for transmitting the rotation of the diesel engine 10 to the gearbox 32. Similarly, a second vibration isolation unit 62 may be provided between the gear box 32 and the hull simulation base 40. The second vibration isolation unit 62 is mainly used to damp the vibration of the gear box 32 to reduce the transmission of the vibration of the gear box 32 to the hull simulation base 40. The second vibration isolation unit 62 may include at least one layer of vibration isolators 624. The second vibration isolating unit 62 may be provided similarly to the first vibration isolating unit 61, and only one layer of the vibration isolators 624 may be provided. As shown in fig. 1, the second vibration isolation unit 62 provided between the gear box 32 and the hull simulation base 40 may include: a gear box transition base, a gear box raft and vibration isolators 624 disposed therebetween, and a gear box mounting base disposed below the gear box raft and on the hull simulation base 40 for supporting components in the second vibration isolation unit 62. Vibration isolator 624 may comprise a stiff elastomeric vibration isolator. The second vibration isolation unit 62 may function to reduce the transmission of the vibrations of the gearbox 32 to the hull simulation base 40, facilitating the replacement of the vibration isolators for testing and verifying the performance of the vibration isolation unit.
Referring to fig. 1, the diesel engine 10 and the transmission device 30 may be disposed on a hull-simulating base 40, and the hull-simulating base 40 may be formed by welding i-beams and steel plates into a whole using an integral platform design. The hull-simulating base 40 may be supported by and height-controlled by the height control assembly 50.
Referring to fig. 1 and 3, the height control assembly 50 may adjust the hull simulating base 40 to a set position height. The height control assembly 50 according to the present application may include: the vertical air spring assemblies 51 are used for supporting the ship body simulation base 40, the vertical air spring assemblies 51 can comprise a plurality of air spring assemblies, and the plurality of air spring assemblies 51 are arranged below the ship body simulation base 40 at equal intervals; the horizontal limiting air spring 54 is arranged corresponding to the vertical air spring assembly 51 and is used for ensuring the stability of the height control assembly 50 in the horizontal direction; a mounting seat 56 for supporting the horizontal limit air spring 54 and the vertical air spring assembly 51; the displacement sensor 52 is positioned below the ship body simulation base 40, wherein the displacement sensor 52 can comprise a plurality of sensors, is arranged corresponding to the vertical air spring assembly 51 and can monitor the position change of the ship body simulation base 40 in real time; an air supply line 53, both ends of which can be respectively communicated with the vertical air spring assembly 51 and the air source 55, so as to input the air in the air source 55 into the air spring height control assembly 50 or discharge part of the air in the air spring height control assembly 50; and a controller (not shown) for monitoring the position of the ship body simulation base 40 in real time through the displacement sensor 52 and changing the supporting height of the vertical air spring assembly 51 by controlling the air supply 55 to inflate and deflate.
For example, when the position of the hull simulation base 40 is lowered, the controller (not shown) inflates the vertical air spring assemblies 51 according to the data monitored by the displacement sensor 52, so that the position of the hull simulation base 40 is raised to the position before the lowering, and the hull simulation base 40 and various structures or components arranged on the hull simulation base 40 are further not affected by external vibration and can be isolated from the vibration of the external environment, thereby ensuring that the hull simulation base 40 is in the boundary condition similar to the floating in the water.
The above contents can be combined to see that: the air spring height control assembly 50 of the present test system provides a soft supportive boundary condition for the hull-simulating base 40 to isolate external vibrations. Meanwhile, the vibration isolation device 60 further improves the vibration isolation effect of the test device, so that the problem that the base in the prior art is directly arranged on the ground and cannot better isolate vibration from the outside is solved.
Referring to fig. 1 and 4, the shaft system 33 includes a drive shaft 331. The drive shaft 331 may be comprised of a thrust plate shaft 3311 and an intermediate shaft 3312. The drive shaft 331 may be inclined at an angle of 3.5 ° with respect to the horizontal. The belt thrust disk shaft is installed on the thrust bearing, the intermediate shaft 3312 is installed on the intermediate bearing and then extends into the self-aligning roller thrust bearing 212 in the dynamic and static separation structure 21, and then the force loaded on the dynamic and static separation structure 21 can be transmitted to the thrust bearing. The thrust bearing is a sliding thrust bearing with a thrust disk for a ship, and functions to support the transmission shaft and receive the thrust of the transmission shaft 331, and transmit the thrust to the hull simulation base 40.
The thrust loading device 20 may include a dynamic and static separation structure 21, a static loading device 22 and a dynamic force loading device 23. The transmission device 30 is connected with the static loading device 22 and the dynamic force loading device 23 through the dynamic-static separation structure 21, so that the static loading device 22 and the dynamic force loading device 23 can respectively provide axial static thrust and a loading device with large axial dynamic force for a diesel engine propulsion shaft system.
Referring to fig. 1, the moving and static separating structure 21 includes: a bearing seat 211, one end of the bearing seat 211 being connectable to the thrust loading device 20; a self-aligning roller thrust bearing 212 which is arranged on the bearing seat 211, one end of the intermediate shaft 3312 can extend into the self-aligning roller thrust bearing 212 and is connected with the self-aligning roller thrust bearing, and the intermediate shaft 3312 can further rotate relative to the bearing seat 211; when the intermediate shaft 3312 rotates, the bearing seat 211 does not rotate and only moves along the axial direction through the T-shaped groove slide rail 213, and the thrust loaded on the thrust loading device 20 can be transmitted to the transmission shaft.
Referring to fig. 5, the static loading device 22 includes: a static loading device mount 221; a guide bearing 222 provided on the static loading apparatus mount 221; an air spring assembly 223 disposed on the static loading device mount 221; and a thrust shaft 224 which is respectively arranged on the air spring assembly 223 and the guide bearing 222 in a penetrating way, so that the thrust shaft 224 can be fixedly arranged relative to the static loading device mounting seat 221. The static loading device mount 221 may also include a pressure regulating switch and an air source with a pressure value of 1.0 MPa. The static loading device 22 adjusts the inflation pressure of the air spring assembly 223 through a pressure adjusting switch to achieve the static thrust in the axial direction required by the test. Among them, the air spring assembly 223 includes a hollow type air spring assembly and a lateral air spring assembly.
Referring to fig. 1, the dynamic force loading unit 23 may include: a dynamic force loading device mount 231; a hydraulic servo actuator 232 provided on the dynamic force loading device mount 231; and a ball joint 233 connected between the hydraulic servo actuator 232 and the static loading device 22, so as to transmit the dynamic force generated by the dynamic force loading device 23 to the static loading device 22 and then to the transmission shaft. The dynamic force loading device 23 further includes a dynamic force loading device base 234 upon which the dynamic force loading device mount 231, the hydraulic servo actuator 232, and the ball joint 233 may be disposed. Certainly, the dynamic loading device 23 can work normally, and may further include a pressure sensor, a high-strength stud locking assembly, a hydraulic oil source, a control cabinet beside the machine, an industrial personal computer, a flexible hose, and the like. The dynamic force loading device 23 provides a maximum of ± 20kN or a maximum frequency of 60Hz and also provides a dynamic force of a combination of 3 frequencies, which simulates the dynamic force of a propeller at a plurality of main frequencies.
When the test system works, firstly, the diesel engine 10 is checked, then the storage battery, the fuel oil system, the lubricating oil liquid level, the water tank liquid level, the cooling water system, the gear box 32 lubricating oil liquid level and the connecting and discharging gear are in a discharging and cooling water state, the cooling water of the transmission device 30 and the actuator oil source and the 1.0MPa air source state, the thrust loading device 20 and the industrial power supply of the height control assembly 50 are adopted, no sundries exist on and near the rotating part, and the screws on the moving part and the equipment machine foot are in a fastening state.
And secondly, starting a fuel oil system, a cooling water system, an industrial power supply switch and a 1.0MPa air source.
Then, the height control assembly 50 is started to adjust the height of the ship body simulation base 40 to a set position, the position of the ship body simulation base is locked by the height control system after the ship body simulation base is 1mm away from the top end of the bottom limit screw, then the thrust loading device 20 is started, the hollow air spring assembly and the horizontal air spring assembly of the thrust loading device 20 structure are inflated, static thrust of 60kN at most is provided for the transmission shaft 331, and stress balance of the test system is guaranteed.
And then, starting the diesel engine 10 to warm up for 10 minutes under an idling working condition, switching a gear of the gear box 32 to a gear combination, after the transmission device 30 operates stably for 5 minutes, accelerating the diesel engine 10 to the working condition of rotating speed required by the test, starting the thrust loading device 20, and after the oil supply pressure is about 14MPa, setting the frequency and amplitude of the dynamic force required by the test to start the thrust loading test.
Finally, the reliability and vibration transmission characteristic test and vibration reduction and isolation equipment performance test of the diesel engine propulsion system are carried out after the rotating speed of the diesel engine 10, the connecting or disconnecting of the gear box 32 and the static and dynamic thrust parameters of the thrust loading device 20 are adjusted according to specific test conditions.
The present invention has been illustrated by the above embodiments, but it should be understood that the above embodiments are for illustrative and descriptive purposes only and are not intended to limit the invention to the scope of the described embodiments. Furthermore, it will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, and that many variations and modifications may be made in accordance with the teachings of the present invention, which variations and modifications are within the scope of the present invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (6)
1. A system for testing the vibration characteristics of a diesel propulsion system, comprising:
a diesel engine;
the thrust loading device is connected with the diesel engine and provides axial static thrust and axial dynamic force for the diesel engine;
the transmission device is connected between the diesel engine and the thrust loading device and comprises a transmission shaft;
the diesel engine and the transmission device are both supported by the ship body simulation base;
the height control subassembly supports hull simulation base, for hull simulation base provides the boundary condition that the simulation floats in aqueous, and for hull simulation base provides the boundary condition that soft support, the height control subassembly includes:
a vertical air spring assembly for supporting the hull-simulating base,
a displacement sensor located below the hull simulating base for detecting a change in height of the hull simulating base, an
The controller adjusts the vertical air spring assembly according to the value of the displacement sensor;
wherein, thrust loading device includes:
a dynamic and static separation structure connected with the transmission shaft,
a static force loading device connected with the dynamic and static separation structure for providing axial static thrust, an
The dynamic force loading device is connected with the static force loading device and used for providing axial dynamic force, the dynamic force loading device can simulate dynamic force of a plurality of main frequencies of the propeller, the frequency of the dynamic force is less than or equal to 60Hz, or the value of the dynamic force is greater than or equal to-20 KN and less than or equal to 20 KN.
2. The testing system of claim 1, wherein the transmission includes a gearbox, and wherein the gearbox and the diesel engine are both supported by a vibration isolation unit.
3. The testing system of claim 1, wherein the drive shaft is disposed at an incline.
4. The testing system of claim 1, wherein the static loading device comprises:
a static loading device mounting seat;
the air spring assembly is arranged on the static loading device mounting seat; and
and the thrust shaft penetrates through the air spring assembly and is connected with the dynamic and static separation structure.
5. The testing system of claim 1, wherein said dynamic and static separation structure comprises:
a bearing seat; and
and the thrust bearing is arranged on the bearing seat and is connected with the transmission shaft.
6. The testing system of claim 2, wherein the vibration isolation unit comprises:
the first vibration isolation unit is arranged between the diesel engine and the ship body simulation base and comprises at least two layers of vibration isolation units;
and the second vibration isolation unit is arranged between the gear box and the ship body simulation base and comprises at least one layer of vibration isolation unit.
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| CN201810349973.4A CN110389035B (en) | 2018-04-18 | 2018-04-18 | Vibration characteristic test system of diesel engine propulsion system |
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| CN201810349973.4A CN110389035B (en) | 2018-04-18 | 2018-04-18 | Vibration characteristic test system of diesel engine propulsion system |
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| CN110389035B true CN110389035B (en) | 2021-09-24 |
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| RU2739905C1 (en) * | 2020-08-18 | 2020-12-29 | Федеральное государственное автономное образовательное учреждение высшего образования "Сибирский федеральный университет" | Autonomous objects propellers test automation device |
| CN114294339B (en) * | 2021-11-23 | 2023-08-18 | 中国船舶重工集团公司第七0四研究所 | Marine floating structure air spring coupling |
| CN115307924B (en) * | 2022-10-12 | 2023-03-24 | 中国航发四川燃气涡轮研究院 | Dynamic ground effect simulation system for shipborne test run of aircraft engine |
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|---|---|---|---|---|
| JP2013181896A (en) * | 2012-03-02 | 2013-09-12 | Ihi Corp | Device for testing performance of ship propulsion mechanism |
| 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 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101767632B (en) * | 2008-12-30 | 2012-08-08 | 中国船舶重工集团公司第七一一研究所 | Test platform for ship propulsion system |
| CN102297753B (en) * | 2011-07-19 | 2013-03-20 | 华中科技大学 | Test bed for simulating longitudinal vibration of marine propulsion shafting |
| CN104792532B (en) * | 2015-04-28 | 2017-09-12 | 中国船舶重工集团公司第七一一研究所 | Thrust bearing equipment test device peculiar to vessel |
| 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 |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013181896A (en) * | 2012-03-02 | 2013-09-12 | Ihi Corp | Device for testing performance of ship propulsion mechanism |
| 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 |
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Address after: 201108 Shanghai city Minhang District Huaning Road No. 3111 Patentee after: The 711 Research Institute of China Shipbuilding Corp. Address before: 201108 Shanghai city Minhang District Huaning Road No. 3111 Patentee before: Shanghai Marine Diesel Engine Research Institute |