CN2729691Y - Crankshaft bending fatigue experiment system - Google Patents
Crankshaft bending fatigue experiment system Download PDFInfo
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- CN2729691Y CN2729691Y CN 200420082674 CN200420082674U CN2729691Y CN 2729691 Y CN2729691 Y CN 2729691Y CN 200420082674 CN200420082674 CN 200420082674 CN 200420082674 U CN200420082674 U CN 200420082674U CN 2729691 Y CN2729691 Y CN 2729691Y
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- 238000005452 bending Methods 0.000 title claims abstract description 14
- 230000001133 acceleration Effects 0.000 claims description 8
- 239000011888 foil Substances 0.000 claims description 7
- 239000000523 sample Substances 0.000 claims description 7
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 238000012360 testing method Methods 0.000 description 15
- 238000000034 method Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000009661 fatigue test Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000010998 test method Methods 0.000 description 3
- 230000003321 amplification Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 238000004364 calculation method Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 238000013523 data management Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000003199 nucleic acid amplification method Methods 0.000 description 2
- 230000008520 organization Effects 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
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- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010205 computational analysis Methods 0.000 description 1
- 230000003750 conditioning effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000007726 management method Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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Abstract
The utility model discloses a crankshaft bending fatigue experiment system. The system is mainly composed of a harmonic vibration table body, a vibration exciter, a frequency changer, a programmable logic controller, a sensor group, a strain magnifying apparatus, and a computer. The utility model greatly reduces the manpower burden, provides convenience for experiment operation of experiment persons, reduces the artificial participating sections which are easy to lead to the operational errors, and makes the complicated algorithm with high accuracy applied, and the utility model obviously raises the accuracy of the crankshaft fatigue experiment.
Description
Technical field
The utility model relates to mechanical field, especially, relates to a kind of crankshaft bending fatigue pilot system that is applied to Mechanical Product Reliability assessment and research.
Background technology
The integrity problem of engineering goods is paid close attention to by people because of produce material impact in the human being's production life always.As crucial carrying parts of internal combustion engine, one of main contents of bent axle reliability are its bending fatigue problems under the high cycle fatigue stress.Along with continually strengthening of internal combustion engine, this problem must be also can be as focus and long-term existence.
Because crankshaft fatigue the complex nature of the problem, by the integrity problem of computational analysis bent axle in real work a lot of limitation are arranged also under the prior art level, it is essential with more needed data in the acquisition research to simulate its course of work by test method.The major advantage of test method is can be than the load-bearing capacity of more comprehensive examination bent axle bent axle under ad hoc structure, material and process conditions, and can directly provide the actual safety and the fatigue limit of bent axle.
The crankshaft bending fatigue testing machine is some dissimilar because of the difference that loads form has, as universal testing machine, hydraulic pulsation fatigue tester, and the program control fatigue tester of electro-hydraulic servo, resonance fatigue tester and high-frequency resonant fatigue tester etc.Because showing stronger advantage aspect operability, testing machine stability and the overall price/performance ratio of test, the resonant mode fatigue tester is used comparatively extensive.
In China, the crankshaft bending fatigue pilot system in the major applications is generally outmoded at present, and subject matter can be summarized as following 3 points:
(1) test unit load precision is on the low side, be about ± 5%;
(2) the load calibration computing method are backward relatively; Do not make full use of accurate mathematical statistics and analytical approach Processing Test data; All there are the problem of authenticity and poor accuracy in test findings and analysis result.
(3) adopt modern test organization's ladder of management of testing control technology and science; Intellectuality, the automatization level of system are lower.
The utility model content
In order to address the above problem, the purpose of this utility model is to provide a kind of crankshaft bending fatigue pilot system.
The technical scheme in the invention for solving the above technical problem is: a kind of crankshaft bending fatigue pilot system, and it comprises: a resonance stage body, form by bent axle and swing arm; One vibrator mainly is made up of eccentric wheel and motor, links to each other with the master arm of swing arm; One frequency converter links to each other with the motor of vibrator; One programmable logic controller (PLC) links to each other with frequency converter; One sensor groups comprises strain transducer, acceleration transducer and speed probe; Speed probe is contained on the motor of vibrator, and links to each other with programmable logic controller (PLC); Strain transducer is made up of foil gauge, dummy gauge and bridge box, and foil gauge and dummy gauge are attached on the bent axle; Acceleration transducer is adsorbed in the swing arm; Instrument is amplified in one strain, links to each other with strain transducer, acceleration transducer and programmable logic controller (PLC) respectively; One computing machine links to each other with programmable logic controller (PLC).
The utlity model has following technique effect: the utility model alleviated the manpower burden in a large number, made things convenient for the test operation of testing crew, reduced the artificial participation link of easy introducing operability error, and the higher complicated algorithm of degree of accuracy is used, improved the accuracy of crankshaft fatigue test significantly.
Description of drawings
Fig. 1 is a crankshaft bending fatigue test system architecture synoptic diagram of the present utility model;
Fig. 2 is the resonance stage body structural representation of system shown in Figure 1;
Fig. 3 is that driving torque scalable of the present utility model loads eccentric sectional view;
Fig. 4 is a test method process flow diagram of the present utility model;
Fig. 5 is test organization of the present utility model and data management database pattern schematic block diagram.
Embodiment
Describe the utility model below with reference to the accompanying drawings in detail.
Fig. 1～3 show the detailed structure of crankshaft bending fatigue pilot system of the present utility model.The load maintainer that the utility model has adopted easy to operate horizontally-arranged formula high speed resonance stage body and swing arm inertia and driving torque to regulate; The upper and lower computer of forming with computing machine with strong data management and calculation process ability and Programmable Logic Controller with long-time steady operation ability and power down protection capability has constituted the observing and controlling core of system.
As shown in Figure 1, the resonance stage body is formed in bent axle 1 and swing arm 11.Foil gauge 2 is attached on the fillet of bent axle 1, and dummy gauge 3 is attached on the bent axle 1, and foil gauge 2 all links to each other with bridge box 4 with dummy gauge 3, and they form strain transducer jointly.Strain is amplified instrument 5 and is linked to each other with bridge box 4.Acceleration transducer 12 is adsorbed in the swing arm 11, and links to each other with strain amplification instrument 5.Programmable logic controller (PLC) 7 amplifies instrument 5 with strain and links to each other.Vibrator 9 mainly is made up of eccentric wheel and motor, is connected on the master arm of swing arm 11.Speed probe 10 is contained on the motor of vibrator 9, and links to each other with programmable logic controller (PLC) 7.Frequency converter 8 links to each other with programmable logic controller (PLC) 7 with vibrator 9 respectively.Computing machine 6 links to each other with programmable logic controller (PLC) 7.
After the loading, foil gauge 2 and dummy gauge 3 produce strain signal in bridge box 4, acceleration transducer 12 produces vibration signal, and strain signal and vibration signal enter programmable logic controller (PLC) 7 after instrument 5 amplification conditionings are amplified in strain, carry out the A/D conversion, the digital signal that converts to is sent into computing machine.Speed probe 10 obtains the rotating speed of motor signal of vibrator 9, also sends into computing machine by programmable logic controller (PLC) 7.The signal that computing machine 6 transmits according to programmable logic controller (PLC) 7 shows each parameter of pilot system in real time, also can come flexible configuration pilot system parameter so that pilot system is applicable to various bent axle models and various testing requirements by computing machine 6 input parameters simultaneously.Programmable logic controller (PLC) 7 can carry out regulating and controlling to system in the controlled quentity controlled variable according to computing machine 6, finishes in demarcation simultaneously and also can independently control test run according to the feedback information of each sensor after entering the operation phase.Under the situation of unscheduled events such as computing machine 6 generation deadlocks, can control system continue operation like this, thereby the power down of programmable logic controller (PLC) 7 keeps function can guarantee also that system is reliable under power-off condition preserves current running status can make the state of system before the power down when starting once more, has guaranteed the accuracy of test figure.Programmable logic controller (PLC) 7 changes the control of the motor speed realization of vibrator 9 to the resonance stage body by driving frequency converter 8.
Fig. 2 shows the basic structure of resonance stage body, and mass 13 is embedded on the passive arm of swing arm 11, and adjustable positions can realize adjusting to stage body resonance inertia by the relative position of quality of regulation piece 13 on the passive arm of swing arm 11.
Fig. 3 shows the sectional view of vibrator 9.Vibrator 9 mainly is made up of eccentric wheel and motor, eccentric wheel 93 and outer eccentric wheel 94 in eccentric wheel comprises, interior eccentric wheel 93 links to each other with the rotation axis 91 of motor by flat key 92, outer eccentric wheel 94 is enclosed within outside the interior eccentric wheel 93, relative angle scalable between them, it is fixing by interior holding screw 95 and outer holding screw 96 to regulate the back.Relative angle by between eccentric wheel 93 in regulating and the outer eccentric wheel 94 can make whole eccentric eccentric throw change in certain scope, thereby driving torque is regulated.The vibrator that the inertia adjustable mechanism of this resonance stage body and driving torque scalable make can be good at adapting to the test to the different model bent axle, can flexibly sample be loaded with different stress levels according to the difference of testing program.
The foregoing description is used for the utility model of explaining; rather than the utility model limited; in the protection domain of spirit of the present utility model and claim, any modification and change to the utility model is made all fall into protection domain of the present utility model.
Claims (3)
1. crankshaft bending fatigue pilot system is characterized in that it comprises:
One resonance stage body is made up of bent axle and swing arm;
One vibrator mainly is made up of eccentric wheel and motor, links to each other with the master arm of swing arm;
One frequency converter links to each other with the motor of vibrator;
One programmable logic controller (PLC) links to each other with frequency converter;
One sensor groups comprises strain transducer, acceleration transducer and speed probe; Speed probe is contained on the motor of vibrator, and links to each other with programmable logic controller (PLC); Strain transducer is made up of foil gauge, dummy gauge and bridge box, and foil gauge and dummy gauge are attached on the bent axle; Acceleration transducer is adsorbed in the swing arm;
Instrument is amplified in one strain, links to each other with strain transducer, acceleration transducer and programmable logic controller (PLC) respectively;
One computing machine links to each other with programmable logic controller (PLC).
2. crankshaft bending fatigue pilot system according to claim 1 is characterized in that, described swing arm has the mass of a scalable swing arm inertia.
3. crankshaft bending fatigue pilot system according to claim 1, it is characterized in that, eccentric wheel and outer eccentric wheel in described eccentric wheel comprises, interior eccentric wheel links to each other with the rotation axis of motor by flat key, outer eccentric wheel is enclosed within outside the interior eccentric wheel, relative angle scalable between interior eccentric wheel and the outer eccentric wheel is regulated the back and is fixed by interior holding screw and outer holding screw.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200420082674 CN2729691Y (en) | 2004-09-06 | 2004-09-06 | Crankshaft bending fatigue experiment system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200420082674 CN2729691Y (en) | 2004-09-06 | 2004-09-06 | Crankshaft bending fatigue experiment system |
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| CN2729691Y true CN2729691Y (en) | 2005-09-28 |
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| CN 200420082674 Expired - Fee Related CN2729691Y (en) | 2004-09-06 | 2004-09-06 | Crankshaft bending fatigue experiment system |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100439896C (en) * | 2006-05-24 | 2008-12-03 | 浙江大学 | Method for investigating fatigue crack expansion |
| CN101196430B (en) * | 2006-12-05 | 2010-12-15 | 上海电气集团股份有限公司 | Electrical control system of crankshaft rotor-bearing system dynamics experimental bench |
| CN102156077A (en) * | 2011-05-06 | 2011-08-17 | 中国石油大学(华东) | Reciprocating bending corrosion fatigue testing machine |
| CN102288406A (en) * | 2011-07-08 | 2011-12-21 | 天润曲轴股份有限公司 | Clamping vibration exciting device for integral torsion fatigue test of crankshaft |
| CN102901560A (en) * | 2012-10-24 | 2013-01-30 | 天津亿利科能源科技发展股份有限公司 | Safe comprehensive monitoring system for structure of offshore jacket platform |
| CN103969042A (en) * | 2014-05-29 | 2014-08-06 | 长城汽车股份有限公司 | Crankshaft testing device |
| CN110389079A (en) * | 2019-08-16 | 2019-10-29 | 武汉钢铁有限公司 | A kind of sheet metal plain bending fatigue test method |
| CN112284660A (en) * | 2020-09-28 | 2021-01-29 | 浙江大学 | Bent torsion composite load test device of bent axle |
-
2004
- 2004-09-06 CN CN 200420082674 patent/CN2729691Y/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100439896C (en) * | 2006-05-24 | 2008-12-03 | 浙江大学 | Method for investigating fatigue crack expansion |
| CN101196430B (en) * | 2006-12-05 | 2010-12-15 | 上海电气集团股份有限公司 | Electrical control system of crankshaft rotor-bearing system dynamics experimental bench |
| CN102156077A (en) * | 2011-05-06 | 2011-08-17 | 中国石油大学(华东) | Reciprocating bending corrosion fatigue testing machine |
| CN102156077B (en) * | 2011-05-06 | 2016-05-11 | 中国石油大学(华东) | Reciprocating bending corrosion fatigue testing machine |
| CN102288406A (en) * | 2011-07-08 | 2011-12-21 | 天润曲轴股份有限公司 | Clamping vibration exciting device for integral torsion fatigue test of crankshaft |
| CN102901560A (en) * | 2012-10-24 | 2013-01-30 | 天津亿利科能源科技发展股份有限公司 | Safe comprehensive monitoring system for structure of offshore jacket platform |
| CN103969042A (en) * | 2014-05-29 | 2014-08-06 | 长城汽车股份有限公司 | Crankshaft testing device |
| CN103969042B (en) * | 2014-05-29 | 2016-08-03 | 长城汽车股份有限公司 | Bent axle assay device |
| CN110389079A (en) * | 2019-08-16 | 2019-10-29 | 武汉钢铁有限公司 | A kind of sheet metal plain bending fatigue test method |
| CN112284660A (en) * | 2020-09-28 | 2021-01-29 | 浙江大学 | Bent torsion composite load test device of bent axle |
| CN112284660B (en) * | 2020-09-28 | 2022-05-03 | 浙江大学 | Bent torsion composite load test device of bent axle |
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| CF01 | Termination of patent right due to non-payment of annual fee |