CN101750245B - Test method for contact stress of cam driving mechanism of diesel fuel system - Google Patents
Test method for contact stress of cam driving mechanism of diesel fuel system Download PDFInfo
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- CN101750245B CN101750245B CN2008100440294A CN200810044029A CN101750245B CN 101750245 B CN101750245 B CN 101750245B CN 2008100440294 A CN2008100440294 A CN 2008100440294A CN 200810044029 A CN200810044029 A CN 200810044029A CN 101750245 B CN101750245 B CN 101750245B
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Abstract
The invention discloses a test method for contact stress of a cam driving mechanism of a diesel fuel system, which tests the contact stress of a cam and a push rod in the cam driving mechanism of a diesel fuel system in the mode combining dynamic and static tests. The method comprises the steps of: measuring dynamic stress values of the push rod in the operating state, and then calculating the action force that the push rod bears; converting the axial action force that the push rod bears into the contact force between the cam and a roller according to the included angle between the cam contact force and the axial action force of the push rod when the cam is under the action of the maximum contact force; finally, loading on a tester in accordance with rated loads, measuring the area of the contact part between the cam and the roller, and calculating the average contact force. The invention can accurately measure the contact force, evaluate strength of the cam driving mechanism, direct the structural design of the cam and the push rod, and can simultaneously distinguish results of simulation analysis to direct simulation analysis.
Description
Technical field
The present invention relates to a kind of method of testing of cam driving mechanism of diesel fuel system, particularly relate to the method for testing of a kind of cam driving mechanism of diesel fuel system cam and tappet contact stress.
Background technology
The cam drive mechanism of diesel fuel system is the power source of mechanical type fuel system, each kinematic pair of the driver part of described cam drive mechanism is under high frequency, heavily stressed, the impact load condition of work, the reliability of its contact stress affects oil supply system.Contact stress is excessive, and the driver part life-span of cam drive mechanism is reduced, and occurs mechanical faults such as overheated, plucking easily.
The most direct acquisition methods of contact stress of described cam drive mechanism cam and tappet is exactly the means acquisition by test.The performance test result can differentiate simulation analysis result's rationality, instructs the simulation analysis flow process, can carry out the strength assessment and the reliability assessment of described cam drive mechanism driver part simultaneously, instructs the structural design and the cam profile design of driver part.
Present stage, for still difficulty relatively of the test of high-power diesel engine cam and tappet contact stress, bibliographical information also is comparatively rare.Conventional measuring technology all is to adopt in small-sized agricultural machinery.General ridge method or the half-bridge connection used carried out static test, but not to the self character radial measurement of material, is the force-bearing situation of rough simulation member, and test result also only for contact internal force, can not reflect the variation that contact stress is trickle completely.
Summary of the invention
The technical problem to be solved in the present invention provides a kind of method of testing of contact stress of cam driving mechanism of diesel fuel system, can accurately record contact stress, cam drive mechanism is carried out strength assessment, instruct the structural design of cam and tappet, also can differentiate simultaneously the result of simulation analysis, instruct simulation analysis.
For solving the problems of the technologies described above, the method of testing of contact stress of cam driving mechanism of diesel fuel system of the present invention, the mode that adopts dynamic test and static test to combine is tested the contact stress of cam driving mechanism of diesel fuel system cam and tappet; Comprise the steps:
Step 3, carry out static test, as demarcating load, adopt the cylinder with described cam same curvature radius to substitute cam, the tinfoil paper of between described cylinder and roller, packing into the contact force of described conversion; Universal testing machine loads according to the load of demarcating, and acts between roller and the cylinder, makes tinfoil paper note the impression that contacts between roller and the cylinder; Calculate the average contact stress of cam and tappet according to the area of contact impression.
The method of testing of the application of the invention, can obtain the contact stress of cam driving mechanism of diesel fuel system cam and tappet accurately, can instruct the design of cam driving mechanism of diesel fuel system and the design of cam profile, improve and optimize the computing method of described contact stress of cam driving mechanism, and then shorten the design cycle, reduce experiment fees.Also can carry out strength assessment, differentiate the result of simulation analysis, instruct simulation analysis described cam drive mechanism.
Description of drawings
The present invention is further detailed explanation below in conjunction with accompanying drawing and embodiment:
Fig. 1 is a tappet paster synoptic diagram;
Fig. 2 is the strain variation rule;
Fig. 3 is the local figure (4～6s) of strain variation;
Fig. 4 is the strain variation rule of measuring point 4～6;
Fig. 5 is the minimum principal strain Changing Pattern of strain rosette (being measuring point 4～6);
The maximum principal strain Changing Pattern of strain rosette during Fig. 6 (measuring point 4～6);
Fig. 7 is the elastic modulus stress-strain curve;
Fig. 8 is the many-body dynamics computation model;
Fig. 9 be tappet axially and the variable angle synoptic diagram of vertical direction;
Figure 10 is a method test process synoptic diagram of the present invention.
Embodiment
Valve actuating mechanism is a work system of being responsible for the internal combustion engine scavenging period, realizes that air-intake of combustion engine process and exhaust process regularly, directly affect the internal combustion engine coefficient of charge, is one of important mechanism of decision in-cylinder combustion performance.Extensively adopt the low formula camshaft air valve formula valve actuating mechanism of putting for quartastroke engine.
Low put formula camshaft air valve formula valve actuating mechanism and mainly form: air valve group (air valve, air valve guide pin bushing, spring for valve, rotary valve mechanism etc.), camshaft (axle, cam, fastener, transmission gear etc.) and driving mechanism (tappet or rocking bar, push rod, rocking arm, rocker arm bracket, valve bridge etc.) by three parts.Camshaft generally is arranged in crankcase or place, cylinder block below, and the air valve group is arranged in top cylinder and covers, and the centre passes to air valve to certain characteristics of motion that cam profile embodies by driving mechanism.
The method of testing of contact stress of cam driving mechanism of diesel fuel system of the present invention, the mode that adopts dynamic test and static test to combine, contact stress to cam driving mechanism of diesel fuel system cam and tappet is tested, and makes test result more rationally reliable.
Dynamic test is under the diesel engine actual working state, the strain that records tappet according to different operating modes, and as demarcating load, be applied in the static indentations test, act between roller and the cam (or alternative cylinder).
During static test, because the off-centre of cam is very easily rolled during loading, therefore line of action of force must adopt the method that replaces cam with the radius-of-curvature cylinder by the axle center of cam rotation axle when loading simultaneously, improves measuring accuracy and accuracy.
The result of static test is a contact force, need survey contact area as obtaining stress, converts stress then to.Contact area adopts indentation method, uses soft tinfoil paper record contact impression.
The contact stress of measuring among the present invention between cam and the tappet adopts the method for measuring indirectly.Referring to shown in Figure 10, at first the dynamic strain value of tappet under the surveying work state calculates the suffered amount of force of tappet then; Be subjected to maximum contact force to do the time spent according to cam, the angle between cam contact force and tappet axial force, the axial force that tappet is subjected to is converted into the contact force between cam and the roller; On testing machine, load at last, measure the contact region area between cam and the roller, calculate its average contact stress by demarcating load.
The dynamic test test
In the tappet design, tappet only bears the axial force of two ends, is not subjected to bend or turned round and have, so tappet can be considered as two power bars, principle is carried out experimental test according to this, directly records the tappet strain, thereby it is stressed to obtain tappet.
In test, the maximum speed of diesel engine is respectively 1455r/min (r/min represents the rotating speed of per minute) and 1500r/min, therefore in twice test, can be scaled 8730 °/s and 9000 °/s (being the angle that diesel engine turns at per second), sample frequency is 6400Hz, and promptly per second is gathered 6400 secondary data.Be equivalent to when testing maximum speed for the first time, the diesel engine revolution is crossed 1.3640625 °, the data on foil gauge of dynamic strain tester record, in like manner, in test for the second time, the diesel engine revolution is crossed 1.40625 °, the data on foil gauge of dynamic strain tester record.
Fig. 1 represents the layout orientation and the angle of foil gauge on the tappet.Foil gauge is arranged on the interlude of tappet, arranges three foil gauges on the tappet altogether, and a strain rosette of being made up of three foil gauges.Wherein three foil gauge 1-3 axially are provided with, and the both sides that are positioned at tappet respectively are provided with a slice foil gauge 1,3, and the centre position is provided with a slice foil gauge 2.Described strain rosette is an arrow-shaped, foil gauge 5 of position is positioned at the upper end (end of forming other two foil gauges 4,6 of strain rosette aligns with the lower end of intermediate 5, and the other end is the two ends that are symmetricly set on intermediate 5 of angle) of the foil gauge 2 in described tappet centre position in the middle of it.Arrange behind foil gauge and put up a bridge that will go between to derive is connected with the dynamic strain tester.
Because in the true process of the test, tappet working position and actual measurement location are far away, need long lead, this can cause that resistance value is bigger than normal; Therefore in the dynamic strain tester, this section resistance is calculated and deducts conductor resistance influence, warranty test precision.
Data on the foil gauge that test is noted to dynamic test are mainly analyzed: at first, remove initial value affecting (so-called initial value is exactly that foil gauge is in the existing data of test part) according to the following steps; Secondly, the data of each foil gauge are handled (conclusion, numerical value arrangement); At last, the data of handling well are drawn.
The operating condition of test table is as shown in table 1:
Because tappet is in real work, except bearing axial force, also can there be the situation of being bent, therefore,,, and obtain the peak value of mean value to the numerical value averaged of four foil gauges in axial direction for eliminating the influence of moment of flexure.
Shown in Fig. 2,3, from the test data of foil gauge 1～3, can obtain the strain variation overall trend of 3 position measurement points, the strain peak value of three test points is all between 1400～1500, but maximal value is slightly different, only be subjected to axial load though it can be said that bright tappet in theory, but in real work, also born moment of flexure, but the influence that moment of flexure produces axial strain is much smaller than the influence of axial load.
From Fig. 2,3, can obtain the strain variation overall trend of 1 foil gauge test point position on the tappet, wherein the measured peak value of foil gauge 2,5 vertically is greater than two other axial peak value of foil gauge 1,3 separately, illustrate that loading direction that tappet mainly bears is for axial.And by calculating the numerical value of maximum strain value and minimum strain value on this position of tappet.
In Fig. 4-6, maximum principal strain value and the minimum principal strain value of strain rosette have been provided, tappet is compression member in practical work process, therefore the absolute value of the minimum principal strain value of tappet is greater than the absolute value of maximum principal strain value, in analytic process, also be to adopt the strain value of pressurized direction to compare.
4 strain values along the foil gauge 1,2,3,5 of tappet axial direction are averaged, utilize mean value to reduce the influence of moment of flexure the tappet axial strain.Utilize program, try to achieve maximum average microstrain value (strain magnitude: * 10 on the tappet
-6), be 1437.71.
Table 2, experimental test are put each operating mode maximum strain value (strain magnitude: * 10
-6)
Can find that by comparing the strain value Changing Pattern of each test point is consistent, and illustrate that the strain value peak value of each measuring point appears at synchronization.By the data of last table, can be relatively under each operating mode, vertically the maximum strain value situation of change of four test points on the tappet.
By comparing the distribution trend and the maximal value of axial strain sheet, can find: the strain maximal value of the test position of described in front four foil gauges of tappet is slightly different, in operating mode seven, it is 86.6 (strain magnitudes: * 10 that foil gauge 1 differs with foil gauge 2 maximal values
-6), this explanation tappet is during operation except that bearing axial load, also bear the influence of other load and test error, but compare with axial load, bending load is to less (the maximal phase difference/mean strain maximal value * 100%=6.023%), therefore suppose that tappet is that two power bars tally with the actual situation of the influence of tappet.
In practical work process, tappet bears moment of flexure and moment of torsion, the measurement result of foregoing four foil gauges has comprised the influence of this part, so in processing to the test result of four axial strain sheets, the strain value of four measuring points done and ask average, thereby eliminate the influence of moment of flexure and moment of torsion.
In operating mode seven, the power of diesel engine and load are maximum, so the power that tappet bears under this operating mode also is maximum, also show by the dynamic test test result, under this operating mode, strain value maximum on the tappet, so take out foil gauge 1,2,3,5 strain values in operating mode seven, with strain value summation and be averaged, obtain the maximal value of mean value, be 1437.71 (strain magnitudes: * 10
-6).
By stress-strain relation:
(, obtain E=2.06 * 10 of tappet by experimental measurement
11Pa) (ε is strain in the formula, σ is a stress, E is the elastic modulus of tappet material) the maximum mean stress in cross section that can calculate tappet is 296.16826MPa, the diameter of tappet stage casing cylinder is 14.50mm, can obtain the maximum axial force that tappet is subjected to by conversion to be:
F
max＝48906.254N
The contact force that the maximum axial force that this tappet is subjected to is scaled on the surface of contact of cam and roller is 48200N, and this result and the 49451.7N as a result that obtains by FEM (finite element) calculation comparatively meet.
Table 3, the test of standard component extension test
| Test specimen 17 | Test specimen 18 | Test specimen 19 | Mean value | |
| Yield strength (MPa) | 374 | 376 | 369 | 373 |
The tappet material is GCr45, according to the result of last table standard component tension test, can find, the dynamic test mean stress of tappet does not surpass yield strength all the time, and promptly tappet is an elastic deformation in the dynamic test process always, and does not reach the destruction level.
Therefore, in the static load rating test, the microstrain value of testing required demarcation for the first time is 1437.7 (strain magnitudes: * 10
-6).With the demarcation load that obtains, be applied in the static indentations test, be about to the contact force on the surface of contact that demarcation load that tappet is subjected to is scaled roller and cam (or alternative cylinder).
The static test test
Static Contact stress test test between cam and the roller is divided into four parts:
1, measures the elastic modulus of tappet material
The measurement of the elastic modulus of tappet material is carried out on universal testing machine, 3 of code test parts.Standard component adopts bar, and size is according to national regulation " GB/T 228-2002 ".
Adopt 3 test specimen experiments, springform is measured the mean value of 3 test specimens.
Typical power-the deformation curve of tappet material as shown in Figure 7.The loaded load of materialsing respectively peaked 10%, 40% calculating reference point as the calculating elastic modulus.
Test specimen elasticity modulus test test value is as shown in table 4:
By calculating as can be known, get different calculating reference points, the elastic modulus that calculates is slightly different, but deviation is less, can not consider.According to engineering experience, get the conduct of 10% and 40% maximum load point with reference to point.The diameter of three test specimens and elastic modulus experiment value see the above table.
The elastic modulus mean value of experimental test is 206GPa, and with engineering numerical value 210GPa commonly used, deviation is less, and visible experiment measuring value is correct, and in subsequent calculations, the elastic modulus of tappet material is taken as 206GPa.
2, the demarcation of dynamic strain value and static strain value
Tappet is loaded, and the foil gauge on the tappet adopts lead to be connected on the statical strain indicator, measures its strain value.Measure tappet respectively at 5KN, 10KN, 15KN, 20KN, the strain value under the loading of 25KN.
Desirable axial compression tappet, four measuring point directions are that axial axial strain value equates.But the axial strain value of four the foil gauge test points of 3-6 in the experimental test is inequality.This mainly is because during the universal testing machine on-load pressure, is to move down by crossbeam, and then the crossbeam lower surface contacts with the tappet upper surface, continues then to move down, and begins to push tappet, makes the tappet pressurized.The face that universal testing machine crossbeam lower surface joint contacts with tappet is not a plane, but a sphere.Cause tappet that axial compression can not only be arranged, but pressurized and be subjected to curved to exist simultaneously make the strain value of four measuring points inequality thus.Simultaneously, can not accomplish the dead in line that tappet axis and universal testing machine load in the actual tests fully, also be to cause four different reasons of measuring point strain value.
Test figure writes down successively is that tappet turns over the strain value under the situation of different angles around axis.Because the influence of pressing, bending, under the same load, it is less that the strain value of same test point partly differs, and part differs bigger than normal.But in same loading condition, the variation of same test point strain value and load is linear.
In order to reduce the influence of moment of flexure, four in the same operating mode axial test point strain values are got its mean value.Contrast three operating modes, can find, the mean value error of axial strain value is less.
Get the mean value of three test axial strain mean values, to eliminate the influence that each test error is brought.Three test axial strain mean value (strain magnitudes: * 10
-6) as shown in table 5.
Table 5
When the static strain value reaches dynamic strain value maximal value 1437.7 * 10
-6The time, static load should be 47.63KN.This load differs very little with the load that directly calculates by the dynamics strain, can think equal.Consider that the envelope test and the dynamic test time interval are longer, and finish factors such as foil gauge may be affected after the dynamic test.In the subsequent calculations, still the strain value by dynamic measurement calculates, and the error that causes thus is very little.
3, the angle between measurement tappet acting force and cam, roller contact force, the acting force that tappet is suffered is scaled the cam contact force.
According to many-body dynamics model (referring to shown in Figure 8), when roller and cam contact force maximum, the angle that calculates contact force and vertical direction according to the contact component of force is θ
1=10.6941 °.And the variable angle curve of tappet and vertical direction as shown in Figure 9.
Because cam-plunger is in uphill process, there is a sudden change in oil pressure, causes the angle of tappet and vertical direction, and cam and roller contact force component all have a sudden change.Further, ram lift oil pressure curve is also rough, causes that tappet change curve axial and the vertical direction angle is not so good as the line smoothing of decline stage in the lift stage.
When contact force is maximum, t=0.0093s, (t express time in the formula, s are chronomere's " second ") tappet angle axial and vertical direction as can be known is θ
2=0.9446 °.When contact force was maximum, the angle between cam contact surface normal direction and tappet was:
θ＝θ
1-θ
2＝9.7495°
By calculating as can be known, it is identical that the peak value that tappet is stressed and the peak value of cam, roller contact force go out now.Can calculate the peak value of this moment cam and roller contact force according to the stressed peak value of tappet.
According to result of calculation, consider that simultaneously the load gap is bigger in the experiment, the impression gap is also more obvious, gets the contact numerical value that peak value of contact forces differs bigger four operating modes and experimentizes, and is respectively 1,2,5,7 operating modes.In the static indentations experiment, contact force is respectively 23.85KN, 33.79N, 40.47KN, the load condition of 48.20KN is tested.
Under each operating mode, the peak value of tappet acting force and cam contact force is as shown in table 6:
4, adopt the feasibility checking that replaces cam with the curvature cylinder
Impression between employing universal testing machine test cam and the roller very easily rolls during static the loading, so design of Clamping Apparatus has been proposed very high requirement owing to the off-centre of cam.Simultaneously, line of action of force must this requirement of excess convexity wheel shaft axle center not only requires very highly during loading to anchor clamps, and the centering of cam initial position has also been proposed high-precision requirement.In order to overcome this difficulty, possible scheme has been carried out feasibility study.
Can determine by calculating, comparison several schemes, it is feasible that employing replaces the method for cam with the radius-of-curvature cylinder, and calculating shows, under the situation that guarantees osculating element consistent size (about 0.314mm), by extracting the cam radius-of-curvature, with the cam equivalence is right cylinder, for the influence of contact stress size very little (cam 315.3MPa, right cylinder 315.7MPa, difference 0.4MPa), and the size of contact area is also constant substantially, and the result is very approaching, is feasible.The contact stress of experiment test is in the present invention adopted with the curvature cylinder and is replaced cam.
The cam indentation test is carried out on universal testing machine.Right cylinder to four different radiis has carried out the impression experiment altogether.The experiment test specimen comprises the cylinder of four different radiis, v block, roller and a fixed mechanism thereof.
Measure impression and can adopt tinfoil paper, paper and material such as spray paint.By comparison to three kinds of experiment materials, can find that it is more satisfactory for interplanar contact effect to spray paint, should adopt, but measure inapplicable for the contact region between between curved surface and plane and curved surface; The impression of paper material is owing to need just seeing more clearlyly to light, although the border is more clearly, because bad processing also should not be adopted; For soft tinfoil paper, the ductility of metal is very good, and the soft and thin tinfoil paper rigidity of opposing extruding almost, is easy to note impression, and is also very little to the stiffness effect between the contact; For the contact between curved surface, record effect is very good, and is suitable equally for contacting between plane and curved surface.For interplanar contact, adopt tinfoil paper just the flatness on its plane to be proposed very high requirement, otherwise border clearly can not be provided, effect is not as spraying paint.
At above a series of exploitative experiments,, adopt soft and thin tinfoil paper record contact impression at the type that contacts between this roller and cylinder two curved surfaces.
After test equipment installed, adopt the mode of displacement control load to load.Measured the contact region of described two curved surfaces under four different loads respectively, according to aforementioned result, load is respectively: 23.8509KN, 33.78846KN, 40.46768KN, 48.19987KN.In actual experiment, load just can not be controlled at above-mentioned numerical value, have certain deviation.Simultaneously, adopt the displacement control load, after displacement was fixing, load may be drifted about to some extent, but amplitude is very little, can ignore.
Table 7 has provided in the actual loaded, the maximal value that each operating mode was loaded into.
| The cylinder sequence number | Diameter (mm) | Operating mode 1 (KN) | Operating mode 2 (KN) | Operating mode 3 (KN) | Operating mode 4 (KN) |
| 1 | 106.1 | 23.535 | 34.375 | 41.096 | 49.321 |
| 2 | 106.8 | 24.362 | 34.221 | 40.709 | 48.540 |
| 3 | 108.7 | 23.804 | 34.029 | 41.027 | 49.331 |
| 4 | 107.3 | 24.024 | 34.126 | 41.428 | 48.850 |
Measure the width in three places of impression respectively, get the width of its mean value, multiply each other with bearing length (28mm) then, obtain the contact region area as impression.Divided by Method for Area, calculate the mean stress of contact region according to power.From measured data as can be seen, along with the increase of load, the width of contact area increases gradually, but load increases multiple and width increases the disproportionate relation of multiple, exists nonlinear relationship.
By above-mentioned experiment test as can be known, the radius of No. three cylinders (referring to table 7) is 54.35mm, and is in numerical evaluation, identical in the curvature of the position of cam contact force maximum.Under the maximum load operating mode, calculated value and trial value that cam contacts average contact stress compare.
Record by test, under the maximum load operating mode (operating mode four, load setting value 48.19987KN), the contact region mean breadth 1.81221mm of No. 3 cylinders, contact area is 50.74188mm
2
Adopt the computation model of fixed constraint at cam middle part, mean stress is 743.5MPa, with experimental test mean stress error be 23.5%.
The computation model that the mode that adopts the simulation V shape iron to retrain retrains the cam two positions, mean stress is 991.952.MPa.With experiment test mean stress error be 2.03%.
Because the way of restraint counter stress distributes and value effect is bigger, calculate and experiment checking mutually in order to make, increase computation's reliability on the one hand, set up analytical standard, therefore select suitable boundary condition to seem very important.
Claims (4)
1. the method for testing of a contact stress of cam driving mechanism of diesel fuel system is characterized in that: the mode that adopts dynamic test and static test to combine, the contact stress of cam driving mechanism of diesel fuel system cam and tappet is tested; Comprise the steps:
Step 1, the dynamic test of carrying out are measured the dynamic strain value of tappet under the diesel engine actual working state, the amount of force that calculates tappet then and born;
Step 2, be subjected to maximum contact force to do the time spent according to cam, the angle between cam contact force and the tappet axial force is converted into contact force between cam and the roller with the tappet axial force;
Step 3, carry out static test, as demarcating load, adopt the cylinder with described cam same curvature radius to substitute cam, the tinfoil paper of between described cylinder and roller, packing into the contact force of described conversion; Universal testing machine loads according to demarcating load, acts between roller and the cylinder, makes tinfoil paper note the impression that contacts between roller and the cylinder; Calculate the average contact stress of cam and tappet according to the area of contact impression.
2. method of testing as claimed in claim 1, it is characterized in that: the area of contact impression calculates as follows, measure the width of at least three positions of contact impression respectively, get the width of its mean value as the contact impression, this width is multiplied each other with the length that contacts impression, obtain contacting the area of impression.
3. method of testing as claimed in claim 1 is characterized in that: during the dynamic strain value of test tappet, at the tappet interlude, what be positioned at its both sides and centre position axially respectively is provided with a slice foil gauge; At the tappet interlude, a strain rosette of being made up of three foil gauges also is set, this strain rosette is an arrow-shaped, foil gauge of position is positioned at the upper end of the foil gauge in described tappet centre position in the middle of it, an end of other two foil gauges aligns with the lower end of the foil gauge in strain rosette centre position in the strain rosette, the angled two ends that are symmetricly set on the foil gauge in strain rosette centre position of the other end.
4. method of testing as claimed in claim 3 is characterized in that: adopt the data on the dynamic strain tester record foil gauge; The data of gathering are handled as follows, removed initial value affecting; Data to each foil gauge are handled, and to the data averaged of four foil gauges that in axial direction are provided with, and obtain the peak value of mean value; The data of handling well are drawn.
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| CN102680241B (en) * | 2011-03-18 | 2015-09-30 | 中国船舶重工集团公司第七一一研究所 | Marine diesel valve actuating mechanism performance test signal collection device |
| CN103868633B (en) * | 2014-03-17 | 2016-01-27 | 中国北方发动机研究所(天津) | Engine overhead air distribution camshaft contact stress method of testing |
| CN106770659B (en) * | 2016-12-28 | 2019-05-10 | 南京林业大学 | Synchronous dynamic measures modulus of elasticity of wood, the method for modulus of shearing and Poisson's ratio |
| CN106599525B (en) * | 2017-01-12 | 2019-07-26 | 山东理工大学 | The simulation calculation method of the offset frequencys type three-level progressive rate plate spring suspension brackets offset frequency characteristic such as non- |
| CN108267253A (en) * | 2018-01-23 | 2018-07-10 | 安徽华菱汽车有限公司 | The test method of contact stress between engine rocker roller and camshaft |
| CN108458821B (en) * | 2018-03-19 | 2020-07-17 | 中车青岛四方机车车辆股份有限公司 | Wheel seat axial stress measuring method and calibrating device |
| CN111425302A (en) * | 2020-04-01 | 2020-07-17 | 广西玉柴机器股份有限公司 | Early warning method for avoiding tile burning |
Citations (1)
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Patent Citations (1)
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