CN104006967A - Connecting rod fatigue testing device - Google Patents
Connecting rod fatigue testing device Download PDFInfo
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- CN104006967A CN104006967A CN201410235164.2A CN201410235164A CN104006967A CN 104006967 A CN104006967 A CN 104006967A CN 201410235164 A CN201410235164 A CN 201410235164A CN 104006967 A CN104006967 A CN 104006967A
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Abstract
The invention discloses a connecting rod fatigue testing device. The connecting rod fatigue testing device comprises a base, a connecting rod and a loading device. One end of the connecting rod is fixed to the base, the other end of the connecting rod is loaded by the loading device, and the loading device repeatedly exerts continuously-changing pressure and tension on the connecting rod. The tension load and the pressure load change continuously from zero to the amplitude value, and the tension and the pressure are converted automatically instead of being exerted or removed forcefully, namely, the stress process of the connecting rod is continuous. Due to the fact that the connecting rod does not bear suddenly-changing loads, the problem of excessive shock is avoided, the phenomenon that a testing result is abnormal cannot occur and the accuracy and the reliability of the testing result are improved.
Description
Technical field
The present invention relates to technical field of engines, particularly a kind of connecting rod fatigue experimental device.
Background technology
Connecting rod is the important component in engine, and it has small end of connecting rod, big end and is connected to the gonnecting rod body between the two, and wherein, small end of connecting rod is used for installing piston pin, is connected with piston; Big end is used for connecting crank pin, and then is connected with bent axle.
In the course of the work, connecting rod is subject to from the pressure of gas gas in the jar and reciprocal inertial force engine all the time, and transmits interaction force between piston and bent axle, such as, change the linear reciprocating motion of piston into bent axle rotatablely move.In arbitrary moment in four strokes of engine, the stressed of connecting rod is all inhomogeneous, and connecting rod all bears the effect of the alternate loads such as stretching, compression, bending, working environment complexity.Therefore, in modern production process, need to carry out torture test to connecting rod, connecting rod be applied to certain alternation constant amplitude load, until destroy, observe it and destroy position and cycle life.
The most modes that adopt hydraulic loaded of typical connecting rod fatigue experimental device, one end and the pedestal of connecting rod test specimen are fixed, the other end is connected with bidirectional hydraulic oil cylinder, hydraulic oil is transported to bidirectional hydraulic oil cylinder by oil pipe, not only can, by the pressure-loaded of hydraulic oil to connecting rod test specimen, can also simulate by the bi-directional expansion of piston in hydraulic jack the situation of connecting rod under tension.But this test method has following shortcoming:
The first, loading procedure often can produce excess impact and cause test findings abnormal, and the reliability of test findings is low;
The second, be subject to the odjective cause such as the version restriction of oil cylinder, test loading frequency cannot improve, and test efficiency is lower;
The 3rd, hydraulic loaded often produces huge noise, harmful to staff's health;
The 4th, hydraulic oil is easily revealed, and not only easily pollutes workplace, also may cause hidden fire-fighting danger, jeopardizes safety.
Therefore, how to provide a kind of test unit, can simulate real engine the force-bearing situation of connecting rod when work, to obtain higher test reliability, be those skilled in the art's technical issues that need to address.
Summary of the invention
Object of the present invention is for providing a kind of connecting rod fatigue experimental device.This test unit can simulate real engine the force-bearing situation of connecting rod when work, to obtain higher test reliability.
For solving the problems of the technologies described above, the invention provides a kind of connecting rod fatigue experimental device, comprise pedestal, connecting rod and charger, described pedestal is fixed in one end of described connecting rod, the other end is loaded by described charger, and described charger applies continually varying pressure and pulling force repeatedly to described connecting rod.
Drag load and pressure load all change continuously from zero to amplitude, and, the conversion of pulling force and pressure all forms automatically, and optionally apply or remove, the loading process that is connecting rod is continuous, does not bear sudden change load, does not have the problem of excess impact, can there is not the phenomenon that test findings is abnormal, improve accuracy and the reliability of test findings.
Preferably, described charger comprise eccentric wheel, with the wheel shaft of described eccentric wheel adaptation, and the swing part that is connected in described wheel shaft, swings around described wheel shaft; Described wheel shaft is perpendicular to described connecting rod axis arranged, and described swing part applies described pulling force and described pressure to described connecting rod.
Preferably, described swing part comprises eccentric swing frame described in overcoat, and described swing frame forms accommodating described eccentric chamber.
Preferably, also comprise and be fixed on described pedestal, the swinging mounting axle vertical, parallel with described wheel shaft with described connecting rod axis; Described swing frame is connected with described swinging mounting axle, and can swing around described swinging mounting axle.
Preferably, described connecting rod is between described swinging mounting axle and described wheel shaft.
Preferably, also comprise the second bearing, described swinging mounting axle is connected with described swing frame by described the second bearing.
Preferably, described swing frame is provided with some fixed positions that are connected with wheel shaft, to regulate the distance of described wheel shaft and described swinging mounting axle.
Preferably, also comprise along described swinging mounting axle and take turns to described the slideway that direction of principal axis is installed, and with the lockable mechanism of described slideway adaptation, described lockable mechanism is connected with described wheel shaft.
Preferably, also comprise with described pedestal fix, with the guide rail that described pitman shaft line parallel is installed, described swing part is installed on described guide rail, and can slide along described guide rail.
Preferably, also comprise and pressure-adjusting spring that described pitman shaft line parallel arranges, the two ends of described pressure-adjusting spring are resisted against respectively described pedestal and described swing part, and lay respectively at the both sides of described swing part along described connecting rod axis and described connecting rod.
Preferably, also comprise link supporting plate, one end of described connecting rod is fixed by described link supporting plate and described pedestal; Described pedestal is provided with some installation sites along described connecting rod axis, to fix described link supporting plate.
Preferably, also comprise force cell, described force cell measures described eccentric wheel and acts on the size of the power of described swing part.
Brief description of the drawings
Fig. 1 is the structural representation of a kind of embodiment of connecting rod fatigue experimental device provided by the invention;
Fig. 2 is the side view of Fig. 1;
Fig. 3 is the stressed sketch of connecting rod in Fig. 1, wheel shaft, swinging mounting axle, illustrates that connecting rod, between wheel shaft and swinging mounting axle, bears pressure load;
Fig. 4 is the stressed sketch of connecting rod in Fig. 1, wheel shaft, swinging mounting axle, illustrates that connecting rod is between wheel shaft and swinging mounting axle, bearing tension load.
Fig. 1-Fig. 4:
Pedestal 100, connecting rod 200, big end end 201, small end of connecting rod end 202, gonnecting rod body 203, eccentric wheel 300, wheel shaft 301, clutch shaft bearing 302, swing frame 400, swinging mounting axle 500, the second bearing 502, axle bed 600, shaft-cup 601, pressure-adjusting spring 700, pressure-adjusting screw 701, link supporting plate 800, first connecting rod fixed block 801, second connecting rod fixed block 802, force cell 900
Embodiment
In order to make those skilled in the art understand better technical scheme of the present invention, below in conjunction with the drawings and specific embodiments, the present invention is described in further detail.
Please refer to Fig. 1 and Fig. 2, Fig. 1 is the structural representation of a kind of embodiment of connecting rod fatigue experimental device provided by the invention; Fig. 2 is the side view of Fig. 1.
This connecting rod fatigue experimental device comprises pedestal 100, connecting rod 200 and the charger that connecting rod 200 is loaded, and one end of connecting rod 200 and pedestal 100 are fixing, and the other end bears the load from described charger.
In fact, in the time of engine operation, connecting rod 200 is not only subject to the pressure-acting from piston, also be subject to reciprocal inertia force and swing inertial force effect, although this inertial force and pressure Comparatively speaking numerical value are less, but for improving the reliability of test, the load that the charger of this test unit applies connecting rod 200 comprises drag load and pressure load.
The load amplitude that the amplitude of above-mentioned load imposes on connecting rod 200 while comparing with engine operation is than consistent, and drag load and pressure load are from zero change procedure to amplitude, and the two process changing mutually, are all designed to continuous variation.
The fixing one end of connecting rod 200 and pedestal 100 is equivalent to the stiff end of connecting rod 200, and the other end is applied to above-mentioned two kinds of load repeatedly, i.e. this connecting rod 200 effect of under tension and pressure repeatedly, under its effect in alternate load all the time, until fatigure failure.The process of imposed load is as follows:
Charger is to connecting rod 200 load of exerting pressure, its numerical value is from being zero to be increased to gradually setting amplitude, then be reduced to gradually zero from setting amplitude, now, this pressure load is automatically converted to drag load, the numerical value of drag load is increased to setting amplitude gradually from zero, is then reduced to gradually zero from setting amplitude.
Said process is one-period, repeatedly once, will produce several times circulation, to simulate the process of bearing fatigue load when connecting rod 200 is worked in process of the test.
This connecting rod fatigue experimental device has following advantage:
Drag load and pressure load all change continuously from zero to amplitude, and, the conversion of pulling force and pressure all forms automatically, and optionally apply or remove, the loading process that is connecting rod 200 is continuous, does not bear sudden change load, does not have the problem of excess impact, can there is not the phenomenon that test findings is abnormal, improve accuracy and the reliability of test findings.
Further, above-mentioned charger can comprise eccentric wheel 300 and the wheel shaft 301 that drives this eccentric wheel 300 to rotate, this wheel shaft 301 is arranged vertically with the axis of connecting rod 200, between wheel shaft 301 and connecting rod 200, be also connected with the swing part loading to described connecting rod 200, this swing part is connected with wheel shaft 301 by clutch shaft bearing 302, when wheel shaft 301 freely rotates, by centrifugal action in swing part.
Wheel shaft 301 during with constant rotational speed, will be with movable eccentric wheel 300 synchronously to rotate around wheel shaft 301, and meanwhile, the reacting force that eccentric wheel 300 produces wheel shaft 301 will act on this swing part.Because the radius of gyration of eccentric wheel 300 is not definite value, it is in the time that wheel shaft 301 rotates, centrifugal force will drive swing part to produce small elastic deformation, this elastic deformation is equivalent to swing part and does slight past renaturation motion, the swing part connecting with wheel shaft 301 will be synchronizeed swing (small elastic deformation) with the rotation of eccentric wheel 300, above-mentioned centrifugal force is passed to connecting rod 200, thereby realizes the loading to connecting rod 200.
It should be noted that, swing as herein described is the microdeformation that swing part produces under the effect of centrifugal force, but not visual displacement.
Because the rotation process of eccentric wheel 300 is stable and continuous, therefore, the drag load transmitting to connecting rod 200 and pressure load are also continually varyings.The concrete load mode of above-mentioned continually varying pulling force and pressure is as follows:
In same eccentric wheel 300, the radius of gyration changes continuously from maximal value to minimum value, therefore, when the maximum rotating radius of eccentric wheel 300 moves to its process parallel with the axis of connecting rod 200 towards connecting rod 200 from beginning, it is exerted pressure to connecting rod 200, force value is increased to amplitude from zero, is decreased to zero again from amplitude; Afterwards, maximum rotating radius starts to deviate from connecting rod 200 and moves, and to its process parallel with the axis of connecting rod 200, it applies pulling force to connecting rod 200, and value of thrust is increased to amplitude from zero, is decreased to zero again from amplitude.
Said process is a loading cycle, in the time that pulling force is decreased to zero, prepares to exert pressure to connecting rod 200 in next cycle.
Visible, this scheme does not adopt cylinder structure, therefore, does not have the impact of the odjective causes such as cylinder structure on loading frequency, can need to set loading frequency according to test, improves the accuracy of test; Do not need hydraulic oil that power source is provided, handling safety, does not jeopardize staff, and environment is not polluted yet.
In addition, eccentric wheel 300 mechanism structure compactnesses, take up room littlely, be conducive to reduce the overall dimensions of test unit; The more important thing is, the surface configuration of eccentric wheel 300 is through reasonably design, and the centrifugal force producing can make its motion time is according to the variation of similar sinusoidal waveform, and also, this test unit is loaded on the acting force of connecting rod 200 also according to same variation.This kind of version a kind of good stability, control continuous version easily just.
Certainly, can also adopt other versions, as long as can produce periodic continually varying acting force to swing part, as toggle etc., just, the size of toggle is larger.
Can also not adopt the combination of above-mentioned eccentric wheel 300 and swing part, and use loading instrument directly connecting rod 200 to be loaded, can pass through the loading frequency of control strategy controlled loading instrument, load the parameters such as amplitude, make this loading instrument produce the continually varying acting force with predetermined amplitude and frequency according to testing requirements, just, this scheme likely improves experimentation cost.
As shown in Figures 1 and 2, above-mentioned swing part specifically can comprise the swing frame 400 of the above-mentioned eccentric wheel 300 of overcoat, and this swing frame 400 has the chamber of accommodating eccentric wheel 300.This chamber can be hexahedral shape, can be also spherical or irregularly shaped etc., as long as can be connected with wheel shaft 301, and loads to connecting rod 200.If this chamber is hexahedral shape, two of this chamber relative sidewalls are connected by above-mentioned clutch shaft bearing 302 with wheel shaft 301.One in two side is connected in connecting rod 200 in addition, with to connecting rod 200 transmitted loads.
Swing frame 400 has the sidewall being connected, and therefore it has good stability compared with the structures such as above-mentioned swing arm; And above-mentioned chamber can be designed as the chamber of sealing, so, eccentric wheel 300 is completely enclosed within chamber, avoids eccentric wheel 300 faults, flies out and hurts sb.'s feelings, and improves the security of test.
Certainly, this swing frame 400 can be also open, as long as possess the sidewall being connected with connecting rod 200; Or, can also not adopt swing frame 400, and adopt swing arm etc., as one end of swing arm is connected by above-mentioned clutch shaft bearing 302 with wheel shaft 301, the other end is connected with connecting rod 200, and so, the naked environment that is exposed on the external of eccentric wheel 300, is not protected.
Please refer to Fig. 3 and Fig. 4, Fig. 3 is the stressed sketch of connecting rod in Fig. 1, wheel shaft, swinging mounting axle, illustrates that connecting rod, between wheel shaft and swinging mounting axle, bears pressure load; Fig. 4 is the stressed sketch of connecting rod in Fig. 1, wheel shaft, swinging mounting axle, illustrate connecting rod and swinging mounting axle between, bearing tension load.
In one embodiment, can also fixedly mount swinging mounting axle 500 in pedestal 100, this swinging mounting axle 500 can not rotate freely, and only plays supporting swing part, and being it provides the effect of fulcrum.This swinging mounting axle 500 is parallel to wheel shaft 301, and perpendicular to the axis of connecting rod 200, the swing parts such as above-mentioned swing frame 400 or swing arm are connected with this swinging mounting axle 500, and can swing around this swinging mounting axle 500.
In this embodiment, the position relationship of connecting rod 200, wheel shaft 301 and swinging mounting axle 500 can have following three kinds:
The first, connecting rod 200 is between wheel shaft 301 and swinging mounting axle 500;
The second, wheel shaft 301 is between swinging mounting axle 500 and connecting rod 200;
The 3rd, swinging mounting axle 500 is between connecting rod 200 and wheel shaft 301.
In above-mentioned three kinds of position relationships, between the two, refer to, spatially between the two, be not positioned at certain on the two line.
As shown in Fig. 3 and Fig. 4 (position relationship of each parts is all with reference to the visual angle in figure 1), no matter connecting rod, between wheel shaft 301 and swinging mounting axle 500, bears pressure load or drag load, and in fact, three forms a lever construction:
Swinging mounting axle 500 provides the fulcrum of lever, wheel shaft 301 provides the first acting force of lever, wheel shaft 301 to the distance of swinging mounting axle 500 provides moving first arm of force of lever, the junction of connecting rod 200 and swing frame 400 provides the second acting force of lever, and this junction to the distance of swinging mounting axle 500 provides second arm of force of lever.
Above-mentioned the first acting force, first arm of force, the second acting force, second arm of force are defined as respectively to F1, L1, F2, L2.From lever principle:
F1×L1＝F2×L2
While test, by the distance of connecting rod 200 and swinging mounting axle 500 is rationally set, be L2, and the distance of wheel shaft 301 and swinging mounting axle 500, be L1, and provide known power, i.e. F1 for eccentric wheel 300, can calculate the load that imposes on connecting rod 200, i.e. F2 by above-mentioned formula.Correspondingly, in the situation that not improving power, can be by changing the distance between three, adjust first arm of force and second arm of force, the load (the second acting force) that connecting rod 200 is subject to is amplified according to certain ratio, and the motor of live axle 301 is required to reduce, only adopt fairly simple motor, reduce experimentation cost, make connecting rod 200 stablized, safety load.
When connecting rod 200, wheel shaft 301, swinging mounting axle 500 are during in above-mentioned the second position relationship, obviously, second arm of force is greater than first arm of force, the second acting force that acts on connecting rod 200 is by the first acting force that is less than wheel shaft 301 and provides, and the power heavy losses that wheel shaft 301 is provided can not pass to connecting rod 200 completely.
When connecting rod 200, wheel shaft 301, swinging mounting axle 500 are during in above-mentioned the third position relationship, when second arm of force between connecting rod 200 and swinging mounting axle 500 is greater than first arm of force between wheel shaft 301 and swinging mounting axle 500, the second acting force that acts on connecting rod 200, by the first acting force that is less than wheel shaft 301 and provides, causes power waste equally; When second arm of force between connecting rod 200 and swinging mounting axle 500 is less than first arm of force between wheel shaft 301 and swinging mounting axle 500, also can proportionally amplify the second acting force, but will increase the physical dimension of test unit.
Compared with the second, the third position relationship, the first position relationship can either reduce the physical dimension of test unit, does not cause again power waste, can obtain with less power the loaded load of larger connecting rod 200, and therefore, it is for preferred embodiment.
Further, above-mentioned swing frame 400 swings and can realize in the following manner around swinging mounting axle 500: the second bearing 502 is set between swinging mounting axle 500 and swing frame 400, this second bearing 502 is offset the component perpendicular to connecting rod 200 axis producing in swing frame 400 swing process, ensures that connecting rod 200 is along axis stably in being only subject to the state of above-mentioned drag load or pressure load.
Bearing cost is lower, and can make swing frame 400 swing around swinging mounting axle 500 swimmingly, is conducive to improve test efficiency.In addition, described the second bearing 502 can be rolling bearing, can be also sliding bearing.
Certainly, swing frame 400 can also be connected by articulated manner with swinging mounting axle 500, and swinging mounting axle 500 is hinge axes, and just, this linkwork may need complicated utility appliance, complicated operation.
Further, be provided with some fixed positions on swing frame 400, this fixed position is used for being connected with wheel shaft 301, thereby makes wheel shaft 301 different with the distance of swinging mounting axle 500.
So, for same test unit, only wheel shaft 301 need to be connected to different fixed positions, can obtain different above-mentioned first arm of forces, thereby in other test parameterss, such as, in the situation that the first acting force, second arm of force, position of the fulcrum etc. all remain unchanged, obtain the second different acting forces, drag load and pressure load that connecting rod 200 is born are adjustable, realize a tractor serves several purposes, make the adaptability of this test unit stronger.
Particularly, direction that can be along swinging mounting axle 500 to wheel shaft 301 is installed slideway, and with the lockable mechanism of slideway adaptation, this lockable mechanism should be able to be limited to slideway, and this lockable mechanism is connected with wheel shaft 301.Above-mentioned some fixed positions are set can realize by following method:
In the time that lockable mechanism moves along slideway, wheel shaft 301 and its synchronizing moving; When moving to the distance of wheel shaft 301 and swinging mounting axle 500 when suitable, by lockable mechanism and slideway engagement, the relative swinging mounting axle 500 of wheel shaft 301 is fixed, and completes described fixed position is set.
In the time need to adjusting the distance of wheel shaft 301 and swinging mounting axle 500, discharge lockable mechanism, again implement said method.
The design that slideway and lockable mechanism cooperatively interact can obtain continually varying fixed position, can finely tune the distance of wheel shaft 301 and swinging mounting axle 500, easy to use.Certainly, can also adopt other versions, as on swing frame 400, along the setting party of slideway to some draw-in grooves are set, wheel shaft 301 should be able to this draw-in groove engagement, just, this scheme can only obtain the distance of wheel shaft 301 with the swinging mounting axle 500 of specifying numerical value, compares with the scheme that slideway and locking structure are set, and adaptability is slightly poor.
Be different from above-mentioned taking lever principle as the scheme according to design, in another embodiment, there is not the swinging mounting axle 500 in such scheme, there is not the fulcrum of wheel shaft 301, and not based on lever principle, but, be still provided with the structures such as eccentric wheel 300, wheel shaft 301 and swing part in such scheme.In addition, be also provided with the guide rail fixing with pedestal 100, the axis of this guide rail and connecting rod 200 be arranged in parallel, and above-mentioned swing part is installed on this guide rail after being connected with wheel shaft 301.
In the time that eccentric wheel 300 is driven by wheel shaft 301 and rotates, to drive swing part to produce the linear reciprocating motion along guide rail, this linear reciprocating motion refers to that swing part is due to the micro-displacement that is subject to centrifugal force and produces, thereby makes swing part apply pulling force and the pressure along axis to connecting rod 200.Visible, swing part not only can be swung and be realized by the pendulum model in such scheme the load mode of connecting rod 200, also can realize by the integral translation in this programme.
With above-mentioned taking lever principle as according to design embodiment compared with, this scheme is without swinging mounting axle 500 etc. is set, compact conformation, cost is lower, just, can not realize a tractor serves several purposes, when power one timing that wheel shaft 301 provides, only can provide to connecting rod 200 pulling force and the pressure of single amplitude; And guide rail structure easily produces fault, maintenance maintenance will affect test efficiency.
In above-mentioned each embodiment, all can be provided with pressure-adjusting spring 700, the two ends of this pressure-adjusting spring 700 are resisted against respectively pedestal 100 and swing part, and pressure-adjusting spring 700 does not have annexation with swing part; And in the direction of connecting rod 200 axis, this pressure-adjusting spring 700 and connecting rod 200 lay respectively at the both sides of swing part.
No matter swing taking swinging mounting axle 500 as fulcrum, still moving linearly on guide rail:
When swing part to connecting rod 200 near time, pressure-adjusting spring 700 not to its produce acting force, the amplitude of the pressure load that connecting rod 200 is subject to is the centrifugal force size of eccentric wheel 300 in this moment;
When swing part is during away from connecting rod 200, swing part applies drag load to connecting rod 200, simultaneously, pressure-adjusting spring 700 is compressed to pedestal 100 by swing part, produce predetermined decrement, provide along the restoring force of connecting rod 200 axis to swing part, this restoring force and swing part impose on the drag load opposite direction of connecting rod 200, drag load is produced to consumption, the drag load amplitude that connecting rod 200 the is subject to centrifugal force numerical value that moment eccentric wheel 300 provides for this reason and above-mentioned restoring force numerical value poor, the amplitude of drag load is less than the amplitude of pressure load.
Visible, arrange after this pressure-adjusting spring 700, the pressure load amplitude that can be subject to connecting rod 200 and the ratio of drag load amplitude adjust, can work with actual engine time, the pulling force that connecting rod 200 is subject to is less than the situation coupling of pressure, makes test findings more accurately, reliably.
In this scheme, pressure-adjusting spring 700 can be fixing with pedestal 100, also can only be resisted against on pedestal 100, as long as in the time that it is subject to the compression of swing part, can produce decrement, as shown in fig. 1, between pedestal 100 and swing part, be fixedly connected with pressure-adjusting screw 701, this pressure-adjusting spring 700 is coated at pressure-adjusting screw 701, and is only resisted against on pedestal 100.Certainly, one end of pressure-adjusting spring 700 also can be fixedly welded on pedestal 100, just, so, is not easy to it and changes, and uses inconvenience.
Swinging mounting axle 500 in above-mentioned each scheme can be fixedly connected with pedestal 100 by axle bed 600, and, the shaft-cup 601 mating with axle bed 600 can also be set, this shaft-cup 601 and the common swinging mounting axle 500 that surrounds of axle bed 600.This shaft-cup 601 removably connects with axle bed 600, not only swinging mounting axle 500 is fixed on to axle bed 600, and in the time that swinging mounting axle 500 needs repairing, changes, shaft-cup 601 is removed, easy to operate.
Further, in such scheme, can also be provided with link supporting plate 800, this link supporting plate 800 is for connecting one end and the pedestal 100 of connecting rod 200, one in big end end 201 or small end of connecting rod end 202 is connected to this link supporting plate 800, and, pedestal 100 is provided with some installation sites along connecting rod 200 axis, and this link supporting plate 800 can be fixed on any one in above-mentioned some installation sites.
So, in the time that the connecting rod 200 of the gonnecting rod body 203 to having different size is tested, only need link supporting plate 800 to fix from different installation sites, realize and by same test unit, different connecting rod 200 being tested.
Particularly, can be in pedestal 100 deployment rails and the lockable mechanism that can be limited to track, this lockable mechanism and link supporting plate 800 are fixing, and this lockable mechanism provides different installation sites in the time that track slides; Some threaded holes also can be set on pedestal 100, and link supporting plate 800 can be threaded with pedestal 100, and different threaded holes provides different installation sites.
Further, in such scheme, can also be provided with force cell 900, this force cell 900 acts on the actual acting force numerical value of swing part for measuring eccentric wheel 300.In test, the rotation of eccentric wheel 300 is subject to the impact of many factors, its actual acting force that acts on swing part may and be not equal to its centrifugal force numerical value, if can not accurately obtain eccentric wheel 300 and act on the acting force of swing part, can not accurately test the force-bearing situation of connecting rod 200, will have a strong impact on accuracy and the reliability of test.
Consider above-mentioned technical matters, the acting force that force cell 900 is applied to swing part to eccentric wheel 300 is set and monitors, to accurately obtain connecting rod 200 force-bearing situations, improve experimental accuracy and reliability.
It should be noted that, in above-mentioned each scheme, swing part all can directly be connected with connecting rod 200 with connecting rod 200, pedestal 100, directly contacts with one end of connecting rod 200; Also can indirectly connect by other structures, indirectly be connected with swing part as Fig. 1 and Fig. 2 illustrate connecting rod 200, big end end 201 is connected with swing part by first connecting rod fixed block 801, small end of connecting rod end 202 is connected with link supporting plate 800 by second connecting rod fixed block 802, and then is fixed on pedestal 100.
Obviously, swing part and connecting rod 200 are connected to good indirectly, are so conducive to protect the end construction of connecting rod 200.
Above a kind of connecting rod fatigue experimental device provided by the present invention is described in detail.Applied specific case herein principle of the present invention and embodiment are set forth, the explanation of above embodiment is just for helping to understand method of the present invention and core concept thereof.It should be pointed out that for those skilled in the art, under the premise without departing from the principles of the invention, can also carry out some improvement and modification to the present invention, these improvement and modification also fall in the protection domain of the claims in the present invention.
Claims (12)
1. a connecting rod fatigue experimental device, comprise pedestal (100), connecting rod (200) and charger, described pedestal (100) is fixed in one end of described connecting rod (200), the other end is loaded by described charger, it is characterized in that, described charger applies continually varying pressure and pulling force repeatedly to described connecting rod (200).
2. connecting rod fatigue experimental device as claimed in claim 1, it is characterized in that, described charger comprises eccentric wheel (300), the wheel shaft (301) adaptive with described eccentric wheel (300), and the swing part that is connected in described wheel shaft (301), swings around described wheel shaft (301); Described wheel shaft (301) is perpendicular to described connecting rod (200) axis arranged, and described swing part applies described pulling force and described pressure to described connecting rod (200).
3. connecting rod fatigue experimental device as claimed in claim 2, it is characterized in that, described swing part comprises the swing frame (400) of eccentric wheel (300) described in overcoat, and described swing frame (400) forms the chamber of accommodating described eccentric wheel (300).
4. connecting rod fatigue experimental device as claimed in claim 3, it is characterized in that, also comprise and be fixed on described pedestal (100), the swinging mounting axle (500) vertical, parallel with described wheel shaft (301) with described connecting rod (200) axis; Described swing frame (400) is connected with described swinging mounting axle (500), and can swing around described swinging mounting axle (500).
5. connecting rod fatigue experimental device as claimed in claim 4, is characterized in that, described connecting rod (200) is positioned between described swinging mounting axle (500) and described wheel shaft (301).
6. connecting rod fatigue experimental device as claimed in claim 5, it is characterized in that, also comprise the second bearing (502), described swinging mounting axle (500) is connected with described swing frame (400) by described the second bearing (502).
7. connecting rod fatigue experimental device as claimed in claim 6, it is characterized in that, described swing frame (400) is provided with the fixed position that some and described wheel shaft (301) is connected, to regulate the distance of described wheel shaft (301) and described swinging mounting axle (500).
8. connecting rod fatigue experimental device as claimed in claim 7, it is characterized in that, also comprise the slideway of installing along described swinging mounting axle (500) to described wheel shaft (301) direction, and with the lockable mechanism of described slideway adaptation, described lockable mechanism is connected with described wheel shaft (301).
9. connecting rod fatigue experimental device as claimed in claim 2, it is characterized in that, also comprise fixing with described pedestal (100), with the guide rail of the parallel installation of described connecting rod (200) axis, described swing part is installed on described guide rail, and can be along described guide rail slip.
10. the connecting rod fatigue experimental device as described in claim 2-9 any one, it is characterized in that, also comprise the pressure-adjusting spring (700) be arrangeding in parallel with described connecting rod (200) axis, the two ends of described pressure-adjusting spring (700) are resisted against respectively described pedestal (100) and described swing part, and lay respectively at the both sides of described swing part along described connecting rod (200) axis and described connecting rod (200).
11. connecting rod fatigue experimental devices as claimed in claim 10, it is characterized in that, also comprise link supporting plate (800), one end of described connecting rod (200) is fixing by described link supporting plate (800) and described pedestal (100); Described pedestal (100) is provided with some installation sites along described connecting rod (200) axis, to fix described link supporting plate (800).
12. connecting rod fatigue experimental devices as claimed in claim 11, it is characterized in that, also comprise force cell (900), described force cell (900) measures described eccentric wheel (300) and acts on the size of the power of described swing part.
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105388008A (en) * | 2015-12-14 | 2016-03-09 | 中国北方发动机研究所(天津) | Large-bore engine crankshaft asymmetric bending fatigue test method |
| CN104374563B (en) * | 2014-11-26 | 2017-01-25 | 南京汽车集团有限公司 | Auxiliary cushion block for connecting rod fatigue test |
| CN107202694A (en) * | 2017-06-26 | 2017-09-26 | 常州机电职业技术学院 | Fatigue durability testing device for engine connecting rod |
| CN110346223A (en) * | 2019-07-03 | 2019-10-18 | 中国商用飞机有限责任公司 | Bending shear coupling test device |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001296223A (en) * | 2000-04-12 | 2001-10-26 | Mitsubishi Heavy Ind Ltd | Changing device for fitting position of connecting rod |
| WO2002030603A1 (en) * | 2000-10-10 | 2002-04-18 | Sameh Guirgis | Process to fracture connecting rods |
| CN1485604A (en) * | 2003-07-18 | 2004-03-31 | 明门实业股份有限公司 | Swing arm testing machine and testing method thereof |
| CN102393340A (en) * | 2011-09-01 | 2012-03-28 | 浙江大学 | Hydraulic fatigue test system of connecting rod |
| CN202693276U (en) * | 2012-05-31 | 2013-01-23 | 浙江吉利汽车研究院有限公司杭州分公司 | Fatigue test table of engine connecting rod |
-
2014
- 2014-05-29 CN CN201410235164.2A patent/CN104006967B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001296223A (en) * | 2000-04-12 | 2001-10-26 | Mitsubishi Heavy Ind Ltd | Changing device for fitting position of connecting rod |
| WO2002030603A1 (en) * | 2000-10-10 | 2002-04-18 | Sameh Guirgis | Process to fracture connecting rods |
| CN1485604A (en) * | 2003-07-18 | 2004-03-31 | 明门实业股份有限公司 | Swing arm testing machine and testing method thereof |
| CN102393340A (en) * | 2011-09-01 | 2012-03-28 | 浙江大学 | Hydraulic fatigue test system of connecting rod |
| CN202693276U (en) * | 2012-05-31 | 2013-01-23 | 浙江吉利汽车研究院有限公司杭州分公司 | Fatigue test table of engine connecting rod |
Non-Patent Citations (1)
| Title |
|---|
| 景国玺 等: "发动机连杆疲劳强度试验及寿命预测方法研究", 《车用发动机》 * |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104374563B (en) * | 2014-11-26 | 2017-01-25 | 南京汽车集团有限公司 | Auxiliary cushion block for connecting rod fatigue test |
| CN105388008A (en) * | 2015-12-14 | 2016-03-09 | 中国北方发动机研究所(天津) | Large-bore engine crankshaft asymmetric bending fatigue test method |
| CN105388008B (en) * | 2015-12-14 | 2018-11-06 | 中国北方发动机研究所(天津) | A kind of large bore engine bent axle asymmetric curvature fatigue test method |
| CN107202694A (en) * | 2017-06-26 | 2017-09-26 | 常州机电职业技术学院 | Fatigue durability testing device for engine connecting rod |
| CN110346223A (en) * | 2019-07-03 | 2019-10-18 | 中国商用飞机有限责任公司 | Bending shear coupling test device |
| CN110346223B (en) * | 2019-07-03 | 2021-08-10 | 中国商用飞机有限责任公司 | Bending shear coupling test device |
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