CN2901278Y - Analogue test table frame for automobile front axle rocking arm dynamic strength durability - Google Patents
Analogue test table frame for automobile front axle rocking arm dynamic strength durability Download PDFInfo
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- CN2901278Y CN2901278Y CNU2006200417364U CN200620041736U CN2901278Y CN 2901278 Y CN2901278 Y CN 2901278Y CN U2006200417364 U CNU2006200417364 U CN U2006200417364U CN 200620041736 U CN200620041736 U CN 200620041736U CN 2901278 Y CN2901278 Y CN 2901278Y
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Abstract
A dynamic strength durable simulator test bed of front axle winding arm of vehicle can simultaneously imitate the rigidity bound of axial linear and radial non-linear, wherein, one side of the prevention diversion gripper mechanism imitates the axial linear rigidity bound, while another side is respectively connected with two triangle cranks-spring steel plate mechanisms. Via the pull force of the charger or pressure action, the prevention diversion gripper mechanism drives one triangle crank mechanism to rotate clockwise or another one to rotate anticlockwise. A roller bearing on the top-point of the triangle crank mechanism vertically moves along the projection on the upper end of the variable cross-section spring plate, so cause different acting forces and arms of force on the variable--section spring plate, which makes the prevention diversion gripper mechanism produce a non-linear rigidity binding reaction force conformity with the radial rigidity feature of the swing arm. The back beam support of the vehicle front axle winding arm is bound in the prevention diversion gripper mechanism, thereby reproducing the working condition of the vehicle front axle winding arm and improving the confidence level of the simulation test.
Description
Technical field
The utility model relates to vehicle testing equipment, relates in particular to the durable simulation test stand of vehicle dynamic intensity, the durable simulation test stand of particularly a kind of dynamic strength of automobile front axle rocker arm.
Background technology
The develop rapidly of auto industry is had higher requirement to auto parts and components reliability and R﹠D cycle.The actual condition of simulated automotive parts, to its carry out the resistance to vibration long duration test be research its reliability effective way.If yet adopt car load under actual condition, to carry out actual road test, the test period will be very very long, and consume a large amount of human and material resources and financial resources.Therefore in order to shorten the test period, must strengthen bench test.Certain motor corporation once entrusted parts factory that the automobile front axle rocking arm is carried out dynamic durable bench test.Find that in process of the test early stage undesired damage takes place the rubber-metal bearing of rocking arm rear axle supporting place.Finish test and need tens of losses even more rubber-metal bearings.For this reason, changed test method, be about to the supporting of rocking arm rear axle and directly be fixed in the rigid frame.But in process of the test, but find, occurred abnormal damage near the rocking arm rear axle, and the life-span is very short.Its reason is to change the rubber-metal bearing into non-yielding prop, has changed the constraint or the boundary condition of rocking arm, has therefore destroyed the deformation distribution and the stress distribution of rocking arm each point when stressed.Therefore, test-bed must have the constraint condition identical with actual vehicle, and the rigidity of test-bed restraint device (or elasticity) characteristic must be consistent with the characteristic of the assembly (being designated hereinafter simply as carriage rubber assembly) that comprises parts such as carriage and rubber-metal bearing.After tested, the stiffness characteristics of carriage rubber assembly axially is being linear, and the stiffness characteristics of carriage rubber assembly radially is being non-linear.
Summary of the invention
The purpose of this utility model provides the durable simulation test stand of a kind of dynamic strength of automobile front axle rocker arm, and the durable simulation test stand of described this dynamic strength of automobile front axle rocker arm will solve the actual condition that test-bed in the prior art can not simulated automotive propons rocking arm, the technical matters of a large amount of tested parts of loss.
The durable simulation test stand of this dynamic strength of automobile front axle rocker arm of the present utility model, anti-deflection clamp system by an automobile front axle rocking arm rear axle supporting constitutes, one side of described anti-deflection clamp system is set with a linear rigidity restraint device, described linear rigidity restraint device is made of lateral bearing steel spring plate and two two power bars, the anti-deflection clamp system is connected with described lateral bearing steel spring plate by described two two power bars, the opposite side of anti-deflection clamp system is set with a non-linear rigidity restraint device, described non-linear rigidity restraint device by a radially non-linear tensile machine and one radially nonlinear pressure mechanism constitute, described radially non-linear tensile machine is made of the first variable cross section elastic panel and secondary first a triangle crank member, the described one secondary first triangle crank member is made of two first triangle crank members, one side of the first variable cross section elastic panel is provided with a fixed support, the upper end of the side of the first variable cross section elastic panel opposite side is set with a projection, described projection is the wedge shape block that the bottom has the radian that caves inward, be provided with one first bearing in the described fixed support, first bearing is connected with the position, first summit of the described first triangle crank member by bearing, the position, second summit of the first triangle crank member is connected with one first rolling bearing by bearing pin, first rolling bearing rests on the projection side of the first variable cross section elastic panel, be provided with one first chute in the first triangle crank member, described radially nonlinear pressure mechanism is made of the second variable cross section elastic panel and secondary second a triangle crank member, the described one secondary second triangle crank member is made of two second triangle crank members, one side of the second variable cross section elastic panel is provided with a fixed support, the upper end of the side of the second variable cross section elastic panel opposite side is set with a projection, described projection is the wedge shape block that the bottom has the radian that caves inward, be provided with one second bearing in the described fixed support, second bearing is connected with the position, first summit of the described second triangle crank member by bearing, the position, second summit of the second triangle crank member is connected with one second rolling bearing by bearing pin, second rolling bearing rests on the projection side of the second variable cross section elastic panel, be provided with one second chute in the second triangle crank member, be provided with a center in first chute and second chute and be connected rod member, described center connects rod member and passes the first triangle crank member and the second triangle crank member, the first triangle crank member and the second triangle crank member are about being connected the vertical line symmetry in rod member axle center through the center, first chute and second chute are about being connected the vertical line symmetry in rod member axle center through the center, the two ends that described center connects rod member are connected with radially two power bars separately, and described radially two power bars are connected with described anti-deflection clamp system.
Further, described anti-deflection clamp system is connected with a firm banking by plural two power bars.
Further, the described first variable cross section elastic panel and the second variable cross section elastic panel are made of the lateral bearing steel spring plate respectively.
Further, described anti-deflection clamp system is connected with a conventional charger.
Principle of work of the present utility model is as follows: the rear axle supporting of automobile front axle rocking arm is connected in the anti-deflection clamp system, charger pushes away or draws the anti-deflection clamp system then, when the anti-deflection clamp system is subjected to displacement, be connected with the center that two two power bars that rod member links to each other drive the first triangle crank member or the second triangle crank member rotatablely moves, the rolling bearing at the place, second summit of the first triangle crank member or the second triangle crank member is close to the projection vertical movement of first or second tapered spring plate upper end, thereby produce the different acting forces and the arm of force thereof, make the tapered spring plate produce deformation, the tapered spring plate produces corresponding non-linear reacting force because of deformation.Layout just because of the triangle crank member, the variation of the variation of acting force arm and spring plate piece area of section, the triangle crank member is had and the corresponding to non-linear rigidity characteristic of rocking arm radial rigidity characteristic, and, because the first triangle crank member and the second triangle crank member and chute wherein are symmetrical arranged, when a secondary triangle crank member produces drag load, another secondary triangle crank member can not produce pressure load with regard to being in release conditions, and when a secondary triangle crank member produces pressure load, another secondary triangle crank member can not produce drag load with regard to being in release conditions, the said mechanism simulation has realized the real load situation of automobile, be the automobile front axle rocking arm diametrically or be subjected to drag load, load perhaps is under pressure.In addition, when being in pressure load, the direction of the reacting force of pressure and two power bars is difficult to conllinear, and there is tolerance in accessory size, so the anti-deflection clamp system may deflect, in the utility model, parallel on the baseplane of anti-deflection clamp system two two power bars have been installed, the upper end of two two power bars is fixed on the bottom surface of anti-deflection clamp system, and the lower end is fixed on the baseplane, has prevented that the anti-deflection clamp system from deflecting.
The utility model and prior art contrast, and its effect is actively with tangible.The utility model utilizes the power that the triangle crank member changes and the change rigidity of the arm of force and variable cross section elastic panel thereof, clamp system is produced non-linear reacting force, thereby make the restraint device of rear axle supporting of automobile front axle rocking arm can produce and the corresponding to constraint condition of rocking arm radial rigidity characteristic, thereby true reappearance automobile front axle rocking arm duty, improved the confidence level of simulation test.The utility model can be simulated the different qualities and the rigidity of carriage rubber assembly both direction simultaneously, wherein radially is non-linear, axially is linear.
Description of drawings
Fig. 1 is the synoptic diagram of automobile front axle rocking arm.
Fig. 2 is the plan structure synoptic diagram (nonlinear pressure mechanism does not mark) of the durable simulation test stand of dynamic strength of automobile front axle rocker arm of the present utility model.
Fig. 3 looks synoptic diagram (nonlinear pressure mechanism does not mark) for the master of the durable simulation test stand of dynamic strength of automobile front axle rocker arm of the present utility model.
Fig. 4 looks synoptic diagram (linear rigidity constraint mechanism) for the right side of the durable simulation test stand of dynamic strength of automobile front axle rocker arm of the present utility model.
Fig. 5 is that the first triangle crank member in the durable simulation test stand of dynamic strength of automobile front axle rocker arm of the present utility model and the installation site of the second triangle crank member concern synoptic diagram.
Embodiment
As shown in Figure 1, in the dynamic durable bench test that the automobile front axle rocking arm is carried out of the prior art, early stage undesired damage takes place in the rubber-metal bearing 2 that the rocking arm rear axle supports 1 place.Finish test and need tens of losses even more rubber-metal bearing 2.For this reason, change the mode of having tested, be about to rocking arm rear axle supporting 1 and directly be fixed in the rigid frame.But in process of the test, but find abnormal damage to have occurred near the rocking arm rear axle, and the life-span is very short.Its reason is to change rubber-metal bearing 2 into non-yielding prop, has changed the constraint or the boundary condition of rocking arm, has therefore destroyed the deformation distribution and the stress distribution of rocking arm each point when stressed.
According to similarity theory, be contained in any 2 points (supposing to be called A point and B point) of the rocking arm on the vehicle, the stress σ in actual travel
AVAnd σ
BV, with the stress σ under the stand strenuous test state
ATAnd σ
BTFollowing relational expression should be arranged:
And satisfying following formula, test-bed must have the constraint condition identical with actual vehicle.Therefore rigidity (or elasticity) characteristic of test-bed restraint device must be consistent with the characteristic of the assembly (being designated hereinafter simply as carriage rubber assembly) that comprises parts such as carriage and rubber-metal bearing.
After tested, the stiffness characteristics of carriage rubber assembly is linear in axially (Z-direction among Fig. 1), and the stiffness characteristics of carriage rubber assembly is non-linear in radially (Y direction among Fig. 1).
The durable simulation test stand of dynamic strength of automobile front axle rocker arm of the present utility model is made of the anti-deflection clamp system 5 of an automobile front axle rocking arm rear axle supporting, as Fig. 2, Fig. 3 and shown in Figure 4, one side of described anti-deflection clamp system 5 is set with a linear rigidity restraint device, described linear rigidity restraint device is made of lateral bearing steel spring plate 14 and two two power bars 13, and anti-deflection clamp system 5 is connected with described lateral bearing steel spring plate 14 by described two two power bars 13.
The opposite side of anti-deflection clamp system 5 is set with a non-linear rigidity restraint device, described non-linear rigidity restraint device by a radially non-linear tensile machine and one radially nonlinear pressure mechanism constitute, only represented radially non-linear tensile machine among Fig. 2 and Fig. 3.Described radially non-linear tensile machine is made of the first variable cross section elastic panel 4 and secondary first a triangle crank member 3, the described one secondary first triangle crank member 3 is made of two first triangle crank members, one side of the first variable cross section elastic panel 4 is provided with a fixed support, the upper end of the side of the first variable cross section elastic panel, 4 opposite sides is set with a projection 11, described projection 11 is wedge shape blocks that the bottom has the radian that caves inward, be provided with one first bearing in the described fixed support, first bearing is connected with the position, first summit of the described first triangle crank member 3 by bearing 10, the position, second summit of the first triangle crank member 3 is connected with one first rolling bearing 12 by bearing pin, first rolling bearing 12 contacts with projection 11 sides of the first variable cross section elastic panel 4, is provided with one first chute 6 in the first triangle crank member 3.
Described radially nonlinear pressure mechanism is made of the second variable cross section elastic panel and secondary second a triangle crank member, the described one secondary second triangle crank member is made of two second triangle crank members, one side of the second variable cross section elastic panel is provided with a fixed support, the upper end of the side of the second variable cross section elastic panel opposite side is set with a projection, described projection is the wedge shape block that the bottom has the radian that caves inward, be provided with one second bearing in the described fixed support, second bearing is connected with the position, first summit of the described second triangle crank member by bearing, the position, second summit of the second triangle crank member is connected with one second rolling bearing by bearing pin, second rolling bearing contacts with the projection side of the second variable cross section elastic panel, be provided with one second chute in the second triangle crank member, be provided with a center in first chute 6 and second chute and be connected rod member 7, described center connects rod member 7 and passes the first triangle crank member 3 and the second triangle crank member, the first triangle crank member 3 and the second triangle crank member are about being connected the vertical line symmetry in rod member 7 axle center through the center, first chute 6 and second chute are about being connected the vertical line symmetry in rod member 7 axle center through the center, the two ends that described center connects rod member 7 are connected with radially two power bars 9 separately, and described radially two power bars 9 are connected with described anti-deflection clamp system 5.
Further, described anti-deflection clamp system 5 is connected with a firm banking by plural two power bars 8.
Further, the described first variable cross section elastic panel 4 and the second variable cross section elastic panel are made of the lateral bearing steel spring plate respectively.
Further, described anti-deflection clamp system 5 is connected with a conventional charger.
Concrete principle of the present utility model is as follows:
The failure of existing test unit comes from not being inconsistent in the stiffness characteristics of constraint mechanism of rocking arm and the actual car load.Can find according to test result, carriage rubber assembly stiffness characteristics vertically is linear, and stiffness characteristics radially is non-linear, and its property class is similar to trigonometric function, and imagination adopts the trigonometric function of triangle crank member to concern and simulates carriage rubber assembly thus.The application point of exerting all one's strength by the rotation of triangle crank member produces change up and down, produces the different acting forces and the arm of force thereof thus, adopts the steel spring plate of variable cross section simultaneously, constitutes a whole set of triangle component restraint device that becomes rigidity thus.The triangle crank mechanism is connected with anti-deflection clamp system 5 by two power bars 9, and the rigidity that need simulate in the Y direction is non-linear.
In dynamic long duration test; rocking arm both had been subjected to the drag load load that also is under pressure diametrically; therefore in rear axle supporting radial constraint mechanism; two triangle crank mechanisms of oppositely installing are arranged; they one of them only under drag load, work and inoperative under pressure load, another is then opposite.Both symmetries structurally.
In any cover triangle crank mechanism and steel spring plate, a projection 11 is equipped with at the top of steel spring plate, and projection 11 bottoms have the wedge block of the radian that caves inward.In the test, beginning loading tensile load, when the anti-deflection clamp system was subjected to displacement, two power bars 9 were rotated counterclockwise the triangle crank mechanism, rolling bearing 12 on it will be close to projection 11 and move upward, and at this moment steel spring plate is because deformation produces non-linear reacting force.
Reserve chute in the triangle crank mechanism.Do the time spent when a cover triangle crank mechanism wherein, the connection rod member at center just can slide in the chute of another set of triangle crank mechanism, the effect that this moment, another set of triangle crank mechanism did not stress.That is to say, in test, when load cylinder loads, loading force in one direction once, be load cylinder when at every turn loading, have only a cover triangle crank mechanism and a steel spring plate to work, an other cover triangle crank mechanism and a steel spring plate are inoperative.
When being in pressure load, the reacting force of pressure F and two power bars 9 is difficult to conllinear (and there is tolerance in accessory size), so anti-deflection clamp system 5 may deflect.So be fixed on the bottom surface of anti-deflection clamp system 5 in the upper end that 8, two two power bars 8 of two two power bars have been installed on the baseplane of anti-deflection clamp system 5, the lower end is fixed on the baseplane, so 5 deflections of anti-deflection clamp system have been prevented.
The restraint device of the change rigidity in the utility model has following feature:
1. simulate the non-linear rigidity characteristic of carriage rubber assembly by following three methods:
1.1 adopt the trigonometric function relation of triangle component.
1.2 the application point of exerting all one's strength by triangle component rotation produces moving up and down, produces the different acting forces and the arm of force thereof thus.
1.3 adopt the steel spring plate of variable cross section.
2. the four-bar mechanism bar of the anti-deflection clamp system effect of having offset the deflection force of extra generation guarantees that the motion of anti-deflection clamp system is translation motion.
This design proposal can be simulated the stress distribution under any load fully, though in loading procedure or the stress distribution that can both guarantee part at the peak value place of load consistent with the stress distribution of real vehicle state under same load.
Claims (4)
1. durable simulation test stand of dynamic strength of automobile front axle rocker arm, it is characterized in that: the anti-deflection clamp system by an automobile front axle rocking arm rear axle supporting constitutes, one side of described anti-deflection clamp system is set with a linear rigidity restraint device, described linear rigidity restraint device is made of lateral bearing steel spring plate and two two power bars, the anti-deflection clamp system is connected with described lateral bearing steel spring plate by described two two power bars, the opposite side of anti-deflection clamp system is set with a non-linear rigidity restraint device, described non-linear rigidity restraint device by a radially non-linear tensile machine and one radially nonlinear pressure mechanism constitute, described radially non-linear tensile machine is made of the first variable cross section elastic panel and secondary first a triangle crank member, the described one secondary first triangle crank member is made of two first triangle crank members, one side of the first variable cross section elastic panel is provided with a fixed support, the upper end of the side of the first variable cross section elastic panel opposite side is set with a projection, described projection is the wedge shape block that the bottom has the radian that caves inward, be provided with one first bearing in the described fixed support, first bearing is connected with the position, first summit of the described first triangle crank member by bearing, the position, second summit of the first triangle crank member is connected with one first rolling bearing by bearing pin, first rolling bearing contacts with the projection side of the first variable cross section elastic panel, be provided with one first chute in the first triangle crank member, described radially nonlinear pressure mechanism is made of the second variable cross section elastic panel and secondary second a triangle crank member, the described one secondary second triangle crank member is made of two second triangle crank members, one side of the second variable cross section elastic panel is provided with a fixed support, the upper end of the side of the second variable cross section elastic panel opposite side is set with a projection, described projection is the wedge shape block that the bottom has the radian that caves inward, be provided with one second bearing in the described fixed support, second bearing is connected with the position, first summit of the described second triangle crank member by bearing, the position, second summit of the second triangle crank member is connected with one second rolling bearing by bearing pin, contact on the projection side of second rolling bearing and the second variable cross section elastic panel, be provided with one second chute in the second triangle crank member, be provided with a center in first chute and second chute and be connected rod member, described center connects rod member and passes the first triangle crank member and the second triangle crank member, the first triangle crank member and the second triangle crank member are about being connected the vertical line symmetry in rod member axle center through the center, first chute and second chute are about being connected the vertical line symmetry in rod member axle center through the center, the two ends that described center connects rod member are connected with radially two power bars separately, and described radially two power bars are connected with described anti-deflection clamp system.
2. the durable simulation test stand of dynamic strength of automobile front axle rocker arm as claimed in claim 1 is characterized in that: described anti-deflection clamp system is connected with a firm banking by plural two power bars.
3. the durable simulation test stand of dynamic strength of automobile front axle rocker arm as claimed in claim 1 is characterized in that: the described first variable cross section elastic panel and the second variable cross section elastic panel are made of the lateral bearing steel spring plate respectively.
4. the durable simulation test stand of dynamic strength of automobile front axle rocker arm as claimed in claim 1 is characterized in that: described anti-deflection clamp system is connected with a conventional charger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2006200417364U CN2901278Y (en) | 2006-05-12 | 2006-05-12 | Analogue test table frame for automobile front axle rocking arm dynamic strength durability |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2006200417364U CN2901278Y (en) | 2006-05-12 | 2006-05-12 | Analogue test table frame for automobile front axle rocking arm dynamic strength durability |
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| Publication Number | Publication Date |
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| CN2901278Y true CN2901278Y (en) | 2007-05-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2006200417364U Expired - Fee Related CN2901278Y (en) | 2006-05-12 | 2006-05-12 | Analogue test table frame for automobile front axle rocking arm dynamic strength durability |
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| CN (1) | CN2901278Y (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103471856A (en) * | 2013-08-30 | 2013-12-25 | 奇瑞汽车股份有限公司 | Device and method for testing front sub-frame assembly of automobile |
| CN103612226A (en) * | 2013-11-21 | 2014-03-05 | 奇瑞汽车股份有限公司 | Auxiliary frame double-shaft testing clamp device |
| CN104697758A (en) * | 2013-12-04 | 2015-06-10 | 广州汽车集团股份有限公司 | Two force member test bed |
| CN106840723A (en) * | 2017-01-17 | 2017-06-13 | 烟台中宇航空液压有限公司 | Hydraulic rocker loading device and its loading method |
| CN112394035A (en) * | 2021-01-21 | 2021-02-23 | 佛山市南海盐步康士柏机电有限公司 | Intelligent automobile chassis detection method and device |
-
2006
- 2006-05-12 CN CNU2006200417364U patent/CN2901278Y/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103471856A (en) * | 2013-08-30 | 2013-12-25 | 奇瑞汽车股份有限公司 | Device and method for testing front sub-frame assembly of automobile |
| CN103612226A (en) * | 2013-11-21 | 2014-03-05 | 奇瑞汽车股份有限公司 | Auxiliary frame double-shaft testing clamp device |
| CN104697758A (en) * | 2013-12-04 | 2015-06-10 | 广州汽车集团股份有限公司 | Two force member test bed |
| CN104697758B (en) * | 2013-12-04 | 2017-05-31 | 广州汽车集团股份有限公司 | Two power rod member test-beds |
| CN106840723A (en) * | 2017-01-17 | 2017-06-13 | 烟台中宇航空液压有限公司 | Hydraulic rocker loading device and its loading method |
| CN112394035A (en) * | 2021-01-21 | 2021-02-23 | 佛山市南海盐步康士柏机电有限公司 | Intelligent automobile chassis detection method and device |
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