CN104462834A - Frame complex work condition multi-axial fatigue calculation method including welding simulation - Google Patents
Frame complex work condition multi-axial fatigue calculation method including welding simulation Download PDFInfo
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Abstract
The invention discloses a frame complex work condition multi-axial fatigue calculation method including welding simulation. The method includes welding and structural unit grouping, finite element welding simulation, complex work condition defining, multi-axial building and multi-axial fatigue calculation. The complex work condition defining includes defining the magnitude, directions and loading positions of fatigue load and optional one of fatigue circulation work conditions comprising tilting moment fatigue, S-shaped turning fatigue, continuous brake fatigue, torsional fatigue and multi-freedom-degree fatigue. Multi-axial building includes building at least two fatigue life axes according to the defined fatigue load and the fatigue circulation work condition. Multi-axial fatigue calculation includes using fatigue life calculation software to build calculation channels corresponding to the fatigue axes in number so as to perform multi-channel multi-axial fatigue life calculation according to the defined complex work condition and the built fatigue life axes. The frame complex work condition multi-axial fatigue calculation method has the advantages that accurate fatigue life calculation is achieved, repeated research and development can be avoided, and energy saving and social progress are benefited.
Description
Technical field
The present invention relates to a kind of fatigue mechanisms method in Vehicle Frame Design stage, particularly a kind of vehicle frame complex working condition non-proportional loading computing method comprising welding analog.
Background technology
Vehicle frame is the main load bearing component of automobile, particularly truck, some box-structures can be welded with between longeron at the crossbeam of vehicle frame, be used for strengthening the bulk strength of vehicle frame, and the vehicle frame of general automobile is made up of two longerons being positioned at both sides and several crossbeams, the fatigue lifetime of vehicle frame is determined by the bench test of vehicle frame material object.For reducing cost of development and shortening the construction cycle, need to carry out design verification in the design phase of vehicle by Calculation of Fatigue Life software, must Work condition analogue and optimum configurations be carried out before calculating.At present, common way adopts single shaft computing method, and its result of calculation differs larger with the actual life of vehicle frame.And there is Various Complex operating mode in vehicle frame in real work, as car brakeing, turn to, tumble, reverse, the complex working condition such as the rotation of rotary table of multi-freedom-degree vibration, special vehicle, and the load of each load working condition is all that single shaft fatigue is insurmountable, stressing conditions is complicated, tired operating mode is many, needs to set up a kind of hyperchannel multiaxial loading carry out fatigue mechanisms for these features.The Calculation of Fatigue Life of vehicle frame under complex working condition is to rationally distributed property, the local optimum great significance for design of correct assessment vehicle frame.Key fatigue lifetime calculating vehicle frame complex working condition is that operating mode definition and fatigue load size, load mode set.But in the prior art, the secrecy technology that the arranging of fatigue load spectrum all belongs to vehicle development unit and will not disclosing, exists and repeats research and development problem, be unfavorable for saving resource and promote social progress.
Summary of the invention
The object of the invention is for the deficiencies in the prior art, a kind of vehicle frame complex working condition non-proportional loading computing method comprising welding analog are provided, the method is arranged by rational welding analog and appropriate complex working condition non-proportional loading load, improve the accuracy of Calculation of Fatigue Life, open and the application of these computing method, can avoid repeating research and development, be beneficial to saving resource and promote social progress.
For realizing aforementioned object, the present invention adopts following technical scheme.
Comprise vehicle frame complex working condition non-proportional loading computing method for welding analog, comprise the following steps:
S1, welding unit and structural unit grouping: the space coordinates of setting X, Y, Z and true origin, and welding unit and structural unit are divided into groups;
S2, finite element welding analog: finite element welding analog is carried out to board welding and curved surface welding in fillet weld mode; Wherein, welding unit adopts quadrilateral mesh, and the grid length of side is 3 ~ 5mm; The angularity of grid is less than 5%; Weld seam layer triangle-free unit; The grid cell intermediate cam shape number of grid accounting being welded to connect layer adjoined with weld seam layer is less than 5%;
S3, complex working condition defines: comprise definition fatigue load and fatigue and cyclic operating mode; Described fatigue load comprises the size of load, direction and loading position; Described fatigue and cyclic operating mode comprises the tired operating mode of tilting moment, S shape turns to tired operating mode of tumbling, continuously braking to tumble any one in tired operating mode, torsional fatigue operating mode, the tired operating mode of multi-freedom-degree vibration;
S4, multiaxis is set up: according to defined fatigue load and fatigue and cyclic operating mode set up at least two fatigue lifetime axle;
S5, non-proportional loading calculates: axle fatigue lifetime pressed defined complex working condition He set up, employing Calculation of Fatigue Life software, sets up the calculating passage corresponding with number of axle fatigue lifetime and carries out the hyperchannel non-proportional loading life-span and calculate; Comprise and welding unit and structural unit are divided into groups again, select tired algorithm, definition material surface parameter, definition planar residual stress and height cycle facigue life-span, carry out weld seam and solder joint unit fatigue lifetime and structural strength Calculation of Fatigue Life according to computing rule; Wherein, weld seam and solder joint unit fatigue mechanisms rule select BS weld life (CP) algorithm; Structural strength fatigue mechanisms rule selects " depending on structured material " algorithm.
Adopt the present invention of preceding solution, by carrying out finite element analogy and complex working condition definition to welding unit, under complex working condition fatigue load size, direction, loading position setting after, set up multiple calculating passage and adopt Calculation of Fatigue Life software to carry out the hyperchannel non-proportional loading life-span and calculate.Wherein, described complex working condition comprises the tired operating mode of tilting moment, S shape turns to tired operating mode of tumbling, brake tired operating mode of tumbling, torsional fatigue operating mode, the tired operating mode of multi-freedom-degree vibration etc. continuously.These computing method effectively can improve the accuracy of vehicle frame analog computation fatigue lifetime, meanwhile, by the method openly can avoid repeat research and development, be beneficial to saving resource and promote social progress.
Preferably, the initiating terminal of described fillet weld holds mesh free warpage unit and triangular mesh unit with ending.In order to ensure the consistance that welding is transmitted; The sideline of best weld seam layer grid as far as possible be welded to connect layer and keep straight, do not form certain angle.Triangular element is not comprised, distortion warpage unit at the head be welded to connect and afterbody.
Preferably, described tilting moment fatigue load is made up of vertical load, chassis equivalent load and space tilting moment; Described tilting moment fatigue load size, direction and loading position determine to comprise setting vertical load, the size of chassis equivalent load, direction and application point, the size of setting space tilting moment and loading area; Described vertical load size for the vertical component of vehicle frame institute bearing load, load(ing) point be frame mass centre; Described chassis equivalent load size is vehicle frame and annex gross weight, and load(ing) point is determined according to body frame structure for automotive; Described space tilting moment size is determined for being obtained mechanics parameter by dynamic analysis or rule of thumb calculating, and its application point overlaps with the load(ing) point of vertical load; The tired operating mode of described tilting moment comprises tumble form operating mode and space tilting moment loading condition; Described form operating mode of tumbling comprises that front-right is tumbled, tumble in right back, tumble in dead astern, tumble in left back, front-left is tumbled; Described space tilting moment loading condition comprises by following state of cyclic operation: operating mode one, from front-right through right back to dead astern, then return front-right in reverse order; Operating mode two, from front-left through left back to dead astern, then return front-left in reverse order; Operating mode three, from front-right through right back, dead astern, left back to front-left, then return front-right in reverse order; Operating mode four, from right back through dead astern to left back, then return to positive right back in reverse order; Operating mode five, from right back through dead astern, then returns to right back; Described foundation of tumbling operating mode multiaxis comprise first by flywheel moment to a certain plane projection, then split axle is carried out according to the quantity of projection angle, space tilting moment application point and acting force load, wherein, vertical load is an axle, chassis equivalent load is an axle, and space tilting moment is divided into disalignment according to the loading condition of different angle of revolution; Wherein, when calculating tumbled by simulation car load, by X, Y, Z tri-freedom of axial movement constraints of bottom of frame corner, vehicle frame bottom surface and ground distance are 0.5m, simultaneously, by the space vector of space tilting moment to XY face, YZ face and ZX face project, with the vector correlation synthesis Sum decomposition of the axle will defined according to angle of revolution by moment.By the tired operating mode of the tilting moment of multiple complexity of simulated frame, and fatigue load is quantitatively located, to obtain tilting moment Calculation of Fatigue Life result accurately, be applicable to the tilting moment Calculation of Fatigue Life of the special vehicle vehicle frame of straight frame and band panoramic table.
Preferably, described S shape turns to the fatigue load size of tired operating mode of tumbling, direction, loading position to be, tire force and moment parameter equivalent when being carried out simulating obtained turning to by snakelike test or many-body dynamics software is carried in the junction of tire and suspension and vehicle frame, comprise force and moment totally eight load that are left front, right front, right back, left rear wheel; Described S shape turns to tired operating mode of tumbling to comprise following state of cyclic operation, operating mode one, from the right-hand rotation limit through middle to limit on the left position; Operating mode two, gets back to meta to right-hand rotation extreme position from left-hand rotation extreme position; Operating mode three, from right-hand rotation extreme position to meta to left-hand rotation extreme position, finally gets back to again right-hand rotation extreme position; Operating mode four, from meta to right-hand rotation extreme position, returns meta and gets back to meta to left-hand rotation extreme position; Operating mode five, from meta to left-hand rotation extreme position, returns meta and returns meta to right-hand rotation extreme position; Describedly the tired number of axle is turned to be 12 times of vehicle bridge number, corresponding with the projection of force and moment in XY, YZ and XZ tri-planes of vehicle bridge left and right sides tire respectively.Tired operating mode of tumbling is turned to by the S shape of multiple complexity of simulated frame, and fatigue load is quantitatively located, turn to obtain S shape accurately Calculation of Fatigue Life result of tumbling, the S shape being applicable to the special vehicle vehicle frame of straight frame and band panoramic table turns to Calculation of Fatigue Life of tumbling.
Preferably, the tumble fatigue load size of tired operating mode, direction, loading position of described continuous braking is, for by left front, right front, the mechanics parameter of right back, left rear wheel damping force and braking moment totally eight load is carried in the link position of vehicle frame and suspension, and ensures power, moment to be correctly delivered on whole vehicle frame; Described continuous braking tired operating mode of tumbling is the tired operating mode that bridge on-position and Vehicle Speed combine with the combination of brake pressure; Described bridge on-position comprises propons foot brake, back axle braking and full-bridge braking; Described Vehicle Speed comprises high speed, middling speed and low speed; Described brake pressure comprises light braking and braking with all strength; Described bridge on-position comprises, operating mode one, and propons foot brake, back axle braking and full-bridge braking are carried out in circulation; Operating mode two, hocket propons foot brake and back axle braking; Operating mode three, hocket propons foot brake and full-bridge braking; Operating mode four, the back axle that hockets braking and full-bridge braking; The combination of described Vehicle Speed and brake pressure comprises, operating mode one, and hocket light braking at a high speed and braking with all strength at a high speed; Operating mode two, the middling speed that hockets gently is braked and middling speed braking with all strength; Operating mode three, the low speed that hockets gently is braked and low speed braking with all strength; Operating mode four, high speed gently braking is carried out in circulation, middling speed is gently braked and low speed is gently braked; Operating mode five, braking and the low speed braking with all strength with all strength of high speed braking with all strength, middling speed is carried out in circulation; High speed in described Vehicle Speed, middling speed and low speed are respectively 75 ~ 85Km/h, 55 ~ 65Km/h and 25 ~ 35Km/h; The brake pressure of described light braking and braking is with all strength respectively 2.5 ~ 4.5bar and 6.0 ~ 7.5bar; The described continuous braking tired number of axle of tumbling is 6 times of tire number, corresponding with the projection of space vector in XY, YZ and XZ tri-planes of force and moment respectively.By the tired operating mode of the braking of multiple complexity of simulated frame, and fatigue load is quantitatively located, brake Calculation of Fatigue Life result accurately to obtain, be applicable to the braking Calculation of Fatigue Life of the special vehicle vehicle frame of straight frame and band panoramic table.Wherein, propons foot brake refers to the vehicle foot brake situation when back axle brake fade; Back axle braking refers to the vehicle foot brake situation when propons foot brake lost efficacy.
Preferred further, the high speed in described Vehicle Speed, middling speed and low speed are respectively 80Km/h, 60Km/h and 30Km/h; The brake pressure of described light braking and braking is with all strength respectively 3 ~ 4bar and 6.5 ~ 7bar.To obtain result of calculation more accurately further.
Preferably, described torsional fatigue magnitude of load, direction, loading position comprise the X, Y, Z axis six-freedom degree retraining vehicle frame two longeron rear end, the Z axis one-movement-freedom-degree of constraint vehicle frame medium position; At two tie point places that front end first crossbeam and vehicle frame two longeron are formed respectively, load two respectively perpendicular to the contrary power in vehicle frame upper surface equal and opposite in direction direction, wherein the size of power is determined for being obtained mechanics parameter by dynamic analysis or rule of thumb calculating; Described torsional fatigue operating mode be two acting forces in alternating directions; The multiaxis of described foundation is the diaxon corresponding with two acting forces.By the torsional fatigue operating mode of multiple complexity of simulated frame, and quantitatively locate fatigue load, to obtain torsional fatigue life result of calculation accurately, the torsional fatigue life being applicable to the special vehicle vehicle frame of straight frame and band panoramic table calculates.
Preferably, described multi-freedom-degree vibration fatigue load loaded position comprises the multiple point of excitation except center of gravity; The displacement spectra at the corresponding point of excitation place that the size and Orientation of described load is obtained by platform experiment or acceleration spectrum; Described load working condition is, to 1/4 cycle from 0, then to 1/2 cycle, finally to the state of cyclic operation of 1 end cycle; The number of described multiaxis is encourage three extraordinarily two that count, respectively the vertical load of the projection of corresponding point of excitation load in XY, YZ and XZ tri-planes and center of gravity and moment.By the tired operating mode of the multi-freedom-degree vibration of multiple complexity of simulated frame, and fatigue load is quantitatively located, to obtain multi-freedom-degree vibration Calculation of Fatigue Life result accurately, be applicable to the multi-freedom-degree vibration Calculation of Fatigue Life of the special vehicle vehicle frame of straight frame and band panoramic table.
Preferred further, the multi-axial type of described multi-freedom-degree vibration is displacement load; The excitation of described load is counted and position is determined according to body frame structure for automotive form; Wherein, the point of excitation of straight frame is 6 ~ 10; Integral frame is then by the principle that each surface of vehicle frame all covers, and the quantity of point of excitation is no less than 2 times of the limit number sum forming each surface.Be convenient to the applying obtaining fatigue load parameter and fatigue load more accurately, and for the version of different vehicle frame, determine that the excitation of multi-freedom-degree vibration fatigue is counted, guarantee the accuracy of multi-freedom-degree vibration Calculation of Fatigue Life result further.
Further, described point of excitation comprises the left front point of vehicle frame, right front point, left back point, right back point, left front portion mid point, right front portion mid point, vehicle frame middle beam mid point.By limiting point of excitation position, further guarantee the accuracy of multi-freedom-degree vibration Calculation of Fatigue Life result.
The invention has the beneficial effects as follows, arranged by rational welding analog and appropriate complex working condition non-proportional loading load, improve the accuracy of Calculation of Fatigue Life, disclosing of the method, can avoid repeating research and development, be beneficial to saving resource and promote social progress.
Accompanying drawing explanation
Fig. 1 is process flow diagram of the present invention.
Fig. 2 is the model configuration schematic diagram of A, B two sheet material overlap joints welding in the present invention, and the dash area in figure is weld seam.
Fig. 3 is the grid schematic diagram of sheet material welding analog in the present invention, and in figure, the grid of dash area is weld seam layer grid, and the grid be close to weld seam layer grid is for being welded to connect a layer grid.
Fig. 4 is the grid schematic diagram of the curved surface welding analog on C, D two faces of cylinder in the present invention, and in figure, the grid of dash area is weld seam layer grid, and the grid be close to weld seam layer grid is for being welded to connect a layer grid.
Fig. 5 is the effect schematic diagram of mean camber welding analog of the present invention.
Fig. 6 is tilting moment load fatigue operating mode orientation schematic diagram in the present invention.
Fig. 7 is the vehicle frame space tilting moment loading position schematic diagram of special vehicle in the present invention.
Fig. 8 is the vehicle frame upper unit turning circle schematic diagram of special vehicle in figure of the present invention.
Fig. 9 is the straight frame space tilting moment loading position schematic diagram of general heavy goods vehicles in the present invention.
Figure 10 is that in the present invention, S shape turns to tumble tired operating mode and multiaxis distribution schematic diagram.
Figure 11 brakes tumble tired operating mode and multiaxis distribution schematic diagram in the present invention.
Figure 12 is torsional fatigue operating mode and multiaxis distribution schematic diagram in the present invention.
Figure 13 is the point of excitation distribution plan of the tired operating mode of multi-freedom-degree vibration of straight frame in the present invention.
Embodiment
Below in conjunction with accompanying drawing, the present invention is further illustrated, but therefore do not limit the present invention among described scope of embodiments.
Embodiment 1, a kind of vehicle frame tilting moment tired complex working condition non-proportional loading computing method comprising welding analog, comprise the following steps:
S1, welding unit and structural unit grouping: the space coordinates of setting X, Y, Z and true origin, and welding unit and structural unit are divided into groups;
S2, finite element welding analog: finite element welding analog is carried out to board welding and curved surface welding in fillet weld mode; Wherein, welding unit adopts quadrilateral mesh, and the grid length of side is 3 ~ 5mm; The angularity of grid is less than 5%; Weld seam layer triangle-free grid, the grid cell intermediate cam shape number of grid accounting being welded to connect layer adjoined with weld seam layer is less than 5%; The initiating terminal of optimum angle weld seam and ending end mesh free warpage unit and triangular mesh unit, the sideline of weld seam layer grid be welded to connect layer and keep straight, do not want angulation;
S3, complex working condition defines: comprise definition tilting moment fatigue load and tilting moment fatigue and cyclic operating mode; Described fatigue load comprises the size of load, direction and loading position; Described tilting moment fatigue load is made up of vertical load, chassis equivalent load and space tilting moment; Described tilting moment fatigue load size, direction and loading position determine to comprise setting vertical load, the size of chassis equivalent load, direction and application point, the size of setting space tilting moment and loading area; Described vertical load size for the vertical component of vehicle frame institute bearing load, load(ing) point be frame mass centre; Described chassis equivalent load size is vehicle frame and annex gross weight, and load(ing) point is determined according to body frame structure for automotive; The center of gravity of general chassis equivalent load and vertical load is not at same position, and described space tilting moment size is determined for being obtained mechanics parameter by dynamic analysis or rule of thumb calculating, and its application point overlaps with the load(ing) point of vertical load; The tired operating mode of described tilting moment comprises tumble form operating mode and space tilting moment loading condition; Describedly tumble that the form operating mode front-right comprised as shown in Figure 6 is tumbled, tumble in right back, tumbling in dead astern, tumbles in left back, front-left is tumbled; Described space tilting moment loading condition comprises by following state of cyclic operation: operating mode one, from front-right through right back to dead astern, then return front-right in reverse order; Operating mode two, from front-left through left back to dead astern, then return front-left in reverse order; Operating mode three, from front-right through right back, dead astern, left back to front-left, then return front-right in reverse order; Operating mode four, from right back through dead astern to left back, then return to positive right back in reverse order; Operating mode five, from right back through dead astern, then returns to right back;
For in such as Fig. 7, there is a rigidly connected circular race vehicle frame center of special vehicle, the centre of gyration is X, Y, Z axis true origin, the space tilting moment of circulation is applied, at applying chassis, the position equivalent load away from centre of gyration position heart certain distance in the centre of gyration position of seat ring; Wherein, space tilting moment is that vehicle frame is being subject to a kind of a kind of moment that can cause vehicle rollover of dangerous working condition; Because special vehicle vehicle frame needs carrying and freight handling, therefore, need the revolution carrying out vehicle frame upper unit, turning circle rotates clockwise past vehicle frame dead astern to the positive left field of vehicle frame in the positive right side area of vehicle frame, the turning circle between as shown in Figure 80 ° to 180 °; Special vehicle is owing to bearing revolution, carrying function, therefore suffered tilting moment is larger, particularly in figure, in 45 ° ~ 135 ° reciprocation cycle, fatigue load is particularly outstanding, therefore this angular regions is must calculate in fatigue load in the design of endless loop region;
For heavy type vehicle as Fig. 9, general heavy type vehicle is straight frame, it is identical that its fatigue load applying mode and special vehicle fatigue load apply mode, and difference is that suffered space tilting moment is less than special vehicle, but load applying mode still can be used for reference; General heavy type vehicle frame fatigue load comprises vertical load, chassis equivalent load and space tilting moment; Owing to there is not the centre of gyration of special vehicle in applying mode, so the vehicle frame stage casing centre of gravity place of general heavy type vehicle frame is between the 4th crossbeam the 5th crossbeam, and be rigidly connected with the side bar of around both sides, the mobile constraint of X, Y, Z tri-axis is carried out in the rear and front end of vehicle frame; Then apply vertical load at center of gravity place, in distance, center of gravity 200 ~ 300mm place applies chassis equivalent load, applies space tilting moment according to mode in Fig. 8;
S4, multiaxis is set up: set up according to defined tilting moment fatigue load and tilting moment fatigue and cyclic operating mode the multiple calculating axle of operating mode of tumbling, specifically, first by flywheel moment to a certain plane projection, then carry out split axle according to the quantity of projection angle, space tilting moment application point and acting force load, wherein, vertical load is an axle, chassis equivalent load is an axle, and space tilting moment is divided into disalignment according to the loading condition of different angle of revolution; When calculating tumbled by simulation car load, by X, Y, Z tri-freedom of axial movement constraints of bottom of frame corner, vehicle frame bottom surface and ground distance are 0.5m, simultaneously, by the space vector of space tilting moment to XY face, YZ face and ZX face project, with the vector correlation synthesis Sum decomposition of the axle will defined according to angle of revolution by moment;
S5, non-proportional loading calculates: multiple tilting moment axles fatigue lifetime pressed the tired operating mode of defined tilting moment and set up, adopt Calculation of Fatigue Life software, sets up the calculating passage corresponding with number of axle fatigue lifetime and carries out the hyperchannel non-proportional loading life-span and calculate; Comprise and welding unit and structural unit are divided into groups again, select tired algorithm, definition material surface parameter, definition planar residual stress and height cycle facigue life-span, carry out weld seam and solder joint unit fatigue lifetime and structural strength Calculation of Fatigue Life according to computing rule;
Wherein, weld seam and solder joint unit fatigue mechanisms rule select BS weld life (CP) algorithm; Weld layer and weld seam are carried out classification by this algorithm, need the thickness of input welding, welding grade (B-W) level, and default level F level can be selected also can to need to select according to different designs, and welding unit thickness is selected according to design standards; Structural strength fatigue mechanisms rule selects " depending on structured material " algorithm, finally structural unit as main analytic target, and is defined as analysis references object by welding unit, weld seam unit, namely not using tired for structural unit as main basis; Definition material surface parameter, the definition of material surface parameter is inaccurate, and the fatigue mechanisms life-span can differ decades of times.Because the breakage on top layer causes time fatigue mechanisms is initial, wait the stage through surface crack-crack growth-fracture.The roughness of different materials to be defined before calculating fatigue.Roughness can be chosen in following scope, minute surface (roughness is very little)-Ra≤0.25um; 0.25 < Ra≤0.6um; 0.6 < Ra≤1.6um; 1.6 < Ra≤4um, are divided into 8 grades available, and last grade roughness is Ra>=75um; Material surface parameter can also be tried to achieve by accurate Calculation except can selecting roughness, and by roughness calculated value, is imparted in material surface parameter list; Planar residual stress defines, calculate the tired planar residual stress needing definition structure, some structures are in the fabrication process owing to being subject to the Effect and impact of various processing technology, certain unrelieved stress can be there is in structure, in finite element fatigue mechanisms, this value selects acquiescence equilibrium value, namely thinks that residual stress does not have an impact to fatigue or structure does not exist residual stress; The high and low cycle fatigue life-span defines, and fatigue lifetime, definition was according to designed life, when calculating tired, fatigue was defined as low-cycle fatigue 1 ~ 10
3secondary, high cycle fatigue 10
3-10
6or infinite life 10
6~ ∞; Parameter designed life is defined as 2N by the type according to calculating, and wherein N is cycle index designed life.
Embodiment 2, a kind of S shape comprising welding analog turns to tired complex working condition non-proportional loading computing method of tumbling, and comprises S1 welding unit and structural unit grouping; S2 finite element welding analog; S3 complex working condition defines; The step that S4 multiaxis is set up and S5 non-proportional loading calculates;
Wherein, complex working condition defines, and comprises definition S shape and turns to tumble fatigue load and fatigue and cyclic operating mode; Described fatigue load comprises the size of load, direction and loading position; Described S shape turns to the load parameter such as fatigue load size, direction, loading position of tired operating mode of tumbling can be obtained the attitude parameter of car load by snakelike test, i.e. pitching, lateral thrust angle, tilting moment and acceleration parameter; Also analog parameter acquisition can be carried out by many-body dynamics software; And tire force and moment parameter equivalent during obtained turning to is carried in the junction of tire and suspension and vehicle frame, comprise left front, right front, force and moment totally eight load of right back, left rear wheel, FA, MA, FB, MB, FC, MC, FD, MD respectively in corresponding Figure 10; Described S shape turns to tired operating mode of tumbling to comprise following state of cyclic operation, operating mode one as shown in Figure 10, from the right-hand rotation limit through middle to limit on the left position; Operating mode two, gets back to meta to right-hand rotation extreme position from left-hand rotation extreme position; Operating mode three, from right-hand rotation extreme position to meta to left-hand rotation extreme position, finally gets back to again right-hand rotation extreme position; Operating mode four, from meta to right-hand rotation extreme position, returns meta and gets back to meta to left-hand rotation extreme position; Operating mode five, from meta to left-hand rotation extreme position, returns meta and returns meta to right-hand rotation extreme position; Describedly the tired number of axle is turned to be 12 times of vehicle bridge number, corresponding with the projection of vehicle bridge left and right sides force and moment (i.e. FA, MA, FB, MB, FC, MC, FD, MD) in XY, YZ and XZ tri-planes respectively.If exist certain axially stressed the or moment of institute be 0, then the projection of its three coordinate axis is also 0.Determine that multiaxis definition accurately calculates tired key, only have many axial directions and vector definition accurately can carry out non-proportional loading calculating.
Non-proportional loading calculates: turn to tired operating mode of tumbling to turn to multiple S shapes of setting up axle fatigue lifetime of tumbling by defined S shape, adopt Calculation of Fatigue Life software, set up the calculating passage corresponding with number of axle fatigue lifetime and carry out the hyperchannel non-proportional loading life-span and calculate.
The content of all the other steps in the present embodiment is identical with embodiment 1, does not repeat them here.
Embodiment 3, a kind of continuous braking comprising welding analog is tumbled tired complex working condition non-proportional loading computing method, comprises S1 welding unit and structural unit grouping; S2 finite element welding analog; S3 complex working condition defines; The step that S4 multiaxis is set up and S5 non-proportional loading calculates;
Wherein, complex working condition defines, and comprises definition S shape and turns to tumble fatigue load and fatigue and cyclic operating mode; Described fatigue load comprises the size of load, direction and loading position; Wherein, the tumble fatigue load size of tired operating mode, direction, loading position of continuous braking is, for by left front, right front, the mechanics parameter of right back, left rear wheel damping force and braking moment totally eight load is carried in the link position of vehicle frame and suspension, and ensure power, moment to be correctly delivered on whole vehicle frame, FA, MA, FB, MB, FC, MC, FD, MD respectively in corresponding Figure 11; Wherein mechanics parameter can carry out analog parameter acquisition by many-body dynamics software; Described continuous braking tired operating mode of tumbling is the tired operating mode that bridge on-position and Vehicle Speed combine with the combination of brake pressure; Described bridge on-position comprises propons foot brake, back axle braking and full-bridge braking; Described Vehicle Speed comprises high speed, middling speed and low speed; Described brake pressure comprises light braking and braking with all strength; Described bridge on-position comprises, operating mode one, and propons foot brake, back axle braking and full-bridge braking are carried out in circulation; Operating mode two, hocket propons foot brake and back axle braking; Operating mode three, hocket propons foot brake and full-bridge braking; Operating mode four, the back axle that hockets braking and full-bridge braking; The combination of described Vehicle Speed and brake pressure comprises, operating mode one, and hocket light braking at a high speed and braking with all strength at a high speed; Operating mode two, the middling speed that hockets gently is braked and middling speed braking with all strength; Operating mode three, the low speed that hockets gently is braked and low speed braking with all strength; Operating mode four, high speed gently braking is carried out in circulation, middling speed is gently braked and low speed is gently braked; Operating mode five, braking and the low speed braking with all strength with all strength of high speed braking with all strength, middling speed is carried out in circulation; High speed in described Vehicle Speed, middling speed and low speed are respectively 75 ~ 85Km/h, 55 ~ 65Km/h and 25 ~ 35Km/h; The brake pressure of described light braking and braking is with all strength respectively 2.5 ~ 4.5bar and 6.0 ~ 7.5bar; The described continuous braking tired number of axle of tumbling is 12 times of vehicle bridge number, corresponding with the projection of space vector in XY, YZ and XZ tri-planes of the force and moment of vehicle bridge left and right sides tire respectively.If exist certain axially stressed the or moment of institute be 0, then the projection in its three coordinate axis is also 0.Determine that multiaxis definition accurately calculates tired key, only have many axial directions and vector definition accurately can carry out non-proportional loading calculating.
Wherein, propons foot brake refers to the vehicle foot brake situation when back axle brake fade; Back axle braking refers to the vehicle foot brake situation when propons foot brake lost efficacy; High speed in Vehicle Speed, middling speed and low speed are preferably respectively 80Km/h, 60Km/h and 30Km/h; The brake pressure of light braking and braking with all strength is preferably respectively 3 ~ 4bar and 6.5 ~ 7bar.
The content of all the other steps in the present embodiment is identical with embodiment 1, does not repeat them here.
Embodiment 4, a kind of torsional fatigue complex working condition non-proportional loading computing method comprising welding analog, comprise S1 welding unit and structural unit grouping; S2 finite element welding analog; S3 complex working condition defines; The step that S4 multiaxis is set up and S5 non-proportional loading calculates;
Wherein, complex working condition defines, and comprises definition torsional fatigue load and fatigue and cyclic operating mode; Described torsional fatigue magnitude of load, direction, loading position comprise the X, Y, Z axis six-freedom degree retraining vehicle frame two longeron rear end, the Z axis one-movement-freedom-degree of constraint vehicle frame medium position; At two tie point places that front end first crossbeam and vehicle frame two longeron are formed respectively, load two respectively perpendicular to the contrary power in vehicle frame upper surface equal and opposite in direction direction, as FA and FB in Figure 12, wherein FA is forward, and FB is reverse; The size of power is determined for being obtained mechanics parameter by dynamic analysis or rule of thumb calculating; Described torsional fatigue operating mode be two acting forces in alternating directions; The multiaxis of described foundation is the diaxon corresponding with two directed force F A and FB.
The content of all the other steps in the present embodiment is identical with embodiment 1, does not repeat them here.
Embodiment 5, a kind of multi-freedom-degree vibration tired complex working condition non-proportional loading computing method comprising welding analog, comprise S1 welding unit and structural unit grouping; S2 finite element welding analog; S3 complex working condition defines; The step that S4 multiaxis is set up and S5 non-proportional loading calculates;
Wherein, complex working condition defines, and comprises definition multi-freedom-degree vibration fatigue load and fatigue and cyclic operating mode; Described multi-freedom-degree vibration fatigue load loaded position comprises the multiple point of excitation except center of gravity; The displacement spectra at the corresponding point of excitation place that the size and Orientation of described load is obtained by platform experiment; Described load working condition is, to 1/4 cycle from 0, then to 1/2 cycle, finally to the state of cyclic operation of 1 end cycle; The number of described multiaxis is encourage three extraordinarily two that count, respectively the vertical load of the projection of corresponding point of excitation load in XY, YZ and XZ tri-planes and center of gravity and moment; The multi-axial type of described multi-freedom-degree vibration is displacement load; The excitation of described load is counted and position such as the point of excitation of the straight frame in the present embodiment Figure 13 is 6 ~ 10; Comprise the left front point 1 of vehicle frame, right front point 2, left back point 3, right back point 4, left front portion mid point 5, right front portion mid point 6, be positioned at the 3rd crossbeam mid point 7 totally 7 point of excitation in the middle part of vehicle frame.
The acceleration load of the acceleration spectrum at the corresponding point of excitation place that the load in the present embodiment is also obtained by platform experiment.
The content of all the other steps in the present embodiment is identical with embodiment 1, does not repeat them here.
Embodiment 6, a kind of multi-freedom-degree vibration tired complex working condition non-proportional loading computing method comprising welding analog, comprise S1 welding unit and structural unit grouping; S2 finite element welding analog; S3 complex working condition defines; The step that S4 multiaxis is set up and S5 non-proportional loading calculates;
The number of described multiaxis is encourage three extraordinarily two that count, respectively the vertical load at the unit frame rotation of rotary table center of special vehicle and moment in the projection of corresponding point of excitation load in XY, YZ and XZ tri-planes and the present embodiment; The principle that the excitation of described load is counted and position all covers by each surface of vehicle frame, and the quantity of point of excitation is no less than 2 times of the limit number sum forming each surface.
The content of all the other steps in the present embodiment is identical with embodiment 5, does not repeat them here.
More than describe preferred embodiment of the present invention in detail.Should be appreciated that those of ordinary skill in the art just design according to the present invention can make many modifications and variations without the need to creative work.Therefore, all technician in the art, all should by the determined protection domain of claims under this invention's idea on the basis of existing technology by the available technical scheme of logical analysis, reasoning, or a limited experiment.
Claims (10)
1. comprise vehicle frame complex working condition non-proportional loading computing method for welding analog, it is characterized in that, comprise the following steps:
S1, welding unit and structural unit grouping: the space coordinates of setting X, Y, Z and true origin, and welding unit and structural unit are divided into groups;
S2, finite element welding analog: finite element welding analog is carried out to board welding and curved surface welding in fillet weld mode; Wherein, welding unit adopts quadrilateral mesh, and the grid length of side is 3 ~ 5mm; The angularity of grid is less than 5%; Weld seam layer triangle-free grid; The grid cell intermediate cam shape number of grid accounting being welded to connect layer adjoined with weld seam layer is less than 5%;
S3, complex working condition defines: comprise definition fatigue load and fatigue and cyclic operating mode; Described fatigue load comprises the size of load, direction and loading position; Described fatigue and cyclic operating mode comprises the tired operating mode of tilting moment, S shape turns to tired operating mode of tumbling, continuously braking to tumble any one in tired operating mode, torsional fatigue operating mode, the tired operating mode of multi-freedom-degree vibration;
S4, multiaxis is set up: according to defined fatigue load and fatigue and cyclic operating mode set up at least two fatigue lifetime axle;
S5, non-proportional loading calculates: axle fatigue lifetime pressed defined complex working condition He set up, employing Calculation of Fatigue Life software, sets up the calculating passage corresponding with number of axle fatigue lifetime and carries out the hyperchannel non-proportional loading life-span and calculate; Comprise and welding unit and structural unit are divided into groups again, select tired algorithm, definition material surface parameter, definition planar residual stress and height cycle facigue life-span, carry out weld seam and solder joint unit fatigue lifetime and structural strength Calculation of Fatigue Life according to computing rule; Wherein, weld seam and solder joint unit fatigue mechanisms rule select BS weld life (CP) algorithm; Structural strength fatigue mechanisms rule selects " depending on structured material " algorithm.
2. the vehicle frame complex working condition non-proportional loading computing method comprising welding analog according to claim 1, is characterized in that, initiating terminal and the ending of described fillet weld hold mesh free warpage unit and triangular mesh unit.
3. the vehicle frame complex working condition non-proportional loading computing method comprising welding analog according to claim 1 and 2, it is characterized in that, described tilting moment fatigue load is made up of vertical load, chassis equivalent load and space tilting moment; Described tilting moment fatigue load size, direction and loading position determine to comprise setting vertical load, the size of chassis equivalent load, direction and application point, the size of setting space tilting moment and loading area; Described vertical load size for the vertical component of vehicle frame institute bearing load, load(ing) point be frame mass centre; Described chassis equivalent load size is vehicle frame and annex gross weight, and load(ing) point is determined according to body frame structure for automotive; Described space tilting moment size is determined for being obtained mechanics parameter by dynamic analysis or rule of thumb calculating, and its application point overlaps with the load(ing) point of vertical load; The tired operating mode of described tilting moment comprises tumble form operating mode and space tilting moment loading condition; Described form operating mode of tumbling comprises that front-right is tumbled, tumble in right back, tumble in dead astern, tumble in left back, front-left is tumbled; Described space tilting moment loading condition comprises by following state of cyclic operation: operating mode one, from front-right through right back to dead astern, then return front-right in reverse order; Operating mode two, from front-left through left back to dead astern, then return front-left in reverse order; Operating mode three, from front-right through right back, dead astern, left back to front-left, then return front-right in reverse order; Operating mode four, from right back through dead astern to left back, then return to positive right back in reverse order; Operating mode five, from right back through dead astern, then returns to right back; Described foundation of tumbling operating mode multiaxis comprise first by flywheel moment to a certain plane projection, then split axle is carried out according to the quantity of projection angle, space tilting moment application point and acting force load, wherein, vertical load is an axle, chassis equivalent load is an axle, and space tilting moment is divided into disalignment according to the loading condition of different angle of revolution; Wherein, when calculating tumbled by simulation car load, by X, Y, Z tri-freedom of axial movement constraints of bottom of frame corner, vehicle frame bottom surface and ground distance are 0.5m, simultaneously, by the space vector of space tilting moment to XY face, YZ face and ZX face project, with the vector correlation synthesis Sum decomposition of the axle will defined according to angle of revolution by moment.
4. the vehicle frame complex working condition non-proportional loading computing method comprising welding analog according to claim 1 and 2, it is characterized in that, described S shape turns to the fatigue load size of tired operating mode of tumbling, direction, loading position to be, tire force and moment parameter equivalent when being carried out simulating obtained turning to by snakelike test or many-body dynamics software is carried in the junction of tire and suspension and vehicle frame, comprise force and moment totally eight load that are left front, right front, right back, left rear wheel; Described S shape turns to tired operating mode of tumbling to comprise following state of cyclic operation, operating mode one, from the right-hand rotation limit through middle to limit on the left position; Operating mode two, gets back to meta to right-hand rotation extreme position from left-hand rotation extreme position; Operating mode three, from right-hand rotation extreme position to meta to left-hand rotation extreme position, finally gets back to again right-hand rotation extreme position; Operating mode four, from meta to right-hand rotation extreme position, returns meta and gets back to meta to left-hand rotation extreme position; Operating mode five, from meta to left-hand rotation extreme position, returns meta and returns meta to right-hand rotation extreme position; Describedly the tired number of axle is turned to be 12 times of vehicle bridge number, corresponding with the projection of force and moment in XY, YZ and XZ tri-planes of vehicle bridge left and right sides tire respectively.
5. the vehicle frame complex working condition non-proportional loading computing method comprising welding analog according to claim 1 and 2, it is characterized in that, the tumble fatigue load size of tired operating mode, direction, loading position of described continuous braking is, for by left front, right front, the mechanics parameter of right back, left rear wheel damping force and braking moment totally eight load is carried in the link position of vehicle frame and suspension, and ensures power, moment to be correctly delivered on whole vehicle frame; Described continuous braking tired operating mode of tumbling is the tired operating mode that bridge on-position and Vehicle Speed combine with the combination of brake pressure; Described bridge on-position comprises propons foot brake, back axle braking and full-bridge braking; Described Vehicle Speed comprises high speed, middling speed and low speed; Described brake pressure comprises light braking and braking with all strength; Described bridge on-position comprises, operating mode one, and propons foot brake, back axle braking and full-bridge braking are carried out in circulation; Operating mode two, hocket propons foot brake and back axle braking; Operating mode three, hocket propons foot brake and full-bridge braking; Operating mode four, the back axle that hockets braking and full-bridge braking; The combination of described Vehicle Speed and brake pressure comprises, operating mode one, and hocket light braking at a high speed and braking with all strength at a high speed; Operating mode two, the middling speed that hockets gently is braked and middling speed braking with all strength; Operating mode three, the low speed that hockets gently is braked and low speed braking with all strength; Operating mode four, high speed gently braking is carried out in circulation, middling speed is gently braked and low speed is gently braked; Operating mode five, braking and the low speed braking with all strength with all strength of high speed braking with all strength, middling speed is carried out in circulation; High speed in described Vehicle Speed, middling speed and low speed are respectively 75 ~ 85Km/h, 55 ~ 65Km/h and 25 ~ 35Km/h; The brake pressure of described light braking and braking is with all strength respectively 2.5 ~ 4.5bar and 6.0 ~ 7.5bar; The described continuous braking tired number of axle of tumbling is 12 times of vehicle bridge number, corresponding with the projection of space vector in XY, YZ and XZ tri-planes of the force and moment of vehicle bridge left and right sides tire respectively.
6. the vehicle frame complex working condition non-proportional loading computing method comprising welding analog according to claim 5, it is characterized in that, the high speed in described Vehicle Speed, middling speed and low speed are respectively 80Km/h, 60Km/h and 30Km/h; The brake pressure of described light braking and braking is with all strength respectively 3 ~ 4bar and 6.5 ~ 7bar.
7. the vehicle frame complex working condition non-proportional loading computing method comprising welding analog according to claim 1 and 2, it is characterized in that, described torsional fatigue magnitude of load, direction, loading position comprise the X, Y, Z axis six-freedom degree retraining vehicle frame two longeron rear end, the Z axis one-movement-freedom-degree of constraint vehicle frame medium position; At two tie point places that front end first crossbeam and vehicle frame two longeron are formed respectively, load two respectively perpendicular to the contrary power in vehicle frame upper surface equal and opposite in direction direction, wherein the size of power is determined for being obtained mechanics parameter by dynamic analysis or rule of thumb calculating; Described torsional fatigue operating mode be two acting forces in alternating directions; The multiaxis of described foundation is the diaxon corresponding with two acting forces.
8. the vehicle frame complex working condition non-proportional loading computing method comprising welding analog according to claim 1 and 2, it is characterized in that, described multi-freedom-degree vibration fatigue load loaded position comprises the multiple point of excitation except center of gravity; The displacement spectra at the corresponding point of excitation place that the size and Orientation of described load is obtained by platform experiment or acceleration spectrum; Described load working condition is, to 1/4 cycle from 0, then to 1/2 cycle, finally to the state of cyclic operation of 1 end cycle; The number of described multiaxis is encourage three extraordinarily two that count, respectively the vertical load at the projection of corresponding point of excitation load in XY, YZ and XZ tri-planes and center of gravity or rotation of rotary table center and moment.
9. the vehicle frame complex working condition non-proportional loading computing method comprising welding analog according to claim 8, it is characterized in that, the multi-axial type of described multi-freedom-degree vibration is displacement load; The excitation of described load is counted and position is determined according to body frame structure for automotive form; Wherein, the point of excitation of straight frame is 6 ~ 10; Unit frame is then by the principle that each surface of vehicle frame all covers, and the quantity of point of excitation is no less than 2 times of the limit number sum on each surface.
10. the vehicle frame complex working condition non-proportional loading computing method comprising welding analog according to claim 9, it is characterized in that, described point of excitation comprises the left front point of vehicle frame, right front point, left back point, right back point, left front portion mid point, right front portion mid point, vehicle frame middle beam mid point.
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