CN108608811B - Design method for front wheel assembly structure of dumper - Google Patents

Design method for front wheel assembly structure of dumper Download PDF

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CN108608811B
CN108608811B CN201810361554.2A CN201810361554A CN108608811B CN 108608811 B CN108608811 B CN 108608811B CN 201810361554 A CN201810361554 A CN 201810361554A CN 108608811 B CN108608811 B CN 108608811B
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load
hub
steering knuckle
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rim
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CN108608811A (en
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王卓周
罗朋
蒋宽
林羽
石能芳
郭骏
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Guangzhou Electrical Locomotive Co Ltd
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B37/00—Wheel-axle combinations, e.g. wheel sets
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/001—Hubs with roller-bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0047—Hubs characterised by functional integration of other elements
    • B60B27/0052—Hubs characterised by functional integration of other elements the element being a brake disc
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/15—Vehicle, aircraft or watercraft design
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]

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Abstract

The design method of the front wheel assembly structure of the dumper comprises a hub piece, a steering knuckle, a tire, a rim, a hub bearing, a brake and a brake disc, the hub bearing comprises an outer side tapered roller bearing and an inner side tapered roller bearing, a hub piece is matched with the steering knuckle through the hub bearing, a rim is sleeved on the hub piece and is matched with the hub piece, the brake disc is sleeved on the hub piece and is matched with the hub piece, a brake is arranged on the brake disc, the tire is sleeved on the steering knuckle and is matched with the steering knuckle, the rim comprises a rim piece, the rim part is provided with a web plate connected with the hub part, the outer surface of the rim part is sleeved with a locking ring, a seat ring and a retainer ring, the wheel rim piece is further provided with an inflating valve device and a clamping support, the inflating valve device penetrates through the web and is connected with the clamping support, and the wheel rim piece is reasonable in structural design and convenient and fast to install.

Description

Design method for front wheel assembly structure of dumper
Technical Field
The invention relates to a design method of a front wheel assembly structure of a dumper.
Background
At present, the structure of the front wheel assembly of the dumper still adopts an empirically designed value taking method, and the reasonable design cannot be well carried out according to the requirements of actual road condition use scenes.
Disclosure of Invention
The invention aims to provide a dumper front wheel assembly structure which is reasonable in structural design and convenient and fast to install.
In order to solve the technical problem, the wheel hub bearing comprises an outer side tapered roller bearing and an inner side tapered roller bearing, the wheel hub is matched with the steering knuckle through the wheel hub bearing, the wheel rim is sleeved on the wheel hub and matched with the wheel hub, the brake disc is sleeved on the wheel hub and matched with the wheel hub, the brake is arranged on the brake disc, the tire is sleeved on the steering knuckle and matched with the steering knuckle, the wheel rim comprises a wheel rim part, a web plate connected with the wheel hub is arranged on the wheel rim part, a locking ring, a seat ring and a check ring are sleeved on the outer surface of the wheel rim part, an air valve device and a clamping support are further arranged on the wheel rim part, and the air valve device penetrates through the web plate and is connected with the clamping support.
As a further improvement of the invention, the web of the rim member is secured to the hub member by means of a bolted connection.
As a further improvement of the invention, the brake is a J6 series brake, and three brakes are arranged on the brake disc, wherein two brakes are arranged at the left end and the right end of the brake disc, and one brake is arranged at the top end of the brake.
The invention also comprises a design method of the front wheel assembly structure of the dumper, which comprises the following steps:
selecting tires according to the actual working conditions of the dump truck and referring to specification, size, air pressure and load of engineering machinery tires;
secondly, calculating the strength of the wheel hub piece:
(1) selecting a hub part as a forging structure according to the actual working condition of the dumper, and adopting a 42CrMo material;
(2) the load calculated by the strength of the hub piece refers to the technical specification parameters of the dumper, and the extreme working condition is taken to evaluate the static strength of the hub;
(3) establishing a finite element calculation model of the self-discharging wheel hub piece, determining constraint conditions and a load loading position, and then carrying out finite element strength analysis on the wheel hub piece;
thirdly, designing a steering knuckle:
(1) and selecting the structure and parameters of the steering knuckle: the steering knuckle and the steering knuckle arm are considered as a single part for analysis, the steering knuckle is of a forged piece structure and is made of 40CrMo materials;
(2) determining basic parameters of the front axle assembly, including the trim mass mbFront axle mass mqRated cargo mass mrMass m of overloaded cargooRadius R of wheel, distance l between axial center of wheel and center of suspension hydraulic cylinder, and thrust F of steering hydraulic cylinderzxFront axle braking force FzG gravity acceleration, E elastic modulus, gamma Poisson ratio and 42CrMo yield strength;
(3) respectively calculating an abnormal load and an operating load of the front axle assembly, wherein the abnormal load is used for evaluating the static strength of the front axle assembly, and the simulated operating load is used for evaluating the fatigue strength of the front axle assembly;
(4) a steering knuckle finite element calculation model is established based on HYPERMESH 11.0.0 and ANSYS12.1 finite element analysis software, a steering knuckle is dispersed by adopting entity units, and the matching part of the steering knuckle and the single tapered roller bearing, the tie rod connecting hole and the steering cylinder mounting seat are dispersed into corresponding longitudinal, transverse and vertical spring units according to the actual stress condition so as to better simulate the actual contact condition and determine the constraint condition and the load loading position;
(5) and carrying out finite element strength analysis on the steering knuckle.
As a further improvement of the present invention, in step two (3): based on HYPERMESH 11.0.0 and ANSYS12.1 finite element analysis software, a hub member finite element calculation model is established, and a hub body maximum Von Mises equivalent stress cloud chart is calculated and created and compared with the yield limit of the selected material of the hub body.
As a further improvement of the present invention, in step three (5): when fatigue evaluation is carried out on the steering knuckle, points with larger stress in the steering knuckle main body are selected, the stress state of each point is simplified into a uniaxial stress state based on the direction of the maximum main stress according to the calculation condition, and the maximum stress value sigma of each point is calculatedmaxAnd minimum stress value sigmaminGo forward and go forwardAnd according to R ═ σmin/σmaxAnd calculating the stress ratio, judging the structural strength through a fatigue curve in a Moore-Kommer-Japer form, and calculating the fatigue safety coefficient of a point with larger stress.
Drawings
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
FIG. 1 is a schematic structural diagram of the present invention.
FIG. 2 is a cloud diagram of equivalent stress of Von Mises in a hub member.
FIG. 3 is a Moore-Kommer-Japer fatigue curve of a 42CrMo base material.
FIG. 4 is a cloud diagram of equivalent stress of a first operating mode steering knuckle Von Mises.
FIG. 5 is a diagram of equivalent stress clouds of a steering knuckle Von Mises under a second operating condition.
FIG. 6 is an equivalent stress cloud diagram of a steering knuckle Von Mises under a fifth operating condition.
FIG. 7 is a cloud diagram of equivalent stress of a steering knuckle Von Mises under a sixth operating condition.
FIG. 8 is a cloud diagram of equivalent stress of a steering knuckle Von Mises under a seventh operating condition.
FIG. 9 is an equivalent stress cloud diagram of a steering knuckle Von Mises under an eighth operating condition.
FIG. 10 is a cloud diagram of equivalent stress of a ninth operating mode knuckle Von Mises.
FIG. 11 is a fatigue evaluation chart of a steel structure base material.
Detailed Description
As shown in fig. 1, the invention comprises a hub member 1, a knuckle 2, a tire 3, a rim, a hub bearing, brakes 4 and a brake disc 5, wherein the hub bearing comprises an outer tapered roller bearing 6 and an inner tapered roller bearing 7, the hub member 1 is matched with the knuckle 2 through the hub bearing, the rim is sleeved on the hub member 1 and is matched with the hub member 1, the brake disc 5 is sleeved on the hub member 1 and is matched with the hub member 1, three brakes 4 are arranged on the brake disc 5, the brakes 4 are J6 series brakes 4, two brakes 4 are arranged at the left end and the right end of the brake disc 5, one brake 4 is arranged at the top end of the brake 4, the tire is sleeved on the knuckle 2 and is matched with the knuckle 2, the rim comprises a rim member 8, a web plate 9 connected with the hub member 1 is arranged on the rim member 8, the web plate 9 of the rim member 8 is fixed with the hub member 1 through a bolt connection, the outer surface of the rim piece 8 is sleeved with a locking ring 10, a seat ring 11 and a retainer ring 12, the rim piece 8 is further provided with an inflating valve device 13 and a clamping bracket, and the inflating valve device 13 penetrates through the web 9 and is connected with the clamping bracket.
The invention also comprises a design method of the front wheel assembly structure of the dumper, which comprises the following steps:
the tyre is selected according to the actual working condition of the dumper and referring to 'specification, size, air pressure and load of engineering machinery tyre', the tyre is used as one of important parts of the electric drive dumper, is directly contacted with a road surface, not only bears the total mass of the dumper and the load, but also buffers the impact and vibration suffered by the dumper during running together with suspension, keeps the running control stability and smoothness of the dumper, and the quality of the performance directly influences the stability and safety of the dumper.
The front tire is a 36.00R51 type tire according to the design task specification. According to the specification of GB/T2980-2009 specification, dimension, air pressure and load of engineering machinery tires, the tire parameters are shown in the following table:
Figure GDA0002212815330000041
Figure GDA0002212815330000051
as can be seen from the table, under the condition of 50km/h, the 36.00R51 tire has the load capacity of 46250kg, the maximum full-load speed of the 150t electric dumper is 45km/h, and the dead load of a single wheel of a front axle is 41833kg, so the 36.00R51 tire can meet the design requirement.
Secondly, calculating the strength of the wheel hub piece:
(1) selecting a hub part as a forging structure according to the actual working condition of the dumper, and adopting a 42CrMo material;
(2) and calculating the strength of the hub piece according to the technical specification parameters of the dumper, and taking the limit working condition to evaluate the static strength of the hub:
and the load of the hub strength calculation refers to the technical specification parameters of the vehicle, and the limit working condition is taken for evaluating the static strength of the hub.
Vertical load:
Fz＝mqc×3g＝1104.6kN
transverse load:
Fy＝0.5mq×g＝66.7kN
longitudinal load:
Figure GDA0002212815330000052
(3) based on HYPERMESH 11.0.0 and ANSYS12.1 finite element analysis software, a hub part finite element calculation model is established, constraint conditions and a load loading position are determined, a maximum Von Mises equivalent stress cloud chart of the hub body is calculated and created, as shown in figure 2, the maximum Von Mises equivalent stress cloud chart is compared with the yield limit of the material selected by the hub body, and the calculation result shows that the maximum Von Mises equivalent stress of the hub body is 91.6MPa and is far smaller than the yield limit of the material, the safety coefficient of the hub is 10.15, a large safety margin is provided, and the strength meets the design requirement;
thirdly, designing a steering knuckle:
(1) and selecting the structure and parameters of the steering knuckle: the steering knuckle and the steering knuckle arm are considered as a single part for analysis, the steering knuckle is of a forged piece structure and is made of 40CrMo materials;
(2) determining basic parameters of the front axle assembly, and obtaining the following table:
Figure GDA0002212815330000061
Figure GDA0002212815330000071
(3) respectively calculating an abnormal load and an operating load of the front axle assembly, wherein the abnormal load is used for evaluating the static strength of the front axle assembly, and the simulated operating load is used for evaluating the fatigue strength of the front axle assembly;
wherein the abnormal load is as follows:
the extraordinary load is the maximum load that can occur in service.
Vertical load
Mass m borne by the front wheelqc
Figure GDA0002212815330000072
Vertical vibration of 1g, 1.5g and 3g of vertical load in the abnormal load is considered according to different working conditions:
Fz1g＝mqc×g＝368.2kN
Fz1.5g＝mqc×1.5g＝552.3kN
Fz3g＝mqc×3g＝1104.6kN
torque generated by vertical load:
Mz1g＝Fz1g×l＝328kN·m
Mz1.5g＝Fz1.5g×l＝493kN·m
Mz3g＝Fz3g×l＝985kN·m
transverse load:
the lateral load in the extraordinary load needs to take into account a lateral vibration of 1 g:
Fy1g＝0.5mq×g＝66.7kN
torque generated by lateral load:
My1g＝Fy1g×R＝107.2kN·m
longitudinal load:
the friction coefficient of the tire and the ground is 0.3.
The longitudinal load under the limit condition is 3g of vertical load:
Figure GDA0002212815330000081
the vertical load of 1g is considered in the longitudinal load when the dump truck is started:
Figure GDA0002212815330000082
the vertical load and the braking load of 3g are considered in the longitudinal load during braking of the dump truck:
Figure GDA0002212815330000083
the vertical load of 1.5g is taken into account by the longitudinal load in the curve:
Figure GDA0002212815330000084
simulating an operation load:
the simulated operation load is a load which is frequently generated in actual application and is used for checking the fatigue strength of the front wheel.
Vertical load:
mass m 'carried by front wheel'qc
Figure GDA0002212815330000091
The vertical load in the simulated operation load needs to consider 0.5g of vertical vibration: f'z1g＝m′qc×g＝337.1kN
F′z1.5g＝m′qc×1.5g＝505.7kN
F′z0.5g＝m′qc×0.5g＝168.6kN
Torque generated by vertical load:
M′z1g＝F′z1g×l＝300.7kN·m
M′z1.5g＝F′z1.5g×l＝451.1kN·m
M′z0.5g＝F′z0.5g×l＝150.4kN·m
transverse load:
the lateral load in the simulated operating load needs to take into account a lateral vibration of 0.7 g: f'y0.7g＝0.5×mq×0.7g＝46.7kN
Torque generated by lateral load:
M′y0.7g＝F′y0.7g×R＝75kN·m
longitudinal load:
the longitudinal load in the simulated operating load needs to take into account a longitudinal vibration of 0.5 g:
Figure GDA0002212815330000092
Figure GDA0002212815330000093
calculating load conditions
The operating load conditions and the extraordinary load conditions are shown in the following table:
steering knuckle load condition combination meter
Figure GDA0002212815330000101
(4) The method comprises the steps of establishing a finite element calculation model of the steering knuckle based on HYPERMESH 11.0.0 and ANSYS12.1 finite element analysis software, dispersing the steering knuckle by using entity units, dispersing the matching position of the steering knuckle and a single tapered roller bearing, the connecting hole of a tie rod and the mounting hole of a steering hydraulic cylinder into corresponding longitudinal, transverse and vertical spring units according to actual stress conditions so as to better simulate the actual contact condition and determine a constraint condition and a load loading position, wherein in the finite element calculation model, the constraint condition adopts an elastic boundary. Applying vertical, longitudinal and transverse elastic boundaries at the matching part of the steering knuckle and the single tapered roller bearing and the steering hydraulic cylinder in a non-curve working condition, and applying a transverse elastic boundary at the connecting part of the steering knuckle and the tie rod; in a curve working condition, vertical, longitudinal and transverse elastic boundaries are applied to the matching position of the steering knuckle and the single tapered roller bearing, and the transverse elastic boundary is applied to the connecting position of the steering knuckle and the tie rod. The loading position of the load is applied in a node force manner according to the actual acting position of the load. And (3) defining coordinates of the finite element model: the X axis is the longitudinal direction of the steering knuckle, the Y axis is the transverse direction of the steering knuckle, the Z axis is the vertical direction of the steering knuckle, a coordinate system accords with the right hand rule, and the origin of coordinates is located at the circle center of an end cover of the steering knuckle;
(5) and carrying out finite element strength analysis on the steering knuckle:
static Strength evaluation
Under the action of the abnormal load working condition, the stress of any point of the steering knuckle cannot exceed the yield limit of the material. Namely, for the working conditions of 6-9, the Von Mises stress of each point of the steering knuckle is smaller than the yield strength of 42 CrMo.
Evaluation of fatigue Strength
The fatigue strength evaluation of the base material of the knuckle forging structure is carried out with reference to the provisions of German industry Standard DIN 17100 and weld Standard DVS 1612, FIG. 3 giving the Moore-Kommer-Japer-form fatigue curve of the material 42 CrMo.
During fatigue evaluation, points with large stress in the steering knuckle main body are selected, the stress state of each point is simplified into a uniaxial stress state based on the direction of the maximum main stress aiming at the calculation working condition 1-5, and the maximum stress value sigma of each point is calculatedmaxAnd minimum stress value sigmaminAnd further according to R ═ σmin/σmaxAnd calculating the stress ratio, judging the structural strength through a fatigue curve in a Moore-Kommer-Japer form, and calculating the fatigue safety coefficient of a point with larger stress.
The equivalent stress under each load working condition is shown in the attached figures 4-10. The yield strength of the 42CrMo material is 930 MPa. Under all the abnormal load working conditions in the following table, the maximum equivalent stress value of the steering knuckle is smaller than an allowable value, and the strength requirement of the abnormal load on the steering knuckle is met.
Partial operating mode calculation results
Figure GDA0002212815330000111
Figure GDA0002212815330000121
And judging the parent metal according to a knuckle fatigue analysis method. The points with larger stress in the knuckle are selected, the stress ratio of each node and the maximum stress value are put into a Moore-Kommer-Japer fatigue curve graph for comparison, and the result shows that all the points are within the fatigue curve of the parent metal, as shown in FIG. 11, the fatigue strength of the parent metal of the knuckle meets the requirement. Because the knuckle is of a forged piece structure, the fatigue of the welding seam is not evaluated.
And (3) carrying out finite element strength analysis on the steering knuckle of the dump truck according to the technical specification parameters of the dump truck, wherein the calculation result shows that:
under various working conditions of abnormal load, the maximum equivalent stress of the steering knuckle is less than the yield limit of a 42CrMo material, and the static strength requirement is met.
Under the action of simulated operation load, the fatigue strength of all nodes of the steering knuckle under 5 working conditions is analyzed, the fatigue strength does not exceed the Moore-Kommer-Japer parent metal fatigue curve of a corresponding material, and the steering knuckle structure meets the requirement of the fatigue strength.

Claims (3)

1. A design method of a front wheel assembly structure of a dumper is characterized by comprising the following steps: the front wheel assembly structure of the dumper comprises a hub piece, a steering knuckle, a tire, a rim, a hub bearing, a brake and a brake disc, wherein the hub bearing comprises an outer side tapered roller bearing and an inner side tapered roller bearing, the hub piece is matched with the steering knuckle through the hub bearing, the rim is sleeved on the hub piece and matched with the hub piece, the brake disc is sleeved on the hub piece and matched with the hub piece, the brake is arranged on the brake disc, the tire is sleeved on the steering knuckle and matched with the steering knuckle, the rim comprises the rim piece, a web connected with the hub piece is arranged on the rim piece, a locking ring, a seat ring and a check ring are sleeved on the outer surface of the rim piece, an air valve device and a clamping support are further arranged on the rim piece, and the air valve device penetrates through the web and is connected with the clamping support;
the design method comprises the following steps:
firstly, selecting tires according to the actual working condition of the dumper;
secondly, calculating the strength of the wheel hub piece:
(1) selecting a hub part as a forging structure according to the actual working condition of the dumper, and adopting a 42CrMo material;
(2) taking the limit working condition to evaluate the static strength of the hub;
(3) establishing a finite element calculation model of the self-discharging wheel hub piece, determining constraint conditions and a load loading position, and then carrying out finite element strength analysis on the wheel hub piece;
thirdly, designing a steering knuckle:
(1) and selecting the structure and parameters of the steering knuckle: the steering knuckle and the steering knuckle arm are considered as a single part for analysis, the steering knuckle is of a forged piece structure and is made of 40CrMo materials;
(2) determining basic parameters of the front axle assembly, including the trim mass mbFront axle mass mqRated cargo mass mrMass m of overloaded cargooRadius R of wheel, distance l between axial center of wheel and center of suspension hydraulic cylinder, and thrust F of steering hydraulic cylinderzxFront axle braking force FzG gravity acceleration, E elastic modulus, gamma Poisson ratio and 42CrMo yield strength;
(3) respectively calculating the abnormal load and the operation load of the front axle assembly, wherein the abnormal load is used for evaluating the static strength of the front axle assembly, and the simulated operation load is used for evaluating the fatigue strength of the front axle assembly;
wherein the abnormal load is as follows:
the maximum load occurring in use;
vertical load:
mass m borne by the front wheelqc，
Figure FDA0002372204880000021
Vertical vibration of 1g, 1.5g and 3g of vertical load in the abnormal load is considered according to different working conditions:
Fz1g＝mqc×g；
Fz1.5g＝mqc×1.5g；
Fz3g＝mqc×3g；
torque generated by vertical load:
Mz1g＝Fz1g×l；
Mz1.5g＝Fz1.5g×l；
Mz3g＝Fz3g×l；
transverse load:
the lateral load in the extraordinary load needs to take into account a lateral vibration of 1 g:
Fy1g＝0.5mq×g；
torque generated by lateral load:
My1g＝Fy1g×R；
longitudinal load:
taking the friction coefficient of the tire and the ground to be 0.3;
the longitudinal load under the limit condition is 3g of vertical load:
Figure FDA0002372204880000031
the vertical load of 1g is considered in the longitudinal load when the dump truck is started:
Figure FDA0002372204880000032
the vertical load and the braking load of 3g are considered in the longitudinal load during braking of the dump truck:
Figure FDA0002372204880000033
the vertical load of 1.5g is taken into account by the longitudinal load in the curve:
Figure FDA0002372204880000034
simulating an operation load:
the simulated operation load is a load generated in actual application and is used for checking the fatigue strength of the front wheel;
vertical load:
mass m 'carried by front wheel'qc，
Figure FDA0002372204880000035
The vertical load in the simulated operation load needs to consider 0.5g of vertical vibration:
F′z1g＝m′qc×g；
F′z1.5g＝m′qc×1.5g；
F′z0.5g＝m′qc×0.5g；
torque generated by vertical load:
M′z1g＝F′z1g×l；
M′z1.5g＝F′z1.5g×l；
M′z0.5g＝F′z0.5g×l；
transverse load:
the lateral load in the simulated operating load needs to take into account a lateral vibration of 0.7 g:
F′y0.7g＝0.5×mq×0.7g；
torque generated by lateral load:
M′y0.7g＝F′y0.7g×R；
longitudinal load:
the longitudinal load in the simulated operating load needs to take into account a longitudinal vibration of 0.5 g:
Figure FDA0002372204880000041
Figure FDA0002372204880000042
(4) establishing a steering knuckle finite element calculation model based on HYPERMESH 11.0.0 and ANSYS12.1 finite element analysis software, wherein the steering knuckle is dispersed by adopting entity units, and the matching part of the steering knuckle and the single tapered roller bearing, the tie rod connecting hole and the steering cylinder mounting seat are dispersed into corresponding longitudinal, transverse and vertical spring units according to the actual stress condition so as to simulate the actual contact condition and determine the constraint condition and the load loading position;
(5) and carrying out finite element strength analysis on the steering knuckle.
2. The method of designing a front wheel assembly structure for a dump truck according to claim 1, wherein: in step two (3): based on HYPERMESH 11.0.0 and ANSYS12.1 finite element analysis software, a hub member finite element calculation model is established, and a hub body maximum Von Mises equivalent stress cloud chart is calculated and created and compared with the yield limit of the selected material of the hub body.
3. The method of designing a front wheel assembly structure for a dump truck according to claim 1, wherein: in step three (5): when fatigue evaluation is carried out on the steering knuckle, points with larger stress in the steering knuckle main body are selected, the stress state of each point is simplified into a uniaxial stress state based on the direction of the maximum main stress according to the calculation condition, and the maximum stress value sigma of each point is calculatedmaxAnd minimum stress value sigmaminAnd further according to R ═ σmin/σmaxAnd calculating the stress ratio, judging the structural strength through a fatigue curve in a Moore-Kommer-Japer form, and calculating the fatigue safety coefficient of a point with larger stress.
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CN114523803B (en) * 2022-03-14 2024-03-08 宝武集团马钢轨交材料科技有限公司 Lightweight heavy-duty wheel set and design method thereof

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