CN113340626B - Method for measuring real-time interference magnitude between wheel axles and measurement early warning device - Google Patents

Method for measuring real-time interference magnitude between wheel axles and measurement early warning device Download PDF

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CN113340626B
CN113340626B CN202110571778.8A CN202110571778A CN113340626B CN 113340626 B CN113340626 B CN 113340626B CN 202110571778 A CN202110571778 A CN 202110571778A CN 113340626 B CN113340626 B CN 113340626B
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CN113340626A (en
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王旭
张玉茹
喻学广
刘新田
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Shanghai University of Engineering Science
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Abstract

The invention belongs to the technical field of traffic measurement, and discloses a method for measuring real-time interference between wheel shafts, which can well measure the real-time interference of running wheels and axles. The invention also discloses a device for measuring and early warning the real-time interference between the wheel shafts, which can monitor the running wheel shafts in real time and early warn in time when the real-time interference does not meet the requirement.

Description

Method for measuring real-time interference magnitude between wheel axles and measurement early warning device
Technical Field
The invention belongs to the technical field of traffic measurement, and particularly relates to a method for measuring real-time interference magnitude between wheel axles and a measurement early warning device.
Background
In the design of a wheel axle of a train, the wheels are connected and matched with the axle in an interference fit mode. The size difference between the wheel hole and the axle is mainly used to generate physical deformation on the combination surface of the wheel hole and the axle, and the wheel and the axle are tightly combined together through the contact stress generated by the deformation.
The interference fit can generate contact stress on the contact surface of the wheel and the shaft, if the interference is too large, the contact stress is increased, the axle is damaged, and the service life of the wheel shaft is shortened; and if the magnitude of interference is too small, under the high-speed movement of the train, the magnitude of interference can be reduced by the centrifugal force generated on the wheels and the axle, so that the contact stress cannot meet the tight connection of the wheel axle, and safety accidents are caused.
At present, no perfect means is available for measuring the interference magnitude of the running wheels and axles and monitoring in real time.
Disclosure of Invention
Aiming at the defects of the prior art, the intensive research finds that the matching problem of the wheel and the axle can be converted into a combined cylinder model because the axle is only pressed by the inner wall of the hub of the wheel and the inner wall of the hub of the wheel is only pressed by the axle, the analysis can be carried out according to the problem of the strength of the thick-wall cylinder, when the maximum stress between the joint surfaces of the interference fit of the wheel and the axle is less than the minimum stress allowed by the parts without generating plastic deformation, the surface of the axle circumferential surface and the surface of the wheel hole inner circumferential surface do not generate plastic deformation, the connection and combination surface is in an elastic deformation state, the contact stress between the faying surfaces can be deduced by elastic theory and the wheel and axle are subjected to much smaller forces in the axle direction than in other directions when the wheel axle is running, and therefore can be ignored, i.e. the wheel and axle can be equivalent to a thin disc and a thin circular axle, respectively.
The invention provides a method for measuring the real-time interference magnitude between wheel shafts and a measurement early warning device, which can well measure the real-time interference magnitude of the running wheels and the running axles and can monitor the interference magnitude in real time.
In order to achieve the purpose, the invention provides the following technical scheme:
a method for measuring the interference between wheel shafts in real time is applied to the wheel shaft formed by assembling wheels and an axle by initial interference, and is characterized by comprising the following steps of:
step S1, making the wheel shaft still, and obtaining the wheel shaft static contact stress on the assembly surface of the wheel and the axle based on the outer diameter of the wheel, the outer diameter of the axle and the inner diameter of the axle;
step S2, rotating the wheel shaft, setting wheel preset points on the wheel and axle preset points on the axle;
step S3, establishing an axle elastic mechanical differential equation related to the rotating centrifugal force on the wheel axle and the stress of the axle preset point in three dimensional directions, and establishing a wheel elastic mechanical differential equation related to the rotating centrifugal force on the wheel axle and the stress of the wheel preset point in three dimensional directions;
step S4: establishing an axle elastic mechanical constitutive equation and an axle elastic mechanical geometric equation related to the stress, the strain value and the displacement of the axle predetermined point in three dimensional directions, and establishing a wheel elastic mechanical constitutive equation and a wheel elastic mechanical geometric equation related to the stress, the strain value and the displacement of the wheel predetermined point in three dimensional directions;
step S5: obtaining the axle radial displacement and the wheel radial displacement based on the wheel axle static contact stress, the wheel or axle elastic mechanics differential equation, the wheel or axle elastic mechanics constitutive equation and the wheel or axle elastic mechanics geometric equation,
step S6: and obtaining real-time interference according to the initial interference, the axle radial displacement and the wheel radial displacement.
Preferably, in step S1, the wheel axle static contact stress pcComprises the following steps:
Figure BDA0003082974610000021
delta is the initial interference, a is the inner diameter of the axle, b is the outer diameter of the axle, c is the outer diameter of the wheel, E1Is the modulus of elasticity of the wheel, E2Is the modulus of elasticity, μ, of the axle1Is the Poisson's ratio, mu, of the wheel2Is the poisson ratio of the axle.
Preferably, the material of the wheel and the axle is the same, the wheel axle rotates at a constant preset angular speed, the radial distance of a preset point of the wheel is taken as the outer radial distance, the radial distance of a preset point of the axle is taken as the inner radial distance,
the differential equation of wheel elastodynamics is:
Figure BDA0003082974610000031
σorradial stress, σ, at predetermined points of the wheeloθCircumferential stress, σ, for a predetermined point of the wheelozPositive stress at predetermined points of the wheel, τozThe axial shear stress of the wheel at a predetermined point, rho is the material density of the wheel shaft, omega is a predetermined angular velocity, or is an outer radial distance,
the differential equation of the elasticity mechanics of the axle is as follows:
Figure BDA0003082974610000032
σirradial stress, σ, for a predetermined point of the axleiθCircumferential stress, σ, for predetermined points of the axleizPositive stress at predetermined point of axle, tauizThe axle-wise shear stress, ir, is the inner radial distance for the axle predetermined point.
Further, the wheel elastic mechanical constitutive equation is as follows:
Figure BDA0003082974610000033
εorvalue of radial strain, epsilon, for predetermined points of the wheeloθValue of circumferential strain, epsilon, for predetermined points of the wheelozThe axial strain value of a wheel preset point is, mu is the poisson ratio of a wheel shaft,
the elastic mechanical constitutive equation of the axle is as follows:
Figure BDA0003082974610000034
εirvalue of radial strain, epsilon, for predetermined point of axleiθValue of circumferential strain, epsilon, for predetermined points of the axleizFor axle reservationThe axial strain value of the point, E is the elastic modulus of the wheel shaft,
the wheel elastic mechanics geometric equation is as follows:
Figure BDA0003082974610000041
uoamount of radial displacement, gamma, of predetermined point of wheelorθValue of shear strain, v, for a predetermined point of the wheeloA tangential displacement angle at a predetermined point of the wheel at an outer radial distance of the wheel, (or) a circumferential displacement amount at the predetermined point of the wheel at the outer radial distance of the wheel corresponding to d theta,
the elastic mechanical geometrical equation of the axle is as follows:
Figure BDA0003082974610000042
uiradial displacement of predetermined point of axle, gammairθValue of shear strain, v, for predetermined point of axleiA tangential displacement angle of the predetermined point of the axle in the inner radial distance of the axle, (ir) d theta is a circumferential displacement amount of the predetermined point of the axle in the inner radial distance of the axle corresponding to d theta,
δt＝δ-(uo+ui)
δtand delta is the initial interference amount for the real-time interference amount.
Still further, in step S5, the wheel stress boundary conditions are as follows:
Figure BDA0003082974610000043
the axle stress boundary conditions are as follows:
Figure BDA0003082974610000044
the utility model provides a measurement early warning device of real-time magnitude of interference between wheel axles which characterized in that includes:
the acquisition unit comprises a rotary encoder which is coaxially arranged on a preset wheel shaft, and the wheel shaft is the wheel shaft;
the measurement control unit comprises a processor, a memory and a processing program which is stored on the memory and executed on the processor, and when the processor executes the processing program, the measurement early warning unit is used for implementing the measurement method of the real-time interference between the wheel shafts and sending out an early warning driving signal when the real-time interference is larger than 1.5% of the outer diameter of the wheel or smaller than 1.2% of the outer diameter of the wheel; and
and the early warning piece carries out early warning when receiving the early warning driving signal.
Preferably, the early warning piece is a buzzer and/or an early warning lamp.
Compared with the prior art, the invention has the beneficial effects that:
1. the method for measuring the real-time interference between the wheel shafts firstly obtains the static contact stress of the wheel shafts by analyzing the static wheel shafts, then combines the differential equation, the constitutive equation and the geometric equation related to the stress, the strain value and the displacement of the wheels and the axles in the rotating wheel shafts, substitutes the static contact stress as a boundary condition, and finally obtains the real-time interference according to the initial interference, the radial displacement of the axles and the radial displacement of the wheels, so the method can well measure the real-time interference of the wheels and the axles in running.
2. The device for measuring and early warning the real-time interference between the wheel shafts comprises the rotary encoder coaxially arranged on the preset wheel shaft, the measurement control unit which can implement the measurement method of the real-time interference between the wheel shafts and send out the early warning driving signal, and the early warning part which carries out early warning when the early warning driving signal is received, so that the device can carry out real-time monitoring on the running wheel shafts, and can carry out early warning in time when the real-time interference does not meet the requirement.
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Fig. 1 is a schematic step diagram of a method for measuring inter-axle interference in real time according to an embodiment of the present invention.
Detailed Description
In order to make the technical means, the original characteristics, the achieved objects and the effects of the present invention easily understood, the following embodiments are specifically described with reference to the accompanying drawings, and it is to be noted that the description of the embodiments is provided for the understanding of the present invention, but the present invention is not limited thereto.
As shown in fig. 1, the method S100 for measuring the real-time interference between the wheel axles in this embodiment is applied to a wheel axle formed by assembling the wheel and the axle with the initial interference, the material of the wheel and the axle is the same, the wheel axle rotates at a constant predetermined angular speed, the radial distance of the predetermined point of the wheel is used as the outer radial distance, and the radial distance of the predetermined point of the axle is used as the inner radial distance.
The method S100 for measuring the real-time interference magnitude between the wheel shafts comprises the following steps:
and step S1, making the wheel shaft still, and obtaining the wheel shaft static contact stress on the assembling surface of the wheel and the axle based on the outer diameter of the wheel, the outer diameter of the axle and the inner diameter of the axle.
In particular, the wheel axle static contact stress pcComprises the following steps:
Figure BDA0003082974610000061
delta is the initial interference, a is the inner diameter of the axle, b is the outer diameter of the axle, c is the outer diameter of the wheel, E1Is the modulus of elasticity of the wheel, E2Is the modulus of elasticity, μ, of the axle1Is the Poisson's ratio, mu, of the wheel2Is the poisson ratio of the axle.
Step S2, rotating the wheel shaft, setting wheel preset points on the wheel and axle preset points on the axle;
and step S3, establishing an axle elasticity differential equation related to the rotating centrifugal force on the wheel axle and the stress of the axle preset point in three dimensional directions, and establishing a wheel elasticity differential equation related to the rotating centrifugal force on the wheel axle and the stress of the wheel preset point in three dimensional directions.
Step S4: and establishing an axle elastic mechanical constitutive equation and an axle elastic mechanical geometric equation related to the stress, the strain value and the displacement in the three-dimensional directions of the axle predetermined point, and establishing a wheel elastic mechanical constitutive equation and a wheel elastic mechanical geometric equation related to the stress, the strain value and the displacement in the three-dimensional directions of the wheel predetermined point.
Step S5: and obtaining the radial displacement of the axle and the radial displacement of the wheel based on the static contact stress of the axle, the elastic mechanical differential equation of the wheel or the axle, the elastic mechanical constitutive equation of the wheel or the axle and the elastic mechanical geometric equation of the wheel or the axle.
Specifically, the differential equation of wheel elastodynamics is:
Figure BDA0003082974610000062
σorradial stress, σ, at predetermined points of the wheeloθCircumferential stress, σ, for a predetermined point of the wheelozPositive stress at predetermined points of the wheel, τozThe axle axial shear stress of a wheel preset point, rho is the material density of a wheel axle, omega is a preset angular velocity, or is an outer radial distance, rho omega is2(or) is the centrifugal force at a predetermined point of the wheel.
In practice, the axle receives a small force in the axial direction (i.e., Z axis) relative to the forces in other directions, so the axle can be simplified into a thin disk, and thus can be expressed as a plane stress state (Z axis is not considered), and equation (2) simplifies the Z axis stress state after being ignored as:
Figure BDA0003082974610000071
the elastic mechanical differential equation of the axle is as follows:
Figure BDA0003082974610000072
σirradial stress, σ, for predetermined points of the axleiθCircumferential stress, σ, for predetermined points of the axleizPositive stress at predetermined points of the axle, τizAxial shear stress at a predetermined point of the axle, ir is the inner radial distance, ρ ω2(ir) centrifugal force at a predetermined point of the axle.
The Z-axis stress state is simplified to be neglected in the formula (4):
Figure BDA0003082974610000073
the wheel elastic mechanics constitutive equation is as follows:
Figure BDA0003082974610000074
εorvalue of radial strain, epsilon, for predetermined point of wheeloθValue of circumferential strain, epsilon, for predetermined points of the wheelozThe axial strain value of the wheel at a preset point is represented by mu, and the Poisson ratio of the wheel shaft is represented by mu.
The wheel elastic mechanics geometric equation is as follows:
Figure BDA0003082974610000081
uoradial displacement of predetermined points of the wheel, gammaorθValue of shear strain, v, for a predetermined point of the wheeloA tangential displacement angle at a predetermined point of the wheel at an outer radial distance of the wheel, and (or) d θ is a circumferential displacement amount at the predetermined point of the wheel at the outer radial distance of the wheel corresponding to d θ.
Eliminating the radial displacement u of the wheel predetermined point from the first two equations in equation (7)oObtaining a strain coordination equation:
Figure BDA0003082974610000082
introduction of adjuvantsStress-assisting function psi1(or)＝(or)σorAnd substituting the formula (3) to obtain:
Figure BDA0003082974610000083
the differential transformation is performed by combining equations (6), (8) and (9):
Figure BDA0003082974610000084
solving equation (10) yields:
Figure BDA0003082974610000085
wherein C is3、C4Is the integration constant to be solved.
By means of an auxiliary stress function psi1(or), formula (9) and formula (11) are provided:
Figure BDA0003082974610000086
Figure BDA0003082974610000087
the wheel stress boundary conditions are as follows:
Figure BDA0003082974610000088
can obtain C3、C4And C is prepared by3、C4Substituting for the formulae (12) and (13) and obtaining, in conjunction with the formulae (6) and (7):
Figure BDA0003082974610000091
delta is the initial interference.
The elastic mechanical constitutive equation of the axle is as follows:
Figure BDA0003082974610000092
εirvalue of radial strain, epsilon, for predetermined point of axleiθValue of circumferential strain, epsilon, for predetermined points of the axleizThe axial strain value of the axle at a predetermined point of the axle, and E is the modulus of elasticity of the wheel axle.
The elastic mechanical geometrical equation of the axle is as follows:
Figure BDA0003082974610000093
uiamount of radial displacement, gamma, of predetermined point of axleirθValue of shear strain, v, for predetermined point of axleiThe tangential displacement angle of the predetermined point of the axle in the inner radial distance of the axle, and (ir) d theta is the circumferential displacement amount of the predetermined point of the axle in the inner radial distance of the axle, which corresponds to d theta.
Eliminating the radial displacement u of the predetermined point of the axle from the first two equations in the equation (17)iObtaining a strain coordination equation:
Figure BDA0003082974610000094
introducing an auxiliary stress function psi2(ir)＝(ir)σirAnd substituted into formula (5) to obtain:
Figure BDA0003082974610000095
the differential transformation is performed by combining equations (16), (18) and (19):
Figure BDA0003082974610000096
solving equation (20) yields:
Figure BDA0003082974610000101
wherein C1、C2Is the integration constant to be solved.
By means of an auxiliary stress function psi2(ir), formula (19) and formula (20) are given:
Figure BDA0003082974610000102
Figure BDA0003082974610000103
the axle stress boundary conditions are as follows:
Figure BDA0003082974610000104
can obtain C1、C2And C is prepared by1、C2Substituting for the formulae (22), (23) and, in conjunction with the formulae (16) and (17), yields:
Figure BDA0003082974610000105
step S6: and obtaining real-time interference according to the initial interference, the axle radial displacement and the wheel radial displacement.
In particular, the amount of the solvent to be used,
δt＝δ-(uo+ui) (26)
δtthe real-time interference magnitude.
The measuring and early warning device for the real-time interference magnitude between the wheel shafts in the embodiment is characterized by comprising a collecting unit, a measuring and controlling unit and an early warning piece.
The acquisition unit comprises a rotary encoder which is coaxially arranged on a preset wheel shaft, and the wheel shaft is the wheel shaft mentioned in the method S100 for measuring the interference between the wheel shafts in real time.
The measurement control unit comprises a processor, a memory and a processing program which is stored on the memory and executed on the processor, when the processor executes the processing program, the measurement early warning unit is used for implementing a measurement method S100 of the real-time interference between the wheel shafts and sending out an early warning driving signal when the real-time interference mentioned in the measurement method of the real-time interference between the wheel shafts is more than 1.5 percent of the outer diameter of the wheel or less than 1.2 percent of the outer diameter of the wheel; and
and the early warning piece carries out early warning when receiving the early warning driving signal and is a buzzer and/or an early warning lamp.
The above embodiments are preferred embodiments of the present invention, and are not intended to limit the scope of the present invention, and various modifications or changes that can be made by those skilled in the art without inventive skill within the scope of the appended claims will still fall within the scope of the present invention.

Claims (3)

1. A method for measuring the real-time interference between wheel shafts is applied to the wheel shaft formed by assembling wheels and an axle by using initial interference, and is characterized by comprising the following steps of:
step S1, making the wheel shaft still, and obtaining the wheel shaft static contact stress on the assembly surface of the wheel and the axle based on the outer diameter of the wheel, the outer diameter of the axle and the inner diameter of the axle;
the wheel axle static contact stress pcComprises the following steps:
Figure FDA0003562617430000011
δ is the initial interference, a is the inner diameter of the axle, b is the outer diameter of the axle, c is the outer diameter of the wheel, E1Is the modulus of elasticity of the wheel, E2Is the modulus of elasticity, μ, of the axle1Is the Poisson's ratio, mu, of the wheel2Is the poisson's ratio of the axle,
step S2, rotating the wheel shaft, setting wheel preset points on the wheel and axle preset points on the axle;
step S3, establishing an axle elastic mechanical differential equation related to the rotating centrifugal force on the wheel axle and the stress of the axle predetermined point in three dimensional directions, and establishing a wheel elastic mechanical differential equation related to the rotating centrifugal force on the wheel axle and the stress of the wheel predetermined point in three dimensional directions;
the wheels and the axles are made of the same material, the wheel axles rotate at a constant preset angular speed, the radial distance of a preset point of each wheel is used as an outer radial distance, the radial distance of a preset point of each axle is used as an inner radial distance,
the wheel elastic mechanics differential equation is as follows:
Figure FDA0003562617430000012
σorradial stress, σ, for a predetermined point of said wheeloθCircumferential stress at predetermined points of said wheel, σozFor positive stress at predetermined points of said wheel, τozThe axial shear stress of the wheel at a predetermined point is defined as rho, the material density of the wheel shaft is defined as omega, the predetermined angular velocity is defined as omega, and the radial distance is defined as or,
the axle elastic mechanics differential equation is as follows:
Figure FDA0003562617430000021
σirradial stress, σ, for a predetermined point of said axleiθCircumferential stress, σ, for predetermined points of the axleizPositive stress at predetermined point of said axle, tauizAn axial shear stress for the predetermined point of the axle, ir is the inner radial distance,
step S4: establishing an axle elastic mechanical constitutive equation and an axle elastic mechanical geometric equation related to the stress, the strain value and the displacement of the axle predetermined point in three dimensional directions, and establishing a wheel elastic mechanical constitutive equation and a wheel elastic mechanical geometric equation related to the stress, the strain value and the displacement of the wheel predetermined point in three dimensional directions;
the wheel elastic mechanical constitutive equation is as follows:
Figure FDA0003562617430000022
εorvalue of radial strain, ε, for said wheel predetermined pointoθValue of circumferential strain, ε, for said wheel predetermined pointozAn axial strain value for a predetermined point of the wheel, mu is a poisson's ratio of the wheel axle,
the elastic mechanical constitutive equation of the axle is as follows:
Figure FDA0003562617430000023
εirvalue of radial strain, ε, for said axle predetermined pointiθA value of circumferential strain, ε, for said axle predetermined pointizAn axial strain value of the axle at a predetermined point, E is an elastic modulus of the wheel axle,
the wheel elastic mechanics geometric equation is as follows:
Figure FDA0003562617430000031
uois the radial displacement of a predetermined point of said wheel, gammaorθA shear strain value, v, for a predetermined point of said wheeloA tangential displacement angle at a predetermined point of said wheel at an outer radial distance of said wheel, (or) d θ is a circumferential displacement of said predetermined point of said wheel at an outer radial distance of said wheel corresponding to d θ,
the elastic mechanical geometrical equation of the axle is as follows:
Figure FDA0003562617430000032
uiradial displacement of a predetermined point of said axle, gammairθValue of shear strain, v, for said predetermined point of axleiA tangential displacement angle at an inner radial distance of the axle for the predetermined point of the axle, (ir) d θ is a circumferential displacement amount at the inner radial distance of the axle for the predetermined point of the axle corresponding to d θ,
step S5: obtaining the axle radial displacement and the wheel radial displacement based on the wheel axle static contact stress, the wheel or axle elastic mechanical differential equation, the wheel or axle elastic mechanical constitutive equation and the wheel or axle elastic mechanical geometric equation,
the wheel stress boundary conditions are as follows:
Figure FDA0003562617430000033
the axle stress boundary conditions are as follows:
Figure FDA0003562617430000034
step S6: and obtaining the real-time interference according to the initial interference, the axle radial displacement and the wheel radial displacement as follows:
δt＝δ-(uo+ui)
δtand delta is the real-time interference magnitude and the initial interference magnitude.
2. The utility model provides a measurement early warning device of real-time magnitude of interference between wheel axles which characterized in that includes:
an acquisition unit comprising a rotary encoder coaxially mounted on a predetermined wheel axle, the wheel axle being the wheel axle of claim 1;
a measurement control unit including a processor, a memory, and a processing program stored in the memory and executed on the processor, wherein when the processor executes the processing program, the measurement warning unit is configured to implement the method for measuring the inter-wheel axle real-time interference according to claim 1 and to issue a warning drive signal when the real-time interference according to claim 1 is greater than 1.5% of the outer diameter of the wheel or less than 1.2% of the outer diameter of the wheel; and
and the early warning piece carries out early warning when receiving the early warning driving signal.
3. The device for measuring and warning the magnitude of interference between the wheel axles according to claim 2, wherein:
wherein, the early warning piece is buzzer and/or early warning lamp.
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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090114004A1 (en) * 2006-03-08 2009-05-07 Takayoshi Ozaki Wheel Support Bearing Assembly Equiped with Sensor
CN107609245A (en) * 2017-09-04 2018-01-19 杭州萧山鼎立机械有限公司 A kind of hub bearing inner ring and the end-play modification method of ring flange interference fit
CN108197416A (en) * 2018-02-16 2018-06-22 谢红太 One kind is based on Simulation rolling stocks wheel shaft elastic conjunction contact stress analysis method
CN109376503A (en) * 2018-12-29 2019-02-22 中南大学 Consider the high-speed railway subgrade Coupling method analysis method of wheel rail rolling contact
CN110186701A (en) * 2019-06-05 2019-08-30 燕山大学 A kind of Railway wheelset interference fit face fretting damage test device
US20200363277A1 (en) * 2018-02-05 2020-11-19 Rototest International Ab Method and apparatus for dynamometer testing of a motor vehicle
CN112560168A (en) * 2020-11-17 2021-03-26 湖北文理学院 Hub bearing unit interference magnitude determination method, device, equipment and storage medium

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109002676B (en) * 2018-10-11 2022-12-16 安徽合力股份有限公司 Simulation modeling method for rim

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090114004A1 (en) * 2006-03-08 2009-05-07 Takayoshi Ozaki Wheel Support Bearing Assembly Equiped with Sensor
CN107609245A (en) * 2017-09-04 2018-01-19 杭州萧山鼎立机械有限公司 A kind of hub bearing inner ring and the end-play modification method of ring flange interference fit
US20200363277A1 (en) * 2018-02-05 2020-11-19 Rototest International Ab Method and apparatus for dynamometer testing of a motor vehicle
CN108197416A (en) * 2018-02-16 2018-06-22 谢红太 One kind is based on Simulation rolling stocks wheel shaft elastic conjunction contact stress analysis method
CN109376503A (en) * 2018-12-29 2019-02-22 中南大学 Consider the high-speed railway subgrade Coupling method analysis method of wheel rail rolling contact
CN110186701A (en) * 2019-06-05 2019-08-30 燕山大学 A kind of Railway wheelset interference fit face fretting damage test device
CN112560168A (en) * 2020-11-17 2021-03-26 湖北文理学院 Hub bearing unit interference magnitude determination method, device, equipment and storage medium

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
列车轮轴疲劳寿命预估与可靠性研究;耿双龙;《中国优秀博硕士学位论文全文数据库(硕士)》;20210415(第4期);C033-236 *

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