CN-122020834-A - Design method, system, equipment and medium of brake shell capable of tolerating 87.5Mpa

CN122020834ACN 122020834 ACN122020834 ACN 122020834ACN-122020834-A

Abstract

The application provides a design method, a system, equipment and a medium of a brake shell capable of tolerating 87.5Mpa, the method respectively obtains the dimension parameters of a brake cylinder, a transition changeover section and a skirt section through two iterations, the torsional rigidity and the strength of the brake cylinder meet the requirements through the first iteration, thereby reducing the torsional deformation of the barrel part, reducing the tensile stress, enhancing the rigidity and the strength of the transition joint section and the skirt section through the second iteration, reducing the axial deformation of the skirt section and reducing the tensile stress of the transition joint section. According to the application, under the condition that the high-pressure hydraulic source of the aircraft is directly connected with the brake shell, parameters of each structural dimension of the brake shell are obtained based on the tolerance of the rated brake shell, and basic theoretical guidance is provided for the weight reduction of the aircraft and the design of the brake shell of the aircraft.

Inventors

LOU JINTAO
SHI WEIBO
ZHANG YI
ZHANG MENGJIE
ZHANG WANSHUN
LIU GANG
ZHAO BOXIN
Dang Shuwei
LIU ZHAO
CHEN PEIJUN

Assignees

西安航空制动科技有限公司

Dates

Publication Date: 20260512
Application Date: 20251215

Claims (10)

1. A method of designing a brake housing that is tolerant to 87.5Mpa, comprising the steps of: Step S1, based on basic information of a brake cylinder material, obtaining allowable stress of the brake cylinder, and based on brake pressure and a piston acting area, obtaining axial load of the brake cylinder; S2, presetting a value range of the outer diameter of a brake cylinder and the inner diameter of the brake cylinder based on the brake moment requirement of an aircraft, the deformation of a hub and the heat dissipation gap of a shell; S3, respectively selecting the maximum brake cylinder outer diameter and the maximum brake cylinder inner diameter from the value ranges of the brake cylinder outer diameter and the brake cylinder inner diameter, and obtaining the brake cylinder axial tensile stress and the brake cylinder shearing stress based on the maximum brake cylinder outer diameter and the maximum brake cylinder inner diameter and the brake cylinder axial load; S4, obtaining the equivalent stress of the brake cylinder based on the axial tensile stress of the brake cylinder and the shearing stress of the brake cylinder, if the equivalent stress of the brake cylinder is more than or equal to the allowable stress of the brake cylinder, reducing the inner diameter of the brake cylinder according to a preset first iteration thickness until the equivalent stress of the brake cylinder is less than the allowable stress of the brake cylinder, and taking the inner diameter of the brake cylinder as the optimal inner diameter of the brake cylinder at the moment; s5, connecting a skirt section to the bottom of the brake cylinder through a transition switching section, and calculating the bending stress of the transition switching section based on the thickness of the skirt section, the acting force arm of external load to the skirt section and the connection radius of the transition switching section; And S6, obtaining a corresponding force concentration coefficient and a shearing stress concentration coefficient based on the skirt edge outer diameter and the brake cylinder outer diameter, obtaining a transition switching section equivalent stress based on the corresponding force concentration coefficient and the brake cylinder axial tensile stress, and the shearing stress concentration coefficient and the brake cylinder shearing stress, if the transition switching section equivalent stress is more than or equal to the brake cylinder allowable stress, increasing the length of the transition switching section connection radius according to a preset iteration length, and simultaneously increasing the skirt edge section thickness according to a preset second iteration thickness until the transition switching section equivalent stress is less than the brake cylinder allowable stress, wherein the transition switching section connection radius length and the skirt edge section thickness are used as an optimal transition switching section connection radius length and an optimal skirt edge section thickness, and obtaining the brake shell capable of tolerating 87.5Mpa based on the optimal brake cylinder inner diameter, the optimal transition switching section connection radius length and the optimal skirt edge section thickness.
2. The method for designing a brake housing capable of withstanding 87.5Mpa according to claim 1, wherein the axial load of the brake cylinder in step S1 is The method comprises the following steps: ; Wherein C is a safety margin coefficient, and is taken as 2.5; and S is the sum of the acting areas of the pistons and is the braking pressure.
3. The method for designing a brake housing capable of tolerating 87.5Mpa according to claim 1, wherein the obtaining the range of values of the brake cylinder outer diameter and the brake cylinder inner diameter in step S2 comprises the following steps: obtaining the medium diameter of a brake disc according to the brake moment requirement of the aircraft : ; In the formula, Is a braking moment; is the coefficient of friction; Is the total area of the piston; Braking pressure; friction couple number; according to the inner diameter of the hub Considering the deformation of the hub Obtaining the outer diameter of the brake disc : ; From the outer diameter of the brake disc And brake disc pitch diameter Obtaining the inner diameter of the brake disc : ; According to the inner diameter of the brake disc Consider the shell heat dissipation gap Obtaining the outer diameter of the brake cylinder The range of the values is as follows: ; Because of the weight requirement of the airplane, the brake shell body cannot be infinitely thickened to meet the strength and rigidity requirement, and the initial thickness of the shell body is defined as Obtaining the inner diameter of the cylinder The range of the values is as follows: 。
4. The method for designing a brake housing resistant to 87.5Mpa according to claim 1, wherein in the step S3, the brake cylinder is axially pulled to a tensile stress The method comprises the following steps: ; ; In the formula, Is the cross section area of the brake cylinder; Is the maximum brake cylinder outer diameter; The inner diameter of the cylinder body is the largest; The shear stress of the brake cylinder The method comprises the following steps: ; 。
5. the method for designing a brake housing resistant to 87.5Mpa according to claim 4, wherein the equivalent stress of the brake cylinder is equal in step S4 The method comprises the following steps: ; the first iteration thickness is 0.2mm.
6. The method for designing a brake housing capable of withstanding 87.5Mpa according to claim 1, wherein the bending stress of the transition joint in step S5 is The method comprises the following steps: ; ; ; ; In the formula, The force arm is the action force arm of the external load to the skirt section; The distance between the connecting part of the transition joint section and the skirt section and the axis of the shell; the connection radius of the transition switching section; Is the thickness of the skirt section.
7. The method for designing a brake housing capable of withstanding 87.5MPa according to claim 6, wherein the step S5 is a step of equalizing the stress of the transition joint The method comprises the following steps: ; ; ; In the formula, And Are normal stress concentration coefficients; Is the shear stress concentration coefficient.
8. A design system of a brake housing capable of tolerating 87.5Mpa is characterized in that, a method of designing a brake housing resistant to 87.5Mpa according to claim 1, comprising: The preprocessing unit is configured to obtain allowable stress of the brake cylinder based on basic information of the brake cylinder material and obtain axial load of the brake cylinder based on brake pressure and piston acting area; the initialization unit is configured to preset the value ranges of the outer diameter of the brake cylinder and the inner diameter of the brake cylinder based on the brake moment requirement of the aircraft, the hub deformation and the shell heat dissipation gap; The first processing unit is configured to respectively select the maximum brake cylinder outer diameter and the maximum brake cylinder inner diameter in the value ranges of the brake cylinder outer diameter and the brake cylinder inner diameter, and obtain the brake cylinder axial tensile stress and the brake cylinder shearing stress based on the maximum brake cylinder outer diameter and the maximum brake cylinder inner diameter and the brake cylinder axial load; The first iteration unit is configured to obtain the equivalent stress of the brake cylinder based on the axial tensile stress of the brake cylinder and the shearing stress of the brake cylinder, if the equivalent stress of the brake cylinder is more than or equal to the allowable stress of the brake cylinder, the inner diameter of the brake cylinder is reduced according to the preset first iteration thickness until the equivalent stress of the brake cylinder is less than the allowable stress of the brake cylinder, and the inner diameter of the brake cylinder is used as the optimal inner diameter of the brake cylinder; The second processing unit is configured to obtain the bending stress of the transition switching section by calculating the connection radius of the transition switching section and the acting force arm of the skirt section based on the thickness of the skirt section and the external load on the skirt section; The second iteration unit is configured to obtain a corresponding force concentration coefficient and a corresponding shear stress concentration coefficient based on the skirt edge outer diameter and the brake cylinder outer diameter, obtain a transition switching section equivalent stress based on the corresponding force concentration coefficient and the brake cylinder axial tensile stress, and the corresponding shear stress concentration coefficient and the corresponding brake cylinder shear stress, increase the length of the transition switching section connection radius according to a preset iteration length if the transition switching section equivalent stress is more than or equal to the brake cylinder allowable stress, and increase the skirt edge section thickness according to a preset second iteration thickness simultaneously until the transition switching section equivalent stress is less than the brake cylinder allowable stress, and obtain the brake shell capable of tolerating 87.5Mpa based on the optimal brake cylinder inner diameter, the optimal transition switching section connection radius length and the optimal skirt edge section thickness.
9. An electronic device, characterized in that, the electronic device includes: at least one processor, and A memory communicatively coupled to the at least one processor, wherein, The memory stores instructions executable by the at least one processor to enable the at least one processor to perform the method of designing a brake housing tolerant to 87.5Mpa according to any one of claims 1 to 7.
10. A non-transitory computer-readable storage medium storing computer instructions for causing the computer to perform the method of designing a brake housing resistant to 87.5Mpa according to any one of claims 1 to 7.

Description

Design method, system, equipment and medium of brake shell capable of tolerating 87.5Mpa Technical Field The invention belongs to the technical field of aircraft brake and particularly relates to a design method, a system, equipment and a medium of a brake shell capable of tolerating 87.5 Mpa. Background Aircraft wheels generally consist of a wheel assembly and a brake device. The braking device is composed of a thermal reservoir component, a cylinder seat component, a braking shell and the like. The pressing disc assembly, the static disc assembly and the inner convex key of the bearing disc of the thermal warehouse assembly are arranged on the guide rail convex key of the brake shell and are in a relatively static state, and the outer convex key of the moving disc assembly of the thermal warehouse assembly is driven by the guide rail of the machine wheel assembly, so that synchronous rotation can be realized. The cylinder seat assembly and the brake housing are fixedly connected together through bolts or other mechanical structures, and the thermal reservoir assembly is arranged between the cylinder seat assembly and the brake housing assembly. When braking, high-pressure hydraulic oil enters a piston cavity of the wheel braking device through a braking system pipeline, the piston moves forwards under the action of pressure to compress a dynamic braking disc and a static braking disc of the thermal warehouse assembly, and at the moment, the dynamic disc and the static disc generate relative friction movement under the action of an aircraft wheel and generate friction force to brake and slow down the aircraft. During braking, the brake housing assembly is subjected to axial thrust and circumferential torque. The hydraulic drive is needed by a plurality of parts on the aircraft, and the needed hydraulic pressure is different, so that the front end of each part is provided with a pressure reducing valve, and the pressure of a high-pressure hydraulic source is reduced and then is input into each part. The front end of the input of the brake device is also provided with a pressure reducing valve. The hydraulic pressure source of the aircraft is not more than 35MPa, and the normal braking pressure of the current aircraft wheel braking device is not more than 28MPa. Due to the continuous weight-reducing demands of aircraft, the elimination of pressure relief valves is a trend in the technological development. If the aircraft wheel brake device is directly connected with a high-pressure hydraulic source, the brake shell designed in the prior art is not enough in rigidity, and when the brake shell bears 35MPa of brake pressure, the brake shell is large in axial deformation, the drag brake phenomenon possibly occurs in the use process, the strength and the rigidity of the brake shell are also high in requirements, the conventional brake shell structure is provided with a straight cylindrical shell, the wall thickness of the shell is thinner, and the brake shell is easy to deform under the high-pressure brake pressure. The brake block is installed in barrel lower part shirt rim department, and the barrel is connected near the right angle with the shirt rim, produces stress concentration in the junction corner easily, and the brake casing barrel that appears afterwards adopts big R to be connected with the shirt rim mostly, can effectively reduce stress concentration. The shell design must meet the combination of higher strength, less deformation and lower weight. Therefore, a brake housing capable of withstanding a normal brake pressure of 35MPa is required, and the brake housing is required to withstand 87.5MPa under a safety margin of 2.5 times, but the related dimensional parameters of the brake housing cannot be directly obtained in the prior related art. The present application therefore contemplates a sizing method that is capable of withstanding the rated brake housing. Disclosure of Invention In order to solve the technical problem that reasonable size parameters of a brake device cannot be directly obtained in order to meet the technical development requirement that an airplane high-pressure hydraulic source is directly connected with the brake device in the prior art, the invention provides a design method, a system, equipment and a medium of a brake shell capable of tolerating 87.5 Mpa. In order to achieve the above purpose, the present invention provides the following technical solutions: in a first aspect, embodiments of the present disclosure provide a method of designing a brake housing that is tolerant to 87.5Mpa, comprising the steps of: Step S1, based on basic information of a brake cylinder material, obtaining allowable stress of the brake cylinder, and based on brake pressure and a piston acting area, obtaining axial load of the brake cylinder; S2, presetting a value range of the outer diameter of a brake cylinder and the inner diameter of the brake cylinder based on the brake moment requirement