CN117272551B - Most preferred type method of ball screw in optical image quality monitoring system - Google Patents
Most preferred type method of ball screw in optical image quality monitoring system Download PDFInfo
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Abstract
The invention discloses a ball screw optimal selection method in an optical image quality monitoring system, which belongs to the technical field of mechanical-electrical integration of optical systems and comprises the following steps: based on the axial load-permitting influence element of the ball screw, obtaining the minor diameter of the reference thread of the ball screw; obtaining a reference outer diameter of the ball screw based on the non-resonant rotation speed influencing element of the ball screw; obtaining a reference rated static load of the screw nut based on an allowable maximum axial load required by the screw nut; based on the service life influencing elements of the ball screw, obtaining the reference service life of the ball screw; and selecting the ball screw to be selected in the optical image quality monitoring system to obtain the optimal ball screw. The invention fully considers various typical load working conditions, ensures that the ball screw has enough precision, and simultaneously focuses on the load capacity of the screw nut so as to obtain better dynamic performance, thereby solving the problem that the optimal ball screw is difficult to quickly select during optical image quality monitoring.
Description
Technical Field
The invention belongs to the technical field of mechanical and electrical integration of optical systems, and particularly relates to a most preferred type method of a ball screw in an optical image quality monitoring system.
Background
Scanning mechanisms in optical image quality detection systems are often required to have the ability to move radially and axially. The realization of the linear motion linear feeding mechanism is indispensable for the one-dimensional position adjustment of the plane mirror. Whereas current linear feed mechanisms typically require a ball screw for mechanical transmission. The linear feeding mechanism constructed based on the ball screw has the outstanding advantages of high rigidity, high reliability, simple structure, insensitivity to interference and the like, is used for realizing various linear feeding motions, and is widely applied in the industrial field. The selection of a proper ball screw is a core step for guaranteeing the system performance, and how to quickly and accurately finish the ball screw type selection becomes a key problem to be solved urgently.
The ball screw type selection work is mainly completed by engineers according to experience, the process is repeated, the efficiency is low, meanwhile, in order to ensure the stability, the accuracy and the efficiency of a linear feeding mechanism in an optical image quality monitoring system, the ball screw with the high precision grade is always directly selected, the cost and the performance waste are easy to be caused, and the experience method is difficult to effectively popularize.
Disclosure of Invention
Aiming at the defects in the prior art, the most preferred method of the ball screw in the optical image quality monitoring system provided by the invention fully considers various typical load working conditions, ensures that the ball screw has enough precision, simultaneously focuses on the load capacity of the screw nut to obtain better dynamic performance, and solves the problem that the optimal ball screw is difficult to quickly select during optical image quality monitoring.
In order to achieve the aim of the invention, the invention adopts the following technical scheme:
the invention provides a most preferred method of a ball screw in an optical image quality monitoring system, which comprises the following steps:
s1, obtaining a small diameter of a reference thread of a ball screw based on an axial load influence element of the ball screw;
s2, obtaining a reference outer diameter of the ball screw based on the non-resonant rotation speed influence element of the ball screw;
s3, obtaining a reference rated static load of the screw nut based on the allowable maximum axial load required by the screw nut;
s4, obtaining the reference service life of the ball screw based on the service life influencing elements of the ball screw;
s5, selecting the ball screw to be selected in the optical image quality monitoring system based on the small diameter of the ball screw reference screw, the outer diameter of the ball screw reference, the rated static load of the screw nut reference and the service life of the ball screw reference, so as to obtain the optimal ball screw.
The beneficial effects of the invention are as follows: the invention provides a ball screw optimal selection method in an optical image quality monitoring system, which is used for selecting a ball screw to be selected in the optical image quality monitoring system from axial load bearing requirement, non-resonance rotating speed requirement, axial load requirement of a screw nut and service life requirement of the ball screw respectively, fully controlling and selecting the ball screw from load bearing capacity, anti-ball screw mechanism resonance capacity, nut load bearing capacity and service life length, and finally selecting the ball screw optimally under the condition of meeting all quality control selection modes, thereby fully considering various typical load conditions, ensuring that the ball screw has enough precision, simultaneously focusing on the screw nut load capacity, effectively saving time and economic cost and improving the optimal selection efficiency of the ball screw in the optical image quality monitoring system.
Further, the step S1 includes the following steps:
s11, obtaining allowable buckling load, allowable pulling and lifting compression load, allowable tensile and compression stress, interval to be installed and mode to be installed required by the ball screw, and taking the allowable buckling load, the allowable pulling and lifting compression load, the allowable tensile and compression stress, the interval to be installed and the mode to be installed as an axial allowable load influence element of the ball screw;
s12, respectively constructing a buckling load critical model and a pulling-up compression load critical model;
s13, based on the axial load influence elements of the ball screw, calculating to obtain a first screw shaft thread minor diameter and a second screw shaft thread minor diameter through a buckling load critical model and a pulling compression load critical model respectively;
s14, selecting a relatively larger thread diameter value from the first screw shaft thread diameter and the second screw shaft thread diameter as the ball screw reference thread diameter.
The beneficial effects of adopting the further scheme are as follows: according to the invention, the buckling load critical model and the pulling compression load critical model are respectively constructed from the fact that the ball screw cannot bend and cannot yield under the action of the maximum axial load, and critical calculation is carried out on the screw thread minor diameter from the ball screw installation requirement, the axial load bearing requirement and the pulling compression load bearing requirement to obtain the ball screw reference screw thread minor diameter, so that a foundation is provided for realizing the optimal selection of the ball screw in the optical image quality monitoring system.
Further, the calculation expression of the buckling load critical model in S12 is as follows:
wherein,representing admissible contusion Qu Zaihe>Representing the first coefficient related to the mode to be installed, < ->Representing a second coefficient related to the mode to be installed, < >>Representing Young's modulus, I representing the minimum end face secondary distance of the screw shaft, < >>Representing the minor diameter of the first screw shaft thread, +.>Representing the pitch to be installed.
The beneficial effects of adopting the further scheme are as follows: the invention provides a calculation method of a buckling load critical model, which is used for limiting the screw thread minor diameter critically through the allowable buckling load, the to-be-installed mode and the to-be-installed interval required by a ball screw in an optical image quality monitoring system, and provides a basis for defining the reference screw thread minor diameter of the ball screw.
Further, the calculation expression of the pull-up compression load critical model in S12 is as follows:
wherein,indicating allowable pull-up compression load,/->Indicating allowable tensile compressive stress +.>Representing the minor diameter of the second screw shaft thread.
The beneficial effects of adopting the further scheme are as follows: the invention provides a calculation method of a critical model of a lifting compression load, which is used for limiting the minor diameter of a screw thread in a critical way through the allowable lifting compression load and the allowable lifting compression stress required by a ball screw in an optical image quality monitoring system, thereby providing a foundation for defining the reference minor diameter of the screw thread of the ball screw.
Further, the step S2 includes the following steps:
s21, acquiring the allowable critical rotation speed, the interval to be installed, the parameters related to the section and the moment of inertia, the material density and the mode to be installed required by the ball screw, and taking the parameters as non-resonance rotation speed influencing elements of the ball screw;
s22, constructing a non-resonance rotating speed critical model;
s23, calculating the minimum diameter of the screw groove through a non-resonance rotation speed critical model based on the non-resonance rotation speed influencing element of the ball screw, and taking the minimum diameter as the reference outer diameter of the ball screw.
The beneficial effects of adopting the further scheme are as follows: according to the invention, the natural frequency of the ball screw shaft is gradually approaching to the natural frequency of the screw shaft along with the increase of the rotational speed of the ball screw, but resonance cannot occur, a non-resonance rotational speed critical model is constructed, and critical calculation is performed on the outer diameter of the ball screw according to the installation requirement, the material requirement and the rotational speed requirement of the ball screw, so that the reference outer diameter of the ball screw is obtained, and a basis is provided for realizing the optimal selection of the ball screw in an optical image quality monitoring system.
Further, the calculation expression of the non-resonant rotation speed critical model in S22 is as follows:
wherein,indicating allowable critical rotation speed, ">Representing a third coefficient related to the mode to be installed, < ->Representing Young's modulus, & lt & gt>Representing the coefficient of correlation of screw section and moment of inertia, +.>Indicating the rotational speed safety proportionality coefficient>Represents the distance to be installed, r represents the density of the material, A represents the area of the section where the minimum diameter of the screw groove is located, +.>Represents the minimum diameter of the screw groove, < >>And the fourth coefficient related to the mode to be installed is represented.
The beneficial effects of adopting the further scheme are as follows: the invention provides a calculation method of a non-resonance rotating speed critical model, which is used for limiting the outer diameter of a screw in a critical way through the allowable critical rotating speed, the distance to be installed, the parameters related to the section and the moment of inertia and the material density required by the ball screw in an optical image quality monitoring system, and providing a basis for defining the reference outer diameter of the ball screw.
Further, the calculation expression of the reference rated dead load of the lead screw nut in the step S3 is as follows:
wherein,indicating that the screw nut is referenced to nominal load, < >>Indicating the allowable maximum axial load +.>Representing the static safety proportionality coefficient of the nut.
The beneficial effects of adopting the further scheme are as follows: the invention provides a calculation method for a reference rated load of a screw nut, aiming at the screw nut with a definite steel ball circulation mode, the influence of inertia during impact, starting and stopping is considered, and the reliability of a linear feeding mechanism constructed by a ball screw is ensured by setting a static safety proportion coefficient of the nut.
Further, the step S4 includes the following steps:
s41, acquiring a rated dynamic load, a motion speed and a vibration impact related load coefficient, an allowable maximum axial load, an allowable critical rotation speed, a lead and a stroke of a nut required by the ball screw, and taking the rated dynamic load, the motion speed and the vibration impact related load coefficient, the allowable maximum axial load, the allowable critical rotation speed, the lead and the stroke as service life influencing elements of the ball screw;
s42, constructing a service life model;
s43, calculating the service life of the ball screw through a service life model based on the service life influencing element of the ball screw, and taking the service life as the reference service life of the ball screw.
The beneficial effects of adopting the further scheme are as follows: according to the invention, aiming at the fatigue damage of the rolling surface of the ball screw when the bearing stress exceeds the limit, which is expressed as the total rotation number of the ball screw, a service life model is constructed, and the service life of the ball screw is calculated in a critical way from the total rotation number requirement and the actual running time requirement of the ball screw, so that the reference service life of the ball screw is obtained, and a basis is provided for realizing the optimal selection of the ball screw in an optical image quality monitoring system.
Further, the calculation expression of the service life model in S42 is as follows:
wherein,indicating the service life of the ball screw, < >>Indicating the rated dynamic load of the nut->Representing the motion speed and the vibration impact related load factor, < + >>Indicating the allowable maximum axial load +.>Represents the allowable critical rotation speed, s represents the rotation speed safety ratio coefficient, < ->Indicates the lead, n indicates the number of reciprocations per minute of the linear feed mechanism, +.>Representing travel.
The beneficial effects of adopting the further scheme are as follows: the invention provides a calculation method of a service life model, which is characterized in that the service life of a ball screw is limited in a critical way through the rated dynamic load, the motion speed and the vibration impact related load coefficient, the allowable maximum axial load, the allowable critical rotating speed, the ball screw lead, the ball screw stroke and the reciprocating times of a linear feeding mechanism per minute of a nut required by the ball screw in an optical image quality monitoring system, and a foundation is provided for defining the reference thread diameter of the ball screw.
Further, the step S5 includes the following steps:
s51, acquiring a specification parameter table of a ball screw to be selected in the optical image quality monitoring system, and taking the specification parameter table as a first specification parameter table of the ball screw to be selected;
s52, based on the first to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws with the small diameters of the ball screw threads smaller than the small diameters of the reference ball screw threads in the table, deleting all information of all selected to-be-selected ball screws, and obtaining a second to-be-selected ball screw specification parameter table;
s53, based on the second to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws with the outer diameters of the ball screws larger than the reference outer diameter of the ball screws in the table, and deleting all information of all selected to-be-selected ball screws to obtain a third to-be-selected ball screw specification parameter table;
s54, based on the third to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws smaller than the rated static load of the screw nut in the table, deleting all information of all to-be-selected ball screws to obtain a fourth to-be-selected ball screw specification parameter table;
s55, based on the fourth to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws with the service lives of the ball screws being less than the reference service lives of the ball screws in the table, deleting all information of all to-be-selected ball screws, and obtaining a fifth to-be-selected ball screw specification parameter table;
and S56, selecting the ball screw to be selected with the lowest price as the optimal ball screw based on the fifth ball screw specification parameter table to be selected.
The beneficial effects of adopting the further scheme are as follows: based on the requirement of the optical image quality monitoring system on the ball screw, the ball screw reference screw thread diameter, the ball screw reference outer diameter, the screw nut reference rated static load and the ball screw reference service life are obtained through analysis and processing, and the ball screw to be selected after meeting the above required conditions can be used for the ball screw of the linear feeding mechanism in the optical image quality monitoring system, so that the most preferred type of the ball screw in the optical image quality monitoring system can be completed quickly, accurately and efficiently only by controlling the cost.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are needed in the embodiments will be briefly described below, it being understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and other related drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a flow chart of the steps of a method for optimizing a ball screw in an optical image quality monitoring system according to an embodiment of the present invention.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. The components of the embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations. Thus, the following detailed description of the embodiments of the invention, as presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be made by a person skilled in the art without making any inventive effort, are intended to be within the scope of the present invention.
Rated static load: when the sum of permanent deformation of the ball and the raceway reaches 0.0001 times of the diameter of the ball, the contact part bearing the maximum stress is subjected to a static load with unchanged size and direction.
The screw rod is used for a one-dimensional motion platform in an optical image quality monitoring system and is mainly used for linear motion of a plane mirror and a plane mirror adjusting mechanism. The lead represents the distance of the nut moving along the axial direction when the screw rotates for one circle (360 degrees), the unit is mm, and the lead of the common screw pair takes 1/4-1/2 of the diameter of the screw; the lead is too large, so that the manufacturing difficulty of the ball screw pair is increased, the precision is difficult to improve, the bearing of the screw pair is reduced, and the starting moment of the servo motor is also increased. The screw supporting mode is mainly selected according to the length, the rotating speed and the positioning precision of the screw. The simple installation mode with two fixed ends can be selected in the occasions of longer screw length and lower rotating speed, especially in the occasions of vertically lifting the load.
In one embodiment of the present invention, as shown in fig. 1, the present invention provides a most preferred method for a ball screw in an optical image quality monitoring system, comprising the steps of:
under a certain outer diameter of the screw rod, the screw rod can possibly not bear the maximum axial load under the use condition to bend, so that the screw rod has enough rigidity to ensure that the screw rod can not bend and deform under the maximum axial load due to the fact that the small diameter and the outer diameter of the screw rod thread are selected to meet the requirement of the axial allowable load; the axial load is the basis for calculating the torque load, and the torque load can be calculated only after the axial load is calculated, and the torque load is an important basis for motor model selection.
S1, obtaining a small diameter of a reference thread of a ball screw based on an axial load influence element of the ball screw;
the step S1 comprises the following steps:
s11, obtaining allowable buckling load, allowable pulling and lifting compression load, allowable tensile and compression stress, interval to be installed and mode to be installed required by the ball screw, and taking the allowable buckling load, the allowable pulling and lifting compression load, the allowable tensile and compression stress, the interval to be installed and the mode to be installed as an axial allowable load influence element of the ball screw;
s12, respectively constructing a buckling load critical model and a pulling-up compression load critical model;
the calculation expression of the buckling load critical model in S12 is as follows:
wherein,representing admissible contusion Qu Zaihe>Representing the first coefficient related to the mode to be installed, < ->Representing a second coefficient related to the mode to be installed, < >>Representing Young's modulus, I representing the minimum end face secondary distance of the screw shaft, < >>Representing the minor diameter of the first screw shaft thread, +.>Representing the pitch to be installed.
In this embodiment, when the to-be-mounted manner adopted at two ends of the ball screw is fixed-free, the value of the correlation coefficient between the first and to-be-mounted manners is: and 0.25, wherein the correlation coefficient of the second mode and the mode to be installed has the following value: 1.3; when the to-be-installed mode adopted at the two ends of the ball screw is fixed-supported, the value of the correlation coefficient of the first to-be-installed mode is as follows: 2, the value of the correlation coefficient of the second mode and the mode to be installed is as follows: 10; when the to-be-installed mode adopted at the two ends of the ball screw is fixed-fixed, the value of the correlation coefficient of the first to-be-installed mode is as follows: and 4, the value of the correlation coefficient of the second mode and the mode to be installed is as follows: 20, a step of;
the calculation expression of the pull-up compression load critical model in S12 is as follows:
wherein,indicating allowable pull-up compression load,/->Indicating allowable tensile compressive stress +.>Representing the minor diameter of the second screw shaft thread.
S13, based on the axial load influence elements of the ball screw, calculating to obtain a first screw shaft thread minor diameter and a second screw shaft thread minor diameter through a buckling load critical model and a pulling compression load critical model respectively;
s14, selecting a relatively larger thread diameter value from the first screw shaft thread diameter and the second screw shaft thread diameter as the ball screw reference thread diameter.
As the rotational speed of the ball screw increases, the natural frequency of the screw shaft gradually approaches, and resonance occurs, so that the ball screw cannot continue to rotate. Therefore, it is necessary to use the material below the resonance point (dangerous speed). When the ball screw is selected, bending and yield checking are needed, and the screw is required to be used on the premise of not generating resonance. As the rotational speed of the screw increases, the natural frequency of the screw gradually approaches, and the ball screw mechanism resonates and cannot be used. The natural frequency corresponds to a critical rotation speed of the screw, and the outer diameter of the screw is closely related to the natural frequency, so that reference selection is needed to ensure that the screw runs below the natural frequency (critical rotation speed), namely the maximum rotation speed of the screw cannot exceed the critical rotation speed, and the rotation speed safety proportionality coefficient is 0.8 in the embodiment.
S2, obtaining a reference outer diameter of the ball screw based on the non-resonant rotation speed influence element of the ball screw;
the step S2 comprises the following steps:
s21, acquiring the allowable critical rotation speed, the interval to be installed, the parameters related to the section and the moment of inertia, the material density and the mode to be installed required by the ball screw, and taking the parameters as non-resonance rotation speed influencing elements of the ball screw;
s22, constructing a non-resonance rotating speed critical model;
the calculation expression of the non-resonance rotation speed critical model in the S22 is as follows:
wherein,indicating allowable critical rotation speed, ">Representing a third coefficient related to the mode to be installed, < ->Representing Young's modulus, & lt & gt>Representing the coefficient of correlation of screw section and moment of inertia, +.>Indicating the rotational speed safety proportionality coefficient>Represents the distance to be installed, r represents the density of the material, A represents the area of the section where the minimum diameter of the screw groove is located, +.>Represents the minimum diameter of the screw groove, < >>And the fourth coefficient related to the mode to be installed is represented.
In this embodiment, when the to-be-mounted mode adopted at two ends of the ball screw is fixed-fixed, the value of the correlation coefficient between the third and to-be-mounted modes is: 4.73, the fourth and the mode to be installed have the following correlation coefficients: 21.9; when the to-be-installed mode adopted at the two ends of the ball screw is fixed-supported, the third and to-be-installed mode correlation coefficient is valued as follows: 3.927, the fourth and the to-be-installed mode correlation coefficients are as follows: 15.1; when the mounting mode to be adopted at the two ends of the ball screw is support-support, the third and the coefficient related to the mounting mode are as follows: 3.142, the fourth and the mode to be installed have the following correlation coefficients: 9.7; when the to-be-installed mode adopted at the two ends of the ball screw is fixed-free, the value of the correlation coefficient of the third to-be-installed mode is as follows: 1.875, the fourth and the mode to be installed have the following correlation coefficients: 3.4;
s23, calculating the minimum diameter of the screw groove through a non-resonance rotation speed critical model based on the non-resonance rotation speed influencing element of the ball screw, and taking the minimum diameter as the reference outer diameter of the ball screw.
The screw nut is a core part of the ball screw mechanism, and the quality of the ball nut determines the operation characteristics of the whole ball screw mechanism. The nuts of the ball screw can be divided into a bent pipe type, a circulator type and an end cover type according to the circulation mode of the steel ball, and the three circulation modes can be confirmed in advance as subjective requirements before the screw nuts are determined to refer to rated static loads; when the ball nut is in a static state or an operating state, if the ball nut bears excessive load or impact load, local permanent deformation can occur between the ball and the rollaway nest, and the normal operation of the ball screw mechanism can be influenced when the permanent deformation exceeds a certain degree.
S3, obtaining a reference rated static load of the screw nut based on the allowable maximum axial load required by the screw nut;
the calculation expression of the reference rated static load of the screw nut in the step S3 is as follows:
wherein,indicating that the screw nut is referenced to nominal load, < >>Indicating the allowable maximum axial load +.>Representing the static safety proportionality coefficient of the nut.
The static safety proportionality coefficient of the nut is related to the using machine and the load condition, in the embodiment, when the using machine is a common machine and the load condition is no vibration or impact, the value range of the static safety proportionality coefficient of the nut is as follows: 1.0 to 3.5; when the machine is a common machine and the load condition is vibration or impact, the value range of the static safety proportionality coefficient of the nut is as follows: 2.0 to 5.0; when the machine is used as a machine tool and the load condition is no vibration or impact, the value range of the static safety proportionality coefficient of the nut is as follows: 1.0 to 4.0; when the machine is used as a machine tool and the load condition is vibration or impact, the value range of the static safety proportionality coefficient of the nut is as follows: 2.5-7.0;
s4, obtaining the reference service life of the ball screw based on the service life influencing elements of the ball screw;
the step S4 comprises the following steps:
s41, acquiring a rated dynamic load, a motion speed and a vibration impact related load coefficient, an allowable maximum axial load, an allowable critical rotation speed, a lead and a stroke of a nut required by the ball screw, and taking the rated dynamic load, the motion speed and the vibration impact related load coefficient, the allowable maximum axial load, the allowable critical rotation speed, the lead and the stroke as service life influencing elements of the ball screw;
s42, constructing a service life model;
the calculation expression of the service life model in S42 is as follows:
wherein,representation ofService life of ball screw>Indicating the rated dynamic load of the nut->Representing the motion speed and the vibration impact related load factor, < + >>Indicating the allowable maximum axial load +.>Represents the allowable critical rotation speed, s represents the rotation speed safety ratio coefficient, < ->Indicates the lead, n indicates the number of reciprocations per minute of the linear feed mechanism, +.>Representing travel.
The motion speed and the vibration impact related load coefficient are related to the vibration, the impact degree and the running speed of the ball screw, in this embodiment, when the vibration and the impact degree of the ball screw are small and the speed is a micro speed (less than 0.25 m/s), the motion speed and the vibration impact related load coefficient are taken as: 1.0-1.2; when the vibration and impact degree of the ball screw are small and the speed is low (more than 0.25 m/s and less than 1 m/s), the motion speed and the vibration impact related load coefficient are in the range of: 1.2-1.5; when the vibration and impact degree of the ball screw are medium and the speed is medium (more than 1 meter per second and less than 2 meters per second), the range of the motion speed and the vibration impact related load coefficient is as follows: 1.5-2.0; when the vibration and impact degree of the ball screw are large and the speed is high (more than 0.25 m/s and less than 1 m/s), the motion speed and the vibration impact related load coefficient are in the range of: 2.0-3.5; the magnitude of vibration and impact degree can be selected according to actual conditions.
S43, calculating the service life of the ball screw through a service life model based on the service life influencing element of the ball screw, and taking the service life as the reference service life of the ball screw.
S5, selecting the ball screw to be selected in the optical image quality monitoring system based on the small diameter of the ball screw reference screw, the outer diameter of the ball screw reference, the rated static load of the screw nut reference and the service life of the ball screw reference, so as to obtain the optimal ball screw.
The step S5 comprises the following steps:
s51, acquiring a specification parameter table of a ball screw to be selected in the optical image quality monitoring system, and taking the specification parameter table as a first specification parameter table of the ball screw to be selected;
s52, based on the first to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws with the small diameters of the ball screw threads smaller than the small diameters of the reference ball screw threads in the table, deleting all information of all selected to-be-selected ball screws, and obtaining a second to-be-selected ball screw specification parameter table;
s53, based on the second to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws with the outer diameters of the ball screws larger than the reference outer diameter of the ball screws in the table, and deleting all information of all selected to-be-selected ball screws to obtain a third to-be-selected ball screw specification parameter table;
s54, based on the third to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws smaller than the rated static load of the screw nut in the table, deleting all information of all to-be-selected ball screws to obtain a fourth to-be-selected ball screw specification parameter table;
s55, based on the fourth to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws with the service lives of the ball screws being less than the reference service lives of the ball screws in the table, deleting all information of all to-be-selected ball screws, and obtaining a fifth to-be-selected ball screw specification parameter table;
and S56, selecting the ball screw to be selected with the lowest price as the optimal ball screw based on the fifth ball screw specification parameter table to be selected.
According to the invention, the critical model construction is objectively carried out on the requirement of the ball screw in the optical image quality monitoring system, so that the critical parameters meeting the specification parameters of the construction requirement of the optical image quality monitoring system are conveniently obtained, and the cost is controlled under the condition of meeting the objective necessary condition, so that the ball screw is selected by the optical image quality monitoring system more quickly, efficiently, accurately and cost-effectively.
The foregoing is merely illustrative of the present invention, and the present invention is not limited thereto, and any person skilled in the art will readily recognize that variations or substitutions are within the scope of the present invention.
Claims (2)
1. A method of most preferred type of ball screw in an optical image quality monitoring system, comprising the steps of:
s1, obtaining a small diameter of a reference thread of a ball screw based on an axial load influence element of the ball screw;
the step S1 comprises the following steps:
s11, obtaining allowable buckling load, allowable pulling and lifting compression load, allowable tensile and compression stress, interval to be installed and mode to be installed required by the ball screw, and taking the allowable buckling load, the allowable pulling and lifting compression load, the allowable tensile and compression stress, the interval to be installed and the mode to be installed as an axial allowable load influence element of the ball screw;
s12, respectively constructing a buckling load critical model and a pulling-up compression load critical model;
the calculation expression of the buckling load critical model in S12 is as follows:
wherein,representing admissible contusion Qu Zaihe>Representing the first coefficient related to the mode to be installed, < ->Representing a second coefficient related to the mode to be installed, < >>Represents the young's modulus,Irepresenting the minimum end face secondary distance of the screw shaft, < >>Representing the minor diameter of the first screw shaft thread, +.>Representing the space to be installed;
the calculation expression of the pull-up compression load critical model in S12 is as follows:
wherein,indicating allowable pull-up compression load,/->Indicating allowable tensile compressive stress +.>Representing the minor diameter of the second screw shaft thread;
s13, based on the axial load influence elements of the ball screw, calculating to obtain a first screw shaft thread minor diameter and a second screw shaft thread minor diameter through a buckling load critical model and a pulling compression load critical model respectively;
s14, selecting a relatively larger thread small diameter value from the first screw shaft thread small diameter and the second screw shaft thread small diameter as a ball screw reference thread small diameter;
s2, obtaining a reference outer diameter of the ball screw based on the non-resonant rotation speed influence element of the ball screw;
the step S2 comprises the following steps:
s21, acquiring the allowable critical rotation speed, the interval to be installed, the parameters related to the section and the moment of inertia, the material density and the mode to be installed required by the ball screw, and taking the parameters as non-resonance rotation speed influencing elements of the ball screw;
s22, constructing a non-resonance rotating speed critical model;
the calculation expression of the non-resonance rotation speed critical model in the S22 is as follows:
wherein,indicating allowable critical rotation speed, ">Representing a third coefficient related to the mode to be installed, < ->Representing Young's modulus, & lt & gt>Representing the coefficient of correlation of screw section and moment of inertia, +.>Indicating the rotational speed safety proportionality coefficient>Indicating the distance to be installed,rindicating materialThe density of the material is set at the same time,Arepresents the area of the section where the minimum diameter of the screw groove is located, < >>Represents the minimum diameter of the screw groove, < >>Representing a fourth coefficient related to the mode to be installed;
s23, calculating the minimum diameter of a screw groove based on a non-resonant rotating speed influence element of the ball screw through a non-resonant rotating speed critical model, and taking the minimum diameter as a reference outer diameter of the ball screw;
s3, obtaining a reference rated static load of the screw nut based on the allowable maximum axial load required by the screw nut;
the calculation expression of the reference rated static load of the screw nut in the step S3 is as follows:
wherein,indicating that the screw nut is referenced to nominal load, < >>Indicating the allowable maximum axial load +.>Representing the static safety proportionality coefficient of the nut;
s4, obtaining the reference service life of the ball screw based on the service life influencing elements of the ball screw;
the step S4 comprises the following steps:
s41, acquiring a rated dynamic load, a motion speed and a vibration impact related load coefficient, an allowable maximum axial load, an allowable critical rotation speed, a lead and a stroke of a nut required by the ball screw, and taking the rated dynamic load, the motion speed and the vibration impact related load coefficient, the allowable maximum axial load, the allowable critical rotation speed, the lead and the stroke as service life influencing elements of the ball screw;
s42, constructing a service life model;
the calculation expression of the service life model in S42 is as follows:
wherein,indicating the service life of the ball screw, < >>Indicating the rated dynamic load of the nut->Representing the motion speed and the vibration impact related load factor, < + >>Indicating the allowable maximum axial load +.>Indicating the allowable critical rotation speed of the motor,sindicating the rotational speed safety proportionality coefficient>The lead is indicated as the term "lead",nindicates the reciprocating times of the linear feeding mechanism per minute, +.>Representing a trip;
s43, calculating the service life of the ball screw based on the service life influencing element of the ball screw through a service life model, and taking the service life as the reference service life of the ball screw;
s5, selecting the ball screw to be selected in the optical image quality monitoring system based on the small diameter of the ball screw reference screw, the outer diameter of the ball screw reference, the rated static load of the screw nut reference and the service life of the ball screw reference, so as to obtain the optimal ball screw.
2. The method of claim 1, wherein S5 comprises the steps of:
s51, acquiring a specification parameter table of a ball screw to be selected in the optical image quality monitoring system, and taking the specification parameter table as a first specification parameter table of the ball screw to be selected;
s52, based on the first to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws with the small diameters of the ball screw threads smaller than the small diameters of the reference ball screw threads in the table, deleting all information of all selected to-be-selected ball screws, and obtaining a second to-be-selected ball screw specification parameter table;
s53, based on the second to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws with the outer diameters of the ball screws larger than the reference outer diameter of the ball screws in the table, and deleting all information of all selected to-be-selected ball screws to obtain a third to-be-selected ball screw specification parameter table;
s54, based on the third to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws smaller than the rated static load of the screw nut in the table, deleting all information of all to-be-selected ball screws to obtain a fourth to-be-selected ball screw specification parameter table;
s55, based on the fourth to-be-selected ball screw specification parameter table, selecting all to-be-selected ball screws with the service lives of the ball screws being less than the reference service lives of the ball screws in the table, deleting all information of all to-be-selected ball screws, and obtaining a fifth to-be-selected ball screw specification parameter table;
and S56, selecting the ball screw to be selected with the lowest price as the optimal ball screw based on the fifth ball screw specification parameter table to be selected.
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106763601A (en) * | 2016-12-29 | 2017-05-31 | 重庆田畸实业有限公司 | Ball-screw selection designing method |
| CN108896297A (en) * | 2018-04-20 | 2018-11-27 | 南京理工大学 | A kind of ball screw assembly, rated static load test macro and method |
| CN109387363A (en) * | 2018-10-22 | 2019-02-26 | 北京工业大学 | A kind of ball screw assembly, positioning accuracy decline prediction technique |
| CN110633515A (en) * | 2019-08-29 | 2019-12-31 | 南京理工大学 | Method for calculating fatigue life of ball screw pair under extreme load extremely short time working condition |
| CN112835325A (en) * | 2021-01-03 | 2021-05-25 | 清华大学 | Servo motor model selection method for ball screw feeding system |
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2023
- 2023-11-20 CN CN202311547143.XA patent/CN117272551B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106763601A (en) * | 2016-12-29 | 2017-05-31 | 重庆田畸实业有限公司 | Ball-screw selection designing method |
| CN108896297A (en) * | 2018-04-20 | 2018-11-27 | 南京理工大学 | A kind of ball screw assembly, rated static load test macro and method |
| CN109387363A (en) * | 2018-10-22 | 2019-02-26 | 北京工业大学 | A kind of ball screw assembly, positioning accuracy decline prediction technique |
| CN110633515A (en) * | 2019-08-29 | 2019-12-31 | 南京理工大学 | Method for calculating fatigue life of ball screw pair under extreme load extremely short time working condition |
| CN112835325A (en) * | 2021-01-03 | 2021-05-25 | 清华大学 | Servo motor model selection method for ball screw feeding system |
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