CN114462277B - Design method of pipeline fluid control direct-acting electromagnetic valve in chemical field - Google Patents
Design method of pipeline fluid control direct-acting electromagnetic valve in chemical field Download PDFInfo
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- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims abstract description 43
- 238000012795 verification Methods 0.000 claims abstract description 8
- 239000000463 material Substances 0.000 claims description 11
- 238000004804 winding Methods 0.000 claims description 11
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- 229910052802 copper Inorganic materials 0.000 claims description 5
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- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/02—Reliability analysis or reliability optimisation; Failure analysis, e.g. worst case scenario performance, failure mode and effects analysis [FMEA]
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Abstract
The invention discloses a design method of a direct-acting electromagnetic valve, which mainly comprises a valve body, a spring, an electromagnetic coil, a movable iron core and a fixed iron core; the method comprises the following steps: determining the basic dimensions of the voltage, the switch closing time and the outer diameter of the electromagnetic valve; calculating the spring force required by closing the electromagnetic valve; designing a spring according to the spring force, and performing function verification on the spring; calculating the electromagnetic force required by the electromagnetic valve when the electromagnetic valve is opened; and constructing a magnetic circuit structure of the electromagnetic valve according to the electromagnetic force and performing magnetic force verification. The electromagnetic valve is wide in application range and high in universality, can design the electromagnetic valve with more stable performance according to the response speed requirements of the electromagnetic valve and the voltage provided by the actual use field under different use conditions, can effectively avoid the electromagnetic coil from heating when the electromagnetic valve works for a long time, and can effectively avoid the burning of the electromagnetic coil and the reduction of the tightness of the valve body caused by the long-time use of the electromagnetic valve due to the large electromagnetic force, thereby reducing the equipment failure rate and the power consumption of the electromagnetic valve, and further ensuring the safe operation of the electromagnetic valve.
Description
Technical Field
The invention relates to a design method of a direct-acting electromagnetic valve, in particular to a design method of a direct-acting electromagnetic valve taking spring force and electromagnetic force of the electromagnetic valve into consideration.
Background
Solenoid valves are the basic elements of automation for controlling industrial equipment by electromagnetic force, and play an extremely important role in chemical plant systems. The chemical production needs to be precisely controlled aiming at different loops to generate controllable chemical reaction, so that the required products can be efficiently produced, and the purpose of precisely controlling each loop is to control important variables in the chemical production: pressure, flow, liquid level, temperature, etc., each of the critical loops has a corresponding indicator and alarm device to ensure that the control variables are within the operating range. Solenoid valves are the most commonly used variable regulating elements in process flows. The electromagnetic valve receives the control signal to regulate the movement of the substances in the pipeline to control the process reaction according to a set mode, so that the electromagnetic valve plays a vital role in chemical production.
Along with the rapid development of science and technology, the requirements of chemical production on the reliability of a process control system are higher and higher, and the currently used electromagnetic valve has the following problems under the working condition: the coil is heated when the electromagnetic valve is electrified for a long time, so that the electromagnetic coil is easy to burn out, and the service life of the electromagnetic valve is shortened; when the electromagnetic valve is opened, the electromagnetic force is larger, so that the tightness of the electromagnetic valve can be reduced after long-time use; the time of the opening and closing process of the electromagnetic valve cannot be flexibly designed according to the corresponding actual requirements of industry.
Disclosure of Invention
The invention aims to: the invention aims to provide a direct-acting electromagnetic valve design method which is wide in application range and strong in universality.
The technical scheme is as follows: the invention relates to a pipeline fluid control direct-acting electromagnetic valve in the chemical field, which consists of a valve body (3), a spring (5), an electromagnetic coil (1), a movable iron core (2) and a fixed iron core (4); the design method comprises the following steps:
(1) Determining working parameters of the electromagnetic valve according to the place where the electromagnetic valve is used;
(2) Calculating the spring force when the electromagnetic valve is closed;
(3) Designing a spring according to the spring force, performing functional verification on the spring, judging whether the spring force performance of the spring meets the requirement, and if not, redesigning the structural parameters of the spring;
(4) Calculating the electromagnetic force required by the electromagnetic valve when the electromagnetic valve is opened;
(5) And designing magnetic circuit structure parameters of the electromagnetic valve according to the electromagnetic force required by the electromagnetic valve in a stable working state, constructing a magnetic circuit structure and performing magnetic force verification until the magnetic circuit structure meets the requirements, and otherwise, redesigning the magnetic circuit structure.
The working parameters of the electromagnetic valve in the step (1) comprise rated voltage, the number of spring supporting turns n, the mass m of the movable iron core, the working stroke x 1, the opening time t 1 and the closing time t 2.
The spring force in step (2) is calculated as follows:
Wherein F T1 is the spring force when the compression amount of the spring is x 1; f T2 is a preset spring pre-tightening force; m is the mass of the movable iron core; v is the moving speed of the movable iron core; t is the closing time of the electromagnetic valve; x 1 is the movable iron core displacement; x 2 is the spring compression when the pre-load force is applied by the spring; g is gravitational acceleration.
The step (3) comprises the following steps:
The maximum spring force applied during closing of the solenoid valve is calculated as follows:
FT＝-k(x1+x2)
Where k is the spring stiffness coefficient.
The stiffness coefficient of the spring is mainly equal to the material of the spring, the diameter of the spring wire, the effective number of turns and the diameter of the spring, and the expression is as follows:
Wherein G is the shear elastic modulus of the spring and is determined by the material of the spring; d is the diameter of the spring wire; n is the effective number of turns; d is the spring pitch diameter.
The spring winding ratio C, the spring wire diameter D and the spring pitch diameter D are determined as follows, depending on the work load that the spring is required to achieve in the mechanism device:
According to the determined shear elastic modulus, the spring wire diameter and the spring intermediate diameter D of the spring material, the effective number of turns n of the spring is determined as follows:
in the step (4), the electromagnetic force required for opening the electromagnetic valve is calculated as follows:
wherein, For the average effective force of F T1 during the plunger movement, the following equation is calculated:
in the step (5), the air gap sectional area S, the copper wire diameter D, the leakage inductance K f, the air gap length delta, the winding outer diameter D 1 and the winding shaft diameter D 2 of the electromagnetic valve are designed according to the following formula, so that the electromagnetic force F and the magnetic circuit structure parameters of the electromagnetic valve required under the stable working state of the electromagnetic valve meet the following formula:
The beneficial effects are that: compared with the prior art, the invention has the following remarkable advantages: the electromagnetic valve has the advantages that the electromagnetic valve is wide in application range and strong in universality, the electromagnetic valve with more stable performance can be designed according to the response speed requirements of the electromagnetic valve and the voltage provided by the actual use site under different use conditions, the problems that the electromagnetic coil burns out due to heating of the coil and the tightness of the valve body is reduced due to large electromagnetic force caused by long-time working of the electromagnetic valve can be effectively avoided, the equipment failure rate is reduced, the power consumption of the electromagnetic valve is reduced, and the safe operation of the electromagnetic valve is guaranteed. The electromagnetic valve structure can be designed in advance according to the actual requirements of industrial production, and the reliability of the electromagnetic valve performance is improved.
Drawings
Fig. 1 is a structural diagram of a solenoid valve according to the present invention.
FIG. 2 is a logic diagram of the structural design of the solenoid valve spring of the present invention.
Fig. 3 is a logic diagram of the design of the magnetic circuit structure of the electromagnetic valve.
Detailed Description
The technical scheme of the invention is further described below with reference to the accompanying drawings.
The working principle of the direct-acting electromagnetic valve in the embodiment is as follows: when the electromagnetic valve is powered on, a magnetic field generated by the electromagnetic coil magnetizes the movable iron core and the static iron core, the movable iron core moves upwards under the action of magnetic force, and at the moment, the valve is opened; when the electromagnetic valve is powered off, the movable iron core is reset under the action of the spring, and the valve is closed. The valve consists of a valve body (3), a spring (5), an electromagnetic coil (1), a movable iron core (2) and a fixed iron core (4); the design method comprises the following steps:
(1) Determining the basic dimensions of the voltage, the switching-on and switching-off time and the outer diameter of the electromagnetic valve according to the use requirements;
(2) Calculating the spring force required by closing the electromagnetic valve;
(3) Designing a spring according to the spring force, and performing function verification on the spring until the function of the spring meets the requirement, otherwise, redesigning the structure of the spring;
(4) Calculating the electromagnetic force required by the electromagnetic valve when the electromagnetic valve is opened;
(5) And constructing a magnetic circuit structure of the electromagnetic valve according to the electromagnetic force and performing magnetic force verification until the magnetic circuit structure meets the requirements, otherwise, redesigning the magnetic circuit structure.
1. The rated voltage, the number of spring supporting turns n, the moving iron core mass m, the working stroke x 1, the opening time t 1 and the closing time t 2 are determined according to the use place of the electromagnetic valve.
2. Movable iron core movement analysis when electromagnetic valve is closed
In order to enhance the tightness between the movable iron core and the base after the electromagnetic valve is closed, a pretightening force is applied to the spring, and the pretightening force F T2 is set according to the requirement.
FT2＝-kx2
At the moment of the power failure of the electromagnetic valve, the movable iron core starts to move under the action of spring force, and the movable iron core can be obtained according to a kinetic motion equation Sigma F=ma:
FT1＝kx1
Then the acceleration a 1 is:
wherein m is the mass of the movable iron core; v is the moving speed of the movable iron core; t is the closing time of the electromagnetic valve; f T1 is the spring force when the compression amount of the spring is x 1; f T2 is the pre-tightening force of the spring; x 1 is the working stroke of the movable iron core; x 2 is the amount of spring compression generated by the set spring preload.
After the electromagnetic valve is closed, the movable iron core starts to move downwards under the action of spring force and gravity of the movable iron core, the time used in the closing process of the movable iron core is t 1, and the electromagnetic valve can be obtained according to a kinetic equation of motion Sigma F=ma:
then the acceleration a 2 is:
During closing of the solenoid valve, F T1 becomes smaller as the plunger moves until it is 0. In the process, F T1 does work as follows:
Wherein W is F T1 which does work in the closing process of the movable iron core; is the average effective force of F T1 during the motion of the movable iron core.
The motion of the movable iron core in the closing process of the electromagnetic valve meets the energy conservation theorem, and the equation is as follows:
Then there is
The method can obtain:
F T1 can be obtained by substituting the known data m and F T2、x2、t1.
3. Spring design
According to the elasticity calculation formula of the compression spring, can obtain:
FT＝-kx
FT＝FT1+FT2
FT1＝-kx1
the maximum elastic force applied to the electromagnetic valve in the closing process is as follows:
FT＝-k(x1+x2)
Then:
The stiffness coefficient of the spring is mainly equal to the material of the spring, the diameter of the spring wire, the effective number of turns and the diameter of the spring, and the expression is as follows:
Wherein G is the shear elastic modulus of the spring material; d is the diameter of the spring wire; n is the effective number of turns; d is the spring pitch diameter.
From the above formula:
g is determined according to the material used for the spring, and the relation of the spring coiling ratio C is as follows:
The spring winding ratio has higher influence on the strength, the rigidity and the stability of the spring and the manufacturing difficulty of the spring. When the coiling is smaller, the spring stiffness is larger, and the coiling difficulty is larger; when the coiling ratio is large, the spring stiffness is small and the spring is easy to deform. The coiling ratio C of the general spring is approximately equal to 5-8, and the value range according to the coiling ratio C can be obtained:
The spring winding ratio, the spring wire diameter D and the spring pitch diameter D are determined according to the work load that the spring is required to achieve in the mechanism device. The spring twist ratio was selected according to the following table:
| d | 0.2～0.4 | 0.5～1 | 1.2～2 | 2.5～6 | 7～16 | ＞16 |
| C＝D/d | 7-14 | 5-12 | 5-10 | 4-9 | 4-8 | 4-6 |
The effective number of turns n of the spring is determined by the determined shear elastic modulus of the spring material, the spring wire diameter and the spring intermediate diameter D, namely:
and determining the structure of the spring according to the obtained spring wire diameter, the spring pitch diameter, the effective number of turns and the supporting number of turns, and verifying whether the strength, the stability and the fatigue strength of the spring meet the requirements or not according to the structural parameters of the spring.
The strength condition of the spring needs to satisfy the following formula:
wherein τ max is the maximum torsion force generated inside the spring wire under the maximum working load; k 1 curvature coefficients; [ tau ] allows torsional stress.
The stability condition of the spring needs to satisfy the following formula:
Wherein b c is a critical aspect ratio.
The spring wire is cylindrical and μ is selected according to the following table:
| Two-end slewing bearing μ=1 | 2.6 |
| One end is fixed, and the other end slewing bearing mu=0.7 | 3.7 |
| Two fixed supports μ=0.5 | 5.3 |
The fatigue strength of the spring needs to satisfy the following formula:
Wherein [ s ] is an allowable safety factor; τ 0 is the fatigue limit of the spring material.
4. Analysis of moving iron core movement when electromagnetic valve is opened
When the electromagnetic valve is opened, the moving iron core overcomes the pretightening force of the spring and the gravity of the moving iron core by means of electromagnetic force at the moment of energization, and drives the moving iron core to move upwards, and the method can be obtained according to a kinetic motion equation Sigma F=ma:
then the plunger acceleration a 3 is:
after the electromagnetic valve is electrified, the movable iron core starts to move upwards by overcoming spring force, spring pretightening force and movable iron core gravity through electromagnetic force until the displacement of the movable iron core is x=x 1, and the movable iron core is obtained according to a kinetic motion equation ΣF=ma:
The acceleration a 4 at this time is:
the movable iron core meets the energy conservation theorem in the opening process of the electromagnetic valve, namely:
The electromagnetic force required by the simplification can be expressed by the following formula:
known data F T1、FT2、m、x1、t2, Substituting the electromagnetic force F.
5. Construction of magnetic circuit of electromagnetic valve
The electromagnetic force of the electromagnetic valve mainly depends on the design of a magnetic circuit structure, and the calculation formula of the electromagnetic force of the electromagnetic valve under the stable working condition is as follows:
Φ＝BS
Then there are:
wherein F is electromagnetic force; phi is working air gap flux; mu is air permeability; s is the air gap sectional area; and beta is the magnetic induction intensity.
Because the magnetic circuit has magnetic leakage, the magnetic induction intensity in the working air gap is:
wherein N is the number of coil bundles; i is the current intensity; k f is the leakage inductance; delta is the air gap length.
The calculation formula of the number of turns N of the electromagnetic coil is as follows:
the current in the coil is calculated as follows:
The simplification can be obtained:
Wherein L is the winding width; d 1 is the winding outer warp; d 2 spool diameter; d is the diameter of the copper enameled wire; u is voltage; r is the resistance of the enameled wire; ρ is the resistivity of the copper wire.
The length calculation formula of the copper enameled wire is as follows:
the length of the simplified copper enameled wire is as follows:
Wherein l is the length of the copper enameled wire; Is the average diameter of the wire.
Namely, the magnetic induction intensity formula is as follows:
To sum up, it is possible to obtain:
The magnetic circuit structure of the electromagnetic valve is designed according to the parameters such as the air gap cross section area, the copper wire diameter, the leakage magnetic coefficient, the air gap length, the winding diameter, the winding shaft diameter and the like of the electromagnetic valve according to the magnetic circuit structure design logic diagram of the electromagnetic valve shown in fig. 2, the structural parameters of the structural components of the electromagnetic valve are combined through a control variable method, an experimental scheme is created, simulation modeling analysis is carried out, a finite element simulation model is built based on MATLAB and Ansoft Maxwell, finite element analysis is carried out, the electromagnetic valve structure is determined, and the electromagnetic force generated by the electromagnetic valve under corresponding voltage is F.
Parts of the embodiment not described in detail may be implemented by using the prior art, so they will not be described in detail.
Claims (2)
1. A design method of a pipeline fluid control direct-acting electromagnetic valve in the chemical field comprises a valve body (3), a spring (5), an electromagnetic coil (1), a movable iron core (2) and a fixed iron core (4); the design method is characterized by comprising the following steps of:
(1) Determining the voltage, opening and closing time and the outer diameter of the electromagnetic valve according to the use requirement;
(2) According to the motion analysis of the movable iron core, calculating the spring force required by closing the electromagnetic valve;
(3) Designing a basic structure of the spring according to the spring force, and performing software analysis and verification on the performance of the spring until the performance of the spring meets the requirement;
(4) Calculating the electromagnetic force required by the electromagnetic valve when the electromagnetic valve is opened;
(5) Determining related parameters of a magnetic circuit structure of the electromagnetic valve according to electromagnetic force and working voltage required by the electromagnetic valve in a stable working state, constructing the magnetic circuit structure and performing magnetic force verification until the magnetic circuit structure meets the requirements;
The working parameters of the electromagnetic valve in the step (3) comprise rated voltage, the number of spring supporting turns n, the mass m of the movable iron core, the spring compression amount when the working stroke x 1、x2 of the movable iron core is the spring loading pre-tightening force, the opening time t 1 and the closing time t 2;
The step (3) comprises the following steps:
(31) The maximum spring force applied during closing of the solenoid valve is calculated as follows:
FT＝-k(x1+x2)
where k is the spring stiffness coefficient, calculated as:
wherein G is the shear elastic modulus of the spring and is determined by the material of the spring; d is the diameter of the spring wire; n is the effective number of turns; d is the spring pitch diameter;
(32) The spring twist ratio C is determined according to the work load that the spring needs to achieve in the mechanism device as follows:
(33) Based on the determined shear modulus of elasticity, spring wire diameter, and spring pitch diameter of the spring material, the effective number of turns n of the spring is determined as follows:
in the step (4), the electromagnetic force required for opening the electromagnetic valve is calculated as follows:
Wherein g is gravity acceleration, F T1 is spring force when the compression amount of the spring is x 1, F T2 is spring pretightening force, For the average effective force of F T1 during the plunger movement, the following equation is calculated:
The related parameters of the magnetic circuit structure in the step (5) include an air gap sectional area S, a leakage inductance K f, an air gap length delta, a winding outer diameter D 1 and a winding shaft diameter D 2, wherein rho are the resistivity of copper wires, and the parameters enable electromagnetic force F and working voltage U required by the electromagnetic valve in a stable working state to meet the following formula:
the strength condition of the spring needs to satisfy the following formula:
Wherein τ max is the maximum torsion force generated inside the spring wire under the maximum working load; k 1 curvature coefficients; [ tau ] allowable torsional stress;
the stability condition of the spring needs to satisfy the following formula:
Wherein b c is critical aspect ratio;
the fatigue strength of the spring needs to satisfy the following formula:
Wherein [ s ] is an allowable safety factor; τ 0 is the fatigue limit of the spring material.
2. The method of designing a solenoid valve according to claim 1, wherein the spring force in step (2) is calculated as follows:
Wherein v is the moving speed of the movable iron core.
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| 连续供墨式电磁阀设计及其铁芯受力与运动分析;史兆森 等;制造业自动化;20171025;第39卷(第10期);45-47 * |
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