Research Article  Open Access
Yuanbo Chu, Zhaohui Yuan, Xuegong He, Zhichao Dong, "Model Construction and Performance Degradation Characteristics of a Deflector Jet Pressure Servo Valve under the Condition of Oil Contamination", International Journal of Aerospace Engineering, vol. 2021, Article ID 8840084, 17 pages, 2021. https://doi.org/10.1155/2021/8840084
Model Construction and Performance Degradation Characteristics of a Deflector Jet Pressure Servo Valve under the Condition of Oil Contamination
Abstract
The deflector jet pressure servo valve is a kind of highprecision hydraulic component that can be widely used in the antiskid braking system of an aircraft. In actual service, it will be faced with extreme working conditions of gradual oil contamination, which will cause performance degradation and function maladjustment of the whole valve. To this end, the paper proposes a performance degradation characteristic analysis method. In which, firstly, the structural characteristics and working principle of the deflector jet pressure valve are analyzed; then, the entire dynamics model of the pressure valve is built using the braking cavity as the load blind cavity. Secondly, the two main failure modes induced by oil contamination such as erosion wear of pilot stage and stuck of slide valve stageâ€™s valve core are determined based on the engineering experience, aimed at which the failure mechanism is analyzed; then, the sensitivity simulation model of the servo valveâ€™s output pressure with respect to key degradation parameters is established and the sensitivity analysis is performed. Finally, combining the theoretical analysis with multiphysics simulation correction methods, the performance degradation model of the typical failure modes are established, and then, the performance degradation characteristics under dynamic contamination conditions are analyzed, which is combined with the failure threshold determined by the dynamics simulation to finish the service life prediction of the deflector jet servo valve.
1. Introduction
An electrohydraulic servo valve is the core hydraulic component of electrohydraulic control, after receiving the input electric control signal, which outputs corresponding modulated flow or pressure. Among them, the pressure servo valve with pressure as output is essentially a relief valve, which has the advantages of fast response, high sensitivity, large output power, and controllable output pressure [1]. The pressure valve was first used in the antiskid braking system of an aircraft around 1950. After nearly 70 yearsâ€™ development, a twostage pressure valve can be applied to the antiskid braking system mainly including the nozzle flapper servo valve, jet pipe servo valve, direct drive servo valve, and deflector jet servo valve. The working environment of a highly reliable antiskid braking system of the aircraft determines the basis for evaluating the performance of the pressure valve involving the pilot stageâ€™s driving force, static and dynamic performances, and anticontamination performance [2].
The design and process technology of the nozzle flapper pressure valve are mature. The flapper of the pilot stageâ€™s moving part has a small inertia, fast response speed, and high control sensitivity. However, the size between nozzle and flapper is just 0.03â€‰mm0.05â€‰mm, which has the drawbacks of easy block, poor anticontamination ability, and can only work under NAS6 or NAS7 oil for a long time. In the pilot stage of the jet pipe pressure valve, the 0.2â€‰mm0.4â€‰mm clearance between the nozzle and receiver determines its relatively high anticontamination ability, which can also work normally at the oil level of GJB420B 9, but the jet pipe amplifier has shortcomings including complicated structure, more welding parts, stress concentration, poor stiffness of impulse pipe, and insufficient pressure stability. The direct drive pressure valve formed by replacing the hydraulic pilot stage with an electronic drive has the advantages of small size, light weight, strong anticontamination ability, and good performance. However, the pilot drive capacity of the electric feedback form is low, and the volume of servo valve for required driving force is too large to meet the requirements. To overcome the above deficiencies, the deflector jet pressure servo valve is proposed which integrates the main advantages of the three pressure valves [3].
The deflector jet pressure servo valve uses the principle of the jet pipe servo valve [4], and a deflector plate is added between the jet outlet and the receiver, by which the deflection of jet pipe is replaced with the deflection of deflection plate controlled by the torque motor to realize the pilot stage jet control. Because the gap among the nozzle of the jet sheet, the deflector plate, and the jet plate are large, it has the advantages of not easy to block, strong driving ability, strong anticontamination ability, and small inertia of moving parts. In order to meet the stable pressure output, the clearance between the spool valve and valve sleeve is only 2â€‰ÎĽm4â€‰ÎĽm. Oil contamination will not only cause erosion wear on the working surface of pilot stage but also induce the valve coreâ€™s stuck of the spool stage, which will bring about performance degradation of the deflector jet pressure valve and even cause a major failure of the braking system. Therefore, the model construction, performance degradation characteristic analysis, and service life prediction of the deflector jet pressure valve under oil contamination are a major issue that needs to be solved urgently.
At present, the public literature related to the deflector jet pressure valve is less. Only AVIC has given a new type of deflector jet pressure valve; the mechanism of torque motor, deflector jet amplifier, and slide valve has been studied, and the whole valve model has been established, which has certain theoretical support for the development of the deflector jet pressure valve [3]. However, there are many researches about the pilot stage which can be divided into three aspects [5, 6]: (1) the performance researches about traditional deflector jet servo valve. The researches mainly take pressure characteristics and flow characteristics as starting point, then establish corresponding mathematical models to analyze and infer the key factors affecting the performance of servo valve [7, 8]. (2) Structural improvement of deflector jet servo valves: the improvement works mainly focuses on the optimization of key structural parameters of the pilot stage [9, 10]. (3) Process technology improvement of the deflector jet servo valve: carrying out the process improvement studies to improve the process quality of the pilot stage [11]. At the same time, there are also researches involving the erosion wear and the reliability of the servo valve. For the erosion of the jet pipe servo valveâ€™s pilot stage, the trajectory of the oil and particles in the multiphase flow was analyzed by Yin et al.; then, the influence law of parameters such as the velocity and impact angle of particles to the erosion wear was carried out [12]. Based on the Fluent software, Chu et al. established a visual simulation model of nozzle to receiver in the pilot stage, then carried out simulation of erosion rate and calculation of the servo valveâ€™s theoretical life [13, 14]. Based on the GSPN theory, collected basic failure modes, and failure rate data of the jet pipe servo valve, Chu et al. propose a novel modeling and simulating method for the systemâ€™s dynamic behavior [15]. The oil flow and particleâ€™s moving trajectory of the deflector jet servo valveâ€™s pilot stage was analyzed by Ji et al.; then, the maximum speed of particles with different diameters and its influence on the erosion for the pilot stage were calculated [16]. The rest of research is mainly based on the comparison between pilot stage clearance size and particle size and then qualitatively gives other types of servo valvesâ€™ advantages and disadvantages [17], or qualitatively analysis through experiments to show the oil quality control should be strengthened [18]. Based on the above, the main deficiencies of the current performance degradation characteristics of the deflector jet pressure valve under oil contamination conditions are as follows: (1) most analyses about the performance of the pilot stage are only the qualitative analysis, (2) without considering the performance degradation of oil contamination to the special clearance structure of the slide valve stage, (3) the influence of oil pollution level is not considered, and (4) the quantitative analysis of the performance degradation and service life of the entire valve under oil contamination are not performed.
To solve these issues, this paper is focused on the performance degradation characteristics of a DJPSV induced by oil contamination. Firstly, the entire valve dynamics model is built using the braking cavity as the load blind cavity. Secondly, the two main failure modes induced by oil contamination such as erosion of pilot stage and stuck of valve core are determined based on the engineering experience, aimed at which the failure mechanism is analyzed; then, the sensitivity simulation model of the servo valveâ€™s output pressure with respect to key degradation parameters are established and the sensitivity analysis is performed. Finally, combining the theoretical analysis with multiphysics simulation correction methods, the performance degradation model of the typical failure modes is established, and then, the performance degradation characteristics under dynamic pollution conditions are analyzed, which is combined with the failure threshold determined by the dynamics simulation to finish the service life prediction of the deflector jet servo valve.
2. Structural Feature and Working Principle of the DJPSV
The deflector jet pressure valve is composed of a torque motor, armaturedeflection plate assembly, jet amplifier, and slide valve assembly. The structure of deflector jet pressure valve is shown in Figure 1, where , , , and represent the oil return port, slide valve pressure inlet, pilot stage pressure inlet, and braking port of the servo valve, respectively; and provide 21â€‰MPa oil pressure for the servo valve, and when the braking port is connected with the braking system of the aircraft, the braking cavity is a special blind cavity structure.
When the control signal is input to the coil of the servo valve, a control torque is generated to the armature assembly, which makes the armature assembly deflect clockwise, the deflector plate deviate to the left, and a control pressure difference is generated on the annular surface at both ends of the valve core, which makes the valve core move to the right, the oil return control edge is gradually closed, the oil inlet control edge is gradually opened, and the braking pressure is increased. When the control force acting on the valve core is balanced with the feedback force, the valve core is stable at a certain position (the oil inlet, the brake port and the oil return port are not mutually connected), and the servo valve outputs a braking pressure proportional to the input current to realize the pressure control with positive gain.
3. Mathematical Model of the DJPSV
3.1. Mathematical Model of the Torque Motor
The function of a torque motor in the servo valve is to convert electrical signal into mechanical motion, after receiving input current signal output the final driving torque : where is the middle position electromagnetic torque coefficient of torque motor. is the electromagnetic spring stiffness of the torque motor. is the radius from the armature shaft to the center of the guide magnet. is the length of the armature. is the coil turns. is the fixed flux. is the reluctance. is the deflector angle of the armature.
The stable process of the armature assembly is the balance process of various moments acting on it; the motion equation of the armature assembly is as follows: where is the moment inertia of the armature assembly. is the viscous damping coefficient of the armature assembly. is the spring pipe stiffness.
The deflector plate deflects under the action of the torque motor, the deflector angle is , and the deflector displacement is ; their relation is expressed as follows: where is the distance from the end of deflector plate to its rotating center.
3.2. Mathematical Model of the Jet Amplifier
The deflector jet amplifier is a nonthrottling hydraulic amplifier. The deflector deflects a relative position of the receiver, which results in a pressure difference between the two receiving holes, so as to realize the conversion and amplification of the control slide valve. The relation between the pressure difference of the two cavities and the offset distance of the deflector is deduced as
3.3. Mathematical Model of the Slide Valve
3.3.1. The Force Balance Equation of Main Valve Core
The valve core is driven by combined action of the pressure difference of control chamber and the pressure difference of the feedback chamber and the return spring. When the valve core moves in the valve sleeve, the force it receives also includes inertia force, damping force, and friction force. Therefore, the dynamic equation of the deflector jet pressure valveâ€™s valve core can be expressed as where is the displacement of the valve core. is the braking pressure. is the return prerssure. is the quality of valve core. is the viscous damping of valve core and load. is the stiffness of the return spring. is the friction between the spool and sleeve mainly induced by hydraulic stagnation and contamination stagnation, which is calculated as
where is the friction induced by contamination stagnation and is the friction induced by hydraulic stagnation.
The friction induced by hydraulic stagnation is calculated as where is the hydraulic stagnation coefficient. is the influence coefficient of three equalizing grooves on the hydraulic stagnation force. is the shoulder length of valve core. is the diameter of the valve core at shoulder. is the pressure difference between both sides of the shoulder.
3.3.2. Flow Equation of the Slide Valve
When the deflector plate deflects in the positive direction, the pressure difference between the control chambers causes the valve core to move in the positive direction, and the input highpressure oil enters the braking chamber to increase the braking pressure. Simultaneously, the braking chamber is connected with the feedback chamber on one side of the valve core, and the return oil is connected with the feedback chamber on the other side to generate the pressure difference of the feedback chamber. The flow from oil supply inlet to braking chamber is where is the flow coefficient. is the area gradient of valve core opening. is the displacement of spool core. is the overlap between spool core and spool sleeve.. is the supply oil pressure. is the braking pressure.
The linearized equation of Equation (8) is showed as where is the flow amplification coefficient. is the flow pressure amplification coefficient.
Furthermore, the relation between the load flow and the braking chamber pressure is shown as where is the hydraulic oil bulk modulus.
3.4. Mathematical Model of the Entire Valve
Based on Equations (1)â€“(10), the dynamic characteristic block diagram of the deflector jet pressure valve can be obtained as Figure 2.
Building a MATLAB/SIMULINK simulation program, the pressure response of the deflector jet servo valve when the step current is input is shown in Figure 3. It can be seen under the initial structural parameters that the system pressure quickly stabilizes at 21â€‰MPa after receiving the 60â€‰mA input signal. However, the output pressure will gradually deteriorate because of the extension of service time and the increase of the contamination oil level.
4. Oil Contamination Sensitivity of the DJPSV
4.1. Dominant Mode of Gradual Failure Induced by Oil Contamination
By performing FMEA on the deflector jet pressure valve, it can be found that oil contamination is the main and the highest probability cause of servo valveâ€™s failure. Failure modes caused by oil contamination include sudden failures and gradual failures. The socalled gradual failures mean with the extension of service life, a certain performance index of the servo valve, cannot be maintained within the specified normal range. The gradual failure mode of the deflector jet pressure valve due to oil contamination mainly includes erosion wear of pilot stage and spool movement failure of slide valve stage. (1)The erosion wear of pilot stage. Erosion wear is defined as the process of material loss when the solid surface contacts with the fluid containing particles and moves relatively, in which the particle diameter is usually less than 1â€‰mm and the particle speed is not more than 550â€‰m/s. As shown in Figure 4, a certain number of particles are ejected from the jet nozzle along with the oil. After encountering the deflector, they impact on the inner wall of the wedge and the receiving holes on both sides at a certain speed and angle and produce erosion wear, which leads to the performance degradation of the jet amplifier and affects the performance of the whole pressure valve(2)Spool movement failure of slide valve stage. Under the two conditions of valve coreâ€™s frequent action and longtime static, the movement failure of valve core induced by oil contamination comes from two different failure mechanisms. For the longtime static valve core, the clamping force mainly comes from the friction caused by the filter cake during the static time, which has certain regularity. In the deflector jet pressure valve, after the valve core is stationary for a certain time, â€śsensitive particles,â€ť will enter the clearance between the valve core valve sleeve, some of the contaminated particles will flow out of the clearance along with the leakage fluid, some of them will be trapped in the clearance, they will intercept other contaminated particles, after which the filter cake will be formed in the clearance shown in Figure 5, which will affect the response of slide valve. When the driving force is not big enough to push the valve core, the slide valve fails to move.
(a) The profile of pilot stageâ€™s core structure
(b) Comparison before and after erosion wear
4.2. Sensitivity Analysis about the Deterioration Parameters
Based on the mathematical model and assuming , , and , the state space model of DJPSV can be obtained as Equation (11). From which, the factors affecting system performance caused by oil contamination include pressure gain of pilot stage and stuck friction of the valve core, the erosion can cause the changing of , and the stuck of the valve core will raise the value of . Therefore, it is necessary to carry out the sensitivity analysis of DJPSV to and , that is, to analyze the sensitivity of key parameters induced by oil contamination. where ,
The sensitivity analysis of key parameters induced by oil contamination is carried out using the firstorder trajectory sensitivity model. Trajectory sensitivity is to study the change of state vector caused by the change of parameters according to the state equation. The state equation of the DJPSV can be expressed as
where is dimensional state vector, is dimensional input independent of , and is time.
The solution of Equation (13) is
The sensitivity function of vector to parameter and its initial condition are defined as
In this work, and are independent, taking the derivative of Equation (13) on both sides of as
Select related vector of the DJPSV as where the state vector parameter of the DJPSV is , , and ; the input vector parameter is ; the parameter vector parameter is , , , , , , , , , , , , , , , , and .
Then, the state space model of the DJPSV can be expanded into
The partial derivative of state equation function to the state vector is conducted; then, the coefficient term of sensitivity function can be obtained as
The partial derivative of state equation function to the state vector is conducted; then, the free term of sensitivity function can be obtained as
The initial value of state vector is ; then, the initial value of sensitivity function is
Based on the simulation model, the differential equation is solved in the command interface of MATLAB using the fourthorder/fifthorder RungeKutta algorithm; then, the sensitivity function of step response to parameter are shown in Figure 6.
(a) Sensitivity function
(b) Sensitivity function
According to the curves of sensitivity function shown in Figure 6, the sensitivity of the system decreases rapidly in the dynamic response process and gradually stabilizes to a nonzero value in the steady state process, that is, the change of and will affect system performance in the whole response process and the friction induced by hydraulic stagnation is simplified as constant. Therefore, it is necessary to analyze the failure modesâ€™ law induced by oil contamination and will finally bring out performance degradation of the deflector jet pressure servo valve.
5. Performance Degradation Characteristics and Service Life Prediction of the DJPSV
5.1. The Erosion Wear of Pilot Stage
5.1.1. Mathematical Model of the Degradation Process
(1) Basic Fluid Flow. Neglecting the heat conduction and compressibility of the flow, the numerical simulation of oil flow in the pilot stage of the deflector jet pressure valve can be performed through the mass conservation equation, the momentum conservation equation, and the standard transport equation. The mass conservation equation and momentum conservation equation are shown as where is the fluid density. is the fluid velocity. is the pressure on fluid microelement. is the stress tensor. and are the gravitational body force and force body force, respectively.
(2) Discrete Phase Model. The volume fraction of solid particles in the hydraulic oil of the servo valve is far less than 10%; thus, the discrete phase model (DPM) in FLUENT can be used to simulate the movement of solid particles.
Particle force equation: analyzing the force of particles, the particle motion equation is established shown in Equation (25), then solve the differential equation in the Lagrangian coordinate system to obtain the motion orbit of particles. where and are the velocity of the particle and liquid. and are the density of particle and liquid. is the drag force on particles. is the gravity of particles. is the additional force
Wall collision model: the particles move with hydraulic oil and will be back to the flow field when bounced against the wall. The rebound coefficient proposed by Grant and Tabakoff is used to describe the change of normal and tangential directionsâ€™ momentum of particles before and after collision with the wall [19]
Particle distribution model: different diameter particles are distributed in the contaminated oil, which can be expressed by RosinRammler [20] shown as where and are the diameter and the mean diameter of particles, respectively; the value of is obtained by noting that value of at which ; is the mass fraction with diameter greater than ; and is the spread parameter, and the value for n is given as [20]
Erosion wear model: the model proposed by Edwards et al. [21] through carrying out erosion experiments of sand to the surface of carbon steel, which is used for the erosion rateâ€™s calculation of servo valve shown in Equation (29). where is the erosion rate. is the particle number. is the mass flow rate of the particle. is the diameter of particle. is the function of particle diameter. is the impact angle between particle trajectory and wall. is the function of impact angle; the value of f(Î±) is shown as Table 1. is the function of particleâ€™s relative velocity. is the area of the particle impact wall

(3) Performance Degradation Mechanism Model. Contaminated oil is ejected from the deflector at a high speed and impact angle, and erosion wear will occur on the two receivers and the platform between them, which cause material removal at the top of the boss as shown in Figure 7. During the erosion wear process, the size change of pilot stage includes the increase of longitudinal wear dimension and the increase of distance between the receiver holes, where the relationship between and is shown in Equation (30). Ignoring the effect of â€™s change on the pressure gain of pilot stage, it is necessary to theoretically analyze the effect of â€™s change on the pressure gain.
The flow diagram of oil in the pilot stage is shown in Figure 8; the oil enters the Vgroove of deflector plate with pressure from the top and then ejects from the deflector plate nozzle with after accelerating and reducing pressure. The pressure at the left and right receivers is, respectively, and , and some oil flows out of the pilot stage with flow and through the gap. The top view of the dotted line part is shown in Figure 9.
When the deflector plate is in zero position, the load flow is zero, and the inlet pressure of the two receivers is equal: where , which is used to indicate the positional relationship between the deflector nozzle and the inlet of receivers.
The pressure gain of pilot stage is shown in Equation (32) [23]. The parameter change caused by erosion will not change , so the analysis of pilot stage pressure gain â€™s change trend is shown in Figure 10, which is combined with Equation (30) to prove erosion wear will cause a decrease in the value of and will cause system performance to deteriorate.
5.1.2. The Erosion Wear Simulation and Analysis of Pilot Stage
The flow field from the deflector to receiver is relatively complicated, and the erosion rate is the largest; thus, the grid is encrypted in these places and numerical simulation of erosion rate is performed using FLUENT. Set 21â€‰MPa pressure as the inlet boundary condition, 0.5â€‰MPa pressure as the outlet boundary condition, 1070â€‰kg/m^{3} as the oil density, and 0.0123â€‰Pas as the oil dynamic viscosity. On the basis of continuous phaseâ€™s convergence, the discrete phase model is set up to simulate the movement of particles and calculate the erosion rate. The concentration and distribution of particles in the oil is determined according to the GJB420B standard shown in Table 2 [24]. The particle distribution obey the RosinRammler distribution, the average diameter of particles is set as 44â€‰ÎĽm, the spread parameter is set as 1.52, and the Discrete Random Walk model is used to deal with the interaction between the particles and the discrete vortex of the fluid; based on all the above setting, the actual different operating conditions are numerically simulated.

(1) Simulation When Deflector is in Zero Position. When the deflector is in zero position, the flow velocity distribution of the pilot stage is shown in Figure 11. The oil enters the jet disc from the inlet, decreases pressure and increases speed at the constriction neck, and finally collides with the receiver and its middle part and flows to the outlet. The trajectory of the contaminated particles moving along is shown in Figure 12. The place where the most intense collision of particles is the boss in the middle of the receivers can be found, and according to the model of erosion rate on the impact angle and velocity parameters, it can be inferred that the maximum erosion rate is shown in Figure 13; its maximum value is (kg/m^{2}s).
(2) The Relation between the Erosion Rate and Offset of Deflector. According to the actual situation, several groups of oil velocity and erosion rate are calculated after changing the offset of deflector, of which the relation curves shown in Figure 14 are fitted using MATLAB. It is easy to find that the maximum oil velocity of pilot stage is basically the same and fluctuates up and down at 188â€‰m/s, the reason of which is the pressure difference between inlet and outlet and the structures are the same. However, the change of erosion rate shows a certain rule. In the range of 00.07â€‰mm, the erosion rate basically fluctuates up and down at (kgÂ·m^{2}Â·s^{1}) and reaches the maximum value at 0.07â€‰mm, and then decreases rapidly with the increase of offset. The reason is the width of middle boss is 0.14â€‰mm; thus, 0.07â€‰mm is the contact point between the boss and receiving hole, and the difference of flow track of 00.07â€‰mm is small, while the special structure, that 0.07â€‰mm is the contact point, results in the maximum erosion rate, and after which the erosion rate decreases rapidly with the increase of displacement due to the space between the receive get bigger.
(3) The Relation between the Erosion Rate and Diameter of Particles. The diameter of particles is set as 1â€‰ÎĽm, 3â€‰ÎĽm, 5â€‰ÎĽm, 7â€‰ÎĽm, 8â€‰ÎĽm, 10â€‰ÎĽm, 15â€‰ÎĽm, 20â€‰ÎĽm, 25â€‰ÎĽm, 50â€‰ÎĽm, 60â€‰ÎĽm, 70â€‰ÎĽm, 80â€‰ÎĽm, 90â€‰ÎĽm, and 100â€‰ÎĽm, respectively, and other parameters are completely consistent. The simulation and fitting results shown in Figure 15 are the relation curves among oil velocity, erosion rate, and particle diameter. It is not difficult to know that the oil velocity follows the same rule, that is, it fluctuates slightly up and down at 188â€‰m/s. However, the erosion rate increases with the increase of particle diameter on the whole; the reason is under the same condition of other parameters, the increase of particle diameter will lead to the increase of erosion rate because of the larger impact energy of particles. However, there are many fluctuations in the whole particle range, and the particle diameter corresponding to the minimum erosion rate is 7â€‰ÎĽm, while the difference is small in the range of 150â€‰ÎĽm.
(4) The Relation between the Erosion Rate and Concentration of Particle. Figure 16 shows the relation curves among the oil velocity, erosion rate, and concentration of particles, in which the particle diameter is fixed at 50â€‰ÎĽm; the concentration of particles is set, respectively, as â€‰kg/s, â€‰kg/s, â€‰kg/s, â€‰kg/s, â€‰kg/s, â€‰kg/s, â€‰kg/s, â€‰kg/s, â€‰kg/s, andâ€‰kg/s, and other parameters are completely consistent. The oil velocity follows the same rule, that is, it fluctuates slightly up and down at 188â€‰m/s. However, the relationship between the increase of erosion rate and the increase of particle concentration is almost linear, because in the effective range of particle concentration, the removal amount of the receiver as the target is directly proportional to the amount of contamination particles.
(5) The Relation between the Erosion Rate and Oil Pollution Level. According to GJB420B, different oil pollution levels contain the same particle diameter distribution, but the particle concentration is different. The oil pollution levels are set as 1, 2, 3, 4, 5, 6, 7, 8, 9, and 10, respectively, and other parameters are completely consistent. The simulation and fitting results shown in Figure 17 is the relation curves among oil velocity, erosion rate, and oil level. The oil velocity follows the same rule, that is, it fluctuates slightly up and down 188â€‰m/s. However, the erosion rate increases exponentially with the increase of oil pollution level. The reason for this result is that although the particle diameter distribution of different oil pollution level is completely consistent, but the particle concentration between adjacent oil pollution levels meets the relationship of twice.
5.2. Spool Movement Failure of Slide Valve Stage
The movement of contamination particles in the clearance is mainly the translation with the oil and the rotation around its center of gravity. Because most of them are ellipsoidal, when the size of particles along the radial direction of slide valve is smaller than the clearance, they can enter the clearance with oil. In the rotation movement, the size of ellipsoidal particles along the radial direction of the clearance will change due to the different rotation angles. When the radial size of particles increases to the same size as the radial size of clearance, the particles are trapped in the clearance of the slide valve.
5.2.1. Mathematical Model of the Degradation Process
(1) Interaction Model between Contamination Particles and Motion Pair Surfaces. As shown in Figure 18, when the contamination particles contact with the valve core and valve sleeve, the normal deformation and are generated in the upper and lower hemispheres under the action of clamping force and due to different surface hardness of the valve core and valve sleeve, which make the shape of particles from a dotted line profile to a solid line profile. When the bearing stress reaches the stress limit, the contamination particles are crushed [25].
The hardness of valve core and valve sleeve is and , respectively; the stress limit of particles is ; and the equivalent diameter of particles is . It can be seen from the analysis of elasticity that
There are
The research shows that the eccentricity of valve core and valve sleeve is generally between 15% and 20%. For the contamination particles with diameter ( refers to the maximum diameter of particles, and the ratio of maximum diameter to minimum diameter is defined as ), the interaction types on the surface of slide valve pair with eccentricity varies with its position in the clearance, which is shown in Figure 19.
For particles with diameter in the sensitive dimension (, )), the radial clearance is divided into three areas according to the different interaction between the particle and surface of slide valve pair. (1)No action area. In the area with circumferential angle of , the minimum diameter of particles is larger than the clearance, and the contamination particles cannot enter the clearance; in the area with a circumferential angle of , the maximum diameter of particles is smaller than the clearance and there are no interaction between the contamination particles and slide valve pairs in the above areas. The and are calculated as follows [25]:(2)Crushing area. In the area with a circumferential angle of , the particles with diameter enter the clearance. When the slide valve starts, the equivalent diameter of particles is equal to its maximum diameter , and the deformation reaches the maximum value. The calculation of is as follows:(3)Deformation zone. In the area with a circumferential angle of , the particles with diameter can enter and be trapped in the clearance due to rotation. When the valve core is started, the particles will be squeezed and deformed, and there will be a certain clamping force among the valve core, valve sleeve, and contamination particles
(2) Clamping Force Model of Single Particle. (1)Calculation of clamping force in crushing area. In the area of circumferential angle , the particles with diameter reaches the stress limit and the deformation reaches the maximum value when the valve core is started. At this time, the equivalent diameter of the particle has not reached its diameter , the equivalent diameter is related to the position of the particle, namely,
When the circumferential angle is ,
In the strength limit region, the deformation of particles reaches the maximum value and , so the clamping force of particles is (2)Calculation of clamping force in deformation area. In the area of circumferential angle , when the valve core is started, the particles are squeezed by the valve core and valve sleeve, and the equivalent diameter of the contamination particles is the maximum diameter , namely,
(3) Interception Probability model. (1)Theoretical interception probability. The interception probability of ellipsoid particles with diameter and ratio of long axis to short axis can be intercepted at the circular angle is(2)Actual interception probability. The actual interception probability P (Î¸) iswhere the determination of is related to the probability of the system oil entering into the clearance and the probability of particles sticking in the clearance:
(4) Performance Degradation Mechanism Model. (1)Clamping force of single particles in the clearance of slide valve
Because the clamping force of the particles with diameter in the crushing area and deformation area changes with the change of circumference angle , and the actual interception probability is also related to the circular angle , there is where and are, respectively, the clamping forces of particles in the crushing area and the deformation area (2)The clamping force of contamination particles in the clearance of slide valve
The research results show the size distribution of contamination particles in the hydraulic system is close to the modified lognormal distribution, which can be expressed as follows: where B is the distribution parameter
Since the slide valve pairâ€™s initial clearance of deflector jet pressure servo valve is 2â€‰ÎĽm4â€‰ÎĽm, the particle data below 5â€‰ÎĽm is not involved in NAS1638, so the determination of contamination particleâ€™s mass fraction distribution basing on GJB420B is shown in Figure 20.
When the static time of valve core is , the leakage of the slide valve is where is the time constant of filter cake from stable stage to saturation stage. When the structure of valve core and valve sleeve is determined, the value of time constant is mainly related to oil pollution level and particle distribution, and its calculation is shown in where is the ratio of hollow diameter of filter cake to clearance. is the total number of contamination particles in oil pollution level of . is the specific resistance of filter cake. is the increment of particle diameter when counting the particle number.
The clamping force produced by contamination particles in the clearance is as follows:
The axial clamping friction force to be overcome in the movement of valve core is where is the clamping coefficient.
5.2.2. Calculation and Analysis of Clamping Force of Valve Core
(1) The Relation between the Friction Force and Particle Diameter. In order to obtain the relation between clamping force of particle diameter, the contamination oil is designed to meet the pollution level of GJB420B 7, and the diameter of contamination particles is selected as 1â€‰ÎĽm, 2â€‰ÎĽm, 3â€‰ÎĽm, 4â€‰ÎĽm, 5â€‰ÎĽm, 6â€‰ÎĽm, 7â€‰ÎĽm, 8â€‰ÎĽm, 9â€‰ÎĽm, and 10â€‰ÎĽm, respectively. The clamping friction force is 7.66â€‰N under 3â€‰ÎĽm contamination particles. Similarly, the friction force under 5â€‰ÎĽm particles is 2.05â€‰N, while 1â€‰ÎĽm, 2â€‰ÎĽm, 6â€‰ÎĽm, 7â€‰ÎĽm, 8â€‰ÎĽm, 9â€‰ÎĽm, and 10â€‰ÎĽm are not within the range of effective particle diameter, so the friction force calculated are 0â€‰N. Thus, the relation between clamping force of the valve core and the particles diameter is shown in Figure 21.
(2) The Relation between the Friction Force and Particle Concentration. Set the particle diameter as 3â€‰ÎĽm and take the particle concentration (particle number) as 2307/100â€‰mL, 9225/100â€‰mL, 36905/100â€‰mL, 147596/100â€‰mL, 590824/100â€‰mL, and 2362494/100â€‰mL, respectively. After calculation, the curve between the clamping force of valve core and the particle concentration is obtained as Figure 22. It is not difficult to find the clamping force under 3â€‰ÎĽm particles increases with the increase of the particle concentration, and the relationship between them is almost linear.
(3) The Relation between the Friction Force and Oil Pollution Level. In order to research the effect of oil pollution on the clamping force as real as possible, the particle diameter range was extended from 3â€‰ÎĽm to the full scale range, and the oil pollution level is selected as level 1, level 3, level 5, level 7, level 9, and level 11 based on the GJB420B. According to the analysis and calculation results, the curve between the clamping friction force of valve core and the oil pollution level is shown in Figure 23. It can be found that the increase of oil pollution level will cause the clamping friction force of the valve core to increase exponentially.
5.3. The Service Life Prediction of Deflector Jet Pressure Servo Valve
Under the condition of oil pollution, the service life of the deflector jet pressure servo valve is closely related to the erosion of the pilot stage and the clamping of the valve core. The erosion rate of pilot stage and the clamping force of valve core increase with the increase of oil pollution level. Through the analysis and calculation, the erosion rate and the clamping force of the valve core can be obtained under different pollution levels, and then, the service life of the pressure valve can be obtained by combining the failure critical value of the key deterioration parameter.
5.3.1. The Determination of Failure Critical Value
According to the regulation time, overshoot and steady state error of pressure valveâ€™s dynamic response, the failure critical value of its life, is determined. There are many kinds of actual systems and there is no unified system index requirement. In this paper, is set as the multiple of required initial regulation time , that is, with the decline of system performance, when the regulation time exceeds , the system is considered failure. is the required overshoot index, is the ratio of the required steady state error to the desired output of the system, and the failure critical value of the system is determined according to Equation (49). Select , , and to determine the critical value of the parameters when the valve system fails. where is the critical value of valve failure parameter. is the critical value determined by regulating time of valve failure parameter. is the critical value determined by overshoot of valve failure parameter. is the critical value determined by steady state error of valve failure parameter.
5.3.2. The Service Life Prediction Model
Shown in Figure 24 is the mission profile of an aircraftâ€™s braking system. In one flight cycle, the servo valve receives the electric control signal from the flight control system except the flight phase, in which the servo valve do not work. Therefore, in one flight cycle, the time of pilot stageâ€™s erosion wear is 20â€‰min; then, the service life of pilot stageâ€™s erosion is carried out according to Equations (50)â€“(59).
where is the erosion service life in flight takeoff landing. is the erosion distance generated under the oil level of . is the erosion rate under the oil level of . is the erosion time of single flight takeoff landing. is the density of receivers; is the maintenance times of oil level from to . It can be determined according to the actual maintenance; is the number of flight takeoff landing experienced in single maintenance.
In one flight cycle, the corresponding maximum friction force will be generated in each static phase of valve core such as the takeoff phase, and the friction force will be accumulated from small to large after the switch action of valve core. Therefore, the service life under the influence of friction force can be calculated according to the longest time phase, which is shown in Equations (53) and (54). where is the service life of clamping failure in flight takeoff landing. and are the life factor and friction force corresponding to the oil level of . is the critical friction force of clamping failure.
5.3.3. The Service Life Prediction of Deflector Jet Pressure Servo Valve under the Action of Two Failure Modes
In practice, the service life prediction is relatively complex when the erosion of pilot stage and the stuck of slide valve stage are induced by oil pollution together. It is necessary to comprehensively consider the two failure modes and the changes of key deterioration parameters under different oil pollution levels. Firstly, the clamping friction force under different oil levels are calculated, which is input into the system simulation software and the critical value of pressure gain and erosion distance under different oil levels based on the critical value judgment rule are calculated, then basing on Equation (50)â€“(54), the life under different oil pollution levels are determined and finally the service life of whole valve is determined as shown in Table 3.

6. Conclusion
Aiming at the deflector jet pressure servo valve, a method for performance degradation analysis and service life prediction under the influence of oil pollution is presented. (1)The sensitivity equation of the output pressure about the key deterioration parameters of the pilot stageâ€™s erosion and the slide valve stageâ€™s clamping is established and the sensitivity analysis is carried out. It is found that the pilot stageâ€™s pressure gain and the slide valve stageâ€™s friction force will have a significant impact on the output pressure during the whole response process(2)Based on the theory of fluid mechanics and erosion, considering the influence of oil pollution level, the numerical simulation of pilot stageâ€™s erosion is carried out. The erosion rate increases exponentially with the increase of oil pollution level; when the offset of deflector plate is 0.07â€‰mm, the erosion rate is the largest(3)Based on the theory of elasticity and filter cake, considering the influence of oil pollution, the friction forceâ€™s theoretical calculation of slide valve pairâ€™s special matching clearance is carried out. The friction force increases exponentially with the increase of oil pollution level, and the friction force caused by the contamination particles with the average clearance diameter of 3â€‰ÎĽm is the largest
Data Availability
The data used to support the findings of this study have not been made available because further research.
Conflicts of Interest
The authors declared no potential conflicts of interest with respect to the research, authorship, and/or publication of this article.
Acknowledgments
The authors disclosed receipt of the following financial support for the research, authorship, and/or publication of this article. This work was supported by the National Natural Science Foundation of China (NSFC 51805403), the project supported by Natural Science Basic Research Plan in Shaanxi Province of China (NSBRP 2019JQ836), the Natural Science Foundation of Shaanxi Provincial Department of Education (NSSXE 19JK0416), and the project supported by Xiâ€™an postdoctoral Foundation (2020621).
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