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Article

Strength Enhancement and Redundant Design of the Electromagnetic Repulsion Valve for High-Speed Switch Hydraulic Mechanisms

by
Youpeng Zhang
1,2,
Jianying Zhong
1,3,
Zhijun Wang
1,2 and
Yingqian Du
2,*
1
School of Electrical Engineering, Shenyang University of Technology, Shenyang 110870, China
2
Pinggao Group Co., Ltd., Zhengzhou 450046, China
3
China Electric Equipment Group Science and Technology Research Institute Co., Ltd., Shanghai 200040, China
*
Author to whom correspondence should be addressed.
Energies 2025, 18(8), 2022; https://doi.org/10.3390/en18082022
Submission received: 2 March 2025 / Revised: 1 April 2025 / Accepted: 5 April 2025 / Published: 15 April 2025
(This article belongs to the Section F: Electrical Engineering)
Browse Figures
Versions Notes

Abstract

:
As a control structure, the magnetic repulsion device is applied in the high-speed switch hydraulic operating mechanism. It must not only move quickly but also stop precisely. The repulsion disk is subjected to high impact loads, resulting in the phenomenon of fracture and damage. In this paper, the magnetic repulsion value of the engineering prototype was obtained through simulation. A super-elastic material was selected as the buffer, and impact dynamics simulation was carried out. A double-repulsion-disk structure was designed, which reduced the structural impact stress and satisfied the operation time of less than 2 milliseconds. This realized redundant design and improved the reliability of the high-speed switch hydraulic operating mechanism, which is of great significance for the safe operation of high-speed switches.

1. Introduction

Operating mechanisms for circuit breakers based on magnetic repulsion induced by an eddy current feature structural simplicity, few movable components, low mechanical delay time, and minimal performance scattering, allowing for rapid separation of electrical contacts in a short time [1]. This principle was first proposed in the 1960s [2,3] and first applied by Fuji Electric in Japan in the design of fast vacuum switches in the 1990s [4,5].
A typical design of the magnetic repulsion operating mechanism for vacuum switches is shown in Figure 1. During the opening operation of the switch, the opening capacitor (capacity to hold energy for opening the switch) discharges and generates a magnetic repulsion force between the coil and the repulsion disk. The repulsion disk causes the electrical contact to separate. During the closing operation, the closing capacitor discharges, and the repulsion disk moves in the reverse direction [6,7].
Since 2000, the magnetic repulsion operating mechanism has been increasingly widely used in vacuum circuit breakers [8,9,10,11], and it has also been applied in other fields such as marine equipment [12,13]. The operating power required for vacuum circuit breakers is relatively small, generally not exceeding 3 kJ, and the opening time is relatively long, usually within 30 ms. Therefore, the magnetic mechanism has not been applied in gas-insulated switches with large operating power.
In recent years, the power grid has put forward the demand for high-speed circuit breakers [14,15], and the magnetic repulsion force has been applied in the operating mechanism of gas-insulated switches. The so-called high-speed circuit breaker refers to a gas-insulated switch with a significantly reduced opening time and a hydraulic operating mechanism [16,17], which requires an opening time of less than 8 milliseconds. In the hydraulic operating mechanism, the response time and performance characteristics of the traditional control valve cannot meet the functional requirements of rapid opening [18,19,20]. The internal part of the circuit-breaker’s hydraulic drive mechanism is a system with stable pressure. External disturbances will introduce some nonlinear factors, affecting the stability of the hydraulic system [21]. Improvement of the hydraulic drive mechanism should not affect the main hydraulic system. Therefore, the magnetic repulsion device has been applied in the hydraulic drive mechanism of high-speed circuit breakers [22], and a valve body with control function based on the principle of magnetic repulsion (hereinafter referred to as the repulsion valve) has been designed. The repulsion valve is used in conjunction with the conventional control valve and is mechanically interlocked with the pressure-relief valve. After the repulsion valve is started, the pressure-relief valve opens at the same time, and the main system begins to relieve pressure; the repulsion valve continues to move, pushing the control valve to move quickly. The repulsion valve not only improves the response speed of the hydraulic drive mechanism but also does not affect the stability of the main hydraulic system.
During the action, the repulsion disc is subjected to the magnetic repulsion force and the hydraulic preload. If the design is not correct, damage such as fracture may occur, as shown in Figure 2.
The buffer structure absorbs the energy of moving parts during the process, and has a significant impact on the desired mechanical strength of the repulsion disk. Currently, the main buffering techniques in magnetic repulsion mechanisms include bistable spring buffering, hydraulic buffering, material buffering, pneumatic cylinder buffering, and magnetic buffering [23,24,25]. The response of the bistable spring structure is relatively slow, and its buffering effect does not meet the needs of the system [26,27]. Additionally, inconsistent movement of the springs on both sides can lead to eccentricity of the drive shaft, which may cause material stress to exceed the load limit. This can result in issues such as fracture of the repulsion disk and damage to transmission components [28,29]. Limited by factors such as available space and cost, magnetic repulsion valves for high-speed switching hydraulic mechanisms usually do not utilize hydraulic buffering, pneumatic cylinder buffering, or magnetic buffering [30,31]. Instead, material buffering technology is favored [32,33,34]. The structural principle of this is shown in Figure 3.

2. Research Methodology

To address the mechanical strength issues of the magnetic repulsion valve structure, the magnetic repulsion force was calculated and optimized in the present work to have the repulsive force match the parameter of the repulsion-disc discharge circuit. The mechanical properties of the buffer material were studied, and a governing equation was derived for the hyper-elastic buffer material. The optimized repulsion force and the properties of the hyper-elastic material were then applied to a well-accepted impact dynamics simulation model to verify the mechanical design and travel characteristics of the magnetic repulsion valve. The process is shown in Figure 4. A redundant structure with dual repulsion disks was designed and has been successfully implemented in engineering applications.

3. Model and Calculation of Magnetic Repulsion Force

The equivalent circuit diagram of the magnetic repulsion disk is shown in Figure 5. In this diagram, C is the energy storage capacitor; Uc is the capacitor voltage; D is a freewheeling diode; R1 is the equivalent resistance of the coil; L1 is the self-inductance of the coil; L2 represents the equivalent inductance of the metal disk; R2 represents the equivalent resistance of the metal disk; and M represents the mutual inductance between the coil and the metal disk, whose value varies with the distance between the metal disk and the coil [35,36].
During the operation, when switch S is closed, the pre-charged capacitor C discharges through the coil, generating a pulse current i1. This pulse current produces a changing magnetic field around the coil. Due to the phenomenon of electromagnetic induction, an eddy current i2 is induced in the metal disk. This flows in the opposite direction to the coil current. The eddy current generates a magnetic field in the opposite direction to the original magnetic field, resulting in a magnetic repulsion force between the coil and the metal disk, thereby causing the mechanism to move.
In this study, a model to simulate the operation of a prototype magnetically operated valve was established, together with all necessary boundary conditions. The repulsion disk was made of aluminum alloy. The parameters of the coil were set according to the design of the prototype. The computational domain was filled with air in space not occupied by solid parts. The repulsion disk was initially stationary. The mass of each component, the capacitance and internal electrical resistance of the capacitor, and voltage were also assigned appropriate values. The structure of the computational domain built for the finite element model is shown in Figure 6. The magnetic induction intensity and magnetic force were derived from the simulation results.
The pre-charging voltage of the energy storage capacitor directly controlled the total amount of energy available. Its influence on the magnitude of the magnetic repulsion force is shown in Figure 7, and was consistent with the expected trend. With a fixed value of 2.5 mF for the capacitance, the peak magnetic force was proportional to the pre-charging voltage while the time to reach the peak value of the magnetic force was not affected, at 0.38 ms from the start. A charging voltage of 1100 V produced a peak repulsion force of 0.057 × 106 N, and 1300 V led to 0.074 × 106 N, an increase of 30% in force for an increase in pre-charging voltage of 18%.
A variation in the capacitance was expected to change the system response, as evidenced in Figure 8. With a fixed pre-charging voltage of 1200 V, the peak time for the repulsion force was 0.27 ms with 1 mF, 0.38 ms with 2.5 mF, and 0.43 ms with 5 mF. The minimum capacitance (1 mF) used in the study produced a peak repulsion force of 0.038 × 106 N while the maximum capacitance (5 mF) produced a peak repulsion force of 0.084 × 106 N, an increase of 121%.
It can be seen that an increase in the pre-charging voltage and capacitance produced a larger discharge current, thereby increasing the peak value of the magnetic repulsion force and the movement speed of the mechanism. Within the optional design parameter range, the capacitance value had a greater impact on the magnetic repulsion force, while the pre-charging voltage had a relatively smaller impact. A cost-effective way to achieve improved performance of the valve was, therefore, to have a capacitance value of 2.5 mF and a pre-charging voltage in the range of 1100–1300 V.

4. Research on Buffer Materials

The buffer material used in this work was polyurethane, which is a hyper-elastic material with satisfactory strength and toughness. Transmission of compressive stress in this material is relatively uniform and stable under conditions of high stress and considerable strain. In addition, it has excellent shock-absorption ability. Therefore, it is widely used in numerous engineering fields, such as transportation, construction, and aviation [37].

4.1. Load Test

There are two main types of polyurethane materials, namely polyether and polyamine. To obtain meaningful results, five batch samples of each material were chosen for testing. These were randomly selected from the supplier’s monthly production samples and represented the quality of the material. Samples with a diameter of 29 mm were selected to carry out the load test, and the required load-force value with the pre-fixed compression length was measured, as shown in Figure 9.
Load tests were performed on five material batches with 10 specimens per batch. The prototypes were compressed 24 mm using a press machine to determine the load values sustained by each batch at 24 mm compression displacement.
For a pre-fixed compression of 24 mm, test results showed that the force values that caused compression were different. The load value for polyether was in the range of 18–31 kN, while that for polyamine was in the range of 2.5–2.7 kN, as shown in Table 1 below.
As can be seen from Table 1, under the same compression, the force corresponding to polyether was much greater than that for polyamine. For buffer structures, stability is crucial and serves as the prerequisite for ensuring design reliability.
There was noticeable scattering in the measured force on the polyether material despite a new disc being used for each operation. The maximum peak value of the magnetic repulsion force did not exceed 90 kN in the present work and the designed compression was not greater than 24 mm. The volume of the buffer structure was about 11 times that of the test sample. It is clear that the polyamine material could withstand the maximum impact force within the compression and had more stable performance. Therefore, the polyamine polyurethane (hereinafter referred to as polyurethane) was selected as the buffer structure material.

4.2. Material Constitutive Equation

In order to better understand the mechanical properties of polyurethane, the classical hyper-elastic material constitutive equations are used to describe the operation. There are two main models. The first is the thermodynamic statistical model, and the other is the continuum mechanics model based on the phenomenological theory [38]. The phenomenological model assumes that the hyper-elastic material is isotropic when no deformation occurs. The basic characteristics of the material are described by the strain energy function U per unit volume. The strain energy function can be expressed as a function of three strain invariants of the deformation tensor Ii or the principal stretch ratio λi, as follows:
U = f ( I 1 , I 2 , I 3 )
U = f ( λ 1 , λ 2 , λ 3 )
The N-order polynomial model is a commonly used phenomenological model. The Mooney–Rivlin model [39] is the simplest of the polynomial models. When the order N equals 1, it can be expressed as follows:
U = C 10 ( I 1 ¯ − 3 ) + C 01 ( I 2 ¯ − 3 ) + 1 D i ( J − 1 ) 2
The experimental data of the polyurethane material were used to obtain the constitutive model parameters of the hyper-elastic model by curve-fitting. The result was C10 = 1.081 and C01 = 0.213.
The above-mentioned hyper-elastic constitutive model parameters were then applied in the dynamic model of the magnetic repulsion valve to simulate the polyurethane buffering process.

5. Impact Dynamics Simulation

Impact dynamics is an analytical method for addressing dynamic challenges and tackling simulations like automobile collisions [40] and explosive propagation [41]. Impact dynamics simulation can be used to obtain the characteristic quantities such as structural displacement, strain stress, concussion contact force, and deformation elastic potential energy.
In this work, the LS-DYNA R8 software was used to implement the impact dynamics simulation model for the repulsion valve, and a comparative study was conducted on the single repulsion disk and the double repulsion disk redundant structure. The double repulsion disk redundant structure used two repulsion disks as the driving elements, with the two repulsion disks serving as backups for each other.
The simplified model included a coil, repulsion disk, polyurethane buffer, transmission shaft, and other components, as shown in Figure 10. The boundary conditions for the repulsion value were derived from the calculation results under a 2.5 mF capacitor and a 1300 V pre-charge voltage, as presented in Section 2. The curve of repulsion force values was applied to the surface of the repulsion disk near the adjacent coil; for the single-disk structure, the applied force value was the calculated force value, and for the double-disk structure, the calculated force value was evenly distributed between the two repulsion disks, i.e., 50% of the calculated force value was applied to each repulsion disk, on nodes of the simulation model. The Mooney–Rivlin constitutive equation parameters were assigned to the polyurethane buffer material.
The impact-dynamics calculation results showed that the Mooney–Rivlin equation exhibited satisfactory convergence and simulated the hyper-elastic buffering process of the polyurethane material. The maximum stress of the repulsion disks of the two structures is shown in Figure 11.
The variable potential energy and peak collision contact force of the structure were also extracted from the calculation results and compared with the maximum stress in Table 2 below.
The dynamic calculation results of the two structures showed that the redundant-structure repulsion disk had better mechanical properties, mainly in the following aspects:
  • Firstly, the peak value of the collision contact force of the redundant-structure repulsion disk was smaller. The peak value of the contact force of the single-disk structure was 0.7 × 106 N, and that of the double-disk structure was 0.8 × 106 N. Both of these values were much larger than the applied peak repulsion of 0.074 × 106 N, which also verifies that the impact is a short-time release process of kinetic energy and cannot be simply compared by the force-value boundary condition. The kinetic energy of the redundant structure was distributed on two repulsion disks, resulting in a peak contact force smaller than that of the single-disk structure.
  • Secondly, the time at which the maximum stress value of the redundant-structure repulsion disk appeared was later. The time taken for peak stress in the single-disk structure was 2.2 ms, while that of the redundant-structure repulsion disk was 4.8 ms, indicating that the buffer structure of the redundant structure delayed the impact process.
  • Thirdly, the maximum stress value of the redundant-structure repulsion disk was 419 MPa, which was lower than the material yield strength (469 MPa). The maximum stress of the single-disk-structure repulsion disk was 517 MPa, indicating that the equal distribution of the repulsion value and the doubling of the buffer structure significantly reduced the stress level of the repulsion disk.
  • Fourthly, the variable potential energy of the redundant-structure repulsion disk was significantly smaller than that of the single-disk structure. The peak value of the variable potential energy of the redundant-structure repulsion disk was 12 J, while that of the single-disk-structure repulsion disk was 40 J, indicating that the more polyurethane material was applied, the more kinetic energy was absorbed, and the elastic deformation of the repulsion disk was thus reduced.

6. Prototype Design

Based on the above results and analysis, a dual-repulsive-force disk was adopted in the design of a magnetic repulsive-force-valve structure with redundancy, as shown in Figure 12. In this structure, the transmission is fixed with two repulsive-force disks. The two repulsive-force disks have their own independent switching drive coils and corresponding driving circuits. Their mechanical and electrical parameters are the same. The circuits for driving the two repulsion discs are independent, and do not affect each other. Each repulsive-force disk corresponds to a hyper-elastic buffer structure. After moving a distance “d”, the transmission axis completes the operation of the magnetic repulsive-force valve. The repulsive-force disk then react with the hyper-elastic buffer and decelerates. The repulsive-force disk eventually stops moving under the buffer action. The preload force pushes the transmission axis back to the starting position, and the magnetic repulsive-force valve completes the operation.
The use of a dual-repulsion-disk structure means that under the same driving force, the output force on each repulsion disk is half of that of a single-repulsion-disk structure, which improves the reliability of the transmission structure and electrical components and achieves redundancy backup. The main technical parameters of the dual-repulsion-disk magnetic repulsion valve prototype are shown in Table 3.

7. Result of the Prototype Test

The structural reliability and travel of the redundant design of the magnetic repulsion valve were verified by means of test on the prototype of the hydraulic mechanism of the high-speed circuit breaker.
The motion characteristics of the double repulsion disk magnetic repulsion valve were obtained by using a laser displacement sensor, as shown in Figure 13. The travel data were collected by the KOCOS circuit breaker characteristic tester, which is widely used in the high-voltage switch industry and serves as a common tool for testing the movement stroke of equipment.
The motion characteristic curves of the double repulsion disk electromagnetic repulsion valve under different charging voltages were measured, and the influence of the voltage on the travel and the maximum travel time was investigated. The specific values are shown in Table 4. It can be seen that as the charging voltage increased, the maximum travel of the electromagnetic repulsion valve increased, and meanwhile, the time to reach the maximum travel decreased. The maximum travel error and the action time met the engineering design requirements.
The data under the charging voltage of 1300 Vdc were adopted to compare the characteristic curves of the double repulsion disk magnetic repulsion mechanism between simulation and experiment, as shown in Figure 14. At t1 (0.803 ms), the simulated value coincided with the measured value (17.49 mm); at t2, the difference between the simulated value (21.76 mm) and the measured value (18.92 mm) reached the maximum of 15.01%, and at the end of the movement at t3 (1.46 ms), the difference between the simulated value (22.26 mm) and the measured value (21.19 mm) was 5.04%. It can be seen that the simulation and test values of the total travel and the initial stage of the movement agreed reasonably well. In the later stage of the travel, the difference between the predicted and measured displacement increased. A possible reason may be that the constitutive equation of the polyurethane cannot accurately describe the characteristics of the hyper-elastic transient buffer process.
Test results also showed that the mechanical strength of the repulsion valve with redundancy resign met the requirement of 10,000 mechanical operations. The repulsion value generated by the 2.5 mF capacitor and 1100–1300 V met the design requirements for operating time. The finalized design achieved the expected features of rapid action and transient buffering, and satisfied the product design requirements.

8. Conclusions

A design of a magnetically driven repulsion valve for use in the hydraulic driving mechanism of high-speed power switches has been proposed, optimized by simulation, and verified by test. A dual-repulsion-disk redundancy design was used to successfully reduce the maximum impact force and stress to a level that was safe for the chosen material and met the operational requirements, especially the 10,000 mechanical operations. This was attributed to the evenly distribution of the repulsion value on the two repulsion disks.
With the optimized design proposed in this work, a 2.5 mF capacitor delivers sufficient driving power to rapidly operate the valve. The preferred range of the pre-charging voltage of the capacitor is 1100–1300 V to drive the transmission shaft and the time to reach the peak value of the magnetic force is insensitive to the pre-charging voltage, staying around 0.38 ms. The magnitude of the magnetic force can, however, be adjusted by varying the pre-charging voltage in the range of 0.057 × 106 N–0.074 × 106 N. The repulsion valve, designed according to the above parameters, completed the operation within 2 ms, ensuring the design parameters of the hydraulic mechanism and meeting the functional requirements of high-speed current interruption.
It has been found that the capacitance has large influence on the time to peak of the repulsive magnetic force, the smaller the capacitance, the shorter the time to peak value.
A key element in the design is the choice of the buffer material. It was categorically shown that polyurea polyurethane is better than polyether polyurethane in terms of operational stability and buffering effect. The dual-repulsion-disk redundant structure completed the prototype test. The mechanical structures and electrical circuits of the two disks did not affect each other, demonstrating its value for engineering promotion.

Author Contributions

Y.Z. formulated the technical route involved in this research, implemented the research plan, and produced the draft of the manuscript; J.Z. reviewed the plan and checked the manuscript; simulation and testing was carried out by Z.W., and Y.D. processed the data and edited the manuscript. All authors have read and agreed to the published version of the manuscript.

Funding

This research received no external funding.

Data Availability Statement

The data in this article were collected from tests conducted during the product development process. Due to the involvement of confidential corporate product information, they are not being made public.

Conflicts of Interest

Authors Youpeng Zhang and Zhijun Wang were Ph.D. students at Shenyang University of Technology and employed by the company Pinggao Group Co., Ltd. Author Yingqian Du was employed by the company Pinggao Group Co., Ltd. Author Jianying Zhong was employed by the company China Electric Equipment Group Science and Technology Research Institute Co., Ltd. Authors declare that the research was conducted in the absence of any commercial or financial relationships that could be construed as a potential conflict of interest.

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Figure 1. Schematic diagram illustrating the structure of a magnetic repulsion operating mechanism.
Figure 1. Schematic diagram illustrating the structure of a magnetic repulsion operating mechanism.
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Figure 2. Fracturing of the repulsion disk.
Figure 2. Fracturing of the repulsion disk.
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Figure 3. Diagram illustrating the principle of the repulsive valve.
Figure 3. Diagram illustrating the principle of the repulsive valve.
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Figure 4. Flow diagram for the optimization process of the repulsive valve.
Figure 4. Flow diagram for the optimization process of the repulsive valve.
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Figure 5. Equivalent circuit of magnetic repulsion mechanism.
Figure 5. Equivalent circuit of magnetic repulsion mechanism.
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Figure 6. Computational domain used for the calculation of the magnetic repulsion force.
Figure 6. Computational domain used for the calculation of the magnetic repulsion force.
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Figure 7. Influence of pre-charging voltage on peak value of magnetic repulsion force.
Figure 7. Influence of pre-charging voltage on peak value of magnetic repulsion force.
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Figure 8. Influence of capacitance on peak value of the magnetic repulsion force.
Figure 8. Influence of capacitance on peak value of the magnetic repulsion force.
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Figure 9. Set-up for the compression test of the polyurethane buffer material.
Figure 9. Set-up for the compression test of the polyurethane buffer material.
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Figure 10. Simplified model of single repulsion disk and redundant structure. (a) The single repulsion disk and (b) the double repulsion disk.
Figure 10. Simplified model of single repulsion disk and redundant structure. (a) The single repulsion disk and (b) the double repulsion disk.
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Figure 11. Stress comparison between single-disk structure and redundant structure. (a) Maximum stress of single disk and (b) maximum stress of redundant structure.
Figure 11. Stress comparison between single-disk structure and redundant structure. (a) Maximum stress of single disk and (b) maximum stress of redundant structure.
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Figure 12. Magnetic repulsion valve redundancy design.
Figure 12. Magnetic repulsion valve redundancy design.
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Figure 13. Prototype test of magnetic repulsion mechanism with double repulsion disks.
Figure 13. Prototype test of magnetic repulsion mechanism with double repulsion disks.
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Figure 14. Comparison of simulation and test values for the travel characteristics of the repulsion valve.
Figure 14. Comparison of simulation and test values for the travel characteristics of the repulsion valve.
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Table 1. Load test of different types of polyurethane materials.
Table 1. Load test of different types of polyurethane materials.
Material TypeCompression/mmMean Load Value/kN for Each Batch
Polyether2418, 19, 25, 30, 31
Polyamine242.5, 2.5, 2.6, 2.6, 2.7
Table 2. Comparison of dynamic calculation results between single disk and dual disk.
Table 2. Comparison of dynamic calculation results between single disk and dual disk.
ParametersSingle-Disk StructureDual-Disk Structure
The peak value of collision contact force0.8 × 106 N0.7 × 106 N
The moment of maximum stress4.8 ms2.2 ms
Maximum stress517 MPa419 MPa
Strain energy peak40 J12 J
Table 3. Main technical parameters of electromagnetic repulsion mechanism prototype with double repulsion disks.
Table 3. Main technical parameters of electromagnetic repulsion mechanism prototype with double repulsion disks.
ParameterValue
The outer radius of the coil (mm)80
The number of turns of the coil (turns)44
The outer radius of the metal disk (mm)80
The capacitance value (in mF) corresponding to each repulsion disk2.5
The charging voltage of the capacitor (Vdc)1100–1300
The full travel (mm)20 ± 2
Action duration≤2 ms
The number of repulsion disks and corresponding discharging circuits (units)2
Table 4. The travel characteristics of the magnetic repulsion valve under different voltages.
Table 4. The travel characteristics of the magnetic repulsion valve under different voltages.
Charging Voltage/VdcTravel/mmThe Time of Maximum Travel/ms
110019.71.86
120021.21.66
130021.81.53
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MDPI and ACS Style

Zhang, Y.; Zhong, J.; Wang, Z.; Du, Y. Strength Enhancement and Redundant Design of the Electromagnetic Repulsion Valve for High-Speed Switch Hydraulic Mechanisms. Energies 2025, 18, 2022. https://doi.org/10.3390/en18082022

AMA Style

Zhang Y, Zhong J, Wang Z, Du Y. Strength Enhancement and Redundant Design of the Electromagnetic Repulsion Valve for High-Speed Switch Hydraulic Mechanisms. Energies. 2025; 18(8):2022. https://doi.org/10.3390/en18082022

Chicago/Turabian Style

Zhang, Youpeng, Jianying Zhong, Zhijun Wang, and Yingqian Du. 2025. "Strength Enhancement and Redundant Design of the Electromagnetic Repulsion Valve for High-Speed Switch Hydraulic Mechanisms" Energies 18, no. 8: 2022. https://doi.org/10.3390/en18082022

APA Style

Zhang, Y., Zhong, J., Wang, Z., & Du, Y. (2025). Strength Enhancement and Redundant Design of the Electromagnetic Repulsion Valve for High-Speed Switch Hydraulic Mechanisms. Energies, 18(8), 2022. https://doi.org/10.3390/en18082022

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