Electronic pressure limiting valve and vehicle with same

Abstract

The invention provides an electronic pressure limiting valve and a vehicle with the same. The electronic pressure limiting valve comprises a valve body, a magnetic attraction assembly and an elastic piece, a containing cavity is formed in the valve body, a valve seat and a cover plate are arranged at the two ends of the valve body respectively, and the cover plate and the valve seat are used for being connected with a hydraulic system of a vehicle; the magnetic attraction assembly is arranged in the containing cavity and comprises an armature rod, an armature and an electromagnet, the armature rod is movably connected with the cover plate, the armature rod is provided with an abutting position abutting against the valve seat and a working position separated from the valve seat, the armature is arranged in the circumferential direction of the armature rod, one end of the electromagnet abuts against the cover plate, and the other end of the electromagnet abuts against the valve seat. An air gap is formed between the other end of the electromagnet and the armature; the electromagnet has an adsorption working state of adsorbing the armature to enable the armature to be far away from the valve seat; the elastic piece is arranged between the armature and the electromagnet to drive the armature to be away from the electromagnet. The electronic pressure limiting valve solves the problem that in the prior art, an electronic pressure limiting valve needs high electromagnetic force in a high-pressure use environment, and consequently the electromagnet generates large heat.

Description

Technical Field

[0001] The present invention relates to the technical field of solenoid valves, and in particular to an electronic pressure limiting valve and a vehicle having the same. Background Art

[0002] In the existing technology of common rail systems for diesel engines in vehicles, electronic pressure-limiting valves (EPVs), as a key control component, are widely used to regulate fuel pressure within the system. Most conventional EPVs adopt a normally closed design, with their sealing force primarily driven by electromagnetic force and spring force to ensure accurate control of system pressure in high-pressure environments. However, this design has certain limitations, particularly when the diesel engine common rail system operates under high-pressure conditions. In high-pressure environments, conventional EPVs require increased electromagnetic force to maintain sufficient sealing force, which often causes significant heating of the electromagnet. Heat accumulation in the electromagnet not only affects its service life but can also adversely affect surrounding electronic components. The requirement for high electromagnetic force also requires a larger electromagnet to generate sufficient driving force. This not only increases the overall size of the EPV but can also limit its application in certain space-constrained vehicle systems.

[0003] For the above problems, no effective solution has been proposed yet. Summary of the Invention

[0004] The main purpose of the present invention is to provide an electronic pressure limiting valve and a vehicle having the same, so as to solve the problem in the prior art that the electronic pressure limiting valve requires a high electromagnetic force under high pressure conditions, resulting in high heating of the electromagnet.

[0005] In order to achieve the above-mentioned purpose, according to one aspect of the present invention, an electronic pressure-limiting valve is provided, comprising: a valve body, a accommodating chamber is provided in the valve body, a valve seat and a cover plate are respectively provided at both ends of the valve body, wherein the cover plate and the valve seat are used to connect to the hydraulic system of the vehicle; a magnetic attraction component, the magnetic attraction component is arranged in the accommodating chamber, the magnetic attraction component comprises: an armature rod, an armature and an electromagnet, the armature rod is movably connected to the cover plate, the armature rod has a first working position abutting the valve seat, and a second working position separated from the valve seat, the armature is arranged along the circumference of the armature rod, one end of the electromagnet abuts the cover plate, and an air gap is provided between the other end of the electromagnet and the armature, the electromagnet has an adsorption working state of adsorbing the armature to keep the armature away from the valve seat, and the electromagnet has a non-working state without power; an elastic member, the elastic member is arranged between the armature and the electromagnet to drive the armature away from the electromagnet; wherein the hydraulic pressure, electromagnetic force and elastic force acting on both ends of the armature rod form a hydraulic pressure difference at both ends of the armature rod.

[0006] Furthermore, the armature rod has a first working position in which the armature rod moves toward the valve seat so as to abut against the valve seat, and a second working position in which the armature rod moves away from the valve seat so as to separate from the valve seat.

[0007] Furthermore, a first oil inlet is provided in the valve seat, one end of the first oil inlet is connected to the hydraulic system, and the other end of the first oil inlet is communicated with the accommodating chamber. A sealing steel ball is provided at one end of the valve seat close to the accommodating chamber, and the sealing steel ball is arranged between the valve seat and the armature rod, wherein the inner diameter of the first oil inlet is smaller than the diameter of the sealing steel ball.

[0008] Furthermore, a second oil inlet is provided in the cover plate, one end of the second oil inlet is connected to the hydraulic system, the other end of the second oil inlet is communicated with the accommodating cavity, and at least part of the armature rod is located in the second oil inlet.

[0009] Furthermore, when the armature rod is in the first working position, the armature rod presses the sealing steel ball against the valve seat to block the first oil inlet. When the armature rod is in the second working position, the sealing steel ball is separated from the valve seat. At this time, the first oil inlet is connected to the oil outlet to form a valve seat oil channel.

[0010] Furthermore, the armature rod includes: a first component segment, at least the first component segment is located in the second oil inlet, and the other end of the first component segment is extended along the axial direction of the valve body; a second component segment, one end of the second component segment is connected to the first component segment, wherein the outer diameter of the second component segment is larger than the outer diameter of the first component segment; a third component segment, one end of the third component segment is connected to the second component segment, and the other end of the third component segment is arranged relatively to the axial direction of the valve body close to the valve seat, and the outer diameter of the third component segment gradually decreases toward the valve seat.

[0011] Furthermore, a recessed structure is provided at one end of the third segment close to the valve seat. When the armature rod is located at the first working position, the armature rod abuts against the sealing steel ball through the recessed structure. The size of the recessed structure is set corresponding to the inner diameter of the sealing steel ball.

[0012] Furthermore, the armature is arranged along the circumference of the first component segment and abuts against the end face of the second component segment. The armature and the first component segment have an interference fit. A stepped hole is opened at the end of the valve body away from the valve seat. The electromagnet is arranged along the circumference of the first component segment and has an interference fit with the stepped hole.

[0013] Furthermore, the electronic pressure limiting valve also includes: a sealing ring, which is arranged between the side wall of the cover plate and the side wall of the stepped hole; a locking nut, which is arranged at the end of the cover plate away from the electromagnet, and the locking nut is threadedly connected to the valve body to fix the cover plate or the locking nut is laser welded to the valve body.

[0014] To achieve the above object, according to one aspect of the present invention, a vehicle is provided, comprising an electronic pressure limiting valve, where the electronic pressure limiting valve is any one of the above electronic pressure limiting valves.

[0015] According to the technical solution of the present invention, the pressure limiting valve includes a valve body, a magnetic assembly and an elastic member. The valve body is provided with a receiving cavity, a valve seat is provided at one end, and a cover plate is provided at the other end. The cover plate and the valve seat are both connected to the hydraulic system of the vehicle. The magnetic assembly is composed of an armature rod, an armature and an electromagnet. The hydraulic pressure at both ends of the armature rod, the electromagnetic force generated by the magnetic assembly and the elastic force generated by the elastic member cause a preset hydraulic pressure difference to exist at both ends of the armature rod, thereby driving the armature rod to move along the axial direction of the valve body. Compared with the prior art, only a relatively small electromagnetic force is required to achieve stable operation of the electronic pressure limiting valve, which greatly reduces the energy consumption and heat generation problems of the electromagnet and reduces the volume of the electromagnet. The present application solves the problem in the prior art that the electronic pressure limiting valve requires a high electromagnetic force under high-pressure use environment, resulting in high heat generation of the electromagnet. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The accompanying drawings, which constitute part of this application, are intended to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are intended to explain the present invention and do not constitute an undue limitation of the present invention. In the accompanying drawings:

[0017] Figure 1 It shows a structural schematic diagram of a first embodiment of an electronic pressure limiting valve according to the present invention;

[0018] Figure 2 It shows a structural schematic diagram of a second embodiment of an electronic pressure limiting valve according to the present invention;

[0019] Figure 3 An enlarged schematic diagram of point A of the second embodiment of the electronic pressure limiting valve according to the present invention is shown.

[0020] The above drawings include the following reference numerals:

[0021] 1. Valve seat;

[0022] 100, valve seat oil passage;

[0023] 101, first oil inlet;

[0024] 102, oil outlet;

[0025] 2. Adjust the gasket;

[0026] 3. Valve body;

[0027] 31. Stepped hole;

[0028] 4. Armature rod;

[0029] 41. The first group of paragraphs;

[0030] 42. The second group of paragraphs;

[0031] 43. The third group of paragraphs;

[0032] 431, concave structure;

[0033] 5. Armature;

[0034] 6. Electromagnet;

[0035] 7. Sealing ring;

[0036] 8. Lock nut;

[0037] 9. Cover plate;

[0038] 91, second oil inlet;

[0039] 10. Elastic parts;

[0040] 11. Sealing steel ball. DETAILED DESCRIPTION

[0041] It should be noted that, in the absence of conflict, the embodiments and features of the embodiments in this application can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0042] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0043] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way are interchangeable where appropriate, so that the embodiments of the present application described herein can, for example, be implemented in an order other than those illustrated or described herein. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0044] Now, exemplary embodiments according to the present application will be described in more detail with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in a variety of different forms and should not be interpreted as being limited to the embodiments described herein. It should be understood that these embodiments are provided to make the disclosure of this application thorough and complete, and to fully convey the concepts of these exemplary embodiments to those of ordinary skill in the art. In the accompanying drawings, for the sake of clarity, the thickness of layers and regions may be exaggerated, and the same reference numerals are used to represent the same devices, and thus their descriptions will be omitted.

[0045] Combine Figures 1 to 3 As shown, according to a specific embodiment of the present application, an electronic pressure limiting valve is provided.

[0046] Specifically, the electronic pressure limiting valve includes: a valve body 3, a magnetic attraction component and an elastic member 10. The valve body 3 is provided with an accommodating cavity, and a valve seat 1 and a cover plate 9 are provided at both ends of the valve body 3, wherein the cover plate 9 and the valve seat 1 are used to connect to the hydraulic system of the vehicle; the magnetic attraction component is arranged in the accommodating cavity, and the magnetic attraction component includes: an armature rod 4, an armature 5 and an electromagnet 6. The armature rod 4 is movably connected to the cover plate 9. The armature rod 4 has a first working position abutting the valve seat 1, and has a second working position separated from the valve seat 1. The armature 5 is arranged along the circumference of the armature rod 4, one end of the electromagnet 6 is in contact with the cover plate 9, and there is an air gap between the other end of the electromagnet 6 and the armature 5. The electromagnet 6 has an adsorption working state to adsorb the armature 5 so that the armature 5 is away from the valve seat 1, and the electromagnet 6 has a non-working state without power; the elastic member 10 is arranged between the armature 5 and the electromagnet 6 to drive the armature 5 away from the electromagnet 6; wherein, the hydraulic pressure, electromagnetic force and elastic force acting on the two ends of the armature rod 4 form a hydraulic pressure difference at both ends of the armature rod 4.

[0047] According to the technical solution of the present invention, the pressure limiting valve includes a valve body 3, a magnetic assembly and an elastic member 10. The valve body 3 is provided with a receiving cavity, a valve seat 1 is provided at one end, and a cover plate 9 is provided at the other end. Both the cover plate and the valve seat are connected to the hydraulic system of the vehicle. The magnetic assembly is composed of an armature rod 4, an armature 5 and an electromagnet 6. The hydraulic pressure at both ends of the armature rod 4, the electromagnetic force generated by the magnetic assembly and the elastic force generated by the elastic member 10, create a preset hydraulic pressure difference between the two ends of the armature rod 4, thereby driving the armature rod 4 to move along the axial direction of the valve body 3. Compared with the prior art, only a relatively small electromagnetic force is required to achieve stable operation of the electronic pressure limiting valve, which greatly reduces the energy consumption and heat generation of the electromagnet and reduces the size of the electromagnet. The present application solves the problem in the prior art that the electronic pressure limiting valve requires a high electromagnetic force under high-pressure use conditions, resulting in high heat generation of the electromagnet.

[0048] It should be further explained that a hydraulic pressure difference is formed at both ends of the armature rod 4 to drive the armature rod 4 to move along the axial direction of the valve body 3 to control the opening and closing of the electronic pressure limiting valve.

[0049] Specifically, the armature rod 4 has a first working position in which it moves toward the valve seat 1, abutting the valve seat 1, and a second working position in which it moves away from the valve seat 1, separating the armature rod 4 from the valve seat 1. When the electromagnet is de-energized, i.e., the electromagnetic force is zero, the hydraulic pressure Fleft on the left side of the armature rod 4 is less than the combined pressure Fright on the right side of the armature rod 4 and the spring force of the elastic member 10, causing the armature rod 4 to press against the valve seat 1, forming a seal and placing the electronic pressure limiting valve in a closed state. When the electromagnet is energized, the electromagnetic force it generates overcomes the preload of the spring and the hydraulic pressure on the right side (i.e., the combined force of the hydraulic pressure Fleft on the left side of the armature rod 4 and the electromagnetic force generated by the electromagnet is greater than the combined pressure Fright on the right side of the armature rod 4 and the spring force of the elastic member 10), causing the armature rod 4 to move closer to the cover plate 9, away from the first working position, and toward the second working position. At this point, the armature rod 4 is separated from the valve seat 1, allowing fluid to pass. As the electromagnetic force increases, the armature rod continues to move closer to the cover plate 9 until it reaches the maximum stroke of the second working position, at which time the fluid flow rate also reaches the maximum value.

[0050] Specifically, if Figure 1 As shown, a first oil inlet 101 is provided in the valve seat 1. One end of the first oil inlet 101 is connected to the hydraulic system, and the other end of the first oil inlet 101 is in communication with the accommodating chamber. A sealing steel ball 11 is provided at the end of the valve seat 1 near the accommodating chamber. The sealing steel ball 11 is disposed between the valve seat 1 and the armature rod 4. The inner diameter of the first oil inlet 101 is smaller than the diameter of the sealing steel ball 11. By providing the first oil inlet 101 in the valve seat and utilizing the difference in diameter between the first oil inlet 101 and the sealing steel ball 11, the size design of the first oil inlet ensures that a good seal is formed between the sealing steel ball and the valve seat in the closed state, effectively preventing leakage of high-pressure fluid and ensuring the safety and operational reliability of the system.

[0051] In this embodiment, the first oil inlet 101 is designed as two interconnected component sections, the first component section is directly connected to the hydraulic system, and the second component section is connected to the accommodating chamber, and the inner diameter of the first component section is larger than the inner diameter of the second component section. As the part directly connected to the hydraulic system, the first component section has a larger inner diameter, which can allow the fluid to flow in more smoothly. As the fluid enters the second component section, the speed of the fluid will increase due to the sudden decrease in the inner diameter. The acceleration of the fluid speed is conducive to forming a certain pressure gradient in the second component section, promoting the smooth passage of the fluid. At the same time, by controlling the diameter ratio of the first component section to the second component section, the pressure loss of the fluid when passing through the oil inlet can be adjusted to achieve preliminary regulation of the fluid pressure. The inner diameter of the second component section is smaller than the diameter of the sealing steel ball 11, ensuring that the sealing steel ball can form a more compact seal on the second component section.

[0052] Specifically, a second oil inlet 91 is provided in the cover plate 9. One end of the second oil inlet 91 is connected to the hydraulic system, and the other end of the second oil inlet 91 is connected to the accommodating chamber. At least part of the armature rod 4 is located inside the second oil inlet 91. At least part of the armature rod is located inside the second oil inlet 91, which means that when the fluid passes through the second oil inlet 91, it will directly contact the armature rod, generating hydraulic pressure on one end of the armature rod 4. One end of the armature rod 4 is in close contact with the sealing steel ball 11 and is connected to the first oil inlet of the valve seat 1. The other end of the armature rod 4 is connected to the second oil inlet 91. By adjusting the contact area (i.e., diameter) of these two ends, the magnitude of the force exerted by the hydraulic pressure on the armature rod 4 can be changed, so that there is a controllable hydraulic pressure difference between the left and right ends of the armature rod 4 axially. Combined with the spring force of the elastic member 10 and the electromagnetic force of the electromagnet 6, the electronic pressure limiting valve can operate stably. When the electronic pressure limiting valve is in the closed state, the hydraulic pressure Fleft on the left side of the armature rod 4 is less than the pressure Fright on the right side of the armature rod 4 and the spring force of the elastic member 10, so that the armature rod 4 remains in the first working position. At this time, the sealing steel ball 11 forms a tight seal with the valve seat 1.

[0053] Specifically, when the armature rod 4 is in the first working position, the armature rod 4 presses the sealing steel ball 11 against the valve seat 1 to block the first oil inlet 101. When the armature rod 4 is in the second working position, the sealing steel ball 11 is separated from the valve seat 1. At this time, the first oil inlet 101 is connected to the oil outlet 102 to form the valve seat oil passage 100. When the electromagnet 6 is not energized or the electromagnetic force is insufficient to overcome the hydraulic pressure difference formed at both ends of the armature rod 4, the armature rod 4 is in the first working position. At this time, the armature rod presses the sealing steel ball 11 against the valve seat 1, causing the sealing steel ball 11 to fit tightly into the groove of the valve seat, thereby effectively blocking the first oil inlet 101. This blocked state prevents high-pressure fluid from flowing from the first oil inlet 101 into the accommodating chamber, ensuring the stability of the system pressure and avoiding energy waste and equipment damage. When the electromagnetic force generated by the electromagnet is sufficient to overcome the hydraulic pressure differential across the ends of the armature rod 4, the armature rod 4 moves to its second operating position, moving closer to the cover plate 9 and away from the valve seat 1, no longer exerting pressure on the sealing ball 11. At this point, the sealing ball 11, under the action of the hydraulic pressure, no longer contacts the valve seat 1. The first oil inlet 101 is released and communicates with the oil outlet 102, forming a complete valve seat oil passage 100. This passage allows high-pressure fluid to flow smoothly from the first oil inlet to the oil outlet, thereby achieving pressure regulation or fluid discharge.

[0054] It should be further explained that the valve seat 1 is typically inserted into a pre-set hole at one end of the valve body 3 through an interference fit, or is fastened to the valve body 3 via a threaded connection, ensuring sufficient preload between the valve seat and the valve body to maintain good sealing and stability. The adjustment gasket 2 is located between the valve seat 1 and the valve body 3. Its main function is to adjust the initial gap between the valve seat 1 and the sealing steel ball 11, thereby affecting the preload of the sealing steel ball 11 and the opening pressure of the entire valve. By replacing gaskets of different thicknesses, the contact pressure between the sealing steel ball 11 and the valve seat 1 can be fine-tuned to ensure optimal sealing and responsiveness under different operating conditions.

[0055] Specifically, if Figure 2 As shown, the armature rod 4 includes: a first component segment 41, a second component segment 42, and a third component segment 43. At least the first component segment 41 is located within the second oil inlet 91, and the other end of the first component segment is arranged to extend axially along the valve body 3. One end of the second component segment 42 is connected to the first component segment 41, wherein the outer diameter of the second component segment 42 is larger than the outer diameter of the first component segment 41. One end of the third component segment 43 is connected to the second component segment 42, and the other end of the third component segment 43 is arranged axially relative to the valve seat 1 along the valve body 3, and the outer diameter of the third component segment 43 gradually decreases toward the valve seat 1. The segmented design also takes into account the structural strength of the armature rod 4. The change in outer diameter of the different components not only optimizes the fluid dynamic performance, but also ensures that the armature rod 4 maintains the necessary rigidity and stability when subjected to high-pressure fluid and electromagnetic force, avoiding structural deformation or failure.

[0056] The conical design of the third segment 43 guides the sealing steel ball 11 to form a good contact seal with the valve seat 1, thereby reducing leakage and improving sealing performance.

[0057] The outer diameter of the second component segment 42 is larger than that of the first component segment 41. This design can reduce the contact area with the inner wall of the valve body 3 when the armature rod 4 moves, thereby reducing the friction, so that the armature rod 4 can respond more quickly under the drive of the electromagnetic force and the spring force, and realize rapid opening and closing actions.

[0058] Specifically, if Figure 3 As shown, the third segment 43 has a recessed structure 431 at one end near the valve seat 1. When the armature rod 4 is in the first working position, the armature rod 4 contacts the sealing steel ball 11 through the recessed structure 431. The size of the recessed structure 431 corresponds to the inner diameter of the sealing steel ball 11. The end of the third segment 43 is designed with a recessed structure 431, which is sized to match the inner diameter of the sealing steel ball 11, forming a precise contact surface. When the armature rod is in the first working position (i.e., closed), the recessed structure 431 directly contacts the sealing steel ball 11, allowing the sealing steel ball 11 to be accurately and stably placed on the valve seat 1, forming a seal.

[0059] In this embodiment, the recessed structure 431 is an arc surface, which reduces the contact area between the sealing steel ball 11 and the third component segment 43 of the armature rod 4. In the traditional design, the contact between the sealing steel ball 11 and the armature rod 4 is surface contact, while the recessed structure 431 is converted into point contact. This change significantly reduces the pressure distribution and friction in the contact area, thereby reducing the wear between the sealing steel ball 11 and the armature rod 4 during the frequent switching of the electronic pressure limiting valve, and extending the service life of the component. When the electronic pressure limiting valve is closed (that is, the armature rod 4 is in the first working position), the sealing steel ball 11 can be naturally positioned in the recessed structure 431, and even under the impact of high-pressure fluid, it can remain stable and will not easily deviate. This self-positioning feature helps to improve the sealing performance and maintain a high sealing effect even after long-term operation. The design of the arc surface allows the force from the elastic member 10 and the electromagnet 6 to be more evenly distributed on the sealing steel ball 11, rather than concentrated on a few points. This uniform distribution of force reduces the local stress concentration of the sealing steel ball 11 , reduces the risk of fatigue damage to the sealing steel ball 11 , and further extends the service life of the electronic pressure limiting valve.

[0060] It should be further explained that the diameter of the sealing steel ball directly affects the size of its contact surface with the valve seat, and thus the hydraulic pressure P passing through the first oil inlet 101. If the diameter of the sealing steel ball is designed to be too large, the contact area with the valve seat will increase, thereby increasing the effect of the hydraulic pressure P on the sealing steel ball in the closed state, requiring greater electromagnetic force and spring force to overcome. Conversely, a smaller diameter will reduce the impact of the hydraulic pressure, but may reduce the sealing effect. The diameter of the armature rod is directly related to the force acting on the hydraulic pressure P. Adjusting the diameter of the armature rod in different sections (such as the first component section 41, the second component section 42, and the third component section 43) can optimize the force generated by the hydraulic pressure on both ends of the armature rod, ensuring force balance in the open and closed states. When the electronic pressure limiting valve is closed, by adjusting the diameters of the sealing steel ball and the armature rod, as well as the hydraulic system pressure P, the designer can calculate and set an ideal "hydraulic pressure difference." This hydraulic pressure difference threshold ensures that under normal operating conditions, the sealing steel ball can tightly seal the first oil inlet 101, and its sealing performance is not affected even when the hydraulic system pressure P is high. When electromagnet 6 is energized, the electromagnetic force generated overcomes the spring force of elastic member 10, driving the armature rod to its second operating position, thereby releasing the sealing ball. As the armature rod moves, the hydraulic pressure differential generated by the hydraulic system pressure P at both ends of the armature rod's axial direction varies. By optimizing the diameters of the sealing ball and armature rod, designers can control this hydraulic pressure differential, ensuring smooth movement of the armature rod 4 and achieving precise control of the fluid passage.

[0061] Specifically, the armature 5 is arranged circumferentially along the first segment 41 and abuts the end surface of the second segment 42. The armature 5 forms an interference fit with the first segment 41. A stepped hole 31 is defined at the end of the valve body 3 facing away from the valve seat 1. The electromagnet 6 is arranged circumferentially along the first segment 41 and forms an interference fit with the stepped hole 31. The circumferential arrangement and interference fit between the armature 5 and the armature rod 4, as well as the interference fit between the electromagnet 6 and the stepped hole 31, not only ensure the effective transmission and response of the electromagnetic force, but also improve the structural stability and operating precision of the electronic pressure-limiting valve, reduce energy consumption and wear, and extend the service life of the components.

[0062] The armature 5 is arranged circumferentially along the first segment 41, abutting the end surface of the second segment 42. This circumferential arrangement ensures that the electromagnetic force acts directly on the armature rod 4, thereby driving the entire armature rod 4 in the axial direction. The interference fit between the armature 5 and the first segment 41 provides additional securing force, ensuring that the armature 5 moves synchronously with the armature rod 4 under the action of the electromagnetic force, thereby avoiding force transmission losses and component wear caused by relative sliding or friction.

[0063] In another optional embodiment, the armature 5 is welded to the armature rod 4. Welding, as a permanent connection, significantly enhances the structural rigidity between the armature and the armature rod, forming an inseparable unit. Welding eliminates any gap between the armature 5 and the armature rod 4, ensuring direct, lossless transmission of electromagnetic force to the armature rod 4, thereby improving force transmission efficiency and response speed. This direct connection reduces energy loss during force transmission, making the electromagnetic control of the electronic pressure-limiting valve more sensitive and precise. It also prevents relative slip between the armature and the armature rod, reduces friction and contact wear, and extends the service life of the assembly.

[0064] The stepped hole 31 formed at the end of the valve body 3 facing away from the valve seat 1 forms an interference fit with the electromagnet 6, that is, the electromagnet 6 is tightly fixed inside the stepped hole 31. This interference fit not only ensures the stable position of the electromagnet 6, but also improves the alignment between the electromagnet 6 and the armature 5, so that the electromagnetic force can act on the armature 5 more accurately and effectively. The interference fit between the armature 5 and the armature rod 4 and the interference fit between the electromagnet 6 and the stepped hole 31 ensures the efficient conversion of electromagnetic force into mechanical motion. This design reduces energy loss during force transmission and improves the response speed and control accuracy of the electromagnetic pressure limiting valve. The interference fit design simplifies the assembly process of the components, reduces the need for precise positioning and adjustment, and improves assembly efficiency and component consistency.

[0065] In this embodiment, the air gap between the electromagnet 6 and the armature 5 ranges from 0.1 to 0.3 mm. When the electromagnet attracts the armature, the magnitude of the electromagnetic force is inversely proportional to the size of the air gap. In other words, the smaller the air gap, the greater the attractive force generated by the electromagnet. When designing an electronic pressure-limiting valve, by setting the air gap size, the minimum attractive force required by the electromagnet can be adjusted, thereby controlling the electromagnet's current and optimizing energy consumption. The air gap between the electromagnet and the armature prevents direct contact between the two. During operation of the pressure-limiting valve, direct contact between the armature and the electromagnet can cause wear and even jamming of the components due to mechanical friction or collision, affecting the normal opening and closing of the valve. This air gap design ensures smooth movement of the armature under the influence of the electromagnetic force, improving the reliability and service life of the valve. In this embodiment, maintaining a small air gap of 0.1 to 0.3 mm between the electromagnet and the armature increases the magnetic resistance of the magnetic circuit without excessively weakening the electromagnetic force. This helps the electromagnet generate sufficient magnetic force to drive the armature rod 4 at low currents while preventing electromagnetic force attenuation caused by excessive magnetic resistance. The small air gap helps the heat generated by the electromagnet to dissipate quickly, avoiding the degradation or damage of the electromagnet due to overheating.

[0066] Specifically, the electronic pressure limiting valve also includes: a sealing ring 7 and a locking nut 8, the sealing ring 7 is arranged between the side wall of the cover plate 9 and the side wall of the stepped hole 31; the locking nut 8 is arranged at the end of the cover plate 9 away from the electromagnet 6, and the locking nut 8 is threadedly connected to the valve body 3 to fix the cover plate 9 or the locking nut 8 is laser welded to the valve body 3.

[0067] The sealing ring 7 is arranged between the side wall of the cover plate 9 and the side wall of the stepped hole 31 on the valve body 3. The sealing ring 7 effectively prevents air, moisture and other external impurities from entering the interior of the valve body 3, creating a reliable sealing environment, avoiding these impurities from corroding or interfering with components such as the electromagnet 6 and the armature rod 4, and keeping the interior clean.

[0068] The main function of the lock nut 8 is to secure the cover plate 9 in place, ensuring that the electromagnet 6 is stably installed within the valve body 3. The lock nut 8 is typically located at the end of the cover plate 9 away from the electromagnet 6 and is threadedly connected to the valve body 3. The threaded connection of the lock nut 8 provides sufficient tightening force, ensuring the stability of the cover plate 9 under various operating conditions and preventing loosening or displacement of components due to vibration or pressure fluctuations. This threaded connection allows the user to easily remove the lock nut 8 when necessary, facilitating inspection, cleaning, or replacement of internal components such as the electromagnet 6 and armature rod 4, thereby improving the maintainability of the electronic pressure-limiting valve.

[0069] In another optional embodiment, the locking nut 8 can be connected to the valve body 3 using laser welding, in addition to traditional threaded connections. Laser welding permanently secures the locking nut 8 to the valve body 3, providing greater vibration resistance and water resistance than threaded connections, making it suitable for applications requiring higher stability and sealing. Compared to threaded connections, the weld formed by laser welding is less susceptible to mechanical vibration, significantly reducing the risk of high-pressure oil leakage caused by loose connections.

[0070] Optionally, the cover plate 9 and the armature rod 4 are a pair of mating parts, and form a mating seal. Their contact surfaces are precisely designed and processed, with a high degree of surface finish and geometric accuracy, to ensure that liquid cannot leak through the gap between them under high-pressure working conditions. That is, the high-pressure fluid introduced from the second oil inlet will not leak. This seal is usually achieved in the following ways: the contact surface of the cover plate 9 and the armature rod 4 is finely processed to make the surface very smooth, reducing the possibility of liquid leaking through tiny gaps; the geometric shape and size of the contact surface are precisely controlled to ensure that the cover plate 9 and the armature rod 4 can be accurately aligned during assembly to form a tight fit. Materials with good wear resistance and corrosion resistance are used to ensure sealing performance under long-term operation.

[0071] In this embodiment, the electronic pressure-limiting valve is designed as a normally closed valve, meaning it is closed when the electromagnet is not energized. This valve can be modified to a normally open valve, meaning it is open when the electromagnet is not energized. In this normally closed valve configuration, the combination of spring force and hydraulic pressure forces the sealing steel ball to press firmly against the valve seat, closing the fluid passage. At this time, the electromagnet is de-energized, thus generating no additional electromagnetic force. Only when the electromagnet is energized and generates sufficient electromagnetic force to overcome the spring force and sealing fluid pressure does the armature rod pull toward the electromagnet, thereby pulling the sealing steel ball away from the valve seat, opening the valve and allowing fluid to flow. In a normally open valve design, the spring no longer serves as the power source for closing the valve. Instead, it is used to push the armature rod away from the electromagnet when the electromagnet is de-energized, thereby opening the fluid passage. Therefore, the spring's mounting position and pre-compression need to be redesigned or adjusted to ensure that the spring force is sufficient to push the sealing steel ball away from the valve seat when the electromagnet is not energized. To ensure the valve remains open when the solenoid is deactivated, the dimensions of the sealing ball and armature rod, as well as their relative positioning to the valve body's internal structure, must be carefully adjusted to achieve a balanced hydraulic pressure. The goal is for the hydraulic pressure to push the sealing ball away from the valve seat when the solenoid is deactivated. When the solenoid is activated, the electromagnetic force combined with the adjusted hydraulic pressure effectively presses the sealing ball back into the valve seat, closing the fluid passage. In the normally open valve state, the solenoid acts as a trigger to close the fluid passage, rather than opening it. Therefore, the solenoid's control circuitry and logic must be adjusted to ensure that, when energized, the electromagnetic force is strong enough to overcome the adjusted spring force and hydraulic pressure, thereby closing the valve.

[0072] From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects:

[0073] 1. Using hydraulic pressure to assist the opening or closing of the solenoid valve significantly reduces the demand for electromagnetic force, thereby reducing the energy consumption of the electromagnet, improving the energy utilization efficiency of the overall equipment, and reducing the heat burden during operation.

[0074] 2. Through optimized design, especially the recessed structure of the third segment of the armature rod, the armature rod contacts the sealing steel ball through the recessed structure, thereby reducing the wear of the sealing steel ball and the armature rod.

[0075] The above embodiments can also be used in the field of equipment technology. That is, according to another aspect of the present invention, a vehicle is provided, including an electronic pressure limiting valve, characterized in that the electronic pressure limiting valve is the electronic pressure limiting valve of any one of the above embodiments.

[0076] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used herein to describe the spatial positional relationship of a device or feature to other devices or features as shown in the figures. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figures. For example, if the device in the drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0077] In addition to the above, it should be noted that references to "one embodiment," "another embodiment," "an embodiment," and the like in this specification refer to specific features, structures, or characteristics described in conjunction with that embodiment as included in at least one embodiment generally described in this application. The appearance of the same expression in multiple places in the specification does not necessarily refer to the same embodiment. Furthermore, when a specific feature, structure, or characteristic is described in conjunction with any embodiment, it is intended that such feature, structure, or characteristic, when implemented in conjunction with other embodiments, also falls within the scope of the present invention.

[0078] In the above embodiments, the description of each embodiment has its own focus. For parts that are not described in detail in a certain embodiment, reference can be made to the relevant descriptions of other embodiments.

[0079] The foregoing description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Those skilled in the art will readily appreciate that various modifications and variations of the present invention are possible. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention are intended to be within the scope of protection of the present invention.

Claims

1. An electronic pressure limiting valve, characterized in that: include: A valve body (3), wherein a receiving cavity is provided in the valve body (3), and a valve seat (1) and a cover plate (9) are respectively provided at both ends of the valve body (3), wherein the cover plate (9) and the valve seat (1) are used to connect to a hydraulic system of a vehicle; A magnetic attraction component, wherein the magnetic attraction component is arranged in the accommodating cavity, and the magnetic attraction component comprises: an armature rod (4), an armature (5) and an electromagnet (6); the armature rod (4) is movably connected to the cover plate (9); the armature rod (4) has a first working position abutting against the valve seat (1), and a second working position separated from the valve seat (1); the armature (5) is arranged along the circumference of the armature rod (4); one end of the electromagnet (6) abuts against the cover plate (9); an air gap is provided between the other end of the electromagnet (6) and the armature (5); the electromagnet (6) has an adsorption working state of adsorbing the armature (5) to keep the armature (5) away from the valve seat (1); and the electromagnet (6) has a non-working state of not being energized; an elastic member (10), the elastic member (10) being arranged between the armature (5) and the electromagnet (6) to drive the armature (5) away from the electromagnet (6); The hydraulic pressure, electromagnetic force and elastic force acting on the two ends of the armature rod (4) form a hydraulic pressure difference at the two ends of the armature rod (4).

2. The electronic pressure limiting valve according to claim 1, characterized in that: The armature rod (4) has a first working position in which it moves toward the valve seat (1) so as to make the armature rod (4) abut against the valve seat (1), and the armature rod (4) has a second working position in which it moves away from the valve seat (1) so as to separate the armature rod (4) from the valve seat (1).

3. The electronic pressure limiting valve according to claim 1, characterized in that: A first oil inlet (101) is provided in the valve seat (1), one end of the first oil inlet (101) is connected to the hydraulic system, and the other end of the first oil inlet (101) is communicated with the accommodating cavity. A sealing steel ball (11) is provided at one end of the valve seat (1) close to the accommodating cavity, and the sealing steel ball (11) is arranged between the valve seat (1) and the armature rod (4), wherein the inner diameter of the first oil inlet (101) is smaller than the diameter of the sealing steel ball (11).

4. The electronic pressure limiting valve according to claim 3, characterized in that: A second oil inlet (91) is provided in the cover plate (9), one end of the second oil inlet (91) is connected to the hydraulic system, the other end of the second oil inlet (91) is communicated with the accommodating cavity, and at least part of the armature rod (4) is located in the second oil inlet (91).

5. The electronic pressure limiting valve according to claim 4, characterized in that: When the armature rod (4) is located at the first working position, the armature rod (4) presses the sealing steel ball (11) against the valve seat (1) to seal the first oil inlet (101); when the armature rod (4) is located at the second working position, the sealing steel ball (11) is separated from the valve seat (1), and at this time, the first oil inlet (101) is connected to the oil outlet (102) to form a valve seat oil channel (100).

6. The electronic pressure limiting valve according to claim 5, characterized in that: The armature rod (4) comprises: a first component section (41), at least the first component section (41) is located in the second oil inlet (91), and the other end of the first component section is extended along the axial direction of the valve body (3); a second component segment (42), one end of the second component segment (42) being connected to the first component segment (41), wherein the outer diameter of the second component segment (42) is greater than the outer diameter of the first component segment (41); A third component segment (43), one end of the third component segment (43) is connected to the second component segment (42), the other end of the third component segment (43) is arranged relatively close to the valve seat (1) along the axial direction of the valve body (3), and the outer diameter of the third component segment (43) gradually decreases toward the valve seat (1).

7. The electronic pressure limiting valve according to claim 6, characterized in that: A recessed structure (431) is provided at one end of the third component segment (43) close to the valve seat (1); when the armature rod (4) is located at the first working position, the armature rod (4) abuts against the sealing steel ball (11) through the recessed structure (431); and the size of the recessed structure (431) is set corresponding to the inner diameter of the sealing steel ball (11).

8. The electronic pressure limiting valve according to claim 6, characterized in that: The armature (5) is arranged along the axial direction of the first component segment (41) and abuts against the end face of the second component segment (42). The armature (5) is interference-fitted with the first component segment (41). A stepped hole (31) is provided at one end of the valve body (3) away from the valve seat (1). The electromagnet (6) is arranged along the circumference of the first component segment (41) and is interference-fitted with the stepped hole (31).

9. The electronic pressure limiting valve according to claim 8, characterized in that: The electronic pressure limiting valve further includes: a sealing ring (7), the sealing ring (7) being arranged between a side wall of the cover plate (9) and a side wall of the stepped hole (31); A locking nut (8), wherein the locking nut (8) is arranged at one end of the cover plate (9) away from the electromagnet (6), and the locking nut (8) is threadedly connected to the valve body (3) to fix the cover plate (9) or the locking nut (8) is laser welded to the valve body (3).

10. A vehicle comprising an electronic pressure limiting valve, characterized in that: The electronic pressure limiting valve is the electronic pressure limiting valve according to any one of claims 1 to 9.

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