Iron core assembly, electromagnetic valve, shock absorber, suspension system, and vehicle

Abstract

The application discloses a kind of iron core assembly, solenoid valve, shock absorber, suspension system and vehicle.Iron core assembly includes fixed iron core, body and moving iron core component.Body is connected to fixed iron core, and with fixed iron core jointly form accommodating cavity.Moving iron core component includes moving iron core and valve core connected to moving iron core, moving iron core is movably arranged in accommodating cavity, and outer peripheral wall of moving iron core is provided with communication groove, communication groove is used for fluid flow, and communication groove includes abutting first slot and second slot in the axial direction of moving iron core, and the size of first slot in the circumferential direction of moving iron core is greater than the size of second slot in the circumferential direction.In the application, moving iron core component is subjected to damping force during movement, so that the continuous vibration of valve core when subjected to liquid flow impact and disturbance can be quickly converged, and the stability of solenoid valve operation is improved.

Description

Technical Field

[0001] This application relates to the field of vehicle technology, and more specifically, to a core assembly, a solenoid valve, a shock absorber, a suspension system, and a vehicle. Background Technology

[0002] Shock absorbers are typically installed between the vehicle body and wheels to improve ride comfort. In related technologies, solenoid valves control the movement of the valve core by controlling the on / off state and magnitude of the current, thereby controlling the damping force of the shock absorber. Generally, when the solenoid valve is operating, the valve core is suspended in the fluid flow. The valve core is susceptible to fluid flow impacts and disturbances, leading to an unstable state and causing continuous vibration of the valve core, which affects the stability of the solenoid valve's operation. Summary of the Invention

[0003] This application provides a core assembly, a solenoid valve, a shock absorber, a suspension system, and a vehicle to solve at least one of the aforementioned technical problems.

[0004] The core assembly of this application includes a fixed core, a body, and a moving core component. The body is connected to the fixed core and together with the fixed core forms a receiving cavity. The moving core component includes a moving core and a valve core connected to the moving core. The moving core is movably disposed in the receiving cavity. A communicating groove is provided on the outer peripheral wall of the moving core for fluid flow. The communicating groove includes a first groove and a second groove that are connected in the axial direction of the moving core. The circumferential dimension of the first groove in the moving core is larger than the circumferential dimension of the second groove.

[0005] In some embodiments, the connecting slots include at least two, and the at least two connecting slots are spaced apart on the outer peripheral wall of the moving iron core in the circumferential direction of the moving iron core.

[0006] In some embodiments, the first groove has a dimension w1 in the circumferential direction, and the second groove has a dimension w2 in the circumferential direction, wherein the value of w1 / w2 is [1.5, 2.5].

[0007] In some embodiments, the equivalent diameter of the second groove is d, and the length of the second groove in the axial direction is L, wherein the value of L / d is [0.5, 4.0].

[0008] In some embodiments, there is a gap (107) between the outer peripheral wall (511) of the moving iron core (51) and the body (30), the gap (107) being used for fluid flow; the moving iron core is used to divide the accommodating cavity into a first cavity and a second cavity, and the gap and the communicating groove are both used to connect the first cavity and the second cavity.

[0009] In some embodiments, when the moving iron core component moves relative to the body, the flow rate of the fluid flowing through the communicating groove is Q1, the flow rate of the fluid flowing through the gap is Q2, the pressure difference between the first cavity and the second cavity is ΔP, and the relationships between Q1 and ΔP, and between Q2 and ΔP, satisfy:

[0010] ΔP∝Q1 2 ;or,

[0011] ΔP∝Q²; or,

[0012] Among them, c v ρ is the flow coefficient; A is the cross-sectional area of ​​the moving iron core; ρ is the density of the fluid; d is the maximum dimension of the cross-section of the moving iron core; δ is the radial dimension of the gap in the moving iron core; s is the axial length of the moving iron core; v is the moving speed of the valve core.

[0013] In some embodiments, the first trough has a circumferential dimension of w1, the second trough has a circumferential dimension of w2, and the flow coefficient c v Calculated using the following formula:

[0014]

[0015] Among them, c v The value is [0.4, 0.65].

[0016] In some embodiments, when the fluid flows through the communicating channel, the damping force on the valve core is F1, and when the fluid flows through the gap, the damping force on the valve core is F2, and the moving speed of the valve core is v. The relationships between F1 and v, and between F2 and v, satisfy:

[0017] F1 = cv 2 ;

[0018] F2 = cv;

[0019] Where c is the damping coefficient.

[0020] In some embodiments, the gap is connected in parallel with the connecting groove; when the moving iron core component moves relative to the body and fluid flows through the connecting groove and the gap, the damping force on the valve core is F. c The valve core moves at a speed of v, and the flow rate of the fluid passing through the gap and the connecting groove is Q. t The pressure difference between the first chamber and the second chamber is ΔP, F c With v, and Q t The relationship with △P satisfies:

[0021]

[0022]

[0023] Where c2 and c3 are damping coefficients.

[0024] In some embodiments, the body includes a valve body and a magnetic shielding ring. The valve body covers the moving iron core, and the magnetic shielding ring surrounds the moving iron core and is connected between the valve body and the fixed iron core. The valve body, the magnetic shielding ring, and the fixed iron core together form the receiving cavity.

[0025] In some embodiments, the body has a guide groove on the inner wall of the moving iron core along the axial direction; the iron core assembly also includes a first guide sleeve disposed in the guide groove, and the valve core is movably fitted with the first guide sleeve.

[0026] In some embodiments, the fixed iron core is provided with a guide hole; the iron core assembly further includes a second guide sleeve disposed in the guide hole, and the valve core is movably fitted with the second guide sleeve.

[0027] In some embodiments, the moving iron core includes opposing first and second ends in the axial direction; the core assembly further includes a first elastic member and a second elastic member. The first elastic member is disposed between the first end of the moving iron core and the body. The second elastic member is disposed between the second end of the moving iron core and the body; wherein the first elastic member and the second elastic member together apply a spring force to the moving iron core to maintain the moving iron core and the body at a distance between their opposite sides in the axial direction.

[0028] The solenoid valve in this application includes the iron core assembly described in any of the above embodiments.

[0029] The vibration damper in this application includes the solenoid valve described in the above embodiments.

[0030] The suspension system of this application includes the shock absorber described in the above embodiments.

[0031] The vehicle described in this application includes the suspension system described in the above embodiments.

[0032] In the iron core assembly, solenoid valve, shock absorber, suspension system, and vehicle of the present application embodiments, a connecting groove is provided on the outer peripheral wall of the moving iron core. The connecting groove is used for fluid flow. Thus, when the valve core and the moving iron core move relative to the body, the fluid can flow through the connecting groove in the accommodating cavity. This allows the moving iron core component to be subjected to the damping force generated by the fluid flowing through the flow groove during the movement, thereby quickly converging the continuous vibration generated by the valve core when it is subjected to liquid flow impact and disturbance, and improving the stability of the solenoid valve operation.

[0033] Additional aspects and advantages of this application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of this application. Attached Figure Description

[0034] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, wherein:

[0035] Figure 1 This is a structural schematic diagram of a vehicle according to certain embodiments of this application;

[0036] Figure 2 yes Figure 1 The diagram shows a three-dimensional structural schematic of the core assembly of the solenoid valve in the vehicle.

[0037] Figure 3 yes Figure 2 A schematic diagram of the cross-sectional structure of the iron core assembly shown;

[0038] Figure 4 yes Figure 2 A three-dimensional structural diagram of the moving iron core component in the iron core assembly shown;

[0039] Figure 5 yes Figure 4 A schematic diagram of the planar structure of the moving iron core component shown;

[0040] Figure 6 yes Figure 2 A three-dimensional structural diagram of the fixed core in the core assembly shown;

[0041] Figure 7 This is a schematic diagram showing the displacement of the valve core of a solenoid valve in a vehicle under hydraulic pressure according to certain embodiments of this application.

[0042] Explanation of key component symbols:

[0043] 6000 vehicles; 5000 suspension system; 4000 body; 3000 wheels; 2100 shock absorbers; 2300 suspension;

[0044] 1000 solenoid valve;

[0045] 100 Core assembly, 101 Accommodating cavity, 103 First cavity, 105 Second cavity, 107 Gap;

[0046] 10 Fixed iron core, 11 Guide hole, 13 Flow hole;

[0047] 30 Body, 31 Valve body, 33 Magnetic shielding ring, 35 Guide groove;

[0048] 50 Moving iron core component, X-axis; Y-radial; 51 Moving iron core, 511 Outer peripheral wall, 513 Connecting groove, 5131 First groove, 5133 Second groove, 515 First end, 517 Second end, 518 First clearance groove, 519 Second clearance groove, 53 Valve core;

[0049] 60 First guide sleeve; 70 Second guide sleeve; 80 First elastic element; 90 Second elastic element. Detailed Implementation

[0050] To make the above-mentioned objectives, features, and advantages of this application more apparent and understandable, the specific embodiments of this application are described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of this application. However, this application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of this application. Therefore, this application is not limited to the specific embodiments disclosed below.

[0051] In the description of this application, it should be understood that the terms "center", "length", "upper", "lower", "front", "rear", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0052] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0053] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "joining," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0054] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0055] Please see Figure 1 The vehicle 6000 in this embodiment includes a suspension system 5000. The vehicle 6000 includes, but is not limited to, passenger vehicles such as pure electric vehicles and hybrid vehicles, or large engineering vehicles operating under relatively mild conditions.

[0056] Furthermore, in some embodiments, the vehicle 6000 also includes a body 4000 and wheels 3000. The wheels 3000 are disposed on the body 4000 and are movable relative to the body 4000 to achieve movement of the vehicle 6000 (e.g., forward, reverse, or steering). One end of the suspension system 5000 is connected to the body 4000, and the other end is connected to the wheels 3000. The suspension system 5000 can adjust the relative distance between the body 4000 and the wheels 3000 to improve the ride comfort of the vehicle 6000.

[0057] Since the vehicle 6000 in this embodiment includes a suspension system 5000, it is understood that the vehicle 6000 has at least the same beneficial effects as the suspension system 5000. Therefore, for the beneficial effects of the vehicle 6000, please refer to the beneficial effects of the suspension system 5000 described below.

[0058] Please continue reading. Figure 1 The suspension system 5000 of this application includes a shock absorber 2100.

[0059] The shock absorber 2100 is a device in the suspension system 5000 that absorbs vibration energy and accelerates vibration attenuation. In some embodiments of this application, the suspension system 5000 further includes a suspension 2300, which connects the vehicle body 4000 and the wheels 3000, and the shock absorber 2100 is connected to the suspension 2300. When the wheel 3000 is subjected to an impact force, the impact force can be transmitted through the suspension 2300. In this case, the shock absorber 2100 can generate a damping force, which can offset or weaken the impact force, thereby reducing the impact force transmitted to the vehicle body 4000, and thus improving the driving stability and ride comfort of the vehicle 6000.

[0060] Specifically, in some embodiments, the shock absorber 2100 includes a cylinder and a piston disposed within the cylinder. The cylinder contains a fluid (e.g., oil), and the piston divides the internal cavity of the cylinder into a compression chamber and a recovery chamber. The piston is connected to the suspension 2300 via a piston rod. When the piston rod moves the piston up and down, the fluid flows between the compression chamber and the recovery chamber, generating a damping force.

[0061] For example, when the vehicle 6000 is in motion, if the wheel 3000 is impacted by the road surface, the wheel 3000 bounces upward. At this time, the suspension 2300 can move upward along with the wheel 3000. In this case, the piston rod of the shock absorber 2100 moves downward and drives the piston downward. The fluid in the compression chamber flows to the recovery chamber through the orifice valve system (such as the solenoid valve 1000 mentioned below) and through the piston valve, thereby generating a damping force to buffer the vibration of the suspension 2300 and improve the driving performance of the vehicle 6000. When the wheel 3000 bounces downward, the suspension 2300 can move downward along with the wheel 3000. In this case, the piston rod of the shock absorber 2100 moves upward and drives the piston upward. The fluid in the recovery chamber can flow to the compression chamber through the piston valve, thereby generating a damping force to buffer the vibration of the suspension 2300 and improve the driving performance of the vehicle 6000.

[0062] Since the suspension system 5000 in this embodiment includes a shock absorber 2100, it is understood that the suspension system 5000 has at least the same beneficial effects as the shock absorber 2100. Therefore, for the beneficial effects of the suspension system 5000, please refer to the beneficial effects of the shock absorber 2100 described below.

[0063] Please continue reading. Figure 1 The shock absorber 2100 of this application embodiment includes a solenoid valve 1000. The solenoid valve 1000 can control the flow rate of fluid according to the road surface conditions or the mechanical motion state, thereby adjusting the damping force of the shock absorber 2100.

[0064] Specifically, in some embodiments, the vehicle 6000 may also include a detection device that can detect information such as road surface conditions, the speed of the vehicle 6000, and the acceleration of the vehicle 6000, and adjust the magnitude of the electromagnetic force according to the information to control the flow rate of the fluid, thereby achieving adjustable damping force and effectively meeting the driving comfort requirements of the vehicle 6000.

[0065] Since the damper 2100 in this embodiment includes the solenoid valve 1000, it is understood that the damper 2100 has at least the same beneficial effects as the solenoid valve 1000. Therefore, for the beneficial effects of the damper 2100, please refer to the beneficial effects of the solenoid valve 1000 described below.

[0066] Please see Figure 1 and Figure 2 The solenoid valve 1000 of this application embodiment includes an iron core assembly 100. Since the solenoid valve 1000 of this embodiment includes an iron core assembly 100, it is understood that the solenoid valve 1000 includes at least the same beneficial effects as the iron core assembly 100. Therefore, for the beneficial effects of the solenoid valve 1000, please refer to the beneficial effects of the iron core assembly 100 described below.

[0067] Please see Figures 2 to 4 The core assembly 100 of this application includes a fixed core 10, a body 30, and a moving core component 50. The body 30 is connected to the fixed core 10 and together with the fixed core 10 forms a receiving cavity 101. The moving core component 50 includes a moving core 51 and a valve core 53 connected to the moving core 51. The moving core 51 is movably disposed in the receiving cavity 101. A connecting groove 513 is provided on the outer peripheral wall 511 of the moving core 51 for fluid flow. The connecting groove 513 includes a first groove 5131 and a second groove 5133 in the axial direction X of the moving core 51. The dimension of the first groove 5131 in the circumferential direction of the moving core 51 is larger than the dimension of the second groove 5133 in the circumferential direction.

[0068] Furthermore, please combine Figure 1In some embodiments, the solenoid valve 1000 may further include a coil wound around the body 30 and corresponding at least to the moving iron core 51. The coil is a structure made of insulated wire; the wire may be made of at least one of copper, aluminum, and silver. Specifically, when the coil is energized, it generates a magnetic field, which acts on the moving iron core 51, causing it to become magnetic and attract the fixed iron core 10. This allows the moving iron core 51 to move the valve core 53 within the receiving cavity 101, thereby regulating the fluid flow rate and consequently adjusting the damping force of the shock absorber 2100. In other words, the solenoid valve 1000 can control the fluid flow rate through electromagnetic induction. This electromagnetic induction method is accurate and rapid, ensuring the regulating performance of the solenoid valve 1000.

[0069] It is understood that the fixed iron core 10 is a structure in the iron core assembly 100 used to mount the main body 30 and other devices. The fixed iron core 10 can be made of magnetic materials such as electromagnetic pure iron, silicon steel sheets, electrical soft iron, and soft magnetic stainless steel. For example, the fixed iron core 10 can be formed by stacking multiple silicon steel sheets; or, the fixed iron core 10 can be composed of a single iron core.

[0070] The body 30 is a structure in the core assembly 100 used to load and protect the moving core component 50, and can define the direction of movement of the moving core component 50. Parts of the body 30 may be made of magnetic material. The cross-sectional shape of the accommodating cavity 101 includes, but is not limited to, circles, squares, polygons, etc. In some embodiments, the body 30 and the fixed core 10 may be joined together by a detachable connection, including but not limited to snap-fit ​​or bolted connections. In other embodiments, the body 30 and the fixed core 10 may be joined together by a non-detachable connection, including but not limited to bonding or welding.

[0071] Furthermore, in some embodiments, a sealing element may be provided between the body 30 and the fixed iron core 10. The sealing element is used to seal the gap between the body 30 and the fixed iron core 10 to prevent the fluid in the accommodating cavity 101 from leaking through the gap between the body 30 and the fixed iron core 10, thereby ensuring the stability and reliability of the operation of the solenoid valve 1000.

[0072] The moving iron core component 50 is a structure in the iron core assembly 100 that can move relative to the body 30 to achieve fluid flow regulation. The moving iron core 51 can be made of magnetic materials such as electromagnetic pure iron, silicon steel sheet, electrical soft iron, and soft magnetic stainless steel. In some embodiments of this application, the valve core 53 is connected to the moving iron core 51, and part of the valve core 53 passes through the fixed iron core 10 and extends out of the receiving cavity 101. When the coil is energized, the moving iron core 51 can generate magnetism and attract each other to the fixed iron core 10. Thus, the moving iron core 51 can drive the valve core 53 to move together relative to the body 30, so that the valve core 53 can cooperate with external structures (such as the pilot valve of the shock absorber 2100) to achieve fluid flow regulation, thereby regulating the damping force of the shock absorber 2100.

[0073] It should be noted that the outer contour shape of the cross-section of the moving iron core 51 is approximately the same as the cross-sectional shape of the receiving cavity 101, which ensures the stability of the moving iron core 51 in the receiving cavity 101. For example, the cross-sectional shape of the receiving cavity 101 is circular, and the outer contour shape of the cross-section of the moving iron core 51 is also circular.

[0074] In some embodiments of this application, the moving iron core 51 is used to divide the accommodating cavity 101 into a first cavity 103 and a second cavity 105, and the connecting groove 513 is used to connect the first cavity 103 and the second cavity 105.

[0075] When the valve core 53 vibrates due to the impact and disturbance of the liquid flow, the fluid can flow through the connecting groove 513 between the first chamber 103 and the second chamber 105, generating a throttling pressure difference that acts on the moving iron core 51 and the valve core 53. This causes the moving iron core 51 and the valve core 53 to be subjected to damping force during their movement, and the continuous large-amplitude vibrations converge quickly, thereby improving the stability of the solenoid valve 1000 and reducing the noise generated by the continuous vibration of the valve core 53.

[0076] In some embodiments, the moving iron core 51 and the valve core 53 are an integral structure, that is, the moving iron core 51 and the valve core 53 are a single structure manufactured using an integral molding process. This ensures the bonding strength between the moving iron core 51 and the valve core 53, preventing separation of the moving iron core 51 and the valve core 53 during the movement of the moving iron core component 50, thereby improving the stability and reliability of the iron core assembly 100. In other embodiments, the moving iron core 51 and the valve core 53 are separate structures, that is, the moving iron core 51 and the valve core 53 are two different structures. The moving iron core 51 and the valve core 53 can be combined using either a non-removable connection method or a detachable connection method. Non-removable connection methods include bonding, welding, or riveting; detachable connection methods include, but are not limited to, snap-fit ​​or threaded connections.

[0077] In the iron core assembly 100 of this application embodiment, a connecting groove 513 is provided on the outer peripheral wall 511 of the moving iron core 51. The connecting groove 513 is used to connect the first cavity 103 and the second cavity 105. Thus, when the valve core 53 and the moving iron core 51 move in the accommodating cavity 101, the fluid can flow between the first cavity 103 and the second cavity 105 through the connecting groove 513. This allows the moving iron core component 50 to be subjected to damping force during movement, thereby quickly converging the continuous vibration generated when the valve core 53 is subjected to liquid flow impact and disturbance, and improving the stability of the solenoid valve 1000 operation.

[0078] The core assembly 100 will be further described below with reference to the accompanying drawings.

[0079] Please see Figures 2 to 4 In some embodiments, the outer peripheral wall 511 of the moving iron core 51 has a gap 107 between it and the body 30, and the gap 107 is used for fluid flow.

[0080] In this embodiment, when the valve core 53 vibrates due to fluid flow impact and disturbance, the fluid can flow between the first chamber 103 and the second chamber 105 through the gap 107 and the connecting groove 513, generating a throttling pressure difference that acts on the moving iron core 51 and the valve core 53. This causes the moving iron core 51 and the valve core 53 to be subjected to two forms of damping force during their movement, resulting in rapid convergence of continuous large-amplitude vibrations. This improves the stability of the solenoid valve 1000 and reduces the noise generated by the continuous vibration of the valve core 53. In addition, in this embodiment, the connecting groove 513 also ensures smoother movement of the moving iron core component 50, avoids large overshoot, and improves the stability of the valve core 53.

[0081] Specifically, since the circumferential dimension of the first groove 5131 in the moving iron core 51 is larger than that of the second groove 5133 in the circumferential direction, the throttling type of the connecting groove 513 is short-hole throttling, and the throttling effect of the connecting groove 513 is mainly caused by local pressure loss; while the throttling type of the gap 107 is slot throttling, and the throttling effect of the gap 107 is mainly caused by friction pressure loss. Thus, when the fluid flows between the first cavity 103 and the second cavity 105 through the gap 107 and the connecting groove 513, the moving iron core 51 and the valve core 53 can be subjected to two forms of damping force.

[0082] Please see Figure 3 and Figure 4 In some embodiments, the connecting slots 513 include at least two, and at least two connecting slots 513 are spaced apart on the outer peripheral wall 511 of the moving iron core 51 in the circumferential direction. For example, when there are multiple connecting slots 513, the multiple connecting slots 513 are spaced apart on the moving iron core 51 in the circumferential direction, and the distance between two adjacent connecting slots 513 may be the same or different.

[0083] Furthermore, in some embodiments of this application, at least two connecting slots 513 are evenly distributed on the outer peripheral wall 511 of the moving iron core 51 in the circumferential direction. For example, when there are two connecting slots 513, the two connecting slots 513 are symmetrically arranged on the moving iron core 51.

[0084] In this design, at least two connecting grooves 513 are evenly distributed on the outer peripheral wall 511 of the moving iron core 51 in the circumferential direction. This ensures that the moving iron core 51 is subjected to a more uniform damping force, preventing the moving iron core 51 from deviating relative to the body 30 and improving the stability and reliability of the solenoid valve 1000. It is understood that in some embodiments, at least two connecting grooves 513 have the same shape and size.

[0085] Please combine Figure 5 In some embodiments, the first groove 5131 has a circumferential dimension of w1, and the second groove 5133 has a circumferential dimension of w2, wherein the value of w1 / w2 is [1.5, 2.5]. Specifically, in some embodiments, the value of w1 / w2 can be any one of 1.5, 1.6, 1.7, 1.8, 1.9, 2.0, 2.1, 2.2, 2.3, 2.4, and 2.5, or any value between any two of these values.

[0086] The value of w1 / w2 is [1.5, 2.5]. This allows the connecting groove 513 to basically meet the short-orifice throttling type. The throttling effect of the connecting groove 513 is mainly caused by local pressure loss and is less affected by temperature. It can effectively adapt to different working conditions of the solenoid valve 1000 and improve the stability of the solenoid valve 1000. On the other hand, it can prevent the size of the connecting groove 513 from being too large, which would result in the volume of the moving iron core 51 being too small, thus ensuring the magnitude of the electromagnetic force.

[0087] For example, along the axial direction X of the moving iron core 51, the circumferential dimension of the first groove 5131 remains unchanged, the circumferential dimension of the second groove 5133 remains unchanged, and the first groove 5131 and the second groove 5133 are smoothly connected. At this time, the circumferential dimension w1 of the first groove 5131 can be the maximum circumferential dimension of the connecting groove 513, and the circumferential dimension w2 of the second groove 5133 can be the minimum circumferential dimension of the connecting groove 513.

[0088] Furthermore, in some embodiments, the equivalent diameter of the second groove 5133 is d, and the length of the second groove 5133 in the axial direction X is L, where the value of L / d is [0.5, 4.0]. It should be noted that the equivalent diameter refers to the diameter of an object whose shape and size are similar to a sphere of the same volume. For example, when the cross-sectional shape of the second groove 5133 is approximately rectangular, the formula for the equivalent diameter d of the second groove 5133 can be: Where a is the length of the cross-section of the second groove 5133; b is the width of the cross-section of the second groove 5133.

[0089] The value of L / d is [0.5, 4.0], which allows the throttling effect of the connecting groove 513 to be mainly caused by local pressure loss, satisfying the short-orifice throttling type. Specifically, in some embodiments, the value of L / d can be any one of 0.5, 1.0, 1.5, 2.0, 2.5, 3.0, 3.5 and 4.0 or any value between any two of these.

[0090] Please see Figure 3 and Figure 4 In some embodiments, when the moving iron core component 50 moves relative to the body 30, the flow rate of the fluid flowing through the connecting groove 513 is Q1, the flow rate of the fluid flowing through the gap 107 is Q2, and the pressure difference between the first cavity 103 and the second cavity 105 is ΔP. ​​The relationships between Q1 and ΔP, and between Q2 and ΔP, satisfy the following:

[0091] ΔP∝Q1 2 ;

[0092] ΔP∝Q2.

[0093] Furthermore, in some embodiments, when the fluid flows through the connecting groove 513, the damping force on the valve core 53 is F1, and when the fluid flows through the gap 107, the damping force on the valve core 53 is F2. The moving speed of the valve core 53 is v, and the relationships between F1 and v, and between F2 and v, satisfy:

[0094] F1 = cv 2 ;

[0095] F2 = cv;

[0096] Where c is the damping coefficient.

[0097] Specifically, in some embodiments, since the formula for calculating flow rate Q satisfies Q=Av and the formula for calculating pressure difference ΔP satisfies F / A, the relationships between F1 and v and between F2 and v can be derived by combining the above relationships between Q1 and ΔP and Q2 and ΔP. That is, when the moving iron core component 50 moves relative to the body 30, the fluid flows between the first cavity 103 and the second cavity 105 through the gap 107 and the connecting groove 513, and a throttling effect is generated, so the moving iron core 51 is subjected to a damping force related to velocity.

[0098] In some embodiments, the gap 107 is connected in parallel with the connecting groove 513. When the moving iron core component 50 moves relative to the body 30 and fluid flows through the connecting groove 513 and the gap 107, the damping force on the valve core 53 is F. c The moving speed of valve core 53 is v, and the flow rate of fluid flowing through gap 107 and connecting groove 513 is Q. t The pressure difference between the first chamber 103 and the second chamber 105 is ΔP, F c The relationship with v satisfies:

[0099]

[0100] Where c2 and c3 are damping coefficients.

[0101] Specifically, in some embodiments, since the gap 107 is connected in parallel with the connecting groove 513, therefore, Q t =Q1+Q2, therefore, combining the above relationships between Q1 and △P, Q2 and △P, F1 and v, and F2 and v, we can derive F c The relationship with v. That is, the moving iron core component 50 can be subjected to two forms of damping force simultaneously during its movement. The two forms of damping force are c2v (hereinafter referred to as the first damping force) and (Hereinafter referred to as the second damping force). Specifically, when the valve core 53 moves at a relatively low speed, for example, less than 1 m / s, the second damping force plays a major role, and the movement of the moving iron core component 50 is subjected to a large second damping force, resulting in rapid absorption and reduction of vibration energy. When the valve core 53 moves at a relatively high speed, for example, greater than 1 m / s, the first damping force plays a major role, and the movement of the moving iron core component 50 is subjected to a large first damping force, resulting in rapid absorption and reduction of vibration energy.

[0102] More specifically, in some embodiments, the relationships between Q1 and ΔP, and between Q2 and ΔP, satisfy:

[0103]

[0104]

[0105] Among them, c v ρ is the flow coefficient; A is the cross-sectional area of ​​the moving iron core 51; ρ is the density of the fluid; d is the maximum dimension of the cross-section of the moving iron core 51; δ is the dimension of the gap 107 in the radial Y direction of the moving iron core 51; s is the length of the moving iron core 51 in the axial X direction; v is the moving speed of the valve core 53.

[0106] Flow coefficient c v Calculated using the following formula:

[0107]

[0108] Among them, the larger the value of w1 / w2, the greater the flow coefficient c. v The smaller the value, the better the flow-throttling effect. As mentioned above, the value of w1 / w2 is [1.5, 2.5], therefore, the flow coefficient c... v The value is [0.4, 0.65]. This can prevent the size of the connecting groove 513 from being too large, thus ensuring the magnitude of the electromagnetic force; on the other hand, it can make the connecting groove 513 meet the short hole throttling type and the gap 107 meet the slot throttling type, thus ensuring the vibration reduction effect.

[0109] As can be seen from the above, when the gap 107 and the connecting groove 513 are connected in parallel, Q t =Q1 + Q2. Therefore, Q t The relationship with △P satisfies: By solving, we can obtain the damping force F on the valve core 53 when the gap 107 and the connecting groove 513 are connected in parallel. c The relationship between the moving speed v of valve core 53 and the valve core 53 is satisfied.

[0110] In other embodiments, the gap 107 is connected in series with the connecting groove 513; when the moving iron core component 50 moves relative to the body 30 and fluid flows through the connecting groove 513 and the gap 107, the damping force on the valve core 53 is F. c The moving speed of valve core 53 is v, F c The relationship with v satisfies:

[0111] F c =c1v 2 +c2v;

[0112] Where c1 and c2 are damping coefficients.

[0113] Specifically, in some embodiments, F can be derived by combining the above-mentioned relationships between Q1 and ΔP, Q2 and ΔP, F1 and v, and F2 and v. cThe relationship with v. That is, the moving iron core component 50 can be subjected to two forms of damping force simultaneously during the movement, namely c2v (the first damping force) and c1v. 2 (Hereinafter referred to as the third damping force).

[0114] Please see Figure 7 , Figure 7 This is a schematic diagram showing the displacement of valve core 53 under hydraulic pressure. Figure 7 In Scheme 1, there is a gap 107 between the outer peripheral wall 511 of the moving iron core 51 and the body 30, but the outer peripheral wall 511 of the moving iron core 51 is not provided with a connecting groove 513. Figure 7 In Scheme 2, there is a gap 107 between the outer peripheral wall 511 of the moving iron core 51 and the body 30, and a connecting groove 513 is provided on the outer peripheral wall 511 of the moving iron core 51, and the gap 107 and the connecting groove 513 are connected in series. Figure 7 In Scheme 3, there is a gap 107 between the outer peripheral wall 511 of the moving iron core 51 and the body 30, and a connecting groove 513 is provided on the outer peripheral wall 511 of the moving iron core 51, and the gap 107 and the connecting groove 513 are connected in parallel.

[0115] As can be seen from the above, the damping orifice in Scheme 1 is a slot throttling type, and the throttling effect of the slot is mainly caused by the pressure loss along the friction. In this case, the damping force experienced by the moving iron core component 50 when it moves is the first damping force. In Scheme 2, the damping orifice is a combination of a slot throttling type and a short-hole throttling type connected in series. In this case, the damping force experienced by the moving iron core component 50 when it moves is the first damping force and the third damping force. In Scheme 3, the damping orifice is a combination of a slot throttling type and a short-hole throttling type connected in parallel. In this case, the damping force experienced by the moving iron core component 50 when it moves is the first damping force and the second damping force.

[0116] Specifically, by Figure 7 It can be seen that the moving iron core component 50 in Schemes 1 and 2 exhibits continuous vibration and significant motion overshoot; the moving iron core component 50 in Scheme 3 shows no continuous vibration and has less motion overshoot, resulting in the best vibration reduction effect. This indicates that the damping orifice arrangement provided in this embodiment of the application provides better stability for the valve core 53. It is understood that since the damping force experienced by the moving iron core component 50 during movement in Scheme 3 includes a second damping force, when the valve core 53's moving speed is low, for example, less than 1 m / s, the effect of the second damping force is greater than that of the third damping force. Therefore, the vibration reduction effect of Scheme 3 is superior to that of Scheme 2.

[0117] Please see Figure 3 and Figure 4In some embodiments, the main body 30 includes a valve body 31 and a magnetic shielding ring 33. The valve body 31 covers the moving iron core 51, and the magnetic shielding ring 33 surrounds the moving iron core 51 and connects between the valve body 31 and the fixed iron core 10. The valve body 31, the magnetic shielding ring 33, and the fixed iron core 10 together form a receiving cavity 101. The magnetic shielding ring 33 prevents the magnetic field generated when the coil is energized from affecting the fixed iron core 10, so that the magnetic field generated by the coil mainly acts on the moving iron core 51, thereby increasing the electromagnetic force generated between the moving iron core 51 and the fixed iron core 10.

[0118] In some embodiments, the valve body 31 and the magnetic shielding ring 33 can be an integral structure, that is, the valve body 31 and the magnetic shielding ring 33 can be an integral structure manufactured by an integral molding process. This can improve the bonding strength between the valve body 31 and the magnetic shielding ring 33, prevent the valve body 31 and the magnetic shielding ring 33 from separating during the operation of the solenoid valve 1000, thereby ensuring the stability and reliability of the solenoid valve 1000. In other embodiments, the valve body 31 and the magnetic shielding ring 33 can be separate structures, that is, the valve body 31 and the magnetic shielding ring 33 are two different structures. The valve body 31 and the magnetic shielding ring 33 can be joined together by means of interference fit, welding, bonding, snap-fit, or threaded connection.

[0119] In some embodiments of this application, when the valve body 31 and the magnetic isolation ring 33 are connected, the inner side of the valve body 31 (the side of the valve body 31 facing the accommodating cavity 101) and the inner side of the magnetic isolation ring 33 (the side of the magnetic isolation ring 33 facing the accommodating cavity 101), as well as the outer side of the valve body 31 and the outer side of the magnetic isolation ring 33, are flush. This prevents the magnetic isolation ring 33 from interfering with the movement of the moving iron core component 50, thereby ensuring the normal operation of the solenoid valve 1000; it also improves the visual effect of the iron core assembly 100. It is understood that in some embodiments, the magnetic isolation ring 33 and the fixed iron core 10 can be connected together by interference fit, welding, bonding, snap-fit, or threaded connection.

[0120] Please continue reading. Figure 3 and Figure 4 In some embodiments, the main body 30 has a guide groove 35 on the inner wall of the moving iron core 51 along the axial direction X; the iron core assembly 100 also includes a first guide sleeve 60, which is disposed in the guide groove 35, and the valve core 53 is movably fitted into the first guide sleeve 60. The fixed iron core 10 has a guide hole 11. The iron core assembly 100 also includes a second guide sleeve 70, which is disposed in the guide hole 11, and the valve core 53 is movably fitted into the second guide sleeve 70.

[0121] The valve core 53 is movably inserted into the first guide sleeve 60 and the second guide sleeve 70. The arrangement of the first guide sleeve 60 and the second guide sleeve 70 provides a guiding and constraining effect, preventing the valve core 53 from deflecting during movement relative to the body 30, thereby improving the stability and reliability of the solenoid valve 1000. It is understood that the first guide sleeve 60 can be installed in the guide groove 35 with an interference fit, thus ensuring the stability of its installation; similarly, the second guide sleeve 70 can be installed in the guide hole 11 with an interference fit, thus ensuring the stability of its installation.

[0122] Please combine Figure 6 In some embodiments, the fixed iron core 10 is further provided with a flow hole 13 penetrating the fixed iron core 10. The flow hole 13 includes at least two holes, and the at least two flow holes 13 are evenly distributed on the fixed iron core 10. The arrangement of the flow hole 13 can ensure the fluid flow balance in the accommodating cavity 101, so that the moving iron core 51 can move normally without being affected by fluid pressure, thereby ensuring the stability and reliability of the iron core assembly 100.

[0123] Please see Figure 3 and Figure 4 In some embodiments, the moving iron core 51 includes a first end 515 and a second end 517 opposite each other in the axial direction X. The iron core assembly 100 also includes a first elastic member 80 and a second elastic member 90. The first elastic member 80 is disposed between the first end 515 of the moving iron core 51 and the body 30. The second elastic member 90 is disposed between the second end 517 of the moving iron core 51 and the body 30; wherein, the first elastic member 80 and the second elastic member 90 together apply a spring force to the moving iron core 51 to maintain the moving iron core 51 and the body 30 at a distance between their opposite sides in the axial direction X. Thus, the arrangement of the first elastic member 80 and the second elastic member 90 can reduce the possibility of collision damage between the moving iron core 51 and the body 30 or the fixed iron core 10, thereby extending the service life of the iron core assembly 100 and ensuring the normal operation of the solenoid valve 1000.

[0124] Furthermore, in some embodiments, the moving iron core 51 is provided with a first clearance groove 518, in which the first end 515 of the automatic iron core 51 is recessed toward the second end 517 of the moving iron core 51, and a portion of the first elastic member 80 is accommodated in the first clearance groove 518. The first clearance groove 518 serves two purposes: firstly, it limits the movement of the first elastic member 80, ensuring that the first elastic member 80 can extend and retract along the axial direction X; secondly, it reduces the space occupied by the first elastic member 80, which is beneficial for miniaturizing the iron core assembly 100. Similarly, the moving iron core 51 is also provided with a second clearance groove 519, in which the second end 517 of the automatic iron core 51 is recessed toward the first end 515 of the moving iron core 51, and a portion of the second elastic member 90 is accommodated in the second clearance groove 519. The second clearance groove 519 can limit the second elastic member 90 to ensure that the second elastic member 90 can extend and retract along the axial direction X; on the other hand, it can reduce the space occupied by the second elastic member 90, which is conducive to the miniaturization of the iron core assembly 100.

[0125] The technical features of the embodiments described above can be combined arbitrarily. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as the combination of these technical features does not contradict each other, it should be considered within the scope of this specification. Furthermore, other implementation methods can be derived from the above embodiments, allowing for structural and logical substitutions and changes without departing from the scope of this disclosure.

[0126] The embodiments described above are merely illustrative of several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of this application. Therefore, the protection scope of this patent application should be determined by the appended claims.

Claims

1. A core assembly (100), characterized in that, include: Fixed iron core (10); Body (30), the body (30) being connected to the fixed iron core (10) and together with the fixed iron core (10) forming a receiving cavity (101); and A moving iron core component (50) includes a moving iron core (51) and a valve core (53) connected to the moving iron core (51). The moving iron core (51) is movably disposed in the accommodating cavity (101). A connecting groove (513) is provided on the outer peripheral wall (511) of the moving iron core (51). The connecting groove (513) is used for fluid flow. The connecting groove (513) includes a first groove (5131) and a second groove (5133) that are connected in the axial direction of the moving iron core (51). The first groove (5131) has a larger circumferential dimension in the moving iron core (51) than the second groove (5133) has a larger circumferential dimension in the moving iron core (51).

2. The core assembly (100) according to claim 1, characterized in that, The connecting groove (513) includes at least two, and the at least two connecting grooves (513) are distributed at intervals on the outer peripheral wall (511) of the moving iron core (51) in the circumferential direction of the moving iron core (51).

3. The core assembly (100) according to claim 1, characterized in that, The first groove (5131) has a dimension of w1 in the circumferential direction, and the second groove (5133) has a dimension of w2 in the circumferential direction, wherein the value of w1 / w2 is [1.5, 2.5].

4. The core assembly (100) according to claim 3, characterized in that, The equivalent diameter of the second groove (5133) is d, and the length of the second groove (5133) in the axial direction is L, wherein the value of L / d is [0.5, 4.0].

5. The core assembly (100) according to claim 1, characterized in that, The outer peripheral wall (511) of the moving iron core (51) has a gap (107) with the body (30), the gap (107) is used for fluid flow; the moving iron core (51) is used to divide the accommodating cavity (101) into a first cavity (103) and a second cavity (105), the gap (107) and the connecting groove (513) are both used to connect the first cavity (103) and the second cavity (105).

6. The core assembly (100) according to claim 5, characterized in that, When the moving iron core component (50) moves relative to the body (30), the flow rate of the fluid flowing through the connecting groove (513) is Q1, the flow rate of the fluid flowing through the gap (107) is Q2, the pressure difference between the first cavity (103) and the second cavity (105) is ΔP, and the relationships between Q1 and ΔP, and between Q2 and ΔP satisfy: ΔP∝Q1 2 ;or, ΔP∝Q²; or, Among them, c v ρ is the flow coefficient; A is the cross-sectional area of ​​the moving iron core (51); ρ is the density of the fluid; d is the maximum dimension of the cross-section of the moving iron core (51); δ is the radial dimension of the gap (107) in the moving iron core (51); s is the axial length of the moving iron core (51); v is the moving speed of the valve core (53).

7. The core assembly (100) according to claim 6, characterized in that, The first groove (5131) has a circumferential dimension of w1, the second groove (5133) has a circumferential dimension of w2, and the flow coefficient c v Calculated using the following formula: Among them, c v The value is [0.4, 0.65].

8. The core assembly (100) according to claim 6, characterized in that, When the fluid flows through the connecting groove (513), the damping force on the valve core (53) is F1, and when the fluid flows through the gap (107), the damping force on the valve core (53) is F2. The moving speed of the valve core (53) is v. The relationships between F1 and v, and between F2 and v, satisfy: F1=cv 2 ; F2 = cv; Where c is the damping coefficient.

9. The core assembly (100) according to claim 8, characterized in that, The gap (107) is connected in parallel with the connecting groove (513); when the moving iron core component (50) moves relative to the body (30) and fluid flows through the connecting groove (513) and the gap (107), the damping force on the valve core (53) is F. c The moving speed of the valve core (53) is v, and the flow rate of the fluid flowing through the gap (107) and the connecting groove (513) is Q. t The pressure difference between the first chamber (103) and the second chamber (105) is ΔP, F c With v, and Q t The relationship with △P satisfies: Where c2 and c3 are damping coefficients.

10. The core assembly (100) according to any one of claims 1-9, characterized in that, The main body (30) includes a valve body (31) and a magnetic shielding ring (33). The valve body (31) covers the moving iron core (51). The magnetic shielding ring (33) surrounds the moving iron core (51) and is connected between the valve body (31) and the fixed iron core (10). The valve body (31), the magnetic shielding ring (33) and the fixed iron core (10) together form the receiving cavity (101).

11. The core assembly (100) according to any one of claims 1-9, characterized in that, The body (30) has a guide groove (35) on the inner wall of the moving iron core (51) along the axial direction; the iron core assembly (100) also includes: A first guide sleeve (60) is disposed in the guide groove (35), and the valve core (53) is movably fitted to the first guide sleeve (60).

12. The core assembly (100) according to any one of claims 1-9, characterized in that, The fixed iron core (10) is provided with a guide hole (11); the iron core assembly (100) further includes: The second guide sleeve (70) is disposed in the guide hole (11), and the valve core (53) is movably fitted to the second guide sleeve (70).

13. The core assembly (100) according to any one of claims 1-9, characterized in that, The moving iron core (51) includes, in the axial direction, a first end (515) and a second end (517) opposite each other; the iron core assembly (100) further includes: A first elastic element (80) is disposed between the first end (515) of the moving iron core (51) and the body (30); and The second elastic element (90) is disposed between the second end (517) of the moving iron core (51) and the body (30); wherein the first elastic element (80) and the second elastic element (90) are used together to apply elastic force to the moving iron core (51) to maintain the moving iron core (51) and the body (30) on opposite sides in the axial direction.

14. A solenoid valve (1000), characterized in that, include: The core assembly (100) according to any one of claims 1-13.

15. A vibration damper (2100), characterized in that, include: The solenoid valve (1000) according to claim 14.

16. A suspension system (5000), characterized in that, include: The vibration damper (2100) according to claim 15.

17. A vehicle (6000), characterized in that, include: The suspension system (5000) as claimed in claim 16.

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