Spring assembly and overflow valve

Abstract

The utility model belongs to the technical field of hydraulic valves, and discloses a spring assembly and an overflow valve. The spring assembly comprises a first spring and a second spring, the second spring is located on the periphery of the first spring, and the first spring and the second spring are integrally formed. The spring coil diameter of the first spring is different from that of the second spring, so that the frequencies of the first spring and the second spring are different. When the pressure of the valve body applying the spring assembly continuously changes, the spring assembly can drive the valve element assembly to continuously move up and down, and when the excitation frequency of oil pressure is the same as the frequency of one of the first spring and the second spring, the other one of the first spring and the second spring can effectively restrain vibration of the first spring and the second spring, the resonance phenomenon is reduced, and the self-stabilization state is achieved; therefore, the valve element assembly is kept stable, vibration and noise are reduced, the service life of the valve body is prolonged, and the reliability of the valve body is improved. The spring assembly is integrally formed, the manufacturing process can be simplified, the manufacturing cost is reduced, and the assembling time is shortened.

Description

Technical Field

[0001] This utility model relates to the field of hydraulic valve technology, and in particular to a spring assembly and a relief valve. Background Technology

[0002] Relief valves are commonly used in hydraulic equipment, primarily serving functions such as pressure stabilization, flow regulation, system unloading, and safety protection. When pressure fluctuates, the adjusting spring causes the valve core to move up and down continuously. When the excitation frequency of the oil pressure is close to the frequency of the valve core and the adjusting spring, resonance occurs, causing the valve core to continuously impact the valve port, generating vibration and noise. Furthermore, frequent opening and closing subject the valve core and seat to high-frequency rigid impacts, leading to significant wear on both and reducing the overall reliability and lifespan of the relief valve.

[0003] Therefore, there is a need to provide a spring assembly and an overflow valve to solve the above problems. Utility Model Content

[0004] The purpose of this invention is to provide a spring assembly and an overflow valve. This spring assembly can reduce the occurrence of resonance, extend the service life of the valve body, and improve the reliability of the valve body.

[0005] To achieve this objective, the present invention adopts the following technical solution:

[0006] A spring assembly, comprising:

[0007] First spring;

[0008] The second spring is located on the outer periphery of the first spring, and the first spring and the second spring are integrally formed.

[0009] Preferably, the first spring and the second spring have opposite directions of rotation.

[0010] Preferably, at least three turns at both ends of the second spring are pressed together to form a support ring, and both ends of the support ring are planar.

[0011] An overflow valve, the overflow valve comprising:

[0012] The valve seat has an oil inlet hole, an oil return hole, and an oil passage, wherein the oil inlet hole and the oil return hole can be connected through the oil passage;

[0013] A valve core assembly is disposed within the valve seat, and the valve core assembly is axially slidable to close or open the oil passage;

[0014] An end cap is disposed at the end of the valve seat away from the oil inlet hole;

[0015] As described above, the two ends of the spring assembly abut against the valve core assembly and the end cap, respectively.

[0016] Preferably, the valve core assembly includes:

[0017] The valve core body and the spring seat are provided, wherein the spring seat is located at the end of the valve core body away from the oil passage, and one end of the spring assembly is connected to or abuts against the spring seat.

[0018] Preferably, there is an oil passage gap between the valve core body and the valve seat, the oil passage gap is connected to the oil inlet hole, the valve core body includes a first part and a second part connected together, the first part extends into the oil passage, and the outer peripheral surface of the second part is a conical surface, the conical surface can abut against the valve seat to close the oil passage.

[0019] Preferably, the valve core body further includes a third part, which is disposed at the end of the first part away from the second part, and the third part is slidably guided and engaged in the oil passage of the valve seat.

[0020] Preferably, the end cap includes:

[0021] An adjusting rod is provided with an axially oriented receiving groove at one end, at least a portion of the spring assembly is located in the receiving groove, the adjusting rod is connected to the valve seat, and the adjusting rod is capable of axial movement.

[0022] Preferably, the end cap further includes:

[0023] An adjusting sleeve is connected to the valve seat and is used to limit the extreme positions of the valve seat's axial movement.

[0024] Preferably, the end cap further includes:

[0025] A locking nut is threaded onto the portion of the adjusting rod located outside the valve seat, and the locking nut is able to abut against the adjusting sleeve.

[0026] The beneficial effects of this utility model are:

[0027] The spring assembly includes a first spring and a second spring, with the second spring located on the outer periphery of the first spring, and the first and second springs are integrally formed. It is understood that because the coil diameters of the first and second springs are different, their frequencies are different. When the pressure on the valve body using this spring assembly fluctuates continuously, the spring assembly drives the valve core assembly to move up and down continuously. When the excitation frequency of the oil pressure matches the frequency of one of the first and second springs, the other can effectively suppress its vibration, reduce resonance, and achieve a self-stabilizing state. This keeps the valve core assembly stable, reduces vibration and noise, extends the valve body's service life, and improves the valve body's reliability.

[0028] This one-piece spring assembly simplifies the manufacturing process and reduces costs. It also simplifies and speeds up assembly, reducing assembly time and costs. Most importantly, compared to separate first and second springs, this one-piece spring assembly offers higher stiffness. This significantly improves space utilization within the valve body's effective assembly space, and the overall length of the spring assembly can be reduced according to stiffness requirements, further decreasing the overall valve body length and contributing to cost reduction.

[0029] This relief valve includes a valve seat, a valve core assembly, an end cap, and the aforementioned spring assembly. The valve seat has an oil inlet, an oil return, and an oil passage. The oil inlet and the oil return are connected through the oil passage. The valve core assembly is disposed within the valve seat and can slide axially to close or open the oil passage. The end cap is disposed at the end of the valve seat away from the oil inlet. The two ends of the spring assembly abut against the valve core assembly and the end cap, respectively.

[0030] When the pressure within the hydraulic system exceeds the preload of the spring assembly, hydraulic oil enters the valve seat through the inlet port, exerting pressure on the valve core assembly. This pressure is the hydraulic system pressure. Since the hydraulic system pressure exceeds the set pressure, which is also greater than the preload of the spring assembly, the valve core assembly moves to the left to open the oil passage. After flowing into the valve seat, the hydraulic oil returns to the oil tank through the return port, reducing the hydraulic system pressure. When the hydraulic system pressure drops below the preload of the spring assembly, the spring assembly resets, pushing the valve core assembly to the right to block the oil passage. Due to the continuous fluctuations in the hydraulic system pressure, the spring assembly drives the valve core assembly to move up and down continuously. When the excitation frequency of the oil pressure matches the frequency of one of the first and second springs, the other effectively suppresses its vibration, reduces resonance, and achieves a self-stabilizing state. This keeps the valve core assembly stable, reduces vibration and noise, extends the service life of the relief valve, and improves its reliability. Attached Figure Description

[0031] Figure 1This is a schematic diagram of the spring assembly provided by this utility model;

[0032] Figure 2 This is a cross-sectional schematic diagram of the overflow valve provided by this utility model;

[0033] Figure 3 This is a schematic diagram of the valve core body provided by this utility model.

[0034] In the picture:

[0035] 1. Spring assembly; 11. First spring; 12. Second spring; 121. Support ring;

[0036] 2. Valve seat; 21. Oil inlet; 22. Oil return hole; 23. Oil passage;

[0037] 3. Valve core assembly; 31. Valve core body; 311. First part; 312. Second part; 313. Third part; 314. Fourth part; 32. Spring seat;

[0038] 4. End cap; 41. Adjusting rod; 42. Adjusting sleeve; 43. Locking nut. Detailed Implementation

[0039] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present invention and not intended to limit it. Furthermore, it should be noted that, for ease of description, the accompanying drawings show only the parts relevant to the present invention, not the entire structure.

[0040] In the description of this utility model, unless otherwise explicitly specified and limited, the terms "connected," "linked," and "fixed" 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. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0041] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0042] In the description of this embodiment, the terms "upper," "lower," "right," etc., refer to the orientation or positional relationship shown in the accompanying drawings. They are used only for ease of description and simplification of operation, 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 utility model. In addition, the terms "first" and "second" are only used for distinction in description and have no special meaning.

[0043] Relief valves are commonly used in hydraulic equipment, primarily serving functions such as pressure stabilization, flow regulation, system unloading, and safety protection. When pressure fluctuates, the adjusting spring causes the valve core to move up and down continuously. When the excitation frequency of the oil pressure is close to the frequency of the valve core and the adjusting spring, resonance occurs, causing the valve core to continuously impact the valve port, generating vibration and noise. Furthermore, frequent opening and closing subject the valve core and seat to high-frequency rigid impacts, leading to significant wear on both and reducing the overall reliability and lifespan of the relief valve.

[0044] To solve the above problems, such as Figure 1 , Figure 2 As shown, this embodiment provides a spring assembly 1, which includes a first spring 11 and a second spring 12. The second spring 12 is located on the outer periphery of the first spring 11, and the first spring 11 and the second spring 12 are integrally formed. It is understood that because the spring coil diameters of the first spring 11 and the second spring 12 are different, their frequencies are different. When the pressure on the valve body using this spring assembly 1 continuously changes, the spring assembly 1 will drive the valve core assembly 3 to move up and down continuously. When the excitation frequency of the oil pressure is the same as the frequency of one of the first spring 11 and the second spring 12, the other can effectively suppress its vibration, reduce resonance, and achieve a self-stabilizing state. This keeps the valve core assembly 3 stable, reduces vibration and noise, extends the service life of the valve body, and improves the reliability of the valve body.

[0045] This one-piece spring assembly 1 simplifies the manufacturing process and reduces manufacturing costs; it also makes the assembly process simpler and faster, reducing assembly time and costs. Most importantly, compared to separating the first spring 11 and the second spring 12, this one-piece spring assembly 1 has higher stiffness, which greatly improves space utilization within the effective assembly space of the valve body. Furthermore, the overall length of the spring assembly 1 can be reduced according to stiffness requirements, further reducing the overall valve length and thus reducing costs.

[0046] Specifically, the first spring 11 and the second spring 12 have opposite directions of rotation. This allows for further differentiation of the frequencies of the first spring 11 and the second spring 12, enabling them to better suppress each other's vibrations. Furthermore, it simplifies the manufacturing process of this spring assembly 1. In this embodiment, the spring assembly 1 is formed by winding a single wire. First, the wire is wound to form the first spring 11, and then wound in the opposite direction to form the second spring 12.

[0047] It should be noted that this spring assembly 1 can be applied to any valve body with a spring or elastic element, including but not limited to its application in relief valves.

[0048] Specifically, if Figure 1 As shown, at least three turns at both ends of the second spring 12 are pressed together to form a support ring 121, and both ends of the support ring 121 are flat. The support ring 121 can improve the stability of this spring assembly 1, making the spring assembly 1 more stable when under force; setting the outer end of the support ring 121 as a flat surface helps to ensure the stability of the spring assembly 1 after it is assembled into the valve body, and it is not easy to skew or shift.

[0049] In specific implementation, after pressing together at least three coils at both ends of the second spring 12, the end of the support ring 121 can be made into a flat surface by grinding or flattening. It should be noted that the specific number of coils pressed together depends on actual needs, and this embodiment does not limit this. For example, in this embodiment, the support ring 121 is formed by pressing together three coils.

[0050] like Figure 2 As shown, this embodiment also provides an overflow valve, which includes a valve seat 2, the aforementioned valve core assembly 3, an end cap 4, and the aforementioned spring assembly 1. The valve seat 2 has an oil inlet hole 21, an oil return hole 22, and an oil passage 23. The oil inlet hole 21 and the oil return hole 22 can communicate through the oil passage 23. The valve core assembly 3 is disposed inside the valve seat 2, and the valve core assembly 3 can slide axially to close or open the oil passage 23. The end cap 4 is disposed at the end of the valve seat 2 away from the oil inlet hole 21. The two ends of the spring assembly 1 abut against the valve core assembly 3 and the end cap 4, respectively.

[0051] When the pressure in the hydraulic system exceeds the preload of spring assembly 1, hydraulic oil enters the oil passage 23 through inlet 21 and exerts pressure on valve core assembly 3. This pressure is the hydraulic system pressure. Since the hydraulic system pressure exceeds the preload of spring assembly 1, the hydraulic oil in oil passage 23 overcomes the elastic force of spring assembly 1 and pushes valve core assembly 3 to the left, so that oil passage 23 connects inlet 21 and return port 22. After flowing into valve seat 2 from oil passage 23, the hydraulic oil flows to the oil tank through return port 22, thus reducing the hydraulic system pressure. When the hydraulic system pressure drops below the preload of spring assembly 1, spring assembly 1 resets to push valve core assembly 3 to the right to block oil passage 23. As the pressure of the hydraulic system changes continuously, the spring assembly 1 will drive the valve core assembly 3 to move up and down continuously. When the excitation frequency of the oil pressure is the same as the frequency of one of the first spring 11 and the second spring 12, the other can effectively suppress its vibration, reduce the occurrence of resonance, and achieve a self-stabilizing state. This will keep the valve core assembly 3 stable, reduce vibration and noise, extend the service life of the relief valve, and improve the reliability of the relief valve.

[0052] Furthermore, the end cap 4 can adjust the preload of the spring assembly 1, thereby improving the applicability of the relief valve and ensuring that it can be applied to a variety of different working conditions, making the overall relief valve more applicable and versatile.

[0053] Specifically, if Figure 2 As shown, the valve core assembly 3 includes a valve core body 31 and a spring seat 32. The spring seat 32 is located at the end of the valve core body 31 away from the oil passage 23, and one end of the spring assembly 1 is connected to or abuts against the spring seat 32. The spring seat 32 facilitates the installation of the spring assembly 1, improving the ease of installation and the stability of the spring assembly 1 when compressed.

[0054] Specifically, if Figure 3 As shown, the valve core body 31 includes a first part 311 and a second part 312 connected together. The first part 311 extends into the oil passage 23, and the outer peripheral surface of the second part 312 is a conical surface. The conical surface can abut against the valve seat 2 to close the oil passage 23. That is, along the direction away from the first part 311, the diameter of the second part 312 gradually increases, so that the outer peripheral surface of the second part 312 is a conical surface. The second part 312 can abut against the valve seat 2 to form a conical seal, thereby closing the oil passage 23.

[0055] Specifically, if Figure 3As shown, the valve core body 31 also includes a third part 313, which is located at the end of the first part 311 away from the second part 312. Along the radial direction of the valve core body 31, the third part 313 has an oil passage gap with the valve seat 2, which communicates with the oil inlet 21. The third part 313 is slidably guided within the oil passage 23 of the valve seat 2. The third part 313 provides guidance for the axial movement of the valve core body 31, ensuring the stability of the valve core body 31 during axial sliding and effectively preventing the valve core body 31 from shaking, thus improving the reliability and stability of the relief valve. Simultaneously, hydraulic oil entering the oil passage 23 through the oil inlet 21 can flow through the oil passage gap to the bottom of the oil passage 23, acting axially on the third part 313 to open the valve core body 31 and ensure the overflow effect. It should be noted that the bottom of the oil passage 23 refers to the end of the oil passage 23 away from the spring assembly 1; this is only used to indicate the location and does not limit its structure.

[0056] Specifically, if Figure 3 As shown, the valve core body 31 also includes a fourth part 314, which is disposed at the end of the second part 312 away from the first part 311, and is connected to the spring seat 32. In some embodiments, the fourth part 314 is detachably connected to the spring seat 32, which makes disassembly and reinstallation simpler and faster when maintenance or replacement of the spring seat 32 at one end of the valve core body 31 is required, thus helping to reduce maintenance difficulty and maintenance costs.

[0057] Specifically, if Figure 2 As shown, the end cap 4 includes an adjusting rod 41. One end of the adjusting rod 41 has an axially oriented receiving groove. At least a portion of the spring assembly 1 is located in the receiving groove. The adjusting rod 41 is connected to the valve seat 2 and can move axially. By adjusting the position of the adjusting rod 41, the preload of the spring assembly 1 can be adjusted, thereby adjusting the set pressure of the relief valve and improving the versatility of the relief valve.

[0058] In this embodiment, the adjusting rod 41 is threadedly connected to the valve seat 2. That is, the adjusting rod 41 can be fixed to the valve seat 2 by screwing on the adjusting rod 41, and the depth of insertion of the adjusting rod 41 into the valve seat 2 can be changed by changing the depth of screwing, thereby changing the set pressure of the relief valve. This is convenient, quick and easy to operate.

[0059] Specifically, if Figure 2 As shown, this end cover 4 also includes an adjusting sleeve 42, which is connected to the valve seat 2. The adjusting sleeve 42 is used to limit the extreme positions of the valve seat 2's axial movement. Through the limiting function of the adjusting sleeve 42, it is possible to prevent the adjusting rod 41 from being over-adjusted, which could lead to dangerous situations such as oil leakage.

[0060] Furthermore, such as Figure 2As shown, this end cap 4 also includes a locking nut 43, which is threadedly connected to the portion of the adjusting rod 41 located outside the valve seat 2. The locking nut 43 can abut against the adjusting sleeve 42. The locking nut 43, through its threaded connection to the portion of the adjusting rod 41 located outside the valve seat 2, can tightly fix the adjusting rod 41, preventing it from loosening due to vibration or pressure fluctuations during operation. This improves the stability of the adjusting rod 41 and ensures that the preload of the spring assembly 1 will not change due to loosening of the adjusting rod 41, thereby guaranteeing the stable operation of the hydraulic system. When it is necessary to adjust the preload of the spring assembly 1, loosen the locking nut 43 and then screw the adjusting rod 41 to the desired position, and then screw the locking nut 43 until it abuts against the adjusting sleeve 42, thus locking the adjusting rod 41 to prevent loosening.

[0061] Obviously, the above embodiments of this utility model are merely examples for clearly illustrating the present utility model, and are not intended to limit the implementation of the present utility model. Those skilled in the art can make various obvious changes, readjustments, and substitutions without departing from the protection scope of this utility model. It is neither necessary nor possible to exhaustively describe all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this utility model should be included within the protection scope of the claims of this utility model.

Claims

1. A spring assembly (1), characterized in that, include: First spring (11); The second spring (12) is located on the outer periphery of the first spring (11), and the first spring (11) and the second spring (12) are integrally formed.

2. The spring assembly (1) according to claim 1, characterized in that, The first spring (11) has the opposite rotation direction to the second spring (12).

3. The spring assembly (1) according to claim 1, characterized in that, At least three turns at both ends of the second spring (12) are pressed together to form a support ring (121), and both ends of the support ring (121) are planar.

4. An overflow valve, characterized in that, The overflow valve includes: The valve seat (2) has an oil inlet (21), an oil return (22) and an oil passage (23), wherein the oil inlet (21) and the oil return (22) are connected through the oil passage (23); A valve core assembly (3) is disposed within the valve seat (2), and the valve core assembly (3) is axially slidable to close or open the oil passage (23); End cap (4) is disposed at one end of the valve seat (2) away from the oil inlet (21); The spring assembly (1) as described in any one of claims 1-3, wherein both ends of the spring assembly (1) abut against the valve core assembly (3) and the end cap (4), respectively.

5. The overflow valve according to claim 4, characterized in that, The valve core assembly (3) includes: The valve core body (31) and the spring seat (32) are provided at one end of the valve core body (31) away from the oil passage (23), and one end of the spring assembly (1) is connected to or abuts against the spring seat (32).

6. The overflow valve according to claim 5, characterized in that, There is an oil passage gap between the valve core body (31) and the valve seat (2), and the oil passage gap is connected to the oil inlet (21). The valve core body (31) includes a first part (311) and a second part (312) connected together. The first part (311) extends into the oil passage (23), and the outer peripheral surface of the second part (312) is a conical surface. The conical surface can abut against the valve seat (2) to close the oil passage (23).

7. The overflow valve according to claim 6, characterized in that, The valve core body (31) further includes a third part (313), which is disposed at the end of the first part (311) away from the second part (312), and the third part (313) is slidably guided and fitted in the oil passage (23) of the valve seat (2).

8. The overflow valve according to claim 4, characterized in that, The end cap (4) includes: An adjusting rod (41) is provided with an axially oriented receiving groove at one end. At least a portion of the spring assembly (1) is located in the receiving groove. The adjusting rod (41) is connected to the valve seat (2), and the adjusting rod (41) is capable of moving axially.

9. The overflow valve according to claim 8, characterized in that, The end cap (4) also includes: Adjusting sleeve (42) is connected to valve seat (2) and is used to limit the extreme position of valve seat (2) along the axial direction.

10. The overflow valve according to claim 9, characterized in that, The end cap (4) also includes: A locking nut (43) is threaded to the portion of the adjusting rod (41) located outside the valve seat (2), and the locking nut (43) can abut against the adjusting sleeve (42).

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