An overflow valve with secondary pressurization function

Abstract

This utility model relates to the field of engineering machinery technology and discloses a relief valve with a secondary pressurization function. It includes a valve sleeve with an oil inlet, an oil return port, and an oil discharge port. A valve body is fitted over the valve sleeve, and a main valve core is slidably disposed within the valve sleeve. A main valve seat is fixed to one end of the valve sleeve, and a return spring is provided between the main valve seat and the main valve core. A first chamber is formed between the main valve core and the main valve seat. A first damping channel is provided on the main valve core, and a second damping channel is provided on the main valve seat. A pressure regulating valve seat is fixed within the valve body, and a pilot valve core and a spool valve core are slidably disposed within the pressure regulating valve seat. A pressure regulating spring abuts against the pilot valve core and the spool valve core. A pressure regulating rod is internally threaded to the tail end of the pressure regulating valve seat, and the pressure regulating rod abuts against the spool valve core. A second chamber is formed between the pressure regulating rod and the spool valve core. A pressure boosting hole is provided on the valve body, and a pressure boosting channel is provided within the spool valve core. The relief valve of this utility model has a simpler structure, is easier to install, and reduces processing costs and assembly difficulty.

Description

Technical Field

[0001] This utility model relates to the field of engineering machinery technology, specifically to an overflow valve with a secondary pressurization function. Background Technology

[0002] Relief valves are primarily used in construction machinery to regulate and control fluid pressure. For example, the main relief valve in an excavator is a crucial component of its hydraulic system. Its main function is to control the maximum working pressure of the hydraulic system and protect it from overload damage. The main relief valve operates based on the principle of pressure balance. By adjusting the valve core position, it controls the working pressure of the hydraulic system. When the pressure in the hydraulic system exceeds the set value, the main relief valve automatically opens, allowing excess hydraulic oil to flow back to the oil tank, thus protecting the normal operation of the hydraulic system. This main relief valve has a pilot pressure. In special working conditions, such as encountering excessively hard rocks or obstacles that cannot be dug, secondary pressurization is required to improve the excavator's digging ability.

[0003] For example, the related technology disclosed in CN209414290U discloses a relief valve with a two-stage control function, which realizes a secondary pressurization function for the relief valve. This is achieved by adjusting the pre-compression of the pilot valve core spring to regulate the opening pressure of the pilot valve core, thus setting the primary and secondary relief pressures. Specifically, the pilot valve core spring is adjusted by turning the adjusting screw, which pushes the adjusting plunger and the pressurizing plunger to the right, thereby changing the pre-compression of the pilot valve core spring and thus changing the opening pressure of the pilot valve core, thereby achieving a pressure change at the opening point of the main valve core. In other words, the left end of the pilot valve core spring is compressed sequentially through the pressurizing plunger, the adjusting plunger, and the adjusting screw. This results in numerous parts, a complex structure, cumbersome installation, and increased processing costs and assembly difficulty.

[0004] Therefore, there is an urgent need to provide an overflow valve with secondary pressure regulation function to solve the above problems. Utility Model Content

[0005] The purpose of this invention is to provide an overflow valve with a secondary pressure regulating function, which has a simpler structure, is easier to install, and reduces costs.

[0006] This utility model is achieved through the following technical solution:

[0007] A relief valve with secondary pressurization function includes:

[0008] A valve sleeve is provided with an oil inlet, an oil return port, and an oil discharge port. A valve body is fitted onto one end of the valve sleeve. A main valve core is slidably disposed inside the valve sleeve. A main valve seat is fixed at one end of the valve sleeve near the valve body. A return spring abuts against the main valve seat and the main valve core. A chamber is formed between the main valve core and the main valve seat. A damping channel one is provided on the main valve core, connecting the oil inlet and the chamber one. A damping channel two is provided on the main valve seat, connecting the oil discharge port and the chamber one.

[0009] A pressure regulating valve seat is fixed to the valve body. A pilot valve core and a slide valve core are slidably disposed inside the pressure regulating valve seat. The pilot valve core is used to open or block the second damping channel. A pressure regulating spring abuts between the pilot valve core and the slide valve core. A pressure regulating rod is internally threaded to the tail end of the pressure regulating valve seat. The pressure regulating rod can abut against the slide valve core. A second chamber can be formed between the pressure regulating rod and the slide valve core. A pressure boosting hole is provided on the valve body. A pressure boosting channel communicating with the second chamber and the pressure boosting hole is provided inside the slide valve core.

[0010] As an optional solution, an annular groove is formed on the circumferential surface of the pressure regulating rod, and a sealing ring is provided in the annular groove, which is in sealing fit with the inner wall of the pressure regulating valve seat.

[0011] As an optional solution, the pressure regulating valve seat includes a threaded section, a large-diameter section, and a small-diameter section. The large-diameter section is connected between the threaded section and the small-diameter section. The inner diameter of the threaded section is smaller than the inner diameter of the large-diameter section but larger than the inner diameter of the small-diameter section. The threaded section is threadedly engaged with the pressure regulating rod, and the sealing ring is sealed with the small-diameter section.

[0012] As an optional solution, a buffer ramp is provided between the large-diameter section and the small-diameter section.

[0013] As an optional solution, a pressure boosting port is provided on the side wall of the pressure regulating valve seat, and a pressure boosting gap is formed between the pressure regulating valve seat and the valve body. The pressure boosting channel is connected to the pressure boosting hole through the pressure boosting port and the pressure boosting gap in sequence.

[0014] As an optional solution, a receiving groove is provided in one end of the main valve core near the main valve seat, and part of the return spring is located in the receiving groove and abuts against the bottom of the receiving groove.

[0015] As an optional solution, a filter screen is provided inside the second damping channel.

[0016] As an optional solution, a spring seat is abutted against the end of the main valve seat near the main valve core, and the end of the return spring away from the main valve core abuts against the spring seat.

[0017] As an alternative, the spring seat presses the filter screen into the damping channel two.

[0018] As an optional solution, the outer periphery of the main valve seat is provided with a raised edge, and the inner periphery of the valve body is provided with a limiting boss. One side of the raised edge abuts against the end face of the valve sleeve, and the other side abuts against the limiting boss.

[0019] The beneficial effects of this utility model are as follows:

[0020] This invention provides a relief valve with a secondary pressurization function. This relief valve has two relief pressures, high and low, and is mainly used in the hydraulic system of excavators. During normal operation, the primary pressure control is sufficient. When encountering excessive loads, the primary pressure may be insufficient, and a higher secondary pressure can be activated through the pressure boosting port. This effectively improves the excavator's working efficiency and protects the hydraulic system from overload damage. In actual operation, the primary and secondary pressures can be easily switched freely. Furthermore, structurally, the relief valve of this invention replaces the function of the two components—adjusting screw and adjusting plunger—in the existing technology by using an adjusting rod. This reduces the use of one component, resulting in a simpler structure. The adjusting rod has a more regular structure, making it easier to manufacture. Compared to two separate components, it offers better manufacturing consistency and easier assembly, reducing manufacturing costs and assembly difficulty. Attached Figure Description

[0021] To more clearly and understandably illustrate the embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0022] Figure 1 This is a schematic diagram of the structure of the overflow valve with secondary pressurization function provided in this embodiment of the utility model;

[0023] Figure 2 This is a cross-sectional view of the overflow valve with secondary pressurization function provided in this embodiment of the utility model;

[0024] Figure 3 This is a partial schematic diagram of an overflow valve with a secondary pressurization function provided in an embodiment of this utility model.

[0025] In the picture:

[0026] 1. Valve sleeve; 11. Oil inlet; 12. Oil return port; 13. Oil discharge port; 2. Valve body; 21. Pressure boosting hole; 22. Limiting boss; 3. Main valve core; 31. Damping channel one; 32. Receiving groove; 4. Main valve seat; 41. Damping channel two; 42. Filter screen; 43. Spring seat; 44. Raised edge; 5. Return spring; 6. Pressure regulating valve seat; 601. Threaded section; 602. Large diameter section; 603. Small diameter section; 604. Buffer slope; 61. Pressure boosting port; 62. Pressure boosting gap; 63. First locking nut; 7. Pilot valve core; 8. Slide valve core; 81. Pressure boosting channel; 9. Pressure regulating spring; 10. Pressure regulating rod; 101. Second locking nut; 102. Annular groove; 103. Sealing ring; X1. Chamber one; X2. Chamber two. Detailed Implementation

[0027] 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.

[0028] 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.

[0029] 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.

[0030] In the description of this embodiment, the terms "upper," "lower," "left," and "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.

[0031] like Figure 1 and Figure 2 As shown, this embodiment provides a relief valve with a secondary pressurization function, including a valve sleeve 1. The valve sleeve 1 has an oil inlet 11, an oil return port 12, and an oil discharge port 13. A valve body 2 is fitted around one end of the valve sleeve 1. A main valve core 3 is slidably disposed inside the valve sleeve 1. The main valve core 3 is used to connect or disconnect the oil inlet 11 and the oil return port 12. A main valve seat 4 is fixed at the end of the valve sleeve 1 near the valve body 2. A return spring 5 abuts against the main valve seat 4 and the main valve core 3. The return spring 5 is configured to always have the tendency to prevent the main valve core 3 from moving to the left relative to the valve sleeve 1 to connect the oil inlet 11 and the oil return port 12, so that the main valve core 3 can be kept in a blocked position when there is no overflow, thereby ensuring the reliability of the relief valve. A chamber X1 is formed between the main valve core 3 and the main valve seat 4. The valve core 3 has a damping channel 31 that connects the oil inlet 11 and the first chamber X1. The main valve seat 4 has a damping channel 41 that connects the oil outlet 13 and the first chamber X1. The overflow valve also includes a pressure regulating valve seat 6, which is fixed inside the valve body 2. A pilot valve core 7 and a spool valve core 8 are slidably arranged inside the pressure regulating valve seat 6. The pilot valve core 7 is used to open or block the second damping channel 41. A pressure regulating spring 9 abuts between the pilot valve core 7 and the spool valve core 8. A pressure regulating rod 10 is internally threaded at the tail end of the pressure regulating valve seat 6. The pressure regulating rod 10 can abut against the spool valve core 8. A second chamber X2 can be formed between the pressure regulating rod 10 and the spool valve core 8. The valve body 2 has a pressure boosting hole 21. A pressure boosting channel 81 that connects the second chamber X2 and the pressure boosting hole 21 is opened inside the spool valve core 8.

[0032] Combination Figure 2 The working principle of this relief valve is described in detail below:

[0033] Hydraulic oil enters through inlet 11 and flows into chamber X1 through damping channel 31 on the main valve core 3. When the pressure in chamber X1 is less than the set pressure of the adjusting spring 9, the relief valve is closed and no overflow occurs. The pressure in chamber X1 gradually increases as the load at inlet 11 increases. When the pressure in chamber X1 is greater than the set pressure of the adjusting spring 9, the pressure in chamber X1 is transmitted to the right end of the pilot valve core 7 through damping channel 41 on the main valve seat 4, pushing the pilot valve core 7 to overcome the elastic force of the adjusting spring 9 and move to the left. When the pilot valve core 7 moves, it opens the second damping channel 41, so that the first chamber X1 is connected to the unloading port 13 through the second damping channel 41. The hydraulic oil in the first chamber X1 flows out from the unloading port 13 along the oil circuit A to unload. At the same time, the pressure in the first chamber X1 drops, so a pressure difference will be generated between the left and right ends of the main valve core 3. Driven by the pressure difference, the main valve core 3 moves to the left against the force of the return spring 5, opening the oil circuit from the inlet port 11 to the return port 12. The hydraulic oil flows from the inlet port 11 to the return port 12 along the oil circuit C to unload under high pressure.

[0034] The first-stage set pressure of the relief valve is achieved by turning the pressure adjusting rod 10. At this time, the pressure adjusting rod 10 and the slide valve core 8 are in abutting state. By turning the pressure adjusting rod 10, the pressure adjusting rod 10 pushes the slide valve core 8 to the right, changing the pre-compression of the pressure adjusting spring 9, thereby changing the opening point pressure of the pilot valve core 7, so as to realize the pressure change of the opening point of the main valve core 3 and set the first-stage relief pressure. Under special working conditions, when encountering excessively hard rocks or obstacles that cannot be dug out, secondary pressurization is required to improve the excavator's digging ability. At this time, pilot oil is provided through oil circuit B. The pilot oil flows through the pressurization hole 21 on the valve body 2 into the pressurization channel 81 inside the spool valve 8, and then flows into chamber two X2 and acts on the left end face of the spool valve 8, causing the spool valve 8 to move to the right. At this time, the pressure regulating rod 10 and the spool valve 8 are not in contact. After the spool valve 8 moves to the right, it compresses the pressure regulating spring 9 a second time, thereby changing the opening point pressure of the pilot valve 7 to realize the pressure change of the opening point of the main valve 3, setting the secondary overflow pressure, improving the system's pressure resistance, and thus improving the excavator's digging ability.

[0035] Therefore, this relief valve has two relief pressures, high and low, and is mainly used in the hydraulic system of excavators. During normal operation, the first-level pressure control is sufficient. When encountering excessive loads, the first-level pressure cannot meet the requirements, and a higher second-level pressure is activated through the pressure boosting port 21. This effectively improves the excavator's working efficiency and protects the hydraulic system from overload damage. In actual operation, the first-level and second-level pressures can be easily switched freely. Furthermore, in this embodiment, the relief valve, structurally speaking, replaces the function of the two components—the adjusting screw and the adjusting plunger—in the prior art by using the adjusting rod 10. This reduces the use of one component, making the structure simpler. The adjusting rod 10 has a more regular structure, making it easier to manufacture. Compared to two separate components, it offers better manufacturing consistency and is easier to assemble, reducing manufacturing costs and assembly difficulty.

[0036] In this embodiment, the oil inlet 11 is located at one axial end of the valve sleeve 1, and the oil return port 12 and the oil discharge port 13 are located on the outer periphery of the valve sleeve 1. Specifically, the oil discharge port 13 is formed by the gap between the valve body 2 and the valve sleeve 1 after the valve body 2 is fitted onto the valve sleeve 1. Both the damping channel one 31 and the damping channel two 41 are stepped holes, each having a small-diameter section and a large-diameter section. The large-diameter section mainly serves to guide the flow, while the small-diameter section mainly serves to delay damping.

[0037] Specifically, such as Figure 2 As shown, a pressure-boosting port 61 is provided on the side wall of the pressure regulating valve seat 6, and a pressure-boosting gap 62 is formed between the pressure regulating valve seat 6 and the valve body 2. The pressure-boosting channel 81 is connected to the pressure-boosting hole 21 through the pressure-boosting port 61 and the pressure-boosting gap 62 in sequence. Under special working conditions, when secondary pressurization is required to improve the digging capacity of the excavator, pilot oil is provided through oil circuit B. That is, the pilot oil flows into the pressure-boosting gap through the pressure-boosting hole 21 on the valve body 2, and then enters the pressure-boosting channel 81 flowing into the slide valve core 8 through the pressure-boosting port 61 on the pressure regulating valve seat 6. Finally, it flows into the chamber II X2 through the pressure-boosting channel 81 and acts on the left end face of the slide valve core 8 to achieve the effect of pressurization.

[0038] In an optional embodiment, such as Figure 3 As shown, an annular groove 102 is formed on the circumferential surface of the pressure regulating rod 10, and a sealing ring 103 is provided in the annular groove 102. The sealing ring 103 is in sealing fit with the inner wall of the pressure regulating valve seat 6. The sealing ring 103 can achieve the sealing at the mating point between the pressure regulating rod 10 and the pressure regulating valve seat 6, preventing pressurized oil from leaking between the pressure regulating rod 10 and the pressure regulating valve seat 6.

[0039] In an optional embodiment, such as Figure 3As shown, the pressure regulating valve seat 6 includes a threaded section 601, a large-diameter section 602, and a small-diameter section 603. The large-diameter section 602 connects between the threaded section 601 and the small-diameter section 603. The inner diameter of the threaded section 601 is smaller than the inner diameter of the large-diameter section 602 but larger than the inner diameter of the small-diameter section 603. The threaded section 601 is threadedly engaged with the pressure regulating rod 10, and the sealing ring 103 is sealed with the small-diameter section 603. The pressure regulating rod 10 is configured as a two-section stepped rod, one section having a larger outer diameter and threadedly engaged with the threaded section 601, and the other section having an annular groove 102 and a smaller outer diameter and engaged with the small-diameter section 603. By setting the inner diameter of the pressure regulating valve seat 6 to three sections, the outer diameter of the sealing ring 103 can be slightly smaller than the inner diameter of the threaded section 601 and slightly larger than the inner diameter of the small diameter section 603. This ensures that the sealing ring 103 will not rub against the threaded section 601 during the installation of the pressure regulating rod 10 into the pressure regulating valve seat 6, thus affecting the sealing performance of the sealing ring 103. Furthermore, after assembly, the sealing ring 103 can be press-fitted with the small diameter section 603 to ensure sealing reliability. Adding a large diameter section 602 between the threaded section 601 and the small diameter section 603 also prevents the sealing ring 103 from being easily damaged by wear if the threaded section 601 is directly connected to the small diameter section 603.

[0040] Optionally, such as Figure 3 As shown, a buffer slope 604 is provided between the large-diameter section 602 and the small-diameter section 603. The buffer slope 604 can act as a buffer, preventing the sharp right-angle corners from causing cutting or other damage to the sealing ring 103. In an optional embodiment, such as... Figure 2 As shown, a receiving groove 32 is provided in the end of the main valve core 3 near the main valve seat 4. The receiving groove 32 is coaxially connected with the damping channel 31. Part of the return spring 5 is located in the receiving groove 32 and abuts against the bottom of the receiving groove 32. Most of the length of the return spring 5 is located in the receiving groove 32 of the main valve core 3, which can shorten the overall length of the relief valve to a certain extent and reduce the space occupied.

[0041] In an optional embodiment, such as Figure 2 As shown, a filter screen 42 is installed inside the damping channel 41. The filter screen 42 can filter out solid impurities in the hydraulic oil, prevent blockage inside the relief valve, and ensure the normal operation of the relief valve.

[0042] In an optional embodiment, such as Figure 2As shown, a spring seat 43 abuts against the end of the main valve seat 4 near the main valve core 3, and the end of the return spring 5 away from the main valve core 3 abuts against the spring seat 43. The spring seat 43 is constructed in the shape of a stepped shaft with a through hole at its center. The larger outer diameter portion of the spring seat 43 is housed within the main valve seat 4, and the end of the return spring 5 away from the main valve core 3 is fitted over the smaller outer diameter portion of the spring seat 43 and abuts against the stepped surface of the spring seat 43. This allows the spring force of the return spring 5 to be directly applied to the spring seat 43, and the spring seat 43 can guide and support the extension or compression of the return spring 5.

[0043] Optionally, the spring seat 43 presses the filter screen 42 into the damping channel 41. In this way, the spring seat 43 can directly press the filter screen 42 into the damping channel 41 by the elastic force of the return spring 5, without the need for an additional connection to fix the filter screen 42, making the assembly of the filter screen 42 more convenient and quick.

[0044] Optionally, such as Figure 2 As shown, the outer periphery of the main valve seat 4 is provided with a protruding flange 44, and the inner periphery of the valve body 2 is provided with a limiting boss 22. One side of the protruding flange 44 abuts against the end face of the valve sleeve 1, and the other side abuts against the limiting boss 22. The valve body 2 can be threaded onto the valve sleeve 1. When the valve body 2 and the valve sleeve 1 are in place, the protruding flange 44 of the main valve seat 4 is clamped between the limiting boss 22 and the left end face of the valve sleeve 1, thereby achieving axial fixation of the main valve seat 4. Therefore, the installation of the main valve seat 4 can be achieved by the cooperation of the valve body 2 and the valve sleeve 1, without the need for additional connection methods to fix the main valve seat 4, making the installation of the main valve seat 4 more convenient and quick.

[0045] In one optional embodiment, the pilot valve core 7 is a cone valve core, and the cone-shaped sealing surface of the pilot valve core 7 contacts the inner wall of the damping channel 41 to form a cone seal. The sealing surface is a line contact seal formed by the annular line and the cone surface, which has a better sealing effect.

[0046] In one optional embodiment, the main valve core 3 contacts the conical inner wall of the valve sleeve 1 to form a conical seal, and the sealing surface is a line contact seal formed by the annular line and the conical surface, which has a better sealing effect.

[0047] Optionally, the pressure regulating valve seat 6 is threaded into the valve body 2, and a first locking nut 63 is externally threaded onto the end of the pressure regulating valve seat 6 away from the main valve seat 4. The first locking nut 63 abuts against the end face of the valve body 2. The first locking nut 63 is used to lock the pressure regulating valve seat 6 into the valve body 2 to prevent the pressure regulating valve seat 6 from moving axially relative to the valve body 2.

[0048] Optionally, a second locking nut 101 is externally threaded onto the end of the pressure regulating rod 10 away from the spool valve core 8. The second locking nut 101 abuts against the end face of the pressure regulating valve seat 6. The second locking nut 101 is used to lock the pressure regulating rod 10 inside the pressure regulating valve seat 6 to prevent the pressure regulating rod 10 from moving axially relative to the pressure regulating valve seat 6.

[0049] 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 other variations or modifications based on the above description. It is neither necessary nor possible to exhaustively list all possible implementations 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 relief valve with a secondary pressurization function, characterized in that, include: A valve sleeve (1) is provided with an oil inlet (11), an oil return port (12) and an oil discharge port (13). A valve body (2) is fitted on one end of the valve sleeve (1). A main valve core (3) is slidably arranged inside the valve sleeve (1). A main valve seat (4) is fixed at one end of the valve sleeve (1) near the valve body (2). A return spring (5) abuts between the main valve seat (4) and the main valve core (3). A chamber 1 (X1) is formed between the main valve core (3) and the main valve seat (4). A damping channel 1 (31) is provided on the main valve core (3) to connect the oil inlet (11) and the chamber 1 (X1). A damping channel 2 (41) is provided on the main valve seat (4) to connect the oil discharge port (13) and the chamber 1 (X1). A pressure regulating valve seat (6) is fixed inside the valve body (2). A pilot valve core (7) and a slide valve core (8) are slidably arranged inside the pressure regulating valve seat (6). The pilot valve core (7) is used to open or block the damping channel two (41). A pressure regulating spring (9) abuts between the pilot valve core (7) and the slide valve core (8). A pressure regulating rod (10) is internally threaded at the tail end of the pressure regulating valve seat (6). The pressure regulating rod (10) can abut against the slide valve core (8). A chamber two (X2) can be formed between the pressure regulating rod (10) and the slide valve core (8). A pressure boosting hole (21) is provided on the valve body (2). A pressure boosting channel (81) is provided inside the slide valve core (8) to connect the chamber two (X2) and the pressure boosting hole (21).

2. The overflow valve with secondary pressurization function according to claim 1, characterized in that, The pressure regulating rod (10) has an annular groove (102) on its circumferential surface. A sealing ring (103) is provided in the annular groove (102), and the sealing ring (103) is sealed to the inner wall of the pressure regulating valve seat (6).

3. The overflow valve with secondary pressurization function according to claim 2, characterized in that, The pressure regulating valve seat (6) includes a threaded section (601), a large diameter section (602), and a small diameter section (603). The large diameter section (602) is connected between the threaded section (601) and the small diameter section (603). The inner diameter of the threaded section (601) is smaller than the inner diameter of the large diameter section (602) and larger than the inner diameter of the small diameter section (603). The threaded section (601) is threadedly engaged with the pressure regulating rod (10), and the sealing ring (103) is sealed with the small diameter section (603).

4. The overflow valve with secondary pressurization function according to claim 3, characterized in that, A buffer ramp (604) is provided between the large diameter section (602) and the small diameter section (603).

5. The overflow valve with secondary pressurization function according to claim 1, characterized in that, A pressure-boosting port (61) is provided on the side wall of the pressure regulating valve seat (6), and a pressure-boosting gap (62) is formed between the pressure regulating valve seat (6) and the valve body (2). The pressure-boosting channel (81) is connected to the pressure-boosting hole (21) in sequence through the pressure-boosting port (61) and the pressure-boosting gap (62).

6. The overflow valve with secondary pressurization function according to claim 1, characterized in that, The main valve core (3) has a receiving groove (32) at one end near the main valve seat (4), and part of the return spring (5) is located in the receiving groove (32) and abuts against the bottom of the receiving groove (32).

7. The overflow valve with secondary pressurization function according to claim 1, characterized in that, A filter screen (42) is installed inside the second damping channel (41).

8. The overflow valve with secondary pressurization function according to claim 7, characterized in that, The main valve seat (4) has a spring seat (43) at one end near the main valve core (3), and the return spring (5) has abutting the spring seat (43) at one end away from the main valve core (3).

9. The overflow valve with secondary pressurization function according to claim 8, characterized in that, The spring seat (43) presses the filter screen (42) into the damping channel (41).

10. The overflow valve with secondary pressurization function according to any one of claims 1 to 9, characterized in that, The outer periphery of the main valve seat (4) is provided with a protruding edge (44), and the inner periphery of the valve body (2) is provided with a limiting boss (22). One side of the protruding edge (44) abuts against the end face of the valve sleeve (1), and the other side abuts against the limiting boss (22).

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