Damping type overflow valve

Abstract

The utility model discloses a damping type overflow valve, and belongs to the technical field of overflow valves. The damping type overflow valve comprises a valve seat and a valve element. The valve seat is provided with a valve port and an oil inlet hole. The valve element is arranged in the valve seat in a sliding mode along the X axis, the valve element is provided with an annular conical face, the valve element can slide in the axial direction of the valve element to close the valve port, the conical face moves to abut against the inner wall of the valve port to form a sealing face, and the included angle alpha between the conical face and the axis of the valve seat ranges from 12 degrees to 22 degrees. According to the damping type overflow valve, the valve port is opened or closed through mutual cooperation between the conical face of the valve element and the inner wall of the valve port, the acting force of oil on the conical face of the valve element is appropriate, it is guaranteed that the buffering effect on the oil is good, the pressure adjusting deviation of the damping type overflow valve can be reduced, and the timeliness of overflow is guaranteed.

Description

TECHNICAL FIELD

[0001] The utility model relates to the technical field of overflow valve especially relates to damping formula overflow valve. BACKGROUND

[0002] In the overflow valve, mainly through the mutual cooperation between the inner wall of the valve port of the valve core and the valve seat to realize the closing and opening of the valve port, generally in order to reduce the internal leakage of fluid, the valve core and the valve seat are provided with a tapered surface sealing, and the included angle between the tapered surface of the valve core and the axis of the valve seat is defined as alpha, but the included angle alpha is too large, which makes the force of oil liquid on the tapered surface too large, so that the opening displacement of the valve core is small, which leads to the large pressure regulating deviation of the overflow valve, and the working stability and reliability of the overflow valve cannot be guaranteed.

[0003] In view of the above problems, a damping formula overflow valve is needed to solve the above problems. UTILITY MODEL CONTENTS

[0004] The utility model discloses a kind of damping formula overflow valves, so that the force of oil liquid on the tapered surface of valve core is more appropriate, guarantee the buffering effect of oil liquid is good, and can reduce the pressure regulating deviation of damping formula overflow valve and guarantee the timeliness of overflow.

[0005] To achieve this purpose, the utility model adopts the following technical scheme:

[0006] Damping formula overflow valve, comprising:

[0007] Valve seat, the valve seat is respectively provided with valve port and oil inlet hole;

[0008] Valve core, along X-axis slidingly arranged in the valve seat, the valve core has annularly arranged tapered surface, the valve core can slide along its axial direction to close the valve port, the tapered surface moves to abut with the inner wall of the valve port to form sealing surface, the included angle alpha between the tapered surface and the axis of the valve seat is 12 °-22 °, and the axis of the valve seat is parallel to X-axis.

[0009] As an optional scheme, the valve seat is provided with more than six oil inlet holes, and each oil inlet hole is uniformly distributed along the circumference of the valve seat.

[0010] As an optional scheme, the valve core includes a first tapered body, a first cylindrical body and a second tapered body connected in sequence, the outer peripheral surface of the first tapered body is the tapered surface, the first cavity is formed between the tapered surface, the outer peripheral surface of the first cylindrical body, the outer peripheral surface of the second tapered body and the inner wall surface of the valve seat, and the first cavity is communicated with the oil inlet hole.

[0011] As an option, the oil inlet hole is arranged downwardly from right to left, and the damping overflow valve comprises a valve closing state, in which, along the X axis, the right edge of the oil inlet hole is located left of the right edge of the second conical body, and the interval h1 therebetween is 0.43-0.63 mm.

[0012] As an option, the valve seat is further provided with an oil outlet hole, the sealing surface is located between the oil outlet hole and the oil inlet hole, and the aperture of the oil outlet hole is larger than that of the oil inlet hole; the valve core further comprises:

[0013] a second cylinder connected to the side of the first conical body not connected to the first cylinder;

[0014] a flow guide disc arranged on the second cylinder, the flow guide disc comprising a circular ring surface and an arc-shaped inner recessed flow guide surface connected to each other, the circular ring surface being capable of abutting against the inner wall surface of the valve seat, along the X axis, the inner recessed flow guide surface and the inner side wall of the valve seat forming a second cavity therebetween, the second cavity being in communication with the oil outlet hole, and the extension surface of the sealing surface penetrating through the inner recessed flow guide surface.

[0015] As an option, the valve seat is provided with more than four oil outlet holes, and each oil outlet hole is uniformly distributed along the circumference of the valve seat.

[0016] As an option, the included angle γ between the inner recessed flow guide surface and the radial direction of the valve seat is 20.2-30.2°.

[0017] As an option, the damping overflow valve comprises a valve closing state, in which, along the X axis, the right edge of the circular ring surface is located left of the right edge of the oil outlet hole, and the interval h2 therebetween is 0.41-0.61 mm.

[0018] As an option, the damping overflow valve further comprises:

[0019] an adjusting member, at least a part of the adjusting member being threadedly connected into the valve seat, the adjusting member being provided with a limiting groove;

[0020] a resilient member, one end of the resilient member being arranged in the limiting groove, and the other end of the resilient member being connected to the valve core.

[0021] As an option, the damping overflow valve further comprises:

[0022] a limiting member arranged in the valve seat, one side of the limiting member abutting against the valve seat along the X axis, and the other side of the limiting member being capable of abutting against the adjusting member to axially limit the adjusting member.

[0023] The damping overflow valve has the advantages that:

[0024] By setting the valve port and the oil inlet hole in the valve seat respectively, the valve core is arranged in the valve seat and slides along the X axis, the valve core has a tapered surface arranged in a ring shape, the valve core can slide along the axial direction to close the valve port, the tapered surface moves to abut with the inner wall of the valve port to form a sealing surface between the tapered surface and the valve port, and the included angle α between the tapered surface and the axial line of the valve seat is 12°-22°, so that the inclination angle of the tapered surface relative to the axial line of the valve seat is appropriate, on the one hand, the tapered surface can provide a good flow guiding effect on the oil flowing to the oil inlet hole, so that the buffering effect on the oil is good, and the impact of the oil on the valve core can be avoided to be too large, so that the impact noise can be reduced, and at the same time, the force of the oil on the tapered surface is appropriate due to the angle, the valve core opening displacement can be avoided to be small, so that the pressure regulating deviation of the damping overflow valve is reduced, and then the working stability and reliability of the damping overflow valve can be ensured, on the other hand, the valve core can quickly respond to move due to the appropriate force of the oil on the tapered surface, so that the time of opening the overflow is short, and thus the timeliness of opening the overflow can be ensured. BRIEF DESCRIPTION OF DRAWINGS

[0025] Figure 1 is a structural schematic view of the damping overflow valve provided by the utility model, and

[0026] Figure 2 is a sectional view of the damping overflow valve provided by the utility model, and

[0027] Figure 3 is a sectional view of the valve seat provided by the utility model, and

[0028] Figure 4 is a structural schematic view of the valve core provided by the utility model, and

[0029] Figure 5 is a sectional view of the valve core provided by the utility model, and

[0030] Figure 6 is a marked enlarged structural schematic view of the distance h1 provided by the utility model, and

[0031] Figure 7 is a marked enlarged structural schematic view of the distance h2 provided by the utility model.

[0032] BRIEF DESCRIPTION OF DRAWINGS

[0033] 1-valve seat;11-valve port;12-oil inlet hole;13-oil outlet hole;14-limit wall surface;

[0034] 2-Valve core; 21-First cone; 211-Conical surface; 22-First cylinder; 23-Second cone; 24-Second cylinder; 25-Guide plate; 251-Annular surface; 252-Concave guide surface; 26-Third cylinder; 27-Limiting ring groove; 28-Fourth cylinder;

[0035] 3-First cavity; 4-Second cavity; 5-Adjusting component; 51-Limiting groove; 52-Limiting protrusion; 6-Elastic component; 7-Limiting component; 8-Sealing surface; 9-Locking nut. Detailed Implementation

[0036] All features disclosed in this specification, or all steps in all disclosed methods or processes, may be combined in any way, except for mutually exclusive features and / or steps.

[0037] Any feature disclosed in this specification, unless specifically stated otherwise, may be replaced by other equivalent or similar features. That is, unless specifically stated otherwise, each feature is merely one example of a series of equivalent or similar features. Throughout this specification, the same reference numerals indicate the same elements.

[0038] To make the technical problem solved by this utility model, the technical solution adopted, and the technical effect achieved clearer, the technical solution of this utility model will be further described below with reference to the accompanying drawings and specific embodiments.

[0039] This embodiment proposes a damped relief valve, which provides good buffering of the hydraulic fluid, reduces impact noise and pressure regulation deviation, and ensures timely relief opening, thereby guaranteeing the operational stability and reliability of the damped relief valve. Specifically, in this embodiment, the damped relief valve can be a direct-acting relief valve. This damped relief valve is suitable for hydraulic systems in aerial work platforms, construction machinery, warehousing and logistics, agricultural machinery, and industrial fields, serving functions such as pressure stabilization, pressure limiting relief, system unloading, and safety protection.

[0040] Specifically, such as Figures 1 to 3 As shown, the damping relief valve includes a valve seat 1 and a valve core 2; wherein, the valve seat 1 is provided with a valve port 11 and an oil inlet 12; the valve core 2 is slidably disposed in the valve seat 1 along the X-axis, and the valve core 2 has a conical surface 211 arranged in an annular shape. The valve core 2 can slide along its axial direction to close the valve port 11, and the conical surface 211 moves to abut against the inner wall of the valve port 11 to form a sealing surface 8.

[0041] Specifically, when the valve core 2 slides to the right along the X-axis, the conical surface 211 moves to abut against the inner wall of the valve port 11 to form a sealing surface 8, thus closing the valve port 11. When the valve core 2 slides to the left along the X-axis, the conical surface 211 moves to disengage from the inner wall of the valve port 11, creating a gap between the conical surface 211 and the valve port 11, thus opening the valve port 11. In other words, the valve port 11 is closed and opened by the mutual cooperation between the conical surface 211 of the valve core 2 and the inner wall of the valve port 11.

[0042] It is worth noting that after the overflow ends and during the automatic reset of the valve core 2 along the X-axis to the right, that is, during the process of the valve core 2 sliding along the X-axis to the right to drive the conical surface 211 to abut against the inner wall of the valve port 11, the oil remaining between the valve core 2 and the valve seat 1 will pass through the valve port 11, that is, it will be discharged to the outside of the damping relief valve through the gap between the conical surface 211 and the valve port 11. As the gap between the conical surface 211 and the valve port 11 gradually decreases during the process of the valve core 2 sliding along the X-axis to the right, the oil remaining between the valve core 2 and the valve seat 1 flows out through the smaller gap, thereby providing a damping buffer for the valve core 2 to move and reset along the X-axis to the right, thereby reducing the pressure impact of the valve core 2 during the process of closing the valve port 11, and thus improving the pressure stability of the entire damping relief valve.

[0043] Furthermore, such as Figure 2 As shown, the angle α between the conical surface 211 and the axis of the valve seat 1 is 12° to 22°, making the inclination angle of the conical surface 211 relative to the axis of the valve seat 1 suitable. On the one hand, the conical surface 211 can provide good guidance for the oil flowing to the oil inlet 12, resulting in a good buffering effect on the oil and avoiding excessive impact of the oil on the valve core 2, thus reducing impact noise. On the other hand, this angle allows the force of the oil on the conical surface 211 to be suitable, avoiding small valve opening displacement of the valve core 2, thereby reducing the pressure regulation deviation of the damped relief valve and ensuring the working stability and reliability of the damped relief valve. The axis of the valve seat 1 is parallel to the X-axis.

[0044] However, because the current included angle α is too small, the force exerted by the oil on the conical surface is too small, resulting in a slow response rate of the valve core, which makes the opening overflow time longer and cannot guarantee the timeliness of overflow.

[0045] Therefore, in this embodiment, by making the included angle α between the conical surface 211 and the axis of the valve seat 1 12° to 22°, the force exerted by the oil on the conical surface 211 is made more suitable, allowing the valve core 2 to respond quickly and move, ensuring a short opening and overflow time, thereby ensuring timely overflow opening. Specifically, as... Figures 1 to 3As shown, the valve seat 1 is provided with more than six oil inlet holes 12, and each oil inlet hole 12 is uniformly distributed along the circumference of the valve seat 1. In this embodiment, the valve seat 1 is provided with eight oil inlet holes 12. Here, the number of oil inlet holes 12 is not specifically limited, as long as each oil inlet hole 12 is uniformly arranged to make the oil force in the damping overflow valve more uniform and balanced.

[0046] By providing the valve core 2 with a conical surface 211 arranged in a ring shape, that is, by increasing the area of the conical surface 211 to increase the area of the entire valve core 2, the acting area between the oil and the valve core 2 can be increased, thereby increasing the number of oil inlet holes 12, and effectively enhancing the flow capacity of the entire damping overflow valve. At the same time, the acting area between the oil and the valve core 2 is increased to ensure that the valve core 2 has high working stability and reliability.

[0047] Further, as shown in Figure 2 , Figure 4 and Figure 5 , the valve core 2 includes a first conical body 21, a first cylindrical body 22 and a second conical body 23 connected in sequence; wherein the outer circumferential surface of the first conical body 21 is the conical surface 211 described above, the conical surface 211, the outer circumferential surface of the first cylindrical body 22 and the outer circumferential surface of the second conical body 23 form a first cavity 3 with the inner wall surface of the valve seat 1, and the first cavity 3 communicates with the oil inlet hole 12.

[0048] It is worth noting that the oil left between the valve core 2 and the valve seat 1 will be discharged through the valve port 11, specifically, the oil left in the first cavity 3 after the overflow is ended will be discharged to the outside of the damping overflow valve through the valve port 11.

[0049] Specifically, as shown in Figure 2 and Figure 3 , the oil inlet hole 12 is inclined downward from right to left, that is, the included angle β between the axis of the oil inlet hole 12 and the axis of the valve seat 1 is an acute angle, and the included angle β is associated with the movement stroke of the entire valve core 2 on the X-axis. Here, the specific value of the included angle β is not limited, and needs to be determined according to the movement stroke of the valve core 2 on the X-axis. In this embodiment, the movement stroke of the valve core 2 on the X-axis is 0-4.5mm.

[0050] Further, as shown in Figure 2 and Figure 6 , the damping overflow valve includes a valve closing state, in which along the X-axis, the right side edge of the oil inlet hole 12 is located to the left of the right side edge of the second conical body 23, and the spacing h1 therebetween is 0.43mm-0.63mm.

[0051] By setting the interval h1 to 0.43mm-0.63mm, the oil inlet hole 12 can be completely located in the first cavity 3 during the opening and closing of the valve port 11, avoiding the structure of the valve core 2 from blocking part of the oil inlet hole 12, so as to ensure the stability and reliability of the oil inlet of the oil inlet hole 12.

[0052] Further, as shown in Figures 1 to 3 , the valve seat 1 is also provided with an oil outlet hole 13, and the sealing surface 8 is located between the oil outlet hole 13 and the oil inlet hole 12, that is, the oil outlet hole 13 is located on the left side of the oil inlet hole 12, so that the sealing surface 8 can separate the oil outlet hole 13 from the first cavity 3; and the hole diameter of the oil outlet hole 13 is larger than that of the oil inlet hole 12, so as to ensure that the oil inlet amount of the oil inlet hole 12 is matched with the oil outlet amount of the oil outlet hole 13, thereby ensuring the smoothness and reliability of the overflow.

[0053] Specifically, as shown in Figure 4 and Figure 5 , the valve core 2 further comprises a second cylinder 24 and a flow guide disc 25; wherein the second cylinder 24 is connected to the side of the first tapered body 21 which is not connected to the first cylinder 22, that is, the second cylinder 24 is connected to the left side of the first tapered body 21; the flow guide disc 25 is arranged on the second cylinder 24, and the flow guide disc 25 comprises a connected annular surface 251 and an arc-shaped inner recessed flow guide surface 252, the annular surface 251 can abut against the inner wall surface of the valve seat 1; and along the X axis, the inner recessed flow guide surface 252 and the inner side wall of the valve seat 1 form a second cavity 4 therebetween, the second cavity 4 is communicated with the oil outlet hole 13, and the extension surface of the sealing surface 8 passes through the inner recessed flow guide surface 252. Wherein, the valve core 2 further comprises a third cylinder 26, a limiting ring groove 27 and a fourth cylinder 28, the limiting ring groove 27 is connected between the third cylinder 26 and the flow guide disc 25; the fourth cylinder 28 is connected to the right side of the second tapered body 23, and the fourth cylinder 28 abuts against the inner wall surface of the valve seat 1, so as to provide guiding and limiting effect for the movement of the valve core 2 along the X axis in the valve seat 1. In the embodiment, the flow guide disc 25 and the second cylinder 24 are integrally formed.

[0054] By setting the arc-shaped inner recessed flow surface 252 and making the extension surface of the sealing surface 8 pass through the inner recessed flow surface 252, on the one hand, the area of the entire valve core 2 can be increased by the larger area of the inner recessed flow surface 252, so as to further increase the acting area between the oil and the valve core 2, thereby increasing the number of the oil inlet hole 12 and the oil outlet hole 13, and effectively enhancing the flow capacity of the entire damping overflow valve; at the same time, the acting area between the oil and the valve core 2 is increased, which further ensures the working stability and higher reliability of the valve core 2; on the other hand, the inner recessed flow surface 252 can provide flow guiding effect for the oil flowing into the second cavity 4, so as to provide buffering effect for the oil and avoid excessive impact of the oil on the inner recessed flow surface 252, so as to better reduce the impact noise. In the embodiment, the acting area of the entire valve core 2 can be increased by 46%, and the flow capacity of the entire damping overflow valve can be increased by 26%.

[0055] Specifically, as shown in Figure 2 , the included angle γ between the inner recessed flow surface 252 and the radial direction of the valve seat 1 is 20.2°-30.2°, so that the inner recessed degree of the inner recessed flow surface 252 is appropriate, which can better ensure the buffering effect of the oil, and further ensure that the acting area between the oil and the valve core 2 is appropriate.

[0056] Further, as shown in Figure 2 and Figure 7 , in the closed valve state of the damping overflow valve, along the X axis, the right side edge of the circular annular surface 251 is located on the left side of the right side edge of the oil outlet hole 13, and the spacing h2 therebetween is 0.41mm-0.61mm, so as to ensure that the second cavity 4 is always in communication with the oil outlet hole 13 during the opening and closing of the valve port 11, avoiding that the flow guide disc 25 will cut off the second cavity 4 and the oil outlet hole 13, so that the oil in the second cavity 4 can be discharged to the outside of the entire damping overflow valve through the oil outlet hole 13, so as to ensure the overflow effect.

[0057] Further, as shown in Figures 1 to 3 , the valve seat 1 is provided with more than four oil outlet holes 13, and each oil outlet hole 13 is uniformly distributed along the circumferential direction of the valve seat 1. In the embodiment, the valve seat 1 is provided with six oil outlet holes 13. Here, the number of the oil outlet holes 13 is not specifically limited, as long as each oil outlet hole 13 is uniformly arranged, so that the acting force of the oil in the damping overflow valve is more uniform and balanced.

[0058] Further, as shown in Figure 1 and Figure 2As shown, the damping overflow valve further comprises an adjusting member 5 and an elastic member 6; wherein at least part of the adjusting member 5 is threadedly connected into the valve seat 1, a limiting groove 51 is arranged in the adjusting member 5, one end of the elastic member 6 is arranged in the limiting groove 51, and the other end of the elastic member 6 is directly connected with the valve core 2. In this embodiment, the adjusting member 5 can be specifically an adjusting rod, and the elastic member 6 can be specifically a pressure regulating spring.

[0059] As shown, Figure 2 by arranging the internal thread threadedly engaged with the adjusting member 5 directly in the valve seat 1, the adjusting member 5 is directly threadedly connected with the valve seat 1, so that the sleeve nut threadedly engaged with the adjusting member 5 in the prior art can be cancelled, the number of components of the entire damping overflow valve can be reduced, the cost is lower, and the structure of the damping overflow valve is simple and compact, which is beneficial to the lightweight design of the damping overflow valve.

[0060] Furthermore, as shown, Figure 2 by directly connecting the other end of the elastic member 6 with the valve core 2, i.e. arranging the valve core 2 and the elastic member 6 as an integrated connection structure, the valve core 2 provides a connection limiting action for the elastic member 6, so that the spring seat connected with the elastic member 6 in the prior art can be cancelled, the number of components of the entire damping overflow valve can be further reduced, the cost is lower, and the structure of the damping overflow valve is more simple and compact, which is more beneficial to the lightweight design of the damping overflow valve.

[0061] Further, as shown, Figure 2 the damping overflow valve further comprises a limiting member 7 arranged in the valve seat 1, which abuts against the valve seat 1 on one side along the X axis and can abut against the adjusting member 5 on the other side to axially limit the adjusting member 5. In this embodiment, the limiting member 7 can be specifically a steel wire retainer.

[0062] It is worth noting that, while the sleeve nut threadedly engaged with the adjusting member 5 in the prior art is cancelled, the limiting member 7 can also achieve the limiting and resisting action on the adjusting member 5, i.e. the use function provided by the sleeve nut before can also be ensured while the sleeve nut is saved.

[0063] Specifically, a limiting protrusion 52 is arranged on the outer circumferential surface of the adjusting member 5, the limiting protrusion 52 is located between the limiting member 7 and the valve core 2, i.e. the limiting protrusion 52 is located on the right side of the limiting member 7, and the other side of the limiting member 7 can abut against the limiting protrusion 52; and an external thread is arranged on the outer circumferential surface of the limiting protrusion 52, which is threadedly engaged with the internal thread of the valve seat 1.

[0064] As shown in Figure 2 , by setting the adjusting member 5, the elastic member 6 and the limiting member 7 which are used in cooperation, the adjusting member 5 can be rotated around the X axis relative to the valve seat 1 to adjust the pressure applied by the elastic member 6 to the valve core 2; when the adjusting member 5 is threadedly rotated to abut against the limiting wall surface 14 in the valve seat 1, the maximum pressure setting limit is achieved, that is, at this time, the adjusting member 5 is located at the position of maximum compression of the elastic member 6; when the adjusting member 5 is loosened around the X axis to abut against the limiting member 7, the minimum pressure setting limit is achieved, that is, at this time, the adjusting member 5 is located at the position of minimum compression of the elastic member 6; and by the resistance and limitation of the limiting member 7 to the limiting protrusion 52 of the outer circumferential surface of the adjusting member 5, the adjusting member 5 can be prevented from rotating out of the valve seat 1.

[0065] Further, as shown in Figure 1 and Figure 2 , the damping overflow valve further comprises a locking nut 9 which is threadedly connected to the part of the adjusting member 5 located outside the valve seat 1; after the adjusting member 5 adjusts the pressure applied by the elastic member 6 to the valve core 2, the locking nut 9 is threadedly locked to the part of the adjusting member 5 located outside the valve seat 1, and the locking nut 9 is abutted against the end surface of the valve seat 1, so that the adjusting member 5 can be locked by the torsion of the locking nut 9 to prevent the pressure applied by the elastic member 6 to the valve core 2 after adjustment from being changed due to accidental touch or accidental vibration.

[0066] The specific working process of the damping overflow valve in the embodiment is as follows:

[0067] Firstly, the oil enters the first cavity 3 through the oil inlet holes 12, at this time, since the oil in the first cavity 3 is subjected to equal forces on the conical surface 211 and the outer circumferential surface of the second conical body 23, the valve core 2 does not displace under the pre-tightening force of the elastic member 6, at this time, the conical surface 211 always abuts against the inner wall of the valve port 11, and the valve port 11 is closed.

[0068] Then, as the oil pressure of the oil inlet holes 12 gradually increases, the oil in the first cavity 3 is subjected to a greater force on the conical surface 211 than on the outer circumferential surface of the second conical body 23, so that the valve core 2 is subjected to a force to the left side; when the force to the left side of the valve core 2 is greater than the pre-tightening force of the elastic member 6, the valve core 2 as a whole moves to the left side along the X axis, at this time, the conical surface 211 is separated from the inner wall of the valve port 11, the valve port 11 is opened, and the oil in the first cavity 3 can flow into the second cavity 4 through the valve port 11, so that the oil in the second cavity 4 is discharged to the outside of the damping overflow valve through the oil outlet holes 13 to achieve the overflow effect.

[0069] Finally, when the overflow ends, the valve core 2 needs to be switched from the overflow state to the closing valve state, and the valve core 2 is automatically moved right along the X axis under the elastic force of the elastic member 6 to reset; during the movement of the valve core 2 to reset, the oil in the first cavity 3 will flow into the second cavity 4 through the small gap between the tapered surface 211 and the valve port 11, thereby providing a damping buffer effect for the movement of the valve core 2 to reset along the X axis.

[0070] The damping overflow valve in the embodiment can provide better flow buffering effect for the oil, and can reduce the pressure regulating deviation, and ensure the working stability and reliability of the entire damping overflow valve.

[0071] The damping overflow valve in the embodiment can increase the area of the entire valve core 2, thereby increasing the number of the oil inlet holes 12 and the oil outlet holes 13, optimizing the number of the oil inlet holes 12 to eight and the number of the oil outlet holes 13 to six, effectively enhancing the effective area of the valve core 2 and the flow capacity of the damping overflow valve, increasing the effective area of the valve core 2 by 46%, and improving the flow capacity of the damping overflow valve by 26%.

[0072] The damping overflow valve in the embodiment directly connects the valve core 2 and the elastic member 6 to omit the spring seat, and directly threads the adjusting member 5 into the valve seat 1 to omit the screw sleeve, thereby reducing the number of components of the entire damping overflow valve, lowering the cost, and making the structure of the damping overflow valve simple and compact, which is conducive to the lightweight design of the damping overflow valve.

[0073] The above is only a preferred embodiment of the present application, and for those skilled in the art, according to the idea of the present application, the specific implementation and application range can be changed, and the content of the specification should not be understood as a limitation of the present application.

Claims

1. A damped spill valve characterized by, The application relates to a damping overflow valve. The valve seat (1) is provided with valve ports (11) and oil inlet holes (12) respectively; The valve core (2) is arranged in the valve seat (1) along the X axis and is provided with a ring-shaped taper surface (211); the valve core (2) can slide along the axial direction to close the valve port (11); the taper surface (211) is moved to abut against the inner wall of the valve port (11) to form a sealing surface (8); the included angle (alpha) between the taper surface (211) and the axis of the valve seat (1) is 12-22 degrees; and the axis of the valve seat (1) is parallel to the X axis.

2. The piloted relief valve of claim 1, wherein The valve seat (1) is provided with more than six oil inlet holes (12); and the oil inlet holes (12) are uniformly distributed along the circumferential direction of the valve seat (1).

3. The piloted relief valve of claim 1, wherein The valve core (2) comprises a first taper body (21), a first cylinder (22) and a second taper body (23) which are sequentially connected; the outer circumferential surface of the first taper body (21) is the taper surface (211); the taper surface (211), the outer circumferential surface of the first cylinder (22) and the outer circumferential surface of the second taper body (23) form a first cavity (3) with the inner wall surface of the valve seat (1); and the first cavity (3) is communicated with the oil inlet hole (12).

4. The piloted relief valve of claim 3, wherein The oil inlet hole (12) is downwardly inclined from the right side to the left side; the damping overflow valve comprises a valve closing state; in the valve closing state, along the X axis, the right side edge of the oil inlet hole (12) is located on the left side of the right side edge of the second taper body (23); and the spacing (h1) between the right side edge of the oil inlet hole (12) and the right side edge of the second taper body (23) is 0.43-0.63 mm.

5. The piloted relief valve of claim 3 wherein, The valve seat (1) is further provided with an oil outlet hole (13); the sealing surface (8) is located between the oil outlet hole (13) and the oil inlet hole (12); the aperture of the oil outlet hole (13) is larger than that of the oil inlet hole (12); the valve core (2) further comprises: A second cylinder (24) connected to the side of the first taper body (21) which is not connected to the first cylinder (22); A flow guide disc (25) arranged on the second cylinder (24); the flow guide disc (25) comprises a circular ring surface (251) and an arc-shaped inner recessed flow guide surface (252); the circular ring surface (251) can abut against the inner wall surface of the valve seat (1); along the X axis, the inner recessed flow guide surface (252) forms a second cavity (4) with the inner side wall of the valve seat (1); the second cavity (4) is communicated with the oil outlet hole (13); and the extension surface of the sealing surface (8) passes through the inner recessed flow guide surface (252).

6. The piloted relief valve of claim 5, wherein, The valve seat (1) is provided with more than four oil outlet holes (13); and the oil outlet holes (13) are uniformly distributed along the circumferential direction of the valve seat (1).

7. The piloted relief valve according to claim 5 or 6, characterized in that The included angle (gamma) between the inner recessed flow guide surface (252) and the radial direction of the valve seat (1) is 20.2-30.2 degrees.

8. The piloted relief valve according to claim 5 or 6, characterized in that The damping overflow valve comprises a valve closing state, in which, along the X axis, the right side edge of the circular surface (251) is located at the left side of the right side edge of the oil outlet hole (13), and the interval h2 therebetween is 0.41-0.61 mm.

9. The piloted relief valve of any one of claims 1-6, wherein, The damping overflow valve further comprises: An adjusting member (5) is at least partially screwed into the valve seat (1), and the adjusting member (5) is provided with a limiting groove (51); An elastic member (6) is arranged in the limiting groove (51) at one end, and the other end of the elastic member (6) is connected with the valve core (2).

10. The piloted relief valve of claim 9, wherein, The damping overflow valve further comprises: A limiting member (7) is arranged in the valve seat (1), and along the X axis, one side of the limiting member (7) abuts against the valve seat (1), and the other side of the limiting member (7) can abut against the adjusting member (5) to axially limit the adjusting member (5).

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