Exhaust valve

Abstract

The exhaust valve comprises a valve seat, a valve element, a spring and an end cover, and the end cover is provided with a balance hole; the valve seat is provided with an air inlet and a valve port part, the end cover and the valve seat define a cavity part, exhaust holes are formed in the peripheral side wall part of the cavity part, the valve element is located in the cavity part, at least part of the spring is located in the cavity part, the valve element can axially move to be close to or away from the valve port part so as to open and close the valve port part, one end of the spring abuts against the valve element, and the other end of the spring abuts against the end cover; the flow area of the valve port part is a first area, the guide gap is a second area, the area of the balance hole is a third area, and the third area is gt; a first area gt; and a second area. According to the exhaust valve, the situation that the exhaust valve is frequently opened and closed due to fluctuation of the internal pressure of a system can be avoided while the internal pressure of the system is kept in a stable state, and therefore the service life of the exhaust valve is prolonged.

Description

Technical Field

[0001] This application relates to the field of automotive control technology, specifically to an exhaust valve. Background Technology

[0002] An exhaust valve typically consists of a valve seat, a valve core, and a spring. The valve seat has a valve port and a cavity that are connected together. The valve core and spring are located in the cavity. Under the action of the spring force, the valve core abuts against the valve port to achieve a seal. When the internal pressure of the system exceeds the rated value, the spring is compressed, the sealing gasket is pushed open, and a bypass channel is opened to achieve rapid exhaust. When the internal pressure returns to below the rated value, the spring returns to its original position and quickly pushes the sealing gasket to block the flow of gas inside and outside, so as to ensure the stability of the internal pressure of the system.

[0003] In actual use, frequent fluctuations in the internal pressure of the system will cause the valve core to frequently open and close the valve port, affecting its service life. Summary of the Invention

[0004] The purpose of this application is to provide an exhaust valve that can maintain a stable internal system pressure while avoiding frequent opening and closing of the exhaust valve due to frequent fluctuations in internal system pressure, thereby reducing noise and extending the service life of the exhaust valve.

[0005] To solve the above-mentioned technical problems, this application provides an exhaust valve, including a valve seat, a valve core, a spring and an end cap, wherein the end cap is provided with a balance hole;

[0006] The valve seat is provided with an air inlet and a valve port. The end cap is fixedly connected to or limited to the valve seat and surrounds it to form a cavity. The peripheral sidewall of the cavity is provided with an exhaust hole. The valve core is slidably disposed in the cavity. The spring is at least partially located in the cavity. The valve core can move axially to approach or move away from the valve port. One end of the spring abuts against the end cap, and the other end of the spring abuts against the valve core.

[0007] The valve should include at least the following operating states: In the fully closed state, the valve core is against the valve port; in the fully open state, the valve core is away from the valve port, and the distance between the end face of the valve core and the valve port is defined as the first distance L1; in the intermediate state, the distance between the end face of the valve core and the valve port is defined as the second distance L2, where L2... <L1;

[0008] Define the flow area of ​​the valve port as the first area S1; there is a guide gap between the valve core and the peripheral side wall, and define the area of ​​the guide gap as the second area S2; the area of ​​the exhaust port end face is the third area S3; satisfy S3>S1, and the relationship among the three is: S2<1.1 S1.

[0009] This invention provides a novel exhaust valve structure, comprising at least the following operating states: in the fully closed state, the valve core abuts against the valve port; in the fully open state, the valve core moves away from the valve port, and the distance between the end face of the valve core and the valve port is defined as L1; in the intermediate state, the distance between the end face of the valve core and the valve port is defined as L2, wherein L2 <L1;

[0010] When the system is under high pressure, the valve core moves away from the valve port to release air. The air release process continues until the internal pressure of the system drops to a predetermined low pressure state. At this point, the valve core comes into contact with the valve port, and the flow area of ​​the valve port is defined as the first area S1. There is a guide gap between the valve core and the peripheral wall, and the area of ​​the guide gap is defined as the second area S2. The area of ​​the exhaust port end face is defined as the third area S3. S3 > S1 and S2 < 1.1 S1, so that a pressure difference is established on both sides of the valve core after the valve port is opened. This achieves the intermediate state of the exhaust process from high pressure to low pressure, thereby relatively reducing the adverse effects of frequent opening and closing of the valve port caused by internal pressure fluctuations and improving the safe service life of the exhaust valve. Attached Figure Description

[0011] Figure 1 This is a cross-sectional view of the exhaust valve in the closed state provided in the embodiment of this application;

[0012] Figure 2 This is a cross-sectional view of the exhaust valve in the open state provided in the embodiment of this application;

[0013] Figure 3 This is a cross-sectional view of the valve core;

[0014] Figure 4 This is a cross-sectional view of the valve seat;

[0015] Figure 5 yes Figure 4 A cross-sectional view of the middle valve seat.

[0016] Appendix Figures 1-5 The reference numerals in the attached figures are explained as follows:

[0017] 1 Valve seat, 11 Air inlet, 12 Valve port, 13 Cavity, 14 Exhaust port, 15 Groove;

[0018] 2. Valve core; 21. Annular stepped structure; 22. Sealing groove; 23. Sealing element; 24. Positioning groove;

[0019] 3 springs;

[0020] 4. Guiding passages;

[0021] 5. Guide clearance;

[0022] 6 end caps, 61 groove structure, 62 balance holes. Detailed Implementation

[0023] To enable those skilled in the art to better understand the technical solutions of this application, the application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0024] This application provides an exhaust valve for balancing the pressure within a system, thereby maintaining the system pressure within a stable range.

[0025] Specifically, such as Figure 1 and Figure 2 As shown, the exhaust valve includes a valve seat 1, a valve core 2, a spring 3, and an end cap 6. The valve seat 1 has an air inlet 11 and a valve port 12 connected in sequence. The end cap 6 is fixedly connected to or limited by the valve seat 1 and encloses a cavity 13. The peripheral sidewall of the cavity 13 has an exhaust hole 14. The valve core 2 is located in the cavity 13 and can move axially within the cavity 13 to approach or move away from the valve port 12. The spring 3 is at least partially located in the cavity 13. One end of the spring 3 abuts against the end cap 6, and the other end abuts against the end of the valve core 2. The spring 3 can act on the valve core 2 and, through the spring force, move the valve core 2 to one side of the valve port 12 until it abuts against the valve port 12.

[0026] When the valve core 2 abuts against the valve port 12 (e.g.) Figure 1 As shown), the exhaust valve is in the closed state. When the valve core 2 disengages from the valve port 12 (as shown), Figure 2 As shown), the exhaust valve is in the open state. When fully open, the valve core 2 is away from the valve port 12. The distance between the end face of the valve core 2 and the valve port 12 is defined as the first distance L1. In the intermediate state, the distance between the end face of the valve core 2 and the valve port 12 is defined as the second distance L2. It is easy to understand that the second distance L2 is less than the first distance L1, that is, L2 <L1。

[0027] The inner peripheral wall of cavity 13 can guide valve core 2, ensuring that valve core 2 can move axially within cavity 13 and can cooperate with valve port 12 for sealing, such as Figure 1 and Figure 2 As shown, a guide gap 5 is formed between the outer peripheral wall of the valve core 2 and the inner peripheral wall of the cavity 13.

[0028] During the axial movement of the valve core 2 along the cavity 13, the balance hole 62 enables the cavity 13 to communicate with the outside. The balance hole 62 balances the air pressure inside and outside the cavity 13, ensuring smooth movement of the valve core 2.

[0029] Define the flow area of ​​valve port 12 as the first area S1 (e.g.) Figure 4 and Figure 5As shown, there is a guiding gap 5 between the valve core 2 and the peripheral side wall portion. Define the area of this guiding gap 5 as the second area S2, and the area of the balance hole 62 as the third area S3. The first area S1, the second area S2, and the third area S3 satisfy: S3 > S1, and S2 < 1.1S1.

[0030] The third area S3 should be greater than the first area S1 to ensure that the valve core 2 can move smoothly at the moment of valve opening. Also, the third area S3 should be greater than the second area S2 to facilitate the timely discharge of the gas on the side of the valve core 2 away from the valve port portion 12 and avoid causing resistance to the movement of the valve core 2.

[0031] After the valve core 2 is disengaged from the valve port portion 12, the high-pressure gas enters the cavity portion 13 through the valve port portion 12 and is exhausted through the exhaust hole 14 provided on the side wall of the valve seat 1. The valve core 2 moves in the direction away from the valve port portion 12 under the combined action of the pressure difference force and the spring force, and the spring 3 reaches the maximum compression amount. Considering the influence of the flow resistance, in this embodiment, it is set that S2 < 1.1S1 to realize the establishment of the pressure difference force on both sides of the valve core 2 after the valve core 2 is disengaged from the valve port portion 12, so as to maintain the state of the valve core 2 being disengaged from the valve port portion 12, extend the valve opening time of the exhaust valve, and further realize the intermediate state of the exhaust process of the valve port portion 12 from high pressure to low pressure, thereby reducing the adverse effects of frequent opening and closing of the valve port portion 12 caused by the internal pressure fluctuation of the system and extending the safe service life of the exhaust valve.

[0032] Specifically, when the pressure in the system is relatively high, the gas in the system can enter the valve seat 1 through the air inlet 11 and act on the valve core 2 through the valve port portion 12. When the gas pressure is greater than the spring force, the valve core 2 is disengaged from the valve port portion 12, and the exhaust valve opens. Part of the gas is discharged along the exhaust hole 14, and part of the gas is discharged through the balance hole 62 through the guiding gap 5 to relieve the pressure of the system. As the pressure relief progresses, the pressure in the system gradually decreases. When the gas pressure is less than the spring force, the spring force acts on the valve core 2 to move towards the side of the valve port portion 12 until it cooperates with the valve port portion 12, and the exhaust valve closes.

[0033] Specifically, the gas pressure at the air inlet of the exhaust valve is P×S, where P is the air inlet pressure and S is the force-bearing area of the valve core 2, and the spring force is F.

[0034] When the exhaust valve is in the closed valve state, as Figure 1 shown, the valve core 2 abuts against the valve port portion 12 under the action of the spring force F1 to achieve sealing. At this time, P0×S1 < F1, where P0 is the air inlet pressure when closing the valve, the first area S1 is the flow area of the valve port portion 12 (i.e., the force-bearing area of the valve core 2 before the exhaust valve opens), and F1 is the initial spring force.

[0035] When the internal pressure of the system increases, the gas pressure on the inlet port 11 side squeezes the valve core 2 and pushes the spring 3 to compress. When the inlet port pressure reaches the first preset value P1 (P1 > P0), the gas pressure P1×S1 on the inlet port 11 side is greater than the initial spring force F1, that is, P1×S1 > F1, and the valve core 2 disengages from the valve port part 12, and the exhaust valve opens. The first preset value P1 is the inlet port pressure at the moment of valve opening.

[0036] After the exhaust valve opens, the force-bearing area of the valve core 2 is the fourth area S4 as shown in Figure 3 Figure. The fourth area S4 is the end face area of the valve core 2 on the side facing the valve port part 12. The valve core 2 squeezes the spring 3 to compress to the maximum compression amount. At this time, the spring force of the spring 3 is F2, and the inlet port pressure reaches the second preset value P2, and P2×S4 = F2.

[0037] It should be noted that the spring 3 being compressed to the maximum compression amount does not refer to the limit compression amount that the spring 3 can withstand, but the compression amount when the spring 3 has the largest deformation during the entire valve opening process. Under normal conditions, this maximum compression amount is not greater than the limit compression amount. Of course, if the internal pressure of the system is relatively large, resulting in the maximum compression amount of the spring 3 reaching its limit compression amount during the valve opening process, the exhaust valve also remains in the open state.

[0038] After the valve core 2 disengages from the valve port part 12, the pressurized gas exhausts along the exhaust hole 14, the pressure inside the system gradually decreases, the inlet port pressure changes, and the spring force also changes with the change of the compression amount of the spring 3. Define the inlet port pressure at this time as P3. There is a dynamic balance between the gas pressure P3×S4 on the inlet port 11 side and the spring force F2, that is, P3×S4 = F2. During this process, the exhaust valve remains in the open state.

[0039] As the system pressure further decreases, the inlet port pressure further decreases. When the gas pressure decreases to the fourth preset value P4, P4×S4 < F1. At this time, the spring 3 extends to drive the valve core 2 to move to one side of the valve port part 12 to cooperate with the valve port part 12 and return to the sealed state, and the exhaust valve closes. Among them, the fourth preset value P4 is the inlet port pressure at the moment of valve closing.

[0040] When the gas pressure reaches the first preset value P1, the exhaust valve opens, and when the inlet port pressure reaches the fourth preset value P4, the exhaust valve closes. That is to say, the exhaust valve remains in the open state and continuously exhausts from the moment the inlet port pressure reaches the first preset value P1 until the gas pressure reaches the fourth preset value P4.

[0041] In this embodiment, the ratio of the first area S1 to the fourth area S4 is designed to be less than 1 / 12. The spring 3 has the same compression at the moment the exhaust valve is opened and closed, and the spring force is F1. Ignoring the influence of other factors, P1×S1=F1=P4×S4, and S1:S4<1:12, it can be concluded that under ideal conditions, P1:P4>12:1, that is, the ratio of the first preset value P1 to the fourth preset value P4 is large, that is, the pressure difference in the system is large at the moment the valve is opened and closed.

[0042] Obviously, if the ratio of the first area S1 to the fourth area S4 is less than 1 / 12, the pressure difference in the system at the moment of valve opening and valve closing will be larger. During the valve opening process, the exhaust volume will be larger, the exhaust time will be longer, and the system gas pressure drop will be larger. This ensures that the valve is closed and the exhaust stops only when the system is in a low-pressure state. This ensures that the system pressure is maintained in a stable state and also avoids the frequent opening and closing of the exhaust valve when the gas pressure in the system fluctuates within a small range. This reduces the noise and wear caused by the frequent opening and closing of the exhaust valve, thereby extending the service life of the exhaust valve.

[0043] In this embodiment, there are no restrictions on the specific values ​​of the first preset value P1, the second preset value P2, the third preset value P3 and the fourth preset value P4, nor are there any specific restrictions on the initial spring force F1 of the spring 3. The values ​​can be set according to the actual situation.

[0044] like Figure 3 As shown, the outer peripheral wall of the valve core 2 is also provided with a guide structure on the side facing the valve port 12. The guide structure and the inner side wall of the cavity 13 form a guide channel 4. When the valve core 2 and the valve port 12 are engaged, that is, when the exhaust valve is in the closed state, the guide channel 4 is connected to the exhaust hole 14.

[0045] With this configuration, at the moment the valve is opened, the exhaust channel formed by the gap between the valve port 12, the valve core 2 and the end of the cavity 13, the guide channel 4 and the exhaust hole 14 is directly connected, and the gas in the system can be directly discharged through the exhaust channel. The valve opening response time is short and the instantaneous exhaust volume is large.

[0046] Specifically, in this embodiment, the guide structure provided on the outer peripheral wall of the valve core 2 is not limited, such as... Figure 3 As shown, the outer peripheral wall of the valve core 2 may be provided with an annular step structure 21 along the circumferential direction. The annular step structure 21 and the inner peripheral wall of the cavity 13 form an annular guide channel 4. The annular guide channel 4 is connected to each exhaust hole 14. Specifically, the number of exhaust holes 14 is not limited. For example, there may be one, two, three, four or more. When the number of exhaust holes 14 is two or more, each exhaust hole 14 is evenly spaced along the circumferential direction of the cavity 13.

[0047] Alternatively, in this embodiment, the outer peripheral wall of the valve core 2 facing the valve port 12 can be configured as a conical structure, with the smaller diameter end facing the valve port 12. This conical structure forms the aforementioned guide structure, and the conical surface and the inner peripheral wall of the cavity 13 enclose each other to form an annular guide channel 4. Alternatively, the outer peripheral wall of the valve core 2 facing the valve port 12 can be provided with multiple guide grooves, each guide groove corresponding to each exhaust hole 14. The guide grooves and the inner wall of the cavity 13 can enclose each other to form independent guide channels 4. No specific limitation is made here.

[0048] By setting the guide structure as a ring-shaped stepped structure 21, the manufacturing process can be simplified. Furthermore, as... Figure 1 As shown, in the closed state, the stepped surface of the annular stepped structure 21 is located on the side of the exhaust hole 14 away from the valve port 12. That is to say, the valve core 2 does not obstruct the exhaust hole 14, and the valve core 2 is completely separated from the exhaust hole 14. This setting can increase the communication area between the guide channel 4 and the exhaust hole 14 at the moment of valve opening, and further increase the instantaneous exhaust volume at the moment of valve opening.

[0049] Of course, in the closed state, the stepped surface can be located on the side of the exhaust hole 14 facing the valve port 12, or in the closed state, the stepped surface can be located in the middle of the exhaust hole 14, that is, the valve core 2 can partially block the exhaust hole 14. When the stepped surface is set to be located on the side of the exhaust hole 14 away from the valve port 12 in the closed state, it can avoid the valve core 2 from contacting the end face of the exhaust hole 14, and avoid the burrs generated by the exhaust hole 14 during the processing from affecting the movement of the valve core 2, thereby reducing the processing requirements.

[0050] like Figure 3 As shown, the valve core 2 has a sealing groove 22 on the side facing the valve port 12, and a sealing element 23 is fixed in the sealing groove 22. The sealing element 23 is used to cooperate with the valve port 12. The valve core 2 can be made of stainless steel or other metal materials to ensure structural strength and stability, and the sealing element 23 can be made of rubber to cooperate with the valve port 12 to ensure sealing performance.

[0051] The specific structure of the sealing groove 22 is not limited, such as Figure 3 As shown, the opening end of the sealing groove 22 has a constricted structure. During installation, the sealing element 23 is deformed by compression and enters the sealing groove 22, where it is press-fitted with the sealing groove 22. Due to the restriction of the constricted structure, it will not detach from the valve core. Furthermore, the overall structure is simple and the installation operation is relatively convenient. Of course, the sealing element 23 and the valve core 2 can also be fixed by means of bonding, fastener connection, etc.

[0052] like Figure 3As shown, the valve core 2 is also provided with a positioning groove 24 on the side away from the sealing groove 22. The end of the spring 3 facing the valve port 12 is located in the positioning groove 24. The positioning groove 24 can provide positioning for the installation of the spring 3. At the same time, the groove wall of the positioning groove 24 can also provide guidance for the extension and contraction of the spring 3, so as to prevent the spring 3 from bending during compression.

[0053] like Figure 4 and Figure 5 As shown, the valve seat 1 is provided with the above-mentioned air inlet 11, the above-mentioned valve port 12 and the groove 15 arranged in sequence. The end cap 6 can be fixed to the valve seat 1 and seal the groove 15. The end cap 6 can be enclosed with the groove 15 to form the above-mentioned cavity 13.

[0054] Of course, the end cap 6 can also be provided with a groove and fixedly enclosed with the valve seat 1 to form the cavity 13 mentioned above; no specific limitation is made here. When the valve seat 1 is provided with a groove 15 and the end cap 6 is fixed to the valve seat 1, the processing technology can be simplified.

[0055] Specifically, the end cap 6 and the valve seat 1 are circumferentially sealed and fixed, which can be achieved by welding or threaded connection, making installation relatively convenient. Of course, other methods can also be used for fixing, such as using fasteners and achieving a seal with a circumferentially positioned sealing gasket.

[0056] like Figure 4 As shown, the end cap 6 is provided with a groove structure 61, which is used to install the end of the spring 3 away from the valve port 12. The groove wall of the groove structure 61 can provide guidance for the extension and contraction of the spring 3, so as to prevent the spring 3 from bending during compression.

[0057] In this embodiment, both the valve seat 1 and the spring 3 can be made of stainless steel. Specifically, both the valve seat 1 and the end cap 6 are made of stainless steel.

[0058] The above are merely preferred embodiments of this application. It should be noted that those skilled in the art can make various improvements and modifications without departing from the principles of this application, and these improvements and modifications should also be considered within the scope of protection of this application.

Claims

1. An exhaust valve, characterized in that, It includes a valve seat (1), a valve core (2), a spring (3) and an end cap (6), wherein the end cap (6) is provided with a balance hole (62); The valve seat (1) is provided with an air inlet (11) and a valve port (12). The end cap (6) is fixedly connected or limitedly connected to the valve seat (1) and surrounds it to form a cavity (13). The peripheral sidewall of the cavity (13) is provided with an exhaust hole (14). The valve core (2) is slidably disposed in the cavity (13). The spring (3) is at least partially located in the cavity (13). The valve core (2) can move axially to approach or move away from the valve port (12). One end of the spring (3) abuts against the end cap (6), and the other end of the spring (3) abuts against the valve core (2). The operation includes at least the following states: in the fully closed state, the valve core (2) abuts against the valve port (12); in the fully open state, the valve core (2) moves away from the valve port (12), and the distance between the end face of the valve core (2) and the valve port (12) is defined as the first distance L1; in the intermediate state, the distance between the end face of the valve core (2) and the valve port (12) is defined as the second distance L2, where L2 <L1; The flow area of ​​the valve port (12) is defined as the first area S1; there is a guide gap (5) between the valve core (2) and the peripheral side wall, the area of ​​the guide gap (5) is defined as the second area S2, and the area of ​​the balance hole (62) is defined as the third area S3; satisfying S3>S1 and S2<1.1S1.

2. The exhaust valve according to claim 1, characterized in that, The end face area of ​​the valve core (2) facing the valve port (12) is the fourth area S4, and the ratio of the first area S1 to the fourth area S4 is less than 1 / 12.

3. The exhaust valve according to claim 1, characterized in that, The outer peripheral wall of the valve core (2) is provided with a guide structure on the side facing the valve port (12). The guide structure and the inner peripheral wall form a guide channel (4). When the valve core (2) and the valve port (12) are engaged, the guide channel (4) is connected to the exhaust hole (14).

4. The exhaust valve according to claim 3, characterized in that, The outer peripheral wall of the valve core (2) is provided with an annular step structure (21) along the circumferential direction, and the annular step structure (21) forms the guide structure.

5. The exhaust valve according to claim 4, characterized in that, When the valve core (2) is engaged with the valve port (12), the stepped surface of the annular stepped structure (21) is located on the side of the exhaust hole (14) away from the valve port (12).

6. The exhaust valve according to any one of claims 1-5, characterized in that, The valve core (2) has a sealing groove (22) on one side facing the valve port (12), and a sealing element (23) is fixedly provided in the sealing groove (22). The sealing element (23) is used to cooperate with the valve port (12).

7. The exhaust valve according to claim 6, characterized in that, The valve core (2) is provided with a positioning groove (24) on the side away from the sealing groove (22). One end of the spring (3) is located in the positioning groove (24) and abuts against the bottom wall of the positioning groove (24).

8. The exhaust valve according to any one of claims 1-5, characterized in that, The valve seat (1) is also provided with a groove (15), and the end cap (6) is fixed to the valve seat (1) and surrounds the groove (15) to form the cavity (13).

9. The exhaust valve according to claim 8, characterized in that, The end cap (6) is provided with a groove structure (61), and one end of the spring (3) is located in the groove structure (61).

10. The exhaust valve according to claim 9, characterized in that, The end cap (6) is fixed to the valve seat (1) by welding or by thread connection.

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