A compressor gas valve suitable for multiple working conditions

Abstract

The present invention discloses a compressor gas valve adapted to multiple working conditions, comprising: a valve seat, a valve body and a gland that are detachably connected from top to bottom, and a gas cavity is formed between the three; an air intake channel connected to the gas cavity is provided on the valve seat; an exhaust channel connected to the gas cavity is provided on the valve body or the gland; a lift limiter is arranged between the valve body and the gland, and the lift limiter is wholly or partially located inside the valve body and can slide along the inner wall of the valve body; a hydraulic cavity is formed between the end of the lift limiter facing the gland and the gland; a valve core is arranged in the gas cavity and can move up and down, and a spring is provided at the bottom of the valve core, and the valve core moves upward under the rebound force of the spring until the air intake channel is closed. The present invention is applied to scenes with multiple working conditions, and can effectively improve the working performance of the gas valve and increase the life of the gas valve.

Description

Technical Field

[0001] The present invention relates to the field of compressor valves, and more particularly to a compressor valve adaptable to multiple working conditions. Background Art

[0002] The natural gas or hydrogen substation adopts the mode of transporting gas by tank trucks. The pressure of the tank trucks is usually 20MPa. As the tank trucks continue to unload gas, the output gas pressure gradually decreases. Therefore, the gas source pressure of the tank truck input compressor is constantly changing, which is a wide range of intake conditions. As the intake pressure changes, the exhaust pressure remains unchanged, the pressure ratio of the compressor will change, and the amount of gas discharged will change. Therefore, the intake and exhaust valves of the compressor need to adapt to this wide range of intake conditions. Most of the existing compressor valves use automatic valves, such as annular valves, mesh valves, mushroom valves, etc. When designing, the intermediate air pressure ratio condition is usually selected as the design condition, and the valve core lift and spring parameters are designed accordingly. When used, they automatically adapt to the intake and exhaust conditions. However, the lift and spring parameters of this type of valve are fixed. When the intake pressure is much lower than the design point, the exhaust valve is prone to flutter. When it is much higher than the design point, the exhaust valve response speed is reduced, and the impact is large when the valve core is seated. Summary of the invention

[0003] An object of the present invention is to solve at least the above problems and to provide at least the advantages which will be described hereinafter.

[0004] In order to achieve these purposes and other advantages according to the present invention, a compressor gas valve adapting to multiple working conditions is provided, comprising:

[0005] The valve seat, valve body and gland are detachably connected from top to bottom, and a gas cavity is formed between the three; the valve seat is provided with an air inlet channel connected to the gas cavity; the valve body or the gland is provided with an exhaust channel connected to the gas cavity;

[0006] A lift limiter is arranged between the valve body and the gland, the lift limiter is wholly or partially located inside the valve body and can slide along the inner wall of the valve body; a hydraulic chamber is formed between the end of the lift limiter facing the gland and the gland;

[0007] A valve core is disposed in the gas cavity and can move up and down, and the valve core is located above the lift limiter. A spring is disposed at the bottom of the valve core, and the valve core moves upward under the rebound force of the spring until the intake passage is closed;

[0008] By adjusting the amount of hydraulic oil in the hydraulic chamber, the lift limiter is driven to slide, and the distance between the lift limiter and the valve seat is adjusted to adjust the air flow speed entering the valve gap, where the valve gap is the gap between the valve core and the bottom of the valve seat.

[0009] Preferably, it also includes: an intake channel sensor, a PLC controller, a flow regulating valve and an oil tank; the intake channel sensor and the flow regulating valve are respectively connected to the PLC controller; the intake channel sensor is arranged at the entrance of the intake channel to measure the intake pressure and the intake temperature; the flow regulating valve is respectively connected to the hydraulic chamber and the oil tank through pipelines to adjust the amount of hydraulic oil in the hydraulic chamber.

[0010] Preferably, the intake passage sensor includes an air pressure sensor and a temperature sensor.

[0011] Preferably, when the lift limiter is entirely located inside the valve body, the cross-section of the valve body is annular, the pressure cover is arranged at the inner bottom of the valve body, and the top surface of the pressure cover, the inner wall of the valve body and the bottom surface of the valve seat together form the gas cavity; a boss is arranged at the center of the top surface of the pressure cover, and a first annular groove is provided on the boss; the shape of the lift limiter matches the shape of the first groove, and can slide up and down along the first groove, and the bottom surface of the lift limiter and the first groove together form the hydraulic cavity; the side wall of the valve body is provided with a liquid inlet and a liquid outlet, and the liquid inlet and the liquid outlet are connected to the hydraulic cavity directly or through a pipeline.

[0012] Preferably, a first mounting groove is downwardly opened on the top surface of the boss, and the diameter of the first mounting groove is smaller than the inner diameter of the first groove; one end of the spring is fixed in the first mounting groove, and the other end is fixedly connected to the valve core; a plurality of exhaust channels are arranged on the pressure cover; a central exhaust channel is arranged at the center of the pressure cover, and the central exhaust channel is connected to the first mounting groove.

[0013] Preferably, there are two flow control valves, namely an inlet flow control valve and an outlet flow control valve; the inlet flow control valve and the outlet flow control valve are respectively connected to the inlet and outlet of the valve body through pipelines, and a flow sensor and a one-way valve are provided between the inlet flow control valve and the inlet and between the outlet flow control valve and the outlet, and the flow sensor is connected to the PLC controller.

[0014] Preferably, when the lift limiter is partially located inside the valve body, a second groove is downwardly provided at one end of the valve body close to the valve seat, the second groove and the bottom surface of the valve seat together form a gas cavity, and the inner bottom surface of the second groove is downwardly provided with two through grooves; the lift limiter includes a base, and two slide posts matching the through grooves are provided on the top surface of the base, and the upper ends of the slide posts extend into the gas cavity through the through grooves; a third groove is upwardly provided on the bottom surface of the base; the pressure cover includes a bottom cover and a connecting The connecting screw is a bottom cover that is detachably connected to the base, and the bottom cover and the third groove together form the hydraulic chamber; one end of the connecting screw passes through the bottom cover, the hydraulic chamber and the base in sequence and is fixedly connected to the valve body; a fixed sleeve is provided with a partition on the part of the connecting screw located in the hydraulic chamber, and the partition divides the hydraulic chamber into an upper hydraulic chamber and a lower hydraulic chamber that are not connected to each other, an upper hydraulic oil port that is connected to the upper hydraulic chamber is provided on the base, and a lower hydraulic oil port that is connected to the lower hydraulic chamber is provided on the bottom cover.

[0015] Preferably, the diameter of the valve core is greater than the distance between the two through grooves; a second mounting groove is downwardly opened on the inner bottom surface of the second groove, one end of the spring is fixed in the second mounting groove, and the other end is fixedly connected to the valve core; and a plurality of exhaust channels are arranged on the valve body.

[0016] Preferably, the flow control valve is connected to the upper hydraulic oil port and the lower hydraulic oil port through pipelines respectively, a flow sensor is provided between the flow control valve and the upper hydraulic oil port, and the flow sensor is connected to the PLC controller.

[0017] Preferably, a guide groove is opened upward on the bottom surface of the valve seat corresponding to the position of the valve core, the diameter of the guide groove is larger than the diameter of the valve core, and the air inlet channel is connected to the guide groove; a plurality of semicircular grooves are opened upward on the bottom surface of the valve seat, and the semicircular grooves are connected to the guide groove.

[0018] The present invention has at least the following beneficial effects:

[0019] The compressor valve adapted to multiple working conditions provided by the present invention realizes control of the valve lift by arranging a hydraulic chamber at the bottom of the lift limiter and adjusting the distance between the lift limiter and the valve seat by controlling the amount of hydraulic oil in the hydraulic chamber; that is, the position of the lift limiter is adjusted according to changes in the intake pressure or temperature to change the air flow velocity entering the valve gap, so that the valve core works at the optimal performance position, avoiding exhaust valve flutter and valve core impact, improving the valve working performance, and increasing the valve life.

[0020] Other advantages, objectives and features of the present invention will be embodied in part through the following description, and in part will be understood by those skilled in the art through study and practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 It is a structural schematic diagram of the gas valve when the lift limiter in the present invention is completely located inside the valve body;

[0022] Figure 2 for Figure 1 Schematic diagram of the AA section structure;

[0023] Figure 3 for Figure 1 Schematic diagram of the BB cross-section structure;

[0024] Figure 4 is a structural schematic diagram of the lift limiter in the present invention when the lift limiter is completely located inside the valve body;

[0025] Figure 5 It is a structural schematic diagram of the gas valve when the lift limiter part of the present invention is located inside the valve body;

[0026] Figure 6 for Figure 5 Schematic diagram of the CC cross-section structure;

[0027] Figure 7 for Figure 5 Schematic diagram of the DD cross-section structure;

[0028] Figure 8 It is a connection schematic diagram of the flow control valve when the lift limiter in the present invention is completely located inside the valve body;

[0029] Fig. 9 It is a connection schematic diagram of the flow control valve when the lift limiter part of the present invention is located inside the valve body; DETAILED DESCRIPTION

[0030] The present invention is further described in detail below in conjunction with the accompanying drawings so that those skilled in the art can implement the invention with reference to the description.

[0031] It should be noted that the experimental methods described in the following embodiments are conventional methods unless otherwise specified, and the reagents and materials are commercially available unless otherwise specified; in the description of the present invention, the terms "lateral", "longitudinal", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0032] like Figures 1 to 9 As shown, the present invention provides a compressor valve adapted to multiple working conditions, characterized in that it includes:

[0033] The valve seat 4, the valve body 3 and the gland 1 are detachably connected from top to bottom, and a gas cavity 9 is formed between the three; the valve seat 4 is provided with an air inlet channel 6 connected with the gas cavity 9; the valve body 3 or the gland 1 is provided with an air exhaust channel 21 connected with the gas cavity 9;

[0034] A lift limiter 5 is arranged between the valve body 3 and the gland 1. The lift limiter 5 is entirely or partially located inside the valve body 3 and can slide along the inner wall of the valve body 3. A hydraulic chamber 17 is formed between one end of the lift limiter 5 facing the gland 1 and the gland 1.

[0035] A valve core 7 is disposed in the gas cavity 9 and can move up and down, and the valve core 7 is located above the lift limiter 5. A spring 8 is disposed at the bottom of the valve core 7. The valve core 7 moves upward under the rebound force of the spring 8 until the intake channel 7 is closed;

[0036] By adjusting the amount of hydraulic oil in the hydraulic chamber 17, the lift limiter 5 is driven to slide, and the distance between the lift limiter 5 and the valve seat 4 is adjusted to adjust the air flow speed entering the valve gap, and the valve gap is the gap between the valve core 7 and the bottom of the valve seat 4.

[0037] In this technical solution, in the gas cavity 9, the valve core 7 is located between the valve seat 4 and the lift limiter 5. When the thrust of the airflow entering through the intake channel 6 is greater than the rebound force of the spring 8, the airflow will push the valve core 7 to move in the direction of the lift limiter 5 and leave the intake channel 6. At this time, the air valve is opened, and the airflow enters the gas cavity 9 and is discharged from the exhaust channel 21. When the air valve is open, when the thrust of the incoming airflow is large enough, the valve core 7 will eventually be pressed against the lift limiter 5. Therefore, the distance between the lift limiter 5 and the valve seat 4 is the moving range of the valve core 7, that is, the lift limit value of the valve core 7. When the thrust of the incoming airflow is less than the rebound force of the spring 8, the valve core 7 gradually moves toward the valve seat 4 under the action of this rebound force, and finally presses against the valve seat 4. At this time, the valve core 7 closes the intake channel 6.

[0038] Considering that the movement state of the valve core 7 depends on the combined effect of the rebound force of the spring 8 and the airflow thrust. g =βa p Δp v , where β is the thrust coefficient, which is related to the valve structure; a p is the flow area at the valve seat outlet; Δp v It is the pressure drop of gas when it flows through the valve gap. Where ρ is the gas density flowing through the valve gap; u t is the instantaneous flow rate of the gas in the valve gap. When the intake pressure becomes higher, the intake density ρ becomes larger, the pressure drop increases, and the airflow thrust becomes larger. At this time, the lift limit value of the valve core 7 should be increased, the airflow velocity should be reduced, thereby reducing the pressure drop, and avoiding a large impact force when the valve core 7 is seated. When the intake pressure becomes lower, the intake density ρ becomes smaller, the pressure drop decreases, and the airflow thrust decreases. At this time, the lift limit value of the valve core 7 should be reduced, the airflow velocity should be increased, thereby increasing the pressure drop, and avoiding valve flutter. Therefore, a hydraulic chamber 17 is formed between the end of the lift limiter 5 facing the pressure cover 1 and the pressure cover 1. When the intake pressure becomes higher, the amount of hydraulic oil in the hydraulic chamber 17 is reduced, so that the lift limiter 5 slides in the direction away from the valve seat 4, the position of the lift limiter 5 is lowered, and the distance between the lift limiter 5 and the valve seat 4 is increased, thereby increasing the up and down movement range of the valve core 7, that is, increasing the lift limit value of the valve core 7 and reducing the air flow speed; when the intake pressure becomes lower, the amount of hydraulic oil in the hydraulic chamber 17 is increased, so that the lift limiter 5 slides in the direction of the valve seat 4, the position of the lift limiter 5 is increased, and the distance between the lift limiter 5 and the valve seat 4 is reduced, thereby reducing the up and down movement range of the valve core 7, that is, reducing the lift limit value of the valve core 7 and increasing the air flow speed.

[0039] Similarly, when the temperature of the airflow entering from the intake passage 6 changes, it will also cause the air valve to vibrate or generate a large impact force when the valve core is seated. Therefore, the position of the lift limiter 5 can be adjusted according to the change of the temperature of the incoming airflow, and then the lift limit value of the valve core 7 can be adjusted to make the valve core 7 work at the best performance position.

[0040] In another embodiment, the compressor air valve adaptable to multiple working conditions also includes: an intake channel sensor 24, a PLC controller 25, a flow regulating valve 28 and an oil tank 30; the intake channel sensor 24 and the flow regulating valve 28 are respectively connected to the PLC controller 25; the intake channel sensor 24 is at the entrance of the intake channel 6, for measuring the intake pressure and the intake temperature; the flow regulating valve 28 is respectively connected to the hydraulic chamber 17 and the oil tank 30 through pipelines, for adjusting the amount of hydraulic oil in the hydraulic chamber 17.

[0041] In this technical solution, the PLC controller 23 receives the intake pressure and intake temperature values ​​measured by the intake passage sensor 29, calculates the difference between the intake pressure and intake temperature and the design value, calculates the lift adjustment amount of the lift limiter 5, and converts the lift adjustment amount into a flow signal and transmits it to the flow control valve 24, and then controls the amount of hydraulic oil entering or discharged from the hydraulic chamber 17 through the flow control valve 24, thereby adjusting the position of the lift limiter 5. Considering that the lift of the valve core 7 is relatively small, the position of the lift limiter 5 is not continuously adjusted. The lift adjustment amount is calculated The adjustment is made only when the lift change is above 0.2mm. Where ΔH is the lift adjustment amount, p t is the measured intake pressure, p s is the design point inlet pressure, H s is the design lift, T s is the design point inlet temperature, T t To measure the intake air temperature. Preferably, a booster pump 29 is provided at the oil outlet of the oil tank 30 so as to pump the hydraulic oil from the oil tank 30 into the flow control valve 28 and then into the hydraulic chamber 17. Furthermore, the intake passage sensor 29 includes an air pressure sensor 241 and a temperature sensor 242. The intake pressure of the intake passage 6 is measured by the pressure sensor 241, and the intake temperature of the intake passage 6 is measured by the temperature sensor 242.

[0042] In another embodiment, referring to Figure 1 to Figure 3When the lift limiter 5 is completely located inside the valve body 3, the cross-section of the valve body 3 is annular, the gland 1 is arranged at the inner bottom of the valve body 3, and the top surface of the gland 1, the inner wall of the valve body 3 and the bottom surface of the valve seat 4 together form the gas cavity 9; a boss 14 is arranged at the center of the top surface of the gland 1, and a first annular groove 20 is opened on the boss 14; the shape of the lift limiter 5 matches the shape of the first groove 20, and can slide up and down along the first groove 20, and the bottom surface of the lift limiter 5 and the first groove 20 together form the hydraulic cavity 17; a liquid inlet 2 and a liquid outlet 13 are opened on the side wall of the valve body 3, and the liquid inlet 2 and the liquid outlet 13 are directly or through a pipeline connected to the hydraulic cavity 17.

[0043] In this technical solution, when the position of the lift limiter 5 needs to be raised, hydraulic oil is injected into the hydraulic chamber 17 from the liquid inlet 2 to lift the lift limiter 5 upward; when the lift limiter 5 needs to be lowered, the hydraulic oil is discharged from the liquid outlet 13, and the lift limiter 5 then descends under the action of gravity. Preferably, in order to facilitate the direct communication between the liquid inlet 2 and the liquid outlet 13 and the hydraulic chamber 17, improve the stability of the lift limiter 5, and increase the contact area between the lift limiter 5 and the valve core 7, protrusions 18 extending to the inner wall of the valve body 3 may be respectively provided on both sides of the boss 14; rectangular grooves are provided on the protrusions 18 on both sides, and annular grooves are provided on the boss 14, and the annular grooves are respectively connected with the rectangular grooves on both sides to form the first grooves 20; at this time, the cross-sectional shape of the first groove 20 and the lift limiter 5 Figure 4 As shown, at this time, the lift limiter 5 slides up and down along the inner wall of the valve body 3 and the outer wall of the boss 14. The bottom of the lift limiter 5 is provided with a seal 12 on the side in contact with the boss 14 and the side in contact with the inner wall of the valve body 3, and a seal 12 is also provided between the gland 1 and the inner wall of the valve body 3.

[0044] In order to prevent the lift limiter 5 from being pushed out of the first groove 20 under the action of hydraulic pressure in an unexpected situation, an inner flange 10 extending horizontally into the groove can be provided at the top of the first groove 20, and an outer flange 11 extending horizontally outward can be provided at the bottom of the lift limiter 5, so that the lift limiter 5 stops when its outer flange 11 presses against the inner flange 10 and no longer continues to rise.

[0045] In another embodiment, the top surface of the boss 14 is provided with a first mounting groove 15 downwardly, and the diameter of the first mounting groove 15 is smaller than the inner diameter of the first groove 20; one end of the spring 8 is fixed in the first mounting groove 15, and the other end is fixedly connected to the valve core 7; a plurality of exhaust channels 21 are provided on the gland 1; a central exhaust channel 16 is provided at the center of the gland 1, and the central exhaust channel 16 is connected to the first mounting groove 15. In this technical solution, the exhaust channel 21 passes vertically downward from the top surface of the gland 1 to the bottom of the gland 1, and preferably, the plurality of exhaust channels 21 are provided in the area outside the boss 14.

[0046] In another embodiment, referring to Figure 8 There are two flow control valves 28, which are an inlet flow control valve and an outlet flow control valve respectively; the inlet flow control valve and the outlet flow control valve are respectively connected to the inlet 2 and the outlet 13 of the valve body 3 through pipelines, and a flow sensor 27 and a one-way valve 26 are provided between the inlet flow control valve and the inlet 2 and between the outlet flow control valve and the outlet 13, and the flow sensor 27 is connected to the PLC controller 25.

[0047] In this technical solution, the PLC controller 25 sends instructions to the inlet flow control valve and the outlet flow control valve respectively, and measures the amount of hydraulic oil flowing into and out of the hydraulic chamber 17 through the flow sensor 27, and feeds back to the PLC controller 25, recording the current lift adjustment amount ΔH. i Considering that ΔH is the lift adjustment relative to the design point, when the lift is adjusted next time, the actual lift adjustment amount ΔH i+1 =ΔH-ΔH i , where ΔH is the p measured next time t and T t The one-way valve 26 ensures that the hydraulic oil can only flow into the hydraulic chamber 17 from the liquid inlet 2 and can only flow out of the hydraulic chamber 17 from the liquid outlet 13 .

[0048] In another embodiment, referring to Figure 5 to Figure 7, when the lift limiter 5 is partially located inside the valve body 3, a second groove is downwardly provided at one end of the valve body 3 close to the valve seat 4, the second groove and the bottom surface of the valve seat 4 enclose the gas cavity 9, and two through grooves are downwardly provided on the inner bottom surface of the second groove; the lift limiter 5 includes a base 51, and two slide posts 52 matching the through grooves are provided on the top surface of the base 51, and the upper ends of the slide posts 52 pass through the through grooves and extend into the gas cavity 9; a third groove is upwardly provided on the bottom surface of the base 51; the gland 1 includes a bottom cover 101 and a connecting screw 102, and the bottom cover 101 and the base 5 1 is detachably connected, and the bottom cover 101 and the third groove together form the hydraulic chamber 17; one end of the connecting screw 102 passes through the bottom cover 101, the hydraulic chamber 17 and the base 51 in sequence and is fixedly connected to the valve body 3; the part of the connecting screw 102 located in the hydraulic chamber 17 is fixedly sleeved with a partition 104, and the partition 104 divides the hydraulic chamber 17 into an upper hydraulic chamber 171 and a lower hydraulic chamber 172 that are not connected to each other, the base 51 is provided with an upper hydraulic oil port 53 connected to the upper hydraulic chamber 171, and the bottom cover 101 is provided with a lower hydraulic oil port 103 connected to the lower hydraulic chamber 172.

[0049] In this technical solution, when it is necessary to increase the position of the lift limiter 5, hydraulic oil is injected from the upper hydraulic oil port 53 into the upper hydraulic chamber 171 to lift the lift limiter 5 upward, and the two slide posts 52 move upward along the through groove, so that the distance between the top surface of the slide post 52 and the valve seat 4 becomes smaller, and the base 51 and the bottom cover 101 slide upward along the connecting bolt 102 to discharge the hydraulic oil in the lower hydraulic chamber 172 from the lower hydraulic oil port 103; when it is necessary to lower the position of the lift limiter 5, hydraulic oil is injected from the lower hydraulic oil port 103 into the lower hydraulic chamber 172 to discharge the hydraulic oil in the upper hydraulic chamber 171 from the upper hydraulic oil port 53, and the base 51 and the bottom cover 101 slide downward along the connecting bolt 102, and the two slide posts 52 move downward along the through groove to lower the lift limiter 5, so that the distance between the top surface of the slide post 52 and the valve seat 4 becomes larger. A fastening nut 23 is also provided at the connection between the connecting screw 102 and the valve body 3. Similarly, a seal 12 is provided at the contact between the sliding column 52 and the inner wall of the through groove, and a seal 12 is provided at the contact between the base 51 and the bottom cover 101, at the contact between the base 51 and the connecting bolt 102, and at the contact between the bottom cover 101 and the connecting bolt 102.

[0050] In order to avoid the lift limiter 5 moving upward more under the action of hydraulic pressure in an unexpected situation, making the movement range of the valve core 7 too small, an inner flange 10 extending horizontally into the groove can be provided at the top of the through groove, and an outer flange 11 extending horizontally outward can be provided on the slide column 52, so that the lift limiter 5 stops when its outer flange 11 presses against the inner flange 10 and no longer continues to rise.

[0051] In another embodiment, the diameter of the valve core 7 is greater than the distance between the two through grooves; a second mounting groove 22 is downwardly opened on the inner bottom surface of the second groove, one end of the spring 8 is fixed in the second mounting groove 22, and the other end is fixedly connected to the valve core 7; and a plurality of exhaust passages 21 are arranged on the valve body 3.

[0052] In this technical solution, when the valve core 7 moves downward, the two slide posts 52 can simultaneously support the valve core 7. The exhaust passage 21 vertically penetrates downward from the inner bottom surface of the second groove to the bottom of the valve body 3. Preferably, a plurality of exhaust passages 21 are arranged in an area outside the through groove and the second mounting groove 22.

[0053] In another embodiment, referring to Fig. 9 The flow control valve 28 is connected to the upper hydraulic oil port 53 and the lower hydraulic oil port 103 through pipelines respectively. A flow sensor 27 is arranged between the flow control valve 28 and the upper hydraulic oil port 53. The flow sensor 27 is connected to the PLC controller 25.

[0054] In this technical solution, the PLC controller 25 sends a command to the flow control valve to inject hydraulic oil into the upper hydraulic chamber 171 or the lower hydraulic chamber 172, and the amount of hydraulic oil flowing into and out of the upper hydraulic chamber 171 is measured by the flow sensor 27 and fed back to the PLC controller 25 to record the lift adjustment amount ΔH currently made. i Considering that ΔH is the lift adjustment relative to the design point, when the lift is adjusted next time, the actual lift adjustment amount ΔH i+1 =ΔH-ΔH i , at this time ΔH is based on the next measured p t and T t Calculated lift adjustment.

[0055] In another embodiment, a guide groove 41 is opened upward on the bottom surface of the valve seat 4 corresponding to the position of the valve core 7, the diameter of the guide groove 41 is larger than the diameter of the valve core 7, and the air inlet channel 6 is connected to the guide groove 41; a plurality of semicircular grooves 19 are opened upward on the bottom surface of the valve seat, and the semicircular grooves 19 are connected to the guide groove 41.

[0056] In this technical solution, the guide groove 41, the valve core 7 and the air inlet passage 6 are coaxially arranged, and the guide groove 41 is used to guide the valve core 7 so that the valve core 7 can accurately close the air inlet passage 6 under the rebound force of the spring 8, so the diameter of the guide groove 41 only needs to be slightly larger than the diameter of the valve core 7. When the thrust of the incoming airflow is slightly larger than the rebound force of the spring 8, the valve core 7 can only move down a very small distance. At this time, the gap between the top surface of the valve core 7 and the inner top surface of the guide groove 41 is small, and the gap between the side wall of the valve core 7 and the side wall of the guide groove 41 is also small. It is difficult for the airflow to enter the gas cavity 9 through this gap. Therefore, the flow area of ​​the airflow between the valve core 7 and the guide groove 41 is increased by a plurality of the semicircular grooves 19, so that the airflow can smoothly enter the gas cavity 9.

[0057] Although the embodiments of the present invention have been disclosed as above, they are not limited to the applications listed in the specification and the implementation modes, and they can be fully applied to various fields suitable for the present invention. For those familiar with the art, additional modifications can be easily implemented. Therefore, without departing from the general concept defined by the claims and the scope of equivalents, the present invention is not limited to the specific details and the illustrations shown and described herein.

Claims

1. A compressor valve adapted to multiple working conditions, characterized in that: include: The valve seat, valve body and gland are detachably connected from top to bottom, and a gas cavity is formed between the three; the valve seat is provided with an air inlet channel connected to the gas cavity; the valve body or the gland is provided with an exhaust channel connected to the gas cavity; A lift limiter is arranged between the valve body and the gland, the lift limiter is wholly or partially located inside the valve body and can slide along the inner wall of the valve body; a hydraulic chamber is formed between the end of the lift limiter facing the gland and the gland; A valve core is disposed in the gas cavity and can move up and down, and the valve core is located above the lift limiter. A spring is disposed at the bottom of the valve core, and the valve core moves upward under the rebound force of the spring until the intake passage is closed; By adjusting the amount of hydraulic oil in the hydraulic chamber, the lift limiter is driven to slide, and the distance between the lift limiter and the valve seat is adjusted to adjust the air flow velocity entering the valve gap, where the valve gap is the gap between the valve core and the bottom of the valve seat; It also includes: an air intake passage sensor, a PLC controller, a flow regulating valve and a fuel tank; the air intake passage sensor and the flow regulating valve are respectively connected to the PLC controller; The intake passage sensor is arranged at the entrance of the intake passage to measure the intake pressure and intake temperature; the flow regulating valve is connected to the hydraulic chamber and the oil tank respectively through pipelines to adjust the amount of hydraulic oil in the hydraulic chamber; When the lift limiter is entirely located inside the valve body, the cross-section of the valve body is annular, the pressure cover is arranged at the inner bottom of the valve body, and the top surface of the pressure cover, the inner wall of the valve body and the bottom surface of the valve seat together form the gas cavity; a boss is arranged at the center of the top surface of the pressure cover, and a first annular groove is provided on the boss; the shape of the lift limiter matches the shape of the first groove, and can slide up and down along the first groove, and the bottom surface of the lift limiter and the first groove together form the hydraulic cavity; the side wall of the valve body is provided with a liquid inlet and a liquid outlet, and the liquid inlet and the liquid outlet are connected to the hydraulic cavity directly or through a pipeline.

2. The compressor gas valve adapted to multiple working conditions as claimed in claim 1, characterized in that: The intake passage sensor includes an air pressure sensor and a temperature sensor.

3. The compressor valve adapted to multiple working conditions as claimed in claim 1, characterized in that: A first mounting groove is downwardly opened on the top surface of the boss, and the diameter of the first mounting groove is smaller than the inner diameter of the first groove; one end of the spring is fixed in the first mounting groove, and the other end is fixedly connected to the valve core; a plurality of exhaust channels are arranged on the pressure cover; a central exhaust channel is arranged at the center of the pressure cover, and the central exhaust channel is connected to the first mounting groove.

4. The compressor gas valve adapted to multiple working conditions as claimed in claim 1, characterized in that: There are two flow control valves, namely an inlet flow control valve and an outlet flow control valve; the inlet flow control valve and the outlet flow control valve are respectively connected to the inlet and outlet of the valve body through pipelines, and a flow sensor and a one-way valve are arranged between the inlet flow control valve and the inlet, and between the outlet flow control valve and the outlet, and the flow sensor is connected to the PLC controller.

5. The compressor gas valve adapted to multiple working conditions as claimed in claim 1, characterized in that: When the lift limiter is partially located inside the valve body, a second groove is downwardly provided at one end of the valve body close to the valve seat, the second groove and the bottom surface of the valve seat are combined to form a gas cavity, and two through grooves are downwardly provided on the inner bottom surface of the second groove; the lift limiter includes a base, and two slide posts matched with the through grooves are provided on the top surface of the base, and the upper ends of the slide posts extend into the gas cavity through the through grooves; a third groove is upwardly provided on the bottom surface of the base; the pressure cover includes a bottom cover and a connecting screw, the bottom cover is detachably connected to the base, and the bottom cover and the third groove jointly form the hydraulic cavity; one end of the connecting screw passes through the bottom cover, the hydraulic cavity and the base in sequence and is fixedly connected to the valve body; a partition is fixedly provided on the part of the connecting screw located in the hydraulic cavity, and the partition divides the hydraulic cavity into an upper hydraulic cavity and a lower hydraulic cavity that are not connected to each other, an upper hydraulic oil port connected to the upper hydraulic cavity is provided on the base, and a lower hydraulic oil port connected to the lower hydraulic cavity is provided on the bottom cover.

6. The compressor gas valve adapted to multiple working conditions as claimed in claim 5, characterized in that: The diameter of the valve core is greater than the distance between the two through grooves; a second mounting groove is downwardly opened on the inner bottom surface of the second groove, one end of the spring is fixed in the second mounting groove, and the other end is fixedly connected to the valve core; a plurality of exhaust channels are arranged on the valve body.

7. The compressor valve adapted to multiple working conditions as claimed in claim 5, characterized in that: The flow control valve is connected to the upper hydraulic oil port and the lower hydraulic oil port through pipelines respectively. A flow sensor is arranged between the flow control valve and the upper hydraulic oil port, and the flow sensor is connected to the PLC controller.

8. The compressor valve adapted to multiple working conditions as claimed in claim 1, characterized in that: A guide groove is provided on the bottom surface of the valve seat upwardly corresponding to the position of the valve core, the diameter of the guide groove is larger than the diameter of the valve core, and the air inlet channel is connected to the guide groove; a plurality of semicircular grooves are provided on the bottom surface of the valve seat upwardly, and the semicircular grooves are connected to the guide groove.

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