CN219774914U - High-pressure interception control device - Google Patents

Abstract

The utility model discloses a high-pressure interception control device which is used for intercepting and controlling a high-pressure fluid pipeline and comprises a pressure control valve and a pressure regulating mechanism; the pressure control valve comprises a piston, a piston cylinder, a valve needle and a valve body, wherein the piston is movably arranged in the piston cylinder and forms a first chamber with the piston cylinder, and the first chamber is communicated with the pressure regulating mechanism through a pressure regulating pipeline; the valve needle is connected with the piston and synchronously moves along with the piston, and the sectional area of the valve needle is smaller than that of the piston; the valve body is communicated with a high-pressure fluid pipeline, a valve port is arranged in the valve body, and the valve needle is matched with the valve port; the pressure regulating mechanism changes the pressure balance of the piston and the valve needle by regulating the pressure value of the first chamber, so as to realize the opening and closing of the valve needle and the valve port. The high-pressure interception control device can be suitable for higher-pressure environments, and has high stability, high control precision and long service life.

Description

High-pressure interception control device

Technical Field

The utility model relates to the technical field of fluid control, in particular to a high-pressure interception control device.

Background

At present, in some fields of chemical industry, machinery and pressure calibration, a certain pressure environment needs to be provided, in order to realize automatic control of pressure, a traditional mode is to set an electromagnetic valve at an outlet of a pressure output source, and realize opening and closing of a pressure output pipeline by controlling the electromagnetic valve, so as to realize pressure regulation and control of the pressure environment.

In particular, in the field of pressure calibration, in order to realize that pressure calibration equipment is suitable for more pressure gauges to be detected and verification ranges of equipment are continuously broken through by large manufacturers, however, as the pressure ranges are gradually increased, the difficulty of accurate control of pressure output is gradually increased, because the traditional pressure calibration equipment is used for pressure output control by adopting electromagnetic valves, the pressure environment suitable for the traditional electromagnetic valves is more under 30MPa, the pressure output control in higher pressure environment (such as more than 60 MPa) cannot be adapted, even if electromagnetic valves suitable for high pressure environment exist in the market, the control precision of the electromagnetic valves is generally lower, the application in the pressure calibration field cannot be realized, the service life of the electromagnetic valves in the high pressure environment is not long, and the stability is poor.

In addition, some manufacturers can also adopt the servo valve to realize opening and closing of the pressure output pipeline, however, the internal structure of the servo valve is worn out due to long-time opening and closing, particularly, the phenomenon that the cut-off port is expanded due to repeated stamping of the servo valve is caused, and the servo valve still moves according to a set feeding thread, so that the pressure pipeline is not tightly closed, and the pressure output control precision is reduced.

Disclosure of Invention

Based on the above, the present utility model aims to provide a high-pressure cut-off control device, which is used for solving the problem that the conventional electromagnetic valve and servo valve cannot be suitable for pressure output control in a high-pressure environment.

In order to solve the problems, the utility model adopts the following technical scheme:

a high-pressure interception control device is used for intercepting and controlling a high-pressure fluid pipeline and comprises a pressure control valve and a pressure regulating mechanism;

the pressure control valve comprises a piston, a piston cylinder, a valve needle and a valve body, wherein the piston is movably arranged in the piston cylinder and forms a first chamber with the piston cylinder, and the first chamber is communicated with the pressure regulating mechanism through a pressure regulating pipeline; the valve needle is connected with the piston and synchronously moves along with the piston, and the sectional area of the valve needle is smaller than that of the piston; the valve body is communicated with a high-pressure fluid pipeline, a valve port is arranged in the valve body, and the valve needle is matched with the valve port;

the pressure regulating mechanism changes the pressure balance of the piston and the valve needle by regulating the pressure value of the first chamber, so as to realize the opening and closing of the valve needle and the valve port.

Further, the high-pressure interception control device further comprises a first pressure sensor, wherein the first pressure sensor is arranged on the pressure regulating pipeline and used for sensing the pressure value in the first cavity so as to feed back the pressure regulating mechanism to perform pressure regulating operation based on the sensed pressure value.

Further, the pressure regulating mechanism comprises a low pressure source and a pressure regulating valve, and the pressure regulating valve is used for controlling the fluid of the low pressure source to enter the first chamber for increasing pressure or releasing the fluid of the first chamber for decreasing pressure.

Further, a sealing ring is sleeved at the contact position of the outer periphery of the piston and the inner wall of the piston cylinder.

Further, one side of the piston cylinder, which is away from the first chamber, forms a second chamber, and a limiting part is arranged in the second chamber and used for limiting the transition movement of the piston towards the valve port.

Further, the second chamber is a closed cavity, and a chamber interface is arranged at one side far away from the first chamber; the high-pressure interception control device further comprises an auxiliary pressure regulating mechanism, and the auxiliary pressure regulating mechanism is connected with the chamber interface through a third pipeline so as to regulate the pressure of the second chamber.

Further, the auxiliary pressure regulating mechanism comprises an auxiliary low pressure source, an auxiliary pressure regulating valve and a second pressure sensor, wherein the auxiliary pressure regulating valve is used for controlling fluid of the auxiliary low pressure source to enter the second chamber for pressure increasing or releasing fluid of the second chamber for pressure decreasing, and the second pressure sensor is used for sensing a pressure value in the second chamber so as to feed back the auxiliary pressure regulating valve to perform pressure regulating work based on the sensed pressure value.

When the pressure control valve is in a closed state, the pressure regulating mechanism controls the pressure value p1 of the first chamber to be larger than (p 2 s2-p0 s2+ p0 s 1)/s 1, wherein s1 is the sectional area of the piston, s2 is the sectional area of the valve needle, p2 is the fluid pressure of the high-pressure fluid pipeline, and p0 is the pressure value of the second chamber.

Further, the valve body further comprises a valve cavity, and a fluid inlet and a fluid outlet which are communicated with the valve cavity, wherein the fluid inlet is connected with the high-pressure fluid pipeline, and the valve port corresponds to the fluid inlet or the fluid outlet.

Preferably, the high-pressure shutoff control device further comprises a sealing assembly, wherein the sealing assembly is assembled in the valve body and sleeved on the valve needle, and is used for sealing the valve cavity.

According to the pressure boosting source, fluid with higher pressure is obtained after the pressure boosting treatment, the higher pressure can exert pressure on the valve needle at the moment, and the sectional area of the piston is far larger than that of the valve needle, so that the valve needle can be pushed to close the valve port by keeping smaller pressure in the first chamber according to the corresponding relation between the pressure and the pressure receiving area, and the stop function of the pressure control valve is realized.

According to the utility model, the pressure balance point between the valve needle and the piston is broken through regulating the pressure change in the first cavity by the pressure regulating mechanism, so that the valve needle can move according to the pressure difference between the valve needle and the piston, and the valve port can be opened or closed. In the whole pressure regulating process of the regulating mechanism, the pressure in the first chamber is changed gently, the pressure difference between the valve needle and the piston is also changed gently, the movement of the valve needle is also moved gently, and further the opening or closing process of the valve port 241 is also smooth, and the phenomena of abrupt rise, abrupt fall and pause can not occur, so that the accuracy of pressure output control is improved.

In order to achieve stable cut-off, the pressure of the first chamber higher than the pressure balance point between the valve needle and the piston is always maintained through the pressure regulating mechanism. That is, the force for achieving the stop is derived from the pressure difference between the piston and the valve needle, and the stable stop function can be achieved as long as the pressure difference exists, that is, the valve needle can be always closed to the valve port, so to speak, the stop at this point is an adaptive stop. Even if the displacement between the valve port and the valve needle changes, or the valve port expands, the valve port can still be cut off as long as a pressure difference exists. Compared with the traditional servo valve, the servo valve is applied to the valve needle through external force, the feeding thread of the valve needle is preset, the external force applied to the valve needle is not related to the pressure force of the high-pressure fluid applied to the valve needle, when the external force applied to the valve needle is overlarge, the problem of transitional impact on the valve port is caused, meanwhile, the feeding thread of the valve needle is preset, that is, the valve needle is considered to be in a cut-off or opening state only when reaching the preset position for the servo valve, however, the feeding movement precision of the servo valve is reduced along with long-time work, so that the valve needle is difficult to reach the preset position, the control precision is reduced, or even if the valve needle can reach the preset position, a gap exists between the valve needle and the valve port when the valve port is cut-off due to the outward expansion of the valve port, and the cut-off cannot be caused.

In conclusion, the high-pressure cut-off control device can adapt to cut-off control in a high-pressure environment, effectively improves high-pressure output control precision, and solves the problems that the traditional electromagnetic valve and the servo valve cannot adapt to high-pressure cut-off control and the control precision is low. Meanwhile, the high-pressure interception control device has high stability and long service life.

The resource utilization rate of each element can be improved, and meanwhile, the compact design of the integral structure of the gas pressure calibrator is realized, so that the gas pressure calibrator is more miniaturized, and the manufacturing cost and the maintenance cost are saved.

Drawings

FIG. 1 is a schematic view of a high pressure shut-off control device according to the present utility model;

fig. 2 is a schematic structural view of a pressure control valve according to the present utility model.

Reference numerals:

10. a boost source;

20. the pressure control valve comprises a pressure control valve body, a pressure control valve 21, a piston, 211, a sealing ring, 22, a piston cylinder, 23, a valve needle, 24, a valve body, 241, a valve port, 242, a fluid inlet, 243, a fluid outlet, 25, a first chamber, 26, a second chamber, 261, a chamber interface, 27, a limiting part, 28 and a sealing component;

30. a pressure regulating mechanism 31, a low pressure source 32, a pressure regulating valve 33 and a first pressure sensor;

40. a pressure regulating pipeline;

50. a high pressure fluid line;

60. an auxiliary pressure regulating mechanism 61, an auxiliary low pressure source 62, an auxiliary pressure regulating valve 63 and a second pressure sensor.

Detailed Description

In order to make the technical objects, technical schemes and advantageous effects of the present utility model more clear, the technical scheme of the present utility model will be further described with reference to fig. 1-2 and specific embodiments.

The utility model provides a high-pressure cut-off control device, which is used for cut-off control of a high-pressure fluid pipeline, and a pressurizing source 10 is connected with the high-pressure fluid pipeline 50 and is used for providing high-pressure fluid.

The high-pressure cut-off control device comprises a pressure control valve 20 and a pressure regulating mechanism 30;

the pressure control valve 20 comprises a piston 21, a piston cylinder 22, a valve needle 23 and a valve body 24, wherein the piston 21 is movably arranged in the piston cylinder 22 and forms a first chamber 25 with the piston cylinder 22, and the first chamber 25 is communicated with the pressure regulating mechanism 30 through a pressure regulating pipeline 40; the valve needle 23 is connected with the piston 21 and synchronously moves along with the piston 21, and the sectional area of the valve needle 23 is smaller than that of the piston 21; the valve body 24 is communicated with the pressurizing source 10 through a high-pressure fluid pipeline 50, a valve port 241 is arranged in the valve body 24, and the valve needle 23 is matched with the valve port 241;

the pressure regulating mechanism 30 changes the pressure balance between the piston 21 and the valve needle 23 by regulating the pressure value of the first chamber 25, so as to realize the opening and closing of the valve needle 23 and the valve port 241.

The valve needle 23 of the present utility model has a needle-like structure, one end of which is provided with a tapered needle portion, and the other end of which is fixedly connected to the center position of the piston 21. In some embodiments, a mounting hole is formed in the center of the piston 21, the valve needle 23 is inserted through the mounting hole of the piston 21, and is screwed on a matching sealing ring of the valve needle 23 through a nut. In other embodiments, the piston 21 may also be integrally formed with the valve needle 23. But is not limited thereto.

The fluid according to the utility model may be a gas or a liquid.

In a specific embodiment, the relative position between the piston cylinder 22 and the valve body 24 is kept stable to ensure that the valve needle 23 is synchronously moved relative to the valve body 24 when the piston 21 moves in the piston cylinder 22. Preferably, the piston cylinder 22 and the valve body 24 may be fixedly connected by a connecting piece, or may be in an integrally formed structure, but is not limited thereto.

According to the pressurizing source 10, fluid with higher pressure, such as 70MPa, is obtained after pressurizing treatment, the higher pressure can apply pressure to the valve needle 23, and the sectional area of the piston 21 is far larger than that of the valve needle, so that according to the corresponding relation between the pressure and the pressure receiving area, the valve needle can be pushed to close the valve port 241 by keeping the smaller pressure in the first chamber 25, and the cut-off function of the pressure control valve 20 is realized.

The pressure regulating mechanism 30 regulates the pressure change in the first chamber 25 to break the pressure balance point between the valve needle and the piston 21, so that the valve needle 23 moves according to the pressure difference between the valve needle 23 and the piston 21, and the valve port 241 is opened or closed. In the whole pressure regulating process of the regulating mechanism, the pressure in the first chamber 25 is changed gradually, the pressure difference between the valve needle 23 and the piston 21 is also changed gradually, the valve needle 23 moves gradually, the opening or closing process of the valve port 241 is further smooth, and the phenomena of abrupt rise, abrupt fall and abrupt pause are avoided, so that the accuracy of pressure output control is improved.

In order to achieve a stable shut-off, the pressure in the first chamber 25 is always maintained above the pressure balance point between the valve needle and the piston 21 by the pressure regulating mechanism 30. That is, the force for achieving the shut-off is derived from the pressure difference between the piston 21 and the needle, and the function of stable shut-off can be achieved as long as the pressure difference exists, that is, the needle 23 can be always closed to the valve port 241, so that the shut-off is an adaptive shut-off. Even if the displacement between the valve port 241 and the needle 23 is changed or the valve port 241 is expanded, the shutoff can be realized if a pressure difference exists. Compared with the traditional servo valve, the servo valve is applied to the valve needle 23 through external force, the feeding thread of the valve needle 23 is preset, the external force applied to the valve needle 23 is not related to the pressure force of high-pressure fluid applied to the valve needle, when the external force applied to the valve needle 23 is overlarge, the problem of transitional impact to the valve port 241 is caused, meanwhile, as the feeding thread of the valve needle 23 is preset, that is to say, as long as the valve needle 23 reaches the preset position, the servo valve is in a cut-off or open state, however, as long as the valve needle 23 works for a long time, the feeding movement precision of the servo valve is reduced, so that the valve needle 23 is difficult to reach the preset position, the control precision is reduced, or even if the valve needle 23 can reach the preset position, but because the valve port 241 is pressed and expands outwards, a gap exists between the valve needle 23 and the valve port 241, and a cut-off incapacity phenomenon is caused.

The high-pressure interception control device of the utility model further comprises a first pressure sensor 33, wherein the first pressure sensor 33 is arranged on the pressure regulating pipeline 40 and is used for sensing the pressure value in the first chamber 25 so as to feed back the pressure regulating mechanism 30 to perform pressure regulating operation based on the sensed pressure value.

The first pressure sensor 33 of the present utility model is used for sensing the pressure values of the pressure regulating line 40 and the first chamber 25, and causes the pressure regulating mechanism 30 to perform pressure regulation according to the sensed pressure values. For example, in the off state, the pressure value of the first chamber 25 needs to be maintained at an initial set value in order to achieve a stable off function. The actual pressure value of the first chamber 25 may change under the influence of environmental or space factors, and the actual pressure value may be adaptively adjusted according to the fed-back actual pressure value, so as to be always kept at the initial set value; when the pressure regulating mechanism 30 is turned off to the open state, the pressure of the first chamber 25 needs to be gradually reduced, and the critical pressure value of the first chamber 25 at the balance point can be calculated according to the sectional area of the piston 21, the sectional area of the valve needle and the stable high-pressure fluid output by the pressurization source 10, at this time, the pressure regulating mechanism 30 needs to determine whether the balance point is reached or passed according to the sensed actual pressure value compared with the critical pressure value, so as to determine whether the valve port 241 is opened.

Specifically, the pressure regulating mechanism 30 includes a low pressure source 31 and a pressure regulating valve 32, where the pressure regulating valve 32 is used to control the fluid of the low pressure source 31 to enter the first chamber 25 for increasing pressure, or release the fluid of the first chamber 25 for decreasing pressure.

It will be appreciated that the low pressure source 31 herein is a low pressure source 31 having a pressure less than the high pressure fluid of the pressurized source 10, because the cross-sectional area of the piston 21 is much greater than the cross-sectional area of the valve needle 23 based on the relationship between pressure and pressure receiving area, and thus, the pressure source acting on the piston 21 may be implemented by selecting a low pressure source 31 having a pressure less than the high pressure fluid of the pressurized source 10. Here, the low pressure source 31 may provide a stable low pressure, the pressure regulating valve 32 is opened to flow the low pressure fluid of the low pressure source 31 into the first chamber 25, so that the pressure of the first chamber 25 is increased, the pressure regulating valve 32 interrupts the low pressure source 31, and simultaneously releases the low pressure fluid of the first chamber 25 to the outside, so that the pressure of the first chamber 25 is reduced.

Preferably, a sealing ring 211 is sleeved at the contact position of the outer periphery of the piston 21 and the inner wall of the piston cylinder 22.

It will be appreciated that by providing the sealing ring 211 on the outer periphery of the piston 21, the swordlike can avoid the overflow of the low-pressure fluid in the first chamber 25, and further avoid the phenomenon of inaccurate pressure regulation of the pressure regulating mechanism 30, thereby ensuring stable control of the pressure control valve 20.

Further, a second chamber 26 is formed on a side of the piston cylinder 22 facing away from the first chamber 25, a limiting portion 27 is disposed in the second chamber 26, and the limiting portion 27 is used for limiting the transitional movement of the piston 21 toward the valve port 241.

According to the utility model, the limiting part 27 is arranged, so that the transitional movement of the piston 21 towards the valve port 241 is effectively limited, and the phenomenon that the valve port 241 expands seriously and is blocked and fails due to the fact that the valve needle 23 transitively punches the valve port 241 is prevented.

In some embodiments, the side of the piston cylinder 22 facing away from the first chamber 25 may also be open, i.e. the two faces of the piston 21, one face being pressed against the first chamber 25 and the other face being pressed against atmospheric pressure.

Further, the second chamber 26 is a closed chamber, and a chamber interface 261 is provided at a side far away from the first chamber 25; the high-pressure interception control device further comprises an auxiliary pressure regulating mechanism 60, and the auxiliary pressure regulating mechanism 60 is connected with the chamber interface 261 through a third pipeline so as to regulate the pressure of the second chamber 26.

It can be understood that the piston cylinder 22 has a cylindrical structure with a closed top and bottom, and both the top and bottom covers of the piston cylinder 22 can be used as the limiting portion 27, and the top cover is used as the limiting portion 27 to prevent the piston 21 from transitionally moving away from the valve port 241, so as to drive the valve needle to be separated from the valve body 24. The lower cover is used as a limiting part 27 to prevent the piston 21 from transitionally moving towards the valve port 241, so that the valve needle 23 transitionally punches the valve port 241, and the valve port 241 is seriously expanded and is stopped to be invalid.

The auxiliary pressure regulating mechanism 60 comprises an auxiliary low pressure source 61, an auxiliary pressure regulating valve 62 and a second pressure sensor 63, wherein the auxiliary pressure regulating valve 62 is used for controlling the fluid of the auxiliary low pressure source 61 to enter the second chamber 26 for pressure increasing or releasing the fluid of the second chamber 26 for pressure decreasing, and the second pressure sensor 63 is used for sensing the pressure value in the second chamber 26 so as to feed back the pressure regulating operation of the auxiliary pressure regulating valve 62 based on the sensed pressure value.

The auxiliary pressure regulating mechanism 60 is arranged, on the one hand, the pressure regulating mechanism 30 is matched to neutralize the pressure at the two sides of the piston 21, namely, when the pressurizing source 10 needs to be emptied, the pressure regulating mechanism 30 controls the pressure of the first chamber 25 to be reduced, however, because the upper pressure bearing surface and the lower pressure bearing surface of the piston 21 are greatly different from each other, even if the pressure regulating mechanism 30 is depressurized to the limit, the lower pressure of the valve needle can still bear pressure of a few megapascals, the lower pressure bearing surface and the upper pressure bearing surface of the piston 21 are balanced, and the valve port 241 is still in a cut-off state, so that the pressurizing source 10 cannot be emptied.

On the other hand, if there is a certain sliding friction between the piston 21 and the piston cylinder 22, if the pressure of the first chamber 25 needs to be increased by the pressure regulating mechanism 30 to promote the piston 21 to move, the lower surface of the piston 21 is not pressed (only under atmospheric pressure) because the upper surface of the piston 21 is pressed only, and thus, during initial movement of the piston 21, a sudden and uneven start may be caused.

When the pressure control valve 20 is in the closed state, the pressure regulating mechanism 30 controls the pressure value p1 of the first chamber 25 to be greater than (p2×s2—p0×s2+p0×s1)/s 1, where s1 is the cross-sectional area of the piston 21, s2 is the cross-sectional area of the valve needle, p2 is the fluid pressure of the boost source 10, and p0 is the pressure value of the second chamber 26. Wherein "/" represents division by multiplication.

In an ideal state, when the compression of the piston 21 and the valve needle 23 reaches the balance point, according to the equality of the forces at the balance point, the forces f1=p1×s1-p0×s1-s2 of the piston 21 can be calculated, the forces f2=p2×s2 of the valve needle can be substituted according to f1=f2, and the pressure value p1= (p2×s2-p0×s2+p0×s1)/s 1 of the first chamber 25 of the balance point in the ideal state can be calculated, so that the balance point needs to be broken and the pressure value p1 of the first chamber 25 needs to be increased appropriately to be larger than (p2×s2-p0×s2+p0×s1)/s 1 to realize stable closing.

Similarly, if the pressure control valve 20 is to be opened or the flow rate of the valve port 241 is to be increased, the pressure value p1 of the first chamber 25 is smaller than (p2×s2—p0×s2+p0×s1)/s 1.

It will be appreciated that when the auxiliary pressure regulating mechanism 60 is not provided, the pressure value p0 is one atmosphere, and when the auxiliary pressure regulating mechanism 60 is provided, the pressure value p0 is the actual pressure value of the second chamber 26.

Further, the valve body 24 further includes a valve cavity, and a fluid inlet 242 and a fluid outlet 243 that are connected to the valve cavity, the fluid inlet 242 is connected to the high-pressure fluid pipeline 50, and the valve port 241 corresponds to the fluid inlet 242 or the fluid outlet 243.

It will be appreciated that the fluid inlet 242 and the fluid outlet 243 may be switched as the application environment changes, i.e. as the flow direction changes, the fluid inlet 242 and the fluid outlet 243 are shown in one flow state, and that when the fluid flows in opposite directions, the designations of the fluid inlet 242 and the fluid outlet 243 in the figures will be reversed.

Further, the high-pressure shutoff control device further comprises a sealing assembly 28, wherein the sealing assembly 28 is assembled in the valve body 24 and sleeved on the valve needle 23, so as to realize sealing of the valve cavity.

Preferably, the seal assembly 28 includes a seal member mounted in the valve body 24 and sleeved on the valve needle, and a lock nut sleeved on the valve needle and threadedly coupled to the valve body 24 to lock the seal member.

It will be appreciated that the seal effectively seals the gap between the valve needle 23 and the valve body 24 as the valve needle 23 moves up and down, avoiding fluid escaping from the gap between the valve needle 23 and the valve body 24.

In addition, the booster pump 10 and the low pressure source 31 of the present utility model may be universal booster pumps, which will not be described in detail herein.

The working principle of the high-pressure interception control device of the utility model is as follows:

when the output of the high-pressure fluid needs to be cut off, the pressure in the first chamber 25 is controlled by the pressure regulating mechanism 30 and kept at an initial set value, the initial set value can be calculated according to the sectional area of the valve needle, the sectional area of the piston 21 and the maximum pressure value output by the pressurizing source 10, and in the cut-off process, the pressure regulating mechanism 30 dynamically stabilizes the pressure based on the real-time pressure fed back by the pressure sensor; that is, if the pressure of the first chamber 25 is lower than the initial set value, the pressure compensation is performed, and if the pressure of the first chamber 25 is higher than the initial set value, the pressure of the first chamber 25 is properly reduced, so that the pressure value of the first chamber 25 is always kept at the initial set value, stable stop is realized, and the valve needle 23 is not prevented from transitionally stamping the valve port 241.

When the output device needs to be pressurized, the pressure in the first chamber 25 is gradually released through the pressure regulating mechanism 30, at this time, the pressure in the first chamber 25 gradually drops, when the pressure drops to the pressure balance point of the piston 21 and the valve needle 23, the pressure balance between the piston 21 and the valve needle 23 is broken by continuously releasing the pressure in the first chamber 25, at this time, since the pressure force of the high-pressure fluid received by the valve needle 23 is greater than the pressure force received by the piston 21 in the first chamber 25, the piston 21 and the valve needle 23 synchronously move away from the valve port 241 and smoothly open the valve port 241, the high-pressure fluid can be output through the valve port 241, so that the pressure supply to the output device is realized, and later, when the pressure of the output device is close to a preset value, the pressure regulating mechanism 30 is promoted to gradually increase the pressure in the first chamber 25 until the pressure balance point of the piston 21 and the valve needle 23 is reached, and further pressurization is carried out, and the piston 21 and the valve needle 23 synchronously move towards the valve port 241 and smoothly close the valve port 241.

It should be noted that any of the apparatus embodiments described above are merely illustrative, where elements described as separate elements may or may not be physically separate, and elements shown as elements may or may not be physical elements, may be located in one place, or may be distributed over a plurality of network elements. The foregoing description of embodiments of the utility model has been presented for purposes of illustration and description, and is not intended to be exhaustive or limited to the embodiments disclosed. Many modifications and variations will be apparent to those of ordinary skill in the art without departing from the scope and spirit of the various embodiments described. The terminology used herein was chosen in order to best explain the principles of the embodiments, the practical application, or the improvement of technology in the marketplace, or to enable others of ordinary skill in the art to understand the embodiments disclosed herein.

Claims (10)

1. The utility model provides a high pressure closure control device for carry out closure control to high pressure fluid pipeline, its characterized in that: comprises a pressure control valve and a pressure regulating mechanism;

the pressure control valve comprises a piston, a piston cylinder, a valve needle and a valve body, wherein the piston is movably arranged in the piston cylinder and forms a first chamber with the piston cylinder, and the first chamber is communicated with the pressure regulating mechanism through a pressure regulating pipeline; the valve needle is connected with the piston and synchronously moves along with the piston, and the sectional area of the valve needle is smaller than that of the piston; the valve body is communicated with a high-pressure fluid pipeline, a valve port is arranged in the valve body, and the valve needle is matched with the valve port;

the pressure regulating mechanism changes the pressure balance of the piston and the valve needle by regulating the pressure value of the first chamber, so as to realize the opening and closing of the valve needle and the valve port.

2. A high pressure shut-off control device according to claim 1, wherein: the pressure regulating device comprises a first cavity, a pressure regulating pipeline, a feedback pressure regulating mechanism and a pressure regulating mechanism, wherein the pressure regulating pipeline is used for regulating pressure of the first cavity, and the pressure regulating mechanism is used for regulating pressure of the first cavity according to the pressure value.

3. A high pressure shut-off control device according to claim 1, wherein: the pressure regulating mechanism comprises a low pressure source and a pressure regulating valve, wherein the pressure regulating valve is used for controlling the fluid of the low pressure source to enter the first chamber for pressure rising or releasing the fluid of the first chamber for pressure reducing.

4. A high pressure shut-off control device according to claim 1, wherein: a sealing ring is sleeved at the contact position of the periphery of the piston and the inner wall of the piston cylinder.

5. A high pressure shut-off control device according to claim 1, wherein: one side of the piston cylinder, which is away from the first chamber, forms a second chamber, and a limiting part is arranged in the second chamber and used for limiting the transition movement of the piston towards the valve port.

6. A high pressure shut-off control device as defined in claim 5, wherein: the second chamber is a closed cavity, and a chamber interface is arranged on one side far away from the first chamber; the high-pressure interception control device further comprises an auxiliary pressure regulating mechanism, and the auxiliary pressure regulating mechanism is connected with the chamber interface through a third pipeline so as to regulate the pressure of the second chamber.

7. A high pressure shut-off control device as defined in claim 6, wherein: the auxiliary pressure regulating mechanism comprises an auxiliary low pressure source, an auxiliary pressure regulating valve and a second pressure sensor, wherein the auxiliary pressure regulating valve is used for controlling fluid of the auxiliary low pressure source to enter the second chamber for pressure increasing or releasing fluid of the second chamber for pressure decreasing, and the second pressure sensor is used for sensing a pressure value in the second chamber so as to feed back the pressure regulating valve to perform pressure regulating work based on the sensed pressure value.

8. A high pressure closure control device according to claim 7, wherein: when the pressure control valve is in a closed state, the pressure regulating mechanism controls the pressure value p1 of the first chamber to be larger than (p 2 s2-p0 s2+ p0 s 1)/s 1, wherein s1 is the sectional area of the piston, s2 is the sectional area of the valve needle, p2 is the fluid pressure of the high-pressure fluid pipeline, and p0 is the pressure value of the second chamber.

9. A high pressure shut-off control device according to any one of claims 1 to 5, wherein: the valve body further comprises a valve cavity, and a fluid inlet and a fluid outlet which are communicated with the valve cavity, wherein the fluid inlet is connected with the high-pressure fluid pipeline, and the valve port corresponds to the fluid inlet or the fluid outlet.

10. A high pressure shut-off control device according to any one of claims 1 to 5, wherein: the valve needle is characterized by further comprising a sealing assembly, wherein the sealing assembly is assembled in the valve body and sleeved on the valve needle and is used for sealing the valve cavity.