CN102168699B - Hydraulic interceptor valve - Google Patents
Hydraulic interceptor valve Download PDFInfo
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- CN102168699B CN102168699B CN 201110106902 CN201110106902A CN102168699B CN 102168699 B CN102168699 B CN 102168699B CN 201110106902 CN201110106902 CN 201110106902 CN 201110106902 A CN201110106902 A CN 201110106902A CN 102168699 B CN102168699 B CN 102168699B
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Abstract
The invention discloses a hydraulic interceptor valve which comprises a pressure oil inlet, a pressure oil outlet, an oil return pipeline, an interceptor slide valve and a restoration control element, wherein the pressure oil outlet is connected with a pressure oil source, and is used for guiding the pressure oil into the interceptor slide valve; the pressure oil outlet is used for outputting the pressure oil which flows from the interceptor slide valve; the oil return pipeline is used for enabling the pressure oil which flows out of the interceptor slide valve to backflow to the pressure oil source; the interceptor slide valve is respectively connected with the pressure oil inlet, the pressure oil outlet, the oil return pipeline and the restoration control element, and is used for guiding the pressure oil which flows from the interceptor slide valve into the oil return pipeline when the pressure at the pressure oil outlet decreases instantly; the restoration control element is connected with the pressure oil inlet, and is used for controlling the pressure oil which flows from the interceptor slide valve to be guided into the pressure oil outlet when the pressure difference of the pressure oil inlet and the pressure oil outlet exceeds the normal range. Through the valve provided by the invention, oil liquid leakage of the high-pressure pipeline can be prevented.
Description
Technical Field
The invention relates to the technical field of hydraulic control, in particular to a hydraulic block valve.
Background
In the existing hydraulic control system, the working temperature is basically all the antiwear hydraulic oil is used as the working medium in the room temperature situation. Generally, an oil source (e.g., a hydraulic pump station) is far away from field actuators (e.g., cylinders, hydraulic motors, etc.), usually several tens to hundreds of meters, and they are connected to each other through hydraulic lines, and high-pressure oil is delivered to each actuator through the hydraulic lines.
The huge external oil pipeline of the hydraulic system is easy to break after hydraulic shock excitation is generated, and the broken oil is sprayed to a high-temperature object in a mist form, so that fire disasters are easy to cause, therefore, the existing hydraulic system in a high-temperature environment generally selects water, glycol or phosphate ester fire-resistant oil as a working medium, and the two media have good fire resistance, but have inherent serious defects.
Water and glycol are mixed flame retardant media, and are a mixture of water and glycol, and the advantage is that the water and glycol cannot be ignited at all when meeting high temperature. At high-temperature sites of the existing metallurgical enterprises (such as steel making plants and the like), hydraulic systems basically use the medium, but the medium has the defects of extremely poor lubricating performance, extremely serious abrasion to hydraulic elements (such as mechanical parts of sliding pairs of plunger pumps, electromagnetic valves, proportional valves and the like) used in the system, only one month of service life of one continuously operated inlet hydraulic oil pump when the abrasion is serious, and replacement of a new hydraulic element after a fault occurs, so that the use condition causes a great deal of cost waste and production delay. In addition, the chemical properties of water and glycol are unstable, because water in the medium is easy to be vaporized and evaporated due to high temperature, the fire resistance of the vaporized water and glycol is greatly reduced, and water needs to be supplemented in time, but quantitative detection of oil in the field working environment is very difficult, and only all oil in the system can be replaced regularly, so that the quantity of spare parts (including damaged hydraulic elements and used for replacing hydraulic oil) needed by the hydraulic system after the hydraulic system is put into operation is very large, and the purchase cost and the replacement cost of the spare parts are also very high.
The phosphate ester fire-resistant oil is another working medium with high ignition point, the ignition point can reach about 600 ℃, the lubricating property is good, and the phosphate ester fire-resistant oil is widely applied to the steam turbine electrohydraulic control systems of various domestic power plants. However, since the phosphate ester is a toxic medium and cannot be degraded in nature, the waste oil causes great pollution to the environment, the phosphate ester fire-resistant oil is the same as nuclear waste, the ordinary maintenance requirements of the phosphate ester fire-resistant oil on the oil in the using process are very strict, the chemical characteristics of the phosphate ester fire-resistant oil can be ensured to be stable only by regular regeneration filtration, the price of the phosphate ester is very high, and the price of the phosphate ester fire-resistant oil with the same volume is almost ten times that of the fire-resistant oil.
The antiwear hydraulic oil has the advantages of good lubricating property, stable chemical property, no need of maintenance during operation, no toxicity, good environmental protection, low price and the like, and is widely applied to various hydraulic systems. However, in a high-temperature working environment (such as a steel-making production line of a metallurgical enterprise, an electrohydraulic control system of a steam turbine and the like), the environment temperature of a site is very high, and high-temperature objects or high-temperature steam pipelines are densely distributed, so that the anti-wear hydraulic oil has a low burning point and an opening flash point of about 240 ℃, once the pipeline is broken, high-pressure oil can splash at the broken part, if the high-pressure oil continuously splashes onto the high-temperature objects (such as high-temperature red steel, high-temperature steam pipelines and the like), fire is very easy to occur, and a fire accident can cause great economic loss, which is a fundamental reason that the anti-wear hydraulic oil cannot be used in the high-temperature environment at present.
Through the analysis, the anti-wear hydraulic oil is a working medium with stable chemical performance and best cost performance in the hydraulic field, and if the anti-wear hydraulic oil is used in a high-temperature environment, the anti-wear hydraulic oil can be used in a hydraulic system working in the high-temperature environment as long as the problem that the high-pressure oil is atomized and splashed after a hydraulic system using the medium is broken in a high-pressure oil pipeline is avoided, so that the defect that water, glycol or phosphate ester is used for resisting fuel oil on site is overcome, and the economy of the existing hydraulic system is greatly improved.
Disclosure of Invention
Accordingly, the present invention provides a hydraulic blocking valve to prevent oil leakage in a high-pressure line.
An embodiment of the present invention provides a hydraulic block valve, including: the device comprises a pressure oil inlet, a pressure oil outlet, an oil return pipeline, a shutoff slide valve and a reset control element; wherein,
the pressure oil inlet is connected with a pressure oil source and used for guiding pressure oil into the interceptor slide valve;
the pressure oil outlet is used for outputting the pressure oil flowing out of the shutoff slide valve;
the oil return pipeline is used for returning the pressure oil flowing out of the interceptor slide valve to a pressure oil source;
the interceptor slide valve is respectively connected with the pressure oil inlet, the pressure oil outlet, the oil return pipeline and the reset control element and is used for guiding the pressure oil flowing out of the interceptor slide valve into the oil return pipeline when the pressure of the pressure oil outlet is instantly reduced;
and the reset control element is connected with the pressure oil inlet and used for controlling the pressure oil flowing through the shutoff slide valve to be led into the pressure oil outlet when the pressure difference between the pressure oil inlet and the pressure oil outlet is in a normal range.
Preferably, the shutoff spool specifically includes:
the valve core is tightly attached to the valve sleeve and can move up and down in the valve sleeve; a valve body sealing the valve housing; wherein the valve spool includes:
the first valve core, the second valve core and the third valve core are fixedly connected from top to bottom; the lower surface area of the third valve element contacting the pressure oil is larger than the surface area of the joint of the first valve element and the second valve element contacting the pressure oil and smaller than the surface area of the joint of the second valve element and the third valve element contacting the pressure oil;
when the pressure of the pressure oil outlet is reduced instantly, the third valve core moves to the bottom of the valve sleeve, so that the second valve core blocks the oil inlet valve port, and the oil outlet valve port is communicated with the oil return valve port; when the reset valve port receives pressure oil introduced by the reset control element, the first valve core moves to the top of the valve sleeve, so that the third valve core blocks the oil return valve port, and the oil inlet valve port is communicated with the oil outlet valve port.
Preferably, the first valve core, the second valve core and the third valve core are of an integrated structure.
Preferably, the reset control element is an electromagnetic directional valve.
Preferably, the electromagnetic valve is a 6-path electromagnetic directional valve.
Preferably, the valve core is made of alloy steel.
Preferably, the valve sleeve is made of alloy steel.
Preferably, the reset control element is fixedly connected to the top of the valve body.
Preferably, the reset control element is fixed by a bolt connection.
Preferably, the reset control element adopts two reset modes of remote control or local operation.
Compared with the prior art, the hydraulic blocking valve provided by the invention is used for a hydraulic control system, and the blocking slide valve contained in the hydraulic blocking valve can automatically judge the working state of an outlet pressure oil pipeline of the hydraulic system, can respond instantly when the pipeline of the outlet pressure oil pipeline is broken, can immediately cut off pressure oil conveyed by a pressure oil source, and can introduce the pressure oil at the outlet into a non-pressure oil return pipeline, so that the oil at the broken pipeline has no pressure source, and high-pressure oil cannot splash into a fog state, thereby avoiding fire accidents caused by the fact that wear-resistant hydraulic oil leaks and splashes to high-temperature objects to cause fire due to the breakage of the pipeline; in addition, the hydraulic system can be also suitable for other hydraulic systems, and can be used for avoiding economic loss and production environment pollution caused by leakage of a large amount of hydraulic oil after the high-pressure pipeline is broken.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art that other drawings can be obtained according to these drawings without creative efforts.
Fig. 1 is a schematic structural view of a hydraulic block valve according to an embodiment of the present invention;
FIG. 2 is a schematic view of a shutoff spool valve according to an embodiment of the present invention;
FIG. 3 is a schematic diagram of a spool of a shutoff spool valve according to an embodiment of the present invention;
FIG. 4 is a schematic view of a shutoff spool valve in a "shutoff position spool state" configuration provided by an embodiment of the present invention;
FIG. 5 is a schematic diagram of a force applied to a valve core according to an embodiment of the present invention;
fig. 6 is a schematic structural view of a shutoff spool valve in an "operating position spool state" according to an embodiment of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The embodiment of the invention provides a hydraulic blocking valve, which is used for preventing oil leakage of a high-pressure pipeline. As shown in fig. 1, the hydraulic block valve includes: a pressure oil inlet 10, a pressure oil outlet 11, an oil return pipeline 12, a shutoff slide valve 13 and a reset control element 14; wherein,
the pressure oil inlet 10 is connected with a pressure oil source and used for guiding pressure oil into the interceptor slide valve 13;
the pressure oil outlet 11 for outputting the pressure oil flowing out from the shutoff spool 13;
the oil return line 12 is configured to return the pressure oil flowing out of the shutoff spool 13 to a pressure oil source;
the interceptor slide valve 13 is respectively connected to the pressure oil inlet 10, the pressure oil outlet 11, the oil return pipeline 12 and the reset control element 14, and is used for guiding the pressure oil flowing out of the interceptor slide valve 13 into the oil return pipeline 12 when the pressure of the pressure oil outlet 11 is instantly reduced;
the reset control element 14 is connected to the pressure oil inlet 10, and is configured to control the pressure oil flowing through the shutoff spool 13 to be introduced into the pressure oil outlet 11 when the pressure difference between the pressure oil inlet 10 and the pressure oil outlet 11 is within a normal range.
It can be seen that the hydraulic blocking valve provided by the above embodiment is applied to a hydraulic control system, and the blocking slide valve included in the hydraulic blocking valve can automatically judge the working state of the outlet pressure oil pipeline of the hydraulic system, when the pressure of the outlet is instantly reduced, the pipeline of the outlet pressure oil pipeline can be determined to be broken, so that a response can be made instantly, the pressure oil delivered by a pressure oil source can be immediately cut off, and meanwhile, the pressure oil at the outlet can be introduced into a non-pressure oil return pipeline, so that the pressure source of the oil at the broken pipeline is eliminated, and the high-pressure oil cannot be splashed in a mist form, thereby avoiding the fire accident caused by the fact that the wear-resistant hydraulic oil leaks and splashes to a high-temperature object due to the breakage; in addition, the hydraulic system can be also suitable for other hydraulic systems, and can be used for avoiding economic loss and production environment pollution caused by leakage of a large amount of hydraulic oil after the high-pressure pipeline is broken.
In order to facilitate a further understanding of the invention, the invention is described in detail below with reference to specific embodiments thereof.
In a specific implementation, as shown in fig. 2, the shutoff spool 13 specifically includes:
an oil inlet valve port 131 connected with the pressure oil inlet, an oil outlet valve port 132 connected with the pressure oil outlet, an oil return valve port 133 connected with the oil return pipeline, a reset valve port 134 connected with the reset control element, and a valve core 135 tightly attached to the valve sleeve 130 and capable of moving up and down in the valve sleeve 130 are arranged on the valve sleeve 130 from top to bottom; a valve body 136 sealing the valve housing 130; the valve body 136 generally serves to protect the valve sleeve 130 and valve core 135 therein;
as shown in fig. 3, the valve spool 135 includes:
a first valve core 1350, a second valve core 1351 and a third valve core 1352 which are fixedly connected from top to bottom; the lower surface area S2 of the third valve core 1352 contacting pressure oil is larger than the surface area S0 of the connection part of the first and second valve cores (1350, 1351) contacting pressure oil and smaller than the surface area S1 of the connection part of the second and third valve cores (1351, 1352) contacting pressure oil.
In the embodiment of the invention, the first valve core, the second valve core and the third valve core are of an integrated structure, and when the valve sleeve moves up and down, the first valve core, the second valve core and the third valve core move integrally.
In addition, when the valve is implemented, the reset control element can be a solenoid directional valve.
When the pressure of the pressure oil outlet is reduced instantly, the third valve core moves to the bottom of the valve sleeve, so that the second valve core blocks the oil inlet valve port, the oil outlet valve port is communicated with the oil return valve port, namely, pressure oil conveyed by a pressure oil source is cut off, and meanwhile, pressure oil at the outlet can be introduced into a non-pressure oil return pipeline; when the reset valve port receives pressure oil introduced by the reset control element, the first valve core moves to the top of the valve sleeve, so that the third valve core blocks the oil return valve port, the oil inlet valve port is communicated with the oil outlet valve port, and normal output of the pressure oil is ensured when an outlet pressure oil pipeline is normal.
The control principle of the hydraulic shutoff valve in the embodiment of the present invention will be described in detail below with reference to the drawings, taking the return control element as an example of the electromagnetic directional valve.
The embodiment of the invention adopts the hydraulic control principle of oil pressure sampling of an oil inlet and an oil outlet, and pressure oil of a system firstly enters an inlet of the interceptor slide valve and then is connected to each actuator on site through an outlet of the interceptor slide valve. The pressure difference of the oil inlet and the oil outlet of the blocking slide valve is used as a judgment basis, and the characteristic that the stress of the valve core of the blocking slide valve is unbalanced is utilized, so that once the external high-pressure pipeline is broken, the pressure in the outlet pipeline is inevitably and instantly reduced greatly, the pressure difference of the inlet and the outlet of the blocking slide valve is instantly increased, the valve core of the blocking slide valve can instantly act, the pressure oil is immediately cut off after the valve core acts, and simultaneously, the pressure of the external pipeline is instantly discharged together with the oil in the oil pipeline with the leakage fault together with the oil.
When the hydraulic block valve in the embodiment of the invention is applied, the installation position of the hydraulic block valve is at the same position as a pressure oil source (such as a pump station), the pressure oil of the oil source firstly enters the block slide valve and then is directly connected into a high-pressure pipeline of a system through an outlet pipeline of the block slide valve, a broken pipeline is usually arranged at the outlet side of the hydraulic block valve, namely a pipeline connected with an oil outlet valve port, and when the pipeline connected with the oil outlet valve port is broken due to external force, the pressure in the pipeline at the section is instantly and greatly reduced, and the amplitude is usually over 80%.
As shown in fig. 4, when the hydraulic blocking valve starts to be activated, the electromagnetic directional valve is in an initial power-off state, pressure oil of a pressure oil source enters from an oil inlet valve port (i.e., valve port 4) on the blocking slide valve, and meanwhile, the pressure oil is also introduced into an oil inlet "P" cavity of the electromagnetic directional valve. At this time, the valve core of the interceptive slide valve is positioned at the bottom of the valve sleeve (not shown in the figure), so that the valve port 2 and the valve port 3 are connected, wherein the valve port 2 is an oil return valve port and is connected with the non-pressure oil return pipeline 12, the valve port 3 is an oil outlet valve port and is connected with the pressure oil outlet pipeline, and the valve core of the interceptive slide valve plugs the oil inlet valve port, so that the pressure oil at the oil outlet valve port is led into the oil return pipeline. At this time, the shutoff spool valve is in the "shutoff position valve state". The force diagram of the valve core is shown in fig. 5, and the specific dimensions of the first valve core, the second valve core and the third valve core are also shown in fig. 5, and the following configurations can be obtained:
| calculation of the stressed area of each surface of the valve core |
| Annular area S3 ═ (pi/4) × (25)2-202)＝176.71mm2 |
| Annular area S0 ═ (pi/4) × (30)2-202)＝392.69mm2 |
| Annular area S1 ═ (pi/4) × (30)2-152)＝530.14mm2 |
| Annular area S4 ═ (pi/4) × (20)2-152)＝137.44mm2 |
| Circular area S2 ═ (pi/4) × (20)2)＝314.16mm2 |
| Valve spool force calculation |
| The valve element component force F1 (S0-S3) 215.98 (P) |
| The valve element component force F2 (P) (S1-S4) 392.7 (P) |
| Valve core resultant force F-F2-F1-176.72P |
| Valve core reset force F3 ═ P ═ S2 ═ 314.16 ═ P |
Assuming that the pressure generated by the source pressure oil is P, the force F1 acting on the annular area S0 of the connection between the first and second valve spools contacting the pressure oil is 215.98 × P, and no oil pressure acts on the annular area S1 of the connection between the second and third valve spools contacting the pressure oil and the annular area S2 of the third valve spool contacting the pressure oil, so that the position of the valve spool is only at the bottom of the valve sleeve, i.e., the "blocking position", due to the pressure F1.
When the shutoff slide valve is required to work normally, namely the shutoff slide valve is utilized to guide the pressure oil flowing through to a high-pressure pipeline, at the moment, the electromagnetic directional valve needs to be electrically or locally manually reset, and the principle of the resetting of the electromagnetic directional valve is as follows: pressure oil led into an oil inlet cavity P inside the electromagnetic valve is led into a working oil port cavity B connected with a reset valve port of the blocking slide valve and then enters the reset valve port of the blocking slide valve, namely valve port 1, at the moment, the valve core is analyzed by combining with figure 5, the force F3 which acts on the circular area S2 is 314.16P, F3 is more than F1, the valve core of the blocking slide valve is quickly moved up to the top of the valve sleeve to block an oil return valve port (valve port 2), and as shown in figure 6, the valve core of the blocking slide valve is in a working position valve core state at the moment, the pressure oil of an oil source is led into an oil outlet valve port (valve port 3) from an oil inlet valve port (valve port 4) and then enters high-pressure pipelines such as a field execution structure and the.
It should be noted that when the electromagnetic directional valve performs the directional operation, the directional operation time usually needs to last about 5 seconds, which is to allow the pipeline connected with the oil outlet valve port (valve port 3) to have sufficient time to be filled with the pressure oil and to build up the working oil pressure. After 5 seconds, the electromagnetic directional valve recovers the initial power-off state, namely pressure oil in the reset valve port (valve port 1) is discharged, at the moment, the valve core of the slide valve can be automatically kept at the position of the top of the valve sleeve, and the principle is as follows: when the spool of the slide valve moves to the top of the valve sleeve, the oil pressure of the oil outlet port (port 3) is established, and the stress condition of the shutoff valve core at the moment is analyzed by combining with fig. 5, the force F2 acting on the annular area S1 on the shutoff valve core is 392.7P, the force F1 acting on the annular area S0 on the shutoff valve core is 215.98P, the direction of the force F1 is opposite to F2, the resultant force F2-F1P applied to the shutoff valve core is 176.72P > 0, and the direction of the resultant force is upward. For a general hydraulic system, during normal operation, the oil pressure is constant, that is, the pressure of an oil inlet valve port and the pressure of an oil outlet valve port of the shutoff valve spool are equal, so that the stress of the shutoff valve spool is kept unchanged, the short valve spool can be kept at the position of the top of the valve sleeve to maintain the normal operating pressure of the system, and the pressure of the oil outlet valve port has small fluctuation and cannot greatly influence the keeping position of the shutoff valve spool.
If the external high-pressure pipeline is broken, the pressure in the pipeline is instantly and greatly reduced, the amplitude can exceed 80%, at this time, the shutoff slide valve can automatically judge the oil pressure state of the oil outlet valve port, the stress condition of the valve core at this time is still analyzed by combining with fig. 5, because the pressure of the oil outlet valve port (valve port 3) is instantly reduced, the pressure acting on the annular area S1 is also instantly reduced, so that the pressure F2 is instantly and greatly reduced, as long as the instantaneous amplitude of the F2 exceeds 45% P, the resultant force F1-F2 which is applied to the shutoff valve core is more than 0, the valve core is instantly moved to the bottom of the valve sleeve under the action of the pressure F1, the oil inlet valve port (valve port 4) of the oil source is blocked, the oil outlet valve port (valve port 3) and the oil return valve port (valve port 2) are connected, the valve core moves to the shutoff position, the pressure oil source in the broken pipeline is cut off, and no continuous pressure oil source exists, oil can not be sprayed out, so that fire can not be started, and the effects of fire prevention and blocking and pressure oil splashing can be achieved.
When the embodiment of the invention is implemented specifically, the electromagnetic valve can be a 6-path electromagnetic directional valve. The solenoid valve has simple control mode and stable performance, has two reset operation modes of remote and local, and can be specifically set according to the practical application environment. The electromagnetic directional valve can be fixedly connected to the top of the valve body, for example: may be mounted on top of the shutoff slide valve by bolts.
In addition, the shutoff slide valve adopts a slide valve type structural design, parts such as a valve core, a valve sleeve, a valve body and the like can be completely machined, the machining process is simple, the valve core and the valve sleeve of the slide valve are made of high-quality alloy steel materials, the hardness and the wear resistance are very good, the requirement on the dimensional accuracy of the valve core and the valve sleeve is high, and the sealing effect is ensured.
The blocking slide valve is integrally designed and manufactured, the blocking slide valve and the reset electromagnetic valve are integrated, and the internal oil return pipeline is processed on the valve body of the blocking slide valve, so that the integral structure is more compact, the external space is saved, and the design difficulty of the whole volume and the installation of the valve block is reduced. When the hydraulic blocking valve is applied, the required blocking control task can be completed only by installing the bottom of the hydraulic blocking valve on a matched oil circuit block through a bolt. The hydraulic blocking valve can continuously work for years without any maintenance, and is an energy-saving design.
The hydraulic fire-proof block valve can also be used for preventing hydraulic oil of external pipelines from leaking, and is used as an oil-proof liquid leakage valve, so that the application range of the hydraulic fire-proof block valve is expanded. If the number of the on-site high-pressure pipelines is too large, the number of on-site actuating mechanisms is too large, and meanwhile, the actuators are widely and complexly distributed, the blocking valves can be arranged in a multi-stage layered mode, and the loss caused by pipeline breakage is reduced to the maximum extent.
The foregoing is merely a preferred embodiment of the invention and is not intended to limit the invention in any manner.
Although the present invention has been described with reference to the preferred embodiments, it is not intended to be limited thereto. Those skilled in the art can make numerous possible variations and modifications to the present invention, or modify equivalent embodiments, using the methods and techniques disclosed above, without departing from the scope of the present invention. Therefore, any simple modification, equivalent change and modification made to the above embodiments according to the technical essence of the present invention are still within the scope of the protection of the technical solution of the present invention, unless the contents of the technical solution of the present invention are departed.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the embodiments. Thus, the present embodiments are not intended to be limited to the embodiments shown herein but are to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (9)
1. A hydraulic interrupter valve, comprising: the device comprises a pressure oil inlet, a pressure oil outlet, an oil return pipeline, a shutoff slide valve and a reset control element; wherein,
the shutoff spool specifically includes:
the valve core is tightly attached to the valve sleeve and can move up and down in the valve sleeve; a valve body sealing the valve housing;
the pressure oil inlet is connected with a pressure oil source and used for guiding pressure oil into the interceptor slide valve;
the pressure oil outlet is used for outputting the pressure oil flowing out of the shutoff slide valve;
the oil return pipeline is used for returning the pressure oil flowing out of the interceptor slide valve to a pressure oil source;
the interceptor slide valve is respectively connected with the pressure oil inlet, the pressure oil outlet, the oil return pipeline and the reset control element and is used for guiding the pressure oil flowing out of the interceptor slide valve into the oil return pipeline when the pressure of the pressure oil outlet is instantly reduced;
the reset control element is connected with the pressure oil inlet and is used for controlling the pressure oil flowing through the shutoff slide valve to be led into the pressure oil outlet when the pressure difference between the pressure oil inlet and the pressure oil outlet is in a normal range;
wherein the valve spool includes:
the first valve core, the second valve core and the third valve core are fixedly connected from top to bottom; the lower surface area of the third valve element contacting the pressure oil is larger than the surface area of the joint of the first valve element and the second valve element contacting the pressure oil and smaller than the surface area of the joint of the second valve element and the third valve element contacting the pressure oil;
when the pressure of the pressure oil outlet is reduced instantly, the third valve core moves to the bottom of the valve sleeve, so that the second valve core blocks the oil inlet valve port, and the oil outlet valve port is communicated with the oil return valve port; when the reset valve port receives pressure oil introduced by the reset control element, the first valve core moves to the top of the valve sleeve, so that the third valve core blocks the oil return valve port, and the oil inlet valve port is communicated with the oil outlet valve port.
2. The hydraulic interrupter valve of claim 1 wherein the first, second, and third spools are of a unitary construction.
3. The hydraulic interrupt valve of claim 1, wherein the reset control element is a solenoid directional valve.
4. The hydraulic interrupter valve of claim 3 wherein the solenoid diverter valve is a 6-way solenoid directional valve.
5. The hydraulic interrupter valve of claim 1 wherein the spool is an alloy steel material.
6. The hydraulic interrupter valve of claim 1 wherein the valve housing is an alloy steel material.
7. The hydraulic interrupter valve of claim 1 wherein the reset control member is fixedly attached to the top of the valve body.
8. The hydraulic interrupt valve of claim 7, wherein the reset control element is secured by bolting.
9. The hydraulic interrupter valve of claim 1 wherein the reset control element is remotely controlled or locally operated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110106902 CN102168699B (en) | 2011-04-27 | 2011-04-27 | Hydraulic interceptor valve |
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| Application Number | Priority Date | Filing Date | Title |
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| CN 201110106902 CN102168699B (en) | 2011-04-27 | 2011-04-27 | Hydraulic interceptor valve |
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| Publication Number | Publication Date |
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| CN102168699A CN102168699A (en) | 2011-08-31 |
| CN102168699B true CN102168699B (en) | 2013-08-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201110106902 Active CN102168699B (en) | 2011-04-27 | 2011-04-27 | Hydraulic interceptor valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110593965B (en) * | 2019-08-19 | 2022-08-09 | 北京博力威格智能传控设备有限公司 | Main valve shutoff valve group, control method thereof and steam turbine |
Citations (4)
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|---|---|---|---|---|
| CN1235248A (en) * | 1999-05-06 | 1999-11-17 | 厦门大学 | Explosive-proof electromagnetic valve |
| CN101025127A (en) * | 2006-02-24 | 2007-08-29 | 同济大学 | Axial-symmetric vector spray-tube A9/A8 area ratio dislocation protection hydraulic system |
| CN101025128A (en) * | 2006-02-24 | 2007-08-29 | 同济大学 | Axial symmetric vector spray-pipe A9 action emergency resetting hydraulic system |
| CN201322016Y (en) * | 2008-12-26 | 2009-10-07 | 迪斯油压工业(昆山)有限公司 | Oil pipe explosion-proof device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6409142B1 (en) * | 1999-10-20 | 2002-06-25 | Hitachi Construction Machinery Co. Ltd. | Pipe breakage control valve device |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1235248A (en) * | 1999-05-06 | 1999-11-17 | 厦门大学 | Explosive-proof electromagnetic valve |
| CN101025127A (en) * | 2006-02-24 | 2007-08-29 | 同济大学 | Axial-symmetric vector spray-tube A9/A8 area ratio dislocation protection hydraulic system |
| CN101025128A (en) * | 2006-02-24 | 2007-08-29 | 同济大学 | Axial symmetric vector spray-pipe A9 action emergency resetting hydraulic system |
| CN201322016Y (en) * | 2008-12-26 | 2009-10-07 | 迪斯油压工业(昆山)有限公司 | Oil pipe explosion-proof device |
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