CN106931176B - Expansion opening blow-off valve for blast furnace - Google Patents

Expansion opening blow-off valve for blast furnace Download PDF

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Publication number
CN106931176B
CN106931176B CN201710113502.9A CN201710113502A CN106931176B CN 106931176 B CN106931176 B CN 106931176B CN 201710113502 A CN201710113502 A CN 201710113502A CN 106931176 B CN106931176 B CN 106931176B
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CN
China
Prior art keywords
valve
diffusing
cylinder
valve cover
hydraulic
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CN201710113502.9A
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CN106931176A (en
Inventor
凌云
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Huatian Engineering and Technology Corp MCC
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Huatian Engineering and Technology Corp MCC
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/36—Valve members
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21B—MANUFACTURE OF IRON OR STEEL
    • C21B7/00—Blast furnaces
    • C21B7/002—Evacuating and treating of exhaust gases
    • C21B7/005—Bleeder valves or slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/023—Excess flow valves, e.g. for locking cylinders in case of hose burst
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/007—Overload
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/087—Control strategy, e.g. with block diagram
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/003—Safety valves; Equalising valves, e.g. pressure relief valves reacting to pressure and temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow control valve

Abstract

The invention discloses a telescopic opening bleeding valve for a blast furnace, which comprises a cylindrical valve body and a valve cover hermetically matched with the upper surface of the valve body; the lower surface of the valve cover is provided with a diffusing cylinder, the outer wall of the diffusing cylinder is in sliding sealing fit with the inner wall of the valve body, the side wall of the diffusing cylinder is provided with a plurality of diffusing through holes, and the lower edge of each diffusing through hole and the lower end of the diffusing cylinder are arranged at intervals; the valve body is provided with a support, the support is provided with a plurality of stand columns, the top end of each stand column is connected with a top plate, and the lower surface of the top plate is connected with the upper end of one or more telescopic devices; the lower end of the telescopic device is connected with the upper surface of the valve cover; the distance between the lower edge of the diffusing through hole and the lower surface of the valve cover is not more than the difference between the maximum length and the minimum length of the telescopic device; the length of the upright post is equal to the maximum length of the telescopic device. The valve cover and the diffusing cylinder are driven to move through the telescopic device, and the gas is diffused through the diffusing holes in the diffusing cylinder, so that the valve body is prevented from being swept, and the service life of the valve body is prolonged.

Description

Expansion opening blow-off valve for blast furnace
Technical Field
The invention relates to a telescopic opening bleeding valve for a blast furnace.
Background
The blow-off valve is a key device of a blow-off system of the crude gas of the iron-making blast furnace and is arranged at the top end of a gas ascending pipe. The main function is that when the blast furnace stops blowing, the relief valve is opened to relieve the pressure in the furnace. In addition, the bleeding valve also plays a role in safety protection for the blast furnace and equipment facilities, and when the pressure of the furnace top exceeds the set pressure, the bleeding valve needs to be automatically opened.
The traditional bleeding valve has two problems, firstly, when the gas is diffused, the blowing and sweeping of the sealing surface of the valve seat are carried out, because a large amount of granular dust is contained in the gas, the gas directly erodes on the sealing surface of the valve seat, the adverse effect can be generated on the service life of the gas, secondly, when the bleeding valve plays a safety protection role, the effect of the disc spring in the valve cover is mainly relied on, when the pressure of the furnace top is greater than the pressure of the disc spring on the valve cover, the valve cover is opened, but at the moment, the bleeding valve is not completely opened, only partially opened, even a small section of gap is opened, so the gas erodes the sealing surfaces of the valve seat and the valve cover very severely, and under the working condition, the bleeding valve can be damaged very quickly.
Disclosure of Invention
In order to solve the problems, the invention provides a telescopic opening bleeding valve for a blast furnace, which can prevent a valve body from being blown.
In order to achieve the aim, the telescopic opening bleeding valve for the blast furnace comprises a cylindrical valve body and a valve cover in sealing fit with the upper surface of the valve body;
the valve cover comprises a valve cover body and a diffusing cylinder connected with the lower surface of the valve cover body, the outer wall of the diffusing cylinder is in sliding sealing fit with the inner wall of the valve body, a plurality of diffusing through holes are formed in the side wall of the diffusing cylinder, and the lower edge of each diffusing through hole and the lower end of the diffusing cylinder are arranged at intervals;
the valve body is provided with a support, the support is provided with a plurality of upright posts, the top end of each upright post is connected with a top plate, and the lower surface of the top plate is connected with the upper ends of one or more telescopic devices;
the lower end of the telescopic device is connected with the upper surface of the valve cover;
the distance between the lower edge of the diffusing through hole and the lower surface of the valve cover is not more than the difference between the maximum length and the minimum length of the telescopic device; the length of the upright column is equal to the maximum length of the telescopic device.
Further, the top plate is connected with the valve cover through a telescopic device, and the axis of the telescopic device is overlapped with the axis of the valve cover;
the telescopic device is a hydraulic cylinder or an air cylinder;
the rod cavity and the rodless cavity of the hydraulic cylinder or the air cylinder are respectively communicated with the positive action liquid outlet/air hole and the reverse action liquid outlet/air hole of the two-position five-way valve; the air inlet of the two-position five-way valve is communicated with an air/hydraulic source;
and a pressure sensor is arranged on an oil path of a rod cavity or a rodless cavity of the hydraulic cylinder or the air cylinder, the pressure sensor is in communication connection with a controller, and the controller controls the electromagnetic valve.
Further, the valve cover is connected with the top plate through more than one hydraulic cylinder;
the hydraulic cylinders are uniformly distributed on the edge of the valve cover along the circumferential direction of the valve cover, and the axis of each hydraulic cylinder is parallel to the axis of the valve cover.
Furthermore, a hydraulic control device is arranged on an oil path of each hydraulic cylinder, each hydraulic control device comprises an electromagnetic directional valve, a hydraulic lock, a double-outlet one-way throttle valve and a secondary pressure compensator which are sequentially connected, and the secondary pressure compensator is arranged on an oil inlet pipeline on the side of a rodless cavity of each hydraulic cylinder; and a load feedback oil path is also arranged between the oil inlet at the rodless cavity side of the hydraulic cylinder and a secondary pressure compensator of a hydraulic control device of the hydraulic cylinder, the oil inlet at the rodless cavity side of each hydraulic cylinder is respectively connected with the load feedback oil path, the spring side of the secondary pressure compensator is connected with the load feedback oil path, and the oil inlet at the rodless cavity side of each hydraulic cylinder is connected with a one-way valve for leading pressure oil to the load feedback oil path.
Further, a brake valve is connected between the secondary pressure compensator and the double-outlet one-way throttle valve.
Furthermore, an overflow valve is arranged on the load feedback oil path.
Further, the telescopic device comprises a hydraulic cylinder, an air cylinder, an electric cylinder or an electro-hydraulic push rod.
Further, the interior of the diffusing cylinder is a conical cavity, and the small-diameter end of the conical cavity faces downwards.
Furthermore, a set of fan blades is arranged at the bottom of the diffusing cylinder, the fan blades are uniformly distributed along the circumferential direction of the cylinder body, and the fan blades are obliquely arranged along the circumferential direction.
Furthermore, the lower surface of the valve cover is connected with a support column, at least one circle of spiral fan blades are arranged on the support column, and the length of each spiral fan blade along the axial direction of the diffusing cylinder is the same as that of the diffusing cylinder;
the outer edge of the spiral fan blade is connected with the inner wall of the diffusing cylinder.
According to the telescopic opening bleeding valve for the blast furnace, when gas is bled, the telescopic device acts to pull the valve cover to be opened upwards, the bleeding cylinder is exposed out of the valve body, the gas is bled outwards from the bleeding cylinder, and the bottom of the bleeding cylinder is provided with the solid ring, so that the valve seat is prevented from being swept by the gas. When the coal gas is required to be closed after being diffused, the telescopic device acts to push the valve cover to move downwards and close the diffusion valve.
Drawings
FIG. 1 is a schematic view of a push-to-open hydraulic cylinder for a blast furnace according to the present invention at the time of closing in embodiment 1;
FIG. 2 is a schematic view of the blast furnace of the present invention when the embodiment 1 of the push-to-open hydraulic cylinder is opened;
FIG. 3 is a positive-acting hydraulic schematic diagram of embodiment 1 of a push-to-open hydraulic cylinder for a blast furnace according to the present invention;
FIG. 4 is a reverse-acting hydraulic schematic diagram of embodiment 1 of a push-to-open hydraulic cylinder for a blast furnace according to the present invention;
FIG. 5 is a hydraulic schematic diagram of embodiment 2 of a push-to-open hydraulic cylinder for a blast furnace according to the present invention.
Detailed Description
The invention is further described with reference to the accompanying drawings.
Example 1
As shown in fig. 1-4, the embodiment provides a telescopic opening bleeding valve for a blast furnace, which comprises a cylindrical valve body 1 and a valve cover 2 hermetically matched with the upper surface of the valve body 1;
the valve cover 2 comprises a valve cover body 21 and a diffusing cylinder 22 connected to the lower surface of the valve cover body 21, the outer wall of the diffusing cylinder 22 is in sliding sealing fit with the inner wall of the valve body 1, a plurality of diffusing through holes are formed in the side wall of the diffusing cylinder 22, and the lower edge of each diffusing through hole is arranged at an interval with the lower end of the diffusing cylinder 22;
the valve body 1 is provided with a support 3, the support 3 is provided with a plurality of upright posts, the top end of each upright post is connected with a top plate, and the lower surface of the top plate is connected with the upper end of one or more telescopic devices 4;
the lower end of the telescopic device 4 is connected with the upper surface of the valve cover 2;
the distance between the lower edge of the diffusing through hole and the lower surface of the valve cover 2 is not more than the difference between the maximum length and the minimum length of the telescopic device 4; the length of the upright is equal to the maximum length of the telescopic device 4.
The top plate is connected with the valve cover 2 through a telescopic device 4, and the axis of the telescopic device 4 is overlapped with the axis of the valve cover 2;
the telescopic device 4 is a hydraulic cylinder or an air cylinder;
the rod cavity and the rodless cavity of the hydraulic cylinder or the air cylinder are respectively communicated with the positive action liquid outlet/air hole and the reverse action liquid outlet/air hole of the two-position five-way valve 5; the air inlet hole of the two-position five-way valve 5 is communicated with an air/hydraulic source;
and a pressure sensor 6 is arranged on an oil path of a rod cavity or a rodless cavity of the hydraulic cylinder or the air cylinder, the pressure sensor 6 is in communication connection with a controller, and the controller controls the electromagnetic valve.
When the bleeding valve needs to be opened, the hydraulic cylinder acts to pull the valve cover 2 to be opened upwards, the bleeding cylinder 22 is exposed out of the valve body, and the gas is diffused outwards from the bleeding cylinder 22.
When the bleeding valve needs to be closed, the hydraulic cylinder acts to push the valve cover 2 to move downwards, and the bleeding valve is closed.
When the condition of the blast furnace is abnormal and the pressure is overlarge, the hydraulic cylinder is pushed by the valve cover 2, the pressure in the whole hydraulic loop is increased, when the pressure is increased to reach a specified pressure value, the pressure sensor 6 sends a signal, the valve group is controlled to act, the valve cover 2 is opened to be diffused, and accidents are avoided.
Example 2
As shown in fig. 1, 2 and 5, the embodiment provides a telescopic opening bleeding valve for a blast furnace, which comprises a cylindrical valve body 1 and a valve cover 2 hermetically matched with the upper surface of the valve body 1;
a diffusing cylinder 22 is arranged on the lower surface of the valve cover 2, the outer wall of the diffusing cylinder 22 is in sliding sealing fit with the inner wall of the valve body 1, a plurality of diffusing through holes are formed in the side wall of the diffusing cylinder 22, and the lower edges of the diffusing through holes and the lower end of the diffusing cylinder 22 are arranged at intervals;
a support 3 is arranged on the valve body 1, a plurality of stand columns are arranged on the support 3, the top end of each stand column is connected with a top plate, and the lower surface of the top plate is connected with the upper end of one or more telescopic devices 4;
the lower end of the telescopic device 4 is connected with the upper surface of the valve cover 2;
the distance between the lower edge of the diffusing through hole and the lower surface of the valve cover 2 is not more than the difference between the maximum length and the minimum length of the telescopic device 4; the length of the upright column is equal to the maximum length of the telescopic device 4.
The valve cover 2 is connected with the top plate through more than one telescopic device 4; the telescoping device 4 in this embodiment is a hydraulic cylinder.
The hydraulic cylinders are uniformly distributed on the edge of the valve cover 2 along the circumferential direction of the valve cover 2, and the axes of the hydraulic cylinders are parallel to the axis of the valve cover 2.
The oil circuit of each hydraulic cylinder is provided with a hydraulic control device, each hydraulic control device comprises an electromagnetic directional valve 7, a hydraulic lock 8, a double-outlet one-way throttle valve 9 and a secondary pressure compensator 11 which are sequentially connected, and the secondary pressure compensator 11 is arranged on an oil inlet pipeline at the rodless cavity side of each hydraulic cylinder; and a load feedback oil path is also arranged between an oil inlet at the rodless cavity side of the hydraulic cylinder and a secondary pressure compensator 11 of a hydraulic control device of the hydraulic cylinder, an oil inlet at the rodless cavity side of each hydraulic cylinder is respectively connected with the load feedback oil path, the spring side of the secondary pressure compensator 11 is connected with the load feedback oil path, and a check valve 12 for leading pressure oil to the load feedback oil path is connected at an oil inlet at the rodless cavity side of each hydraulic cylinder.
In this embodiment, the valve cover 2 is pulled and pushed by a plurality of hydraulic cylinders, and when a plurality of hydraulic cylinders are used, it is necessary to ensure that the actions of the hydraulic cylinders are synchronous, otherwise the bleeding cylinder 22 may be deflected, and damage may be easily caused to the bleeding cylinder 22 or the valve seat.
In the present embodiment, a hydraulic control system of the valve cap 2 is described by taking as an example a hydraulic control system of the valve cap 2 that uses two hydraulic cylinders to realize the operation of the valve cap 2, where the P end is an oil inlet end of the hydraulic control system of the valve cap 2, and the T end is an oil outlet end of the hydraulic control system of the valve cap 2. The first hydraulic cylinder corresponds to a first group of hydraulic control devices, the second hydraulic cylinder corresponds to a second group of hydraulic control devices, and the first group of hydraulic control devices and the second group of hydraulic control devices form a valve cover 2 hydraulic control system. The hydraulic control device of first group, second group all include the hydraulic pressure lock 8 that solenoid directional valve 7, 7 rear ends of solenoid directional valve are connected, the two export one-way choke valve 9 of hydraulic pressure lock 8 rear end connection, the rear end of two export one-way choke valves 9 is provided with secondary pressure compensator 11, secondary pressure compensator 11 set up on the oil inlet pipe of hydraulic cylinder rodless chamber side oil inlet department, simultaneously the spring side of secondary pressure compensator 11 and hydraulic cylinder rodless chamber side oil inlet department are connected with the load feedback oil circuit.
The secondary pressure compensator 11 and the end close to the double-outlet one-way throttle valve 9 are upstream of the secondary pressure compensator 11, and the secondary pressure compensator 11 and the end close to the hydraulic cylinder are downstream of the secondary pressure compensator 11.
The pipeline at the side oil inlet of the rodless cavity of each hydraulic cylinder is connected with a check valve 12, the check valve 12 is positioned at the downstream of the secondary pressure compensator 11, namely the oil inlet pipeline of the check valve 12 is arranged between the secondary pressure compensator 11 and the oil inlet at the side of the rodless cavity of the hydraulic cylinder, the outlet oil paths of all the check valves 12 are connected in parallel, so that the pressure at the side oil inlet of the rodless cavity of each hydraulic cylinder is unified into a load feedback oil path, and the spring side of the secondary pressure compensator 11 is communicated with the load feedback oil path.
When the valve cover 2 system works, the rod cavity of the hydraulic cylinder begins to extend, the side pressure of the rodless cavity begins to build, and a load is formedPressure P L The load pressure P of each hydraulic cylinder is different due to the difference in the opening degree of the outlet throttle valve of each hydraulic cylinder and the difference in the pushing load of each hydraulic cylinder L It will be different that the pressure at the outlet of the check valve 12 is equal to the maximum value P of the load pressures of all the hydraulic cylinders since the outlet ends of all the check valves 12 are connected in the same oil line pipe Lmax I.e. the pressure in the load feedback circuit is the maximum value of the load pressure of all hydraulic cylinders, and since the load feedback circuit is connected to the spring side of each secondary pressure compensator 11, the pressure experienced by each secondary pressure compensator 11 is the pressure in the load feedback circuit, i.e. the maximum value P of the load pressure of all hydraulic cylinders Lmax 。
The spring set pressure difference of all the secondary pressure compensators 11 is Δ P a So that the upstream pressure P of each secondary pressure compensator 11 S ＝P Lmax +ΔP a Equal, because the valve groups are communicated with each other by the oil supply pipe, the pressure P before the oil way enters the electromagnetic directional valve 7 P Are uniform, so that the pressure difference ap from the inlet of the electromagnetic directional valve 7 to the upstream of the secondary pressure compensator 11 b ＝P P -P S And are also equal.
Since the electromagnetic directional valve 7 is fully opened after being energized, the opening degree of each hydraulic lock 8 and the one-way throttle valve 9 on the inlet side can also be considered to be the same, and the differential pressure Δ P from the inlet of the electromagnetic directional valve 7 to the upstream of the secondary pressure compensator 11 b And therefore the flow through each pressure compensator is equal, i.e. the flow into the rodless chambers of the cylinders is equal, and since the flow into the cylinders at the same time is equal, the speeds of the cylinders are equal.
Secondly, because the opening degrees of the valve groups on the oil inlet pipelines at the side of the rodless cavity are equal and are not adjustable, the flow entering the rodless cavity of each hydraulic cylinder is controlled by the pressure difference delta P from the inlet of the electromagnetic directional valve 7 to the upstream of the secondary pressure compensator 11 b Determining, i.e. the speed of operation of each cylinder by the pressure difference Δ P b Determined by the pressure P in front of the solenoid valve 7 P The set differential pressure of the secondary pressure compensator 11 is constant, and Δ P is the same a Also does not change, so each hydraulic cylinderSpeed of the load feedback loop Lmax The maximum working load P is determined by the back pressure generated by the outlet throttle valve of each hydraulic cylinder and the load to be pushed, and since the load pressure of the hydraulic cylinder against the weight of the rod wire is smaller than the back pressure generated by the outlet throttle valve and the load pressure against the weight of the rod is not adjustable, it can be considered that the maximum working load P is Lmax The outlet throttle valve which produces the largest back pressure, i.e. the smallest opening, i.e. the speed of each cylinder is determined by the outlet throttle valve which has the smallest opening. In actual use, the opening degrees of other throttle valves are adjusted to be the maximum, the opening degree of one throttle valve is intentionally adjusted to be proper, and the corresponding hydraulic cylinders generate the maximum back pressure in all the hydraulic cylinders, so that the purposes of controlling the action speed of the hydraulic cylinders of the whole system and realizing synchronization by only operating one throttle valve can be realized.
The valve cover 2 hydraulic control system of the embodiment adopts the load feedback oil path to lead the spring side of the pressure compensator at the oil inlet of the rodless cavity side of the hydraulic cylinder to the maximum load pressure when each hydraulic cylinder acts, so that the pressure on the upstream of the pressure compensator is ensured to be consistent, the oil inlet amount of each hydraulic cylinder is the same, the action synchronization of each hydraulic cylinder is realized, and the influence caused by the asynchronization of each valve cover 2 hydraulic cylinder is avoided. And the feedback oil circuit unifies the load of each hydraulic cylinder into the maximum pressure load, and the maximum load pressure is the load pressure of the hydraulic cylinder with the minimum opening of the one-way throttle valve 9, so that the action speed of the hydraulic cylinder of the whole system can be controlled by only operating one throttle valve by reducing the opening of the throttle valve at the oil circuit outlet of one hydraulic cylinder, and the aim of synchronization is fulfilled. Meanwhile, the hydraulic control system of the valve cover 2 has a simple structure, does not need to install complex pipelines, and achieves good synchronization effect of the hydraulic cylinders by using smaller cost and space.
On the basis of the hydraulic control system of the valve cover 2, a brake valve 10 is connected between each secondary pressure compensator 11 and the double-outlet one-way throttle valve 9, the brake valves 10 are connected with a two-way overflow valve 13 in a group, and the two-way overflow valve 13 can adjust the overflow pressure on two sides of each brake valve 10, so that the highest pressure on two sides of each hydraulic cylinder is well limited, hydraulic elements, the hydraulic oil cylinders and hydraulic oil pipes are effectively protected, and the phenomenon of overlarge long shaft torque is prevented.
A relief valve 13 is provided in the load feedback oil path on the basis of the hydraulic control system. The overflow valve 13 can limit the highest load pressure and prevent the valve bank from being blocked.
Example 3
On the basis of any of the above embodiments, the interior of the diffusion cylinder 22 is a tapered cavity, and the small diameter end of the tapered cavity faces downward. The diffusing cylinder 22 in this embodiment is tapered, and the flow speed of the diffusing gas in the diffusing cylinder 22 is gradually reduced, so that the speed of the diffusing gas flowing out of the diffusing holes is reduced, and the whistle noise during diffusing the gas can be reduced to a certain extent.
Example 4
On the basis of embodiment 1 or 2, a set of fan blades is arranged at the bottom of the diffusing cylinder 22, each fan blade is uniformly distributed along the circumferential direction of the cylinder body, and each fan blade is obliquely arranged along the circumferential direction. When the diffused gas passes through the fan blades, the flow direction of the diffused gas is changed by the fan blades, so that the diffused gas becomes spiral airflow in the diffusing cylinder 22, the spiral airflow cannot directly rush out of the diffusing holes when passing through the diffusing holes, but is diffused from the tangential direction or at a certain angle with the diffusing holes, and the whistle noise during the diffusion of the gas can be greatly reduced.
Example 5
On the basis of the embodiment 1 or 2, the lower surface of the valve cover 2 is connected with a support column, at least one circle of spiral fan blades are arranged on the support column, and the length of the spiral fan blades along the axial direction of the diffusing cylinder 22 is the same as that of the diffusing cylinder 22; the outer edge of the spiral fan blade is connected with the inner wall of the diffusing cylinder 22. When the diffusion gas enters the diffusion cylinder 22, the diffusion gas flows along the space enclosed between the spiral fan blades and the inner wall of the diffusion cylinder 22. Firstly, the flowing direction of the gas can be changed, so that the gas forms spiral gas flow; secondly, this arrangement corresponds to a plurality of diffusion holes along a spiral path, so that the gas is gradually diffused while flowing along the spiral path. Therefore, the squeaking noise when the gas is discharged can be greatly reduced.
The above description is only a preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are also within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope defined by the claims.

Claims (6)

1. The utility model provides a blast furnace is with flexible valve that diffuses that opens which characterized in that: the valve comprises a cylindrical valve body and a valve cover in sealing fit with the upper surface of the valve body;
the valve cover comprises a valve cover body and a diffusing cylinder connected with the lower surface of the valve cover body, the outer wall of the diffusing cylinder is in sliding sealing fit with the inner wall of the valve body, a plurality of diffusing through holes are formed in the side wall of the diffusing cylinder, and the lower edge of each diffusing through hole and the lower end of the diffusing cylinder are arranged at intervals;
the valve body is provided with a support, the support is provided with a plurality of upright posts, the top end of each upright post is connected with a top plate, and the lower surface of the top plate is connected with the upper ends of one or more telescopic devices;
the lower end of the telescopic device is connected with the upper surface of the valve cover;
the distance between the lower edge of the diffusing through hole and the lower surface of the valve cover is not more than the difference between the maximum length and the minimum length of the telescopic device; the length of the upright column is equal to the maximum length of the telescopic device;
the valve cover is connected with the top plate through more than one hydraulic cylinder;
the hydraulic cylinders are uniformly distributed on the edge of the valve cover along the circumferential direction of the valve cover, and the axes of the hydraulic cylinders are parallel to the axis of the valve cover; the hydraulic control device is arranged on the oil path of each hydraulic cylinder and comprises an electromagnetic directional valve, a hydraulic lock, a double-outlet one-way throttle valve and a secondary pressure compensator which are sequentially connected, and the secondary pressure compensator is arranged on an oil inlet pipeline at the rodless cavity side of the hydraulic cylinder; and a load feedback oil path is also arranged between the oil inlet at the rodless cavity side of the hydraulic cylinder and a secondary pressure compensator of a hydraulic control device of the hydraulic cylinder, the oil inlet at the rodless cavity side of each hydraulic cylinder is respectively connected with the load feedback oil path, the spring side of the secondary pressure compensator is connected with the load feedback oil path, and the oil inlet at the rodless cavity side of each hydraulic cylinder is connected with a one-way valve for leading pressure oil to the load feedback oil path.
2. The telescopically opening bleeding valve for a blast furnace as claimed in claim 1, wherein: and a brake valve is connected between the secondary pressure compensator and the double-outlet one-way throttle valve.
3. The telescopically opening bleeding valve for a blast furnace as claimed in claim 1, wherein: and an overflow valve is arranged on the load feedback oil way.
4. The telescopically opening bleeding valve for a blast furnace as claimed in claim 1, wherein: the inner part of the diffusing cylinder is a conical cavity, and the small-diameter end of the conical cavity faces downwards.
5. The telescopically opening bleed valve for a blast furnace as claimed in claim 1, wherein: the bottom of a diffusing cylinder is provided with a group of fan blades, the fan blades are uniformly distributed along the circumferential direction of the cylinder body of the diffusing cylinder, and the fan blades are obliquely arranged along the circumferential direction.
6. The telescopically opening bleed valve for a blast furnace as claimed in claim 1, wherein: the lower surface of the valve cover is connected with a support column, at least one circle of spiral fan blades are arranged on the support column, and the length of the spiral fan blades along the axial direction of the diffusing cylinder is the same as that of the diffusing cylinder;
the outer edge of the spiral fan blade is connected with the inner wall of the diffusing cylinder.
CN201710113502.9A 2017-02-28 2017-02-28 Expansion opening blow-off valve for blast furnace Active CN106931176B (en)

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CN109237194B (en) * 2018-11-12 2021-01-29 上海宏波工程咨询管理有限公司 Temporary pipeline plugging device and temporary pipeline plugging method
CN110012859A (en) * 2019-05-22 2019-07-16 佛山佛塑科技集团股份有限公司 Adjutage and aquaculture pond self-draining arrangement

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5221583A (en) * 1975-08-07 1977-02-18 Bosch Gmbh Robert Hydraulic control device
US4796665A (en) * 1986-02-07 1989-01-10 Societe Lorraine De Laminage Continu - Sollac Multi-purpose draining valve
CN201651463U (en) * 2010-03-04 2010-11-24 宝山钢铁股份有限公司 Pressure-limiting unloading valve
CN102352932A (en) * 2011-09-26 2012-02-15 中冶赛迪工程技术股份有限公司 Double-sealing mechanical type bleeding valve for gas holder
CN205618696U (en) * 2016-04-21 2016-10-05 上海双高阀门(集团)有限公司 Under open up formula buggy and diffuse governing valve
CN206571997U (en) * 2017-02-28 2017-10-20 中冶华天南京工程技术有限公司 Blast furnace opens diffusion valve with flexible

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5221583A (en) * 1975-08-07 1977-02-18 Bosch Gmbh Robert Hydraulic control device
US4796665A (en) * 1986-02-07 1989-01-10 Societe Lorraine De Laminage Continu - Sollac Multi-purpose draining valve
CN201651463U (en) * 2010-03-04 2010-11-24 宝山钢铁股份有限公司 Pressure-limiting unloading valve
CN102352932A (en) * 2011-09-26 2012-02-15 中冶赛迪工程技术股份有限公司 Double-sealing mechanical type bleeding valve for gas holder
CN205618696U (en) * 2016-04-21 2016-10-05 上海双高阀门(集团)有限公司 Under open up formula buggy and diffuse governing valve
CN206571997U (en) * 2017-02-28 2017-10-20 中冶华天南京工程技术有限公司 Blast furnace opens diffusion valve with flexible

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