CN114992378A - Balanced type stop valve - Google Patents

Balanced type stop valve Download PDF

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Publication number
CN114992378A
CN114992378A CN202210604387.6A CN202210604387A CN114992378A CN 114992378 A CN114992378 A CN 114992378A CN 202210604387 A CN202210604387 A CN 202210604387A CN 114992378 A CN114992378 A CN 114992378A
Authority
CN
China
Prior art keywords
valve
clack
valve clack
balanced
piston rod
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202210604387.6A
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Chinese (zh)
Inventor
张伟鹏
罗学武
邹帅超
吴淑民
陈海涛
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Shanghai Figure Cryogenic Valves Co ltd
Original Assignee
Shanghai Figure Cryogenic Valves Co ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shanghai Figure Cryogenic Valves Co ltd filed Critical Shanghai Figure Cryogenic Valves Co ltd
Priority to CN202210604387.6A priority Critical patent/CN114992378A/en
Publication of CN114992378A publication Critical patent/CN114992378A/en
Pending legal-status Critical Current

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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
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • 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
    • 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
    • F16K1/38—Valve members of conical shape
    • 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
    • F16K1/46—Attachment of sealing rings
    • F16K1/465—Attachment of sealing rings to the valve seats
    • 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
    • F16K31/14—Actuating devices; Operating means; Releasing devices actuated by fluid for mounting on, or in combination with, hand-actuated valves
    • F16K31/143—Actuating devices; Operating means; Releasing devices actuated by fluid for mounting on, or in combination with, hand-actuated valves the fluid acting on a piston
    • 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
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/02—Devices for relieving the pressure on the sealing faces for lift valves
    • F16K39/022—Devices for relieving the pressure on the sealing faces for lift valves using balancing surfaces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/30—Hydrogen technology
    • Y02E60/32—Hydrogen storage

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)

Abstract

The invention relates to the technical field of valves. The balanced stop valve is characterized in that the valve body is internally and longitudinally connected with a valve clack in a sliding manner, a balanced sealing assembly is arranged between the valve body and the valve clack, a balanced space communicated with the outlet flow passage is defined by the valve body and one side of the valve clack away from the valve seat, and a flow guide hole communicated with the outlet flow passage and the balanced space is formed in the valve clack; and a clamping spring for driving the valve clack to cling to the valve seat is also arranged in the valve body. The invention is convenient to provide the thrust when the valve clack is closed by additionally arranging the balance space, and improves the sealing and locking effect. The acting force of a driving mechanism is not needed when locking. The driving mechanism is independently used for opening the valve clack, and the design of miniaturization of the whole valve can be realized.

Description

Balanced type stop valve
Technical Field
The invention relates to the technical field of valves, in particular to a stop valve.
Background
With the rapid development of hydrogen energy in China, the storage and transportation technology of hydrogen is continuously updated, and the problems of low transportation pressure (about 25MPa), large mass of a long-tube trailer used for storage, high transportation cost and the like are gradually highlighted because the existing storage and transportation technology of hydrogen still stays in the transportation mode of a tube bundle vehicle (a long-tube trailer). Therefore, the mode of container hydrogen storage and transportation by adopting the high-pressure wound gas cylinder is also researched and found, the pressure of the gas cylinder can reach 52MPa, and the hydrogen storage density and the transportation cost can be effectively reduced. For the convenience of control, the cylinder valve used in the working condition adopts a pneumatic driving mode and a manual driving mode.
At present, the acting force of the opening and closing of the valve clack of the stop valve of the high-pressure hydrogen cylinder bottle mouth is realized by a transmission device alone, the sealing effect can be ensured only by the increased acting force of the transmission device, and the situation that the volume and the weight of the whole valve cannot be increased is avoided.
At present, a stop valve structure which can be miniaturized, has large flow and is good in sealing is lacked.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides a balanced type stop valve to solve the technical problems.
In order to achieve the purpose, the invention provides a balanced type stop valve, which comprises a valve body, wherein an inlet flow passage and an outlet flow passage are arranged on the valve body, a valve seat and a valve clack for switching the on-off of the inlet flow passage and the outlet flow passage are arranged in the valve body, and a driving mechanism for driving the valve clack to move is arranged on the valve body;
the balance space is communicated with the outlet flow channel all the time through a flow guide hole formed in the valve clack.
And a clamping spring for driving the valve clack to cling to the valve seat is further arranged in the valve body.
The invention reduces the influence of the inlet pressure change on the thrust when the valve clack is sealed by additionally arranging the balance space, and the valve seat always keeps a certain range of stress, thereby improving the sealing and locking effect and prolonging the service life of the sealing element. Through the split type design of the piston rod and the valve clack, the acting force of a driving mechanism is not needed during locking. The driving mechanism is independently used for opening the valve clack, and the design of miniaturization of the whole valve can be realized.
Further preferably, the drive mechanism includes at least one of a cylinder and a manual valve.
Preferably, the driving mechanism comprises a cylinder, the cylinder comprises a cylinder body, a piston and a piston rod assembly, the cylinder body and the valve body enclose an air chamber, and the piston divides the air chamber into an upper air chamber and a lower air chamber which are arranged up and down;
the bottom of the piston rod assembly extends into the valve body, and the piston rod assembly pushes the valve clack to move downwards to be separated from the valve seat.
The valve clack is convenient to move through the cylinder.
Further preferably, the top of the piston rod assembly extends through the piston;
the driving mechanism further comprises a manual valve rod, the manual valve rod is mounted at the top of the cylinder body, and the manual valve rod abuts against the top of the piston rod assembly.
The piston is pushed to move downwards by the manual valve rod.
Further preferably, a piston spring is mounted in the lower chamber.
Further preferably, the upper part of the valve flap cooperates with the valve seat to form a first sealing part, the lower part of the valve flap cooperates with the balance sealing assembly to form a second sealing part, the cross-sectional area of the valve flap at the plane of the first sealing part is S1, and the cross-sectional area of the valve flap at the plane of the second sealing part is S2.
It may be that the difference between S1 and S2 is less than 10% of the average of S1 and S2.
The influence of the difference value of the inlet pressure and the outlet pressure on the opening and closing force value is reduced.
Alternatively, S1 is greater than S2.
Because the balance space is communicated with the outlet flow channel all the time, and S1 is larger than S2, under the action of high pressure in the high-pressure space, the valve clack is subjected to upward force which is larger than downward force, and self-sealing is realized.
Further preferably, the valve flap and the piston rod assembly are arranged independently or the valve flap and the piston rod assembly are arranged in a connected manner.
Preferably, the valve clack and the piston rod assembly are arranged independently;
the center of the top of the valve clack is provided with an inwards concave groove, the valve clack is provided with the vertically arranged flow guide hole, and the flow guide hole is communicated with the groove;
the bottom of the piston rod assembly is embedded into the groove, an auxiliary flow channel is formed in the piston rod assembly, and at least one end of the auxiliary flow channel is always communicated with the outlet flow channel;
when the piston rod assembly abuts against the valve clack, the auxiliary flow channel is in butt joint with the flow guide hole, and the flow guide hole is communicated with the outlet flow channel through the auxiliary flow channel.
The balance space is convenient to be communicated with the outlet flow channel all the time.
Further preferably, the clamping spring is clamped between the valve clack and the valve body. The clamping spring is positioned on one side of the valve clack away from the driving mechanism.
Further preferably, a sealing ring which is propped against the valve clack is arranged on the valve seat;
the top of the valve clack is used for propping against the sealing ring to block the inlet flow passage and the outlet flow passage;
a spring mounting groove is formed in the valve body, the upper end of the clamping spring abuts against the valve clack, the lower end of the clamping spring abuts against the spring mounting groove, and the spring mounting groove is in butt joint conduction with the inlet runner;
the spring mounting groove is located above the balance space.
The installation of the spring is convenient to realize.
As another preferred scheme, the valve flap is connected with the piston rod assembly to form a transmission rod, and the transmission rod is provided with a flow guide hole for communicating the balance space with the outlet flow channel.
Further preferably, the clamping spring is located at least one of between the valve flap and the valve body or within the cylinder.
Has the advantages that:
1. the valve can be in a closed state, the closing force borne by the valve clack only comes from the clamping spring and smaller medium pressure, the extra acting force brought by the cylinder or manual driving is reduced, and the damage to the valve seat when the valve clack is closed at high pressure is reduced.
2. The additional sealing force provided by the design of the cylinder and the factors of how to control the force are considered in the design of the cylinder, and the like, so that the design area of the cylinder is reduced. The overall design of the cylinder is more precise and smaller.
3. The design of the flow guide hole ensures that the valve clack balances the pressure balance of the space and the outlet flow passage in any state.
4. The balanced design, through the area adjustment of S1 and S2, under different pressures, the valve clack stress is close to or equal to the spring force, and the influence of inlet pressure change on the valve clack stress is reduced.
Through the design of balanced type structure, can have following advantage:
A) the acting force for opening the valve clack is reduced, and the external force only needs to overcome the acting force of a valve clack spring and a certain medium acting force; therefore, the cylinder can be further reduced, and the requirement on the installation size on site is met;
B) the requirement of bidirectional sealing can be realized;
when the valve is closed, when outlet pressure is greater than inlet pressure, the medium pressure difference that the valve clack receives is unanimous, and sealing area is unanimous basically, if want to open the valve and need satisfy: f1 < Δ P (S1-S2), the pressure difference Δ P to be opened will be very large because S1 and S2 are relatively close. The closing force under the pressure difference of 52MPa is satisfied. F1 shows that the valve flaps are respectively subjected to the closing force of the clamping springs. Δ P is the pressure difference between the high-pressure space and the equilibrium space, i.e. the pressure difference between the high-pressure space and the outlet space.
C) The flow channel diameter can be increased on the basis of self-sealing by the balanced structure, and the requirement on the flow under the working condition is met.
Drawings
FIG. 1 is a cross-sectional view of embodiment 1 of the present invention;
FIG. 2 is a partially enlarged view of the valve seat in the embodiment 1 of the present invention;
FIG. 3 is a schematic representation of the positions S1 and S2 of the present invention;
fig. 4 is a sectional view of embodiment 2 of the present invention.
Wherein: the device comprises a valve body 1, a balance sealing assembly 2, a pressing block 3, a valve clack 4, a clamping spring 5, a valve seat 6, a push rod 7, a packing sealing assembly 8, a piston spring 9, a piston 10, a cylinder 11, a manual valve rod 12, an inlet flow passage a, a balance space B, a high-pressure space C, an outlet flow passage D, a lower air chamber e, an upper air chamber f, an air inlet interface A, an air outlet interface B, a driving air interface C and a breathing opening D.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
Referring to fig. 1 to 2, embodiment 1: the balanced type stop valve comprises a valve body 1, wherein an inlet flow channel a and an outlet flow channel d are formed in the valve body 1. The valve is provided with an air inlet interface A which is butted with the inlet runner and an air outlet interface B which is butted with the outlet runner. The valve comprises a valve body 1 and is characterized in that a valve seat 6 and a valve clack 4 for switching the on-off of an inlet channel and an outlet channel are installed in the valve body 1, and a driving mechanism for driving the valve clack 4 to move is installed on the valve body 1.
The valve body 1 is longitudinally connected with the valve clack 4 in a sliding manner, a balance sealing assembly 2 is arranged between the valve body 1 and the valve clack 4, a balance space b communicated with the outlet flow channel is defined by the valve body 1 and one side of the valve clack 4 far away from the valve seat 6, and a flow guide hole communicated with the outlet flow channel d and the balance space b is formed in the valve clack 4; and a clamping spring 5 for driving the valve clack 4 to be tightly attached to the valve seat 6 is further arranged in the valve body 1.
The drive mechanism includes at least one of a cylinder 11 and a manual valve stem. The driving mechanism comprises a cylinder 11, the cylinder 11 comprises a cylinder body, a piston 10 and a piston rod assembly, the cylinder body is detachably connected with the valve body 1 to form an air chamber, and the piston 10 divides the air chamber into an upper air chamber f and a lower air chamber e which are arranged up and down; the bottom of the piston rod assembly extends into the valve body 1, and the piston rod assembly pushes the valve flap 4 to move downwards to be separated from the valve seat 6. The bottom of the piston rod component is provided with a mandril 7 used for pushing the valve clack. The valve body 1 is provided with a valve cover, and the valve cover is provided with a packing seal assembly 8 which is connected with the piston rod assembly in a sliding seal manner. The movement of the valve flap 4 is facilitated by means of the cylinder 11. The top of the piston rod assembly penetrates through the piston 10; the driving mechanism further comprises a manual valve rod, the manual valve rod 12 is mounted at the top of the cylinder body, and the manual valve rod 12 abuts against the top of the piston rod assembly. Facilitating the downward movement of the piston 10 by the manual valve stem. And a piston spring 9 is arranged in the lower chamber. The lower end of the piston spring 9 is pressed against the valve cover. The upper air chamber is provided with a driving air interface C. The lower air chamber is provided with a breathing port D communicated with the atmosphere.
The valve flap 4 is arranged independently of the piston rod assembly. The center of the top of the valve clack 4 is provided with an inwards concave groove, the valve clack 4 is provided with the vertically arranged flow guide hole, and the flow guide hole is communicated with the groove; the bottom of the piston rod assembly is embedded into the groove, and an auxiliary flow passage is formed in the piston rod assembly; when the piston rod assembly abuts against the valve clack 4, the auxiliary flow channel is in butt joint with the flow guide hole, and the flow guide hole is communicated with the outlet flow channel through the auxiliary flow channel. The balance space is convenient to be communicated with the outlet flow channel all the time. The clamping spring 5 is clamped between the valve clack 4 and the valve body 1, and the clamping spring is positioned on one side, far away from the driving mechanism, of the valve clack 4.
The valve clack 4 comprises a conical structure and a cylindrical structure, wherein the cross section area of the conical structure and the cylindrical structure gradually increases from top to bottom. The outer diameter of the bottom of the conical structure is larger than that of the cylindrical structure. The clamping spring 5 is sleeved at the cylindrical structure, and the top of the clamping spring 5 is abutted against the bottom of the conical structure. The top of the cone-shaped structure serves as a sealing surface for sealing against the valve seat 6.
A sealing ring which is propped against the valve clack 4 is arranged on the valve seat 6; the top of the valve clack 4 is used for propping against the sealing ring to block the inlet flow passage and the outlet flow passage; a spring mounting groove is formed in the valve body 1, the upper end of the clamping spring 5 abuts against the valve clack 4, the lower end of the clamping spring 5 abuts against the spring mounting groove, and the spring mounting groove is in butt joint conduction with the inlet runner; the spring installation groove is positioned above the balance space. The installation of the spring is convenient to realize. A pressing block 3 is arranged in the valve body 1, and a balance sealing component 2 is clamped between the pressing block 3 and the valve body 1. The bottom of the clamping spring 5 is pressed against the pressing block 3. The pressing block 3 is provided with a limiting groove for limiting the spring.
Referring to fig. 3, the upper portion of the valve flap cooperates with the valve seat to form a first seal, the lower portion of the valve flap cooperates with the balanced seal assembly to form a second seal, the cross-sectional area of the valve flap at the plane of the first seal is S1, and the cross-sectional area of the valve flap at the plane of the second seal is S2; the area difference between the S1 and the S2 is adjusted, and the influence degree of the pressure difference between the inlet flow passage and the outlet flow passage on the valve clack 4 is adjusted.
The difference between S1 and S2 was less than 10% of the average of S1 and S2. The influence of the pressure difference on the opening and closing force value is reduced. It may be that S1 is greater than S2. Because the balance space is communicated with the outlet flow channel all the time, and S1 is greater than S2, under the action of high pressure in the high-pressure space, the valve clack is subjected to upward force which is greater than downward force, and self-sealing is realized.
In particular, the method comprises the following steps of,
in the valve closing state, the valve clack is respectively subjected to closing force F1 of a clamping spring, force F2 of differential pressure delta P2 of a high-pressure space c and an outlet space d to S1 (the upper part of the valve clack), and force F3 of differential pressure delta P3 of the high-pressure space c and an equilibrium space b to S2 (the lower part of the valve clack);
therefore, the situation that the valve clack is stressed when in sealing is as follows: f1+ F2-F3 ═ F1+ Δ P2 (S1-S2);
the balance space b and the outlet space d are communicated through the diversion holes, and the pressures are consistent (namely, delta P2 is delta P3), so that the S2 and the S1 are designed to be consistent or close to each other in design, namely, when the difference between the S1 and the S2 is 0 or close to 0, the influence of the pressure difference between the inlet channel and the outlet channel on the valve clack is reduced. Preferably, the difference between S1 and S2 is less than 10% of the average of S1 and S2. In some embodiments, the difference between S1 and S2 is controlled by the diameter tolerance at S1 and S2 during machining, for example, a tolerance level smaller than IT18, and the size relationship between S1 and S2 is controlled by positive and negative tolerances, but IT is obvious to those skilled in the art that the technical effects of the present invention can be achieved by designing S1 and S2 to have different areas directly, as long as the corresponding relationships are satisfied.
The working principle is as follows: the driving gas enters the upper air chamber f from the driving gas interface C to push the piston 10 to move downwards, the piston 10 is connected with the ejector rod 7, and the ejector rod 7 pushes the valve clack 4 away from the valve seat 6 to communicate the high-pressure space C with the outlet flow channel d, so that the opening action of the valve is realized. Otherwise, when the driving gas pressure disappears, the piston spring 9 moves upwards to the piston 10, and simultaneously the valve clack 4 also moves upwards under the thrust of the valve clack spring 5 until the valve clack 4 is attached to the valve seat 6, and the inlet flow channel a is disconnected from the outlet flow channel d, so that the closing action of the valve is realized.
The manual valve is operated in the same way as a pneumatic opening and closing process, and the valve is opened or closed by manually driving the piston to move up and down.
Referring to fig. 3, in embodiment 2, on the basis of embodiment 1, the valve flap is connected to the piston rod assembly to form a transmission rod, and the transmission rod is provided with a diversion hole for communicating the balance space with the outlet flow channel. The clamping spring is located at least one of between the valve flap and the valve body or within the cylinder.
The transmission rod comprises a conical structure and a cylindrical structure, wherein the cross section area of the conical structure and the cylindrical structure gradually increase from top to bottom. The top of the conical structure serves as a sealing surface for sealing against the valve seat. The outer diameter of the bottom of the conical structure is larger than that of the cylindrical structure. The cylindrical structure is sleeved with a clamping spring.
In specific embodiment 3, on the basis of specific embodiment 1 or 2, a contact surface abutting against the valve seat is provided on the valve flap, and a vertical tangent plane is provided in a region of the valve flap below the contact surface. The gas flow rate is increased.
The outer wall of the area in the valve body on the piston rod assembly is provided with a vertical tangent plane. The gas flow rate is increased.
The foregoing is only a preferred embodiment of the present invention, and it should be noted that it is obvious to those skilled in the art that various modifications and improvements can be made without departing from the principle of the present invention, and these modifications and improvements should also be considered as the protection scope of the present invention.

Claims (10)

1. The balanced stop valve is characterized in that the valve body is longitudinally connected with the valve clack in a sliding manner, a balanced sealing assembly is arranged between the valve body and the valve clack, one side of the valve body, far away from the valve seat, of the valve clack and the balanced sealing assembly jointly enclose a balanced space, and a flow guide hole for communicating the outlet flow passage with the balanced space is formed in the valve clack;
the balance space is communicated with the outlet flow channel all the time through a flow guide hole arranged on the valve clack.
2. The balanced shut-off valve of claim 1, wherein: the drive mechanism includes at least one of a cylinder and a manual valve.
3. The balanced shut-off valve of claim 2, wherein: the driving mechanism comprises an air cylinder, the air cylinder comprises a cylinder body, a piston and a piston rod assembly, the cylinder body is detachably connected with the valve body to form an air chamber, and the piston divides the air chamber into an upper air chamber and a lower air chamber which are arranged up and down;
the bottom of the piston rod assembly extends into the valve body, and the piston rod assembly pushes the valve clack to move downwards to be separated from the valve seat.
4. The balanced shut-off valve of claim 3, wherein: the top of the piston rod assembly penetrates through the piston;
the driving mechanism further comprises a manual valve rod, the manual valve rod is mounted at the top of the cylinder body, and the manual valve rod abuts against the top of the piston rod assembly.
5. The balanced shut-off valve of claim 3 or 4, wherein: the valve clack and the driving mechanism are independently arranged;
the piston rod assembly may be closer to or farther from the valve flap, and the piston rod assembly may pass through the valve seat and urge the valve flap away from the valve seat.
6. The balanced shut-off valve of claim 5, wherein: the center of the top of the valve clack is provided with an inwards concave groove, the valve clack is provided with the vertically arranged flow guide hole, and the flow guide hole is communicated with the groove;
the bottom of the piston rod assembly can be embedded into the groove, an auxiliary flow passage is formed in the piston rod assembly, and at least one end of the auxiliary flow passage is always communicated with the outlet flow passage;
when the piston rod assembly abuts against the valve clack, one end of the auxiliary flow passage is in butt joint with the flow guide hole, and the flow guide hole is communicated with the outlet flow passage through the auxiliary flow passage.
7. The balanced shut-off valve of claim 6 wherein: and a clamping spring is clamped between the valve clack and the valve body.
8. The balanced shut-off valve of claim 7, wherein: the valve seat is provided with a sealing ring which props against the valve clack;
the top of the valve clack is used for propping against the sealing ring to block the inlet flow passage and the outlet flow passage;
a spring mounting groove is formed in the valve body, the upper end of the clamping spring is abutted against the valve clack, the lower end of the clamping spring is abutted against the spring mounting groove, and the spring mounting groove is in butt joint conduction with the inlet runner;
the spring mounting groove is located above the balance space.
9. The balanced shut-off valve of claim 1, wherein: the upper part of the valve clack is matched with the valve seat to form a first sealing part, the lower part of the valve clack is matched with the balance sealing assembly to form a second sealing part, the sectional area of the valve clack at the plane where the first sealing part is located is S1, and the sectional area of the valve clack at the plane where the second sealing part is located is S2;
the difference between S1 and S2 was less than 10% of the average of S1 and S2.
10. The balanced shut-off valve of claim 1, wherein: the upper part of the valve clack is matched with the valve seat to form a first sealing part, the lower part of the valve clack is matched with the balance sealing assembly to form a second sealing part, the sectional area of the valve clack at the plane where the first sealing part is located is S1, and the sectional area of the valve clack at the plane where the second sealing part is located is S2;
s1 is greater than S2.
CN202210604387.6A 2022-05-19 2022-05-19 Balanced type stop valve Pending CN114992378A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202210604387.6A CN114992378A (en) 2022-05-19 2022-05-19 Balanced type stop valve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202210604387.6A CN114992378A (en) 2022-05-19 2022-05-19 Balanced type stop valve

Publications (1)

Publication Number Publication Date
CN114992378A true CN114992378A (en) 2022-09-02

Family

ID=83030921

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202210604387.6A Pending CN114992378A (en) 2022-05-19 2022-05-19 Balanced type stop valve

Country Status (1)

Country Link
CN (1) CN114992378A (en)

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