CN112113015A - Pressure stabilizing valve and gas water heater comprising same - Google Patents

Pressure stabilizing valve and gas water heater comprising same Download PDF

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Publication number
CN112113015A
CN112113015A CN202010986605.8A CN202010986605A CN112113015A CN 112113015 A CN112113015 A CN 112113015A CN 202010986605 A CN202010986605 A CN 202010986605A CN 112113015 A CN112113015 A CN 112113015A
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CN
China
Prior art keywords
valve
pressure
valve seat
pressure stabilizing
fluid inlet
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Granted
Application number
CN202010986605.8A
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Chinese (zh)
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CN112113015B (en
Inventor
王雲涛
朱海龙
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Ningbo Fotile Kitchen Ware Co Ltd
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Ningbo Fotile Kitchen Ware Co Ltd
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Priority to CN202010986605.8A priority Critical patent/CN112113015B/en
Publication of CN112113015A publication Critical patent/CN112113015A/en
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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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/20—Excess-flow valves
    • F16K17/22—Excess-flow valves actuated by the difference of pressure between two places in the flow line
    • F16K17/24—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member
    • F16K17/28—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only
    • F16K17/30—Excess-flow valves actuated by the difference of pressure between two places in the flow line acting directly on the cutting-off member operating in one direction only spring-loaded
    • 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
    • F16K17/20—Excess-flow valves
    • F16K17/34—Excess-flow valves in which the flow-energy of the flowing medium actuates the closing mechanism
    • 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/14—Arrangements for connecting different sections, e.g. in water heaters 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/20—Arrangement or mounting of control or safety devices
    • F24H9/2007—Arrangement or mounting of control or safety devices for water heaters
    • F24H9/2035—Arrangement or mounting of control or safety devices for water heaters using fluid fuel

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Magnetically Actuated Valves (AREA)
  • Control Of Fluid Pressure (AREA)

Abstract

The invention discloses a pressure stabilizing valve and a gas water heater comprising the same, wherein the pressure stabilizing valve comprises a shell, a valve core and a valve seat, and the valve seat is arranged to be capable of switching between a first position and a second position according to the hydraulic pressure of a fluid inlet side of the pressure stabilizing valve; when the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is smaller than or equal to the maximum pressure stabilizing value of the pressure stabilizing valve, the valve seat is in the first position, and the pressure stabilizing valve is opened; and when the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is greater than the maximum pressure stabilizing value of the pressure stabilizing valve, the valve seat is in the second position, and the pressure stabilizing valve is closed. The valve seat is designed to open or close the pressure stabilizing valve according to the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve, if the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is within the bearing capacity of the pressure stabilizing valve, the valve core can normally open and close the pressure stabilizing valve, and if the hydraulic pressure exceeds the bearing capacity of the pressure stabilizing valve, the valve seat is switched to the second position and combined with the valve core to close the pressure stabilizing valve, so that the fluid is limited to flow into the water pipe, the water pipe is prevented from being broken, and the safety is improved.

Description

Pressure stabilizing valve and gas water heater comprising same
Technical Field
The invention relates to the field of valve bodies, in particular to a pressure stabilizing valve and a gas water heater comprising the same.
Background
In general, a pressure stabilizing valve in the prior art controls the flow rate of fluid flowing through the pressure stabilizing valve in a unit time by controlling the pressure of the fluid, wherein the larger the flow rate of the fluid is, the larger the pressure formed by the fluid on the pressure stabilizing valve is. When the fluid pressure is greater than the maximum pressure stabilizing value of the pressure stabilizing valve, the fluid flow is increased, the pressure stabilizing effect of the pressure stabilizing valve is reduced, and therefore the fluid flowing into the water pipe in unit time is increased along with the continuous increase of the fluid pressure and exceeds the bearing range of the water pipe. Particularly, in cold weather, the fluid in the water pipe is frozen, so that the water pipe is easy to break, and property loss and potential safety hazard of users are caused.
Disclosure of Invention
The invention provides a pressure stabilizing valve and a gas water heater comprising the same, aiming at overcoming the defect that in the prior art, fluid in a water pipe is easy to damage due to the fact that the fluid in a unit time exceeds the bearing range of the water pipe under the condition that the fluid pressure is larger than the maximum pressure stabilizing value of the pressure stabilizing valve.
The invention solves the technical problems through the following technical scheme:
a pressure maintaining valve comprising a housing, a valve element, a valve seat and a resilient member for biasing the valve element such that the valve element engages the valve seat to close the pressure maintaining valve, the valve seat being arranged to be switchable between a first position and a second position in dependence on hydraulic pressure on a fluid inlet side of the pressure maintaining valve;
when the hydraulic pressure on the fluid inlet side of the pressure maintaining valve is smaller than or equal to the maximum pressure maintaining value of the pressure maintaining valve, the valve seat is in the first position, and the valve core is far away from the valve seat under the hydraulic action to open the pressure maintaining valve;
when the hydraulic pressure on the fluid inlet side of the pressure maintaining valve is larger than the maximum pressure maintaining value of the pressure maintaining valve, the valve seat is located at the second position, the valve core moves to the stroke end, and the valve seat is jointed with the valve core to close the pressure maintaining valve.
According to the scheme, the valve seat is designed to be capable of opening or closing the pressure stabilizing valve according to the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve, the valve core can normally open and close the pressure stabilizing valve under the condition that the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is within the bearing capacity of the pressure stabilizing valve, the flow of the fluid received by the water pipe is larger than the bearing range of the water pipe under the condition that the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve exceeds the bearing capacity of the pressure stabilizing valve, the pressure stabilizing valve cannot be closed when the valve core moves to the stroke tail end, the valve seat is switched to the second position and combined with the valve core to close the pressure stabilizing valve, the fluid is limited to flow into the.
Preferably, the valve seat is slidable relative to the housing, the fluid biasing the valve seat to slide the valve seat from the first position to the second position.
In this scheme, the disk seat can change automatic movement according to hydraulic pressure, does not need the manual work to carry out the removal of hydraulic pressure monitoring and regulation disk seat, improves and closes the feasibility of surge damping valve through the disk seat removes.
Preferably, a sliding groove is formed in an inner wall surface of the housing, the valve seat slides in the sliding groove, and two ends of the sliding groove in the fluid flowing direction are the first position and the second position respectively.
In this scheme, the spout makes the slip of disk seat on the casing more convenient, and on the other hand can also restrict the displacement range of disk seat, prevents that the disk seat from removing excessively and producing excessive extrusion between the case, causes wearing and tearing between them.
Preferably, the length of the slide groove in the fluid flow direction is equal to the maximum movement stroke of the spool.
In this scheme, the case is in order to close the surge damping valve with the disk seat laminating under the hydraulic pressure's the condition not receiving, and the displacement distance that above-mentioned setting can guarantee case and disk seat is the same, and the interact power between the two is equal to the effort size under the hydraulic pressure's the condition not received of case basically, can enough guarantee the sealed effect between the two, also can prevent because the too big wearing and tearing that produce of interact power between the two.
Preferably, the end of the valve seat that engages with the housing is provided with a roller by which the valve seat slides within the housing.
In this scheme, the frictional force that the gyro wheel received in can reducing the disk seat slip process, the removal of the disk seat of being convenient for.
Preferably, the pressure maintaining valve further comprises a magnet engaged with the valve seat such that the valve seat is held at the first position, the magnet applying an attractive force to the valve seat toward the fluid inlet of the pressure maintaining valve, the attractive force being greater than or equal to a maximum pressure stabilizing value of the pressure maintaining valve.
In the scheme, when the hydraulic pressure at the fluid inlet side of the pressure stabilizing valve is less than or equal to the maximum pressure stabilizing value of the pressure stabilizing valve, the hydraulic pressure at the fluid inlet side of the pressure stabilizing valve is also less than or equal to the adsorption force of the magnet on the valve seat, and the valve seat is always adsorbed on the magnet and cannot move; when the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is greater than the maximum pressure stabilizing value of the pressure stabilizing valve, if the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is further greater than the adsorption force of the magnet on the valve seat, the valve seat can move towards the second position under the action of the hydraulic pressure until the valve seat moves to the second position to close the pressure stabilizing valve; when the hydraulic pressure on the fluid inlet side of the pressure maintaining valve is reduced and smaller than the adsorption force of the magnet on the valve seat, the valve seat moves from the second position to the first position under the action of the adsorption force, the pressure maintaining valve is opened, and the pressure maintaining valve can continue to work.
Preferably, the magnet is disposed within the housing and adjacent the fluid inlet of the pressure maintaining valve relative to the valve seat.
In this scheme, above-mentioned setting can reduce the whole size of surge damping valve to increase the adsorption affinity to the disk seat under the same condition of magnet magnetism, thereby can reduce the cost of magnet.
Preferably, the magnet is an electromagnet, the pressure stabilizing valve further comprises a control mechanism, and the control mechanism is used for controlling the electrification of the electromagnet;
when the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is less than or equal to the maximum pressure stabilizing value of the pressure stabilizing valve, the electromagnet is electrified;
and when the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is greater than the maximum pressure stabilizing value of the pressure stabilizing valve, the electromagnet is powered off.
In the scheme, when the hydraulic pressure at the fluid inlet side of the pressure stabilizing valve is less than or equal to the maximum pressure stabilizing value of the pressure stabilizing valve and is also less than or equal to the adsorption force of the electromagnet on the valve seat, the electromagnet needs to be always kept in a power-on state to always generate the adsorption force on the valve seat, and the valve seat is ensured to be at the first position; when the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is greater than the maximum pressure stabilizing value of the pressure stabilizing valve and is further greater than the adsorption force of the electromagnet on the valve seat, the valve seat can move to the second position due to the hydraulic pressure even if the electromagnet is in a power-on state, the electromagnet does not act on the adsorption force of the valve seat, and the electromagnet is powered off, so that the energy consumption can be reduced.
Preferably, the pressure stabilizing valve further comprises a monitoring mechanism, the monitoring mechanism acts on the control mechanism, the monitoring mechanism is used for monitoring the hydraulic pressure of the fluid inlet side of the pressure stabilizing valve, and the control mechanism controls the energization of the electromagnetic valve according to the hydraulic pressure value monitored by the monitoring mechanism.
In the scheme, the monitoring mechanism is used for monitoring the hydraulic pressure of the fluid inlet side of the pressure stabilizing valve in real time and providing the monitored data to the control mechanism in time so that the control mechanism can control the power-on condition of the electromagnetic valve in time.
Preferably, the pressure maintaining valve further comprises a limiting part, the limiting part is arranged in the shell and is located at the downstream of the fluid relative to the valve core, and the limiting part is used for controlling the movement stroke of the valve core.
In this scheme, spacing portion is used for further limiting the case towards the removal of keeping away from the valve port one end of surge damping valve, prevents that the case from still producing further removal when moving to the stroke end, improves the reliability of surge damping valve.
Preferably, the limiting part is a baffle fixed on the inner wall surface of the shell; in the fluid flow direction, one end of the baffle plate facing the fluid inlet of the pressure maintaining valve is jointed with one end of the valve core far away from the fluid inlet of the pressure maintaining valve to limit the valve core to move.
In this scheme, provide a concrete structure of spacing portion, baffle simple structure, it is convenient to make, assemble, and great with the contact surface of case, can restrict the case better and further move towards the valve port one end of keeping away from the surge damping valve.
A gas water heater comprising a pressure maintaining valve as described above.
In the scheme, an application mode of the pressure stabilizing valve is provided.
The positive progress effects of the invention are as follows: the valve seat is designed to open or close the pressure stabilizing valve according to the hydraulic pressure at the fluid inlet side of the pressure stabilizing valve, the valve core can normally open or close the pressure stabilizing valve under the condition that the hydraulic pressure at the fluid inlet side of the pressure stabilizing valve is within the bearing capacity of the pressure stabilizing valve, the flow of the fluid received by the water pipe is larger than the bearing range of the water pipe under the condition that the hydraulic pressure at the fluid inlet side of the pressure stabilizing valve exceeds the bearing capacity of the pressure stabilizing valve, the pressure stabilizing valve cannot be closed when the valve core moves to the stroke tail end, and the valve seat is switched to the second position and combined with the valve core to close the pressure stabilizing valve, so that the fluid is limited to flow into the water pipe.
Drawings
Fig. 1 is a schematic cross-sectional view of a pressure maintaining valve with a valve seat in a first position and the pressure maintaining valve in a closed state, according to an embodiment of the present invention.
Fig. 2 is a schematic sectional view along a-a in fig. 1.
Fig. 3 is a schematic cross-sectional view of a valve element according to an embodiment of the present invention.
Fig. 4 is a left side view schematically illustrating a guide bar according to an embodiment of the invention.
Fig. 5 is a schematic cross-sectional view of a regulator valve with a valve seat in a first position and the regulator valve in an open state in accordance with an embodiment of the present invention.
Fig. 6 is a schematic cross-sectional view of a pressure maintaining valve with its valve seat in a second position and its closed state in accordance with an embodiment of the present invention.
Fig. 7 is a schematic perspective view of a pressure maintaining valve with a valve seat in a second position and the pressure maintaining valve in a closed state according to an embodiment of the present invention.
Description of reference numerals:
housing 1
Water inlet port 11
Water outlet port 12
Chute 13
Valve core 2
Valve core body 21
Valve core base 22
Valve seat 3
Elastic element 4
Guide rod 5
Guide rod body 51
Guide rod base 52
Stopper 6
Magnet 7
First position 81
Second position 82
Detailed Description
The invention is further illustrated by the following examples, which are not intended to limit the scope of the invention.
The embodiment provides a gas water heater, and gas water heater includes surge damping valve and water pipe, and surge damping valve's water inlet and delivery port all are connected with a water pipe, and surge damping valve is used for adjusting the fluid pressure of delivery port. Because the fluid pressure and the fluid flow are generally in direct proportion, the pressure stabilizing valve enables the fluid flow flowing into the water pipe connected with the water outlet of the pressure stabilizing valve to meet the requirements of users by adjusting the fluid pressure, prevents the water pipe on one side of the water outlet from being broken due to overlarge fluid flow, and improves the safety.
As shown in fig. 1 to 4, the surge damping valve includes a housing 1, a valve element 2, a valve seat 3, an elastic element 4, and a guide rod 5, and the valve element 2, the valve seat 3, the elastic element 4, and the guide rod 5 are all disposed inside the housing 1.
As shown in fig. 1, the left and right ends of the casing 1 are respectively provided with a port, the left end of the casing 1 is provided with a water inlet port 11, the right end of the casing 1 is provided with a water outlet port 12, fluid flows into the pressure stabilizing valve from the water inlet port 11 and then flows out of the pressure stabilizing valve from the water outlet port 12, and the specific flow direction of the fluid is shown by an arrow in fig. 1.
As shown in fig. 1 and 3, the spool 2 includes a conical spool body 21 and a cylindrical spool base 22, and the spool body 21 is connected to the spool base 22. The valve core body 21 is close to the water inlet port 11, the valve core base 22 is close to the water outlet port 12, the side surface of the valve core body 21 is jointed with the valve seat 3 to open or close the pressure stabilizing valve, and the valve core base 22 is sleeved on the guide rod 5 to guide the movement of the valve core 2 in the fluid flow direction.
As shown in fig. 4, the guide bar 5 includes a cylindrical guide bar body 51 and a guide bar base 52, and the guide bar base 52 is four elongated columnar structures for fixing the guide bar 5 to the housing 1 and keeping the guide bar 5 stationary with respect to the housing 1. In other alternative embodiments, the guide rod base 52 may adopt other structures or different numbers of elongated columnar structures, and in this embodiment, four elongated columnar structures are used, so that the guide rod 5 can be firmly connected to the housing 1, but because the shielding surface of the guide rod base 52 on the pressure maintaining valve water outlet port 12 is smaller, the influence of the guide rod base 52 on the fluid flow on the side of the water outlet port 12 is also smaller, so that the fluid pressure on the guide rod base 52 is smaller, and the firmness of connection between the guide rod base 52 and the housing 1 can be further improved.
The guide rod body 51 extends along the fluid flowing direction and is used for guiding the movement of the valve core 2, the valve core 2 moves left and right along the extending direction of the guide rod body, and the valve core 2 is prevented from shifting to other positions in the shell 1 in the moving process, so that the valve core 2 cannot completely close the pressure stabilizing valve.
As shown in fig. 1, the valve core base 22 is sleeved on the guide rod body 51, an elastic element 4 is further disposed between the valve core base 22 and the guide rod body 51, the elastic element 4 in this embodiment is a coil spring, the coil spring is disposed in an accommodating space formed by the valve core base 22 and the guide rod body 51, a length direction of the coil spring is parallel to a flow direction of the fluid, and the coil spring applies pressure to the valve core 2 toward one side of the water inlet port 11, so that the valve core 2 can be engaged with the valve seat 3 located on the left side thereof to close the pressure stabilizing valve.
As shown in fig. 2, the pressure stabilizing valve further includes a limiting portion 6, the limiting portion 6 is disposed inside the housing 1 and located downstream of the fluid with respect to the valve core body 21, that is, the limiting portion 6 is closer to the water outlet port 12 of the housing 1 with respect to the valve core body 21, the limiting portion 6 is used for controlling the movement stroke of the valve core 2, further limiting the movement of the valve core 2 toward one side of the water outlet port 12, preventing the valve core 2 from further moving when moving to the stroke end, and improving the reliability of the pressure stabilizing valve. The stroke end of the valve element 2 in the present embodiment refers to the maximum distance that the valve element 2 can move toward the water outlet port 12.
Without the limiting portion 6, the elastic element 4 is compressed to the maximum deformation state, which means that the valve element 2 moves to the stroke end, but if the fluid pressure is further increased, the valve element 2 may further move towards the water outlet port 12, so that the deformation of the elastic element 4 exceeds the deformation range, which may damage the elastic element 4, and may cause the guide rod 5 to bear the pressure from the valve element 2, which may reduce the firmness of the connection between the guide rod 5 and the housing 1.
The limiting part 6 in this embodiment is a baffle fixed on the inner wall surface of the housing 1, and in the fluid flow direction, one end of the baffle facing the fluid inlet of the pressure stabilizing valve is jointed with one end of the valve core 2 away from the fluid inlet of the pressure stabilizing valve to limit the movement of the valve core 2. The baffle plate has the advantages of simple structure, convenience in manufacturing and assembling, larger contact surface with the valve core 2 and capability of better limiting the valve core 2 to further move towards one end of the valve port far away from the pressure stabilizing valve.
As shown in fig. 1, 5 to 6, the valve seat 3 is provided so as to be switchable between a first position 81 and a second position 82 in accordance with the hydraulic pressure on the fluid inlet side of the regulator valve. When the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is smaller than or equal to the maximum pressure stabilizing value of the pressure stabilizing valve, the valve seat 3 is always in the first position 81, and the valve core 2 is far away from the valve seat 3 under the hydraulic action on the water inlet port 11 side so as to open the pressure stabilizing valve. When the hydraulic pressure on the fluid inlet side of the surge damping valve is greater than the maximum surge damping value of the surge damping valve, the valve element 2 is located at the end of its stroke, and the valve seat 3 is switched to the second position 82 to engage with the valve element 2 to close the surge damping valve.
In the embodiment, the valve seat 3 is designed to open or close the pressure stabilizing valve according to the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve, the valve core 2 can normally open and close the pressure stabilizing valve under the condition that the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is within the bearing capacity of the pressure stabilizing valve, the flow of the fluid received by the water pipe on one side of the water outlet port 12 is larger than the bearing range of the water pipe under the condition that the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve exceeds the bearing capacity of the pressure stabilizing valve, the pressure stabilizing valve cannot be closed when the valve core 2 moves to the stroke tail end, the valve seat 3 is switched to the second position 82 and combined with the valve core 2 to close the pressure stabilizing valve, the fluid is limited to flow.
Specifically, the inner wall surface of the casing 1 is provided with a sliding groove 13, and the sliding groove 13 extends outward from the inner wall surface of the casing 1 but does not penetrate through the outer wall surface of the casing 1. The valve seat 3 is accommodated in the slide groove 13 and is combined with the groove bottom of the slide groove 13, and the valve seat 3 is slidable in the slide groove 13. The sliding groove 13 facilitates the sliding of the valve seat 3 on the housing 1, and limits the moving range of the valve seat 3 to prevent the valve seat 3 from moving excessively to generate excessive extrusion with the valve core 2, thereby preventing the valve seat 3 from being worn.
The slide groove 13 has a first position 81 and a second position 82 at both ends in the fluid flow direction, the first position 81 is near the water inlet port 11, and the second position 82 is near the water outlet port 12, and the fluid on the water inlet port 11 side applies a pressure toward the water outlet port 12 side to the valve seat 3 so that the valve seat 3 can slide from the first position 81 to the second position 82. The valve seat 3 can automatically slide according to the hydraulic change of the water inlet end, the movement of the valve seat 3 is not required to be manually monitored and regulated, and the feasibility of closing the pressure stabilizing valve through the movement of the valve seat 3 is improved.
The valve core 2 is attached to the valve seat 3 under the condition of not receiving hydraulic pressure to close the pressure stabilizing valve, and the interaction force between the valve core 2 and the valve seat 3 is in a proper range, so that the sealing of the joint of the valve core 2 and the valve seat 3 can be ensured, and the abrasion caused by the mutual extrusion and the excessive formation of the valve core 2 and the valve seat 3 can be avoided. Preferably, the length of the sliding groove 13 in the fluid flowing direction is equal to the maximum moving stroke of the valve core 2, so that the moving distance of the valve core 2 and the valve seat 3 is the same, the interaction force between the two is basically equal to the interaction force between the two in the state that the valve core 2 is not moved, the joint between the valve core 2 and the valve seat 3 is well sealed, and the excessive compression between the valve core 2 and the valve seat 3 can be prevented.
Further, the end of the valve seat 3, which is received in the slide groove 13 and engages with the housing 1, is provided with a roller (not shown in the drawings), by which the valve seat 3 slides within the housing 1. The roller can reduce the friction that receives in the sliding process of valve seat 3, the removal of the valve seat 3 of being convenient for.
In other alternative embodiments, the valve seat 3 may also slide directly on the inner wall surface of the housing 1 without providing the sliding groove 13, the roller, or other structures, or the valve seat 3 may also be switched from the first position 81 to the second position 82 in other manners, and the specific embodiment may be adjusted by a technician according to actual situations.
The pressure stabilizing valve further comprises a magnet 7, the magnet 7 is arranged inside the shell 1 to reduce the overall size of the pressure stabilizing valve, and the magnet 7 is located on the left side of the valve seat 3, namely, is closer to the water inlet port 11 relative to the valve seat 3. The magnet 7 engages with the valve seat 3 so that the valve seat 3 is held at the first position 81, the magnet 7 applying an attractive force to the valve seat 3 towards the fluid inlet of the pressure maintaining valve, the attractive force being slightly greater than or equal to the maximum pressure stabilizing value of the pressure maintaining valve. The magnet 7 is provided inside the housing 1, and when the magnet 7 is of the same magnetic polarity, the attraction force to the valve seat 3 can be increased, and the cost of the magnet 7 can be reduced.
When the valve seat 3 is at the first position 81, when the hydraulic pressure at the fluid inlet side of the pressure stabilizing valve is less than or equal to the maximum pressure stabilizing value of the pressure stabilizing valve and less than or equal to the adsorption force of the magnet 7 on the valve seat 3, the valve seat 3 is always adsorbed on the magnet 7 and cannot move; when the hydraulic pressure on the fluid inlet side of the pressure maintaining valve is larger than the maximum pressure maintaining value of the pressure maintaining valve and larger than the adsorption force of the magnet 7 to the valve seat 3, the valve seat 3 moves towards the second position 82 under the action of the hydraulic pressure until the valve seat moves to the second position 82 to close the pressure maintaining valve.
When the hydraulic pressure on the fluid inlet side of the surge damping valve is reduced and is smaller than the attraction force of the magnet 7 to the valve seat 3, the valve seat 3 moves from the second position 82 to the first position 81 under the action of the attraction force, and the surge damping valve is opened and can continue to work.
Preferably, the adsorption force is equal to the maximum pressure stabilizing value of the pressure stabilizing valve, so that when the hydraulic pressure on the water inlet port 11 side is greater than the maximum pressure stabilizing value of the flow stabilizing valve, the valve seat 3 can slide to close the pressure stabilizing valve, and the safety of the pressure stabilizing valve is further improved.
Preferably, the magnet 7 in this embodiment is an electromagnet, and the pressure stabilizing valve further includes a control mechanism (not shown in the drawings) for controlling the energization of the electromagnet, and the specific structure of the control mechanism is not specifically described in this embodiment, and a person skilled in the art can use the control mechanism commonly used in the prior art to control the energization of the electromagnet.
When the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is smaller than or equal to the maximum pressure stabilizing value of the pressure stabilizing valve and is also smaller than or equal to the adsorption force of the electromagnet on the valve seat 3, the electromagnet is electrified, the electromagnet needs to be always kept in an electrified state to generate the adsorption force on the valve seat 3 all the time, and the valve seat 3 is ensured to be located at the first position 81.
When the hydraulic pressure on the fluid inlet side of the surge damping valve is larger than the maximum surge damping value of the surge damping valve and further larger than the adsorption force of the electromagnet on the valve seat 3, the electromagnet is powered off, because the valve seat 3 can also move to the second position 82 due to the hydraulic pressure even in the powered-on state of the electromagnet, the electromagnet does not act on the adsorption force of the valve seat 3, and the electromagnet is powered off at the moment, so that the energy consumption can be reduced.
Furthermore, the pressure stabilizing valve also comprises a monitoring mechanism, the monitoring mechanism acts on the control mechanism, and the monitoring mechanism is used for monitoring the hydraulic pressure of the fluid inlet side of the pressure stabilizing valve in real time and providing the monitored data for the control mechanism in time, so that the control mechanism controls the power-on condition of the electromagnetic valve in time according to the hydraulic value monitored by the monitoring mechanism.
The working principle of the pressure maintaining valve of the embodiment is briefly described as follows:
fig. 1 shows fluid not flowing into the interior of the surge valve, which is in a closed state. Fluid flows into the pressure stabilizing valve from the water inlet port 11 of the housing 1, and the fluid applies pressure to both the valve element 2 and the valve seat 3 toward the water outlet port 12 side of the housing 1. When the hydraulic pressure is greater than the pressure applied to the valve core 2 by the elastic element 4 and less than or equal to the adsorption force of the magnet 7 to the valve seat 3, the valve seat 3 does not move and is always kept at the first position 81, the valve core 2 moves towards one side of the water outlet port 12, the pressure stabilizing valve is opened, and the valve core 2 stops moving until the hydraulic pressure is equal to the pressure applied to the valve core 2 by the elastic element 4.
When the right end surface of the spool body 21 is engaged with the left end surface of the stopper portion 6, the spool 2 moves to the stroke end, as shown in fig. 5, for example. At this time, the pressure stabilizing value of the pressure stabilizing valve is the rated maximum pressure stabilizing value of the pressure stabilizing valve, the opening degree of the valve port of the pressure stabilizing valve is maximum, and the fluid flow on the side of the water outlet port 12 is maximum.
When the hydraulic pressure is greater than the attraction force of the magnet 7 to the valve seat 3, the valve element 2 moves to the end of the stroke, the valve seat 3 moves toward the side of the water outlet port 12 under the action of the hydraulic pressure, and since the attraction force of the magnet 7 to the valve seat 3 is inversely proportional to the distance between the magnet 7 and the valve seat 3, the farther the distance between the magnet 7 and the valve seat 3 is, the smaller the attraction force of the magnet 7 to the valve seat 3 is, and the valve seat 3 moves until it stops at the second position 82, as shown in fig. 6-7, for example. At this time, the valve element 2 is held stationary with respect to the housing 1, and the engagement of the valve element 2 with the valve seat 3 is achieved by the movement of the valve seat 3 to close the surge tank valve.
When the hydraulic pressure becomes smaller and smaller than the attraction force of the magnet 7 to the valve seat 3, the valve seat 3 moves to the first position 81 again under the action of the attraction force of the magnet 7, and the pressure maintaining valve is opened and works again.
In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on those shown in the drawings, are merely for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed in a particular orientation, and be operated, and therefore, should not be construed as limiting the present invention unless otherwise specified herein.
While specific embodiments of the invention have been described above, it will be appreciated by those skilled in the art that this is by way of example only, and that the scope of the invention is defined by the appended claims. Various changes and modifications to these embodiments may be made by those skilled in the art without departing from the spirit and scope of the invention, and these changes and modifications are within the scope of the invention.

Claims (12)

1. A pressure maintaining valve comprising a housing, a valve element, a valve seat and a resilient member for biasing the valve element such that the valve element engages the valve seat to close the pressure maintaining valve, characterised in that the valve seat is arranged to be switchable between a first position and a second position in dependence on hydraulic pressure on a fluid inlet side of the pressure maintaining valve;
when the hydraulic pressure on the fluid inlet side of the pressure maintaining valve is smaller than or equal to the maximum pressure maintaining value of the pressure maintaining valve, the valve seat is in the first position, and the valve core is far away from the valve seat under the hydraulic action to open the pressure maintaining valve;
when the hydraulic pressure on the fluid inlet side of the pressure maintaining valve is larger than the maximum pressure maintaining value of the pressure maintaining valve, the valve seat is located at the second position, the valve core moves to the stroke end, and the valve seat is jointed with the valve core to close the pressure maintaining valve.
2. The surge valve according to claim 1, wherein said valve seat is slidable relative to said housing, said fluid biasing said valve seat to slide said valve seat from said first position to said second position.
3. The surge damping valve according to claim 2, wherein an inner wall surface of the housing is provided with a slide groove, the valve seat slides in the slide groove, and both ends of the slide groove in the fluid flow direction are the first position and the second position, respectively.
4. The surge valve according to claim 3, wherein a length of the slide groove in the direction of fluid flow is equal to a maximum travel stroke of the spool.
5. The surge-stabilizing valve according to claim 2, wherein the end of said valve seat engaging said housing is provided with a roller by which said valve seat slides within said housing.
6. The pressure maintenance valve of claim 1, further comprising a magnet engaged with the valve seat to retain the valve seat in the first position, the magnet applying an attractive force to the valve seat toward the fluid inlet port of the pressure maintenance valve, the attractive force being greater than or equal to a maximum pressure maintenance value of the pressure maintenance valve.
7. The regulator valve according to claim 6, wherein said magnet is disposed within said housing adjacent a fluid inlet of said regulator valve relative to said valve seat.
8. The surge damping valve according to claim 6, wherein said magnet is an electromagnet, said surge damping valve further comprising a control mechanism for controlling the energization of said electromagnet;
when the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is less than or equal to the maximum pressure stabilizing value of the pressure stabilizing valve, the electromagnet is electrified;
and when the hydraulic pressure on the fluid inlet side of the pressure stabilizing valve is greater than the maximum pressure stabilizing value of the pressure stabilizing valve, the electromagnet is powered off.
9. The surge valve according to claim 8, further comprising monitoring means acting on said control means for monitoring hydraulic pressure on the fluid inlet side of said surge valve, said control means controlling energization of said solenoid valve in accordance with the value of hydraulic pressure monitored by said monitoring means.
10. The pressure maintenance valve according to claim 1, further comprising a limiting portion disposed within the housing and located downstream of the fluid relative to the valve spool, the limiting portion configured to control a travel of the valve spool.
11. The surge damping valve according to claim 10, wherein the limiting portion is a baffle plate fixed to an inner wall surface of the housing; in the fluid flow direction, one end of the baffle plate facing the fluid inlet of the pressure maintaining valve is jointed with one end of the valve core far away from the fluid inlet of the pressure maintaining valve to limit the valve core to move.
12. A gas water heater including a pressure maintaining valve as claimed in any one of claims 1 to 10.
CN202010986605.8A 2020-09-18 2020-09-18 Pressure stabilizing valve and gas water heater comprising same Active CN112113015B (en)

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WO2023007400A1 (en) * 2021-07-27 2023-02-02 Flsmidth A/S Drain valve assembly for filter plates

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CN1048746A (en) * 1990-04-27 1991-01-23 梁济权 The bidirectional stable pressure valve device
JPH0566378U (en) * 1992-02-18 1993-09-03 株式会社イナックス Check valve with constant flow valve
JPH10176762A (en) * 1996-10-17 1998-06-30 Akume:Kk Flow regulating valve
WO2000043700A1 (en) * 1999-01-20 2000-07-27 Methven Limited Pressure limiting valve
CN102367881A (en) * 2011-09-26 2012-03-07 吴江伊兰吉纺织品有限公司 Adjustable one-way valve used for spray water loom
CN204692841U (en) * 2015-05-18 2015-10-07 中山市雅西环保科技有限公司 A kind of flow regulator
CN106321916A (en) * 2016-11-08 2017-01-11 玉环江林水暖管业有限公司 Flow safety valve

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Publication number Priority date Publication date Assignee Title
US3918481A (en) * 1974-07-16 1975-11-11 Bryan Donkin Co Ltd Gas supply apparatus
FR2353780A1 (en) * 1976-06-02 1977-12-30 Renault Pressure retaining valve for hydraulic equipment - has spring biassed floating seat which may be pushed against shoulder on conical head to close valve on supply line failure
CN1048746A (en) * 1990-04-27 1991-01-23 梁济权 The bidirectional stable pressure valve device
JPH0566378U (en) * 1992-02-18 1993-09-03 株式会社イナックス Check valve with constant flow valve
JPH10176762A (en) * 1996-10-17 1998-06-30 Akume:Kk Flow regulating valve
WO2000043700A1 (en) * 1999-01-20 2000-07-27 Methven Limited Pressure limiting valve
CN102367881A (en) * 2011-09-26 2012-03-07 吴江伊兰吉纺织品有限公司 Adjustable one-way valve used for spray water loom
CN204692841U (en) * 2015-05-18 2015-10-07 中山市雅西环保科技有限公司 A kind of flow regulator
CN106321916A (en) * 2016-11-08 2017-01-11 玉环江林水暖管业有限公司 Flow safety valve

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023007400A1 (en) * 2021-07-27 2023-02-02 Flsmidth A/S Drain valve assembly for filter plates

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