CN211449776U - High-pressure-difference water-control piston type pressure reducing valve - Google Patents
High-pressure-difference water-control piston type pressure reducing valve Download PDFInfo
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- CN211449776U CN211449776U CN201922002363.XU CN201922002363U CN211449776U CN 211449776 U CN211449776 U CN 211449776U CN 201922002363 U CN201922002363 U CN 201922002363U CN 211449776 U CN211449776 U CN 211449776U
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Abstract
The utility model relates to a valve structure technical field specifically indicates a high pressure difference water accuse piston relief pressure valve. Comprises a main valve; the main valve body is a hollow cavity with an inlet flow passage and an outlet flow passage, and a main valve clack is arranged in the main valve body; the main valve clack is fixedly connected with the piston through a valve rod; the lower chamber of the piston is communicated with the outlet flow passage and also comprises a pilot valve; the pilot valve comprises a pilot valve body; an inlet channel of the pilot valve body is communicated with an upper cavity of the piston; the outlet channel of the pilot valve body is communicated with the outlet flow passage; the upper cavity of the piston is communicated with the inlet flow passage; and a control structure which closes the pilot valve when the pressure of the outlet flow passage is less than the set pressure so as to increase the valve clack opening of the main valve and opens the pilot valve when the pressure of the outlet flow passage is greater than the set pressure so as to reduce the valve clack opening of the main valve is arranged in the valve body of the pilot valve. The utility model discloses a relief pressure valve simple structure, control mode is convenient, and need not to arrange fragile structure in the flow, has improved the life of relief pressure valve.
Description
Technical Field
The utility model relates to a valve structure technical field specifically indicates a high pressure difference water accuse piston relief pressure valve.
Background
According to GB/T12244-. The piston type pressure reducing valve is a pressure reducing valve which adopts a piston as a sensitive element to drive a valve clack to move. Like the chinese utility model patent of "high temperature high pressure guide piston relief pressure valve" of "CN 206617631U", this patent has protected a piston relief pressure valve, and this relief pressure valve includes main valve and pilot valve, and the main valve includes the piston of valve clack and control valve clack, is provided with a spring on the valve gap of valve clack below, and the position of piston control valve clack realizes the aperture control to the outlet flow way. The outlet of the pilot valve is communicated with the upper cavity of the piston, the lower cavity of the piston is communicated with the outlet flow passage of the main valve, and the inlet of the pilot valve is communicated with the inlet flow passage of the valve body. When the pressure of the medium in the main valve outlet channel is reduced to be lower than the setting pressure of the pilot valve, the opening degree of the pilot valve is increased, flowing medium enters the upper piston chamber through the pilot valve, the pressure of the upper chamber is increased, the piston is pushed to move downwards, the opening degree of the valve clack is increased, and the pressure of the medium in the main valve outlet channel is increased. On the contrary, when the medium pressure of the outlet channel of the main valve rises to be higher than the setting pressure of the pilot valve, the opening degree of the pilot valve is reduced, the pressure entering the upper chamber of the piston is reduced, the valve clack rises under the action of the thrust of the spring, the opening degree of the main valve is reduced, and the outlet of the main valve falls back through the pressure. The method controls the medium pressure of the main valve outlet channel to be stabilized at the setting pressure value of the pressure setting device. The pressure reducing valve has the advantages of simple structure, convenient control mode and high control precision, and can stably maintain the medium pressure of the main valve outlet flow passage. However, in the pressure reducing valve structure, a pressure spring needs to be arranged in an inlet flow passage of the main valve as a driving part, the spring is soaked in a flowing medium for a long time and is easy to rust and damage, and the elastic damage of the spring is gradually reduced along with the service time of the main valve, so that the control precision is gradually reduced.
SUMMERY OF THE UTILITY MODEL
The utility model aims at solving the defects of the prior art and providing a high pressure difference water control piston type pressure reducing valve.
The technical scheme of the utility model is that: a high pressure difference water control piston type pressure reducing valve comprises a main valve; the main valve comprises a main valve body; the main valve body is a hollow cavity with an inlet flow passage and an outlet flow passage, and a main valve clack for controlling the opening degree of the flow passage is arranged in the main valve body; the main valve clack is fixedly connected with a piston in a piston cylinder on the main valve body through a valve rod; the lower chamber of the piston is in communication with the outlet flow passage,
the method is characterized in that: the device also comprises a pilot valve; the pilot valve comprises a pilot valve body; the pilot valve body is a hollow cavity with an inlet channel and an outlet channel; the inlet channel is communicated with the upper cavity of the piston; the outlet channel is communicated with the outlet flow passage; the upper chamber of the piston is communicated with the inlet flow channel; and a control structure which closes the pilot valve when the pressure of the outlet flow passage is less than the set pressure so as to increase the valve clack opening of the main valve and opens the pilot valve when the pressure of the outlet flow passage is greater than the set pressure so as to reduce the valve clack opening of the main valve is arranged in the valve body of the pilot valve.
Further the control structure comprises an upper flap; a hollow flow passage for communicating the inlet passage and the outlet passage is arranged in the valve body of the pilot valve; the upper valve clack is a block structure which can move in the hollow flow passage to control opening and closing, and a pressure adjusting structure used for adjusting water pressure in the hollow flow passage is arranged in the hollow flow passage below the upper valve clack.
The pressure adjusting structure further comprises a lower valve clack; the lower valve clack is a blocky structure which can move in the hollow flow passage and is arranged at intervals with the upper valve clack, and the lower valve clack, the bottom cover at the lower end of the hollow flow passage and the pilot valve body form a control chamber with variable volume; the control chamber is in communication with the outlet flow passage.
And a pressure setting structure for adjusting the set pressure is further arranged on the pilot valve body above the upper valve clack.
The pressure setting structure further comprises an adjusting screw, a spring seat and a spring; one end of the adjusting screw penetrates through a valve cover at the upper end of the pilot valve body and is fixedly connected with a spring seat in the pilot valve body; one end of the spring is fixed on the spring seat, and the other end of the spring is connected with the upper valve clack.
Furthermore, the main valve clack is of a hollow squirrel-cage structure fixed at the end part of the valve rod, and a plurality of overflowing slotted holes are formed in the circumferential side wall of the main valve clack.
Furthermore, a plurality of strip-shaped through holes which are uniformly arranged at intervals along the circumferential direction are formed in the circumferential side wall of the main valve clack.
The cross-sectional area of the end of the main valve clack far away from the valve rod is smaller than that of the axial end of the piston.
And a throttle valve is arranged on a communication pipeline between the inlet flow channel and the upper cavity of the piston.
And further, a sealing ring is arranged between the circumferential side walls of the upper valve clack and the lower valve clack and the hollow flow channel.
The utility model has the advantages that: 1. the pressure reducing valve of the utility model has simple structure and extremely simple and convenient control mode, the pilot valve is closed when the pressure of the outlet flow passage is less than the set pressure, and the pilot valve is opened when the pressure of the outlet flow passage is more than the set pressure, the control mode is completely different from the prior structure, the control precision is higher, and the main valve of the utility model does not need to be provided with a spring structure as an auxiliary force application structure, so that the problems that the parts are easy to damage and the service life is influenced during flowing are avoided, and the service life of the pressure reducing valve of the utility model is;
2. the hollow runner of the utility model controls the flow to open or close through the movement of the upper valve clack, so as to realize the opening or closing of the pilot valve, the upper valve clack is matched with the pressure regulation structure, the pressure in the hollow runner can be changed to regulate the position of the upper valve clack, the real-time regulation of the opening degree of the hollow runner is realized in turn, and the regulation mode is more accurate and timely;
3. the utility model discloses form inclosed control cavity by lower valve clack, bottom and pilot valve body, control cavity and export runner intercommunication, the pressure source of control cavity and the water pressure change of export runner promptly, control cavity directly acts on the cavity runner again, can be fast accurate with the water pressure reflection of export runner to the cavity runner, the last valve clack in the cavity runner makes quick adjustment to the water pressure change according to the pressure in the cavity runner to control the water pressure of export runner, the regulation mode is very simple, high-efficient and accurate;
4. the utility model is provided with a pressure setting structure for adjusting the set pressure on the pilot valve body, and the position of the upper valve clack in the hollow runner can be adjusted through the pressure setting structure, thereby adapting to different outlet runner pressure requirements and adapting to different pipeline structures;
5. the pressure setting structure of the utility model controls the position of the spring through the adjusting screw, thereby adjusting the position of the upper valve clack in the hollow flow passage, the adjusting mode is very simple, and the pressure setting structure can adapt to various pressure requirements and pipeline structures;
6. the main valve clack of the utility model is a squirrel-cage structure, which can make the water flow entering the main valve clack from the inlet runner generate mutual impact, and can effectively reduce the water pressure of the outlet runner;
7. the long strip-shaped through holes on the main valve clack of the utility model are uniformly distributed, water flow enters the main valve clack from the long strip-shaped through holes, and water column clash is formed in the main valve clack to achieve the effect of energy dissipation and pressure reduction, so when the valve opening is smaller, the valve outlet pressure is far smaller than the valve inlet pressure, and even if the valve is fully opened, the valve outlet pressure is obviously reduced compared with the valve inlet pressure;
8. the utility model discloses be provided with the choke valve between the last cavity of piston and import runner, can the indoor water pressure condition in the effective control piston epicoele.
The utility model discloses a relief pressure valve simple structure, control mode is convenient, and is very accurate to main valve outlet flow way hydraulic control, and reaction time is short, and need not to arrange the fragile structure in the flow, has improved the life of relief pressure valve, has very big spreading value.
Drawings
FIG. 1: the structure schematic diagram of the pressure reducing valve of the utility model;
FIG. 2: the main valve structure schematic diagram of the utility model;
FIG. 3: the structure schematic diagram of the main valve clack of the utility model;
FIG. 4: the schematic diagram of A-A in FIG. 3 of the present invention;
FIG. 5: the structure schematic diagram of the pilot valve of the utility model (C-C view in figure 6);
FIG. 6: the structure schematic diagram of the pilot valve of the utility model (B-B view in figure 5);
wherein: 1-a main valve; 11-main valve body; 12-an inlet channel; 13-outlet flow channel; 14-main valve flap; 15-valve stem; 16-a piston cylinder; 17-a piston; 18-a strip-shaped through hole; 19-a throttle valve; 110-valve seat;
2-a pilot valve; 21-a pilot valve body; 22-inlet channel; 23-an outlet channel; 24-upper flap; 25-lower valve flap; 26-hollow flow channel; 27-a bottom cover; 28-adjusting screws; 29-spring seat; 210-a spring; 211-valve cover; 212-sealing ring.
Detailed Description
The present invention will be described in further detail with reference to the following drawings and specific embodiments.
Referring to fig. 1 to 6, the pressure reducing valve of the present embodiment includes a main valve 1 and a pilot valve 2, fig. 2 is a structure of the main valve 1 of the present embodiment, the main valve 1 includes a main valve body 11, the main valve body 11 is a hollow cavity structure, an inlet channel 12 and an outlet channel 13 are respectively disposed at two ends of the main valve body 11, and water flows into the main valve body 11 from the inlet channel 12 and flows out from the outlet channel 13. The main valve body 11 is provided with a main valve clack 14 for controlling the opening of the flow passage, as shown in fig. 3 to 4, the main valve clack 14 of the present embodiment is a hollow squirrel cage structure, the circumferential side wall of the main valve clack 14 is provided with a plurality of strip-shaped through holes 18 uniformly arranged along the circumferential direction at intervals, water flows enter the main valve clack 14 to form water column clash, so as to achieve the effect of energy dissipation and pressure reduction, when the valve opening is smaller, the pressure of the outlet flow passage 13 is far smaller than that of the inlet flow passage 12, and even when the main valve clack 14 is fully opened, the pressure of the outlet flow passage 13.
As shown in fig. 1-2, a valve seat 110 is disposed in the main valve body 11, and the valve seat 110 cooperates with the main valve flap 14 to open or close the main valve body 11. The main valve flap 14 is secured by a valve stem 15 to a piston 17 in a piston cylinder 16 on the main valve body 11. By varying the pressure across the piston 17, control of the main valve flap 14 is achieved. The piston 17 divides the piston cylinder 16 internal cavity into an upper chamber of the piston 17 and a lower chamber of the piston 17. Since the lower chamber of the piston 17 communicates with the outlet flow channel 13, the main valve body 11 of the present embodiment is actually divided into three pressure areas, i.e., one pressure area is located in the inlet flow channel 12, one pressure area is defined by the lower chamber of the piston 17 and the outlet flow channel 13, and one pressure area is defined by the upper chamber of the piston 17. In order to realize the control of the main valve flap 14 of the present embodiment, the cross-sectional area of the end of the main valve flap 14 away from the valve stem 15 is smaller than the cross-sectional area of the axial end of the piston 17.
As shown in fig. 5 to 6, for the pilot valve 2 of this embodiment, the pilot valve 2 includes a pilot valve body 21, the pilot valve body 21 is a hollow cavity structure arranged along the vertical direction, an inlet channel 22 and an outlet channel 23 are provided on the pilot valve body 21, the inlet channel 22 and the outlet channel 23 are vertically spaced, a height difference exists, and the inlet channel 22 is located above the outlet channel 23. The cavity inside the pilot valve body 21 forms a hollow flow passage 26 communicating the inlet passage 22 and the outlet passage 23, an upper valve flap 24 is arranged in the hollow flow passage 26, as shown in fig. 5-6, the upper valve flap 24 is a block structure which can move in the hollow flow passage 26 to control opening and closing, the upper valve flap 24 is positioned above the inlet passage 22 when the pilot valve 2 is opened, and the upper valve flap 24 moves vertically to open or close the inlet passage 22.
As shown in fig. 5 to 6, in the present embodiment, a pressure setting structure for adjusting the position of the upper valve flap 24 is disposed at the upper end of the pilot valve body 21, the pressure setting structure includes an adjusting screw 28, a spring seat 29 and a spring 210, one end of the adjusting screw 28 penetrates through a valve cover 211 at the upper end of the pilot valve body 21 and is fixedly connected with the spring seat 29 in the pilot valve body 21, one end of the spring 210 is fixed on the spring seat 29, and the other end is connected to the upper valve flap 24. By screwing the adjusting screw 28, the position of the upper valve flap 24 within the pilot valve body 21 can be changed, thereby adjusting the set pressure at which the pilot valve 2 operates.
In addition, the present embodiment is provided with a control chamber at the lower end of the pilot valve body 21, and the control chamber is used for adjusting the pressure in the hollow flow passage 26, thereby changing the position of the upper valve clack 24 and realizing the real-time adjustment control of the pilot valve 2. As shown in fig. 5 to 6, the lower end of the pilot valve body 21 is provided with a bottom cap 27, a lower valve flap 25 is disposed in the hollow flow passage 26 above the bottom cap 27, the lower valve flap 25 is a block structure movable in the hollow flow passage 26 and spaced from the upper valve flap 24, and the lower valve flap 25 forms a control chamber with variable volume with the bottom cap 27 at the lower end of the hollow flow passage 26 and the pilot valve body 21. The bottom cover 27 is provided with a communication through hole, the pressure intensity in the control cavity is changed by connecting other cavities so as to drive the vertical movement of the lower valve clack 25, the movement of the lower valve clack 25 can change the pressure intensity in the hollow flow passage 26, and therefore the position of the upper valve clack 24 is controlled, and the control and adjustment of the whole pilot valve 2 are realized.
A communication pipeline is provided between the pilot valve 2 and the main valve 1 in this embodiment, the pipeline structure is as shown in fig. 1, the inlet flow passage 12 is communicated with the upper chamber of the piston 17 through a pipeline, and a throttle valve 19 is provided on the communication pipeline. The upper chamber of the piston 17 communicates with the inlet passage 22 via a conduit. The outlet passage 23 communicates with the outlet flow passage 13 through a pipe. The control chamber is connected to the outlet channel 13 via a conduit, i.e. substantially no flow medium is generated in the conduit between the control chamber and the outlet channel 13, and only as a pressure conducting structure.
The function to be realized by this embodiment is that no matter the inlet flow passageHow the water pressure of the main valve flap 14 changes, the water pressure of the outlet flow path 13 should be maintained at a set value, and in order to achieve this function, the opening degree of the main valve flap 14 needs to be comprehensively controlled. The force applied to the main valve flap 14 during use is shown in FIG. 2, where P is1For inlet channel 12 water pressure, P2Is the outlet flow passage 13 and the lower chamber water pressure, P, of the piston 173Is the water pressure of the upper chamber of the piston 17, S1Is the cross-sectional area, S, of the end of the main valve flap 14 remote from the valve stem 152Is the cross-sectional area of the axial end of the piston 17, so:
the main valve flap 14 being subjected to upward hydraulic thrust F1＝P1*S1，
The main valve flap 14 being subjected to a downward hydraulic thrust F2＝P2*S1，
The piston 17 is subjected to a downward hydraulic thrust F4＝P3*S2；
Therefore, if the upward direction is positive, the combined force of the main valve flap 14 and the piston 17 is:
F＝F1-F2+F3-F4
＝P1*S1-P2*S1+P2*S2-P3*S2
＝(P1-P2)S1-(P3-P2)S2
wherein S is1<S2(ii) a If F>0, the main valve 1 opening will decrease; if F<0, the main valve 1 opening will increase.
The specific control measures of this embodiment are: a. when the pressure in the outlet flow passage 12 is lower than the set pressure of the pilot valve 2 (i.e. the water pressure in the hollow flow passage 26 cannot overcome the elastic force of the spring 210, and the upper valve flap 24 blocks the inlet passage 22), the pilot valve 2 is in a closed state, and part of the water flow enters the upper chamber of the piston 17 from the inlet flow passage 12 through the throttle 19 (no flow, only pressure conduction), so the water pressure in the upper chamber of the piston 17 should be equal to the water pressure in the upper chamber of the pilot valve 2The water pressure of the port flow path 12, i.e. P3＝P1Then, the main valve flap 14 is stressed:
F＝(P1-P2)S1-(P3-P2)S2
＝(P1-P2)(S1-S2)
and the water pressure of the inlet flow path 12 must be P which is greater than the water pressure of the outlet flow path 131>P2， S1<S2So that the force F exerted on the main valve flap 14 at this time is calculated<0, the piston 17 and the main valve flap 14 are forced downward, the opening of the main valve 1 increases, and the pressure in the outlet flow passage 13 rises.
b. When the pressure in the outlet flow passage 13 is higher than the set pressure of the pilot valve 2, the pilot valve 2 is in an open state (i.e. the water pressure in the hollow flow passage 26 overcomes the elastic force of the spring 210, and the upper valve flap 24 moves upward to open the inlet passage 22), and at this time, part of the water flow enters the upper chamber of the piston 17 from the inlet flow passage 12 through the throttle valve 19, meanwhile, the upper chamber of the piston 17 is also connected with the inlet channel 22, at this time, a smooth passage is formed, water flows from the inlet channel 12 to the upper chamber of the piston 17 through the throttle valve 19 and then flows into the inlet channel 22, the water in the inlet channel 22 flows into the outlet channel 23 through the hollow channel 26 and finally flows into the outlet channel 13, and the upper chamber of the piston 17, the hollow channel 26 and the outlet channel 13 form a passage, so that the water pressure of the upper chamber of the piston 17 is equal to the water pressure of the outlet channel 13, namely, P.3＝P2However, since the flow rate is restricted by the throttle valve 19, the water pressure between the inlet flow passage 12 and the upper chamber of the piston 17 is not equal, and the force applied to the main valve flap 14 in this case is calculated according to the above formula:
F＝(P1-P2)S1-(P3-P2)S2
＝(P1-P2)S1
while the water pressure in the inlet channel 12 must be greater than the water pressure P in the outlet channel 131>P2So that the force F exerted on the main valve flap 14 at this time is calculated>0, piston 17 and main valve flap 14 are forced upward, mainThe valve 1 decreases in opening and the water pressure in the outlet flow channel 13 decreases.
During actual operation, P3Will be at P2To P1The pressure of the outlet flow channel 13 tends to be stable, and the outlet pressure value is equal to the preset pressure of the spring 210 of the pilot valve 2, so that the hydraulic automatic control of the opening degree of the main valve 1 and the stability of the outlet pressure are realized.
When the outlet pressure of the main valve 1 needs to be changed, the adjusting screw 28 of the pilot valve 2 can be adjusted to change the preset pressure of the spring 210, so as to control the outlet pressure of the main valve 1.
A sealing ring 212 is arranged between the circumferential side walls of the upper and lower valve flaps 24, 25 and the hollow flow channel 26.
As shown in fig. 1, the vertical direction of the present embodiment refers to the up-down direction in fig. 1.
The foregoing shows and describes the general principles, essential features, and advantages of the invention. It will be understood by those skilled in the art that the present invention is not limited to the above embodiments, and that the foregoing embodiments and descriptions are provided only to illustrate the principles of the present invention without departing from the spirit and scope of the present invention. The scope of the invention is defined by the appended claims and equivalents thereof.
Claims (10)
1. A high pressure difference water control piston type pressure reducing valve comprises a main valve (1); the main valve (1) comprises a main valve body (11); the main valve body (11) is a hollow cavity with an inlet flow passage (12) and an outlet flow passage (13), and a main valve clack (14) for controlling the opening degree of the flow passage is arranged in the main valve body (11); the main valve clack (14) is fixedly connected with a piston (17) in a piston cylinder (16) on the main valve body (11) through a valve rod (15); the lower chamber of the piston (17) is communicated with the outlet flow passage (13),
the method is characterized in that: the device also comprises a pilot valve (2); the pilot valve (2) comprises a pilot valve body (21); the pilot valve body (21) is a hollow cavity with an inlet channel (22) and an outlet channel (23); the inlet channel (22) is communicated with the upper chamber of the piston (17); the outlet channel (23) is communicated with the outlet flow channel (13); the upper chamber of the piston (17) is communicated with the inlet flow passage (12); and a control structure which closes the pilot valve (2) when the pressure of the outlet flow channel (13) is less than the set pressure so as to increase the opening degree of the main valve clack (14) and opens the pilot valve (2) when the pressure of the outlet flow channel (13) is greater than the set pressure so as to reduce the opening degree of the main valve clack (14) is arranged in the pilot valve body (21).
2. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 1, wherein: the control structure comprises an upper flap (24); a hollow flow passage (26) communicated with the inlet channel (22) and the outlet channel (23) is arranged in the pilot valve body (21); the upper valve clack (24) is a block structure which can move in the hollow flow passage (26) to control opening and closing, and a pressure adjusting structure used for adjusting water pressure in the hollow flow passage (26) is arranged in the hollow flow passage (26) below the upper valve clack (24).
3. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 2, wherein: the pressure regulating structure comprises a lower valve flap (25); the lower valve clack (25) is a block structure which can move in the hollow flow passage (26) and is arranged at intervals with the upper valve clack (24), and the lower valve clack (25), a bottom cover (27) at the lower end of the hollow flow passage (26) and the pilot valve body (21) form a control chamber with variable volume; the control chamber is in communication with the outlet flow passage (13).
4. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 2 or 3, wherein: and a pressure setting structure for adjusting the set pressure is arranged on the pilot valve body (21) above the upper valve clack (24).
5. The high differential pressure, water controlled piston type pressure reducing valve as defined in claim 4, wherein: the pressure setting structure comprises an adjusting screw (28), a spring seat (29) and a spring (210); one end of the adjusting screw (28) penetrates through a valve cover (211) at the upper end of the pilot valve body (21) and is fixedly connected with a spring seat (29) in the pilot valve body (21); one end of the spring (210) is fixed on the spring seat (29), and the other end is connected with the upper valve clack (24).
6. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 1, wherein: the main valve clack (14) is a hollow squirrel cage structure fixed at the end part of the valve rod (15), and a plurality of overflowing slotted holes are formed in the circumferential side wall of the main valve clack (14).
7. The high differential pressure, water controlled piston type pressure reducing valve as defined in claim 6, wherein: the circumferential side wall of the main valve clack (14) is provided with a plurality of strip-shaped through holes (18) which are uniformly arranged at intervals along the circumferential direction.
8. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 6 or 7, wherein: the cross-sectional area of one end of the main valve flap (14) far away from the valve rod (15) is smaller than that of the axial end of the piston (17).
9. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 1, wherein: and a throttle valve (19) is arranged on a communication pipeline between the inlet flow channel (12) and the upper chamber of the piston (17).
10. A high differential pressure, water controlled piston type pressure reducing valve as claimed in claim 3, wherein: and a sealing ring (212) is arranged between the circumferential side walls of the upper valve clack (24) and the lower valve clack (25) and the hollow flow channel (26).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922002363.XU CN211449776U (en) | 2019-11-19 | 2019-11-19 | High-pressure-difference water-control piston type pressure reducing valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922002363.XU CN211449776U (en) | 2019-11-19 | 2019-11-19 | High-pressure-difference water-control piston type pressure reducing valve |
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| Publication Number | Publication Date |
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| CN211449776U true CN211449776U (en) | 2020-09-08 |
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| CN201922002363.XU Active CN211449776U (en) | 2019-11-19 | 2019-11-19 | High-pressure-difference water-control piston type pressure reducing valve |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043365A (en) * | 2019-11-19 | 2020-04-21 | 武汉大禹阀门股份有限公司 | High-pressure-difference water-control piston type pressure reducing valve |
| CN113738924A (en) * | 2021-08-25 | 2021-12-03 | 浙江大学 | Pressure reducing device capable of reducing cavitation damage, valve structure and method |
| CN114704472A (en) * | 2022-04-29 | 2022-07-05 | 江苏大学 | Large-flow series-parallel emergency rescue pump |
-
2019
- 2019-11-19 CN CN201922002363.XU patent/CN211449776U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043365A (en) * | 2019-11-19 | 2020-04-21 | 武汉大禹阀门股份有限公司 | High-pressure-difference water-control piston type pressure reducing valve |
| CN111043365B (en) * | 2019-11-19 | 2024-09-17 | 武汉大禹阀门股份有限公司 | High pressure difference water control piston type pressure reducing valve |
| CN113738924A (en) * | 2021-08-25 | 2021-12-03 | 浙江大学 | Pressure reducing device capable of reducing cavitation damage, valve structure and method |
| CN114704472A (en) * | 2022-04-29 | 2022-07-05 | 江苏大学 | Large-flow series-parallel emergency rescue pump |
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| GR01 | Patent grant |