CN111609159A - Two-way sealing disc valve with asymmetric structure - Google Patents
Two-way sealing disc valve with asymmetric structure Download PDFInfo
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- CN111609159A CN111609159A CN201910142014.XA CN201910142014A CN111609159A CN 111609159 A CN111609159 A CN 111609159A CN 201910142014 A CN201910142014 A CN 201910142014A CN 111609159 A CN111609159 A CN 111609159A
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- 238000007789 sealing Methods 0.000 title claims abstract description 60
- 239000003245 coal Substances 0.000 claims abstract description 51
- 239000000428 dust Substances 0.000 claims abstract description 8
- 239000000843 powder Substances 0.000 claims description 11
- 230000000903 blocking effect Effects 0.000 claims description 8
- 238000003466 welding Methods 0.000 claims description 6
- 230000002457 bidirectional effect Effects 0.000 abstract description 12
- 238000000034 method Methods 0.000 abstract description 11
- 238000009825 accumulation Methods 0.000 abstract description 3
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 239000000463 material Substances 0.000 abstract description 2
- 238000002309 gasification Methods 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000002955 isolation Methods 0.000 description 2
- 238000003786 synthesis reaction Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 1
- 239000002817 coal dust Substances 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000007800 oxidant agent Substances 0.000 description 1
- 239000001301 oxygen Substances 0.000 description 1
- 229910052760 oxygen Inorganic materials 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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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
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
- F16K3/04—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members
- F16K3/06—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members in the form of closure plates arranged between supply and discharge passages
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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
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/30—Details
- F16K3/314—Forms or constructions of slides; Attachment of the slide to the spindle
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Lift Valve (AREA)
Abstract
The invention belongs to the technical field of pipeline engineering, and particularly relates to a bidirectional sealing disc valve with an asymmetric structure. The valve comprises an upper valve body 1, a lower valve body 2, a middle valve body 3, a valve rod 4, an upper valve seat 5, a lower valve seat 6, an upper valve disc 7, a lower valve disc 8, an upper disc spring group 9, a lower disc spring group 10, an upper dust retaining ring 11, a lower dust retaining ring 12, an upper bearing 13 and a lower bearing 14. The technical scheme of the invention has the beneficial effects that: the device can completely meet the special process requirements of the Ningshan coal stove, namely, the reliable two-way sealing under the given pressure difference condition is realized, the possible influence of material accumulation on a valve is also avoided, and the device can be applied to other similar pulverized coal pressurized conveying devices.
Description
Technical Field
The invention belongs to the technical field of pipeline engineering, and particularly relates to a bidirectional sealing disc valve with an asymmetric structure.
Background
Dry coal dust gasification technology is one of the methods for converting raw coal into synthesis gas. The basic process is that the superfine dry coal powder is conveyed from a normal pressure coal bunker to a high pressure coal feeding tank through a coal lock hopper through the cyclic pressurizing and pressure releasing process of the coal lock hopper, and the feeding tank continuously conveys the superfine dry coal powder to a gasification furnaceFeeding the coal into the synthesis gas (CO + H) under the action of oxidants such as oxygen, water and the like2) Is performed. The coal bunker, the coal lock hopper and the coal feeding tank are arranged on the frame from top to bottom, after the coal powder falls into the coal lock hopper from the coal bunker under the action of gravity, the inlet valve of the coal lock hopper is closed and starts to be pressurized, the balance valve is opened after the pressurization is finished, the outlet valve is opened, and the coal powder falls into the feeding tank under the action of gravity.
Under normal conditions, the working pressure of the coal bunker is normal pressure, the feeding tank is maintained in a high-pressure state, the pressure of the coal lock bucket alternates between normal pressure and high pressure, the pressure of the coal lock bucket does not exceed the pressure of the feeding tank under interlocking control, the sealing requirement of the outlet valve of the coal lock bucket is one-way sealing, and in order to increase the reliability of the device, the inlet valve and the outlet valve of the coal lock bucket are both arranged in a double-valve series connection mode.
In addition, in the aspect of the selection of the switch valve in the pressurized pulverized coal conveying section, the disc valve is widely used as a replacement valve of a metal sealing ball valve. According to the one-way sealing process requirement, the outlet valve of the coal lock hopper is generally set to be a single-disc valve, only one valve disc is arranged in a valve cavity, the sealing surface faces upwards, and the high-pressure feed tank and the lock hopper can be completely isolated when the lock hopper is decompressed.
However, under some possible abnormal conditions, such as improper manual operation, failure of a coal lock bucket pressure regulating valve, failure of coal lock bucket overpressure interlocking and the like, the pressure of the lock bucket may exceed the feeding tank and cause pressure to be applied to the feeding tank in series, absolute isolation between the feeding tank and the feeding tank cannot be achieved, but the overpressure generally does not exceed 0.3MPa. Many processes either do not take these extreme conditions into account or impose excessive demands on the valve, even requiring the valve to be sealed bi-directionally at full differential pressure, which are either not very reasonable or not very compliant with actual operating conditions.
The Ningcoal furnace, as a gasification technology developed by absorbing various domestic and foreign gasification technologies, puts more scientific and reasonable requirements on the pressure difference between the coal lock hopper and the feeding tank. The forward/reverse pressure difference from the coal lock hopper to the feed tank is required to be considered according to 0.3/6.2MPa, and the requirement not only considers abnormal working conditions, but also combines the practical operation of the device. If all single-disc valves are selected, the forward pressure difference of 0.3MPa is met, the disc spring force can be greatly improved, but the problems of aggravation of abrasion, large actuating mechanism, high energy consumption, low reliability and the like are caused. If the conventional symmetrical double-disc valve is adopted, the valve switch can not be in place due to the accumulation of pulverized coal in the valve cavity. In addition, the series connection of two-way sealed valves can also bring the problem of pressure build-up jam.
Disclosure of Invention
The invention aims to solve the technical problem that aiming at the special process requirements of a Ningbing coal furnace, on the basis of a conventional double-disc valve, a disc valve with an asymmetric structure is designed, and the disc valve is mainly characterized in that the thicknesses of two valve discs are set to be inconsistent, so that the aims of meeting the process requirements and ensuring the smooth opening and closing are expected to be fulfilled.
In order to realize the purpose, the invention adopts the technical scheme that:
a two-way sealing disc valve with an asymmetric structure comprises an upper valve body 1, a lower valve body 2, a middle valve body 3, a valve rod 4, an upper valve seat 5, a lower valve seat 6, an upper valve disc 7, a lower valve disc 8, an upper disc spring group 9, a lower disc spring group 10, an upper dust retaining ring 11, a lower dust retaining ring 12, an upper bearing 13 and a lower bearing 14;
the upper valve body 1 and the lower valve body 2 are provided with bolt holes which are uniformly distributed along the circumference;
the middle valve body 3 is of a cylindrical structure, is arranged between the upper valve body 1 and the upper valve body 2, and is connected with the upper valve body 1, the lower valve body 2 and the middle valve body 3 together through a group of studs and nuts;
the upper valve body 1 is provided with a through hole, the lower valve body 2 is provided with a blind hole, the valve rod 4 passes through the through hole on the upper valve body 1 and is inserted into the blind hole on the lower valve body 2, the valve rod 4 and the upper valve body 1 are fixed through an upper bearing 13, and the valve rod 4 and the lower valve body 2 are fixed through a lower bearing 14;
the upper valve seat 5 and the lower valve seat 6 are both of stepped structures, and welding grooves are formed in the bottoms of the upper valve seat and the lower valve seat and are used for sealing after the valve is pressed into the upper valve body 1 and the lower valve body 2;
the valve rod 4 is formed by welding three parts: the valve body 1 is inserted into a shaft, the upper valve disc 1 is inserted into a cylindrical sleeve, and the connecting shaft and the sleeve are connecting plates; blind holes are respectively processed on two sides of the columnar sleeve, and disc spring guide columns are arranged in the blind holes;
the upper disc spring group 9 and the lower disc spring group 10 are respectively arranged in blind holes at two sides of a column sleeve in the valve rod 4;
the upper valve disc 7 and the lower valve disc 8 are respectively inserted into a cylindrical sleeve in the valve rod 4;
the upper disc spring group 9 and the lower disc spring group 10 respectively provide initial sealing pretightening force for the upper valve disc 7 and the lower valve disc 8;
the upper ash blocking ring 11 and the lower ash blocking ring 12 are arranged in a groove on the cylindrical sleeve to prevent coal powder from entering the upper disc spring group 9 and the lower disc spring group 10;
the actuating mechanism drives the valve rod 4 to rotate in the upper bearing 13 and the lower bearing 14, and drives the upper valve disc 7 and the lower valve disc 8 to respectively slide freely on the upper valve body 1, the upper valve seat 5, the lower valve body 2 and the lower valve seat 6 while rotating, so that the valve is opened and closed.
Further, according to the asymmetric structure bidirectional sealing disk valve, the actuating mechanism is driven in one of the following three ways: pneumatic, hydraulic, electric.
Further, according to the asymmetric-structure bidirectional sealing disk valve, the thickness of the upper valve disk 7 is 50-60 mm, and the width of the sealing surface is 20-30 mm.
Furthermore, according to the asymmetric structure bidirectional sealing disk valve, the thickness of the lower valve disk 8 is 20-30 mm, and the width of the sealing surface is 10-12 mm.
Further, as for the two-way sealing disk valve with the asymmetric structure, the disk spring force provided by the upper disk spring group 9 is 10000-20000N.
Further, according to the asymmetric structure bidirectional sealing disc valve, the disc spring force provided by the lower disc spring group 10 is 3000-5000N.
Further, according to the asymmetric structure bidirectional sealing disk valve, the width of the sealing surface of the upper valve seat 5 is 18-28 mm.
Further, according to the bidirectional sealing disk valve with the asymmetric structure, the width of the sealing surface of the lower valve seat 6 is 8-10 mm.
Further, according to the asymmetric-structure bidirectional sealing disc valve, gaps are formed between the upper valve disc 7 and the lower valve disc 8 and between the cylindrical sleeves in the valve rod 4, so that the valve discs can slide freely on the upper valve body 1, the upper valve seat 5, the lower valve body 2 and the lower valve seat 6 when the valve is opened and closed.
The technical scheme of the invention has the beneficial effects that: the device can completely meet the special process requirements of the Ningshan coal stove, namely, the reliable two-way sealing under the given pressure difference condition is realized, the possible influence of material accumulation on a valve is also avoided, and the device can be applied to other similar pulverized coal pressurized conveying devices.
Drawings
FIG. 1 is a schematic view of a valve arrangement of a pulverized coal pressurized conveying device of a coal stove;
fig. 2 is a schematic diagram of an asymmetric disk valve structure.
In the figure, 1-upper valve body, 2-lower valve body, 3-middle valve body, 4-valve rod, 5-upper valve seat, 6-lower valve seat, 7-upper valve disc, 8-lower valve disc, 9-upper disc spring group, 10-lower disc spring group, 11-upper dust retaining ring, 12-lower dust retaining ring 13-upper bearing 14-lower bearing.
Detailed Description
The technical scheme of the invention is explained in detail in the following by combining the drawings and the specific embodiment.
The invention relates to a Ning coal stove, which generally adopts a mode of installing a single-disk valve and a double-disk valve in a combined mode, wherein two single-disk valves (1# valve and 2# valve) are arranged at an inlet of a coal lock hopper, a single-disk valve (3#) and a double-disk valve (4# valve) are arranged at an outlet of the coal lock hopper, and the single-disk valve is arranged above the single-disk valve. Specifically, according to the requirement of 0.3/6.2MPa of pressure difference between a coal lock hopper and a coal feeding tank of the coal stove, the conventional symmetrical disc valve is changed, a valve disc on the inlet side is designed into a thick disc, a valve on the outlet side is designed into a thin disc, and the strength and the rigidity of the valve are ensured not to influence the sealing under the pressure difference. The pre-tightening disc spring force and the size of the sealing surface are designed to be different.
As shown in figure 1, the valve arrangement scheme is a common arrangement scheme on a pulverized coal conveying device, in order to improve the reliability of tight isolation between containers, two tight shut-off valves are arranged in series between the containers, and a coal lock bucket inlet valve (1#, 2#) lock bucket outlet valve (3#, 4 #). Except that the structure of the No. 4 valve adopts the special structure provided by the invention, the structures of other valves can adopt single-disc valves.
As shown in fig. 2, the invention provides a bidirectional sealing disk valve with a special structure, and in order to meet special process requirements of a coal burning furnace, the internal part of the bidirectional sealing disk valve is designed to be in an asymmetric structure. The asymmetry is mainly reflected in: upper and lower valve discs 7, 8 of different thickness and different sealing surface dimensions, upper and lower disc spring sets 9, 10 providing different disc spring forces, upper and lower valve seats 5, 6 having different sealing surface dimensions.
Specifically, the invention discloses a bidirectional sealing disk valve with an asymmetric structure, which comprises an upper valve body 1, a lower valve body 2, a middle valve body 3, a valve rod 4, an upper valve seat 5, a lower valve seat 6, an upper valve disk 7, a lower valve disk 8, an upper disk spring group 9, a lower disk spring group 10, an upper ash blocking ring 11, a lower ash blocking ring 12, an upper bearing 13 and a lower bearing 14;
the upper valve body 1 and the lower valve body 2 are provided with bolt holes which are uniformly distributed along the circumference;
the middle valve body 3 is of a cylindrical structure, is arranged between the upper valve body 1 and the upper valve body 2, and is connected with the upper valve body 1, the lower valve body 2 and the middle valve body 3 together through a group of studs and nuts;
the upper valve body 1 is provided with a through hole, the lower valve body 2 is provided with a blind hole, the valve rod 4 passes through the through hole on the upper valve body 1 and is inserted into the blind hole on the lower valve body 2, the valve rod 4 and the upper valve body 1 are fixed through an upper bearing 13, and the valve rod 4 and the lower valve body 2 are fixed through a lower bearing 14;
the upper valve seat 5 and the lower valve seat 6 are both of stepped structures, and welding grooves are formed in the bottoms of the upper valve seat and the lower valve seat and are used for sealing after the valve is pressed into the upper valve body 1 and the lower valve body 2;
the valve rod 4 is formed by welding three parts: the valve body 1 is inserted into a shaft, the upper valve disc 1 is inserted into a cylindrical sleeve, and the connecting shaft and the sleeve are connecting plates; blind holes are respectively processed on two sides of the columnar sleeve, and disc spring guide columns are arranged in the blind holes;
the upper disc spring group 9 and the lower disc spring group 10 are respectively arranged in blind holes at two sides of a column sleeve in the valve rod 4;
the upper valve disc 7 and the lower valve disc 8 are respectively inserted into a cylindrical sleeve in the valve rod 4;
and gaps are arranged between the upper valve disc 7 and the lower valve disc 8 and between the column sleeves in the valve rod 4, so that when the valve is opened and closed, the valve discs freely slide on the upper valve body 1, the upper valve seat 5, the lower valve body 2 and the lower valve seat 6.
The upper disc spring group 9 and the lower disc spring group 10 respectively provide initial sealing pretightening force for the upper valve disc 7 and the lower valve disc 8;
the upper ash blocking ring 11 and the lower ash blocking ring 12 are arranged in a groove on the cylindrical sleeve to prevent coal powder from entering the upper disc spring group 9 and the lower disc spring group 10;
the actuating mechanism drives the valve rod 4 to rotate in the upper bearing 13 and the lower bearing 14, and drives the upper valve disc 7 and the lower valve disc 8 to respectively slide freely on the upper valve body 1, the upper valve seat 5, the lower valve body 2 and the lower valve seat 6 while rotating, so that the valve is opened and closed. In the present embodiment, the actuator is driven in one of three ways: pneumatic, hydraulic, electric.
In the embodiment shown in fig. 2, the valve is mounted vertically and the medium flows from top to bottom when the valve is open. After the valve is closed, the pressure P1 at the inlet side of the valve is the lock hopper pressure, and the pressure P2 at the outlet side is the pressure of the feed tank, and the maximum pressure is 6.2 MPa. When P1 is greater than P2, the upper valve disc is pushed open, the pressure in the valve cavity is P1, the upper valve disc does not bear pressure, the pressure difference delta P borne by the lower valve disc is P1-P2, generally, delta P is less than 0.3MPa, the pressure difference borne by the lower valve disc is small, the thickness of the valve disc is small, the size of the sealing surface of the lower valve disc 8 and the size of the sealing surface of the lower valve seat 6 are small, and the number of disc springs of the lower disc spring group 10 is small. When the lock hopper is depressurized, the pressure P1 is gradually reduced from 6.2MPa to normal pressure, the pressure difference borne by the upper valve disc 7 is increasingly larger, and the maximum value is 6.2+0.3 which is 6.5MPa of the maximum P1. The upper valve disk 7 is subjected to a large pressure difference, and requires greater strength and rigidity, as well as seal surface width and initial preload. Therefore, the thickness of the upper valve plate 7 is 50-60 mm; the sealing surface of the upper valve seat 5 is wider and is 18-28 mm; the number of disc springs included in the upper disc spring group 9 is large, and the provided disc spring force is 10000-20000N. Other specific parameters comprise that the width of the sealing surface of the upper valve disc 7 is 20-30 mm; the thickness of the lower valve disc 8 is 20-30 mm, and the width of the sealing surface is 10-12 mm; the disc spring force provided by the lower disc spring group 10 is 3000-5000N; the width of the sealing surface of the lower valve seat 6 is 8-10 mm.
In the embodiment shown in fig. 2, the lower valve disc 8 is designed to be as thin as possible, so that even if the ultrafine coal powder enters the valve cavity during the blanking process and is gathered to a certain extent, the sharp valve disc can still freely move at intervals of the gathered coal powder to cut and clean the coal powder block, so that the residual coal powder in the valve cavity is kept low, and the opening and closing action of the valve is not influenced.
Claims (10)
1. The utility model provides an asymmetric structure two-way seal disk valve which characterized in that:
the valve comprises an upper valve body (1), a lower valve body (2), a middle valve body (3), a valve rod (4), an upper valve seat (5), a lower valve seat (6), an upper valve disc (7), a lower valve disc (8), an upper disc spring group (9), a lower disc spring group (10), an upper dust retaining ring (11), a lower dust retaining ring (12), an upper bearing (13) and a lower bearing (14);
bolt holes which are uniformly distributed along the circumference are arranged on the upper valve body (1) and the lower valve body (2);
the middle valve body (3) is of a cylindrical structure, is arranged between the upper valve body (1) and the upper valve body (2), and is connected with the upper valve body (1), the lower valve body (2) and the middle valve body (3) together through a group of studs and nuts;
the upper valve body (1) is provided with a through hole, the lower valve body (2) is provided with a blind hole, the valve rod (4) penetrates through the through hole in the upper valve body (1) and is inserted into the blind hole in the lower valve body (2), the valve rod (4) and the upper valve body (1) are fixed through the upper bearing (13), and the valve rod (4) and the lower valve body (2) are fixed through the lower bearing (14);
the upper valve seat (5) and the lower valve seat (6) are both of stepped structures, and welding grooves are formed in the bottoms of the upper valve seat and the lower valve seat and used for sealing after the valve is pressed into the upper valve body (1) and the lower valve body (2);
the valve rod (4) is formed by welding three parts: the valve body 1 is inserted into a shaft, the upper valve disc 1 is inserted into a cylindrical sleeve, and the connecting shaft and the sleeve are connecting plates; blind holes are respectively processed on two sides of the columnar sleeve, and disc spring guide columns are arranged in the blind holes;
the upper disc spring group (9) and the lower disc spring group (10) are respectively arranged in blind holes at two sides of a column-shaped sleeve in the valve rod (4);
the upper valve disc (7) and the lower valve disc (8) are respectively inserted into a cylindrical sleeve in the valve rod (4);
the upper disc spring group (9) and the lower disc spring group (10) respectively provide initial sealing pretightening force for the upper valve disc (7) and the lower valve disc (8);
the upper ash blocking ring (11) and the lower ash blocking ring (12) are arranged in a groove on the cylindrical sleeve to prevent coal powder from entering the upper disc spring group (9) and the lower disc spring group (10);
the actuating mechanism drives the valve rod (4) to rotate in the upper bearing (13) and the lower bearing (14), and drives the upper valve disc (7) and the lower valve disc (8) to respectively freely slide on the upper valve body (1), the upper valve seat (5), the lower valve body (2) and the lower valve seat (6) while rotating, so that the valve is switched on and off.
2. An asymmetric-configuration bi-directional sealing disk valve as in claim 1, wherein: the actuating mechanism is driven in one of the following three ways: pneumatic, hydraulic, electric.
3. An asymmetric-configuration bi-directional sealing disk valve as in claim 1, wherein: the thickness of the upper valve disc (7) is 50-60 mm, and the width of the sealing surface is 20-30 mm.
4. An asymmetric-configuration bi-directional sealing disk valve as in claim 1, wherein: the thickness of the lower valve disc (8) is 20-30 mm, and the width of the sealing surface is 10-12 mm.
5. An asymmetric-configuration bi-directional sealing disk valve as in claim 1, wherein: the disc spring force provided by the upper disc spring group (9) is 10000-20000N.
6. An asymmetric-configuration bi-directional sealing disk valve as in claim 1, wherein: the disc spring force provided by the lower disc spring group (10) is 3000-5000N.
7. An asymmetric-configuration bi-directional sealing disk valve as in claim 1, wherein: the width of the sealing surface of the upper valve seat (5) is 18-28 mm.
8. An asymmetric-configuration bi-directional sealing disk valve as in claim 1, wherein: the width of the sealing surface of the lower valve seat (6) is 8-10 mm.
9. An asymmetric-configuration bi-directional sealing disk valve as in claim 1, wherein: all set up the clearance between going up valve disc (7) and lower valve disc (8) and valve rod (4) center pillar type sleeve to when guaranteeing valve switch, the valve disc is in last valve body (1), go up valve seat (5) and lower valve body (2), lower valve seat (6) and freely slides.
10. An asymmetric-configuration bi-directional sealing disk valve as in claim 1, wherein: the actuating mechanism is driven in one of the following three ways: pneumatic, hydraulic, electric;
the thickness of the upper valve disc (7) is 50-60 mm, and the width of the sealing surface is 20-30 mm;
the thickness of the lower valve disc (8) is 20-30 mm, and the width of the sealing surface is 10-12 mm;
the disc spring force provided by the upper disc spring group (9) is 10000-20000N;
the disc spring force provided by the lower disc spring group (10) is 3000-5000N;
the width of the sealing surface of the upper valve seat (5) is 18-28 mm;
the width of the sealing surface of the lower valve seat (6) is 8-10 mm;
all set up the clearance between going up valve disc (7) and lower valve disc (8) and valve rod (4) center pillar type sleeve to when guaranteeing valve switch, the valve disc is in last valve body (1), go up valve seat (5) and lower valve body (2), lower valve seat (6) and freely slides.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910142014.XA CN111609159A (en) | 2019-02-26 | 2019-02-26 | Two-way sealing disc valve with asymmetric structure |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910142014.XA CN111609159A (en) | 2019-02-26 | 2019-02-26 | Two-way sealing disc valve with asymmetric structure |
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|---|---|
| CN111609159A true CN111609159A (en) | 2020-09-01 |
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|---|---|---|---|
| CN201910142014.XA Pending CN111609159A (en) | 2019-02-26 | 2019-02-26 | Two-way sealing disc valve with asymmetric structure |
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| CN106015611A (en) * | 2016-06-20 | 2016-10-12 | 中节能耐磨技术宜兴有限公司 | Ceramic disk cutting valve |
| CN107269868A (en) * | 2017-07-19 | 2017-10-20 | 浙江日高阀门有限公司 | A kind of electric high-temperature water-cooled blank-plate valve |
| RU176075U1 (en) * | 2017-01-09 | 2017-12-27 | Акционерное Общество "Благовещенский Арматурный Завод" | Butterfly valve |
| CN207195710U (en) * | 2017-08-30 | 2018-04-06 | 苏州安特威阀门有限公司 | The pneumatic anti-device that builds the pressure of moushroom valve |
| CN207814482U (en) * | 2018-01-15 | 2018-09-04 | 上海凯科阀门制造有限公司 | Double plate valve |
| CN209671655U (en) * | 2019-02-26 | 2019-11-22 | 北京航天石化技术装备工程有限公司 | A kind of unsymmetric structure two way seal moushroom valve |
-
2019
- 2019-02-26 CN CN201910142014.XA patent/CN111609159A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5396919A (en) * | 1993-08-18 | 1995-03-14 | Everlasting Valve Co., Inc. | Rotating disc valve |
| CN201437848U (en) * | 2009-07-07 | 2010-04-14 | 北京航天动力研究所 | Axial balanced type disc valve |
| CN105276217A (en) * | 2014-06-05 | 2016-01-27 | Smc株式会社 | Gate valve |
| CN106015611A (en) * | 2016-06-20 | 2016-10-12 | 中节能耐磨技术宜兴有限公司 | Ceramic disk cutting valve |
| RU176075U1 (en) * | 2017-01-09 | 2017-12-27 | Акционерное Общество "Благовещенский Арматурный Завод" | Butterfly valve |
| CN107269868A (en) * | 2017-07-19 | 2017-10-20 | 浙江日高阀门有限公司 | A kind of electric high-temperature water-cooled blank-plate valve |
| CN207195710U (en) * | 2017-08-30 | 2018-04-06 | 苏州安特威阀门有限公司 | The pneumatic anti-device that builds the pressure of moushroom valve |
| CN207814482U (en) * | 2018-01-15 | 2018-09-04 | 上海凯科阀门制造有限公司 | Double plate valve |
| CN209671655U (en) * | 2019-02-26 | 2019-11-22 | 北京航天石化技术装备工程有限公司 | A kind of unsymmetric structure two way seal moushroom valve |
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