CN103115189A - Energy-saving balanced high-pressure single seated valve - Google Patents
Energy-saving balanced high-pressure single seated valve Download PDFInfo
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- CN103115189A CN103115189A CN2013100409767A CN201310040976A CN103115189A CN 103115189 A CN103115189 A CN 103115189A CN 2013100409767 A CN2013100409767 A CN 2013100409767A CN 201310040976 A CN201310040976 A CN 201310040976A CN 103115189 A CN103115189 A CN 103115189A
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- valve
- piston
- valve body
- seat
- spool
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Abstract
The invention provides an energy-saving balanced high-pressure single seated valve which comprises a valve body, a valve cover, a valve rod, a valve core and a valve seat. The valve rod penetrates through the valve cover and extends into the interior of the valve body, the valve core is arranged on the middle portion of the valve rod, and the valve seat matched with the valve core is arranged on the inner wall of the valve body. Two sets of piston devices are arranged in the valve body and on two sides of the valve core in a symmetrical mode, piston cylinders in the two sets of the piston devices are used for processing piston guide stroke holes along the action direction of the valve rod on the inner surface of the valve body, and corresponding pistons are arranged on the valve rod. Acting force generated when a medium in the valve acts on the pistons and the section of the valve core is balanced out mutually, driving force needed by an actuator is reduced and energy is saved, the high pressure difference bearing capability of the valve is improved, and the valve core is free from the phenomenon of oscillating when the high-pressure difference is generated. The valve body is simple in structure, compared with a traditional medium flow channel, a Z-shaped medium flow channel is simple, small in damping coefficient, and therefore energy consumption of the valve is reduced; and processing in the valve body is convenient and easy and the blocking phenomenon of the medium is reduced due to arrangement of the Z-shaped medium flow channel and the piston guide stroke holes.
Description
Technical field
The present invention relates to a kind of valve, specifically a kind of power-saving balanced high pressure single-seat valve.
Background technique
The single-seat valve of prior art as shown in Figure 1, the valve of single seat structural type no matter pressure reduction is large and little, along with valve pressure increases, its valve core valve stem receives that power upwards is very large, the ouput force of required final controlling element is just larger, vice versa.When requiring the final controlling element ouput force excessive when pressure, when pressure reduction is excessive, very easily cause the spool vibration.And its " S " type runner is complicated, affects the medium circulation.
The double seated valve of prior art as shown in Figure 2, though can be applicable to the High Pressure Difference situation, its valve inner structure is complicated, its processing, assembly precision require high, and medium runner is complicated, and be not high compared to its sealing grade of single seat structure because of two-seater sealing cause, easily leaks.
Summary of the invention
The object of the invention is to: provide a kind of simple in structure, be easy to process, assemble, debug conveniently, with low cost, good airproof performance, power-saving balanced high pressure single-seat valve that pressure reduction is high.
The technical solution adopted in the present invention is:
A kind of power-saving balanced high pressure single-seat valve comprises valve body, valve gap, valve rod, spool and valve seat, and described valve rod passes valve gap, stretches into valve inner, and described spool is arranged in the middle part of valve rod, and the valve seat that matches with spool is arranged on described valve interior wall; In described valve body, spool both sides are provided with the piston apparatus of 2 groups of balanced, symmetrical, the piston cylinder of 2 groups of piston apparatus be on valve interior surface along valve rod direction of action machining piston guiding stroke hole, corresponding piston is arranged on valve rod.
When described valve closing, the piston of 2 groups of piston apparatus all is positioned at the bottom in piston guide stroke hole.
The medium runner of described valve internal is " Z " type.
By above-mentioned improvement, the invention has the beneficial effects as follows apparent:
1. the increase equalizing piston, make spool cancelled out each other by the medium active force, and compared to the valve of same size single seat structure, required final controlling element ouput force is less, thereby plays energy-conservation effect;
2. the increase equalizing piston, cancel out each other because it makes the suffered medium active force of spool, and valve can bear that pressure reduction is larger after and before the valve, makes its Applicable scope wider;
3. increase equalizing piston, because of up and down equalizing piston leading role, thereby spool reforming phenomena can not occur;
4. valve inner " Z " type medium runner, compared to " S " type medium runner, its structure is more simply smooth and easy, be difficult for stifled card, and it is easy to process, reduces production costs.
Description of drawings
Fig. 1 is the structural representation of prior art single-seat valve;
Fig. 2 is the structural representation of prior art double seated valve;
Fig. 3 is the structural representation of the power-saving balanced high pressure single-seat valve of the present invention.
Number in the figure represents: 1.: valve body, 2.: influent stream side piston apparatus, 3.: spool, 4.: go out to flow side piston apparatus, 5.: valve rod, 6.: valve gap.
Embodiment
As shown in Figure 3, the present invention is a kind of power-saving balanced high pressure single-seat valve, comprise valve body 1., valve gap 6., valve rod 5., spool 3. and valve seat, valve rod 5. pass valve gap 6., to stretch into valve body 1. inner, spool 3. be arranged on valve rod 5. the middle part, 1. described valve body has the valve seat that 3. matches with spool on inwall, and this is the basic structure of high pressure valve.In this embodiment, 1. the high pressure valve valve body by solid forging processing, also can be other forms.1. valve body is sleeve-shaped, and valve body 1. top is provided with end cap---valve gap 6., valve gap is provided with the hole 5. stretched into for valve rod, parts such as its top connection bracket simultaneously on 6.; 1. the bottom is fixedly connected with guard seal to valve body, 5. anti-valve rod blows out.Innovation of the present invention is:
Valve body of the present invention 1. in, 3. spool be provided with the piston apparatus of 2 groups of balanced, symmetrical in both sides, the piston cylinder of 2 groups of piston apparatus is actual be valve body 1. on internal surface along 5. direction of action machining piston guiding stroke hole of valve rod, corresponding piston is arranged on valve rod and 5. goes up.When valve closing, the piston of 2 groups of piston apparatus all is positioned at the bottom in piston guide stroke hole.The piston apparatus of these 2 groups of balanced, symmetrical offsets medium active force in valve, reduce required final controlling element ouput force and improve the ability that 1. valve body can bear pressure reduction before and after valve.
In this embodiment, 2. the piston apparatus of 2 groups of balanced, symmetrical is respectively influent stream side piston apparatus and goes out to flow the side piston apparatus 4..Spool 3. influent stream side piston apparatus piston cylinder 2. is in the 1. piston guide stroke hole of bottom processing of valve body, and its supporting piston is at the 5. piston slider that is fixedly connected with of end of valve rod.3. spool goes out to flow side piston apparatus piston guide stroke hole 4. is in the 1. piston guide stroke hole of top processing of valve body, and the corresponding valve gap in top in this piston guide stroke hole is the position 6., and its supporting piston is arranged on valve rod corresponding position 5..The length in design influent stream side piston apparatus piston guide stroke hole 2. is l, and the length that goes out to flow side piston apparatus piston guide stroke hole 4. is l '; L 〉=l '.
In addition, influent stream side piston apparatus 2. and go out to flow on the surface of contact in side piston apparatus piston 4. and piston guide stroke hole and be provided with seal arrangement, as the soft seal ring of installation in groove, groove is set on the piston side face.
Attention:
If influent stream side piston apparatus piston diameter 2. is when going out to flow 4. piston diameter of side piston apparatus, valve always is stream open form valve.
If influent stream side piston apparatus piston diameter 2. is when going out to flow 4. piston diameter of side piston apparatus, valve always is stream closed form valve.
Above-mentioned, the high pressure valve valve rod 5., 3. spool reach piston apparatus, can adopt the form of whole processing or the form of segmented combination according to spool seal form 3..This high pressure valve is according to 3. profilogram of different spools, the Flow characteristicss such as its Flow characteristics can be soon and opens, logarithm, linearity.
The medium runner of valve internal is " Z " type, namely spool 3. both sides the influent stream runner with go out that runner is vertical to be arranged 1. axially, in the same way perpendicular to valve body.Compared to runner forms such as two " S " type runners of " S " type of single seat structural type, two-seat structure and " N " types, in the present invention, " Z " type medium runner is more succinct, runner is less for the impact of medium, and damping constant is little, energy-conservation, and it is perfect that rating curve more is tending towards.
As shown in Figure 3,2. valve body has increased influent stream side piston apparatus in 1. and has gone out to flow the side piston apparatus 4., piston apparatus by this group balanced, symmetrical setting, make the medium active force offset, reduce spool and 3. move required stressedly, namely reduce required final controlling element ouput force and increase high pressure valve to can bear pressure reduction after and before the valve.Shown in its theory is calculated as follows:
When following size has following the relation: f 〉=c 〉=a,
Because of medium effect, valve rod 5. the lower end bear one upwards more than or equal to zero stressed:
F1=P1×[π(c/2)
2-π(b/2)
2]-?P1×[π(a/2)
2-π(b/2)
2]
=P1×π(c
2-a
2)/4
Because of medium effect, valve rod 5. the upper end bear one upwards more than or equal to zero stressed:
F2=P2×[π(f/2)
2-π(b/2)
2]-?P1×[π(c/2)
2-π(b/2)
2]
=?P2×π(f
2-c
2)/4
To sum up institute is above-mentioned, and 5. valve rod bears one and make progress and stressedly be:
F?=F1+F2=?P1×π(c
2-a
2)/4+?P2×π(f
2-c
2)/4
When size f levels off to c, c levels off to a, so stressed F is upwards and very little, required final controlling element ouput force is very little, energy-conservation, after and before the valve pressure reduction of high pressure valve (| P1-P2|) can increase, this moment, high pressure valve was always driven valve for stream.
In like manner, when f≤c≤a, when size a levels off to c, c levels off to f, so stressed F is downward and very little, required final controlling element ouput force is very little, energy-conservation, after and before the valve pressure reduction of high pressure valve (| P1-P2|) can increase, this moment, high pressure valve always closed valve for stream.
In contrast to the valve of single seat structural type as shown in Figure 1, when the medium low in and high out is P1〉during P2,5. valve rod is subjected to a power that makes progress:
F=P1×π(a/2)
2-?P2×π[(a/2)
2-(b/2)
2]
=(P1-P2)×π(a/2)
2+P2×π(b/2)
2
When the little P2 of being of pressure reduction levels off to P1, formula P2 * π (b/2)
2Be subjected to upward force large;
When pressure reduction is greatly that P2 levels off to 0 the time, formula (P1-P2) * π (a/2)
2Be subjected to upward force large;
So no matter pressure reduction is large and little for the valve of single seat structural type, along with valve pressure increases, 5. 3. its spool receive that with valve rod power upwards is very large, and the ouput force of required final controlling element is just larger, and vice versa, very easily causes spool 3. to vibrate.And its " S " type runner is complicated, affects the medium circulation.
In contrast to the valve of two-seat structure form as shown in Figure 2, though can be applicable to the High Pressure Difference situation, its valve inner structure is complicated, requires machining accuracy high, and assembling is regulated and is difficult for, and medium runner is complicated.Because of two-seater sealing cause, not high compared to its sealing grade of single seat structure, easily leak.
In sum, power-saving balanced high pressure single-seat valve of the present invention is due to following innovative point: valve body be processed with in 1. " Z " type medium runner and with 3. coaxial piston guide stroke hole of spool, 3. 5. valve rod is gone up at spool respectively has a piston slider in both sides.1. internal structure is simple thereby make valve body, processing, easy to assembly, with low cost.In addition, design concept of the present invention and structure go in the mesolow valve equally.
Claims (3)
1. a power-saving balanced high pressure single-seat valve, comprise valve body, valve gap, valve rod, spool and valve seat, and described valve rod passes valve gap, stretches into valve inner, and described spool is arranged in the middle part of valve rod, and the valve seat that matches with spool is arranged on described valve interior wall; It is characterized in that: in described valve body, spool both sides are provided with the piston apparatus of 2 groups of balanced, symmetrical, the piston cylinder of 2 groups of piston apparatus be on valve interior surface along valve rod direction of action machining piston guiding stroke hole, corresponding piston is arranged on valve rod.
2. power-saving balanced high pressure single-seat valve according to claim 1, it is characterized in that: when described valve closing, the piston of 2 groups of piston apparatus all is positioned at the bottom in piston guide stroke hole.
3. power-saving balanced high pressure single-seat valve according to claim 1, it is characterized in that: the medium runner of described valve internal is " Z " type.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013100409767A CN103115189A (en) | 2013-02-04 | 2013-02-04 | Energy-saving balanced high-pressure single seated valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013100409767A CN103115189A (en) | 2013-02-04 | 2013-02-04 | Energy-saving balanced high-pressure single seated valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103115189A true CN103115189A (en) | 2013-05-22 |
Family
ID=48413604
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013100409767A Pending CN103115189A (en) | 2013-02-04 | 2013-02-04 | Energy-saving balanced high-pressure single seated valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103115189A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103470779A (en) * | 2013-09-17 | 2013-12-25 | 成都华气厚普机电设备股份有限公司 | LNG (liquefied natural gas) large-caliber high-pressure balanced shut-off valve |
| CN105179708A (en) * | 2015-10-14 | 2015-12-23 | 四川华林自控科技有限公司 | Energy-saving balance high-pressure valve and design method |
| CN108150662A (en) * | 2018-02-05 | 2018-06-12 | 潍坊力创电子科技有限公司 | Double valve gas spray valve |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4516599A (en) * | 1981-02-27 | 1985-05-14 | Tokyo Shibaura Denki Kabushiki Kaisha | Valve mechanism for low temperature applications |
| CN101341358A (en) * | 2005-12-22 | 2009-01-07 | 芙罗服务管理公司 | Pressure balancing valve |
| CN201284879Y (en) * | 2008-10-23 | 2009-08-05 | 南通市电站阀门有限公司 | Supercritical self-tightening seal hammered steel break valve with opening degree indication |
| CN203162304U (en) * | 2013-02-04 | 2013-08-28 | 四川华林自控科技有限公司 | Energy-saving balanced high-pressure single-seated valve |
-
2013
- 2013-02-04 CN CN2013100409767A patent/CN103115189A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4516599A (en) * | 1981-02-27 | 1985-05-14 | Tokyo Shibaura Denki Kabushiki Kaisha | Valve mechanism for low temperature applications |
| CN101341358A (en) * | 2005-12-22 | 2009-01-07 | 芙罗服务管理公司 | Pressure balancing valve |
| CN201284879Y (en) * | 2008-10-23 | 2009-08-05 | 南通市电站阀门有限公司 | Supercritical self-tightening seal hammered steel break valve with opening degree indication |
| CN203162304U (en) * | 2013-02-04 | 2013-08-28 | 四川华林自控科技有限公司 | Energy-saving balanced high-pressure single-seated valve |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103470779A (en) * | 2013-09-17 | 2013-12-25 | 成都华气厚普机电设备股份有限公司 | LNG (liquefied natural gas) large-caliber high-pressure balanced shut-off valve |
| CN103470779B (en) * | 2013-09-17 | 2017-01-18 | 成都华气厚普机电设备股份有限公司 | LNG (liquefied natural gas) large-caliber high-pressure balanced shut-off valve |
| CN105179708A (en) * | 2015-10-14 | 2015-12-23 | 四川华林自控科技有限公司 | Energy-saving balance high-pressure valve and design method |
| CN108150662A (en) * | 2018-02-05 | 2018-06-12 | 潍坊力创电子科技有限公司 | Double valve gas spray valve |
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Application publication date: 20130522 |