CN105202233A - High-performance reducing valve with valve closing function - Google Patents

Abstract

The invention discloses a high-performance reducing valve with the valve closing function. The high-performance reducing valve is provided with a valve body, a valve rod, an alarm device and a diaphragm. The high-performance reducing valve is characterized in that two valve ports including the upper valve port and the lower valve port are arranged, a center hole is formed in the center of a transverse partition wall of the valve body, a valve seat sleeve is arranged in the center hole, an O-shaped sealing ring in a groove in the upper end face of the valve seat sleeve is matched with a pressing plate arranged at the corresponding portion of the valve rod, and then the upper valve port is formed; the lower end face of the valve seat sleeve is matched with grooves in the outer cylinder of a piston arranged on the valve rod and matched with the valve seat sleeve in a sliding mode, and then the lower valve port is formed. The piston is cylindrical, the external diameter of the piston is matched with an inner hole of the valve seat sleeve in a sliding mode, the two to four symmetric grooves with the same shape are formed in the outer cylinder of the piston, and a certain distance is formed between the groove tops of the grooves and the bottom face of the cylinder. Due to the change of the types of the valve ports, the hydraulic radius of the high-performance reducing valve is greatly increased compared with that of a common diaphragm type reducing valve, flow capacity is greatly improved, the minimal steady flow rate is low, noise is greatly lowered, and the service life of the valve is prolonged.

Description

There is the high-performance reduction valve of valve closing function

Technical field

The present invention relates to a kind of valve, particularly relate to a kind of high-performance reduction valve with valve closing function.

Background technique

In the water system of high building, widely use reduction valve to regulate the pressure of supply water of each floor, when fluctuation occurs for pressure of supply water or the flow that flows through reduction valve, reduction valve can utilize self structure to realize automatically regulating, and keeps delivery pressure constant.But the plain edition diaphragm type pressure-reducing valve supplied in the market has following two deficiencies:

1, diaphragm is more fragile, when damages user unknown, once damage, high pressure water will flow to downstream, cause damage to upstream device or pipeline.

2, valve port is plane (as shown in Figure 6), and this valve port belongs to fast open form, and when valve seat and flap distance slightly change, namely flow larger change can occur.In water supply process, because flap is according to the change of operating mode, moving up and down every now and then, therefore the fierceness of hydraulic power changes the vibration that will cause the part such as valve rod and flap.

Another shortcoming of this valve port (is such as greater than 3) when Pressure reducing ratio is larger, because the aperture Δ of valve port is very little, therefore MEDIA FLOW is high through valve port hourly velocity, this not only produces noise, and sealing gasket and valve seat are washed away strongly, even cause cavitation to cavitate, significantly shorten the reduction valve life-span.Therefore, propose in China's " building water supply reduction valve application technology code ", when Pressure reducing ratio is greater than 3, the method of two reduction valve series connection should be adopted to be reduced in the pressure drop on every reduction valve, with reduce MEDIA FLOW through valve port time flow velocity, this is all helpless and irrational selection from economy, installation and maintenance equal angles.

In addition, the hydraulic radius of this valve port is very little, causes the flow that passes through when same flow resistance to reduce, causes the negotiability of valve to reduce, and noise is large, pressure adjusting function is poor and small flow time discharge stability poor.

Summary of the invention

The present invention is mainly in order to solve the above-mentioned deficiency of plain edition diaphragm type pressure-reducing valve, thus exploitation one can improve negotiability, reduces noise, the high-performance reduction valve with valve closing function increased the service life.

Above-mentioned technical problem of the present invention is mainly solved by following technical proposals: a kind of high-performance reduction valve with valve closing function, there is valve body, valve rod, described valve body has upper and lower through hole, the snout cavity of valve body and outlet plenum horizontal arrangement, bonnet is had above valve body, bonnet flange edge is equipped with warning device, spring two and spring chamber is had in bonnet, bottom flange is had below valve body, bottom flange central authorities are provided with boss, be provided with diaphragm between valve body and bonnet, described diaphragm and valve rod upper end portion are connected, and it is characterized in that:

Have center hole in the central authorities of valve body across bulkhead, be provided with valve seat cover in described center hole, described valve seat puts end face and coordinates with the pressing plate being arranged at valve rod corresponding site, valve port in formation; The lower end surface of valve seat cover with to be arranged on valve rod, overlap the groove fit on sliding outside piston post of joining with valve seat, formation lower valve port;

The lower end surface of described valve seat cover forms seal arrangement with the sealing gasket be positioned at below piston; When stopping supplying water, prevent medium from leaking from A chamber to B chamber.

Described piston is cylindrical, and endoporus that its external diameter and valve seat overlap is sliding joins, and outer cylinder has the symmetrical and groove that shape is identical of 2-4 bar, and described groove groove top has with a certain distance from bottom cylindrical face;

Technological scheme of the present invention can also be perfect further:

As preferably, the upper-end surface of described valve seat cover is provided with the trapezoidal groove of ring-type, and be provided with O-ring seals one in described groove, as the valve seat of upper valve port, described pressing plate is as the flap of upper valve port;

The lower end surface of described valve seat cover is provided with annular sword limit, and as the valve seat of lower valve port, the groove on described outside piston post is as the flap of lower valve port;

Spring one is provided with between the central boss of described bottom flange and the boss of gasket base lower end.

As preferably, described sealing gasket is arranged in the groove above gasket base; Annular sword limit and the sealing gasket of described valve seat cover lower end form seal arrangement.

As preferably, described groove is 2, and shape is close to half inverted cone, and on different sections, the diameter of circular cone is different, big up and small down.

The invention has the beneficial effects as follows:

1, the present invention is owing to changing valve port pattern, and its hydraulic radius significantly increases than the hydraulic radius of plain edition diaphragm type pressure-reducing valve, especially under high Pressure reducing ratio operating mode.Because the size of flow resistance and hydraulic radius are inversely proportional to, therefore under onesize flow section and pressure drop, the present invention allows by larger flow, and namely negotiability significantly improves.

2, the present invention has valve closing function, and when diaphragm damages, energy is close port in time, stops to downstream water supply, and sends alarm signal or switch off the pump, and protection upstream device or pipeline are from damage.

3, the present invention substantially eliminates hydraulic power change and causes valve vibration of bar.

4, the present invention greatly reduces medium by valve port V ₂time washing away valve port part, eliminate cavitation cavitation erosion, improve the working life of valve.

5, the minimum regime flow of the present invention is little;

6, the present invention significantly reduces noise.

Accompanying drawing explanation

Accompanying drawing 1 is a kind of structural representation of the present invention;

Accompanying drawing 2 is warning device structural representations of Fig. 1;

Accompanying drawing 3 is piston structure sectional drawings of Fig. 1;

Accompanying drawing 4 is plan views of Fig. 3;

Accompanying drawing 5 is that the groove of Fig. 1 piston and valve seat overlap the flow section that sword limit, lower end surface forms lower valve port;

Accompanying drawing 6 is plain edition diaphragm type pressure-reducing valve valve port schematic diagram;

Accompanying drawing 7 is lower valve port schematic diagram of the present invention.

Description of reference numerals: 1, diaphragm, 2, valve body, 3, valve rod, 4, O-ring seals one, 5, across bulkhead, 6, valve seat cover, 7, sealing gasket, 8, gasket base, 9, spring one, 10, piston, 11, back-up ring, 12, pressing plate, 13, spring two, 14, plug screw, 15, O-ring seals two, 16, valve pad 17, valve casing, 18, O-ring seals three, 19, balance spring, 20, valve gap, 21, transmit bar;

A, water-inlet cavity, B, water chamber, V1, upper valve port, V ₂, lower valve port, P ₁, incoming pressure, P ₂, delivery pressure, D, warning device, H, spring chamber;

A, Kong Yi, b, hole two, k, air-through holes, m, groove apex are from the distance of piston bottom surface.

Embodiment

Below by embodiment, and by reference to the accompanying drawings, technological scheme of the present invention is described in further detail.

Embodiment:

Be illustrated in figure 1 the high-performance reduction valve with valve closing function, about the structure of reduction valve and principle well-known, be not described here.

1, the present invention has two valve ports, upper valve port V1 and lower valve port V ₂.Be provided with valve seat cover 6 in the central authorities of valve body 2 across bulkhead 5, overlap at valve seat in the groove of 6 upper-end surfaces and be provided with valve port V in O-ring seals 1 conduct ₁valve seat, be provided with the fixing pressing plate 12 of back-up ring 11 in the stage casing of valve rod 3, as upper valve port V ₁flap; The axostylus axostyle of valve rod 3 hypomere is equipped with nutted piston 10 and gasket base 8, in the groove of gasket base 8, is provided with sealing gasket 7; Between the boss above the boss and bottom of the below of gasket base 8, be provided with spring 1, its function is in order to when inlet pressure P1≤0 (such as upstream equipment cut off the water maintenance or the situation such as pipeline breaking), can not make valve port V ₁close, in order to avoid medium cannot enter water chamber B from water-inlet cavity A when again starting.The center line of above-mentioned each part is consistent with the center line of the upper and lower through hole of valve body 2 after mounting.

The structure of piston 10 as shown in Figure 3,4, the endoporus that its external diameter and valve seat overlap 6 sliding is joined, because the two gap is very little, when hydraulic power changes, piston 10 can not vibrate, and its outer cylinder has two symmetrical grooves, the shape of groove is close to half circular cone, on different sections, the diameter of circular cone is different, up big and down small.Because two grooves are symmetrical, so the imbalance of the power that hydraulic power change produces can be eliminated; The flow section (Fig. 5 dash area) that the annular sword limit that two grooves and valve seat overlap 6 lower end surfaces is formed becomes lower valve port V ₂, the size of flow section is by delivery pressure P ₂determine, delivery pressure is large, the partial below, position of piston 10, and flow section is large, and throttling action reduces; Otherwise, position side on the upper side.In order to not reduce flow coefficient and negotiability, the external diameter of piston 10 should be suitably large, there is certain distance m on the summit of groove far from bottom surface, therefore only have when the bottom surface of piston 10 be moved down into the distance of overlapping 6 lower endless sword limits from valve seat be greater than m time, the path of A, B two between chamber is just opened, owing to going out the distance S > m (see Fig. 7) between head piece and sealing gasket 7 when reaching certain flow, therefore high-speed Medium can not cause too large washing away to sealing gasket 7.Annular sword limit below sealing gasket 7 and valve housing 6 is not re-used as flap and the valve seat of valve port, is only used as at valve port V ₂during closedown, prevent the leakage of A, B bis-medium between chamber.

2. valve closing function

The determination of 2.1 valve closing principles and major parameter

In water supply process, the stressed of valve rod 3 is balance all the time on dynamically, therefore can ensure that delivery pressure is substantially constant, when diaphragm damages suddenly ring, the press water of outlet plenum B enters into spring chamber H, and the upper and lower cavity pressure of diaphragm 1 is equal, the stressed disequilibrium of valve rod 3, under the pressure of spring 2 13, the parts such as diaphragm 1, valve rod 3 move downward, till the lower plane of pressing plate 12 contacts with O-ring seals 1, and upper valve port V ₁close.Sealing reliability after upper valve port closedown is calculated as follows:

The top overlapping 6 from valve seat due to medium flows into, below is flowed out, and now reduction valve loses decompression, therefore P2 goes to zero gradually, therefore closing forces

F＝P ₁×π/4(d ₂ ²-d ₁ ²)+f ₁-f ₂(1)

In formula

P ₁-inlet pressure

D ₁the respective diameters of-valve rod 3

D ₂the diameter of bore of-valve seat cover 6

F ₁the down pressure of-spring 13

F ₂-spring 9 to lifting force

When the pressure f of import hydraulic pressure P1 and spring 2 13 ₁time minimum (height subtract Pressure reducing ratio operating mode under), closing forces F is minimum, now because spring is pressed very loose, therefore f ₁very little, can ignore during calculating.Reliable in order to ensure at the most unfavorable processing condition lower seal, must ensure:

P ₁min×π/4(d ₂ ²-d ₁ ²)-f ₂≥F ₁min(2)

In formula

P ₁the minimum import hydraulic pressure of min-

F ₁mim-ensures the reliable minimum closing forces of sealing.

Specify in the design and devdlop code of reduction valve, P ₁min is at least than outlet pressure P ₂high 0.15MPa, outlet pressure P ₂determined by user, for the purpose of sealing reliably, during calculating, get P ₂min=0.1MPa; F ₁min is for ensureing that the endoporus d of valve seat cover 6 is multiplied by the reliable hydraulic pressure of sealing (generally getting 0.05MPa) ₂area; f ₂specific output hydraulic pressure P ₂time maximum, the pressure of spring 2 13 is bigger, and now spring 2 13 is pressed tighter, and this value can calculate, and also can survey and obtain.Therefore can according to P ₁min, F ₁min and f ₂value calculate d by (2) formula ₁and d ₂relation, then determine d according to the bore of valve and concrete structure ₁and d ₂, due to d ₂comparatively large with flow coefficient relation, size is unsuitable too small.

Now be calculated as follows for DN65 reduction valve:

Get minimum outlet hydraulic pressure P ₂min is 0.1MPa=1kg/cm ², so minimum import hydraulic pressure

P ₁min＝0.1+0.15＝0.25MPa＝2.5Kg/cm ²；

Record f ₂=60N=6kg; F ₁min=0.5 × π/4 × d ₂ ²

Each value is substituted into (2) formula obtain:

2.5×π/4(d ₂ ²-d ₁ ²)-6≥0.5×π/4×d ₂ ²

After arrangement $d_1\≤\sqrt{\frac{1.57{d_2}^2-6}{1.96}}$

Get d ₂=4cm, then d ₁≤ 3.1cm

2.2 valve closing warning functions

Warning device D shown in Fig. 2 is open in CN200834348U patent, is only briefly described here.Warning device D screw thread is arranged on the obliquity prominence platform near the bonnet flange edge that is positioned at above diaphragm, and below the inner chamber of valve casing 17, passing hole a and b communicates with spring chamber H.The internal diameter of cylinder of valve casing 17 is joined with the piston transmitting bar 21 stage casing is sliding, the inner chamber of valve casing 17 is divided into epicoele and cavity of resorption, and stops the leakage of medium between two chambeies by O-ring seals 3 18; The valve gap 20 with air-through holes k screws in the upper end endoporus of valve casing 17, and the cylndrical surface of its lower sleeve and the internal diameter of cylinder of valve casing 17 are slided and joined; The long shaft rod transmitting bar 21 slides in the center hole of valve gap 20, and transmit bar 21 after installation freely can move up and down in inner hole of cylinder, and the upper lower end surface by valve gap 20 sleeve transmitting bar 21 movement is placed restrictions on, and bottom is placed restrictions on by its stub shaft lower end surface; Between the pit bottom surface and piston upper-end surface of valve gap 20 and be respectively provided with balance spring 19 between cylinder barrel bottom surface and piston lower surface, there is certain pre compressed magnitude after upper and lower spring fitting, transmit bar 21 and be in equilibrium position under two spring actions.In reduction valve normal work period, the position transmitting bar 21 is regulated automatically by the air density change in spring chamber H.

Once diaphragm 1 damages, at upper valve port V ₁while closing, press water passing hole one a in spring chamber H and hole two b act on transmit bar 21 piston lower end surface on, promotion transmits bar 21 and moves upward, until its upper shaft lever all stretches out, make electric switch action (not shown in FIG.), send alarm signal or water pump is quit work.

3 hydraulic radiuses calculate

Hydraulic radius R formula is as follows:

R＝A/X

In formula:

The flow cross-section of A-medium

X-wetted perimeter length, namely on the flow cross-section of medium, the contact length of liquid and surrounding solid

The hydraulic radius (see Fig. 6) of 3.1 plain edition diaphragm type pressure-reducing valves

$R_1=\frac{A}{X}=\frac{\mathrm{\π}{d}_2\mathrm{\Δ}}{2\mathrm{\π}{d}_2}=\frac{\mathrm{\Δ}}{2}---\left(3\right)$

3.2 under identical flow cross-section, hydraulic radius of the present invention

Flow cross-section of the present invention, calculates with two semicircles approx, if half circular diameter is d

A＝π/4×d ²＝πd ₂Δ

$d=\sqrt{4d_2\mathrm{\Δ}}=2\sqrt{d_2\mathrm{\Δ}}$

$X=\mathrm{\πd}+2d=(\mathrm{\π}+2)d=2(\mathrm{\π}+2)\sqrt{d_2\mathrm{\Δ}}$

$R_2=\frac{A}{X}=\frac{\mathrm{\π}{d}_2\mathrm{\Δ}}{2(\mathrm{\π}+2)\sqrt{d_2\mathrm{\Δ}}}=\frac{\mathrm{\π}}{2(\mathrm{\π}+2)}\sqrt{d_2\mathrm{\Δ}}=0.306\sqrt{d_2\mathrm{\Δ}}---\left(4\right)$

3.3 the present invention compare with plain edition diaphragm type pressure-reducing valve hydraulic radius

$\frac{R_2}{R_1}=\frac{0.306\sqrt{d_2\mathrm{\Δ}}}{\mathrm{\Δ}/2}=0.612\sqrt{\frac{d_2}{\mathrm{\Δ}}}---\left(5\right)$

From (5) formula, the ratio of the two hydraulic radius and piston diameter d ₂radical be directly proportional, the radical of valve port opening Δ when working with plain edition diaphragm type pressure-reducing valve is inversely proportional to.At piston diameter d ₂after determining, Pressure reducing ratio is larger, and Δ value is less, R ₂/ R ₁be worth larger.

3.4 existing citings with DN65 reduction valve are calculated as follows:

Under high Pressure reducing ratio operating mode, the valve port opening Δ < 2mm of plain edition diaphragm type pressure-reducing valve, now calculates with 2mm,

In addition piston diameter is got

d ₂＝Φ40mm

Calculate by (3) formula:

R ₁＝Δ/2＝1mm

Calculate by (4) formula:

$R_2=0.306\sqrt{d_2\mathrm{\&Delta;}}=2.74\mathrm{mm}$

Or calculate by (5) formula:

$R_2=0.612\sqrt{\frac{d_2}{\mathrm{\&Delta;}}}\&times;R_1=2.74\mathrm{mm}$

R ₂/R ₁＝2.74/1＝2.74

As calculated, only have as Δ>=0.375d ₂time, R ₁>=R ₂.For DN65 reduction valve, as Δ >=0.375 × 40=15

During mm, R ₁>=R2, this operating mode generally there will not be in the reduction valve of all size.

Claims (5)

1. one kind has the high-performance reduction valve of valve closing function, there is valve body (2), valve rod (3), on described valve body (2) has, lower through-hole, the snout cavity (A) of valve body (2) and outlet plenum (B) horizontal arrangement, bonnet is had above valve body, bonnet flange edge is equipped with warning device (D), spring two (13) and spring chamber (H) is had in bonnet, bottom flange is had below valve body, bottom flange central authorities are provided with boss, diaphragm (1) is provided with between valve body and bonnet, described diaphragm (1) and valve rod (3) upper end portion are connected, it is characterized in that:

Center hole is had in the central authorities of valve body (2) across bulkhead (5), valve seat cover (6) is provided with in described center hole, described valve seat cover (6) upper-end surface coordinates with the pressing plate (12) being arranged at valve rod (3) corresponding site, valve port (V in formation ₁); The lower end surface of valve seat cover (6) be arranged at valve rod (3) upper, with the groove fit in sliding piston (10) outer cylinder of joining of valve seat cover (6), form lower valve port (V ₂);

Lower end surface and the sealing gasket (7) be positioned at below piston (10) of described valve seat cover (6) form seal arrangement;

Described piston (10) is for cylindrical, and the endoporus of its external diameter and valve seat cover (6) is sliding joins, and outer cylinder has the symmetrical and groove that shape is identical of 2-4 bar, and described groove groove top has with a certain distance from bottom cylindrical face.

2. the high-performance reduction valve with valve closing function according to claim 1, is characterized in that:

The upper-end surface of described valve seat cover (6) is provided with annular groove, is provided with O-ring seals one (4) in described groove, as upper valve port (V ₁) valve seat, described pressing plate (12) is as upper valve port (V ₁) flap;

The lower end surface of described valve seat cover (6) is provided with annular sword limit, as lower valve port (V ₂) valve seat, the groove in described piston (10) outer cylinder is as lower valve port (V ₂) flap;

Spring one (9) is provided with between the boss of the central boss of described bottom flange and gasket base (8) lower end.

3. the high-performance reduction valve with valve closing function according to claim 2, is characterized in that: described sealing gasket (7) is arranged in the groove above gasket base; Annular sword limit and the sealing gasket (7) of described valve seat cover (6) lower end form seal arrangement.

4. the high-performance reduction valve with valve closing function according to claim 1 and 2, is characterized in that:

Described groove is 2, and shape is close to half inverted cone, and on different sections, the diameter of circular cone is different, big up and small down.

5. the high-performance reduction valve with valve closing function according to claim 3, is characterized in that:

Described groove is 2, and shape is close to half inverted cone, and on different sections, the diameter of circular cone is different, big up and small down.