CN212564409U - Throttling device for flow-regulating pressure-regulating valve - Google Patents
Throttling device for flow-regulating pressure-regulating valve Download PDFInfo
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- CN212564409U CN212564409U CN202021350278.9U CN202021350278U CN212564409U CN 212564409 U CN212564409 U CN 212564409U CN 202021350278 U CN202021350278 U CN 202021350278U CN 212564409 U CN212564409 U CN 212564409U
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Abstract
The utility model discloses a throttling arrangement for transferring a class air-vent valve, including the throttle sleeve that the center link up, the telescopic last fixed surface of throttle has the ring flange, and the several locating hole has been seted up to the ring flange, and the side region that the throttle sleeve is close to the upper surface has seted up several aperture orifice, and the side region that the throttle sleeve is close to the lower surface has seted up several aperture orifice. The device has the linear regulation characteristic, and can realize continuous, stable and accurate regulation in the required flow variation range; the operation is stable in the range of 10-100% opening degree under the maximum or minimum pressure difference, and the cavitation destruction does not occur. Under the operation demands of high pressure difference small flow, low pressure difference large flow, ultra-wide adjusting amplitude and the like, the flow and pressure adjusting effect of the valve can be realized, and meanwhile, cavitation is avoided, and vibration and noise of the valve are reduced. The reinforcing rib can ensure that the whole or part of the sleeve does not deform, and has a certain flow guiding function, so that water flow is sprayed to the central part of the throttling sleeve along the lateral direction of the rib.
Description
Technical Field
The utility model belongs to the technical field of the valve, a throttling arrangement for transferring a class air-vent valve is related to.
Background
The flow regulating and pressure regulating valve is widely used in pipelines requiring pressure reduction or pressure stabilization, water plant water intake ponds and reservoir flood discharge and air release. The flow regulating and pressure regulating valve is generally piston type, the conventional piston valve can realize flow regulation but not pressure reduction, and the flow regulating and pressure regulating valve is developed after a set of throttling energy dissipation sleeve is additionally arranged at the tail end of the piston valve. An axial annular flow passage is formed inside the valve body, a passage with gradually reduced area and gradually increased flow speed is formed from the inlet to the outlet, an energy dissipation groove hole or a circular hole is formed in a sleeve at the tail end of the piston, energy is reduced by mutual collision in the center of the valve body by utilizing the principle of water flow symmetrical collision energy dissipation, the stroke of the piston is adjusted, the outflow area is adjusted, the flow is adjusted, and the effects of pressure reduction and flow adjustment are achieved.
In recent years, with the massive construction of long-distance water transmission pipeline projects, the large-caliber flow regulating and pressure regulating valves are applied more and more, the pipeline projects generally have the conditions of long distance, large flow, large differential pressure between the front and the back of the valve and the like, and simultaneously face the complicated working condition in the operation process, so that high requirements are provided for the design of the flow regulating and pressure regulating valves. The throttling sleeve is used as a key component of the flow regulating and pressure regulating valve, continuous, stable and accurate regulation needs to be realized in a flow change range, and the opening type, the size, the number, the arrangement mode and the like of the throttling sleeve directly determine the flow and pressure regulating capacity of the valve, so that the throttling sleeve also has an important influence on the cavitation characteristic of the valve. In addition, because the valve operating conditions of each engineering are different, the outlet throttling sleeve is designed according to specific hydraulic conditions, most of common open pore types in the existing design are single slotted holes or round holes, the requirements of flow, pressure and cavitation are difficult to be simultaneously met for a large-caliber flow regulating and pressure regulating valve, particularly for some engineering, the valve needs to meet special conditions of high pressure difference small flow, low pressure difference large flow, ultra-wide regulating amplitude and the like, and the existing design mode can not meet the requirements of pressure regulation, energy dissipation and cavitation.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a throttling arrangement for transferring a class air-vent valve has solved current accent and has flowed the air-vent valve and can not satisfy the technical problem who transfers class, pressure regulating, energy dissipation and have cavitation.
The utility model discloses the technical scheme that adopts is a throttling arrangement for shunting the air-vent valve, the throttling sleeve who link up including the center, throttling sleeve's last fixed surface has the ring flange, the several locating hole has been seted up to the ring flange, the side region that throttling sleeve is close to the upper surface has seted up several aperture orifice, the side region that throttling sleeve is close to the lower surface has seted up several large aperture orifice, aperture orifice and large aperture orifice cover the telescopic side of throttling completely, aperture orifice diameter is 1/140 ~ 1/80 of shunting air-vent valve nominal diameter, large aperture orifice diameter is 1/60 ~ 1/35 of shunting air-vent valve nominal diameter.
The utility model discloses a characteristics still lie in:
the large-aperture throttling holes are evenly arranged at intervals along the axial direction and the circumferential direction of the throttling sleeve, and the small-aperture throttling holes are staggered along the axial direction and the circumferential direction of the throttling sleeve according to a quincunx shape.
The side of the throttle sleeve is axially divided into a plurality of throttle bore regions, in which small-bore throttle bores and large-bore throttle bores are distributed.
The throttle hole areas are regularly arranged.
And reinforcing ribs are arranged between two adjacent circles of throttle holes on the inner surface of the throttle sleeve.
The reinforcing rib is provided in plurality.
The reinforcing rib is arranged along the circumferential direction of the inner wall of the throttling sleeve.
The width of each reinforcing rib is not more than the width between two adjacent circles of orifices, and the height of each reinforcing rib is 1/4-1 of the diameter of the orifice with the small aperture or the diameter of the orifice with the large aperture in the vicinity of the reinforcing rib.
The small-aperture throttling hole area is provided with reinforcing ribs every two circles of small-aperture throttling holes, and the large-aperture throttling hole area is provided with reinforcing ribs every one circle of large-aperture throttling holes.
The positioning holes are uniformly arranged.
The utility model discloses effective effect below having:
(1) the throttling hole is arranged, has a linear adjusting characteristic and can realize continuous, stable and accurate adjustment in a required flow variation range; the operation is stable in the range of 10-100% opening degree under the maximum or minimum pressure difference, and the cavitation destruction does not occur.
(2) Under the operation requirements of high pressure difference small flow, low pressure difference large flow, ultra-wide adjusting range and the like, the flow and pressure adjusting effect of the large-diameter valve can be realized, and meanwhile, cavitation is avoided, and vibration and noise of the valve are reduced.
(3) The reinforcing rib can ensure that the whole or part of the large-diameter throttling sleeve does not deform under the condition that a large number of throttling holes and high water pressure are formed in the surface of the large-diameter throttling sleeve, and meanwhile, the reinforcing rib has a certain flow guide effect, so that water flow is sprayed to the central part of the throttling sleeve along the lateral direction of the rib.
Drawings
Fig. 1 is a schematic structural diagram of a throttling device for a flow-regulating pressure-regulating valve according to the present invention;
fig. 2 is an operation schematic diagram of a throttling device for a flow-regulating pressure-regulating valve according to the present invention.
In the figure, 1, a throttling sleeve, 2, a flange, 3, a positioning hole, 4, a small-aperture throttling hole, 5, a large-aperture throttling hole, 6, a throttling hole area, 7, a reinforcing rib, 8, a piston and 9, a connecting rod mechanism.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings and specific embodiments.
As shown in fig. 1, the throttling device for a flow-regulating pressure-regulating valve of the present invention comprises a throttling sleeve 1 with a through center, wherein a flange 2 is fixed on the upper surface of the throttling sleeve 1, the flange 2 is provided with a plurality of positioning holes 3, and the positioning holes 3 are uniformly arranged; the side surface area of the throttling sleeve 1 close to the upper surface is provided with a plurality of small-aperture throttling holes 4, the side surface area of the throttling sleeve 1 close to the lower surface is provided with a plurality of large-aperture throttling holes 5, and the small-aperture throttling holes 4 and the large-aperture throttling holes 5 completely cover the side surface of the throttling sleeve 1; the diameter of the small-aperture throttling hole 4 is 1/140-1/80 of the nominal diameter of the flow regulating pressure regulating valve, and the diameter of the large-aperture throttling hole 5 is 1/60-1/35 of the nominal diameter of the flow regulating pressure regulating valve; the large-aperture throttling holes 5 are uniformly arranged at intervals along the axial direction and the circumferential direction of the throttling sleeve 1, and the small-aperture throttling holes 4 are staggered along the axial direction and the circumferential direction of the throttling sleeve 1 according to a quincunx shape; the side surface of the throttling sleeve 1 is axially divided into a plurality of throttling hole areas 6, and a small-aperture throttling hole 4 and a large-aperture throttling hole 5 are distributed in the throttling hole areas; the orifice regions 6 are regularly arranged; be provided with a plurality of stiffening ribs 7 between the two adjacent circles of orifices of throttle sleeve 1 internal surface, stiffening rib 7 sets up along 1 inner wall circumference of throttle sleeve, the stiffening rib 7 width is not more than the width between two adjacent circles of orifices, the stiffening rib 7 height is 1/4 ~ 1 of the small aperture orifice 4 diameter or the large aperture orifice 5 diameter of its near, the small aperture orifice 4 region sets up stiffening rib 7 every two circles of small aperture orifices, the large aperture orifice 5 region sets up stiffening rib 7 every round large aperture orifices.
As shown in figure 2, the flange 2 of the device is connected with the tail end of a piston 8 in the valve, a positioning hole 3 in the flange 2 penetrates through a nut and then is fixed, and a crank connecting rod mechanism 9 in the valve drives the piston 8 to move along the center of the valve in the valve body during operation, so that the valve is opened and closed.
When the valve works, water flow enters the cavity of the piston valve along an arc shape, the flow channel in the valve is in an axisymmetric annular shape, and the flow channel contracts in a streamline shape towards the axis at the outlet, so that a medium cannot generate turbulent flow when flowing through the valve, and noise and vibration are effectively overcome. The throttling sleeve of the device is provided with an energy dissipation round hole, water flow is sprayed out from the throttling hole to form high-speed jet spraying to play a role in reducing pressure and dissipating energy, and meanwhile, the linear shrinkage of the outlet part of the valve and the guide collision and resistance generated by the outlet throttling sleeve achieve an energy dissipation and pressure reduction effect and avoid cavitation influence on the valve body or the pipeline due to throttling. No matter the piston 8 is driven to any position, the water flow section in the valve cavity is annular, so that the opening degree of the valve is in linear relation with the flow, and the valve has good flow or pressure regulation characteristics. The valve opening is adjusted to realize flow regulation. The valve driving device drives the piston 8 to do axial movement in the valve cavity through the crank connecting rod mechanism 9, so that the flow area of the valve body outlet is changed, and the flow and the pressure are adjusted.
The device is provided with the reinforcing rib 7, so that the rigidity of the throttling sleeve 1 of the large-caliber flow-regulating pressure-regulating valve can be ensured, and a certain flow guide effect is achieved, so that water flow is sprayed to the central part of the throttling sleeve 1 along the lateral direction of the rib.
The aperture size is preliminarily determined according to the flow and the pressure difference before and after the valve, the flow Q in unit time under ideal conditions can be known according to a flow formula in a pressure pipeline0Comprises the following steps:
where v is the flow velocity of the fluid, A is the area of the orifice, μmThe flow coefficient of the liquid is usually 0.82, g is the acceleration of gravity, and Δ p is the differential pressure before and after the valve.
Thus, the differential pressure Δ p across the valve and the flow rate Q have been determined0In the formula, only the area A of the orifice is an unknown number; assuming that the aperture is the same, one circle of holes is arranged at every 10% opening degree, namely 10 circles of holes are arranged on the whole throttling, and meanwhile, the number of the holes in each circle is 64, and the approximate size of the opening can be obtained according to the area formula of the circle.
Example 1:
the throttling device of the embodiment is applied to a DN2000 model flow regulating and pressure regulating valve, the nominal diameter of the throttling device is 2000mm, so that the diameter of the small-bore throttling hole 4 is 1/80 which is 25mm of the nominal diameter of the flow regulating and pressure regulating valve; the diameter of the large-aperture throttling hole 5 is 1/40 mm, namely 50mm, of the nominal diameter of the flow regulating and pressure regulating valve; this example divides 8 orifice regions 6, the orifice regions 6 being arranged uniformly along the surface of the device.
When the valve is below 30% opening degree, 6 circles of small-bore throttling holes 4 are arranged along the periphery 1 of the throttling sleeve in a staggered mode, and the number of the holes is 384 in total, 64 holes per circle; when the opening degree of the valve is more than 30%, the large-diameter orifices 5 are arranged at every 10% of the opening degree, 7 circles of the large-diameter orifices 5 are uniformly arranged along the circumferential direction of the throttling sleeve 1, and the total number of the orifices is 448 every 64 circles.
In the area of the small-aperture throttling hole 4, reinforcing ribs 7 are arranged every two circles, the height of each reinforcing rib 7 in the area is 3/4 mm of the diameter of the throttling hole, namely 18.75mm, and the width of each reinforcing rib is 8 mm; in the area of the large-aperture orifice 5, reinforcing ribs 7 are arranged at intervals, and the height of the reinforcing ribs 7 in the area is 1/4 of the diameter of the orifice, namely the height of the reinforcing ribs is 12mm, and the width of the reinforcing ribs is 10 mm.
Example 2:
the throttling device of the embodiment is applied to a DN2000 model flow regulating and pressure regulating valve, the nominal diameter of the throttling device is 2000mm, so that the diameter of the small-bore throttling hole 4 is 1/140, namely 14mm, of the nominal diameter of the flow regulating and pressure regulating valve; the diameter of the large-aperture throttling hole 5 is 1/35 mm, namely 57mm, of the nominal diameter of the flow regulating and pressure regulating valve; this example divides 8 orifice regions 6, the orifice regions 6 being arranged uniformly along the surface of the device.
When the opening degree of the valve is below 30%, 10 circles of small-aperture throttling holes 4 are arranged along the circumferential direction of the throttling sleeve 1 in a staggered mode, and 128 holes are formed in each circle, wherein the number of the holes is 1280 in total; when the opening degree of the valve is more than 30%, the large-diameter orifices 5 are arranged at every 10% of the opening degree, 7 circles of the large-diameter orifices 5 are uniformly arranged along the circumferential direction of the throttling sleeve 4, and the total number of the orifices is 448 every 64 circles.
For the area of the small-aperture throttling hole 4, reinforcing ribs 7 are arranged every two circles, the height of each reinforcing rib 7 in the area is the diameter of the throttling hole, namely 14mm, and the width is 4 mm; in the area of the large-aperture orifice 5, reinforcing ribs 7 are arranged at intervals, and the height of the reinforcing ribs 7 in the area is 1/2 of the diameter of the orifice, namely the height of the reinforcing ribs is 28.5mm, and the width of the reinforcing ribs is 8 mm.
Example 3:
the throttling device of the embodiment is applied to a DN2000 model flow regulating and pressure regulating valve, the nominal diameter of the throttling device is 2000mm, so that the diameter of the small-bore throttling hole 4 is 1/110 which is 18mm of the nominal diameter of the flow regulating and pressure regulating valve; the diameter of the large-aperture throttling hole 5 is 1/48 mm, namely 42mm, of the nominal diameter of the flow regulating and pressure regulating valve; this example divides 8 orifice regions 6, the orifice regions 6 being arranged uniformly along the surface of the device.
When the opening degree of the valve is less than 30%, 9 circles of small-aperture throttling holes 4 are arranged along the circumferential direction of the throttling sleeve 1 in a staggered mode, 64 holes are formed in each circle, and the number of the holes is 576 in total; when the opening degree of the valve is more than 30%, the large-diameter orifices 5 are arranged at every 10% of the opening degree, 7 circles of the large-diameter orifices 5 are uniformly arranged along the circumferential direction of the throttling sleeve 4, and the total number of the orifices is 448 every 64 circles.
In the area of the small-aperture throttling hole 4, reinforcing ribs 7 are arranged every two circles, the height of each reinforcing rib 7 in the area is 1/2 mm of the diameter of the throttling hole, namely 9mm, and the width of each reinforcing rib is 5 mm; in the area of the large-aperture orifice 5, reinforcing ribs 7 are arranged at intervals, and the height of the reinforcing ribs 7 in the area is the same as the diameter of the orifice, namely the height of the reinforcing ribs 7 is 42mm, and the width of the reinforcing ribs is 12 mm.
In order to verify the performance effect of the device and simultaneously verify the comparison effect of the size of the hole diameter with the throttling device, the following experimental scheme is designed aiming at the above embodiment. The method comprises the following specific steps:
the design requirements of the DN2000 model flow regulating and pressure regulating valve are as follows: when the differential pressure before and after the valve delta p is 61 m-96 m, the flow rate Q0Q is in the range of 2-Q0≤6m3S; when the pressure difference delta p between the front and the back of the valve is 16 m-61 m, the flow rate Q0Q is in the range of 2-Q0≤15.5m3(s) flow rate Q when differential pressure before and after valve Δ p is 11-16 m0Q is in the range of 2-Q0≤14m3/s。
The following three schemes are designed:
1. scheme one (scheme of the patent): when the opening degree of the valve is below 30%, 6 circles of small-aperture throttling holes 4 with the diameter of 25mm are arranged along the circumferential direction of the throttling sleeve 1 in a staggered mode, and the number of the holes is 384 in total for 64 holes in each circle; in the range of 30% opening or more, large-aperture orifices 5 with a diameter of 50mm are provided every 10% opening, 7 circles of large-aperture orifices 5 are uniformly arranged along the circumferential direction of the throttle sleeve 1, and the number of the holes is 448 in total for 64 circles.
2. Scheme two (the opening diameter is the small-aperture orifice diameter in scheme one): when the opening degree of the valve is below 30%, 6 circles of small-aperture throttling holes 4 with the diameter of 25mm are arranged along the circumferential direction of the throttling sleeve 1 in a staggered mode, and the number of the holes is 384 in total for 64 holes in each circle; in the range of more than 30% opening degree, 2 rows of small-bore throttling holes 4 with the diameter of 25mm are arranged at every 5% opening degree, 14 circles are uniformly arranged along the circumferential direction of the throttling sleeve 1, 128 holes are arranged in each circle, and the number of the holes is 1792 in total.
3. Scheme three (the diameter of the opening is the diameter of the large-aperture orifice in scheme one): when the opening degree of the valve is less than 30%, 3 circles of large-aperture orifices 5 with the diameter of 50mm are arranged along the circumferential direction of the throttling sleeve 1 in a staggered mode, and the total number of the orifices is 192 for each circle of 64 orifices; in the range of 30% opening or more, large-aperture orifices 5 with a diameter of 50mm are provided every 10% opening, 7 circles of large-aperture orifices 5 are uniformly arranged along the circumferential direction of the throttle sleeve 1, and the number of the holes is 448 in total for 64 circles.
The CFD software is adopted to carry out numerical simulation on the two opening schemes respectively, the flow field and the cavitation condition of the opening schemes are known, the working conditions when the water head difference between the front and the rear of the valve is 96m, 61m, 16m and 11m are calculated respectively, and the results are as follows:
in the three schemes, the results are completely consistent under the opening degree of 30%, no cavitation occurs, and the working condition of the opening degree of more than 30% can be calculated. Further, the calculation results show different opening degrees at which cavitation occurs at a water head difference of 61m before and after the valve, and the calculation results at 60% opening degree are shown in table 1:
TABLE 1 comparison of the results of the experiments
| Scheme(s) | Flow rate (m)3/s) | Lowest pressure (kPa) | Whether or not to cavitate |
| Scheme one | 15.8 | 75 | Whether or not |
| Scheme two | 19.4 | 214 | Is that |
| Scheme three | 25.2 | 180 | Is that |
As can be seen from Table 1, the design maximum flow rate of 15.5m is close to 61m in the first scheme3S, while no cavitation occurred; scheme two flow rate is far larger than maximum flow rate 15.5m when the flow rate is 61m3The gas etching occurs at the same time, and the design requirement is not met; from the lowest pressure, the lowest pressure in the first scheme is also smaller than that in the second scheme, which shows that the scheme has better energy dissipation and pressure reduction effects. Scheme three flow is far larger than maximum flow of 15.5m when the flow is 61m3And/s, cavitation occurs at the same time, and the design requirements are not met.
The size and the number of the throttling holes of the device are approximately given according to the pressure difference and the flow before and after the valve works, and are further optimized and determined through numerical simulation. The range of pore diameters given meets the flow requirements without cavitation. The throttling hole arrangement has a linear regulation characteristic, and can realize continuous, stable and accurate regulation in a required flow variation range; the operation is stable in the range of 10-100% opening degree under the maximum or minimum pressure difference, and the cavitation destruction does not occur. Under the operation demands of high pressure difference small flow, low pressure difference large flow, ultra-wide adjusting amplitude and the like, the flow and pressure adjusting effect of the valve can be realized, and meanwhile, cavitation is avoided, and vibration and noise of the valve are reduced.
Claims (9)
1. The utility model provides a throttling arrangement for transferring flow air-vent valve, its characterized in that, including the throttle sleeve (1) that the center link up, the last fixed surface of throttle sleeve (1) has ring flange (2), several locating hole (3) have been seted up in ring flange (2), several aperture throttle (4) are seted up near the side region of upper surface in throttle sleeve (1), several aperture throttle (5) have been seted up near the side region of lower surface in throttle sleeve (1), aperture throttle (4) and aperture throttle (5) cover the telescopic side of throttle completely, aperture throttle (4) diameter is 1/140 ~ 1/80 of transferring flow air-vent valve nominal diameter, aperture throttle (5) diameter is 1/60 ~ 1/35 of transferring flow air-vent valve nominal diameter.
2. The throttling device for the pressure regulating valve with flow regulation according to claim 1, wherein the large-aperture throttling holes (5) are uniformly spaced along the axial direction and the circumferential direction of the throttling sleeve (1), and the small-aperture throttling holes (4) are staggered along the axial direction and the circumferential direction of the throttling sleeve (1) in a quincunx manner.
3. The throttling device for a pressure regulating valve according to claim 1 or 2, wherein the side of the throttling sleeve (1) is axially divided into a plurality of throttling hole areas (6), and the small-diameter throttling hole (4) and the large-diameter throttling hole (5) are distributed in the throttling hole areas (6).
4. A throttling device for a flow-regulating pressure-regulating valve according to claim 3, characterized in that said throttling hole regions (6) are regularly arranged.
5. A throttling device for a pressure regulating valve according to claim 2, characterized in that a reinforcing rib (7) is arranged between two adjacent circles of orifices on the inner surface of the throttling sleeve (1).
6. A throttling device for a flow-regulating pressure-regulating valve according to claim 5, characterized in that said reinforcing rib (7) is provided in plurality.
7. A throttling device for a flow-regulating pressure-regulating valve according to claim 6, wherein said reinforcing ribs (7) are circumferentially arranged along the inner wall of the throttling sleeve (1).
8. The throttling device for the pressure regulating valve with the flow regulation according to claim 5 is characterized in that the width of the reinforcing rib (7) is not more than the width between two adjacent circles of orifices, and the height of the reinforcing rib (7) is 1/4-1 of the diameter of the small-aperture throttling hole (4) or the diameter of the large-aperture throttling hole (5) adjacent to the reinforcing rib.
9. A restriction device for a pressure regulating valve according to claim 5, characterized in that the area of the small orifice (4) is provided with reinforcement ribs (7) every second turn of the small orifice, and the area of the large orifice (5) is provided with reinforcement ribs (7) every third turn of the large orifice.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021350278.9U CN212564409U (en) | 2020-07-10 | 2020-07-10 | Throttling device for flow-regulating pressure-regulating valve |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202021350278.9U CN212564409U (en) | 2020-07-10 | 2020-07-10 | Throttling device for flow-regulating pressure-regulating valve |
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| CN212564409U true CN212564409U (en) | 2021-02-19 |
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| CN202021350278.9U Active CN212564409U (en) | 2020-07-10 | 2020-07-10 | Throttling device for flow-regulating pressure-regulating valve |
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