CN110081185B - Air valve in ventilation air-conditioning system - Google Patents
Air valve in ventilation air-conditioning system Download PDFInfo
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- CN110081185B CN110081185B CN201910269124.2A CN201910269124A CN110081185B CN 110081185 B CN110081185 B CN 110081185B CN 201910269124 A CN201910269124 A CN 201910269124A CN 110081185 B CN110081185 B CN 110081185B
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- air valve
- valve
- curved surface
- air
- seal
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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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/16—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members
- F16K1/18—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps
- F16K1/20—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with pivoted closure-members with pivoted discs or flaps with axis of rotation arranged externally of valve member
- F16K1/2042—Special features or arrangements of the sealing
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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
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/32—Details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
Abstract
The invention provides an air valve in a ventilation air-conditioning system, which comprises an air valve main body, a valve plate, a rotating shaft and a first seal, wherein the valve plate is positioned at the upper part of the air valve main body; the air valve further comprises a second seal positioned at the lower part of the air valve main body, when the valve plate rotates to the lower part of the air valve main body around the rotating shaft, the valve plate is in contact with the second seal, and the first seal and the second seal are positioned at the fluid inlet side of the air valve. The result shows that the air valve has obvious drag reduction degree compared with the traditional single-blade valve under different wind speeds (3m/s-12m/s) under the same caliber, and the local drag reduction rate ranges from 81.4% to 87.16%.
Description
Technical Field
The invention belongs to the technical field of resistance reduction of local components of pipelines, relates to resistance evaluation of local components of ventilation air-conditioning pipelines, and particularly relates to an air valve structure in a ventilation air-conditioning system.
Background
With the development of science and technology and economy, people have higher and higher requirements on living standards, so that the ventilation and air-conditioning system becomes an indispensable part of a building, and the energy consumption of the ventilation and air-conditioning system is greatly increased. The energy consumption of the ventilation and air-conditioning system is one of the main energy consumption of the building, which accounts for about 65% of the energy consumption of the building, and the development of building intellectualization still has a trend of increasing, wherein the energy consumption of the fan caused by resistance can account for 30% to 50% of the total energy consumption of the building, and how to reduce the resistance of the ventilation system, so that the final reduction of the energy consumption of the fan is a technical problem to be solved urgently at the present stage.
At present, local components of pipelines such as a tee joint, an elbow and a reducing pipeline are researched more, the attention to the local components such as a valve is less, only the research is focused on the resistance characteristics of an air valve in different opening states, and the research on the resistance reduction problem of the air valve in a fully opening state is basically blank. However, the air valve is a common local resistance component in a ventilation air-conditioning duct system, and is also a large component of local resistance, and the research on the resistance problem is not slow.
Disclosure of Invention
Aiming at the defects and shortcomings in the prior art, the invention aims to provide an air valve structure in a ventilation air-conditioning system, fills the research blank of resistance evaluation of local components of the existing valve, introduces a new visual angle for the field of pipeline drag reduction, and provides a basis for the specification of related manuals and specifications.
In order to achieve the purpose, the invention has the following realization process:
an air valve in a ventilation air-conditioning system comprises an air valve main body, a valve plate, a rotating shaft and a first seal, wherein the valve plate is positioned at the upper part of the air valve main body; the air valve further comprises a second seal positioned at the lower part of the air valve main body, when the valve plate rotates to the lower part of the air valve main body around the rotating shaft, the valve plate is in contact with the second seal, and the first seal and the second seal are positioned at the fluid inlet side of the air valve; the first seal is provided with a first curved surface which is concave to the fluid inlet side of the air valve; the second seal comprises a second curved surface and an inclined surface connected with the second curved surface, and the second curved surface is concave to the lower part of the wind valve main body; the valve plate is a third curved surface which is concave towards the interior of the air valve main body.
Preferably, the functional formula of the first curved surface is:
(x+0.208D)2+(y+0.308D)2＝(1.324D)2
the functional formula of the second curved surface is:
(x-0.181D)2+(y+0.165D)2＝(0.245D)2
the functional formula of the third curved surface is:
(x-2.178D)2+(y+28.826D)2＝(29.842D)2
wherein D is the height of the air valve.
More preferably, the distance from the axis of the rotating shaft to the fluid inlet side of the air valve is 0.2D, the distance from the axis to the fluid outlet side of the air valve is D, the distance from the connecting point of the second curved surface and the inclined surface to the fluid inlet side of the air valve is 0.246D, the distance from the connecting point of the inclined surface and the lower part of the air valve body to the fluid inlet side of the air valve is 0.248D, the perpendicular distance from the connecting point of the second curved surface and the inclined surface to the connecting point of the inclined surface and the lower part of the air valve body is 0.072D, the diameter of the rotating shaft is 0.048D, and D is the height.
The curvature radius of the first curved surface is 1.324D; the curvature radius of the second curved surface is 0.245D; the radius of curvature of the third curved surface is 29.842D, and D is the height of the air valve.
The invention has the beneficial effects that:
1. the invention has proposed a new kind of single-vane blast gates, through studying the valve plate position and valve plate and sealed shape, the result shows, the same bore, the blast gate of the invention is very obvious to the drag reduction degree of the traditional single-vane blast gate under different wind speeds (3m/s to 12m/s), the local drag reduction rate range is 81.4% -87.16%, when the speed is lower, flow in the transition zone of the turbulent flow, the local drag reduction rate increases with the increase of the speed; when the velocity increases to a certain value, the flow is in a completely turbulent region, at which point the local drag reduction will no longer change with increasing velocity.
2. The valve plate and the shaft of the traditional single-vane valve are arranged in the middle of a pipeline, two boundary layers are added, the velocity gradient around the boundary layers is large, so that the energy dissipation of the air valve is large, the shaft and the valve plate are moved to the edge by the novel air valve, the boundary layers and the velocity gradient around the boundary layers are reduced, the turbulent dissipation rate of the novel air valve is obviously reduced, and the drag reduction rate is 60.15%;
3. the valve plate and the seal of the traditional air valve are optimized, the novel air valve reduces the fluid deformation, reduces the strength and the action range of airflow vortex, reduces the inward energy conversion of mechanical energy, obviously reduces the turbulent dissipation rate of the air valve, finally reduces the local resistance coefficient to 0.047, and achieves the resistance reduction rate of 87.11%;
4. along with the change of the wind speed, the experimental numerical value of the air valve has good coincidence with the result of numerical simulation, and the local resistance is obviously reduced compared with other air valves.
Drawings
Fig. 1 shows the structure of the single-vane valve when the air valve of the present invention is opened.
Fig. 2 shows the structure of the single-vane valve when the air valve is closed.
Fig. 3(a) is an angle diagram of three curved surfaces of the present invention, and (b) is a detailed position diagram of the valve plate, the shaft and the seal of the present invention.
Fig. 4 is a schematic flow chart of the blast gate optimization of the invention.
FIG. 5 is a plot of drag reduction using different wind speeds.
Fig. 6 is the turbulent energy dissipation ratio within the damper: (a) a longitudinal section view; (b) cross-sectional view.
FIG. 7 is a graph of the local drag coefficients for different dampers at different wind speeds.
Fig. 8 is a schematic view of several curved surfaces of the present invention.
In the figure: 1 is the blast gate main part, 2 is the valve plate, 3 is the axis of rotation, 4 is first sealed, 5 is the second curved surface, 6 is the inclined plane.
Detailed Description
Example 1:
the embodiment provides a novel structure of a single-vane valve, wherein a valve plate is positioned at the upper part of an air valve main body, a shaft is positioned at one side of the valve plate, an upper seal and a lower seal are positioned at the same side, and when the air valve is closed, the position of the valve plate is greatly different from that of a conventional single-vane valve; in addition, the air valve provided by the invention is characterized in that the first seal is provided with a first curved surface which is concave to the fluid inlet side of the air valve; the second seal comprises a second curved surface and an inclined surface connected with the second curved surface, and the second curved surface is concave to the lower part of the wind valve main body; the valve plate is a third curved surface which is concave towards the interior of the air valve main body, as shown in the figure 1 (the air valve is opened) and the figure 2 (the air valve is closed).
Typically, in an air valve, there is one inlet (i.e., fluid inlet side), one outlet, one valve plate, one shaft and a seal. For a conventional single-vane valve, the valve plate is positioned in the middle of the air valve main body, the shaft is positioned in the center of the valve plate, and the sealing structures are respectively positioned in the air valve main bodyThe middle position of upper portion and lower part, the valve plate rotates the back and forms the effect of closing in the middle part position of main part. The invention is based on the change of the position of the component, in order to further reduce the resistance of the single-vane valve, the structure of the air valve and the sealing is studied, as shown in figure 3, and the result shows that: the function of the upper seal is (x +0.208D)2+(y+0.308D)2＝(1.324D)2The function formula of the lower sealing is (x-0.181D)2+(y+0.165D)2＝(0.245D)2The function formula followed by the valve plate is (x-2.178D)2+(y+28.826D)2＝(29.842D)2Wherein D is the damper height, as shown in fig. 8.
Further, as in fig. 3, in this example:
more preferably, the distance L1 between the axis of the rotating shaft and the fluid inlet side of the damper is 0.2D, the distance L2 between the axis of the rotating shaft and the fluid outlet side of the damper is D, the distance L4 between the connecting point of the second curved surface and the inclined surface and the fluid inlet side of the damper is 0.246D, the distance L3 between the connecting point of the inclined surface and the lower portion of the damper body and the fluid inlet side of the damper is 0.248D, the perpendicular distance H between the connecting point of the second curved surface and the inclined surface and the connecting point of the inclined surface and the lower portion of the damper body is 0.072D, the diameter D1 of the rotating shaft is 0.048D, and D is the height of the. The radius of curvature R2 of the first curved surface is 1.324D; the radius of curvature R3 of the second curved surface is 0.245D; the radius of curvature R1 of the third curved surface is 29.842D.
Under the scheme, a relatively obvious drag reduction effect can be realized, and the research process is as shown in figure 4: firstly, the position of the shaft is researched, and the optimal position of the guide vane is determined. Considering six conditions a 1-a 6, as shown in fig. 4, it was found that the local drag coefficient was decreasing as the shaft moved progressively toward the conduit side, with the local drag at position a6 being the least (the shaft being on the valve plate side) and the drag reduction rate being 60.15%. In order to ensure the tightness of the shut-off valve, a valve plate is arranged on the pipe wall, but the valve plate can generate a boundary layer in the downstream space of the valve plate, and the valve plate can generate a velocity gradient under the action of the fluid resistance. Therefore, the structural form of the baffle needs to be optimized. Therefore, the resistance generated by the valve plate is reduced, the position of the valve plate is optimized on the basis of A6, the local resistance is the minimum when the valve plate is at the position B5, and the resistance reduction rate is 62.71%; meanwhile, the valve plate is inclined, the valve plate generates a streamline shape, C1-C5 is obtained, the local resistance at the position C2 is the minimum, and the resistance reduction rate is 65.57%; the seal on the side of the shaft is optimized on the basis of C2, the seal is streamlined, the local resistance is found to be reduced, the local resistance at the position D3 is the lowest, and the drag reduction rate reaches 61.17%; on the basis of D3, the other side of the seal is optimized, a section of slope is added in front of the seal and the shape of the slope is changed to be streamline, the shapes E1-E16 are obtained, the local resistance of E4 is minimum, the final optimized shape is E4, and the drag reduction rate reaches 87.11%.
The aperture of the air valve is 320mm multiplied by 250mm, a typical wind speed is selected to be 7m/s, and after optimization is finished, resistance characteristics of an optimization model under different wind speeds are simulated and experimentally verified.
(1) Influence of wind speed on drag reduction rate of air valve
As shown in FIG. 5, research shows that the resistance reduction effect of the novel air valve with the same caliber is obvious under different wind speeds, the resistance reduction range is 81.4% -87.16%, the resistance reduction rate increases with the increase of the wind speed in a turbulent transition region, and when the speed reaches a certain degree and enters a complete turbulent region, the resistance reduction rate does not increase with the increase of the wind speed any more, but tends to be stable.
(2) Turbulent dissipation ratio analysis
Previous research found that the local resistance of the damper is related to energy dissipation, which is essentially the process of converting mechanical energy into internal energy due to fluid deformation, so that the mechanical energy at the outlet becomes smaller. The aim of drag reduction can be achieved by reducing or eliminating the conversion of mechanical energy. The analysis of the turbulent dissipation ratios of the single-blade valve and the novel valve at a typical wind speed of 7m/s and a bore diameter of 320mm × 250mm was carried out in the present study, and the analysis of the turbulent dissipation ratios of the longitudinal section and the transverse section was carried out as shown in fig. 6. It can be seen from the comparison of the longitudinal section of (a), the shaft, the valve plate and the sealing part of the single-blade valve have obvious turbulent dissipation rate, and compared with the novel valve, the shaft and the valve plate of the novel valve move to one side close to the pipeline, so that the original middle turbulent dissipation disappears, and the sealing is endowed with a streamline shape, so that the turbulent dissipation behind the sealing is obviously reduced. It can be seen from the cross-sectional view of (b) that the turbulent dissipation is significantly reduced in the left and right sides of the single vane valve, and the turbulent dissipation is significantly reduced in the left and right sides of the new valve. Therefore, the novel air valve obtained through optimization can effectively reduce the turbulent dissipation of the air valve and achieve the purpose of reducing the local resistance of the air valve.
(3) Full-scale experimental verification analysis
For verifying the drag reduction effect of the novel air valve of the application under different wind speeds, the local resistance coefficient of the single-blade valve and the optimized novel air valve is respectively measured by adopting a full-scale experiment, and the comparison is made with other valves. In the full-scale experiment, the material of the air pipe is galvanized iron sheet. The experimental system comprises a centrifugal fan, a soft joint, a static pressure box, a turbulent flow plate, a rectangular air pipe with the caliber of 320mm multiplied by 250mm, a tested air valve and 1 regulating valve. The fan is connected with the air pipe through a soft joint, and the air pipe is connected with the air pipe and the air valve through flanges and is sealed. A static pressure box and a turbulent flow plate are arranged at a position four meters away from a fan, so that the air flow in the pipeline is stabilized, the vibration of the air flow is reduced, the air supply effect is more ideal, the air flow is fully developed before entering an air valve, and the experiment is more accurate. Experiments prove that the local resistance coefficient of the air valve has good coincidence with the change along with the wind speed and the experimental value and the result of numerical simulation. The novel air valve has obvious resistance reduction effect in practical application and is superior to other air valve structures.
Claims (3)
1. An air valve in a ventilation air-conditioning system comprises an air valve main body (1), and is characterized by further comprising a valve plate (2) positioned at the upper part of the air valve main body (1), a rotating shaft (3) arranged on one side of the valve plate (2) and used for rotating the valve plate (2), and a first seal (4) simultaneously connected with the air valve main body (1) and one side of the valve plate (2);
the air valve further comprises a second seal positioned at the lower part of the air valve main body (1), when the valve plate (2) rotates to the lower part of the air valve main body (1) around the rotating shaft (3), the valve plate (2) is in contact with the second seal, and the first seal (4) and the second seal are positioned at the fluid inlet side of the air valve;
the first seal (4) is provided with a first curved surface which is concave to the inlet side of the air valve fluid;
the second seal comprises a second curved surface (5) and an inclined surface (6) connected with the second curved surface (5), and the second curved surface (5) is concave to the lower part of the air valve main body (1);
the valve plate (2) is a third curved surface which is concave towards the interior of the air valve main body (1);
the functional formula of the first curved surface is as follows:
(x+0.208D)2+(y+0.308D)2＝(1.324D)2
the functional formula of the second curved surface is:
(x-0.181D)2+(y+0.165D)2＝(0.245D)2
the functional formula of the third curved surface is:
(x-2.178D)2+(y+28.826D)2＝(29.842D)2
wherein D is the height of the air valve.
2. The damper according to claim 1, wherein the axis of the rotary shaft (3) is spaced from the inlet side of the damper fluid by 0.2D, the axis is spaced from the outlet side of the damper fluid by D, the connecting point of the second curved surface (5) and the inclined surface (6) is spaced from the inlet side of the damper fluid by 0.246D, the connecting point of the inclined surface (6) and the lower portion of the damper body (1) is spaced from the inlet side of the damper fluid by 0.248D, the vertical distance between the connecting point of the second curved surface (5) and the inclined surface (6) and the connecting point of the inclined surface (6) and the lower portion of the damper body (1) is 0.072D, the diameter of the rotary shaft (3) is 0.048D, and D is the height of the damper.
3. The damper of claim 1, wherein the first curved surface has a radius of curvature of 1.324D; the curvature radius of the second curved surface (5) is 0.245D; the radius of curvature of the third curved surface is 29.842D, and D is the height of the air valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910269124.2A CN110081185B (en) | 2019-04-04 | 2019-04-04 | Air valve in ventilation air-conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910269124.2A CN110081185B (en) | 2019-04-04 | 2019-04-04 | Air valve in ventilation air-conditioning system |
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| CN110081185A CN110081185A (en) | 2019-08-02 |
| CN110081185B true CN110081185B (en) | 2021-01-08 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US5618026A (en) * | 1995-02-13 | 1997-04-08 | General Signal Corporation | Hybrid rotary control valve assembly |
| CN203703305U (en) * | 2014-01-23 | 2014-07-09 | 章华 | Valve deck structure of low-flow-resistance check valve |
| CN205654885U (en) * | 2016-04-20 | 2016-10-19 | 江苏特一机械股份有限公司 | Three pole valves |
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