CN210484652U

CN210484652U - Flow balancing device

Info

Publication number: CN210484652U
Application number: CN201921158868.9U
Authority: CN
Inventors: 吴成斌
Original assignee: Ucloud Technology Co ltd
Current assignee: Ucloud Technology Co ltd
Priority date: 2019-07-19
Filing date: 2019-07-19
Publication date: 2020-05-08
Anticipated expiration: 2029-07-19

Abstract

The utility model relates to a flow balancing unit for the flow in the flow size messenger first pipeline in the regulation first pipeline and the flow in the second pipeline reach the balance, include: a first pitot tube to determine a pressure of the fluid in the first line and a second pitot tube to determine a pressure of the fluid in the second line; and a valve body including: the valve wall is arranged in a surrounding manner to form a valve cavity; the liquid inlet and the liquid outlet are arranged on the valve wall, and fluid enters the valve cavity through the liquid inlet and then flows out through the liquid outlet; and the valve core is arranged in the valve cavity, and pressure components are arranged on two sides of the valve core to detect the pressures of the first pitot tube and the second pitot tube and stretch and push the valve core to reciprocate in the valve cavity under the action of the pressures so as to adjust the flow of fluid flowing through the valve cavity. The flow balancing device enables the flow between the pipelines to be balanced, has strong disturbance resistance and high regulation speed, and does not need an additional power supply and an electric device.

Description

Flow balancing device

Technical Field

The utility model relates to a flow control technical field, concretely relates to flow balancing unit.

Background

The problem of hydraulic imbalance of large-scale fluid transmission and distribution pipe networks is common. In air conditioning, heating and other systems, flow balance is often required to be kept among a plurality of parallel pipelines so as to ensure the best operation effect. For example, when the flow rates of a plurality of cooling towers are unbalanced, the cooling tower having a large water flow rate cannot lower the water temperature to a desired temperature because the air-water ratio (the ratio of the air flow rate to the water flow rate of the cooling tower) is low, while the cooling tower having a small water flow rate cannot cover the packing of the cooling tower with the water amount, and cannot sufficiently exhibit the performance of the cooling tower. For example, if the flow rate of each pipeline in the central air-conditioning water system is not balanced, the phenomenon of uneven cooling and heating can be caused, and the air-conditioning effect is affected.

The lengths of a plurality of parallel pipelines are usually different, the pipeline resistances are also different, and certain measures must be taken to realize flow balance. At present, the adjusting device for flow balance between pipelines mainly comprises a manual adjusting valve, an electric flow adjusting valve and a dynamic flow balance valve. The manual regulating valve is regulated in a mode that before the system is used, the flow of each pipeline is balanced by regulating the manual regulating valve, but if a water system is changed, the flow balance is broken, the flow needs to be regulated again, and the dynamic balance of the flow among the pipelines cannot be guaranteed. The adjusting mode of the electric adjusting valve is that the flow meters are used for measuring the real-time flow of each pipeline and comparing the flow rates, the control system automatically adjusts the state of the electric adjusting valve on each pipeline to ensure the flow balance, the adjusting effect of the mode is good, but a power supply needs to be arranged on each pipeline, and the cost is high. The dynamic flow balance valve automatically changes the resistance coefficient according to the change of the static pressure difference between the front and the back of the valve, when the static pressure difference between the front and the back of the valve is increased, the passage of the valve can be automatically closed, otherwise, when the static pressure difference is reduced, the passage of the valve is automatically opened, and the flow passing through the dynamic flow balance valve can be effectively controlled to keep stable within a certain static pressure difference range.

SUMMERY OF THE UTILITY MODEL

In order to solve the technical problem, an object of the utility model is to provide a flow balancing device, but this flow balancing device automatically regulated makes the flow between the pipeline reach the balance, and the disturbance resistance can be strong when system operation operating mode changes, and the governing speed is fast, need not extra power and electric actuator.

In order to achieve the above purpose, the utility model adopts the following technical scheme:

according to the utility model discloses flow balancing unit for adjust the flow size in the first pipeline so that flow in the first pipeline and the flow in the second pipeline reach the balance, include:

a first pitot tube to determine a pressure of the fluid in the first line and a second pitot tube to determine a pressure of the fluid in the second line; and

the valve body is provided with a valve body,

the valve body includes:

the valve wall is provided with a valve cavity in an enclosing manner;

the liquid inlet and the liquid outlet are arranged on the valve wall, and fluid enters the valve cavity through the liquid inlet and then flows out through the liquid outlet; and

the valve core is arranged in the valve cavity, and pressure components are arranged on two sides of the valve core to detect the pressures of the first pitot tube and the second pitot tube and stretch and retract under the action of the pressures to push the valve core to reciprocate in the valve cavity so as to adjust the flow of fluid flowing through the valve cavity.

Preferably, the pressure assembly comprises:

the first full-pressing piece, the first static-pressing piece, the second full-pressing piece and the second static-pressing piece are arranged on one side of the valve core, the second total pressing member and the first static pressure member are provided on the other side opposite to the one side of the spool, the first full-pressing piece and the first static-pressing piece are respectively communicated with a first full-pressure cavity and a first static-pressure cavity of the first pitot tube so as to respectively extend and retract according to the full pressure and the static pressure of the fluid in the first pipeline, the second full-pressing piece and the second static-pressing piece are respectively communicated with a second full-pressure cavity and a second static-pressure cavity of the second pitot tube so as to respectively extend and retract according to the full pressure and the static pressure of the fluid in the second pipeline, the first full pressing piece, the first static pressing piece, the second full pressing piece and the second static pressing piece exert driving force on the valve core through extension and retraction to enable the valve core to reciprocate in the valve cavity.

Further preferably, a first limiting piece and a second limiting piece are respectively arranged at two ends of the valve body in the valve cavity along the movement direction of the valve core, and the first limiting piece and the second limiting piece are used for limiting the movement interval of the valve core.

Still further preferably, the first limiting member and the second limiting member are respectively located in the middle of two ends of the valve body.

Still further preferably, the first full pressing member and the second static pressing member are disposed opposite to each other on both sides of the first limiting member, the second full pressing member and the first static pressing member are disposed opposite to each other on both sides of the second limiting member, and the first full pressing member, the first static pressing member, the second full pressing member, and the second static pressing member are all in contact with the valve element to apply the driving force to the valve element.

Still further preferably, the first full pressure member and the first static pressure member and the second full pressure member and the second static pressure member are equal in contact area with the spool.

Preferably, the valve core comprises a cylindrical body part and a circular plate part which are oppositely arranged, and a rod member connecting the cylindrical body part and the circular plate part.

Further preferably, the diameters of the liquid inlet and the liquid outlet are the same, and the length of the rod is not less than the diameters of the liquid inlet and the liquid outlet.

Further preferably, the first full pressing member and the first static pressing member and the second static pressing member are formed in a bladder shape.

Further preferably, the first full pressing member and the first static pressing member and the second static pressing member are light film-like members.

The beneficial effects of the utility model reside in that:

the pressure of the fluid in the first pipeline and the pressure of the fluid in the second pipeline are respectively measured through the first pitot tube and the second pitot tube, the pressure components are arranged on two sides of the valve core to detect the pressure of the first pitot tube and the second pitot tube and stretch out and draw back under the action of the pressure to push the valve core to reciprocate in the valve cavity, so that the flow of the fluid flowing through the valve cavity is adjusted, the flow balancing device can automatically adjust the flow between the pipelines to be balanced, the anti-disturbance capacity is high when the operation condition of the system changes, the adjusting speed is high, and extra power supplies and electric devices are not needed.

The above description is only an overview of the technical solution of the present invention, and in order to make the technical means of the present invention clearer and can be implemented according to the content of the description, the following detailed description is made with reference to the preferred embodiments of the present invention and accompanying drawings.

Drawings

Fig. 1 is a cross-sectional view of a flow balancing apparatus according to an embodiment of the present invention;

FIG. 2 is a cross-sectional view of the flow balancing device of FIG. 1 used to adjust the flow in the first conduit to balance the flow in the first conduit with the flow in the second conduit;

FIG. 3 is a cross-sectional view of another section of the valve body of FIG. 1;

FIG. 4 is a cross-sectional view of the valve body of FIG. 1 at a maximum flow rate of fluid through the valve chamber;

FIG. 5 is a cross-sectional view of the valve body of FIG. 1 with a minimum flow of fluid through the valve chamber;

FIG. 6 is a schematic view of the first Pitot tube of FIG. 1.

Detailed Description

The following detailed description of the embodiments of the present invention is provided with reference to the accompanying drawings and examples. The following examples are merely illustrative of the present invention and are not intended to limit the scope of the present invention.

As shown in fig. 1-3, a flow balancing device 10 according to an embodiment of the present invention can be used in a fluid distribution network such as an air conditioner, a heating system, and a water supply system, and is used for adjusting a flow in a first pipeline 50 to balance a flow in the first pipeline 50 with a flow in a second pipeline 60, the flow balancing device 10 includes a first pitot tube 20, a second pitot tube 30, and a valve body 40, wherein the first pitot tube 20 is used for measuring a pressure of a fluid in the first pipeline 50, the second pitot tube 30 is used for measuring a pressure of a fluid in the second pipeline 60, the valve body 40 includes a valve wall 41, a liquid inlet 42, a liquid outlet 43, a valve core 44, and a pressure component 45, the valve wall 41 encloses and forms a valve cavity 46, the liquid inlet 42 and the liquid outlet 43 are disposed on the valve wall 41, the liquid inlet 42 and the liquid outlet 43 are disposed opposite to each other, the fluid enters the valve cavity 46 through the liquid inlet 42 and then, the valve core 44 is disposed in the valve cavity 46, and pressure assemblies 45 are disposed on two sides of the valve core 44 to detect pressures of the first pitot tube 20 and the second pitot tube 30, and extend and retract under the pressure to push the valve core 44 to reciprocate in the valve cavity 46, so as to adjust a flow rate of a fluid flowing through the valve cavity 46.

That is, the pressure assembly 45 extends and contracts according to the detected pressures of the first pitot tube 20 and the second pitot tube 30, and pushes the valve core 44 to reciprocate in the valve cavity 46, when the valve core 44 reciprocates in the valve cavity 46, a part of the liquid inlet 42 and the liquid outlet 43 is blocked, so as to adjust the size of the cross section of the flow passage of the fluid flowing through the valve body 40, thereby adjusting the flow rate of the fluid flowing through the valve cavity 46, as shown in fig. 4 and 5, the cross section of the flow passage of the fluid flowing through the valve body 40 in fig. 4 is the largest, so that the flow rate of the fluid flowing through the valve cavity 46 is the largest, and the cross section of the flow passage of the fluid flowing through the valve body 40 in fig. 5 is the smallest, so that the flow rate of the fluid flowing through the.

The pressure of the fluid in the first pipeline 50 and the pressure of the fluid in the second pipeline 60 are respectively measured through the first pitot tube 20 and the second pitot tube 30, the pressure components 45 are arranged on two sides of the valve core 44 to detect the pressure of the first pitot tube 20 and the second pitot tube 30 and stretch and retract under the action of the pressure to push the valve core 44 to reciprocate in the valve cavity 46, so that the flow of the fluid flowing through the valve cavity 46 is adjusted, the flow balance device 10 can automatically adjust to balance the flow between the pipelines, the anti-disturbance capacity is strong when the operation condition of the system changes, the adjusting speed is high, and no additional power supply or electric device is needed.

According to some embodiments of the present invention, the pressure assembly 45 includes a first full compression element 451, a first static compression element 452, a second full compression element 453, and a second static compression element 454, the first full pressing member 451, the second static pressing member 454, the second full pressing member 453, the first static pressing member 452, the first full pressing member 451, the first static pressing member 452, the first full pressing member 21, the second full pressing member 453, the second static pressing member 454, the second full pressing member 451, the first static pressing member 452, the second static pressing member 454, the second full pressing member 454, the second static pressing member 454, the first full pressing member 451, the second static pressing member 454, the second full pressing member 454, the second static pressing member 454, the second full pressing member 46, the second static pressing member 454, and the valve chamber 46. So that the flow balancing device 10 is better self-adjusting to balance the flow between the lines.

Preferably, a first limiting member 47 and a second limiting member 48 are respectively disposed at two ends of the valve body 40 in the valve chamber 46 along the moving direction of the valve core 44, and the first limiting member 47 and the second limiting member 48 are used for limiting the moving range of the valve core 44. So that the cross-section of the flow-through passage through the valve body 40 varies between a maximum and a minimum.

Further preferably, the first stopper 47 and the second stopper 48 are respectively located at the middle portions of both ends of the valve body 40.

Still further preferably, the first full presser 451 and the second static presser 454 are disposed opposite to each other on both sides of the first stopper 47, the second full presser 453 and the first static presser 452 are disposed opposite to each other on both sides of the second stopper 48, and the first full presser 451 and the first static presser 452 and the second full presser 453 and the second static presser 454 are all in contact with the spool 44 to apply the driving force 454 to the spool. So that the positions of the first and second full pressing

members

451, 454 and the second full pressing

members

453, 452 are defined by the first and

second stoppers

47, 48, respectively.

Still further preferably, the contact areas of the first and second

full followers

451, 452, 453 and 454 and the spool 44 are equal.

According to some embodiments of the present invention, the valve core 44 includes a cylindrical portion 441 and a circular plate portion 442 which are oppositely disposed, and a rod 443 connecting the cylindrical portion 441 and the circular plate portion 442. The cylindrical portion 441 is a solid member, and the diameters of the cylindrical portion 441 and the circular plate portion 442 are slightly smaller than the inner diameter of the valve chamber 46 so as to reciprocate in the valve chamber 46, when the valve core 44 reciprocates in the valve chamber 46, the cylindrical portion 441 of the valve core 44 blocks a portion of the liquid inlet 42 and the liquid outlet 43, thereby adjusting the size of the cross section of the flow passage of the fluid flowing through the valve body 40.

Preferably, inlet port 42 and outlet port 43 have the same diameter, and rod 443 has a length not smaller than the diameters of inlet port 42 and outlet port 43. Further, the length of rod 443 is equal to the diameter of inlet port 42 and outlet port 43.

Preferably, the first and second

full presses

451, 452, 453, and 454 are formed as bladders.

Preferably, the first full presser 451 and the first and second

static pressers

452 and 453 and the second static presser 454 are light film-like members. So as to ensure that the first full pressing member 451, the first static pressing member 452, the second full pressing member 453 and the second static pressing member 454 can freely extend and retract under the action of pressure, and further, the valve core 44 is pushed to reciprocate in the valve cavity 46.

Adopt the utility model discloses flow balancing unit 10 adjusts the concrete method of flow as follows:

as shown in fig. 2 and 6, the flow balancing device 10 is used to adjust the flow in the first pipeline 50 to balance the flow in the first pipeline 50 with the flow in the second pipeline 60, the flow balancing device 10 is installed on the first pipeline 50, the liquid inlet 42 is communicated with the upstream of the first pipeline 50, the liquid outlet 43 is communicated with the downstream of the first pipeline 50, the pressure measuring end of the first pitot tube 20 is located at the transverse center of the first pipeline 50, the opening direction of the first full pressure hole 23 of the first pitot tube 20 is opposite to the water flow direction, the opening direction of the first static pressure hole 24 is perpendicular to the water flow direction, the first full pressure element 451 is communicated with the first full pressure chamber 21 of the first pitot tube 20, the first full pressure element 451 extends and retracts according to the full pressure of the fluid in the first pipeline 50, the first static pressure element 452 is communicated with the first static pressure chamber 22 of the first pitot tube 20, the first static pressure element 452 extends and retracts according to the static pressure of the fluid in the first pipeline, the difference between the full pressure of the fluid in the first line 50 and the static pressure of the fluid is the dynamic pressure of the fluid in the first line 50.

The pressure measuring end of the second pitot tube 30 is located in the transverse center of the second pipeline 60, the structure of the second pitot tube 30 is similar to that of the first pitot tube 20, the opening direction of a second full pressure hole of the second pitot tube 30 is opposite to the water flow direction, the opening direction of a second static pressure hole is perpendicular to the water flow direction, a second full pressure member 453 is communicated with a second full pressure cavity of the second pitot tube 30, the second full pressure member 453 extends and retracts according to the full pressure of the fluid in the second pipeline 60, a second static pressure member 454 is communicated with a second static pressure cavity of the second pitot tube 30, a second static pressure member 454 extends and retracts according to the static pressure of the fluid in the second pipeline 60, and the difference between the full pressure of the fluid in the second pipeline 60 and the static pressure of the fluid is the dynamic pressure of the fluid in the second pipeline 60.

When the velocity of the water flow in the first pipe 50 is higher than that of the water flow in the second pipe 60, the dynamic pressure of the fluid in the first pipe 50 is higher than that of the fluid in the second pipe 60, the spool 44 moves to the side of the second full presser 453 and the first static presser 452 by the drive of the first full presser 451, the first static presser 452, the second full presser 453 and the second static presser 454 due to the dynamic pressure difference, the cross-sectional area of the flow passage is made smaller, the flow rate of the water in the first pipe 50 is adjusted to be lower, when the velocity of the water flow in the first pipe 50 is lower than that of the water flow in the second pipe 60, the dynamic pressure of the fluid in the first pipe 50 is lower than that of the fluid in the second pipe 60, the spool 44 moves to the side of the first full presser 451, the first static presser 452, the second full presser 453 and the second static presser 454 by the dynamic pressure difference, the cross-sectional area of the flow passage is enlarged, the flow rate of the water in the first pipeline 50 is adjusted to be increased, and finally, the flow rate in the first pipeline 50 and the flow rate in the second pipeline 60 are balanced under the adjustment of the flow rate balancing device 10.

The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.

The above-mentioned embodiments only represent some embodiments of the present invention, and the description thereof is specific and detailed, but not to be construed as limiting the scope of the present invention. It should be noted that, for those skilled in the art, without departing from the spirit of the present invention, several variations and modifications can be made, which are within the scope of the present invention. Therefore, the protection scope of the present invention should be subject to the appended claims.

Claims

1. A flow balancing device for adjusting the amount of flow in a first conduit to balance the flow in the first conduit with the flow in a second conduit, comprising:

the valve body is provided with a valve body,

the valve body includes:

the valve wall is provided with a valve cavity in an enclosing manner;

2. The flow balancing apparatus of claim 1, wherein the pressure assembly comprises:

3. The flow balancing apparatus of claim 2, wherein a first limiting member and a second limiting member are respectively disposed at two ends of the valve body in the valve chamber along the movement direction of the valve core, and the first limiting member and the second limiting member are used for limiting the movement range of the valve core.

4. The flow balance device of claim 3, wherein the first retaining member and the second retaining member are each located in a middle of two ends of the valve body.

5. The flow balance device of claim 4 wherein the first full compression member and the second static compression member are disposed opposite to each other on both sides of the first limiting member, the second full compression member and the first static compression member are disposed opposite to each other on both sides of the second limiting member, and the first full compression member and the first static compression member and the second static compression member are in contact with the spool to apply the driving force to the spool.

6. The flow balance device of claim 5, wherein the first and second full followers and second static followers have equal areas of contact with the spool.

7. The flow balance device of claim 1, wherein the spool comprises a cylindrical portion and a circular plate portion disposed opposite each other and a rod connecting the cylindrical portion and the circular plate portion.

8. A flow balancing device according to claim 7, wherein the inlet and outlet ports have the same diameter, and the rod member has a length not smaller than the diameters of the inlet and outlet ports.

9. The flow balancing apparatus of claim 2, wherein the first and second full pressure members and the first and second static pressure members are formed as bladders.

10. The flow balancing apparatus of claim 2, wherein the first and second full compression members and the second static compression member are light film-like members.