A hydraulic gas spring constant flow regulating valve

Abstract

The present invention discloses a hydraulic gas spring constant flow regulating valve, comprising a hydraulic gas spring, a valve plate, and a flow plate. The hydraulic gas spring is provided with a piston and a connecting rod. The piston divides the interior of the hydraulic gas spring into an air chamber and an oil chamber. The piston can slide left and right within the hydraulic gas spring. One end of the connecting rod is fixedly connected to the piston, while the other end passes through the oil chamber and is connected to the valve plate at one end of the hydraulic gas spring. The valve plate can slide left and right on the upper portion of the flow plate along with the piston. An oil cylinder is provided outside the air chamber, and the oil cylinder is provided with an upper diaphragm and a lower diaphragm. The oil cylinder is connected to the oil chamber via a pipe. This valve adopts a combined mechanical structure, utilizing the pressure difference generated by airflow on the flow plate to squeeze the diaphragm. The oil pressure of the hydraulic gas spring and the air pressure generate a pressure difference, which pushes the piston to slide. The pressure change in the air chamber reaches equilibrium with the oil pressure, the piston stops sliding, and the piston drives the valve plate to slide, adjusting the flow area and achieving automatic adjustment of the air volume. The present invention has a simple structure, light weight, a wide adjustment range, high stability, and is maintenance-free.

Description

Technical Field

[0001] The present invention relates to an air volume regulating device, in particular to a hydraulic gas spring type constant flow regulating valve, specifically a mechanical force self-operated constant flow regulating valve, belonging to the technical field of cement industry cooling machine equipment. Background Art

[0002] One of the hallmarks of the new generation of cement clinker coolers is the controlled air supply to each grate in the heat recovery area. Fluctuations in operating conditions and material movement during the production process can cause changes in the clinker thickness and particle size distribution on the grate bed. This leads to variations in the resistance of the material layer on the grate, and consequently, in the pressure drop across the grate. This in turn causes fluctuations in the total pressure drop across the channel. Furthermore, since the new generation of coolers utilizes a plenum air supply structure, with each plenum containing several grate units, without proper control measures, some units within the plenum will experience excessive cooling air flow while others will experience insufficient flow. Manual adjustment alone cannot achieve a reasonable air volume distribution.

[0003] In order to overcome the uneven air supply caused by different clinker layer thickness, temperature, particle size distribution, etc., a mechanical self-regulating valve is often installed under each grate plate to control the air supply flow of each grate plate.

[0004] Currently, there are two types of flow control valves for chillers: gravity-operated and spring-loaded. Gravity-operated flow control valves offer the advantages of maintenance-free operation and a long lifespan, but they often have a heavy counterweight, a narrow adjustment range, poor accuracy, and difficulty in installation. Spring-loaded flow control valves offer the advantages of reduced weight, a wide adjustment range, and ease of installation, but they can suffer from spring fatigue. With both types of flow control valves, the valve disc is subjected to fluid dynamics, causing inertia and reciprocating swings at the equilibrium point, resulting in unstable flow. Furthermore, flow control valves within the same air chamber can interfere with each other, affecting the flow control effectiveness. Summary of the Invention

[0005] Purpose of the invention: The purpose of the present invention is to provide a hydraulic gas spring type constant flow regulating valve.

[0006] Technical solution: The hydraulic gas spring constant flow regulating valve of the present invention includes a hydraulic gas spring, a valve plate, and a flow plate. A piston and a connecting rod are provided inside the hydraulic gas spring. The piston divides the interior of the hydraulic gas spring into an air chamber and an oil chamber. The piston can slide left and right in the hydraulic gas spring. One end of the connecting rod is fixedly connected to the piston, and the other end of the connecting rod passes through the oil chamber and one end of the hydraulic gas spring and is connected to the valve plate. The valve plate can slide left and right on the upper part of the flow plate with the piston. An oil cylinder is provided outside the air chamber, and the oil cylinder is provided with an upper diaphragm and a lower diaphragm. The oil cylinder is connected to the oil chamber through a pipeline.

[0007] Furthermore, the valve plate is arranged on the upper part of the flow plate.

[0008] Furthermore, the oil cylinder is fixed on the upper part of the flow plate.

[0009] Furthermore, flanges are provided at both ends of the flow plate for installation and fixation of the hydraulic gas spring type constant flow regulating valve.

[0010] Furthermore, the flow plate is provided with flow holes.

[0011] Furthermore, the number of the through-flow holes is more than one.

[0012] Furthermore, the diameter φ of the through-hole is 3-6 mm.

[0013] Furthermore, the air chamber is filled with high-pressure gas.

[0014] Furthermore, the oil chamber and the oil cylinder are both filled with hydraulic oil.

[0015] Furthermore, the flow hole area is calculated according to the balance between the static pressure difference generated by the air flow through the flow plate and the air pressure in the air chamber. The flow holes are arranged in sequence so that the valve plate moves to different positions with the piston to obtain different flow areas.

[0016] Furthermore, the flow area is calculated as follows:

[0017] According to the fluid mechanics equation, the relationship between the static pressure difference generated by the airflow through the flow hole and the airflow rate is calculated according to formula (1):

[0018]

[0019] Where ΔP x is the static pressure difference generated by the air flow through the flow hole, that is, the working pressure difference of the hydraulic gas spring constant flow control valve; ρ is the density of the air flow; μ is the flow coefficient of the flow hole, which is 0.6; Q is the air flow of the hydraulic gas spring constant flow control valve, A x It is the flow hole area of ​​the hydraulic gas spring constant flow control valve when the piston is at position X.

[0020] A large amount of temperature-stable air flows through the hydraulic gas spring constant flow control valve, and the temperature change in the air chamber can be ignored. According to the ideal gas state equation (2):

[0021] P Gx ·L x ·S Q =P G0 ·L0·S Q (2)

[0022] Among them, P Gx P is the pressure inside the air chamber of the hydraulic gas spring at position x of the piston. G0 is the initial pressure of the air chamber, SQ is the cross-sectional area of ​​the piston, L x is the distance between the piston and the left end of the air chamber, and L0 is the length of the air chamber.

[0023] The valve plate is subjected to the air flow pressure and the air chamber pressure. When the forces are balanced, the equilibrium relationship of formula (3) exists:

[0024] ΔP x ·S Y =P Gx ·S Q (3)

[0025] Where ΔP x is the static pressure difference generated by the airflow passing through the flow hole obtained in formula (1), S Y is the difference between the cross-sectional area of ​​the piston and the cross-sectional area of ​​the connecting rod, P Gx is the pressure of the piston in the air chamber at position x in the hydraulic gas spring, S Q is the cross-sectional area of ​​the piston.

[0026] Substituting equations (2) and (3) into equation (1) yields the piston position L of the hydraulic gas spring constant flow regulating valve: x and the flow hole area A x The corresponding relationship is as shown in formula (4):

[0027]

[0028] The valve plate moves from position i to j, the distance L i -L j The corresponding flow area is ΔA ij According to formula (4), ΔA ij and valve plate position L i 、L j The relationship is as shown in formula (5):

[0029]

[0030] Where ΔA ij The valve plate of the hydraulic gas spring constant flow regulating valve is L i -L j The corresponding flow area.

[0031] Furthermore, the initial pressure P of the gas chamber can be adjusted G0 , adjust the working pressure difference range of the hydraulic gas spring constant flow control valve, the calculation method is as follows:

[0032] Substituting formula (2) into formula (3) to obtain the working pressure difference range of the hydraulic gas spring constant flow control valve:

[0033]

[0034] The piston position L corresponding to the initial working pressure difference ΔP0 x =L0, maximum working pressure difference ΔP max Corresponding piston position L X =L min , L min The working pressure difference range of the hydraulic gas spring type constant flow regulating valve is ΔP0~ΔP max , Substitute into formula (6), ΔP0 is calculated according to formula (7), ΔP max Calculate according to formula (8):

[0035]

[0036] Among them, ΔP0 is the initial working pressure difference of the hydraulic gas spring constant flow control valve.

[0037]

[0038] Where ΔP max is the maximum working pressure difference of the hydraulic gas spring constant flow regulating valve, L min It is the distance between the piston and the left end of the air chamber when the connecting rod is fully retracted into the oil chamber.

[0039] Furthermore, by increasing L X , to improve the control accuracy of the hydraulic gas spring constant flow regulating valve, the principle is as follows:

[0040] Due to factors such as inertia and friction, the valve plate displacement deviation ΔL will be caused x , resulting in a deviation ΔA in the flow area x According to formula (4), the relationship between the actual flow area and the valve plate position is expressed as formula (9):

[0041]

[0042] Where, ΔL x is the deviation of the piston's x position in the hydraulic gas spring, ΔA x is the flow area deviation of the hydraulic gas spring constant flow control valve, displacement deviation ΔL x When a certain time is reached, by increasing L X , which can reduce the valve plate displacement deviation ΔL x influence, thereby improving the control accuracy of the constant flow control valve.

[0043] Beneficial effects: Compared with the prior art, the present invention has the following significant advantages:

[0044] (1) The present invention adopts a hydraulic gas spring constant flow regulating valve, which uses fluid power, hydraulic pressure and air pressure to adjust the flow area and realize automatic adjustment of air volume.

[0045] (2) The valve plate of the present invention is not directly affected by fluid dynamics, and the airflow is more stable.

[0046] (3) The present invention uses piston sliding to drive the valve plate to move more smoothly, the valve plate is less likely to swing back and forth, and the flow control is more stable.

[0047] (4) The present invention can improve the adjustment accuracy of the constant flow control valve by increasing the stroke of the piston in the hydraulic gas spring.

[0048] (5) The present invention can increase the adjustment range of the constant flow control valve by increasing the initial pressure in the air chamber.

[0049] (6) The present invention has a simple structure, light weight, easy installation and is maintenance-free. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] Figure 1 This is a schematic diagram of a hydraulic gas spring constant flow regulating valve according to the present invention;

[0051] Figure 2 This is a top view of the hydraulic gas spring constant flow regulating valve of the present invention;

[0052] Figure 3 This is a schematic diagram of the assembly of the hydraulic gas spring constant flow regulating valve of the present invention. DETAILED DESCRIPTION

[0053] The technical solution of the present invention will be further described below with reference to the accompanying drawings.

[0054] Example 1

[0055] like Figure 1-3 As shown, the hydraulic gas spring constant flow regulating valve of the present invention includes a hydraulic gas spring 1, a valve plate 2, and a flow plate 3. The hydraulic gas spring 1 is provided with a piston 6 and a connecting rod 7. The piston 6 divides the interior of the hydraulic gas spring 1 into an air chamber 4 and an oil chamber 5. One end of the connecting rod 7 is connected to the piston 6, and the other end of the connecting rod 7 passes through the oil chamber 5 and one end of the hydraulic gas spring 1 to connect to the valve plate 2. The valve plate 2 is arranged on the upper part of the flow plate 3 and can slide left and right on the upper part of the flow plate 3 along with the piston 6. The air chamber 4 of the hydraulic gas spring 1 is provided with an oil cylinder 8. The oil cylinder 8 is fixed to the upper part of the flow plate 3. The oil cylinder 8 is provided with an upper diaphragm 9 and a lower diaphragm 10. The oil cylinder 8 is connected to the oil chamber 5 via a pipe 11.

[0056] The through-flow plate 3 is equipped with flanges 12 at both ends for connecting it to the grate plate. The through-flow plate 3 has at least one through-hole for ventilation of the hydraulic gas spring constant flow control valve. The air chamber 4 is filled with high-pressure gas, while the oil chamber 5 and cylinder 8 are filled with hydraulic oil. The piston 6 can slide left and right within the hydraulic gas spring 1.

[0057] The diameter of the flow hole on the flow plate 3 is 3-6mm, which acts as a throttle. The flow hole area is calculated based on the balance between the static pressure difference generated by the airflow through the flow plate 3 and the air pressure in the air chamber 4. The flow area is then adjusted to the position of the valve plate 2 as the piston 6 moves to different positions. The flow area is calculated as follows:

[0058] like Figure 1-3 As shown, according to the fluid mechanics equation, the relationship between the static pressure difference generated by the airflow through the flow hole and the air flow rate is calculated according to formula (1):

[0059]

[0060] Where ΔP x is the static pressure difference generated by the air flow through the flow hole, that is, the working pressure difference of the hydraulic gas spring constant flow control valve; ρ is the density of the air flow; μ is the flow coefficient of the flow hole, which is 0.6; Q is the air flow of the hydraulic gas spring constant flow control valve, A x It is the flow hole area of ​​the hydraulic gas spring constant flow control valve when the piston is at position X.

[0061] A large amount of temperature-stable air flows through the hydraulic gas spring constant flow control valve, and the temperature change in the air chamber can be ignored. According to the ideal gas state equation (2):

[0062] P Gx ·L x ·S Q =P G0 ·L0·S Q (2)

[0063] Among them, P Gx P is the pressure inside the air chamber of the hydraulic gas spring at position x of the piston. G0 is the initial pressure of the air chamber, S Q is the cross-sectional area of ​​the piston, L x is the distance between the piston and the left end of the air chamber, and L0 is the length of the air chamber.

[0064] The valve plate is subjected to the air flow pressure and the air chamber pressure. When the forces are balanced, the equilibrium relationship of formula (3) exists:

[0065] ΔP x ·S Y =P Gx ·S Q (3)

[0066] Where ΔP x is the static pressure difference generated by the airflow passing through the flow hole obtained in formula (1), S Y is the difference between the cross-sectional area of ​​the piston and the cross-sectional area of ​​the connecting rod, P Gx is the pressure of the piston in the air chamber at position x in the hydraulic gas spring, S Qis the cross-sectional area of ​​the piston.

[0067] Substituting equations (2) and (3) into equation (1) yields the piston position L of the hydraulic gas spring constant flow regulating valve: x and the flow hole area A x The corresponding relationship is as shown in formula (4):

[0068]

[0069] The valve plate moves from position i to j, the distance L i -L j The corresponding flow area is ΔA ij According to formula (4), ΔA ij and valve plate position L i , L j The relationship is as shown in formula (5):

[0070]

[0071] Where ΔA ij The valve plate of the hydraulic gas spring constant flow regulating valve is L i -L j The corresponding flow area.

[0072] Furthermore, the initial pressure P of the gas chamber can be adjusted G0 , adjust the working pressure difference range of the hydraulic gas spring constant flow control valve, the calculation method is as follows:

[0073] Substituting formula (2) into formula (3) to obtain the working pressure difference range of the hydraulic gas spring constant flow control valve:

[0074]

[0075] The piston position L corresponding to the initial working pressure difference ΔP0 X =L0, maximum working pressure difference ΔP max Corresponding piston position L X =L min , L min The working pressure difference range of the hydraulic gas spring type constant flow regulating valve is ΔP0~ΔP max , Substitute into formula (6), ΔP0 is calculated according to formula (7), ΔP max Calculate according to formula (8):

[0076]

[0077] Among them, ΔP0 is the initial working pressure difference of the hydraulic gas spring constant flow control valve.

[0078]

[0079] Where ΔP max is the maximum working pressure difference of the hydraulic gas spring constant flow regulating valve, L min It is the distance between the piston and the left end of the air chamber when the connecting rod is fully retracted into the oil chamber.

[0080] Furthermore, by increasing L X , to improve the control accuracy of the hydraulic gas spring constant flow regulating valve, the principle is as follows:

[0081] Due to factors such as inertia and friction, the valve plate displacement deviation ΔL will be caused x , resulting in a deviation ΔA in the flow area x According to formula (4), the relationship between the actual flow area and the valve plate position is expressed as formula (9):

[0082]

[0083] Where, ΔL x is the deviation of the piston's x position in the hydraulic gas spring, ΔA x is the flow area deviation of the hydraulic gas spring constant flow control valve, displacement deviation ΔL x When a certain time is reached, by increasing L X , which can reduce the valve plate displacement deviation ΔL x influence, thereby improving the control accuracy of the constant flow control valve.

[0084] When using:

[0085] When the airflow passes through the flow hole of the flow plate 3, a pressure difference will be formed at the inlet and outlet of the flow hole, acting on the upper diaphragm 9 and the lower diaphragm 10 of the oil cylinder 8. The force is transmitted to the piston 6 through the oil chamber 5 through the hydraulic oil. The piston 6 drives the valve plate 2 to slide, causing the gas volume in the air chamber 4 to change, and the gas pressure changes accordingly. When the oil pressure and the air pressure reach equilibrium, the piston 6 becomes stable and does not move, the position of the valve plate 2 changes, and the area of ​​the flow hole changes accordingly.

[0086] When the wind speed at the through-hole increases, the static pressure differential between the upper diaphragm 9 and the lower diaphragm 10 increases. The force of the hydraulic oil pushes the piston 6 to the left through the oil chamber 5, compressing the gas in the air chamber 4 and increasing the pressure. The force on the piston 6 reaches a new equilibrium. At the same time, the valve plate 2 moves to the left, covering the through-hole located at the bottom of the valve plate 2. The flow area of ​​the flow plate 3 decreases, and the gas flow through the hydraulic gas spring constant flow control valve 1 remains constant.

[0087] Conversely, the air velocity through the flow hole decreases, the static pressure difference between the upper diaphragm 9 and the lower diaphragm 10 decreases, the gas in the air chamber 4 expands, pushing the piston 6 to the right, and the force on the piston 6 reaches a new equilibrium. At the same time, the valve plate 2 moves to the right, the flow area increases, and the gas flow through the hydraulic gas spring constant flow control valve 1 remains constant.

Claims

1. A hydraulic gas spring constant flow regulating valve, characterized in that: The invention comprises a hydraulic gas spring (1), a valve plate (2), and a flow plate (3). The hydraulic gas spring (1) is provided with a piston (6) and a connecting rod (7). The piston (6) divides the interior of the hydraulic gas spring (1) into an air chamber (4) and an oil chamber (5). The piston (6) can slide left and right in the hydraulic gas spring (1). One end of the connecting rod (7) is fixedly connected to the piston (6). The other end of the connecting rod (7) passes through the oil chamber (5) and one end of the hydraulic gas spring (1) and is connected to the valve plate (2). The valve plate (2) can move along with the piston (6) on the flow plate (3). ) slides left and right on the upper part, an oil cylinder (8) is provided outside the air chamber (4), the oil cylinder (8) is provided with an upper diaphragm (9) and a lower diaphragm (10), the oil cylinder (8) is connected to the oil chamber (5) through a pipe (11), the oil cylinder (8) is fixed on the upper part of the flow plate (3), the flow plate (3) is provided with flow holes, and the pressure difference generated by the air flow in the flow plate (3) is balanced with the air pressure in the air chamber (4), and the stroke of the piston (6) and the distribution of the flow holes are calculated, so that the valve plate (2) moves to different positions with the piston (6) to obtain different flow areas.

2. The hydraulic gas spring constant flow regulating valve according to claim 1, characterized in that: Both ends of the through-flow plate (3) are provided with flanges (12) for ventilation of the hydraulic gas spring type constant flow regulating valve.

3. The hydraulic gas spring constant flow regulating valve according to claim 1, characterized in that: The number of the through-flow holes is one or more.

4. The hydraulic gas spring constant flow regulating valve according to claim 1 or 3, characterized in that: The diameter φ of the through-flow hole is 3-6 mm.

5. The hydraulic gas spring constant flow regulating valve according to claim 1, characterized in that: The air chamber (4) is filled with high-pressure gas.

6. The hydraulic gas spring constant flow regulating valve according to claim 1, characterized in that: The oil chamber (5) and the oil cylinder (8) are both filled with hydraulic oil.

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