A super large flow unloading valve loading pressure control system and method

Abstract

The application provides a kind of super large flow unloading valve loading pressure control system and method, control system includes: first pipeline, first pipeline is equipped with first adjusting component;Second pipeline, second pipeline is equipped with second adjusting component;Connecting pipeline, accumulator group is connected on connecting pipeline;Test unloading valve, at least has boost state and unloading state;The working port of test unloading valve is communicated with the first end of connecting pipeline, first pipeline is connected with second pipeline, the second end of connecting pipeline is communicated with the first end of first pipeline, the first end of second pipeline;The load simulation effect of the application is closer to real working condition;Realize the boost duration, loading pressure gradient regulation and control in boost state, realize the unloading duration, unloading pressure gradient regulation and control in unloading state, overall flexible, avoid the problem that pressure impact is too large and system pipeline is vibrated due to accumulator liquid charging and discharging too fast;Accumulator does not have to adopt larger volume.

Description

Technical Field

[0001] This invention relates to the field of hydraulic valve testing technology, and more specifically, to a control system and method for loading pressure on an ultra-large flow unloading valve. Background Technology

[0002] The unloading valve is a key control component of a coal mine emulsion pump station. By regulating the pump station pressure, the unloading valve ensures the stability and flexibility of the emulsion supply process. When the pressure in the pipeline at the working face exceeds the preset maximum working pressure, the unloading valve begins to unload, reducing the emulsion pump's supply pressure. When the pressure in the pipeline at the working face falls below the preset minimum working pressure, the unloading valve stops unloading, and the emulsion pump resumes its supply pressure. This process involves no overflow loss, achieving energy savings.

[0003] Coal industry standards require that the pressure regulation performance test of unloading valves be conducted under full flow conditions. Currently, the development trend of unloading valves is towards ultra-large flow rates (e.g., 2000 L / min), which places stricter requirements on the loading pressure control capability of the test system. If the loading time is too short, it can easily cause problems such as large hydraulic shock and pipeline vibration. If the accumulator is required to have a good energy storage and buffering effect, then the accumulator needs to have a large total volume, which means that more accumulators are needed to form an accumulator group, increasing the complexity of the test system. Summary of the Invention

[0004] The main objective of this invention is to provide a displacement control system and method for a hydraulic valve-controlled actuator, thereby solving at least one of the technical problems in the prior art, such as the limitation of installing linear or angular displacement sensors on valve-controlled actuators by environmental and installation space requirements.

[0005] To achieve the above objectives, the present invention provides a high-flow-rate unloading valve loading pressure control system, comprising:

[0006] A first pipeline, wherein a first regulating component is provided on the first pipeline;

[0007] The second pipeline is equipped with a second regulating component;

[0008] A connecting pipeline, on which an energy storage group is connected;

[0009] The tested unloading valve has at least a pressurization state and an unloading state;

[0010] The working port of the unloading valve under test is connected to the first end of the connecting pipeline, the first pipeline and the second pipeline are connected in parallel, and the second end of the connecting pipeline is connected to the first end of the first pipeline and the first end of the second pipeline.

[0011] Furthermore, when the unloading valve under test is in a pressurized state, the outlet of the unloading valve under test is cut off, the inlet and working port of the unloading valve under test are connected to each other, the second regulating component is closed, and the loading pressure gradient of the accumulator group is adjusted by the first regulating component.

[0012] Furthermore, when the unloading valve under test is in the unloading state, the working port of the unloading valve under test is closed, the inlet and outlet of the unloading valve under test are connected to each other, the first regulating component is closed, and the unloading pressure gradient of the accumulator group is adjusted by the second regulating component.

[0013] Furthermore, the first regulating component includes a first regulating valve, which regulates the loading pressure gradient of the accumulator group.

[0014] Furthermore, the second regulating component includes a second regulating valve, which regulates the unloading pressure gradient of the accumulator group.

[0015] Furthermore, the first regulating component also includes a first switching valve, which is connected in series with the first regulating valve on the first pipeline, and the first pipeline is opened or closed by the first switching valve.

[0016] Furthermore, the second regulating component also includes a second switching valve, which is connected in series with the second regulating valve on the second pipeline, and the second switching valve is used to open or close the second pipeline.

[0017] Furthermore, the operating opening degree of the second regulating valve is smaller than that of the first regulating valve.

[0018] Furthermore, the accumulator group includes at least one accumulator, and the liquid chamber interface of the accumulator is connected to the connecting pipeline.

[0019] This invention also provides a method for controlling the loading pressure of an ultra-high flow unloading valve, employing the aforementioned control system, comprising:

[0020] When the unloading valve under test is in a pressurized state, the second pipeline is closed by the second regulating component, and the first flow rate of the first pipeline is adjusted by the first regulating component to control the change of the loading pressure gradient.

[0021] When the unloading valve under test is in the unloading state, the first pipeline is closed by the first regulating component, and the second flow rate of the second pipeline is adjusted by the second regulating component to control the change of the unloading pressure gradient.

[0022] The ultra-high flow unloading valve loading pressure control system of this invention adopts capacitive loading and uses an accumulator to simulate the liquid cavity of the fully mechanized mining face liquid supply system, making the load simulation effect closer to the real working conditions. The first regulating component realizes the control of the pressurization duration and loading pressure gradient under the pressurization (loading) state, and the second regulating component realizes the control of the unloading duration and unloading pressure gradient under the unloading state. The whole system is flexible and adjustable, which can avoid the problem of excessive pressure shock and system pipeline vibration caused by the accumulator charging and discharging too quickly. Different specifications of the first and second regulating components can be used for large flow and small flow (usually the liquid inlet is large flow and the total liquid discharge flow of the accumulator group is small flow), so that the accumulator does not need to be large in size.

[0023] The ultra-high flow unloading valve loading pressure control method in this invention adopts a control method based on the principle of accumulator gas pressure derivative. The corresponding control system uses capacitive loading, using an accumulator to simulate the liquid cavity of the fully mechanized mining face liquid supply system, and the load simulation effect is closer to the real working condition. This control method realizes the control of the pressurization duration and loading pressure gradient under pressurization (loading) state through the first regulating component, and realizes the control of the unloading duration and unloading pressure gradient under unloading state through the second regulating component. The whole is flexible and adjustable, which can avoid the problem of excessive pressure shock and system pipeline vibration caused by the accumulator charging and discharging too quickly. Different specifications of the first regulating component and the second regulating component can be used for large flow and small flow (usually the liquid inlet is large flow and the total liquid discharge flow of the accumulator group is small flow), so that the accumulator does not need to be large in size. Attached Figure Description

[0024] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0025] Figure 1 This is a structural diagram of the ultra-high flow unloading valve loading pressure control system provided in an embodiment of the present invention;

[0026] Figure 2 This is a structural diagram of the ultra-large flow unloading valve loading pressure control system in a pressurized state, provided in an embodiment of the present invention.

[0027] Figure 3 The diagram shows the structure of the ultra-large flow unloading valve loading pressure control system in the unloading state, as provided in the embodiment of the present invention.

[0028] The above figures include the following reference numerals:

[0029] 1. First pipeline; 11. First regulating valve; 12. First switching valve; 2. Second pipeline; 21. Second regulating valve; 22. Second switching valve; 3. Connecting pipeline; 31. Accumulator group; 4. Test unloading valve. Detailed Implementation

[0030] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0031] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0032] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0033] This invention provides a high-flow unloading valve loading pressure control system, combined with Figure 1 As shown, it includes:

[0034] First pipeline 1, the first pipeline 1 is provided with a first adjustment component;

[0035] The second pipeline 2 is provided with a second adjustment component;

[0036] Connecting pipe 3, on which an energy storage group 31 is connected;

[0037] The tested unloading valve 4 has at least a pressurization state and an unloading state;

[0038] The working port of the unloading valve 4 under test is connected to the first end of the connecting pipe 3. The first pipe 1 and the second pipe 2 are connected in parallel. The second end of the connecting pipe 3 is connected to the first end of the first pipe 1 and the first end of the second pipe 2.

[0039] Specifically, in combination Figure 1 As shown, the first regulating component on the first pipeline 1 can be any device or component that can directly or indirectly regulate the flow rate of the pipeline, and the second regulating component on the second pipeline 2 can be any device or component that can directly or indirectly regulate the flow rate of the pipeline. The first regulating component and the second regulating component can be, for example, a regulating valve or a valve assembly, without specific limitations here.

[0040] An accumulator group 31 is connected to the connecting pipe 3. Exemplarily, the accumulator group 31 includes at least one accumulator, and the liquid chamber interface of the accumulator is connected to the connecting pipe 3. This embodiment... Figure 1 Three energy storage devices are shown in the figure. In practical applications, the appropriate number of energy storage devices can be selected as needed, and no specific limit is made here.

[0041] For example, the unloading valve under test 4 has an inlet P, an outlet T, and a working port A. The unloading valve under test 4 has at least a pressurization state and an unloading state. When the unloading valve under test 4 is in the pressurization state, the outlet T is closed, and the inlet P is connected to the working port A. When the unloading valve under test 4 is in the unloading state, the working port A is closed in the reverse direction, and the inlet P is connected to the outlet T.

[0042] The working principle of the ultra-large flow unloading valve loading pressure control system in this embodiment of the invention is explained in detail below: During the filling and discharging of the accumulator group 31, the gas is compressed, causing a pressure change. When the liquid pressure is lower than the gas pressure, the gas expands and discharges the liquid, resulting in a pressure decrease; when the liquid pressure is higher than the gas pressure, the accumulator fills with liquid, the gas is compressed, and the pressure increases. The volume change of the gas is the same as the volume change of the liquid within the accumulator, but the elastic modulus of the liquid is much greater than that of the gas. During the pressure change, the compression of the liquid is negligible compared to the compression of the gas. Therefore, the hydraulic derivative and the gas pressure derivative are approximately the same, and the following relationship exists:

[0043]

[0044] In the formula:

[0045] V1 — The volume of compressed gas when the accumulator output pressure is P1;

[0046] P1—Accumulator output pressure. When the accumulator is in the charging and discharging stage, the output pressure is approximately equal to the pressure of the gas in the accumulator after compression.

[0047] n—the ratio of the isobaric heat capacity to the isochoric heat capacity of a gas; in an adiabatic state, it is approximately 1.4.

[0048] Q1 – The liquid flow rate of the accumulator when the output pressure of the accumulator is P1.

[0049] As shown in the above formula, the pressure gradient (dP1 / dt) of P1 is positively correlated with Q1; the larger the flow rate, the greater the pressure gradient. It is negatively correlated with V1; when P1 is in the loading phase, V1 increases negatively (i.e., V1 is a positive gain factor), and when P1 is in the unloading phase, V1 increases positively (i.e., V1 is a negative gain factor). Therefore, the rate of pressure change can be altered by controlling the charging and discharging rate of the accumulator.

[0050] Furthermore, when the unloading valve 4 under test is in a pressurized state, the outlet of the unloading valve 4 under test is cut off, the inlet and working port of the unloading valve 4 under test are connected to each other, the second regulating component is closed, and the loading pressure gradient of the accumulator group 31 is adjusted by the first regulating component.

[0051] Combination Figure 2 As shown, the unloading valve 4 under test is in a pressurized state, the second regulating component is closed, preventing liquid from passing through the second pipeline 2, and the first regulating component is open, allowing liquid to pass through the first pipeline 1. At this time, the flow rate at the inlet P is Q, the flow rate from the working port A is Q2, the total filling flow rate of the accumulator group 31 is Q3, the flow rate at the second end of the connecting pipeline 3 is Q4, the flow rate in the first pipeline 1 is Q5, and the first regulating component can adjust the flow rate Q5 in the first pipeline 1. In the above process, the flow rates have the following relationships: Q = Q2 = Q3 + Q4, and Q4 = Q5.

[0052] Therefore, by adjusting the flow rate Q5 of the first pipeline 1 through the first regulating component, if Q5 increases, then Q3 decreases, the loading pressure gradient decreases, and the pressurization duration increases; if Q5 decreases, then Q3 increases, the loading pressure gradient increases, and the pressurization duration decreases.

[0053] Furthermore, when the unloading valve 4 is in the unloading state, the working port of the unloading valve 4 is closed, the inlet and outlet of the unloading valve 4 are connected to each other, the first regulating component is closed, and the unloading pressure gradient of the accumulator group 31 is adjusted by the second regulating component.

[0054] Combination Figure 3As shown, the tested unloading valve 4 is in the unloading state, the first regulating component is closed, preventing liquid from passing through the first pipeline 2, and the second regulating component is open, allowing liquid to pass through the second pipeline 2. At this time, the working port A is reverse-cut off, the total discharge flow rate of the accumulator group 31 is Q3, the flow rate at the second end of the connecting pipeline 3 is Q4, the flow rate in the second pipeline 2 is Q6, and the second regulating component can adjust the flow rate Q6 in the second pipeline 2. In the above process, the flow rates have the relationships: Q3 = Q4 and Q4 = Q6.

[0055] Therefore, by adjusting the flow rate Q6 of the second pipeline 2 through the second regulating component, if Q6 increases, the pressure drop rate becomes faster, the unloading pressure gradient increases, and the unloading duration of the accumulator discharge becomes shorter; if Q6 decreases, the pressure drop rate becomes slower, the unloading pressure gradient decreases, and the unloading duration becomes longer.

[0056] The ultra-high flow unloading valve loading pressure control system of this invention adopts capacitive loading and uses an accumulator to simulate the liquid cavity of the fully mechanized mining face liquid supply system, making the load simulation effect closer to the real working conditions. The first regulating component realizes the control of the pressurization duration and loading pressure gradient under the pressurization (loading) state, and the second regulating component realizes the control of the unloading duration and unloading pressure gradient under the unloading state. The whole system is flexible and adjustable, which can avoid the problem of excessive pressure shock and system pipeline vibration caused by the accumulator charging and discharging too quickly. Different specifications of the first regulating component and the second regulating component can be used for large flow and small flow (usually the liquid inlet P is the large flow and the total liquid discharge flow of the accumulator group 31 is the small flow), so that the accumulator does not need to be large in size.

[0057] Preferably, the first regulating component includes a first regulating valve 11, which regulates the loading pressure gradient of the accumulator group 31.

[0058] Furthermore, the second regulating component includes a second regulating valve 21, which regulates the unloading pressure gradient of the accumulator group 31.

[0059] The first regulating valve 11 and the second regulating valve 21 here can be any valve with flow regulation capability. The flow of the first pipeline 1 and the second pipeline 2 can be adjusted by the first regulating valve 11 and the second regulating valve 2 respectively, thereby realizing the function of regulating the pressurization duration and the unloading duration.

[0060] Preferably, the first regulating component further includes a first switching valve 12, which is connected in series with the first regulating valve 11 on the first pipeline 1, and the first pipeline 1 is opened or closed by the first switching valve 12.

[0061] Furthermore, the second regulating component also includes a second switching valve 22, which is connected in series with the second regulating valve 21 on the second pipeline 2, and the second switching valve 22 is used to open or close the second pipeline 2.

[0062] The first switching valve 12 and the second switching valve 22 here can be any valve with liquid circuit opening and closing function. The first switching valve 12 and the second switching valve 22 can control the liquid circuit opening and closing of the first pipeline 1 and the second pipeline 2 respectively, and thus can control the opening and closing of the corresponding pipeline when switching between pressurization state and unloading state.

[0063] Preferably, the operating opening degree of the second regulating valve 21 is smaller than that of the first regulating valve 11.

[0064] Combination Figure 2 As shown, the first pipeline 1 is opened by the first switching valve 12, and the loading pressure gradient is adjusted by the first regulating valve 11. During this process, the opening range of the first regulating valve 11 is the working opening degree of the first regulating valve 11; combined with... Figure 3 As shown, the second pipeline 2 is opened by the second switching valve 22, and the unloading pressure gradient is adjusted by the second regulating valve 21. During this process, the opening range of the second regulating valve 21 is the working opening degree of the second regulating valve 21.

[0065] The second regulating valve 21 has a smaller operating opening than the first regulating valve 11, which makes it more suitable for ultra-high flow conditions.

[0066] In pressurized state, the liquid flow rate of the liquid source is very large (the ultra-large flow rate is about 2000L / min). It enters the connecting pipe 3 through the inlet P and the working port A, and then leads to the accumulator group 31 and the first pipe 1 respectively. The flow rate Q3 entering the accumulator group 31 is very small (Q3 is relatively small compared to the ultra-large flow rate of 2000L / min), while the flow rate Q5 entering the first pipe 1 is very large. Therefore, the first regulating valve 11 needs to adopt a large working opening to slow down the filling speed of the accumulator group 31 as much as possible and avoid the accumulator being filled too quickly.

[0067] In the unloading state, the working port A is reverse-cut off, and the total discharge flow rate Q6 of the accumulator group 31 is very small (Q3 is relatively small compared to the ultra-large flow rate of 2000L / min). The liquid coming out of the accumulator group 31 enters the second pipe 2 through the connecting pipe 3. The flow rate of the second pipe 2 is Q6 = Q3, and its flow rate value is also very small. The second regulating valve 21 needs to adopt a small working opening, which can achieve better unloading pressure gradient control and also slow down the discharge rate of the accumulator group 31 as much as possible to avoid the accumulator discharge being too fast.

[0068] This invention also provides a method for controlling the loading pressure of an ultra-high flow unloading valve, employing the aforementioned control system, which includes:

[0069] First pipeline 1, the first pipeline 1 is provided with a first adjustment component;

[0070] The second pipeline 2 is provided with a second adjustment component;

[0071] Connecting pipe 3, on which an energy storage group 31 is connected;

[0072] The tested unloading valve 4 has at least a pressurization state and an unloading state;

[0073] The working port of the unloading valve 4 under test is connected to the first end of the connecting pipe 3. The first pipe 1 and the second pipe 2 are connected in parallel. The second end of the connecting pipe 3 is connected to the first end of the first pipe 1 and the first end of the second pipe 2.

[0074] The control method includes:

[0075] When the unloading valve 4 under test is in a pressurized state, the second pipeline 2 is closed by the second regulating component, and the first flow rate of the first pipeline 1 is adjusted by the first regulating component to control the change of the loading pressure gradient.

[0076] When the unloading valve 4 under test is in the unloading state, the first pipeline 1 is closed by the first regulating component, and the second flow rate of the second pipeline 2 is adjusted by the second regulating component to control the change of the unloading pressure gradient.

[0077] The ultra-high flow unloading valve loading pressure control method in this invention adopts a control method based on the principle of accumulator gas pressure derivative. It uses capacitive loading and uses an accumulator to simulate the liquid cavity of the fully mechanized mining face liquid supply system, making the load simulation effect closer to the real working conditions. The first regulating component realizes the control of the pressurization duration and loading pressure gradient under pressurization (loading) state, and the second regulating component realizes the control of the unloading duration and unloading pressure gradient under unloading state. The whole is flexible and adjustable, which can avoid the problem of excessive pressure shock and system pipeline vibration caused by the accumulator charging and discharging too quickly. Different specifications of the first regulating component and the second regulating component can be used for large flow and small flow (usually the liquid inlet P is the large flow and the total liquid discharge flow of the accumulator group 31 is the small flow), so that the accumulator does not need to be large in size.

[0078] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0079] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0080] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A high-flow-rate unloading valve loading pressure control system, characterized in that, include: A first pipeline, wherein a first regulating component is provided on the first pipeline; The second pipeline is equipped with a second regulating component; A connecting pipeline, on which an energy storage group is connected; The tested unloading valve has at least a pressurization state and an unloading state; The working port of the unloading valve under test is connected to the first end of the connecting pipeline, the first pipeline and the second pipeline are connected in parallel, and the second end of the connecting pipeline is connected to the first end of the first pipeline and the first end of the second pipeline; The first regulating component includes a first regulating valve, which regulates the loading pressure gradient of the accumulator group; the second regulating component includes a second regulating valve, which regulates the unloading pressure gradient of the accumulator group; the first regulating component further includes a first switching valve, which is connected in series with the first regulating valve on the first pipeline, and the first switching valve is used to open or close the first pipeline; the second regulating component further includes a second switching valve, which is connected in series with the second regulating valve on the second pipeline, and the second switching valve is used to open or close the second pipeline.

2. The control system according to claim 1, characterized in that, When the unloading valve under test is in a pressurized state, the outlet of the unloading valve under test is closed, the inlet and working port of the unloading valve under test are connected to each other, the second regulating component is closed, and the loading pressure gradient of the accumulator group is adjusted by the first regulating component.

3. The control system according to claim 1, characterized in that, When the unloading valve under test is in the unloading state, the working port of the unloading valve under test is closed, the inlet and outlet of the unloading valve under test are connected to each other, the first regulating component is closed, and the unloading pressure gradient of the accumulator group is adjusted by the second regulating component.

4. The control system according to claim 1, characterized in that, The operating opening degree of the second regulating valve is smaller than that of the first regulating valve.

5. The control system according to claim 1, characterized in that, The accumulator group includes at least one accumulator, and the liquid chamber interface of the accumulator is connected to the connecting pipeline.

6. A method for controlling the loading pressure of an ultra-large flow unloading valve, characterized in that, The control system according to any one of claims 1 to 5 comprises: When the unloading valve under test is in a pressurized state, the second pipeline is closed by the second regulating component, and the first flow rate of the first pipeline is adjusted by the first regulating component to control the change of the loading pressure gradient. When the unloading valve under test is in the unloading state, the first pipeline is closed by the first regulating component, and the second flow rate of the second pipeline is adjusted by the second regulating component to control the change of the unloading pressure gradient.

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