Adaptive Hydraulic-Driven Diaphragm Compressor and Its Control Method

Abstract

This invention provides an adaptive hydraulically driven diaphragm compressor and its control method, relating to the field of compressor technology. After determining the optimal oil quantity required for each operating condition of the compressor, the rotational speed of the plunger drive component and the rotational speed of the reversing drive component are determined for each operating condition. Based on the inlet and outlet pressure signals acquired by the pressure signal acquisition device, the optimal rotational speeds of the plunger drive component and the reversing drive component are determined, and the plunger drive component and the reversing drive component are controlled to operate at their optimal speeds under that operating condition. This allows the compressor to achieve optimal performance, realizing adaptive adjustment of the compressor's operating conditions and alleviating the technical problem in existing hydraulically driven diaphragm compressors that cannot adapt to pressure changes.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to an adaptive liquid-driven diaphragm compressor and its compressor control method. Background Technology

[0002] Hydraulic-driven diaphragm compressors are a new type of diaphragm compressor that has emerged in recent years. They utilize a hydraulic system consisting of a high-pressure plunger pump, a reversing valve, and a relief valve to drive the diaphragm and compress gas to perform work. The hydraulic system generates high-pressure hydraulic oil that directly pushes the diaphragm, eliminating the intermediate transmission structure compared to traditional piston-type diaphragm compressors. This new type of diaphragm compressor offers advantages over traditional piston-type diaphragm compressors, including smaller size and more flexible layout. Furthermore, the absence of mechanical transmission mechanisms such as crankshafts and connecting rods improves reliability and reduces the failure rate.

[0003] Diaphragm compressors have a wide operating range. For hydrogen diaphragm compressors used for filling tube-bundle vehicles, the inlet pressure is generally around 1-3 MPa, and the exhaust pressure is around 5-20 MPa. For hydrogen refueling diaphragm compressors used in hydrogen refueling stations, the inlet pressure is generally around 5-20 MPa, and the exhaust pressure is 25-45 MPa. Diaphragm compressors rely on hydraulic oil periodically entering the compressor head to perform work on the diaphragm to compress the gas. The amount of oil required for each work cycle varies depending on the inlet and exhaust pressures. Generally, the amount of oil supplied by a diaphragm compressor is constant per work cycle and does not change with operating conditions.

[0004] However, with the development of the industry, green hydrogen is being introduced into the hydrogen energy industry more and more. Compared with traditional chemical hydrogen, green hydrogen has a larger range of hydrogen pressure variation, so its operating range is wider. For traditional compressors that use follow-up relief valves, they can only adapt to certain operating conditions for exhaust pressure, and cannot adapt well to changes in intake pressure. Summary of the Invention

[0005] The purpose of this invention is to provide an adaptive liquid-driven diaphragm compressor and its control method, so as to alleviate the technical problem that existing liquid-driven diaphragm compressors cannot adapt to pressure changes.

[0006] In a first aspect, the adaptive hydraulic diaphragm compressor provided by the present invention includes: a primary diaphragm head, a secondary diaphragm head, a plunger pump, a reversing valve, a pressure reducing cylinder, a plunger driving component, a reversing driving component, and a pressure signal acquisition device.

[0007] The primary diaphragm head is used to connect to the intake pipe, and the secondary diaphragm head is used to connect to the exhaust pipe;

[0008] The pressure signal acquisition device is configured to acquire the intake pressure of the intake pipe and the exhaust pressure of the exhaust pipe.

[0009] The plunger drive component is connected to the plunger pump in a driving connection. The plunger drive component is configured to adjust the speed of the plunger pump according to the pressure information collected by the pressure signal acquisition device, so as to control the amount of oil output by the plunger pump.

[0010] The plunger pump is connected to the pressure reducing cylinder through the reversing valve. The reciprocating motion of the pressure reducing cylinder drives the first-stage diaphragm head and the second-stage diaphragm head to alternately compress gas and do work.

[0011] The reversing drive component is connected to the reversing valve, which is used to alternately supply high-pressure oil from the plunger pump to the pressure reducing cylinder. The reversing drive component is configured to adjust the flow area of ​​the reversing valve according to the pressure information collected by the pressure signal acquisition device.

[0012] In an optional implementation,

[0013] The plunger drive component is configured as a variable frequency motor, which is used to adjust the speed of the plunger pump, thereby controlling the amount of oil output by the plunger pump.

[0014] The pressure signal acquisition device inputs the acquired pressure signal to the control terminal of the variable frequency motor to determine the speed of the variable frequency motor.

[0015] In an optional implementation,

[0016] The reversing valve includes a valve core, a valve sleeve, and a valve body;

[0017] One end of the valve core is connected to the reversing drive component in a transmission manner;

[0018] The valve sleeve is fixed to the valve body, and the valve core is configured to rotate within the valve sleeve;

[0019] The valve core is provided with a liquid passage groove, and the valve body is provided with a window. The liquid passage groove can communicate with the window to form an oil passage channel.

[0020] In an optional implementation,

[0021] The valve body is equipped with interface A, interface B, interface P, interface T1 and interface T2.

[0022] In an optional implementation,

[0023] The pressure-reducing cylinder has a primary low-pressure side chamber and a secondary low-pressure side chamber;

[0024] The primary low-pressure side chamber is connected to the primary membrane head, and the secondary low-pressure side chamber is connected to the secondary membrane head.

[0025] In an optional implementation,

[0026] The adaptive hydraulic diaphragm compressor also includes a reversing valve outlet block.

[0027] The pressure reducing cylinder has a primary high-pressure side chamber and a secondary high-pressure side chamber;

[0028] The primary high-pressure side chamber is connected to the A interface via the reversing valve outlet block;

[0029] The secondary high-pressure side chamber is connected to the B interface through the reversing valve outlet block.

[0030] In an optional implementation,

[0031] The adaptive hydraulic diaphragm compressor also includes a pump outlet block.

[0032] The plunger pump is connected to the pump outlet block and the reversing valve;

[0033] The pump outlet block has a high-pressure oil channel and a return oil channel. One end of the high-pressure oil channel is connected to the oil outlet of the plunger pump, and the other end of the high-pressure oil channel is connected to the P interface, so that the high-pressure oil in the plunger pump can be alternately passed to the first-stage high-pressure side chamber and the second-stage high-pressure side chamber by the rotation of the valve core.

[0034] One end of the return oil channel is connected to the oil inlet of the plunger pump, and the other end of the return oil channel is connected to the T1 interface and the T2 interface, so that the A interface and the T1 interface, as well as the B interface and the T2 interface, are intermittently connected by the rotation of the valve core, forming an intermittently connected return oil channel.

[0035] In an optional implementation,

[0036] The pump outlet block is equipped with an overflow valve, a normally open check valve, and a pump replenishment check valve.

[0037] The overflow valve is used to connect the pump outlet block to the oil tank to drain excess hydraulic oil into the oil tank.

[0038] The normally open check valve is configured to open when the system returns oil and close when the system performs work.

[0039] The pump replenishment check valve is used to replenish the hydraulic oil leaking from the plunger pump.

[0040] In an optional implementation,

[0041] The commutation drive component is a servo motor, and the pressure signal acquisition device controls the speed of the servo motor based on the output intake pressure and exhaust pressure signals.

[0042] Secondly, a compressor control method for an adaptive liquid-driven diaphragm compressor includes the following steps:

[0043] Step a: Use simulation software and testing methods to determine the optimal oil quantity required by the compressor under various operating conditions;

[0044] Step b: Calculate the rotational speed of the plunger drive component and the rotational speed of the reversing drive component under each operating condition based on the optimal oil quantity;

[0045] Step c: Write a control program based on the optimal oil quantity and the calculated speed, and write the control program into the motor's control module;

[0046] Step d: Collect the inlet and outlet pressure signals of the compressor through the pressure signal acquisition device, and input the pressure signals into the control program;

[0047] Step e: The control program determines the current operating condition of the compressor based on the pressure signal and calculates the optimal speed of the plunger drive component and the reversing drive component.

[0048] Step f: The control program outputs a speed signal to make the plunger drive component and the reversing drive component operate at the optimal speed under this working condition.

[0049] The adaptive hydraulic diaphragm compressor provided by this invention determines the optimal oil quantity required for each operating condition of the compressor, then determines the rotational speed of the plunger drive component and the reversing drive component for each operating condition. Based on the inlet and outlet pressure signals collected by the pressure signal acquisition device, the optimal rotational speed of the plunger drive component and the reversing drive component is determined, and the plunger drive component and the reversing drive component are controlled to operate at the optimal rotational speed under that operating condition, thereby enabling the compressor to achieve optimal performance and realizing adaptive adjustment of the compressor's operating conditions. This alleviates the technical problem in the prior art where hydraulic diaphragm compressors cannot adapt to pressure changes. Attached Figure Description

[0050] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0051] Figure 1 This is a schematic diagram of the overall structure of the adaptive liquid-driven diaphragm compressor provided in an embodiment of the present invention;

[0052] Figure 2 A quarter-section view of the reversing valve in the adaptive liquid-driven diaphragm compressor provided in an embodiment of the present invention;

[0053] Figure 3 This is a structural cross-sectional view of the pressure reducing cylinder in an adaptive liquid-driven diaphragm compressor provided in an embodiment of the present invention;

[0054] Figure 4 A schematic diagram of an adaptive hydraulically driven diaphragm compressor provided in an embodiment of the present invention;

[0055] Figure 5 Here is the flowchart for the simulation system;

[0056] Figure 6 This is a simulation rendering;

[0057] Figure 7 These are actual measured data for the compressor.

[0058] Icons: 1-First-stage diaphragm head; 2-Second-stage diaphragm head; 3-Plunger pump; 4-Reversing valve; 41-Valve core; 42-Valve sleeve; 43-Valve body; 431-A interface; 432-B interface; 433-P interface; 434-T1 interface; 435-T2 interface; 5-Pressure reducing cylinder; 51-First-stage low-pressure side chamber; 52-Second-stage low-pressure side chamber; 53-First-stage high-pressure side chamber; 54-Second-stage high-pressure side chamber; 6-Relief valve; 7-Normally open check valve; 8-Pump outlet block; 9-Reversing valve outlet block; 10-Plunger drive component; 11-Reversing drive component; 12-Pressure signal acquisition device. Detailed Implementation

[0059] The technical solution of the present invention will now be clearly and completely described with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of the present invention. 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.

[0060] In the description of this invention, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for simplifying the description, and 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. Therefore, they should not be construed as limitations on the invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0061] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0062] The specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit the present invention.

[0063] like Figure 1 , Figure 4 As shown, the adaptive hydraulic diaphragm compressor provided in this embodiment includes: a primary diaphragm head 1, a secondary diaphragm head 2, a plunger pump 3, a reversing valve 4, a pressure reducing cylinder 5, a plunger drive component 10, a reversing drive component 11, and a pressure signal acquisition device 12; the primary diaphragm head 1 is used to connect to the intake pipe, and the secondary diaphragm head 2 is used to connect to the exhaust pipe; the pressure signal acquisition device 12 is connected to the intake pipe and the exhaust pipe respectively, so that the pressure signal acquisition device 12 can acquire the intake pressure of the intake pipe and the exhaust pressure of the exhaust pipe.

[0064] The plunger drive component 10 is connected to the plunger pump 3 in a transmission manner. The plunger drive component 10 is configured to adjust the speed of the plunger pump 3 according to the pressure information collected by the pressure signal acquisition device 12, thereby controlling the amount of oil output by the plunger pump 3.

[0065] The plunger pump 3 is connected to the pressure reducing cylinder 5 through the reversing valve 4. The reciprocating motion of the pressure reducing cylinder 5 drives the first-stage diaphragm head 1 and the second-stage diaphragm head 2 to alternately compress gas and do work.

[0066] The reversing drive component 11 is connected to the reversing valve 4. The reversing valve 4 is used to alternately send the high-pressure oil in the plunger pump 3 to the pressure reducing cylinder 5. The reversing drive component 11 can adjust the flow area of ​​the reversing valve 4 according to the pressure information collected by the pressure signal acquisition device 12.

[0067] Furthermore, the plunger drive component 10 is configured as a variable frequency motor, which can adjust the speed of the plunger pump 3 to control the amount of oil output by the plunger pump 3.

[0068] The pressure signal acquisition device 12 inputs the acquired pressure signal to the control terminal of the variable frequency motor to determine the speed of the variable frequency motor. This allows for adjustment of the motor speed according to different operating conditions, thereby achieving adaptive operation of the compressor.

[0069] Regarding the structure and shape of the reversing valve 4, specifically:

[0070] like Figure 2 As shown, the reversing valve 4 includes a valve core 41, a valve sleeve 42, and a valve body 43. One end of the valve core 41 is connected to the driving component of the reversing valve 4. Under the drive of the driving component of the reversing valve 4, the valve core 41 can rotate. The valve sleeve 42 is fixed inside the valve body 43, and the valve core 41 rotates inside the valve sleeve 42.

[0071] The valve core 41 has a fluid passage groove, and the valve body 43 has a window. When the valve core 41 rotates, the relative positions of the fluid passage groove on the valve core 41 and the window on the valve sleeve 42 change, thereby creating a switching effect to connect or close different oil passages. The valve body 43 has 5 interfaces, namely interface A 431, interface B 432, interface P 433, interface T1 434, and interface T2 435.

[0072] Regarding the structure and shape of the decompression cylinder 5, specifically:

[0073] like Figure 3 As shown, the pressure reducing cylinder 5 is an integrated pressure reducing cylinder 5, which consists of a cylinder body and a piston. The piston is divided into three parts, namely a primary piston, a secondary piston, and a high-pressure piston. All pistons are connected by piston rods.

[0074] The piston and cylinder form four chambers: a primary low-pressure side chamber 51, a secondary low-pressure side chamber 52, a primary high-pressure side chamber 53, and a secondary high-pressure side chamber 54. The primary low-pressure side chamber 51 is connected to the primary diaphragm head 1, the secondary low-pressure side chamber 52 is connected to the secondary diaphragm head 2, the primary high-pressure side chamber 53 is connected to the A port 431 of the directional valve 4 through the directional valve outlet block 9, and the secondary high-pressure side chamber 54 is connected to the B port 432 of the directional valve 4 through the directional valve outlet block 9.

[0075] Furthermore, the adaptive hydraulic diaphragm compressor also includes a pump outlet block 8; the plunger pump 3 is connected to the reversing valve 4 through the pump outlet block 8; the pump outlet block 8 has a high-pressure oil passage and a return oil passage, one end of the high-pressure oil passage is connected to the oil outlet of the plunger pump 3, and the other end of the high-pressure oil passage is connected to the P interface 433, so that the high-pressure oil in the plunger pump 3 can be alternately circulated to the first-stage high-pressure side chamber 53 and the second-stage high-pressure side chamber 54 by the rotation of the valve core 41, and the pressure reducing cylinder 5 reciprocates to drive the first-stage diaphragm head 1 and the second-stage diaphragm head 2 to alternately compress gas to do work.

[0076] One end of the return oil passage is connected to the oil inlet of the plunger pump 3, and the other end of the return oil passage is connected to the T1 interface 434 and the T2 interface 435. By rotating the valve core 41, the A interface 431 and the T1 interface 434, as well as the B interface 432 and the T2 interface 435, are intermittently connected to form an intermittently connected return oil passage.

[0077] Furthermore, the pump outlet block 8 is also equipped with an overflow valve 6, a normally open check valve 7, and a pump replenishment check valve; the overflow valve 6 opens when the diaphragm head exhausts, releasing excess hydraulic oil into the oil tank. The overflow valve 6 serves to prevent the hydraulic system from becoming too hot and to protect the hydraulic system. At the same time, releasing some high-temperature hydraulic oil can also help reduce the system oil temperature.

[0078] Normally open check valve 7 opens when the system returns oil, helping to release the high-temperature hydraulic oil in the system; when the system is working, normally open check valve 7 closes to ensure that the system pressure does not drop.

[0079] The pump replenishment check valve is used to replenish the hydraulic oil leaking from the pump, ensuring the stability of the system.

[0080] Furthermore, the commutation drive component 11 is a servo motor, and the speed of the servo motor is controlled by the intake pressure and exhaust pressure signals output by the pressure signal acquisition device 12.

[0081] Furthermore, since the commutation drive component 11 is configured as a servo motor, the compressor system can also improve the compressor's performance through the following methods:

[0082] For a two-stage hydraulically driven diaphragm compressor, when the first-stage diaphragm head 1 is drawing in air, the second-stage diaphragm head 2 is in a compression and discharge state; similarly, when the second-stage diaphragm head 2 is drawing in air, the first-stage diaphragm head 1 is in a compression and discharge state. The two diaphragm heads do not work at the same time. When the actual operating conditions of the compressor deviate from the design conditions, the reversing valve 4 is adjusted to use different speeds in different cycles to perfectly match the optimal oil quantity required for different operating conditions, thereby improving the efficiency of the compressor, avoiding power waste, and increasing the displacement of the compressor.

[0083] Furthermore, when the reversing valve 4 reverses, when the P port 433 and the A port 431 or the B port 432 are connected, the flow area between them undergoes a process of increasing from small to large and then decreasing again. During this period, when the flow area is small, the throttling loss is large, and the effective oil volume is reduced. Since the reversing drive component 11 uses a servo motor, a partial speed change method can be used at this time. That is, the speed of the valve core 41 is increased in the rotation range with a small flow area, and the speed of the valve core 41 is decreased in the rotation range with a large flow area. This can reduce the throttling loss of the reversing valve 4 and increase the effective oil volume, thereby improving the performance of the compressor. At the same time, due to the reduction of the throttling effect, the throttling heat generated by the reversing valve 4 will be reduced, which helps to reduce the oil temperature of the whole machine.

[0084] Furthermore, this solution is also applicable to single-stage compression hydraulically driven diaphragm compressors. Single-stage compression hydraulically driven diaphragm compressors generally do not use pressure reducing cylinder 5; the hydraulic oil flowing out of reversing valve 4 directly enters the diaphragm head, and the method used in this solution is fully applicable.

[0085] Furthermore, the compressor system can also be connected to signals such as downstream mass flow meters and upstream suction pressure to achieve closed-loop control, enabling the entire green electricity hydrogen production and filling station to achieve complete closed-loop control.

[0086] The adaptive hydraulic diaphragm compressor provided in this embodiment determines the optimal oil quantity required for each operating condition of the compressor, and then determines the rotational speed of the plunger drive component 10 and the rotational speed of the reversing drive component 11 for each operating condition. Based on the inlet and outlet pressure signals collected by the pressure signal acquisition device 12, the optimal rotational speed of the plunger drive component 10 and the reversing drive component 11 is determined, and the plunger drive component 10 and the reversing drive component 11 are controlled to operate at the optimal rotational speed under that operating condition, thereby enabling the compressor to achieve optimal performance and realizing adaptive adjustment of the compressor's operating conditions. This alleviates the technical problem in the prior art where the hydraulic diaphragm compressor cannot adapt to pressure changes.

[0087] The compressor control method for an adaptive liquid-driven diaphragm compressor provided in this embodiment includes the following steps:

[0088] Step a: Use simulation software and testing methods to determine the optimal oil quantity required for each operating condition of the compressor. Each operating condition is determined based on different combinations of suction and discharge pressures.

[0089] Step b: Calculate the rotational speed of the plunger drive component 10 and the rotational speed of the reversing drive component 11 under each operating condition based on the optimal oil quantity.

[0090] Step c: Write a control program based on the optimal oil quantity and the calculated speed, and then write the control program into the motor's control module.

[0091] Step d: Collect the inlet and outlet pressure signals of the compressor through the pressure signal acquisition device 12, and connect the pressure signals to the control program.

[0092] Step e: The control program determines the current operating condition of the compressor based on the pressure signal and calculates the current optimal speed of the plunger drive component 10 and the reversing drive component 11.

[0093] Step f: The control program outputs a speed signal to make the plunger drive component 10 and the reversing drive component 11 operate at the optimal speed under this working condition.

[0094] The compressor control method described above enables adaptive operation, allowing the compressor to automatically adjust its output according to changes in operating conditions. Through program control, the automation level of the compressor is improved. The compressor can operate at its optimal level even when it deviates from its rated operating conditions. The power consumption of the compressor is reduced, and the performance of the compressor is improved. In scenarios where there is hydrogen production or upstream compressors, the suction pressure can be kept stable and frequent shutdowns can be avoided. The system oil temperature of the compressor is reduced, thereby improving the performance and reliability of the compressor.

[0095] Oil quantity V required per minute for a liquid-driven diaphragm compressor P Determined by the following formula:

[0096]

[0097] Among them, V m : Membrane head cavity volume; T: Time required for the membrane cavity to complete one compression; L P : Leakage of the plunger pump; L V : Relief valve leakage; L h : Leakage of the reversing valve.

[0098] The displacement q of the plunger pump t Determined by the following formula:

[0099] q t =V×n

[0100] Where V represents the volume change of the piston pump's sealed cavity, and n represents the motor speed.

[0101] For a compressor, V m and R d It is a fixed value, and because L P L V L h The pressure of the hydraulic system will change due to the pressure of the compressor. Specifically, the hydraulic system pressure is relatively low when the intake and exhaust pressures are low, and relatively low when the intake and exhaust pressures are high. When the hydraulic system pressure is high, L... P L V L h Both will increase, V P It will increase; when the hydraulic system pressure is low, L P L V L h They will all get smaller, V P It will decrease. T can be controlled by adjusting the speed of the rotary valve. To ensure the compressor operates at its optimal state, q needs to be adjusted. t Try to be with V P Equal. In actual runtime, L P L V Lh The pressure is also affected by oil temperature, and there is a certain coupling relationship between pressure and oil temperature. Therefore, it is difficult to determine the optimal operating state of the compressor using only formulas. To determine the optimal operating state of the compressor, we can use system software to build a simulation model, using intake and exhaust pressures, rotary valve speed, and plunger pump motor speed as independent variables for system simulation. The system diagram is shown below. Figure 5 As shown.

[0102] like Figure 6 As can be seen, the horizontal axis represents time, and the vertical axis represents exhaust volume. With the intake pressure controlled at 2 MPa, the exhaust pressure at 20 MPa, and the plunger pump drive motor speed at 1480 r / min, simulation software shows that the exhaust volume is relatively high when the rotary valve speed is 220 r / min. Similarly, the plunger pump motor speed can be used as a variable, with the other parameters as constants, to simulate and determine the reasonable value of the plunger pump motor speed. From the above, it can be seen that simulation software can be used to simulate the optimal combination of intake pressure, exhaust pressure, rotary valve speed, and motor speed.

[0103] like Figure 7 As shown, since there will be differences between the actual compressor and the simulation model, reasonable parameters are obtained by using the simulation model. Then, these parameters are used to adjust the parameters of the actual compressor to obtain experimental data. The simulation model is then corrected using the experimental data. By iterating repeatedly, the optimal parameters for the actual operation of the compressor can be obtained. These parameters are then programmed into the compressor's control system to achieve the optimal operating state of the compressor. Figure 7 This data is from actual compressor measurements. It can be used to correct parameters in a simulation system or as source data for the control program of this compressor model.

[0104] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A condition-adaptive liquid-driven diaphragm compressor, characterized in that, include: Primary diaphragm head (1), secondary diaphragm head (2), plunger pump (3), reversing valve (4), pressure reducing cylinder (5), plunger drive component (10), reversing drive component (11), and pressure signal acquisition device (12). The primary diaphragm head (1) is used to connect to the intake pipe, and the secondary diaphragm head (2) is used to connect to the exhaust pipe; The pressure signal acquisition device (12) is configured to acquire the intake pressure of the intake pipe and the exhaust pressure of the exhaust pipe. The plunger drive component (10) is connected to the plunger pump (3) in a transmission connection. The plunger drive component (10) is configured to adjust the speed of the plunger pump (3) according to the pressure information collected by the pressure signal acquisition device (12) in order to control the amount of oil output by the plunger pump (3). The plunger pump (3) is connected to the pressure reducing cylinder (5) through the reversing valve (4). The pressure reducing cylinder (5) reciprocates to drive the first-stage diaphragm head (1) and the second-stage diaphragm head (2) to alternately compress gas and do work. The reversing drive component (11) is connected to the reversing valve (4) in a transmission manner. The reversing valve (4) is used to allow the high-pressure oil in the plunger pump (3) to alternately flow to the pressure reducing cylinder (5). The reversing drive component (11) is configured to adjust the flow area of ​​the reversing valve (4) according to the pressure information collected by the pressure signal acquisition device (12). The plunger drive component (10) is configured as a variable frequency motor, which is used to adjust the speed of the plunger pump (3) to control the amount of oil output by the plunger pump (3). The pressure signal acquisition device (12) inputs the acquired pressure signal to the control terminal of the variable frequency motor to determine the speed of the variable frequency motor; The reversing drive component (11) is a servo motor. The pressure signal acquisition device (12) controls the speed of the servo motor according to the output intake pressure and exhaust pressure signals so that the plunger drive component (10) and the reversing drive component (11) operate at the optimal speed under this working condition.

2. The adaptive hydraulically driven diaphragm compressor according to claim 1, characterized in that, The reversing valve (4) includes a valve core (41), a valve sleeve (42), and a valve body (43). One end of the valve core (41) is connected to the reversing drive component (11) in a transmission connection; The valve sleeve (42) is fixed inside the valve body (43), and the valve core (41) is configured to rotate within the valve sleeve (42); The valve core (41) is provided with a liquid passage groove, and the valve body (43) is provided with a window. The liquid passage groove can communicate with the window to form an oil passage channel.

3. The adaptive hydraulically driven diaphragm compressor according to claim 2, characterized in that, The valve body (43) is provided with an A interface (431), a B interface (432), a P interface (433), a T1 interface (434), and a T2 interface (435).

4. The adaptive hydraulically driven diaphragm compressor according to claim 3, characterized in that, The pressure reducing cylinder (5) has a primary low-pressure side chamber (51) and a secondary low-pressure side chamber (52). The primary low-pressure side chamber (51) is connected to the primary membrane head (1), and the secondary low-pressure side chamber (52) is connected to the secondary membrane head (2).

5. The adaptive hydraulically driven diaphragm compressor according to claim 4, characterized in that, The adaptive liquid-driven diaphragm compressor also includes a reversing valve outlet block (9). The pressure reducing cylinder (5) has a primary high-pressure side chamber (53) and a secondary high-pressure side chamber (54). The primary high-pressure side chamber (53) is connected to the A port (431) through the reversing valve outlet block (9). The secondary high-pressure side chamber (54) is connected to the B interface (432) through the reversing valve outlet block (9).

6. The adaptive hydraulically driven diaphragm compressor according to claim 5, characterized in that, The adaptive liquid-driven diaphragm compressor also includes a pump outlet block (8). The plunger pump (3) is connected to the pump outlet block (8) and the reversing valve (4); The pump outlet block (8) has a high-pressure oil channel and a return oil channel. One end of the high-pressure oil channel is connected to the oil outlet of the plunger pump (3), and the other end of the high-pressure oil channel is connected to the P interface (433) so that the high-pressure oil in the plunger pump (3) can be alternately passed to the first-stage high-pressure side chamber (53) and the second-stage high-pressure side chamber (54) by the rotation of the valve core (41). One end of the return oil channel is connected to the oil inlet of the plunger pump (3), and the other end of the return oil channel is connected to the T1 interface (434) and the T2 interface (435). By rotating the valve core (41), the A interface (431) and the T1 interface (434), as well as the B interface (432) and the T2 interface (435), are intermittently connected to form an intermittently connected return oil channel.

7. The adaptive hydraulically driven diaphragm compressor according to claim 6, characterized in that, The pump outlet block (8) is equipped with an overflow valve (6), a normally open check valve (7) and a pump replenishment check valve; The overflow valve (6) is used to connect the pump outlet block (8) to the oil tank to drain excess hydraulic oil into the oil tank; The normally open check valve (7) is configured to open when the system returns oil and close when the system performs work; The pump replenishment check valve is used to replenish the hydraulic oil leaking from the plunger pump (3).

8. A compressor control method for an adaptive hydraulically driven diaphragm compressor as described in any one of claims 1-7, characterized in that, Includes the following steps: Step a: Use simulation software and testing methods to determine the optimal oil quantity required by the compressor under various operating conditions; Step b: Calculate the rotational speed of the plunger drive component (10) and the rotational speed of the reversing drive component (11) under each working condition based on the optimal oil quantity; Step c: Write a control program based on the optimal oil quantity and the calculated speed, and write the control program into the motor's control module; Step d: Collect the inlet and outlet pressure signals of the compressor through the pressure signal acquisition device (12) and connect the pressure signals to the control program; Step e: The control program determines the current operating condition of the compressor based on the pressure signal and calculates the current optimal speed of the plunger drive component (10) and the reversing drive component (11); Step f: The control program outputs a speed signal so that the plunger drive component (10) and the reversing drive component (11) operate at the optimal speed under this working condition.

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