Working condition self-adaptive hydraulic drive diaphragm type compressor and compressor control method thereof

Abstract

The invention provides a working condition self-adaptive liquid-driven diaphragm type compressor and a compressor control method thereof, and relates to the technical field of compressors. After the optimal oil quantity required by each working condition of the compressor is determined, the rotating speed of a plunger driving component and the rotating speed of a reversing driving component under each working condition are determined; according to inlet and outlet pressure signals collected by the pressure signal collecting device, the current optimal rotating speed of the plunger driving component and the reversing driving component is determined, and the plunger driving component and the reversing driving component are controlled to operate at the optimal rotating speed under the working condition, so that the compressor achieves the optimal performance, the working condition self-adaptive adjustment of the compressor is realized, and the working efficiency is improved. The technical problem that in the prior art, a hydraulic drive diaphragm type compressor cannot adapt to working conditions of pressure changes is solved.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a working condition self-adaptive liquid-driven diaphragm compressor and a compressor control method thereof. Background Art

[0002] Liquid-driven diaphragm compressor is a new type of diaphragm compressor that has appeared in recent years. Liquid-driven diaphragm compressor uses a hydraulic system consisting of a high-pressure plunger pump, a reversing valve and a relief valve to drive the diaphragm to compress the gas to do work. The hydraulic system generates high-pressure hydraulic oil to directly push the diaphragm, which eliminates the intermediate transmission structure compared to traditional piston diaphragm compressors. Compared with traditional piston diaphragm compressors, this new type of diaphragm compressor has the advantages of small size and flexible layout. At the same time, since there is no mechanical transmission mechanism such as a crankshaft connecting rod, the reliability is improved and the failure rate is reduced.

[0003] The operating range of diaphragm compressors varies greatly. For hydrogen diaphragm compressors used to charge tube bundle trucks, the intake pressure is generally around 1-3MPa, and the exhaust pressure is around 5-20MPa; for hydrogenation diaphragm compressors used in hydrogenation stations, the intake pressure is generally around 5-20MPa, and the exhaust pressure is 25-45MPa. Diaphragm compressors rely on the hydraulic oil that periodically enters the diaphragm compressor diaphragm head to work on the diaphragm to compress the gas. For different intake and exhaust pressures, the amount of oil required for each working cycle is different. The amount of oil supplied by a general diaphragm compressor for each working cycle is constant and will not change with changes in operating conditions.

[0004] However, with the development of the industry, green hydrogen is increasingly being introduced into the hydrogen energy industry. Compared with traditional chemical hydrogen, green hydrogen has a larger range of hydrogen pressure variations, so its operating conditions are wider. For traditional compressors using follow-up relief valves, they can only adapt to certain operating conditions based on the exhaust pressure, but cannot adapt well to changes in the intake pressure. Summary of the invention

[0005] The object of the present invention is to provide a working condition adaptive liquid-driven diaphragm compressor and a compressor control method thereof, so as to alleviate the technical problem existing in the prior art that the liquid-driven diaphragm compressor cannot adapt to the working condition of pressure changes.

[0006] In a first aspect, the present invention provides a working condition self-adaptive liquid-driven diaphragm compressor, comprising: 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 collecting device;

[0007] The first-stage membrane head is used to be connected to an air inlet pipeline, and the second-stage membrane head is used to be connected to an exhaust pipeline;

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

[0009] The plunger driving member is in driving connection with the plunger pump, and the plunger driving member is configured to adjust the rotation speed of the plunger pump according to the pressure information collected by the pressure signal collecting 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, and the pressure reducing cylinder reciprocates to drive the primary membrane head and the secondary membrane head to alternately compress the gas to perform work;

[0011] The reversing drive component is in driving connection with the reversing valve, the reversing valve is used to allow the high-pressure oil in the plunger pump to alternately flow to the pressure reducing cylinder, and the reversing drive component is configured to be able to adjust the flow area of ​​the reversing valve according to the pressure information collected by the pressure signal collection device.

[0012] In an alternative embodiment,

[0013] The plunger driving member is configured as a variable frequency motor, and the variable frequency motor is used to adjust the rotation 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 end of the variable frequency motor to determine the rotation speed of the variable frequency motor.

[0015] In an alternative embodiment,

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

[0017] One end of the valve core is transmission-connected to the reversing drive member;

[0018] The valve sleeve is fixed in the valve body, and the valve core is configured to be rotatable in the valve sleeve;

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

[0020] In an alternative embodiment,

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

[0022] In an alternative embodiment,

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

[0024] The first-level low-pressure side chamber is connected to the first-level membrane head, and the second-level low-pressure side chamber is connected to the second-level membrane head.

[0025] In an alternative embodiment,

[0026] The working condition adaptive liquid-driven diaphragm compressor also includes a reversing valve outlet block;

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

[0028] The first-level high-pressure side chamber is connected to the A interface through 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 alternative embodiment,

[0031] The condition-adaptive liquid-driven diaphragm compressor further includes a pump outlet block;

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

[0033] The pump outlet block has a high-pressure oil channel and an oil return 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 is alternately passed to the primary high-pressure side chamber and the secondary high-pressure side chamber through the rotation of the valve core;

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

[0035] In an alternative embodiment,

[0036] The pump outlet block is provided with an overflow valve, a normally open one-way valve and a pump oil replenishment one-way valve;

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

[0038] The normally open one-way valve is configured to open when the system returns oil and close when the system is working;

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

[0040] In an alternative embodiment,

[0041] The reversing drive component is a servo motor, and the pressure signal acquisition device controls the rotation speed of the servo motor according to the output intake pressure and exhaust pressure signals.

[0042] In a second aspect, a compressor control method for a condition-adaptive liquid-driven diaphragm compressor comprises the following steps:

[0043] Step a: Use simulation software and test methods to determine the optimal amount of oil required for each compressor operating condition;

[0044] Step b: calculating the rotation speed of the plunger driving component and the rotation speed of the reversing driving component in each working condition according to the optimal oil quantity;

[0045] Step c: writing a control program according to the optimal oil volume and the calculated rotation speed, and writing the control program into a control module of the motor;

[0046] Step d: collecting the inlet and outlet pressure signals of the compressor through the pressure signal collection device, and connecting the pressure signals to the control program;

[0047] Step e: the control program determines the current working condition of the compressor according to the pressure signal and calculates the current optimal rotation speed of the plunger drive component and the reversing drive component;

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

[0049] The working condition adaptive liquid-driven diaphragm compressor provided by the present invention determines the optimal oil volume required for each working condition of the compressor, determines the rotation speed of the plunger drive component and the rotation speed of the reversing drive component in each working condition, determines the current optimal rotation speed of the plunger drive component and the reversing drive component according to the inlet and outlet pressure signals collected by the pressure signal collection device, and controls the plunger drive component and the reversing drive component to operate at the optimal rotation speed under the working condition, so that the compressor can achieve optimal performance and realize adaptive adjustment of the working condition of the compressor, alleviating the technical problem in the prior art that the liquid-driven diaphragm compressor cannot adapt to the working condition of pressure changes. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] In order to more clearly illustrate the specific implementation methods of the present invention or the technical solutions in the prior art, the drawings required for use in the specific implementation methods or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some implementation methods of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0051] Figure 1 A schematic diagram of the overall structure of a working condition self-adaptive liquid-driven diaphragm compressor provided by an embodiment of the present invention;

[0052] Figure 2 A quarter cross-sectional view of a reversing valve in a working condition adaptive liquid-driven diaphragm compressor provided by an embodiment of the present invention;

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

[0054] Figure 4 A schematic diagram of a working condition adaptive liquid-driven diaphragm compressor provided in an embodiment of the present invention;

[0055] Figure 5 It is the flow chart of simulation system;

[0056] Figure 6 This is a simulation effect diagram;

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

[0058] Icons: 1-primary diaphragm head; 2-secondary 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-primary low-pressure side chamber; 52-secondary low-pressure side chamber; 53-primary high-pressure side chamber; 54-secondary high-pressure side chamber; 6-overflow valve; 7-normally open one-way valve; 8-pump outlet block; 9-reversing valve outlet block; 10-plunger drive component; 11-reversing drive component; 12-pressure signal acquisition device. DETAILED DESCRIPTION

[0059] The technical solution of the present invention will be described clearly and completely below in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0060] In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first", "second", and "third" are used for descriptive purposes only, and cannot be understood as indicating or implying relative importance.

[0061] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0062] The specific implementation of the present invention is described in detail below in conjunction with the accompanying drawings. It should be understood that the specific implementation described here is only used to illustrate and explain the present invention, and is not used to limit the present invention.

[0063] like Figure 1 , Figure 4 As shown, the working condition adaptive liquid-driven diaphragm compressor provided in this embodiment includes: a first-stage diaphragm head 1, a second-stage diaphragm head 2, a plunger pump 3, a reversing valve 4, a pressure reducing cylinder 5, a plunger driving component 10, a reversing driving component 11 and a pressure signal collecting device 12; the first-stage diaphragm head 1 is used to be connected to the air intake pipeline, and the second-stage diaphragm head 2 is used to be connected to the exhaust pipeline; the pressure signal collecting device 12 is respectively connected to the air intake pipeline and the exhaust pipeline, so that the pressure signal collecting device 12 can collect the intake pressure of the intake pipeline and the exhaust pressure of the exhaust pipeline.

[0064] The plunger driving component 10 is drivingly connected to the plunger pump 3 , and the plunger driving component 10 is configured to adjust the rotation speed of the plunger pump 3 according to the pressure information collected by the pressure signal collecting device 12 , so as to control 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 pressure reducing cylinder 5 reciprocates to drive the primary membrane head 1 and the secondary membrane head 2 to alternately compress the gas to do work.

[0066] The reversing drive component 11 is transmission-connected to the reversing valve 4 , which is used to allow the high-pressure oil in the plunger pump 3 to alternately flow to the pressure reducing cylinder 5 , and 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 collecting device 12 .

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

[0068] The pressure signal acquisition device 12 inputs the collected pressure signal to the control end of the variable frequency motor to determine the speed of the variable frequency motor. The motor speed can be adjusted according to different working conditions, thereby achieving self-adaptation of the compressor working conditions.

[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. The valve core 41 can rotate under the drive of the driving component of the reversing valve 4. The valve sleeve 42 is fixed in the valve body 43, and the valve core 41 rotates in the valve sleeve 42.

[0071] A liquid groove is provided on the valve core 41, and a window is provided on the valve body 43. When the valve core 41 rotates, the relative positions of the liquid groove of the valve core 41 and the window on the valve sleeve 42 change, thereby forming a switching effect to connect or close different oil channels. There are 5 interfaces on the valve body 43, namely, A interface 431, B interface 432, P interface 433, T1 interface 434, and T2 interface 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 is composed of a cylinder body and a piston. The piston is divided into three, namely a primary piston, a secondary piston and a high-pressure piston, and all the pistons are connected by a piston rod.

[0074] The piston and the cylinder body form four chambers, namely the first-level low-pressure side chamber 51, the second-level low-pressure side chamber 52, the first-level high-pressure side chamber 53, and the second-level high-pressure side chamber 54; wherein the first-level low-pressure side chamber 51 is connected to the first-level diaphragm head 1, the second-level low-pressure side chamber 52 is connected to the second-level diaphragm head 2, the first-level high-pressure side chamber 53 is connected to the A interface 431 of the reversing valve 4 through the reversing valve outlet block 9, and the second-level high-pressure side chamber 54 is connected to the B interface 432 of the reversing valve 4 through the reversing valve outlet block 9.

[0075] Furthermore, the working condition adaptive liquid-driven 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 channel and an oil return 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 alternately pass to the first-level high-pressure side chamber 53 and the second-level high-pressure side chamber 54 through the rotation of the valve core 41, and the reciprocating motion of the pressure reducing cylinder 5 drives the first-level diaphragm head 1 and the second-level diaphragm head 2 to alternately compress the gas to do work.

[0076] One end of the oil return channel is connected to the oil inlet of the plunger pump 3, and the other end of the oil return channel is connected to the T1 interface 434 and the T2 interface 435, so that through the rotation of the valve core 41, the A interface 431 and the T1 interface 434 and the B interface 432 and the T2 interface 435 are intermittently connected to form an intermittently connected oil return channel.

[0077] Furthermore, an overflow valve 6, a normally open one-way valve 7 and a pump oil replenishment one-way valve are also provided on the pump outlet block 8; the overflow valve 6 opens when the diaphragm head exhaust is completed to discharge the excess hydraulic oil into the oil tank. The overflow valve 6 prevents the entire hydraulic system from having excessive oil pressure and protects the hydraulic system. At the same time, discharging some high-temperature hydraulic oil can also help reduce the system oil temperature.

[0078] The normally open one-way valve 7 is opened when the system returns oil to help drain the high-temperature hydraulic oil in the system; the normally open one-way valve 7 is closed when the system is working to ensure that the system pressure does not decrease.

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

[0080] Furthermore, the reversing 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 to control the speed of the servo motor.

[0081] In addition, since the reversing drive component 11 is configured as a servo motor, the compressor system can also improve the performance of the compressor by:

[0082] For a two-stage compression liquid-driven diaphragm compressor, when the first-stage diaphragm head 1 is inhaling air, the second-stage diaphragm head 2 is in a compression exhaust state; similarly, when the second-stage diaphragm head 2 is inhaling air, the first-stage diaphragm head 1 is in a compression exhaust state. The two-stage 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 volume required for different working 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 is reversed, when the P interface 433 is connected to the A interface 431 or the B interface 432, the flow area therebetween undergoes a process of changing from small to large and then changing from small to large 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, at this time, a local speed change method can be used, that is, the speed of the valve core 41 is increased within the rotation range of the valve core 41 with a smaller flow area, and the speed of the valve core 41 is decreased within the rotation range of the larger 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 of the reversing valve 4 will be reduced, which helps to reduce the oil temperature of the whole machine.

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

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

[0086] The working condition adaptive liquid-driven diaphragm compressor provided in the present embodiment determines the optimal oil volume required for each working condition of the compressor, determines the rotation speed of the plunger drive component 10 and the rotation speed of the reversing drive component 11 for each working condition, determines the current optimal rotation speed of the plunger drive component 10 and the reversing drive component 11 according to the inlet and outlet pressure signals collected by the pressure signal acquisition device 12, and controls the plunger drive component 10 and the reversing drive component 11 to operate at the optimal rotation speed under the working condition, thereby allowing the compressor to achieve optimal performance and realize adaptive adjustment of the working condition of the compressor, alleviating the technical problem in the prior art that the liquid-driven diaphragm compressor cannot adapt to the working condition of pressure changes.

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

[0088] Step a: Use simulation software and test methods to determine the optimal amount of oil required for each compressor operating condition, wherein each operating condition is determined based on a combination of different suction pressures and exhaust pressures.

[0089] Step b: Calculate the rotation speed of the plunger drive component 10 and the rotation speed of the reversing drive component 11 under each working condition according to the optimum oil quantity.

[0090] Step c: Write a control program according to the optimal oil volume and the calculated rotation speed, and write the control program into the control module of the motor.

[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 working condition of the compressor according to the pressure signal and calculates the current optimal rotation speed of the plunger drive component 10 and the reversing drive component 11.

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

[0094] Through the above-mentioned compressor control method, it is possible to achieve working condition adaptation, that is, the compressor can automatically adjust its output according to changes in working conditions; through program control, the automation level of the compressor is improved; the compressor can also work at an optimal level when it deviates from the rated working conditions; the power consumption of the compressor is reduced, and the performance of the compressor is improved; in the scenario where there is hydrogen production or upstream compressors, the suction pressure can be maintained stable and frequent shutdowns can be avoided; the system oil temperature of the compressor is reduced, and the performance and reliability of the compressor are improved.

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

[0096]

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

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

[0099] q t =V×n

[0100] Wherein, V: volume change of the sealed chamber of the plunger pump; n: motor speed.

[0101] For a compressor, V m and R d is a fixed value, and because L P , L V , L h The hydraulic system pressure will change under the influence of the hydraulic system pressure, and the hydraulic system pressure is mainly affected by the suction pressure and exhaust pressure of the compressor. Specifically, the hydraulic system pressure is relatively low when the suction and exhaust are low, and the hydraulic system pressure is relatively low when the suction and exhaust are high. When the hydraulic system pressure is high, L P , L V , L h will increase, V P will increase; when the hydraulic system pressure is low, L P , L V , L h will become smaller, V P By controlling the speed of the rotary valve, T can be controlled. To make the compressor run at the best state, q t Try to V P Equal. In actual operation, L P , L V , Lh It will also be affected by the oil temperature, and the pressure and oil temperature also have a certain coupling relationship, so it is difficult to determine the optimal operating state of the compressor by formula alone. To determine the optimal operating state of the compressor, we can use system software to build a simulation model, use the intake and exhaust pressures, the rotary valve speed, and the plunger pump motor speed as independent variables to simulate the system. The system diagram is shown below. Figure 5 shown.

[0102] like Figure 6 It can be seen that the horizontal axis is time, the vertical axis is the displacement, the suction pressure is controlled at 2MPa, the exhaust pressure is 20MPa, and the plunger pump drive motor speed is 1480r / min. Using simulation software, it can be concluded that the displacement is relatively high when the rotary valve speed is 220r / min. By analogy, the plunger pump motor speed can also be used as a variable, and the other parameters can be used as constants for simulation to obtain a reasonable value of the plunger pump motor speed. From the above, it can be seen that the simulation software can be used to simulate the best combination of intake pressure, exhaust pressure, rotary valve speed and motor speed.

[0103] like Figure 7 As shown, because there will be differences between the actual compressor and the simulation model, the simulation model is used to obtain reasonable parameters, and then these parameters are used to adjust the parameters of the actual compressor to obtain test data, and the simulation model is corrected using the test data. Repeated iterations can obtain the optimal parameters for the actual operation of the compressor, and then these parameters are programmed and written into the control system of the compressor, thereby achieving the optimal operating state of the compressor. Figure 7 This is the actual measured data of the compressor, which can be used as the parameter correction of the simulation system, and can also be used as the source data of the control program of this model of compressor.

[0104] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or replace some or all of the technical features therein with equivalents. However, these modifications or replacements 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 working condition adaptive liquid-driven diaphragm compressor, characterized in that: include: 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 driving component (10), a reversing driving component (11) and a pressure signal collecting device (12); The first-stage membrane head (1) is used to be connected to an air intake pipeline, and the second-stage membrane head (2) is used to be connected to an exhaust pipeline; The pressure signal acquisition device (12) is configured to acquire the intake pressure of the intake pipeline and the exhaust pressure of the exhaust pipeline; The plunger driving component (10) is in driving connection with the plunger pump (3), and the plunger driving component (10) is configured to be able to adjust the rotation speed of the plunger pump (3) according to the pressure information collected by the pressure signal collecting device (12), so as 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), and the pressure reducing cylinder (5) reciprocates to drive the primary membrane head (1) and the secondary membrane head (2) to alternately compress gas to perform work; The reversing drive component (11) is in transmission connection with the reversing valve (4), the reversing valve (4) is used to allow the high-pressure oil in the plunger pump (3) to flow alternately to the pressure reducing cylinder (5), and the reversing drive component (11) is configured to be able to adjust the flow area of ​​the reversing valve (4) according to the pressure information collected by the pressure signal collecting device (12).

2. The working condition adaptive liquid-driven diaphragm compressor according to claim 1, characterized in that: The plunger driving member (10) is configured as a variable frequency motor, and the variable frequency motor is used to adjust the rotation speed of the plunger pump (3), thereby controlling the amount of oil output by the plunger pump (3); The pressure signal acquisition device (12) inputs the acquired pressure signal into the control end of the variable frequency motor to determine the rotation speed of the variable frequency motor.

3. The working condition adaptive liquid-driven diaphragm compressor according to claim 1, characterized in that: The reversing valve (4) comprises a valve core (41), a valve sleeve (42) and a valve body (43); One end of the valve core (41) is drivingly connected to the reversing drive component (11); The valve sleeve (42) is fixed in the valve body (43), and the valve core (41) is configured to be rotatable in 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 be connected with the window to form an oil passage channel.

4. The working condition adaptive liquid-driven diaphragm compressor according to claim 3, 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).

5. The working condition adaptive liquid-driven diaphragm compressor according to claim 4, characterized in that: The pressure reducing cylinder (5) comprises a primary low-pressure side chamber (51) and a secondary low-pressure side chamber (52); The first-level low-pressure side chamber (51) is connected to the first-level membrane head (1), and the second-level low-pressure side chamber (52) is connected to the second-level membrane head (2).

6. The working condition adaptive liquid-driven diaphragm compressor according to claim 5, characterized in that: The working condition self-adaptive liquid-driven diaphragm compressor further comprises a reversing valve outlet block (9); The pressure reducing cylinder (5) comprises a primary high-pressure side chamber (53) and a secondary high-pressure side chamber (54); The first-stage high-pressure side chamber (53) is connected to the A interface (431) via the reversing valve outlet block (9); The secondary high-pressure side chamber (54) is connected to the B interface (432) via the reversing valve outlet block (9).

7. The working condition adaptive liquid-driven diaphragm compressor according to claim 6, characterized in that: The working condition adaptive liquid-driven diaphragm compressor also includes a pump outlet block (8); The plunger pump (3) is connected to the reversing valve (4) via the pump outlet block (8); The pump outlet block (8) has a high-pressure oil channel and an oil return 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 primary high-pressure side chamber (53) and the secondary high-pressure side chamber (54) through the rotation of the valve core (41); One end of the oil return channel is connected to the oil inlet of the plunger pump (3), and the other end of the oil return channel is connected to the T1 interface (434) and the T2 interface (435), so that through the rotation of the valve core (41), the A interface (431) and the T1 interface (434) and the B interface (432) and the T2 interface (435) are intermittently connected to form an intermittently connected oil return channel.

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

9. The working condition adaptive liquid-driven diaphragm compressor according to claim 1, characterized in that: The reversing drive component (11) is a servo motor, and the pressure signal acquisition device (12) controls the rotation speed of the servo motor according to the output intake pressure and exhaust pressure signals.

10. A compressor control method for a working condition adaptive liquid-driven diaphragm compressor according to any one of claims 1 to 9, characterized in that: The following steps are involved: Step a: Use simulation software and test methods to determine the optimal amount of oil required for each compressor operating condition; Step b: calculating the rotation speed of the plunger drive component (10) and the rotation speed of the reversing drive component (11) in each working condition according to the optimal oil quantity; Step c: writing a control program according to the optimal oil volume and the calculated rotation speed, and writing the control program into a control module of the motor; Step d: collecting the inlet and outlet pressure signals of the compressor through the pressure signal collecting device (12), and connecting the pressure signals to the control program; Step e: the control program determines the current working condition of the compressor according to the pressure signal and calculates the current optimal rotation speed of the plunger drive component (10) and the reversing drive component (11); Step f: The control program outputs a rotation speed signal so that the plunger drive component (10) and the reversing drive component (11) operate at the optimal rotation speed under the working condition.

Images