Control method of air conditioning system

Abstract

The present application relates to a control method for an air-conditioning system, the air-conditioning system includes a compressor and a condenser connected in a fluid, the compressor includes: a diaphragm, a flywheel providing driving force for the diaphragm, and a motor providing driving force for the flywheel; the control method includes: obtaining the pressure of the condenser in real time; if it is determined that the pressure of the condenser is in a first pressure interval, controlling the drive path of the flywheel to the diaphragm to alternately disconnect and engage at a first frequency. The control method of the present application enables the compressor of the air-conditioning system to intermittently provide a large short-term compression force for a long time, which helps to fully compress the refrigerant.

Description

Technical Field

[0001] The present application relates to a control method for an air conditioning system. Background Art

[0002] The air conditioning compressor is the core component of the air conditioning system, and plays the role of compressing and driving the refrigerant in the air conditioning refrigerant circuit. The air conditioning compressor extracts the refrigerant from the low-pressure area, compresses it, and sends it to the high-pressure area for cooling and condensation. The heat is dissipated into the air through the heat sink, and the refrigerant also changes from gas to liquid, and the pressure increases.

[0003] The power of the air conditioner compressor comes from the motor. The output power of the motor is the main factor that determines the working capacity of the compressor. The compression force that the compressor can provide should not be less than the pressure in the air conditioner condenser. The pressure in the air conditioner condenser is not constant, and it is related to many factors such as ambient temperature and refrigerant state. When the condenser pressure is low, the compressor power does not need to be very large; when the condenser pressure is high, the compressor should have a large output power to be able to provide a higher pressure to press the refrigerant into the high-pressure condenser.

[0004] However, in actual applications, due to various reasons, such as when the power supply is relatively small (such as small photovoltaic power supply), or when the space available for placing equipment is very limited, it is not possible to configure the compressor with an ultra-high power motor, which may cause it to fail to work normally and the application scenarios are greatly limited. Summary of the invention

[0005] The technical problem to be solved by the present application is to propose a control method for an air-conditioning system, wherein the control method enables the compressor of the air-conditioning system to have a higher instantaneous compression force, thereby facilitating sufficient compression of the refrigerant.

[0006] The technical solution of this application is:

[0007] In a first aspect, the present application provides a control method for an air conditioning system, wherein the air conditioning system comprises a compressor and a condenser connected in a fluid, wherein the compressor is a diaphragm compressor, and the compressor comprises:

[0008] Diaphragm,

[0009] a flywheel for providing driving force to the diaphragm, and

[0010] A motor providing driving force for the flywheel;

[0011] The control method comprises:

[0012] Obtaining the pressure of the condenser in real time;

[0013] If it is determined that the pressure of the condenser is in a first pressure interval, the driving path of the flywheel to the diaphragm is controlled to be alternately disconnected and engaged at a first frequency.

[0014] In an optional design, the control method further includes:

[0015] If it is determined that the pressure of the condenser is in a second pressure range that has no intersection with the first pressure range, the drive path is controlled to be alternately disconnected and engaged at a second frequency; wherein the lower limit of the second pressure range is greater than the upper limit of the first pressure range, and the ratio of the engagement time to the disconnection time of the drive path in each cycle of the second frequency is less than the ratio of the engagement time to the disconnection time of the drive path in each cycle of the first frequency.

[0016] In an optional design, the control method further includes:

[0017] If it is determined that the pressure of the condenser is greater than a first pressure threshold, the driving path is controlled to be continuously disconnected; wherein the first speed threshold is greater than an upper limit of the first pressure range.

[0018] In an optional design, the control method further includes:

[0019] If it is determined that the rotation speed of the motor is less than a second pressure threshold, the driving path is controlled to be continuously engaged; wherein the second pressure threshold is less than a lower limit of the first pressure interval.

[0020] In an optional design, the air conditioning system includes:

[0021] An electronic control device mechanically connected to the drive path of the flywheel to the diaphragm, and the electronic control device has a first state of connecting the drive path of the flywheel to the diaphragm and a second state of disconnecting the drive path of the flywheel to the diaphragm;

[0022] A pressure sensor, used to detect the pressure of the condenser;

[0023] A control unit is communicatively connected with the electronic control device and the pressure sensor, so as to obtain the pressure of the condenser from the pressure sensor, and control the electronic control device to be selectively in the first state or the second state based on the pressure.

[0024] In a second aspect, the present application provides a control method for an air conditioning system, wherein the air conditioning system comprises a compressor and a condenser connected in a fluid, wherein the compressor is a diaphragm compressor, and the compressor comprises:

[0025] Refrigerant inlet and outlet,

[0026] a working chamber connected between the inlet and the outlet,

[0027] a suction valve disposed between the inlet and the working chamber,

[0028] an electrically controlled valve disposed between the inlet and the working chamber and connected in parallel with the suction valve,

[0029] Power chamber,

[0030] A diaphragm is arranged between the working chamber and the power chamber,

[0031] a flywheel for providing driving force to the diaphragm, and

[0032] A motor providing driving force for the flywheel;

[0033] The control method comprises:

[0034] Obtaining the pressure of the condenser in real time;

[0035] If it is determined that the pressure of the condenser is in the first pressure interval, the electrically controlled valve is controlled to be alternately opened and closed at a first frequency.

[0036] In an optional design, the control method further includes:

[0037] If it is determined that the pressure of the condenser is in a second pressure range that has no intersection with the first pressure range, the electrically controlled valve is controlled to open and close alternately at a second frequency; wherein the lower limit of the second pressure range is greater than the upper limit of the first pressure range, and the ratio of the engagement time to the disconnection time of the drive path in each cycle of the second frequency is less than the ratio of the engagement time to the disconnection time of the drive path in each cycle of the first frequency.

[0038] In an optional design, the control method further includes:

[0039] If it is determined that the pressure of the condenser is greater than a first pressure threshold, controlling the electronically controlled valve to continue to separate; wherein the first speed threshold is greater than an upper limit of the first pressure range;

[0040] If it is determined that the pressure of the condenser is less than a second pressure threshold, the electrically controlled valve is controlled to be continuously closed; wherein the second pressure threshold is less than a lower limit of the first pressure range.

[0041] In a third aspect, the present application provides a control method for an air conditioning system, wherein the air conditioning system comprises a compressor and a condenser connected in a fluid, wherein the compressor is a diaphragm compressor, and the compressor comprises:

[0042] Refrigerant inlet and outlet,

[0043] a working chamber connected between the inlet and the outlet,

[0044] an inlet valve which is an electrically controlled one-way valve and is disposed between the inlet and the working chamber,

[0045] Power chamber,

[0046] A diaphragm is arranged between the working chamber and the power chamber,

[0047] a flywheel for providing driving force to the diaphragm, and

[0048] A motor providing driving force for the flywheel;

[0049] The control method comprises:

[0050] Obtaining the pressure of the condenser in real time;

[0051] If it is determined that the pressure of the condenser is in the first pressure interval, the suction valve is controlled to be open for an eighth time period every seventh time period.

[0052] In an optional design, if it is determined that the pressure of the condenser is greater than a first pressure threshold, the suction valve is controlled to be continuously opened; wherein the first speed threshold is greater than an upper limit of the first pressure range;

[0053] If it is determined that the pressure of the condenser is less than a second pressure threshold, the suction valve is controlled to be continuously closed; wherein the second pressure threshold is less than a lower limit of the first pressure range.

[0054] This application has at least the following beneficial effects:

[0055] The diaphragm pump or diaphragm compressor of the present application is equipped with a flywheel connected to the driving path of the motor to the diaphragm and a power fluid storage chamber connected to the power chamber fluid, and a valve is set on the connecting path between the two. During the operation of the motor, the aforementioned valve can be opened and closed alternately according to the set frequency, and then the driving path of the flywheel to the diaphragm can be alternately disconnected and connected at the frequency, so that the flywheel and the diaphragm intermittently work in each cycle time of the aforementioned frequency, and the motor periodically stores energy to the flywheel. Generally, as long as the energy provided by the continuously running motor and the power consumption of the diaphragm that only works in part of the time can be balanced in each cycle time, the diaphragm pump or diaphragm compressor can continue to operate stably and intermittently work at high power, which helps the diaphragm pump or diaphragm compressor to complete some tasks that cannot be completed originally, such as enabling the working fluid to be smoothly transported to the desired location or compressing the working fluid into the desired state.

[0056] 1. The control method of the air conditioning system of the present application controls the diaphragm compressor with the energy storage flywheel to intermittently compress the refrigerant according to the set frequency when the condenser pressure is in the appropriate range, so that the flywheel intermittently performs work and stores energy in each cycle of the frequency, and thereby enables the diaphragm compressor to intermittently and vigorously compress the refrigerant fluid in the working chamber relatively smoothly. The method further enables the diaphragm compressor equipped with a relatively small power motor, especially a motor powered by household photovoltaic power, to fully compress the refrigerant.

[0057] 2. The control method of the air-conditioning system of the present application continuously disconnects the flywheel and the diaphragm or the workload when the condenser pressure is high to avoid serious overload of the compressor; and continuously connects the flywheel and the diaphragm or the workload when the condenser pressure is low to reduce energy waste and improve work efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0058] Figure 1 It is a longitudinal cross-sectional view of the diaphragm pump in Example 1 of the present application.

[0059] Figure 2 It is a schematic diagram of the appearance of the diaphragm pump in Example 1 of the present application.

[0060] Figure 3 It is a schematic diagram of the partial structure of the transmission system in Example 1 of the present application.

[0061] Figure 4 It is a partial cross-sectional view of the diaphragm pump in Example 1 of the present application.

[0062] Figure 5 It is a schematic diagram of the partial structure of the transmission system in Example 1 of the present application.

[0063] Figure 6 It is a transmission principle diagram of the transmission system in Example 1 of the present application.

[0064] Figure 7 1 is a graph showing the relationship between the moving speed of the lower end of the first connecting rod and the angle β in the first embodiment of the present application.

[0065] Figure 8 It is a graph showing the relationship between piston speed and angle β.

[0066] Fig. 9 yes Figure 6 A deformation diagram of .

[0067] Fig.10 yes Figure 1 Structural block diagram of the control system of the middle valve.

[0068] Fig.11 It is a schematic diagram of the partial structure of the diaphragm pump in Example 1 of the present application.

[0069] Fig.12 yes Fig.11 Longitudinal cross-sectional view of .

[0070] Fig.13 yes Fig.11 Exploded diagram of .

[0071] Fig.14 It is a longitudinal cross-sectional view of the diaphragm pump in the second embodiment of the present application in the first working state.

[0072] Fig.15 It is a longitudinal cross-sectional view of the diaphragm pump in the second embodiment of the present application in the second working state.

[0073] Fig.16 It is a schematic diagram of the partial structure of the transmission system in Example 2 of the present application.

[0074] Fig.17 It is a longitudinal cross-sectional view of the diaphragm pump in Example 3 of the present application.

[0075] Fig.18 It is a schematic diagram of the partial structure of the transmission system in Example 3 of the present application.

[0076] Fig.19 It is a schematic diagram of the appearance of the diaphragm pump in Example 4 of the present application.

[0077] Fig. 20 This is a longitudinal cross-sectional view of the diaphragm pump in the fourth embodiment of the present application.

[0078] Fig.21 It is a schematic diagram of the partial structure of the transmission system in the fourth embodiment of the present application.

[0079] Fig. 22 It is a longitudinal cross-sectional view of the diaphragm pump in Example 5 of the present application.

[0080] Fig.23 It is a schematic diagram of the partial structure of the transmission system in Example 5 of the present application.

[0081] Fig.24 It is a longitudinal cross-sectional view of the diaphragm pump in Example 6 of the present application.

[0082] Fig.25 yes Fig.24 Structural block diagram of the clutch control system.

[0083] Fig.26 It is a longitudinal cross-sectional view of the diaphragm pump in Example 7 of the present application.

[0084] Fig. 27 yes Fig.26 An enlarged view of the X1 section.

[0085] Fig.28 yes Fig. 27Structural block diagram of the control system of the electric control valve.

[0086] Fig.29 It is a longitudinal cross-sectional view of the diaphragm pump in Example 8 of the present application.

[0087] Fig.30 yes Fig.29 Enlarged view of the X2 section.

[0088] Fig.31 yes Fig.30 Structural block diagram of the control system of the electric control valve.

[0089] Fig.32 It is a longitudinal cross-sectional view of the diaphragm pump in Example 9 of the present application.

[0090] Fig.33 yes Fig.32 Structural block diagram of the control system of the discharge valve.

[0091] Fig.34 It is a longitudinal cross-sectional view of the diaphragm pump in the tenth embodiment of the present application.

[0092] Fig.35 yes Fig.34 Structural block diagram of the control system of the suction valve.

[0093] Fig.36 A longitudinal cross-sectional view of the diaphragm pump in Example 11 of the present application.

[0094] Fig.37 yes Fig.36 Enlarged view of the X3 section.

[0095] Fig.38 This is a transverse cross-sectional view of the diaphragm pump in the eleventh embodiment of the present application.

[0096] Fig.39 It is a schematic diagram of the partial structure of the transmission system in Example 11 of the present application.

[0097] Fig.40 A longitudinal cross-sectional view of the diaphragm pump in Example 12 of the present application.

[0098] Fig.41 A longitudinal cross-sectional view of the diaphragm pump in Example 13 of the present application.

[0099] Fig.42 It is a transverse cross-sectional view of the diaphragm pump in Example 13 of the present application.

[0100] Fig.43 It is a longitudinal cross-sectional view of the diaphragm pump in Example 14 of the present application.

[0101] Fig.44 This is a partial structural exploded view of the diaphragm pump in Example 14 of the present application.

[0102] Fig.45 It is a schematic diagram of the appearance of the diaphragm pump in Example 15 of the present application.

[0103] Fig.46 It is a longitudinal cross-sectional view of the diaphragm pump in the fifteenth embodiment of the present application.

[0104] Fig.47 yes Fig.46 A partial enlarged view of .

[0105] Fig.48 yes Fig.47 The schematic diagram of the structure of the part shown is after the push-pull rod moves to the left.

[0106] Fig.49 It is a transverse cross-sectional view of the diaphragm pump in the fifteenth embodiment of the present application.

[0107] Fig.50 It is a longitudinal cross-sectional view of the diaphragm pump in Example 16 of the present application.

[0108] Fig.51 It is a longitudinal cross-sectional view of the diaphragm pump in Example 17 of the present application.

[0109] Fig.52 It is a longitudinal cross-sectional view of the diaphragm pump in the eighteenth embodiment of the present application.

[0110] Fig.53 It is a longitudinal cross-sectional view of the diaphragm pump in the nineteenth embodiment of the present application.

[0111] Fig.54 It is a longitudinal cross-sectional view of the diaphragm pump in Example 20 of the present application.

[0112] Fig.55 It is a structural schematic diagram of the air-conditioning system in Example 21 of the present application.

[0113] Fig.56 yes Fig.55 Structural block diagram of the control system of the throttle valve.

[0114] Fig.57 It is a structural schematic diagram of the air-conditioning system in Example 22 of the present application.

[0115] Fig.58 yes Fig.57 Structural block diagram of the control system of the electric control valve.

[0116] Fig.59 It is a structural schematic diagram of the air-conditioning system in Example 23 of the present application.

[0117] Fig.60 yes Fig.59 Structural block diagram of the control system for the valve on the compressor.

[0118] In order to help readers observe the structure of the diaphragm pump or diaphragm compressor more clearly, some of the drawings intentionally hide the working fluid and the power fluid, and some of the drawings intentionally hide the guide seat.

[0119] Description of reference numerals:

[0120] a-working fluid, b-power fluid, O-pivot axis of crankshaft;

[0121] 1-working chamber, 2-power chamber, 2a-first half chamber, 2b-second half chamber, 3-diaphragm, 3a-deformation folds of diaphragm, 4-piston, 5-motor, 6-inlet, 7-exhaust, 8-intake valve, 9-exhaust valve, 10-power fluid storage chamber, 11-valve, 12-reducer, 13-crankshaft, 14-first connecting rod, 15-second connecting rod, 16-push-pull rod, 17-transmission chamber, 18-third connecting rod, 19-fourth connecting rod, 20-fifth connecting rod, 2 1-sixth connecting rod, 22-pivot, 23-guide seat, 23a-guide groove, 24-flywheel, 25-coupling, 26-skin bag, 27-blocking net, 28-linear bearing, 29-hoop, 30-rigid ring sleeve, 31-flexible ring sheet, 31a-deformation folds of flexible ring sheet, 32-pressure bearing seat, 32a-circular ring groove, 33-housing, 34-motor speed sensor, 35-controller, 36-fuel tank cap, 37-clutch, 38-electric control valve, 39-pressure sensor;

[0122] 100-compressor, 200-condenser, 300-throttle valve, 400-evaporator. DETAILED DESCRIPTION

[0123] In the description of the specification and claims of this application, if there are terms such as "first", "second", etc., they are only used to distinguish the objects described and do not have any order or technical meaning. Therefore, an object defined as "first", "second", etc. may explicitly or implicitly include one or more of the objects. In addition, similar words such as "one" or "a" do not indicate a quantitative limitation, but rather indicate the existence of at least one, and "multiple" means not less than two. The "multiple" mentioned in this application means not less than two.

[0124] In the description of the specification and claims of this application, if there are terms such as "connection", "installation", "fixation", etc., unless otherwise specified, they should be understood in a broad sense. For example, "connection" can be a separate connection or an integral connection; it can be a direct connection or an indirect connection through an intermediate medium; it can be a non-detachable connection or a detachable connection. For those skilled in the art, the specific meanings of the above terms in this application can be understood according to the specific circumstances.

[0125] In the description of the specification and claims of this application, if there are terms such as "upper", "lower", "horizontal" and the like indicating an orientation or positional relationship based on the orientation or positional relationship shown in the drawings, it is only for the convenience of describing the application clearly and simply, and does not indicate or imply that the elements referred to must have a specific direction, be constructed and operated in a specific orientation. These directional terms are relative concepts, used for relative description and clarification, and may change accordingly according to the change in the orientation of the components placed in the drawings. For example, if the device in the figure is turned over, the elements described as "below" other elements will be positioned "above" other elements.

[0126] In the description of the specification and claims of this application, if there is a term "based on" or "according to", it is used to describe one or more factors that affect the determination. The term does not exclude additional factors that affect the determination. That is, the determination may be based only on these factors or at least partially on these factors. For example, the phrase "based on A, B is determined". In this case, A is a factor that affects the determination of B. This phrase does not exclude that the determination of B may also be based on C.

[0127] In the description of the specification and claims of this application, if the term "configured to" is present, it can generally be interchanged with "having the ability to", "designed to", "for" or "capable of", depending on the context.

[0128] Now, embodiments of the present application are described with reference to the accompanying drawings.

[0129] Embodiment 1:

[0130] Figure 1 and Figure 2 A diaphragm pump is shown. Similar to some existing diaphragm pumps, the diaphragm pump of this embodiment also includes an inlet 6 and an outlet 7 for a working fluid a, a working chamber 1 between the inlet 6 and the outlet 7 connected to the fluid, a power chamber 2, a diaphragm 3 sealed between the working chamber and the power chamber, a piston 4 movably disposed in the power chamber, and a motor 5 connected to the piston through a transmission system to drive the piston to reciprocate. A suction valve 8 is disposed between the inlet 6 and the working chamber 1, and a discharge valve 9 is disposed between the outlet 7 and the working chamber 1. It can be understood that the structure of the diaphragm pump of this embodiment is also applicable to a diaphragm compressor.

[0131] The "diaphragm 3 sealed between the working chamber and the power chamber" mentioned in the foregoing means that the diaphragm 3 is not only arranged between the working chamber 1 and the power chamber 2, but also seals and separates the working chamber 1 and the power chamber 2, so that the working fluid a in the working chamber 1 will not enter the power chamber 2, and the power fluid b in the power chamber 2 will not enter the working chamber 1.

[0132] Both the suction valve 8 and the discharge valve 9 are one-way valves. Figure 1 As shown, when in use, the power chamber 2 is filled with power fluid b. When the motor 5 drives the piston 4 Figure 1 When the piston 4 moves to the left, the internal pressure of the power chamber 2 is less than the internal pressure of the working chamber 1, and the diaphragm 3 deforms to the left. The volume of the working chamber 1 increases and the internal pressure decreases. At this time, the suction valve 8 opens because the pressure on the left side is less than the pressure on the right side, and the discharge valve 9 closes because the pressure on the left side is less than the pressure on the right side. The working fluid a flowing at the inlet 6 enters the working chamber 1 through the opened suction valve 8. When the motor 5 drives the piston 4 to Figure 1 When the power fluid b is pushed to the right, the diaphragm 3 is deformed to the right, and the volume of the working chamber 1 is reduced. At this time, the suction valve 8 is closed because the pressure on the left side is greater than the pressure on the right side, and the discharge valve 9 is opened because the pressure on the left side is greater than the pressure on the right side. The working fluid a in the working chamber 1 is discharged to the discharge port 7 through the opened discharge valve 9 and discharged through the discharge port 7. The running motor 5 drives the piston 4 to Figure 1 The working fluid a is reciprocated in the left-right direction, thereby continuously sucking the working fluid provided to the inlet 6 into the working chamber 1, and then discharging the working fluid a in the working chamber 1 to the outlet 7 and discharged from the outlet 7. In this way, the working fluid a is continuously transported.

[0133] The motor 5 indirectly drives the piston 4 to reciprocate through the transmission system, and the moving piston 4 indirectly drives the diaphragm 3 to move with the help of the power fluid b filled in the power chamber, thereby completing the suction and push-out of the working fluid a. The purpose of the operation of the motor 5 is to drive the diaphragm 3 to do work, and the aforementioned transmission system connecting the motor and the piston, the piston 4, and the power fluid b filled in the power chamber are all arranged on the driving path of the motor 5 to the diaphragm 3, and the driving path of the motor 5 to the diaphragm 3 includes the aforementioned transmission system, the piston 4, and the power fluid b filled in the power chamber.

[0134] The suction valve 8 and the discharge valve 9 having the above functions are very common in the field of diaphragm pumps and diaphragm compressors, and can be directly purchased in the market, so they are not described in detail here.

[0135] The power fluid b is usually hydraulic oil, the working fluid a is usually water, and the diaphragm pump is mostly used for transporting water.

[0136] Refer to Figure 1 As shown, the diaphragm pump is also equipped with a power fluid storage chamber 10 and a third valve 11 in addition to the above-mentioned suction valve 8 and discharge valve 9. The power fluid storage chamber 10 is communicated with the power chamber 2, and is used to receive the power fluid b discharged from the power chamber 2 and provide the power fluid b to the power chamber 2. The valve 11 is arranged on the communication path between the power fluid storage chamber 10 and the power chamber 2, and is used to open and close the communication path between the power fluid storage chamber 10 and the power chamber 2.

[0137] In addition, the diaphragm pump is also provided with a flywheel 24 and a reducer 12 on the transmission path between the motor 5 and the piston 4, that is, on the aforementioned transmission system. The flywheel 24 is connected between the motor 5 and the reducer 12, and the reducer 12 is connected between the flywheel 24 and the piston 4. The flywheel 24 is connected between the motor 5 and the reducer 12, and the power provided by the motor 5 needs to pass through the flywheel 24 to be transmitted to the reducer 12. The reducer 12 is connected between the flywheel 24 and the piston 4, and the power provided by the flywheel 24 needs to pass through the reducer 12 to be transmitted to the downstream piston 4 and the diaphragm 3. The function of the reducer 12 is to reduce the transmission ratio to increase the torque, thereby increasing the driving force exerted on the piston 4 and the diaphragm 3. The function of the flywheel 24 is to store energy and provide the diaphragm 3 with sufficiently large driving power and driving force.

[0138] The diaphragm pump of this embodiment is provided with the above-mentioned power fluid storage chamber 10, valve 11 and flywheel 24, and can intermittently perform high-power external work when the output power of the motor 5 itself is relatively small. The specific analysis is as follows:

[0139] Reference Figure 1As shown. In the starting stage of the motor 5, the speed of the motor 5 and the flywheel 24 is low, the kinetic energy of the flywheel is small, and the motor 5 and the flywheel 24 cannot drive the diaphragm 3 to work with high power. At this time, the valve 11 is opened. When the piston 4 moves to the right, the hydraulic oil as the power fluid b in the power chamber 2 easily flows into the power fluid storage chamber 10 through the valve 11 under the thrust of the piston 4, and the hydraulic oil in the power chamber 2 does not obviously push the diaphragm 3 with a higher load to deform and work. When the piston 4 moves to the left, the hydraulic oil in the power fluid storage chamber 10 is easily pumped into the power chamber 2. Obviously, whether the hydraulic oil in the power chamber 2 is pushed into the power fluid storage chamber 10 or the hydraulic oil in the power fluid storage chamber 10 is pumped into the power chamber 2, it will not consume much power. In this process, the power provided by the motor 5 and the flywheel 24 to the piston 4 is small, the motor 5 mainly works on the flywheel 24, and the mechanical energy output by the motor 5 is mainly converted into the kinetic energy of the flywheel 24, so that the speed of the flywheel 24 is getting higher and higher, and the kinetic energy is getting larger and larger. Obviously, the speed of the motor 5 is positively correlated with the speed of the flywheel 24. Specifically in this embodiment, the speed ratio of the motor 5 to the flywheel 24 is 1. When the speed of the motor 5 is increased to a set value, for example, when the motor 5 reaches the rated speed, the valve 11 is closed. The communication path between the power fluid storage chamber 10 and the power chamber 2 is cut off, and the hydraulic oil in the power chamber 2 cannot enter the power fluid storage chamber 10. The piston 4 moving to the right can only push the hydraulic oil in the power chamber 2 to squeeze the diaphragm 3 to the right, so that the diaphragm 3 deforms to the right and squeezes the working fluid a in the working chamber 1 to do work. Even if the workload of the diaphragm pump is very large at this time, the flywheel 24 storing a large amount of kinetic energy can apply a large rightward thrust to the piston 4, and then the hydraulic oil in the power chamber 2 pushes the diaphragm 3 to deform to the right with great force, and applies a sufficiently large pressure to the working fluid a in the working chamber 1, completing high-power work on the working fluid a - such as pushing water to a height of hundreds of meters.

[0140] The power source of the diaphragm pump is the motor 5, which in turn drives the diaphragm 3 to move through the moving flywheel 24 and the piston 4 to perform work. Based on this, it is obvious that there is such a power relationship: the motor 5 provides driving force for the flywheel 24, the piston 4 and the diaphragm 3, the flywheel 24 provides driving force for the piston 4 and the diaphragm 3, and the piston 4 provides driving force for the diaphragm 3.

[0141] If the valve 11 is always kept in the closed state during the operation of the motor 5. The motor 5, as the power source, has a small power and cannot provide energy for the diaphragm 3 to continuously work at high power. The energy consumed by the diaphragm 3 to work comes from the conversion of the additional electrical energy by the motor 5 and the kinetic energy originally stored in the flywheel 24. Therefore, when the additional energy continuously provided by the motor 5 cannot meet the continuous work requirements of the diaphragm 3, the flywheel 24 provides supplementary energy for the work of the diaphragm 3. This causes the kinetic energy of the flywheel 24 to continue to decrease, and the speed becomes smaller and smaller. This not only causes the operating speed of the motor 5 to be unstable, but also ultimately causes the diaphragm 3 to be unable to work due to insufficient energy supply. Therefore, this embodiment provides the following diaphragm pump control method to solve the aforementioned problems, and the control method includes:

[0142] S101, during the operation of the motor 5, the valve 11 is controlled to be alternately opened and closed at a first frequency.

[0143] That is, during the operation of the motor 5, the valve 11 is alternately opened for the twenty-third time period - closed for the twenty-fourth time period - opened for the twenty-third time period - closed for the twenty-fourth time period... according to the set first frequency. That is, the driving path (or driving force transmission path) of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the first frequency. In each cycle of the first frequency, the valve 11 has a continuous opening time period and a continuous closing time period, and the values ​​of the opening time period and the closing time period can be set as needed. It can be understood that the larger the ratio of the opening time period to the closing time period of the valve 11, the greater the proportion of the energy storage time of the flywheel 24 in each cycle; the smaller the ratio of the opening time period to the closing time period of the valve 11, the smaller the proportion of the energy storage time of the flywheel 24 in each cycle.

[0144] For example, during the operation of the motor, the valve 11 is opened and closed alternately at a frequency of 10 times / minute, and each time it is opened for 2 seconds and closed for 4 seconds. Among them, 10 times / minute means that the valve is opened 10 times and closed 10 times every minute, and the opening and closing are performed alternately. Specifically, the valve is opened for 2 seconds (opened and kept open for 2 seconds) - the valve is closed for 4 seconds (closed and kept closed for 4 seconds) - the valve is opened for 2 seconds - the valve is closed for 4 seconds - the valve is opened for 2 seconds - the valve is closed for 4 seconds - the valve is opened for 2 seconds - the valve is closed for 4 seconds...

[0145] During the operation of the motor 5, the valve 11 is alternately opened and closed according to the set first frequency, so that the drive path of the flywheel 24 to the diaphragm 3 is alternately disconnected and engaged, and then the flywheel 24 and the diaphragm 3 intermittently work in each cycle time of the first frequency, and the motor 5 periodically stores energy in the flywheel 24. Generally, in each cycle time, such as the above 2+4=6 seconds, the energy provided by the continuously running motor 5 and the power consumption of the diaphragm 3 that only works in a part of the time period (such as the above 4 seconds) can maintain a balance, so that the diaphragm pump can continue to operate stably.

[0146] It can be understood that when the valve 11 is closed, the flywheel 24 is engaged with the driving path of the diaphragm 3, and the closing time of the valve = the engagement time of the driving path of the flywheel to the diaphragm. When the valve 11 is opened, the driving path of the flywheel 24 to the diaphragm 3 is disconnected, and the opening time of the valve = the disconnection time of the driving path of the flywheel to the diaphragm. For the convenience of description, the engagement time of the driving path of the flywheel 24 to the diaphragm 3 is referred to as the "engagement time of the driving path", and the disconnection time of the driving path of the flywheel 24 to the diaphragm 3 is referred to as the "disconnection time of the driving path".

[0147] It is not appropriate to adopt the control strategy of S101 when the speed of the motor 5 is very low (for example, just started). Therefore, the control strategy of S101 can be adopted only when it is determined that the speed of the motor 5 is in the set first speed range. That is, during the operation of the motor 5, if it is determined that the current speed of the motor 5 is in the first speed range, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the first frequency.

[0148] The first speed range is preferably a range near the rated speed of the motor 5. For example, if the rated speed of the motor 5 is 10,000 rpm, the first speed range can be selected as a range of 9,000-11,000 rpm.

[0149] Of course, the switching frequency of the valve 11 can also be adjusted accordingly when the motor 5 is in different speed intervals. For example, if it is determined that the speed of the motor 5 is in a second speed interval that is different from and has no intersection with the first speed interval and is smaller than the first speed interval, the valve 11 is alternately opened and closed at a second frequency that is different from the first frequency. That is, if it is determined that the speed of the motor 5 is in the second speed interval, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the second frequency. The difference between the second frequency and the first frequency is mainly reflected in: the ratio of the engagement time and the disconnection time of the flywheel to the diaphragm drive path in each cycle of the second frequency ≠ the ratio of the engagement time and the disconnection time of the flywheel to the diaphragm drive path in each cycle of the first frequency.

[0150] S102, in the process of the control valve 11 being alternately opened and closed at the first frequency in the above S101, if it is detected that the speed of the motor 5 decreases continuously within the first time period, the control valve 11 is alternately opened and closed at a third frequency; wherein the ratio of the closing time period to the opening time period of the valve 11 in each cycle of the third frequency is less than the ratio of the closing time period to the opening time period of the valve 11 in each cycle of the first frequency. The aforementioned first time period is usually several to dozens of times of a single cycle of the first frequency.

[0151] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the first frequency in S101, if it is determined that the rotation speed of the motor 5 is continuously reduced within the first time length, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the third frequency. The ratio of the engagement time length to the disconnection time length of the drive path in each cycle of the third frequency is less than the ratio of the engagement time length to the disconnection time length of the drive path in each cycle of the first frequency.

[0152] During the operation of the motor 5, its speed may change due to certain factors. If it is detected that the speed of the motor 5 decreases continuously within a set longer first time period, such as two minutes, it means that within the first time period, the energy provided by the motor 5 is less than the power consumption of the diaphragm 3. Therefore, it is necessary to reduce the proportion of the working time of the diaphragm 3, or to increase the proportion of the no-load energy storage time of the flywheel 24. Therefore, when it is detected that the speed of the motor 5 decreases continuously within the first time period, the control valve 11 is alternately opened and closed at a third frequency. Among them, the ratio of the engagement time to the disconnection time of the drive path in each cycle of the third frequency is less than the ratio of the engagement time to the disconnection time of the drive path in each cycle of the first frequency.

[0153] For example, the third frequency may be: open valve for 4 seconds - close valve for 2 seconds - open valve for 4 seconds - close valve for 2 seconds - open valve for 4 seconds - close valve for 2 seconds ..., still cyclically opening and closing 10 times per minute. Of course, the third frequency may also be adjusted to cyclically open and close 3 times, 6 times or 20 times per minute, etc.

[0154] Those skilled in the art know that judging whether the speed of the motor 5 decreases continuously within the set first duration can be achieved as follows: in the process of the above-mentioned S101 control valve 11 being alternately opened and closed at the first frequency, the speed of the motor 5 is periodically obtained. If the N motor speeds obtained in N consecutive cycles show a trend of gradually decreasing, and the total duration of the aforementioned N cycles is equal to or greater than the first duration, it means that the speed of the motor 5 decreases continuously within the first duration. In some embodiments, a reduction threshold can also be set. Only when the speed of the motor 5 decreases continuously within the first duration and the reduction value exceeds the set reduction threshold, the control valve 11 is alternately opened and closed at a third frequency. Obviously, this control method of setting a reduction threshold is included in the scope of "if it is detected that the speed of the motor 5 decreases continuously within the first duration, the control valve 11 is alternately opened and closed at a third frequency".

[0155] S103. In the process of the above-mentioned S102 control valve 11 being alternately opened and closed at the third frequency, if it is detected that the rotation speed of the motor 5 continuously decreases within the second time period, the control valve 11 is alternately opened and closed at a fourth frequency; wherein the ratio of the closing time to the opening time of the valve 11 in each cycle of the fourth frequency is less than the ratio of the closing time to the opening time of the valve 11 in each cycle of the third frequency.

[0156] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at a third frequency at S102, if it is determined that the rotational speed of the motor 5 continuously decreases within the second time period, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at a fourth frequency; wherein the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the fourth frequency is less than the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the third frequency.

[0157] The rotation speed of the motor 5 decreases continuously in the second time period, indicating that in the second time period, the energy provided by the motor 5 is still less than the power consumption of the diaphragm 3. Therefore, it is necessary to further reduce the proportion of the working time of the diaphragm 3, or further increase the proportion of the no-load energy storage time of the flywheel 24. Therefore, when it is detected that the rotation speed of the motor 5 continues to decrease continuously in the second time period, the control valve 11 is alternately opened and closed at the fourth frequency.

[0158] For example, at the fourth frequency: open the valve for 5 seconds - close the valve for 1 second - open the valve for 5 seconds - close the valve for 1 second - open the valve for 5 seconds - close the valve for 1 second ..., still 10 cycles per minute. For another example, open the valve for 10 seconds - close the valve for 2 seconds - open the valve for 10 seconds - close the valve for 2 seconds - open the valve for 10 seconds - close the valve for 2 seconds ...

[0159] S104. In the process of the above-mentioned S102 control valve 11 being alternately opened and closed at the third frequency, if it is detected that the rotation speed of the motor 5 continuously increases within the third time length, the control valve 11 is alternately opened and closed at the fifth frequency; wherein, the ratio of the closing time length to the opening time length of the valve 11 in each cycle of the first frequency is greater than the ratio of the closing time length to the opening time length of the valve 11 in each cycle of the fifth frequency is greater than the ratio of the closing time length to the opening time length of the valve 11 in each cycle of the third frequency.

[0160] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the third frequency at S102, if it is determined that the rotational speed of the motor 5 continuously increases within the third time length, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the fifth frequency; wherein, the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the first frequency is greater than the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the fifth frequency is greater than the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the third frequency.

[0161] The speed of the motor 5 increases continuously within the third time period, indicating that within the third time period, the energy provided by the motor 5 is greater than the power consumption of the diaphragm 3. Therefore, the proportion of the working time of the diaphragm 3 can be appropriately increased, or the proportion of the no-load energy storage time of the flywheel 24 can be appropriately reduced to improve the working efficiency of the motor 5. Therefore, when it is detected that the speed of the motor 5 increases continuously within the third time period, the control valve 11 is alternately opened and closed at the fifth frequency.

[0162] Exemplarily, at the fifth frequency: open the valve for 3.5 seconds—close the valve for 2.5 seconds—open the valve for 3.5 seconds—close the valve for 2.5 seconds—open the valve for 3.5 seconds—close the valve for 2.5 seconds….

[0163] S105. In the process of the above-mentioned S101 control valve 11 being alternately opened and closed at the first frequency, if it is detected that the rotation speed of the motor 5 continuously increases within the fourth time length, the control valve 11 is alternately opened and closed at a sixth frequency; wherein, the ratio of the closing time length to the opening time length of the valve 11 in each cycle of the sixth frequency is greater than the ratio of the closing time length to the opening time length of the valve 11 in each cycle of the first frequency.

[0164] That is, in the process of S101 controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at a first frequency, if it is determined that the rotational speed of the motor 5 continues to increase within the fourth time length, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at a sixth frequency; wherein the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the sixth frequency is greater than the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the first frequency.

[0165] The rotation speed of the motor 5 decreases continuously in the fourth time period, indicating that in the fourth time period, the energy provided by the motor 5 is greater than the power consumption of the diaphragm 3. Therefore, the proportion of the working time of the diaphragm 3 can be increased, or the proportion of the no-load energy storage time of the flywheel 24 can be shortened to improve the working efficiency of the motor 5. Therefore, when it is detected that the rotation speed of the motor 5 decreases continuously in the fourth time period, the control valve 11 is alternately opened and closed at the sixth frequency.

[0166] Exemplarily, the sixth frequency may be: open the valve for 4 seconds - close the valve for 11 seconds - open the valve for 4 seconds - close the valve for 11 seconds - open the valve for 4 seconds - close the valve for 11 seconds ... , with 4 cycles per minute.

[0167] S106, in the process of the control valve 11 being alternately opened and closed at the sixth frequency in S105, if it is detected that the rotation speed of the motor 5 increases continuously within the fifth duration, the control valve 11 is alternately opened and closed at the seventh frequency. The ratio of the closing duration to the opening duration of the valve 11 in each cycle of the seventh frequency is greater than the ratio of the closing duration to the opening duration of the valve 11 in each cycle of the sixth frequency.

[0168] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the sixth frequency at S105, if it is determined that the rotational speed of the motor 5 continues to increase within the fifth time period, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the seventh frequency; wherein the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the seventh frequency is greater than the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the sixth frequency.

[0169] The speed of the motor 5 increases continuously in the fifth time period, indicating that in the fifth time period, the energy provided by the motor 5 is still greater than the power consumption of the diaphragm 3. Therefore, the proportion of the working time of the diaphragm 3 can be further increased, or the proportion of the no-load energy storage time of the flywheel 24 can be further reduced, thereby further improving the working efficiency of the motor 5. Therefore, when it is detected that the speed of the motor 5 continues to decrease continuously in the fifth time period, the control valve 11 is alternately opened and closed at the seventh frequency.

[0170] Exemplarily, at the seventh frequency: open the valve for 4 seconds—close the valve for 12 seconds—open the valve for 4 seconds—close the valve for 12 seconds—open the valve for 4 seconds—close the valve for 12 seconds….

[0171] S107. In the process of the above-mentioned S105 control valve 11 being alternately opened and closed at the sixth frequency, if it is detected that the rotation speed of the motor 5 continuously decreases within the sixth time period, the control valve 11 is alternately opened and closed at the eighth frequency; wherein, the ratio of the closing time period to the opening time period of the valve 11 in each cycle of the sixth frequency is greater than the ratio of the closing time period to the opening time period of the valve 11 in each cycle of the eighth frequency and greater than the ratio of the closing time period to the opening time period of the valve 11 in each cycle of the first frequency.

[0172] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the sixth frequency at S105, if it is determined that the rotational speed of the motor 5 continuously increases within the sixth time period, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the eighth frequency; wherein, the ratio of the engagement time to the disconnection time of the drive path in each cycle of the sixth frequency is greater than the ratio of the engagement time to the disconnection time of the drive path in each cycle of the eighth frequency is greater than the ratio of the engagement time to the disconnection time of the drive path in each cycle of the first frequency.

[0173] The speed of the motor 5 decreases continuously in the sixth time period, indicating that in the sixth time period, the energy provided by the motor 5 is less than the power consumption of the diaphragm 3. Therefore, the working time ratio of the diaphragm 3 can be appropriately reduced, or the no-load energy storage time ratio of the flywheel 24 can be appropriately increased. Therefore, when it is detected that the speed of the motor 5 increases continuously in the sixth time period, the control valve 11 is alternately opened and closed at the eighth frequency.

[0174] Exemplarily, at the eighth frequency: open the valve for 4 seconds—close the valve for 10 seconds—open the valve for 4 seconds—close the valve for 10 seconds—open the valve for 4 seconds—close the valve for 10 seconds….

[0175] S108, if it is detected that the rotation speed of the motor 5 is less than the first rotation speed threshold, the control valve 11 is continuously opened; wherein the first rotation speed threshold is less than the lower limit of the first rotation speed range.

[0176] That is, if it is determined that the rotation speed of the motor 5 is less than a first relatively small rotation speed threshold, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be continuously disconnected.

[0177] The first speed threshold is a relatively small value, which is smaller than the lower limit of the first speed range. When the speed of the motor 5 is smaller than the first speed threshold, it means that the energy of the motor 5 and the flywheel 24 is seriously insufficient, so the valve 11 can be kept open at this time to keep the driving path of the flywheel 24 to the diaphragm 3 in a disconnected state to avoid serious overload of the motor 5.

[0178] S109, during the process of the control valve 11 being continuously opened in the above S108, if it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold, the control valve 11 is continuously closed; wherein the second rotation speed threshold is not less than the above first rotation speed threshold.

[0179] That is, in the process of controlling the flywheel 24 to continuously disconnect the driving path to the diaphragm 3, if it is determined that the speed of the motor 5 is greater than the second speed threshold, the flywheel 24 is controlled to continuously engage the driving path to the diaphragm 3; wherein the second speed threshold is not less than the first speed threshold.

[0180] It can be understood that after executing the above S108, the flywheel 24 always remains in a no-load energy storage state, and the energy provided by the motor 5 is completely converted into the kinetic energy of the flywheel 24. When the speed of the motor 5 and the flywheel 24 is high enough and the kinetic energy is large enough, if the valve 11 is still kept in an open state, the diaphragm pump runs at no load, resulting in energy waste. Therefore, when it is detected that the speed of the motor 5 is greater than the second speed threshold, the valve 11 can be switched from a continuously open state to a continuously closed state, so that the flywheel 24 is continuously engaged with the driving path of the diaphragm 3, so that the flywheel 24 continuously drives the diaphragm 3 to do work.

[0181] It can be understood that in the present application, the "continuous" in "continuously open" and "continuously closed" and the "alternately" in "alternately open and close" are relative concepts. Continuously open means keeping the valve in an open state, and continuously closed means keeping the valve in a closed state; and alternately opening and closing the valve means periodically opening the valve for a preset time and closing the valve for a preset time according to a set frequency.

[0182] It is understandable that the execution of S109 is not necessarily based on S108. In other embodiments, no matter what working state the valve 11 is in at this time, as long as it is detected that the speed of the motor 5 is greater than the second speed threshold, the valve 11 can be controlled to be continuously closed.

[0183] The second speed threshold should not be less than the first speed threshold, and the second speed threshold is preferably a value that is not within the first speed range. More preferably, the second speed threshold is a value greater than the upper limit of the first speed range.

[0184] Obviously, during the process of the above-mentioned S109 controlling the valve 11 to be continuously closed, if it is detected that the rotation speed of the motor 5 returns to the aforementioned first rotation speed range, the valve 11 can be controlled to continue to be alternately opened and closed at the first frequency.

[0185] In addition, we can also abandon the above strategies of S101-S107 and use the strategies of S108 and S109 alone to control the diaphragm pump:

[0186] That is, if it is determined that the speed of the motor 5 is less than the first speed threshold, the drive path of the flywheel 24 to the diaphragm 3 is continuously disconnected. If it is determined that the speed of the motor 5 is greater than the second speed threshold, the drive path of the flywheel 24 to the diaphragm 3 is continuously engaged; wherein the second speed threshold is not less than the first speed threshold. In this control mode of using S108 and S109 strategies alone, the second speed threshold can usually be equal to the first speed threshold. The disadvantage is that the speed of the motor 5 will be very unstable.

[0187] like Fig.10As shown, in order to better implement the control strategy of S101-S109 above, the valve 11 of this embodiment adopts an electrically controlled valve that can be opened and closed electrically, and is also configured with a motor speed sensor 34 for detecting the speed of the motor 5. The motor speed sensor 34 and the valve 11 are both connected to the controller 35 for communication. The controller 35 is used to obtain the speed of the motor 5 from the motor speed sensor 34, and control the opening and closing of the valve 11 based on the speed to implement the above control method. It is necessary to point out that the opening and closing of the control valve 11 may not be based on the speed of the motor 5. In other embodiments of the present application, the motor speed sensor 34 is removed, and only the controller 35 connected to the valve 11 for communication is used to control the valve 11 to "alternately open and close at a first frequency".

[0188] Specifically, the controller 35 includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor. When the computer instructions are executed by the processor, the various control methods mentioned above are implemented.

[0189] for example:

[0190] During the operation of the motor 5, the controller 35 obtains the speed of the motor 5 from the motor speed sensor 34;

[0191] If it is determined that the rotation speed of the motor 5 is in the first rotation speed range, the controller 35 sends a control instruction to the electrically controlled valve 11, so that the control valve 11 is alternately opened and closed at a first frequency.

[0192] For example:

[0193] During the operation of the motor 5, the controller 35 obtains the speed of the motor 5 from the motor speed sensor 34;

[0194] If it is determined that the speed of the motor 5 is less than the first speed threshold, the controller 35 sends a command signal to the electrically controlled valve 11 to control the valve 11 to be continuously opened;

[0195] If it is determined that the speed of the motor 5 is greater than the second speed threshold, the controller 35 sends different command signals to the electrically controlled valve 11 to control the valve 11 to be continuously closed; wherein the second speed threshold is not less than the above-mentioned first speed threshold.

[0196] For example:

[0197] During the operation of the motor 5 , the controller 35 receives a user instruction (eg, pressing an operation button connected to the controller) to cause the valve 11 to open and close alternately at a first frequency.

[0198] In the description of the above control method, "opening" the valve 11 generally includes two situations: 1) If the valve 11 is originally in a closed state, the controller 35 sends a command signal to the valve 11 to control the valve 11 to switch to an open state. 2) If the valve 11 is already in an open state, such as a normally open valve, the controller 35 may do nothing with the valve 11, or send a command signal to the valve 11 to make the valve 11 open.

[0199] Similarly, "closing" the valve 11 generally includes two situations: 1) If the valve 11 is originally in an open state, the controller 35 sends a command signal to the valve 11 to control the valve 11 to switch to a closed state. 2) If the valve 11 is originally in a closed state, such as if the valve 11 is a normally closed valve, the controller 35 may do nothing with the valve 11, or send a command signal to the valve 11 to make the valve 11 close.

[0200] Therefore, if the valve 11 is a normally closed valve, "controlling the valve 11 to open and close alternately at a first frequency" can be achieved as follows: the controller 35 sends and stops sending the command signal to open the valve to the valve 11 alternately at the first frequency. When the controller 35 sends the command signal to open the valve 11, the valve 11 opens; when the controller 35 stops sending the command signal to open the valve 11, the valve 11 automatically closes. The controller 35 stops sending the command signal to open the valve 11, allowing the normally closed valve 11 to close automatically, which also falls within the scope of "controlling the valve to close" as mentioned in this application. The only special thing is that it "controls" the valve 11 to close by stopping sending the relevant signal or by inaction.

[0201] The valve 11 is generally a solenoid valve. To simplify control, the valve 11 is preferably a normally closed valve or a normally open valve.

[0202] Those skilled in the art can understand that obtaining the speed information of the motor 5 is one of the conditions for smoothly implementing the above-mentioned S101-S109 control method. For example, the speed of the motor 5 can be obtained in real time during the operation of the motor 5. Once it is determined that the motor speed meets the corresponding conditions, the control valve 11 makes a corresponding response action - for example, when it is determined that the motor speed is in a preset first speed range, the control valve 11 is alternately opened and closed at a first frequency, and when it is determined that the motor speed is greater than a preset second speed threshold, the control valve 11 is continuously opened.

[0203] As mentioned above, one of the reasons why the motor 5 is allowed to work externally only when it is running at high speed is that the flywheel 24 is also in a high-speed motion state at this time, and has a large kinetic energy. The flywheel 24 that stores a large amount of kinetic energy at high speed can work externally with high power. Therefore, we can increase the mass of the flywheel 24 appropriately, preferably more than 5kg, to increase the kinetic energy of the flywheel 24 at high speed, and the mass of the flywheel 24 further increases the short-term power of the diaphragm pump.

[0204] The flywheel 24 is generally made of metal or carbon fiber.

[0205] Some motors 5 have low output power when just started or running at low speed. Only when the speed of the motor 5 reaches a certain value, can it have considerable output power. This is one of the reasons why we adopt the above design.

[0206] It is not difficult to understand that even when the motor 5 is running at high speed, its power is not significantly improved. As long as the kinetic energy of the flywheel 24 is large enough at this time, it can do high-power work outward only by relying on the inertia of the flywheel 24. The kinetic energy of the flywheel 24 mainly comes from its speed, and the upper limit of the speed of the flywheel 24 depends on the motor 5, so we can select the above-mentioned motor 5 as a high-speed motor with a rated speed of not less than 10000r / min. Of course, the speed of the transmission system and the piston 4 cannot be too fast, otherwise it is easy to cause mechanical damage. Therefore, when the rated speed of the motor 5 is relatively large, it is preferred to configure a reducer 12 in the transmission system, which can reduce mechanical damage on the one hand, and increase the driving force on the diaphragm 3 on the other hand.

[0207] It should be noted that the motor speed sensor 34 can directly detect the speed of the motor 5, or indirectly obtain the speed of the motor 5 by detecting the speed of other components that are transmission-connected to the motor 5, such as directly detecting the speed of the flywheel 24 or the reducer 12 or the crankshaft 13 described below to indirectly obtain the speed of the motor 5. Even more, the speed of the motor 5 can be indirectly determined by detecting other physical quantities associated with the motor speed. As long as the relevant physical quantities detected by such sensors are highly correlated with the speed of the motor 5, they can be regarded as motor speed sensors. The motor speed sensor 34 can detect the speed of the motor 5 directly or indirectly, and this application does not limit this.

[0208] In this embodiment, the power fluid storage chamber 10 is arranged above the power chamber 2, so that when the valve 11 is in the open state, the power fluid b (hydraulic oil) in the power fluid storage chamber 10 automatically flows into the power chamber 2 whose volume becomes larger (when the piston retracts) under the action of its own gravity, so that the transmission of the power fluid b between the power fluid storage chamber 10 and the power chamber 2 is smoother.

[0209] The power fluid storage chamber 10 is specifically formed in a square oil tank.

[0210] The transmission system for connecting the piston 4 and the motor 5 adopts a crankshaft connecting rod structure, which is as follows:

[0211] Reference Figure 1 , Figure 3 and Figure 4As shown, the transmission system includes the flywheel 24, the reducer 12, the crankshaft 13, the first connecting rod 14, the second connecting rod 15 and the push-pull rod 16 arranged in sequence along the transmission direction. Among them, the input shaft of the reducer 12 is connected to the output shaft of the motor 5 through the coupling 25, and the output shaft of the reducer 12 is connected to one end of the crankshaft 13 through the coupling 25. The other end of the crankshaft 13 is pivotally supported on the housing 33 of the diaphragm pump. One end of the first connecting rod 14 is pivotally connected to the curved part of the crankshaft 13, and the other end is pivotally connected to one end of the second connecting rod 15 through the pivot 22. The other end of the second connecting rod 15 is pivotally connected to the push-pull rod 16 through the second pivot 22. The other end of the push-pull rod 16 is fixedly connected to the piston 4, and of course, the aforementioned other end of the push-pull rod 16 can also be pivotally connected to the piston 4.

[0212] The crankshaft 13, the first connecting rod 14, the second connecting rod 15 and the push-pull rod 16 are accommodated in a transmission chamber 17 formed in the housing 33. The push-pull rod 16 is a linear rod extending left and right (ie, extending linearly along the movement direction of the piston 4).

[0213] Refer to Figure 1 As shown, in order to ensure that during operation, the pivot 22 pivotally connecting the second connecting rod 15 and the push-pull rod 16 can only be Figure 1 In this embodiment, a guide seat 23 is fixedly arranged in the transmission cavity 17, and a guide seat 23 is formed on the guide seat 23. Figure 1 A guide groove 23a is provided in the middle and extends back and forth perpendicularly to the paper surface (perpendicularly to the movement direction of the piston), and the pivot 22 pivotally connecting the second connecting rod 15 and the push-pull rod 16 is slidably arranged in the guide groove 23a.

[0214] In this embodiment, the guide seat 23 is integrally connected with the housing 33 of the diaphragm pump, that is, the guide seat 23 is integrally formed in the housing 33. Figure 1 and Figure 4 Of course, the guide seat 23 can also be an independent component connected to the housing 33 separately, such as Figure 5 .

[0215] During operation, the motor 5 drives the crankshaft 13 to pivot around the pivot axis O through the reducer 12. The crankshaft 13 drives one end of the first connecting rod 14 to rotate (orbit) around the pivot axis O of the crankshaft. The other end of the first connecting rod 14 drives one end of the second connecting rod 15 to reciprocate along the guide groove 23a. The other end of the second connecting rod 15 drives the push-pull rod 16 to move back and forth along the guide groove 23a. Figure 1 Move back and forth in the left and right directions.

[0216] Obviously, the above structural design is also applicable to a diaphragm compressor for compressing a working fluid.

[0217] In many application scenarios, when the piston 4 of the diaphragm pump or diaphragm compressor moves toward the diaphragm 3, the volume of the working chamber 1 becomes smaller and smaller. When the working fluid a in the working chamber is not discharged or cannot be discharged in time during this process, the internal pressure of the working chamber becomes larger and larger (especially when the gaseous fluid in the working chamber is compressed). Therefore, the reaction force exerted by the power fluid b on the piston 4 in the direction away from the diaphragm 3 becomes larger and larger, which requires the push-pull rod 16 to be able to provide more and more driving force to the piston 4 to ensure the normal operation of the diaphragm pump or diaphragm compressor, which puts higher requirements on the output power of the motor 5. The clever thing is that even if the output power and especially the output torque of the motor 5 in this embodiment do not change during this process, the driving force exerted by the push-pull rod 16 on the piston 4 can become larger and larger during the process of the piston 4 moving to the right, which is perfectly adapted to the aforementioned application scenarios. The specific analysis is as follows:

[0218] like Figure 6 And refer to Figure 4 and Figure 5 As shown, the acute angle between the second connecting rod 15 and the push-pull rod 16 is α, and the angle between the curved portion of the crankshaft 13 and the horizontal plane is β. Figure 5 β=0. When the crankshaft 13 is in this Figure 6 When the crankshaft 13 rotates clockwise around its pivot axis O, the curved portion of the crankshaft 13 will drive the left end of the second connecting rod 15 to move downward through the first connecting rod 14, and then push the push-pull rod 16 to move to the right. During this process, the angle β gradually increases and the angle α gradually decreases. When the reduction ratio of the reducer 12 is fixed, the transmission ratio from the motor 5 to the crankshaft 13 is a certain value, so every time the motor 5 rotates an angle, β changes the corresponding angle value in the same proportion. In any equal short time, △β (i.e., the change value of β) is the same. Through simple geometric analysis, it can be estimated that: in the curved portion of the crankshaft 13, Figure 5 On the one hand, the angle β increases uniformly from zero to 90° (Π / 2). Correspondingly, in the first stage, the downward movement speed of the lower end of the first connecting rod 14 (or the left end of the second connecting rod 15) gradually increases until the first connecting rod 14 and the curved part of the crankshaft (i.e. Figure 6 When the portion indicated by the reference numeral 13 in the figure is approximately vertical, the downward movement speed of the lower end of the first connecting rod 14 reaches the maximum; thereafter, in the second stage, the downward movement speed of the lower end of the first connecting rod 14 becomes smaller and smaller. Figure 6When the first connecting rod 14 and the crankshaft are in a straight line, the instantaneous downward movement speed of the lower end of the first connecting rod 14 drops to zero, and the piston 4 moves to the right extreme position; afterwards, in the third stage, the lower end of the first connecting rod 14 moves upward, driving the piston 4 to retreat to the left. It can be seen that in the second half of the period before the piston 4 moves right to the extreme position, that is, the aforementioned second stage, the downward movement speed of the lower end of the first connecting rod 14 is getting smaller and smaller. On the other hand, in the aforementioned first and second stages, the angle α is always gradually reduced. Correspondingly, even if the lower end of the first connecting rod 14 and the left end of the second connecting rod 15 move downward at a uniform speed, when the angle α becomes smaller and smaller, the rightward movement speed of the push-pull rod 16 will inevitably slow down gradually, not to mention that in the second stage, the downward movement speed of the left end of the second connecting rod 15 gradually slows down, so in the second stage, the rightward movement speed of the piston 4 will decrease, and the second stage happens to be the second half of the period when the piston 4 moves right.

[0219] In order to make the readers understand the above inference more intuitively, refer to Figure 6 As shown, in this Figure 6 In the figure, points O, A, B, C, D, and E respectively represent the pivot axis of the crankshaft 13, the transition point between the first connecting rod 14 and the crankshaft curved part, the transition point between the first connecting rod 14 and the second connecting rod 15, the transition point between the second connecting rod 15 and the push-pull rod 16, the position point on the guide slot 23a that is flush with the transition point between the second connecting rod and the push-pull rod in the direction of piston movement, and the position point on the guide slot 23a that is flush with the crankshaft pivot axis in the direction of piston movement. OA is the known radial dimension of the upper curved part of the crankshaft 13, that is, the distance from the transition point between the first connecting rod 14 and the crankshaft 13 to the crankshaft pivot axis O. AB is the known length of the first connecting rod 14. BC is the known length of the second connecting rod 15. DE is known in length, and EO is known in length.

[0220] Assume that the angle between the curved portion of the crankshaft 13 and the horizontal plane is β.

[0221] Through geometric calculations, we know that the length of CD is:

[0222]

[0223] By taking the derivative of equation (1), we can see that when β is in the range of 0 to Π / 2, the rate of change of CD length is:

[0224]

[0225] Assuming AO = 2, E0 = 2, AB = 8, BC = 8, DE = 10, according to the above equation (2), it can be concluded that the rate of change of CD length, that is, the speed of piston 4, and the relationship between the angle β are as follows: Figure 8 , from the Figure 8It is not difficult to see that: as β gradually increases in the range of 0 to Π / 2, the speed at which CD lengthens becomes slower and slower, that is, the transmission ratio from motor 5 to piston 4 becomes smaller and smaller (the reduction ratio becomes larger and larger), and the speed at which piston 4 moves right becomes slower and slower. When the output power of motor 5 is constant, the driving force on piston 4 becomes larger and larger, which confirms the above inference. Figure 8 It can be seen that the piston 4 maintains a very low operating speed for a long period of time before reaching the right limit position. This is perfectly compatible with many working conditions of diaphragm pumps or diaphragm compressors, especially diaphragm compressors, in actual applications. For example, a diaphragm compressor of this structure is used in an air-conditioning system to compress the gaseous refrigerant into a high-pressure state or even a liquid state and then discharge it from the discharge valve 9. Obviously, during the refrigerant discharge process, the diaphragm 3 only needs to provide a relatively stable thrust to push the refrigerant in the working chamber 1 out, and the driving force applied by the push-pull rod 16 to the piston 4 does not need to be greatly increased. This working condition is consistent with Figure 8 The curve perfectly matches the speed reduction ratio of the final stage, which does not decrease sharply but decreases relatively gently, and the piston basically maintains a reasonable and relatively gentle speed. In this way, the compressed refrigerant in the working chamber can be discharged faster without reducing the piston driving force, which helps to improve work efficiency.

[0226] In addition, we also obtain the relationship between the velocity of the lower end of the first connecting rod 14 (i.e., point B) and the angle β through geometric calculation as shown in the figure below: Figure 7 It is not difficult to see that the running speed of the lower end of the first connecting rod 14 first increases, then decreases, and finally moves upward in the opposite direction, which also confirms the above estimation.

[0227] In order to make better use of the above characteristics, Figure 6 In the embodiment, when the crankshaft rotates 360°, it is preferable to ensure that the left end (point B) of the second connecting rod 15 always moves back and forth above or flush with the second connecting rod and the push-pull rod transition part (point C), that is, point B always moves on the same side of the straight line CD (including the overlap of point B and straight line CD). Straight line CD is a straight line parallel to the movement direction of the piston 4 and passing through point C. In other words, point B is always on the same side of the straight line passing through point C and parallel to the movement direction of the piston 4 ( Fig. 9 ) moves to the upper side of the

[0228] Obviously, if the radial dimension of the curved portion of the crankshaft 13 ( Figure 6 The sum of the length of A0, that is, the distance between the first connecting rod and the crankshaft connecting part and the pivot axis) and the length of the first connecting rod 14 is not greater than the length of ED, which will inevitably enable the above functions to be achieved.

[0229] It can be seen that the transmission system is more effective when the piston 4 performs work ( Figure 1In the latter part of the working action (moving to the right in the middle), the greater the reduction ratio is, the greater the rightward driving force received by the piston 4 is in the latter part of the working action, and the driving force received by the piston 4 can be maintained at a (relatively stable) large value for a long time before the piston reaches the working limit position, which is perfectly adapted to many working conditions of diaphragm pumps and diaphragm compressors in actual applications.

[0230] Furthermore, in this embodiment, the guide groove 23a and the pivot axis O are arranged in the same plane and the two are perpendicular to each other, that is, Figure 6 The distance between point E and point O is zero. Fig. 9 When the first connecting rod 14 rotates to the lowest point, the curved part of the first connecting rod 14 and the crankshaft 13 are just in a straight line. Fig. 9 The sum of the radial dimension of the middle crankshaft curved portion and the length of the first connecting rod 14 is set to be equal to the vertical distance between the pivot axis and the second connecting rod and the push-pull rod transition point. In this way, when the curved portion of the crankshaft 13 rotates toward the second connecting rod 15 and is on the same straight line as the first connecting rod 14 ( Fig. 9 The first connecting rod 14 is exactly perpendicular to the second connecting rod 15, and the second connecting rod 15 is exactly parallel to the movement direction of the piston 4. This helps to improve the compactness of the transmission system.

[0231] In order to improve the adaptability of the diaphragm 3 to deform leftward and rightward, and thus to increase the service life of the diaphragm 3, the diaphragm 3 of this embodiment is integrally provided with an annular diaphragm deformation fold 3a protruding rightward in the thickness direction of the diaphragm.

[0232] The main purpose of the operation of the motor 5 is to provide driving force for the diaphragm 3 to drive the diaphragm 3 to move, thereby squeezing and extracting the working fluid. The piston 4 and the transmission system including the flywheel 24 connecting the motor and the piston are arranged on the driving path for the motor 5 to transmit the driving force to the diaphragm 3. The piston 4 and the transmission system connecting the motor and the piston are all components of the driving path of the motor 5 to the diaphragm 3. Among them, the crankshaft 13 is located on the transmission downstream side of the reducer 12, the first connecting rod 14 is located on the transmission downstream side of the crankshaft 13, the second connecting rod 15 is located on the transmission downstream side of the first connecting rod 14, and the piston 4 is located on the transmission downstream side of the transmission system.

[0233] The power fluid b filled in the power chamber 2 is also arranged on the driving path for the motor 5 to transmit the driving force to the diaphragm 3, and has the function of transmitting the driving force to the diaphragm 3. Therefore, the power fluid b filled in the power chamber 2 is also a component of the driving path from the motor 5 (or flywheel 24, or piston 4) to the diaphragm 3.

[0234] Furthermore, the deformation fold 3a of the diaphragm is a circular ring structure to adapt to the deformation characteristics of the diaphragm 3 to the left and right. The diaphragm 3 is composed of a first part accommodated in the working chamber 1 and the power chamber 2 and a second part located outside the working chamber 1 and the power chamber 2, and the deformation fold 3a of the diaphragm is specifically formed on the first part.

[0235] The deformation folds 3a of the diaphragm are arranged close to the outer edge of the first part of the diaphragm so that the enclosed area of ​​the deformation folds 3a of the diaphragm is as large as possible. The purpose of such arrangement is to increase the deformation amount of the diaphragm 3 to the left and right, thereby increasing the squeezing amount of the working fluid.

[0236] The enclosed area of ​​the deformed folds 3a of the diaphragm is preferably not less than 80% of the area of ​​the first portion of the diaphragm.

[0237] Embodiment 2:

[0238] Fig.14 and Fig.15 A second diaphragm pump is shown, the structure of which is basically the same as that of the first embodiment, with the following main differences:

[0239] This embodiment further optimizes the structure of the transmission system. Fig.14 and Fig.15 As shown, the transmission system includes a flywheel not shown in the figure, a reducer not shown in the figure, a crankshaft 13, two connecting rods (respectively a first connecting rod 14 and a second connecting rod 15), a parallelogram, and a push-pull rod 16, which are arranged in sequence along the transmission direction (or power transmission direction). Among them: the input shaft of the reducer is connected to the output shaft of the motor through a coupling, and the output shaft of the reducer is connected to one end of the crankshaft 13 through a coupling. The other end of the crankshaft 13 is pivotally supported on the housing 33 of the diaphragm pump. The parallelogram consists of a third connecting rod 18, a fourth connecting rod 19, a fifth connecting rod 20, and a sixth connecting rod 21, which are pivotally connected in sequence along the circumferential direction. The transition portion (i.e., the pivot connection portion) between the third connecting rod 18 and the fourth connecting rod 19, the transition portion between the fourth connecting rod 19 and the fifth connecting rod 20, the transition portion between the fifth connecting rod 20 and the sixth connecting rod 21, and the transition portion between the sixth connecting rod 21 and the third connecting rod 18 respectively constitute the four vertices of the parallelogram. One end of the first connecting rod 14 is pivotally connected to the curved portion of the crankshaft 13, and the other end is connected to the transition portion of the third connecting rod 18 and the fourth connecting rod 19. One end of the second connecting rod 15 is pivotally connected to another curved portion of the crankshaft 13, and the other end is connected to the transition portion of the fifth connecting rod 20 and the sixth connecting rod 21. One end of the push-pull rod 16 is connected to the transition portion of the fourth connecting rod 19 and the fifth connecting rod 20, and the other end is connected to the piston 4.

[0240] During operation, the motor 5 drives the crankshaft 13 to rotate through the reducer. The crankshaft 13 drives one end of the first connecting rod 14 and the second connecting rod 15 to rotate (revolve) around the pivot axis of the crankshaft. The other ends of the first connecting rod 14 and the second connecting rod 15 drive the upper and lower vertices of the parallelogram to rotate. Fig.14 The parallel four-link periodically approaches and moves away from Fig.14 The horizontal dimension in the middle periodically extends and shortens, thereby driving the piston 4 through the push-pull rod 16. Fig.14 Move back and forth in the left and right directions.

[0241] Refer to Fig.16 As shown, specifically, the third link 18 and the fourth link 19, the fourth link 19 and the fifth link 20, the fifth link 20 and the sixth link 21, and the sixth link 21 and the third link 18 are all pivotally connected through corresponding pivots 22. The “other end” of the first link 14 is specifically connected to the pivot 22 pivotally connected to the third link 18 and the fourth link 19, the “other end” of the second link 15 is specifically connected to the pivot 22 pivotally connected to the fifth link 20 and the sixth link 21, and one end of the push-pull rod 16 is connected to the pivot 22 pivotally connected to the fourth link 19 and the fifth link 20.

[0242] It is not difficult to understand that during operation, the vertical component of the thrust or pull of the push-pull rod 16 by the fourth connecting rod 19 is always in the opposite direction to the vertical component of the thrust or pull of the push-pull rod 16 by the fifth connecting rod 20. The total vertical force applied by the parallelogram linkage to the push-pull rod 16 is small or even zero, thereby reducing the radial external force applied by the push-pull rod 16 to the piston 4, thereby improving the piston 4 and Fig.14 and Fig.15 The service life of the piston and cylinder sleeve (in this embodiment, the piston and cylinder sleeve is the main component used to form the power chamber) shown but not marked in the figure reduces the possibility or severity of oil leakage at the fitting point between the piston 4 and the power chamber 2.

[0243] In order to ensure that during the operation, the vertical component of the thrust or pull of the push-pull rod 16 by the fourth connecting rod 19 is always completely offset to zero by the vertical component of the thrust or pull of the push-pull rod 16 by the fifth connecting rod 20, so that the driving force exerted on the piston 4 is always parallel to the inner wall surface of the power chamber, in this embodiment, the lengths of the third connecting rod 18, the fourth connecting rod 19, the fifth connecting rod 20 and the sixth connecting rod 21 are set to be equal, so that the parallelogram linkage has a diamond structure, and one diagonal of the diamond parallelogram linkage is parallel to the movement direction of the piston 4.

[0244] Furthermore, the first connecting rod 14 and the second connecting rod 15 have the same length, so that the parallel four-bar transmission structure runs more smoothly.

[0245] It is not difficult to understand that the structural combination formed by the crankshaft 13, the first connecting rod 14, the fourth connecting rod 19 and the push-pull stem 16 in the transmission system of this embodiment is similar to that of the first embodiment. Figure 6 or Fig. 9 The structural combination is basically the same, and the motion trajectory during operation is also basically the same, so the transmission system in this embodiment also has the same transmission characteristics as the transmission system in Example 1: the later the piston 4 moves to the right to do work, the greater the reduction ratio from the motor 5 to the piston 4, and the greater the driving force exerted on the piston 4.

[0246] In addition, this embodiment is also configured with a linear bearing 28 sleeved on the outside of the push-pull rod 16. The linear bearing 28 is fixed to the housing 33 of the diaphragm pump. The linear bearing 28 supports and guides the reciprocating motion of the push-pull rod 16, further improving the service life of the piston 4.

[0247] In order to better convert the rotational motion of the crankshaft 13 into the left-right translation of the push-pull rod 16, the present embodiment fixes (or pivots) the pivot 22 pivotally connecting the third connecting rod 18 and the sixth connecting rod 21 to the housing 33 of the diaphragm pump. When the crankshaft 13 drives the parallel four-link to expand and close through the first connecting rod 14 and the second connecting rod 15, the pivot 22 pivotally connecting the third connecting rod 18 and the sixth connecting rod 21 remains in a constant relative position with the housing 33, so that the pivot 22 pivotally connecting the fourth connecting rod 19 and the fifth connecting rod 20 translates to the left or right, thereby driving the piston 4 to translate to the left and right, as shown in FIG. Fig.14 and Fig.15 shown.

[0248] Embodiment three:

[0249] The difference between the diaphragm pump of this embodiment and the second embodiment is only the structure of the transmission system, which is as follows:

[0250] like Fig.17 and Fig.18 As shown, the transmission system of the diaphragm pump of this embodiment includes: a flywheel and a reducer not shown in the figure, a crankshaft 13, a first connecting rod 14, a second connecting rod 15, a third connecting rod 18, a fourth connecting rod 19 and a push-pull rod 16. The input shaft of the reducer is connected to the output shaft of the motor not shown in the figure through a coupling, and the output shaft of the reducer is connected to one end of the crankshaft 13 through a coupling. The other end of the crankshaft 13 is pivotally supported on the housing 33 of the diaphragm pump. One end of the first connecting rod 14, i.e. Fig.18 The upper end of the crankshaft 13 is pivotally connected to the curved portion of the crankshaft 13, and the other end is Fig.18 The lower end of the middle and one end of the third connecting rod 18, that is, Fig.18 The left end of the second connecting rod 15 is pivotally connected by a pivot 22. Fig.18 The upper end of the crankshaft is pivotally connected to the other curved portion of the crankshaft 13, and the other end is Fig.18The lower end of the fourth connecting rod 19 is connected to one end of the fourth connecting rod 19. Fig.16 The left end of the third connecting rod 18 is pivotally connected by a pivot 22. The other end of the third connecting rod 18 is Fig.16 The right end of the fourth connecting rod 19 and the other end of the fourth connecting rod 19 Fig.16 The right end of the push-pull rod 16 is pivotally connected by a pivot 22. One end of the push-pull rod 16 is connected to the pivot 22 pivotally connected to the third connecting rod 18 and the fourth connecting rod 19, and the other end is connected to the piston 4. In order to convert the rotational motion of the crankshaft 13 into the left and right translation of the push-pull rod 16, a guide seat 23 fixed (fixed to the housing 33) in the transmission chamber is also configured. The guide seat 23 is formed with a vertically extending guide groove 23a, such as Fig.18 The pivot 22 pivotally connecting the third link 18 and the first link 14 and the pivot 22 pivotally connecting the fourth link 19 and the second link 15 are both slidably arranged in the aforementioned guide slot 23a, so that the two pivots 22 can only move up and down (approach or move away from each other) along the guide slot 23a.

[0251] During operation, the motor drives the crankshaft 13 to rotate through the reducer. The crankshaft 13 drives the upper ends of the first connecting rod 14 and the second connecting rod 15 to rotate around the pivot axis of the crankshaft. The lower end of the first connecting rod 14 and the lower end of the second connecting rod 15 respectively drive the left end of the third connecting rod 18 and the left end of the fourth connecting rod 19 to move up and down, so that the left end of the third connecting rod 18 and the left end of the fourth connecting rod 19 are vertically close to or away from each other, thereby causing the push-pull rod 16 and the piston 4 to move left and right.

[0252] It is not difficult to understand that during the working process, the vertical component of the thrust or pull of the push-pull rod 16 by the third connecting rod 18 is always in the opposite direction to the vertical component of the thrust or pull of the push-pull rod 16 by the fourth connecting rod 19, and the total vertical force on the push-pull rod 16 is small or even zero, thereby reducing the radial force exerted by the push-pull rod 16 on the piston 4, thereby improving the piston 4 and Fig.17 The service life of the piston and cylinder sleeve (in this embodiment, the piston and cylinder sleeve is the main component used to form the power chamber) shown but not marked in the figure reduces the oil leakage problem at the matching point between the piston 4 and the power chamber 2.

[0253] In order to ensure that during the operation, the vertical component of the thrust or pull force exerted by the third connecting rod 18 on the push-pull rod 16 is always completely offset to zero by the vertical component of the thrust or pull force exerted by the fourth connecting rod 19 on the push-pull rod 16, so that the driving force exerted on the piston 4 is always parallel to the inner wall surface of the power chamber 2, the lengths of the third connecting rod 18 and the fourth connecting rod 19 are set to be equal in this embodiment.

[0254] Furthermore, the first connecting rod 14 and the second connecting rod 15 also have the same length, so that the connecting rod transmission structure runs more smoothly.

[0255] It is not difficult to understand that the structural combination formed by the crankshaft 13, the first connecting rod 14, the third connecting rod 18 and the push-pull stem 16 in the transmission system of this embodiment is similar to that of the first embodiment. Figure 6 or Fig. 9 The structure of the structural combination is basically the same, and the motion trajectory during operation is also basically the same. Therefore, the transmission system in this embodiment also has the same transmission characteristics as the transmission system in the first embodiment: the later the piston 4 moves to the right to do work, the greater the reduction ratio of the motor 5 to the piston 4, and the greater the driving force on the piston 4.

[0256] In addition, the present embodiment is also provided with a linear bearing 28 fixed in the housing 33 and sleeved on the outside of the push-pull rod 16 . The linear bearing 28 supports and guides the reciprocating motion of the push-pull rod 16 , thereby further improving the service life of the piston 4 .

[0257] It is not difficult to see that the transmission system of this embodiment is equivalent to removing the third connecting rod and the sixth connecting rod in the second embodiment, and is provided with a guide seat 23 for limiting the lower ends of the first connecting rod and the second connecting rod to move only vertically.

[0258] Embodiment 4:

[0259] Fig.19 and Fig. 20 A fourth diaphragm pump is shown, which adds a pump head based on the first embodiment, so that it can do work on two parts of working fluid at the same time. The details are as follows:

[0260] The diaphragm pump is equipped with two working chambers 1, two power chambers 2, two diaphragms 3 and two pistons 4. The motor 5 drives the two pistons 4 at the same time through a transmission system. Fig.19 The diaphragms 3 move back and forth in the left and right directions, thereby driving the left and right diaphragms 3 to do work on the working fluid a in the left and right working chambers 1.

[0261] like Fig.21 And refer to Fig. 20 As shown, the structure of the transmission system in the diaphragm pump of this embodiment is similar to that of the first embodiment, except that this embodiment is equipped with two second connecting rods 15 and two push-pull rods 16. The two push-pull rods 16 are respectively connected to the two pistons 4 on the left and right sides. One end of the two second connecting rods 15 is pivotally connected to the lower end of the first connecting rod 14 through a pivot 22, and the other end of the two second connecting rods 15 is respectively pivotally connected to the two push-pull rods 16 on the left and right sides through another pivot.

[0262] When the motor 5 drives the crankshaft 13 to rotate, the crankshaft 13 drives the first connecting rod 14 to move. No matter where the lower end of the first connecting rod 14 moves, it will inevitably drive at least one push-pull rod 16 to move left and right, thereby driving at least one piston 4 to move. However, in order to ensure that during operation, the pivot 22 that pivotally connects the first connecting rod 14 and the two second connecting rods 15 can only be Fig. 20 In the embodiment, a guide seat 23 is fixed in the transmission chamber 17 (fixed with the housing of the diaphragm pump), and a guide seat 23 is formed on the guide seat 23. Fig. 20 A guide slot 23a is provided in the middle and extends vertically to the front and rear of the paper, and the pivot 22 pivotally connecting the second connecting rod 15 and the push-pull rod 16 is slidably arranged in the guide slot 23a.

[0263] Furthermore, in this embodiment, the two second connecting rods 15 are of equal length, so that when the crankshaft 13 rotates, the two push-pull rods 16 move away from or approach each other synchronously in the left-right direction, thereby making the left and right pump heads work in unison.

[0264] During operation, the motor 5 drives the crankshaft 13 to rotate through the reducer 12. The crankshaft 13 drives the upper end of the first connecting rod 14 to rotate (orbit) around the pivot axis of the crankshaft. The lower end of the first connecting rod 14 simultaneously drives one end of the two second connecting rods 15 to reciprocate along the guide groove 23a, thereby causing the other end of the second connecting rod 15 to drive the push-pull rod 16 to move back and forth. Fig. 20 Move back and forth in the left and right direction.

[0265] In this embodiment, the guide seat 23 is an independent component connected to the housing of the diaphragm pump separately. Of course, we can also make the guide seat 23 and the housing into an integral structure as in the first embodiment.

[0266] It is not difficult to understand that the structural combination formed by the crankshaft 13, the first connecting rod 14, the second connecting rod 15 and the push-pull stem 16 in the transmission system of this embodiment is similar to that of the first embodiment. Figure 6 or Fig. 9 The structure and motion trajectory of the structure combination are also basically the same, so the transmission system in this embodiment also has the same transmission characteristics as the transmission system in Example 1: the later the piston 4 moves to the right to do work, the greater the reduction ratio from the motor 5 to the piston 4, and the greater the driving force exerted on the piston 4.

[0267] Embodiment five:

[0268] Fig. 22 A fifth diaphragm pump is shown, which has two pump heads like the fourth embodiment, so that it can work on two parts of working fluid at the same time. The difference between this embodiment and the fourth embodiment lies in the structure of the transmission system, which is as follows:

[0269] like Fig. 22 and Fig.23 As shown, the transmission system for connecting the motor and the piston in this embodiment includes the following components arranged in sequence along the transmission direction: a flywheel, a reducer, a crankshaft 13, two connecting rods (respectively a first connecting rod 14 and a second connecting rod 15), a parallelogram connecting rod, and two push-pull rods 16, which are not shown in the figure. Among them: the input shaft of the reducer is connected to the output shaft of the motor through a coupling, and the output shaft of the reducer is connected to one end of the crankshaft 13 through a coupling. The other end of the crankshaft 13 is pivotally supported on the housing 33 of the diaphragm pump. The parallelogram connecting rod is composed of a third connecting rod 18, a fourth connecting rod 19, a fifth connecting rod 20, and a sixth connecting rod 21, which are pivotally connected in sequence along the circumferential direction. One end of the first connecting rod 14 is pivotally connected to a curved portion of the crankshaft 13, and the other end is connected to the transition portion of the third connecting rod 18 and the fourth connecting rod 19. One end of the second connecting rod 15 is pivotally connected to another curved portion of the crankshaft 13, and the other end is connected to the transition portion of the fifth connecting rod 20 and the sixth connecting rod 21. One end of the right push-pull rod 16 is connected to the transition portion of the fourth connecting rod 19 and the fifth connecting rod 20, and the other end is connected to the right piston 4. One end of the left push-pull rod 16 is connected to the transition portion of the third connecting rod 18 and the sixth connecting rod 21, and the other end is connected to the left piston 4.

[0270] Specifically, Fig.23 And refer to Fig. 22 As shown, the third link 18 and the fourth link 19, the fourth link 19 and the fifth link 20, the fifth link 20 and the sixth link 21, and the sixth link 21 and the third link 18 are all pivotally connected through corresponding pivots 22. The "other end" of the first link 14 is specifically connected to the pivot 22 pivotally connected to the third link 18 and the fourth link 19. The "other end" of the second link 15 is connected to the pivot 22 pivotally connected to the fifth link 20 and the sixth link 21. One end of the right push-pull rod 16 is connected to the pivot 22 pivotally connected to the fourth link 19 and the fifth link 20. One end of the left push-pull rod 16 is connected to the pivot 22 pivotally connected to the third link 18 and the sixth link 21.

[0271] When the motor 5 drives the crankshaft 13 to rotate, the crankshaft 13 drives the first connecting rod 14 and the second connecting rod 15 to move. No matter where the lower ends of the first connecting rod 14 and the second connecting rod 15 move to, the parallelogram linkage will inevitably be deformed, and then at least one push-pull rod 16 will be driven to move left and right, so that at least one piston 4 moves left and right.

[0272] However, in order to ensure that both pistons 4 can operate during operation, a guide seat 23 is provided in the transmission chamber 17 in this embodiment, which is directly or indirectly fixed to the diaphragm pump housing 33. Fig.23The guide slot 23a extending up and down parallel to the paper surface is provided in the guide slot 23a, and the pivot 22 pivotally connecting the third connecting rod 18 and the fourth connecting rod 19 and the pivot 22 pivotally connecting the fifth connecting rod 20 and the sixth connecting rod 21 are slidably arranged in the guide slot 23a. In this way, the two pivots 22 can only move up and down (approach or move away from each other) along the guide slot 23a, thereby ensuring that the rotating crankshaft 13 drives the pistons 4 on both sides to move left and right at the same time during the working process.

[0273] During operation, the motor 5 drives the crankshaft 13 to rotate through the reducer. The crankshaft 13 drives the first connecting rod 14 and one end of the second connecting rod 15 to rotate around the pivot axis of the crankshaft. The other ends of the first connecting rod 14 and the second connecting rod 15 drive the upper and lower vertices of the parallelogram to rotate. Fig. 22 The parallel four-bar linkage moves closer and farther away periodically. Fig. 22 The horizontal dimension in the middle periodically extends and shortens, and then the pistons 4 on the left and right sides are driven by the left and right push-pull rods 16 respectively. Fig. 22 Move back and forth in the left and right directions.

[0274] It is not difficult to understand that during the working process, the vertical component of the thrust or pull of the left push-pull rod 16 by the fourth connecting rod 19 is always in the opposite direction to the vertical component of the thrust or pull of the right push-pull rod 16 by the fifth connecting rod 20, and the vertical component of the thrust or pull of the right push-pull rod 16 by the third connecting rod 18 is always in the opposite direction to the vertical component of the thrust or pull of the right push-pull rod 16 by the sixth connecting rod 21. The vertical forces received by the two push-pull rods 16 are both small or even zero, thereby reducing the radial force exerted by the push-pull rod 16 on the piston 4, thereby improving the piston 4 and Fig. 22 The service life of the piston cylinder sleeve (in this embodiment, the piston cylinder sleeve is the main component used to form the power chamber) shown but not marked in the figure reduces the oil leakage problem at the matching point between the piston 4 and the power chamber 2.

[0275] Furthermore, in order to ensure that during the operation, the vertical component of the thrust or pull of the right push-pull rod 16 by the fourth connecting rod 19 is always completely offset by the vertical component of the thrust or pull of the right push-pull rod 16 by the fifth connecting rod 20, and the vertical component of the thrust or pull of the left push-pull rod 16 by the third connecting rod 18 is always completely offset by the vertical component of the thrust or pull of the left push-pull rod 16 by the sixth connecting rod 21, so that the driving force exerted on the two pistons 4 is always parallel to the inner wall surface of the power chamber 2, in this embodiment, the lengths of the third connecting rod 18, the fourth connecting rod 19, the fifth connecting rod 20 and the sixth connecting rod 21 are set to be equal, so that the parallelogram linkage has a diamond structure.

[0276] Furthermore, the first connecting rod 14 and the second connecting rod 15 also have the same length, so that the parallel four-bar transmission structure runs more smoothly.

[0277] Obviously, the diamond-shaped four-bar linkage design can ensure that the two push-pull rods 16 are always symmetrically moved away from or symmetrically moved toward each other during operation, so that the left and right pump heads work in unison.

[0278] It is not difficult to understand that the structural combination formed by the crankshaft 13, the first connecting rod 14, the third connecting rod 18 and the push-pull rod 16 in the transmission system of this embodiment, and the structural combination formed by the crankshaft 13, the first connecting rod 14, the fourth connecting rod 19 and the push-pull rod 16 are similar to those in the first embodiment. Figure 6 or Fig. 9 The structure of the structural combination is basically the same, and the motion trajectory during operation is also basically the same. Therefore, the transmission system in this embodiment also has the same transmission characteristics as the transmission system in the first embodiment: the later the left piston 4 moves to the left to do work and the right piston 4 moves to the right to do work, the greater the reduction ratio of the motor 5 to the two pistons 4, and the greater the driving force on the two pistons 4.

[0279] In addition, the present embodiment is also provided with a linear bearing 28 fixed in the housing 33 and sleeved on the outside of the push-pull rod 16 . The linear bearing 28 supports and guides the reciprocating motion of the push-pull rod 16 , thereby further improving the service life of the piston 4 .

[0280] Embodiment six:

[0281] Fig.24 A sixth diaphragm pump is shown, the structure of which is similar to that of the first embodiment, except that:

[0282] This embodiment does not have a power fluid storage chamber connected to the power chamber and a valve on the communication path, but a clutch 37 is provided on the transmission system from the flywheel 24 to the piston 4. The clutch 37 is connected in series between the flywheel 24 and the piston 4. Obviously, the clutch 37 is provided on the driving path from the motor 5 to the diaphragm 3, and the clutch 37 is also a component of the driving path from the motor 5 to the diaphragm 3.

[0283] The clutch 37 is operable to be separated and engaged. When the clutch 37 is in the separated state, the driving path from the flywheel 24 to the diaphragm 3 is disconnected; when the clutch 37 is in the engaged state, the driving path from the flywheel 24 to the diaphragm 3 is engaged. It can be seen that the clutch 37 has the same function as the power fluid storage chamber 10 and the valve 11 in the first embodiment.

[0284] like Fig.25As shown, in order to allow the clutch 37 to automatically engage or disengage according to the speed of the motor 5, the clutch 37 adopts an electronically controlled clutch that can be electrically engaged and electrically disengaged, and is equipped with a motor speed sensor 34 for detecting the speed of the motor 5 and a controller 35 that is communicatively connected to the motor speed sensor 34 and the clutch 37. The controller 35 is used to obtain the speed of the motor 5 from the motor speed sensor 34, and control the engagement and disengagement of the clutch 37 based on the speed, so as to realize the following control method that is basically the same as that of the first embodiment:

[0285] This embodiment provides the following control method for the diaphragm pump:

[0286] S201, during the operation of the motor 5, the clutch 37 is controlled to be alternately disengaged and engaged at a first frequency.

[0287] That is, during the operation of the motor 5 , the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the first frequency.

[0288] Preferably, during the operation of the motor 5 , if it is determined that the rotation speed of the motor 5 is in a set first rotation speed range, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at a first frequency.

[0289] In other embodiments, the motor speed sensor 34 may not be configured, and only through a user instruction applied to the controller 35 , the controller 35 controls the clutch 37 to be alternately disengaged and engaged at the first frequency.

[0290] S202. In the process of controlling the clutch 37 to alternately disengage and engage at a first frequency in the above-mentioned S201, if it is detected that the rotation speed of the motor 5 continuously decreases within a first time period, the clutch 37 is controlled to alternately disengage and engage at a third frequency; wherein the ratio of the engagement time to the disengagement time of the clutch 37 in each cycle of the third frequency is less than the ratio of the engagement time to the disengagement time of the clutch 37 in each cycle of the first frequency.

[0291] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the first frequency, if it is determined that the rotation speed of the motor 5 is continuously reduced within the first time length, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the third frequency. Among them, the ratio of the engagement time length to the disconnection time length (of the drive path of the flywheel 24 to the diaphragm 3) in each cycle of the third frequency is less than the ratio of the engagement time length to the disconnection time length of the drive path in each cycle of the first frequency.

[0292] S203, in the process of controlling the clutch 37 to alternately separate and engage at the third frequency in the above S202, if it is detected that the speed of the motor 5 decreases continuously within the second time period, the clutch 37 is controlled to alternately separate and engage at a fourth frequency. The ratio of the engagement time period to the separation time period of the clutch 37 in each cycle of the fourth frequency is less than the ratio of the engagement time period to the separation time period of the clutch 37 in each cycle of the third frequency.

[0293] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the third frequency, if it is determined that the rotation speed of the motor 5 is continuously reduced within the second time period, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the fourth frequency. The ratio of the engagement time length to the disconnection time length of the drive path in each cycle of the fourth frequency is less than the ratio of the engagement time length to the disconnection time length of the drive path in each cycle of the third frequency.

[0294] S204. In the process of controlling the clutch 37 to be alternately separated and engaged at the third frequency in the above-mentioned S202, if it is detected that the rotation speed of the motor 5 continuously increases within the third time length, the clutch 37 is controlled to be alternately separated and engaged at the fifth frequency; wherein, the ratio of the engagement time length to the separation time length of the clutch 37 in each cycle of the first frequency is greater than the ratio of the engagement time length to the separation time length of the clutch 37 in each cycle of the fifth frequency is greater than the ratio of the engagement time length to the separation time length of the clutch 37 in each cycle of the third frequency.

[0295] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at a third frequency, if it is determined that the rotational speed of the motor 5 continuously increases within the third time length, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at a fifth frequency; wherein, the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the first frequency is greater than the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the fifth frequency is greater than the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the third frequency.

[0296] S205. In the process of controlling the clutch 37 to alternately disengage and engage at the first frequency in the above-mentioned S201, if it is detected that the rotation speed of the motor 5 continuously increases within the fourth time period, the clutch 37 is controlled to alternately disengage and engage at a sixth frequency; wherein the ratio of the engagement time to the disengagement time of the clutch 37 in each cycle of the sixth frequency is greater than the ratio of the engagement time to the disengagement time of the clutch 37 in each cycle of the first frequency.

[0297] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at a first frequency, if it is determined that the rotational speed of the motor 5 continuously increases within a fourth time period, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at a sixth frequency; wherein the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the sixth frequency is greater than the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the first frequency.

[0298] S206, in the process of controlling the clutch 37 to alternately separate and engage at the sixth frequency in the above S205, if it is detected that the speed of the motor 5 increases continuously within the fifth duration, the clutch 37 is controlled to alternately separate and engage at the seventh frequency. The ratio of the engagement duration to the separation duration of the clutch 37 in each cycle of the seventh frequency is greater than the ratio of the engagement duration to the separation duration of the clutch 37 in each cycle of the sixth frequency.

[0299] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the sixth frequency, if it is determined that the rotational speed of the motor 5 continues to increase within the fifth time period, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the seventh frequency; wherein the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the seventh frequency is greater than the ratio of the engagement duration to the disconnection duration of the drive path in each cycle of the sixth frequency.

[0300] S207, in the process of controlling the clutch 37 to alternately separate and engage at the sixth frequency in the above S205, if it is detected that the speed of the motor 5 decreases continuously within the sixth duration, the clutch 37 is controlled to alternately open and close at the eighth frequency. The ratio of the engagement duration to the separation duration of the clutch 37 in each cycle of the sixth frequency is greater than the ratio of the closing duration to the opening duration of the valve in each cycle of the eighth frequency, and the ratio of the engagement duration to the separation duration of the clutch 37 in each cycle of the first frequency.

[0301] That is, in the process of controlling the drive path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and engaged at the sixth frequency, if it is determined that the rotation speed of the motor 5 continues to increase within the sixth time period, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the eighth frequency; wherein the ratio of the engagement time to the disconnection time of the drive path in each cycle of the sixth frequency is greater than the ratio of the engagement time to the disconnection time of the drive path in each cycle of the eighth frequency is greater than the ratio of the engagement time to the disconnection time of the drive path in each cycle of the first frequency.

[0302] S208, if it is detected that the rotation speed of the motor 5 is less than the first rotation speed threshold, the clutch 37 is controlled to be continuously disengaged; wherein the first rotation speed threshold is less than the lower limit of the first rotation speed range in S201.

[0303] That is, if it is determined that the speed of the motor 5 is less than a first speed threshold, the drive path of the flywheel 24 to the diaphragm 3 is continuously disconnected; wherein the first speed threshold is less than the lower limit of the first speed range, so as to avoid serious overload of the motor 5.

[0304] S209, if it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold, the clutch 37 is controlled to be continuously engaged; wherein the second rotation speed threshold is not less than the first rotation speed threshold in S208.

[0305] That is, in the process of controlling the flywheel 24 to continuously disconnect the driving path to the diaphragm 3, if it is determined that the speed of the motor 5 is greater than the second speed threshold, the flywheel 24 is controlled to continuously engage the driving path to the diaphragm 3; wherein the second speed threshold is not less than the first speed threshold.

[0306] Preferably, the second speed threshold is greater than the upper limit of the first speed range in S201.

[0307] In other embodiments, the above strategies of S201-S207 may be abandoned, and only the strategies of S208 and S209 may be used to control the diaphragm pump:

[0308] That is, if it is determined that the speed of the motor 5 is less than the first speed threshold, the drive path of the flywheel 24 to the diaphragm 3 is continuously disconnected. If it is determined that the speed of the motor 5 is greater than the second speed threshold, the drive path of the flywheel 24 to the diaphragm 3 is continuously engaged; wherein the second speed threshold is not less than the first speed threshold. Under such a control mode, the second speed threshold can usually be equal to the first speed threshold. The disadvantage is that the speed of the motor 5 will be very unstable.

[0309] The controller 35 configured in the diaphragm pump of this embodiment also includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor. When the computer instructions are executed by the processor, the control method is implemented.

[0310] To ensure that the clutch 37 has a longer service life, a flexible clutch can be selected for the clutch 37. Moreover, the flexible clutch is preferably connected in series between the flywheel 24 and the reducer 12, rather than on the downstream side of the reducer 12, to reduce the force on the flexible clutch.

[0311] Embodiment seven:

[0312] Fig.26The seventh diaphragm pump is shown, which is particularly suitable for the following situation: the fluid pressure at the inlet 6 is much smaller than the fluid pressure at the outlet 7, the extraction force for extracting the working fluid from the inlet 6 to the working chamber 1 is much smaller than the thrust for pushing the working fluid from the working chamber to the outlet 7, and the power consumption for extracting the working fluid is much smaller than the power consumption for pushing the working fluid. For example, the diaphragm pump is arranged at the water source to push water from a low place to a high place. This is similar to the working situation of a diaphragm compressor, so it is also particularly suitable for a diaphragm compressor.

[0313] The structure of the diaphragm pump is similar to that of the sixth embodiment, except that:

[0314] like Fig.26 , Fig. 27 and Fig.28 As shown, the present embodiment is not equipped with a clutch. Instead, in addition to the suction valve 8, an additional electrically controlled valve 38 is provided, which is located between the inlet 6 and the working chamber 1 and is connected in parallel with the suction valve 8. The electrically controlled valve 38 is communicatively connected with the controller 35, so that the working state of the electrically controlled valve 38 can be controlled by the controller 35.

[0315] It can be seen that, in addition to the suction valve 8 originally provided in the conventional diaphragm pump, the present embodiment additionally provides an electrically controlled valve 38 located between the working chamber 1 and the inlet port 6 .

[0316] In this embodiment, the suction valve 8 is a mechanical one-way valve. Different from the suction valve 8 that automatically opens and closes by sensing pressure, the opening and closing of the electric control valve 38 can be controlled by an electric signal that is independent of pressure. In other embodiments, the suction valve 8 can also be an electric control one-way valve. The difference between a mechanical one-way valve and an electric control one-way valve is further described below.

[0317] If the electric control valve 38 is in the closed state, the pump head of the diaphragm pump has the same working process as the conventional diaphragm pump head. At this time, as long as the diaphragm pump has sufficient energy, it can extract the working fluid from the inlet 6 into the working chamber 1 and then push it to the outlet 7. However, as mentioned above, the diaphragm pump consumes a lot of power to push the working fluid. Therefore, when the motor 5 rotates at a low speed and the flywheel 24 has insufficient energy storage, the diaphragm pump cannot push the working fluid in the working chamber 1 to the outlet 7 in sufficient quantity.

[0318] If the electric control valve 38 is in the open state, the piston 4 is in Fig.26 When the piston moves to the left, the working fluid in the inlet 6 is easily drawn into the working chamber 1 through the opened electric control valve 38, and the power consumption of this action is relatively small; Fig.26When the middle right shift occurs, the electric control valve 38 is in an open state, and the discharge valve 9 is kept in a closed state due to the high opening pressure, so the working fluid in the working chamber 1 will be discharged from the opened electric control valve 38 to the inlet 6. At this time, the working fluid in the working chamber is discharged from the inlet 6, and the power consumption of this action is also very small. It is equivalent to disconnecting the working load of the diaphragm 3 (at least partially). Therefore, in this process, part of the output power provided by the motor 5 is used to complete the aforementioned extraction and return action, and the other more part is used to do work on the flywheel 24, so that the flywheel 24 speeds up and stores energy.

[0319] It should be noted in particular that the "disconnecting the workload of the diaphragm" mentioned in the specification and claims of this application is not limited to adjusting the workload of the diaphragm to zero, but also includes "only partially disconnecting" the workload of the diaphragm, that is, including the situation of "reducing" the workload of the diaphragm.

[0320] Therefore, this embodiment provides the following control method of the diaphragm pump:

[0321] S301, during the operation of the motor 5, the electrically controlled valve 38 is controlled to be alternately opened and closed at a first frequency.

[0322] That is, during the operation of the motor 5, the electric control valve 38 is opened for the twenty-third time period - closed for the twenty-fourth time period - opened for the twenty-third time period - closed for the twenty-fourth time period... in turn according to the set first frequency. That is, during the operation of the motor 5, the workload of the control diaphragm 3 is alternately disconnected and connected at the first frequency. Moreover, in each cycle of the first frequency, the electric control valve 38 has a continuous opening time period and a continuous closing time period, and the ratio of the opening time period to the closing time period can be set as required. It can be understood that the larger the ratio of the opening time period to the closing time period of the electric control valve 38, the greater the proportion of the energy storage time of the flywheel 24 in each cycle; the smaller the ratio of the opening time period to the closing time period of the electric control valve 38, the smaller the proportion of the energy storage time of the flywheel 24 in each cycle.

[0323] For example, during the operation of the motor, the electric control valve 38 is alternately opened and closed at a frequency of 10 times / minute, and each time it is opened for 2 seconds and closed for 4 seconds. Among them, 10 times / minute means that the valve is opened 10 times and closed 10 times per minute, and the opening and closing are performed alternately. Specifically, the electric control valve is opened for 2 seconds-closed for 4 seconds-opened for 2 seconds-closed for 4 seconds-opened for 2 seconds-closed for 4 seconds…

[0324] During the operation of the motor 5, the electronically controlled valve 38 is controlled to be alternately opened and closed according to the set first frequency, so that the working load of the diaphragm 3 is alternately disconnected and connected. In turn, the flywheel 24 and the diaphragm 3 intermittently perform work in each cycle of the first frequency. The motor 5 periodically stores energy in the flywheel 24. If in each cycle, the energy provided by the motor 5 that runs continuously (for example, the above-mentioned 2 seconds) is balanced with the energy consumed by the diaphragm 3 that performs normal work only in a part of the time period (for example, the above-mentioned 4 seconds), then the diaphragm pump can operate continuously and stably.

[0325] It can be understood that when the electric control valve 38 is closed, the workload of the diaphragm 3 is connected, and the closing time of the electric control valve 38 = the connection time of the workload of the diaphragm. When the electric control valve 38 is opened, the workload of the diaphragm 3 is disconnected, and the opening time of the electric control valve 38 = the disconnection time of the workload of the diaphragm. For the convenience of description, in this embodiment, the connection time of the workload of the diaphragm is referred to as "the connection time of the workload", and the disconnection time of the workload of the diaphragm is referred to as "the disconnection time of the workload".

[0326] It is not appropriate to adopt the control strategy of S301 when the speed of the motor 5 is very low (such as just started). Therefore, the control strategy of S301 can be adopted only when the speed of the motor 5 is in the set first speed interval. That is, during the operation of the motor 5, if it is determined that the speed of the motor 5 is in the first speed interval, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at a first frequency. It can be understood that the aforementioned first speed interval is preferably an interval near the rated speed of the motor 5. For example, if the rated speed of the motor 5 is 10,000 rpm, the first speed interval can be selected as the interval of 9,000-11,000 rpm.

[0327] Of course, the switching frequency of the electric control valve 38 can also be adjusted when the motor 5 is in different speed intervals. For example, if it is determined that the speed of the motor 5 is in a second speed interval that is different from and has no intersection with the first speed interval and is smaller than the first speed interval, the electric control valve 38 is controlled to be alternately opened and closed at a second frequency different from the first frequency. That is, if it is determined that the speed of the motor 5 is in the second speed interval, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at the second frequency.

[0328] In other embodiments, the motor speed sensor 34 may not be configured, and the electric control valve 38 may be controlled to alternately separate and engage at a first frequency by a user providing a user instruction to the controller 35 .

[0329] S302. In the process of controlling the electric control valve 38 to open and close alternately at a first frequency in the above-mentioned S301, if it is detected that the rotation speed of the motor 5 continuously decreases within a first time period, the electric control valve 38 is controlled to open and close alternately at a third frequency; wherein the ratio of the closing time to the opening time of the electric control valve 38 in each cycle of the third frequency is less than the ratio of the closing time to the opening time of the electric control valve 38 in each cycle of the first frequency.

[0330] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at a first frequency, if it is determined that the rotational speed of the motor 5 continuously decreases within a first time period, for example, one minute, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at a third frequency; wherein the ratio of the connection duration to the disconnection duration of the workload in each cycle of the third frequency is less than the ratio of the connection duration to the disconnection duration of the workload in each cycle of the first frequency.

[0331] The speed of the motor 5 decreases continuously within the set first time period, for example, within two minutes, indicating that within the first time period, the energy provided by the motor 5 is less than the power consumption of the diaphragm 3. Therefore, it is necessary to reduce the proportion of the working time of the diaphragm 3, or to increase the proportion of the no-load energy storage time of the flywheel 24. Therefore, when it is detected that the speed of the motor 5 decreases continuously within the first time period, the control electric control valve 38 is alternately opened and closed at a third frequency different from the first frequency. Among them, the ratio of the connection time to the disconnection time of the workload in each cycle of the third frequency is less than the ratio of the connection time to the disconnection time in each cycle of the first frequency.

[0332] For example, the third frequency may be: open the electric control valve for 4 seconds - close the electric control valve for 2 seconds - open the electric control valve for 4 seconds - close the electric control valve for 2 seconds - open the electric control valve for 4 seconds - close the electric control valve for 2 seconds ..., and the cycle is still 10 times per minute. Of course, the third frequency can also be adjusted to 3, 6 or 20 times per minute, etc.

[0333] S303, in the process of controlling the electric control valve 38 to open and close alternately at the third frequency in the above S302, if it is detected that the speed of the motor 5 decreases continuously within the second time period, the electric control valve 38 is controlled to open and close alternately at a fourth frequency. The ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the fourth frequency is less than the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the third frequency.

[0334] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at the third frequency, if it is determined that the speed of the motor 5 is continuously reduced within the second time period, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at the fourth frequency. The ratio of the workload connection time period to the disconnection time period in each cycle of the fourth frequency is less than the ratio of the workload connection time period to the disconnection time period in each cycle of the third frequency.

[0335] The speed of the motor 5 decreases continuously in the second time period, indicating that in the second time period, the energy provided by the motor 5 is still less than the power consumption of the diaphragm 3. Therefore, it is necessary to further reduce the time proportion of the normal operation of the diaphragm 3, or further increase the time proportion of the no-load energy storage of the flywheel 24. Therefore, when it is detected that the speed of the motor 5 continues to decrease continuously in the second time period, the electronically controlled valve 38 is controlled to open and close alternately at the fourth frequency.

[0336] Exemplarily, at the fourth frequency: open the electric-controlled valve for 5 seconds - close the electric-controlled valve for 1 second - open the electric-controlled valve for 5 seconds - close the electric-controlled valve for 1 second - open the electric-controlled valve for 5 seconds - close the electric-controlled valve for 1 second..., still cycling 10 times per minute.

[0337] S304, in the process of controlling the electric control valve 38 to open and close alternately at the third frequency in the above S302, if it is detected that the speed of the motor 5 increases continuously within the third time period, the electric control valve 38 is controlled to open and close alternately at the fifth frequency. The ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the first frequency is greater than the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the fifth frequency, and the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the third frequency.

[0338] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at a third frequency, if it is determined that the rotation speed of the motor 5 continuously increases within the third time length, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at a fifth frequency; wherein, the ratio of the connection duration to the disconnection duration in each cycle of the first frequency is greater than the ratio of the connection duration to the disconnection duration in each cycle of the fifth frequency is greater than the ratio of the connection duration to the disconnection duration in each cycle of the third frequency.

[0339] The rotation speed of the motor 5 increases continuously within the third time period, indicating that within the third time period, the energy provided by the motor 5 is greater than the power consumption of the diaphragm 3. Therefore, the normal working time proportion of the diaphragm 3 can be appropriately increased, or the no-load energy storage time proportion of the flywheel 24 can be appropriately reduced. Therefore, when it is detected that the rotation speed of the motor 5 increases continuously within the third time period, the electronically controlled valve 38 is controlled to be alternately opened and closed at the fifth frequency.

[0340] Exemplarily, at the fifth frequency: open the electric-controlled valve for 3.5 seconds-close the electric-controlled valve for 2.5 seconds-open the electric-controlled valve for 3.5 seconds-close the electric-controlled valve for 2.5 seconds-open the electric-controlled valve for 3.5 seconds-close the electric-controlled valve for 2.5 seconds….

[0341] S305. In the process of controlling the electric control valve 38 to open and close alternately at the first frequency in the above-mentioned S301, if it is detected that the rotation speed of the motor 5 continuously increases within the fourth time length, the electric control valve 38 is controlled to open and close alternately at a sixth frequency; wherein, the ratio of the closing time length to the opening time length of the electric control valve 38 in each cycle of the sixth frequency is greater than the ratio of the closing time length to the opening time length of the electric control valve 38 in each cycle of the first frequency.

[0342] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at a first frequency, if it is determined that the rotation speed of the motor 5 continuously increases within a fourth time period, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at a sixth frequency; wherein the ratio of the connection duration to the disconnection duration of the workload in each cycle of the sixth frequency is greater than the ratio of the connection duration to the disconnection duration of the workload in each cycle of the first frequency.

[0343] The rotation speed of the motor 5 decreases continuously in the fourth time period, indicating that in the fourth time period, the energy provided by the motor 5 is greater than the power consumption of the diaphragm 3. Therefore, the proportion of time that the diaphragm 3 normally works can be increased, or the proportion of the no-load energy storage time of the flywheel 24 can be shortened. Therefore, when it is detected that the rotation speed of the motor 5 decreases continuously in the fourth time period, the electronically controlled valve 38 is controlled to be alternately opened and closed at the sixth frequency.

[0344] Exemplarily, the sixth frequency may be: open the electric control valve for 4 seconds - close the electric control valve for 11 seconds - open the electric control valve for 4 seconds - close the electric control valve for 11 seconds - open the electric control valve for 4 seconds - close the electric control valve for 11 seconds..., cycling on and off 4 times per minute.

[0345] S306, in the process of controlling the electric control valve 38 to open and close alternately at the sixth frequency in the above S305, if it is detected that the speed of the motor 5 increases continuously within the fifth time period, the electric control valve 38 is controlled to open and close alternately at the seventh frequency. The ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the seventh frequency is greater than the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the sixth frequency.

[0346] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at the sixth frequency, if it is determined that the rotation speed of the motor 5 continuously increases within the fifth time period, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at the seventh frequency; wherein, the ratio of the connection duration to the disconnection duration of the workload in each cycle of the seventh frequency is greater than the ratio of the connection duration to the disconnection duration of the workload in each cycle of the sixth frequency.

[0347] The rotation speed of the motor 5 increases continuously in the fifth time period, indicating that in the fifth time period, the energy provided by the motor 5 is still greater than the power consumption of the diaphragm 3. Therefore, the proportion of time that the diaphragm 3 normally works can be further increased, or the proportion of time that the flywheel 24 stores energy without load can be further reduced. Therefore, when it is detected that the rotation speed of the motor 5 continues to decrease continuously in the fifth time period, the electronically controlled valve 38 is controlled to be alternately opened and closed at the seventh frequency.

[0348] Exemplarily, at the seventh frequency: open the electric-controlled valve for 4 seconds-close the electric-controlled valve for 12 seconds-open the electric-controlled valve for 4 seconds-close the electric-controlled valve for 12 seconds-open the electric-controlled valve for 4 seconds-close the electric-controlled valve for 12 seconds….

[0349] S307, in the process of controlling the electric control valve 38 to open and close alternately at the sixth frequency in the above S305, if it is detected that the speed of the motor 5 decreases continuously within the sixth time period, the electric control valve 38 is controlled to open and close alternately at the eighth frequency. The ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the sixth frequency is greater than the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the eighth frequency, and the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the first frequency.

[0350] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at the sixth frequency, if it is determined that the rotational speed of the motor 5 continuously decreases within the sixth time period, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at the eighth frequency; wherein, the ratio of the connection duration to the disconnection duration of the workload in each cycle of the sixth frequency is greater than the ratio of the connection duration to the disconnection duration of the workload in each cycle of the eighth frequency is greater than the ratio of the connection duration to the disconnection duration of the workload in each cycle of the first frequency.

[0351] The speed of the motor 5 decreases continuously in the sixth time period, indicating that in the sixth time period, the energy provided by the motor 5 is less than the power consumption of the diaphragm 3. Therefore, the proportion of time that the diaphragm 3 normally works can be appropriately reduced, or the proportion of the no-load energy storage time of the flywheel 24 can be appropriately increased. Therefore, when it is detected that the speed of the motor 5 increases continuously in the sixth time period, the electronically controlled valve 38 is controlled to open and close alternately at the eighth frequency.

[0352] Exemplarily, at the eighth frequency: open the electric-controlled valve for 4 seconds-close the electric-controlled valve for 10 seconds-open the electric-controlled valve for 4 seconds-close the electric-controlled valve for 10 seconds-open the electric-controlled valve for 4 seconds-close the electric-controlled valve for 10 seconds….

[0353] S308, if it is detected that the rotation speed of the motor 5 is less than the first rotation speed threshold, the electronically controlled valve 38 is controlled to be continuously opened; wherein the first rotation speed threshold is less than the lower limit of the first rotation speed range in S301.

[0354] That is, if it is determined that the rotation speed of the motor 5 is less than a first relatively small rotation speed threshold, the workload of the control diaphragm 3 is continuously disconnected.

[0355] The first speed threshold is a relatively small value, which is less than the lower limit of the first speed range in this embodiment. When the speed of the motor 5 is less than the very small first speed threshold, it means that the energy of the motor 5 and the flywheel 24 is seriously insufficient, so the electric control valve 38 can be continuously opened to keep the workload of the diaphragm 3 in the disconnected state to avoid serious overload of the motor 5.

[0356] S309, if it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold, the electronically controlled valve 38 is controlled to be continuously closed; wherein the second rotation speed threshold is not less than the first rotation speed threshold in S308.

[0357] That is, in the process of continuously disconnecting the workload of the diaphragm 3 , if it is determined that the rotation speed of the motor 5 is greater than the second rotation speed threshold, the workload of the diaphragm 3 is continuously connected.

[0358] It can be understood that in the process of continuously opening the electric control valve 38 in S308, the flywheel 24 is always kept in a no-load energy storage state, and the energy provided by the motor 5 is completely converted into the kinetic energy of the flywheel 24. When the speed of the motor 5 and the flywheel 24 is high enough and the kinetic energy is large enough, if the electric control valve 38 is still kept in the open state, the diaphragm pump will run without load as a whole, resulting in energy waste. Therefore, when the speed of the motor 5 is detected to be greater than the second speed threshold, the embodiment switches the electric control valve 38 from the punching state to the closed state, connects the workload of the diaphragm 3, and allows the diaphragm 3 to work normally.

[0359] The second speed threshold should not be less than the first speed threshold in S301, and is preferably a value greater than the upper limit of the first speed range.

[0360] Obviously, we can also abandon the above strategies of S301-S307 and only use the strategies of S308 and S309 to control the diaphragm pump:

[0361] That is, if it is determined that the speed of the motor 5 is less than the first speed threshold, the workload of the diaphragm 3 is controlled to be continuously disconnected. If it is determined that the speed of the motor 5 is greater than the second speed threshold, the workload of the diaphragm 3 is controlled to be continuously connected; wherein the second speed threshold is not less than the first speed threshold. Under such a control mode, the second speed threshold can usually be equal to the first speed threshold. The disadvantage is that the speed of the motor 5 will be very unstable.

[0362] The controller 35 configured in the diaphragm pump also includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor. When the computer instructions are executed by the processor, the control method is implemented.

[0363] Embodiment eight:

[0364] Fig.29 The eighth diaphragm pump is shown, which is particularly suitable for the following situation: the extraction force for extracting the working fluid from the inlet port 6 to the working chamber 1 is much greater than the thrust for pushing the working fluid from the working chamber to the outlet port 7, and the power consumption for extracting the working fluid is much greater than the power consumption for pushing the working fluid. For example, the diaphragm pump is arranged at a high place to extract water from a low place to the high place.

[0365] The structure of the diaphragm pump is similar to that of the seventh embodiment, except that:

[0366] In this embodiment, the electrically controlled valve 38 communicating with the controller 35 is disposed between the working chamber 1 and the discharge port 7 and connected in parallel with the discharge valve 9 , rather than being connected between the working chamber 1 and the inlet 6 .

[0367] It can be seen that, in addition to the discharge valve 9 originally provided in the conventional diaphragm pump, the present embodiment additionally provides an electrically controlled valve 38 located between the working chamber 1 and the discharge port 7 .

[0368] In this embodiment, the discharge valve 9 is a mechanical one-way valve. Different from the discharge valve 9 that automatically opens and closes by sensing pressure, the opening and closing of the electric control valve 38 can be controlled by an electric signal that is independent of pressure. In other embodiments, the discharge valve 9 can also be an electric control one-way valve.

[0369] If the electric control valve 38 is in the closed state, the pump head of the diaphragm pump has the same working process as the traditional pump head. At this time, as long as the diaphragm pump has enough energy, it can extract the working fluid from the inlet 6 into the working chamber 1 and then push it to the outlet 7. However, as mentioned above, the power consumption of the diaphragm pump to extract the working fluid is very large, so when the motor 5 rotates at a low speed and the flywheel 24 has insufficient energy storage, the diaphragm pump cannot extract a sufficient amount of the working fluid from the inlet 6 to the working chamber 1. The working fluid or air in the outlet 7 can be extracted to the working chamber 1 with only a small amount of power, so at this time the electric control valve 38 can be opened to reduce the diaphragm 3 in Fig.29 Load with leftward deformation.

[0370] If the electric control valve 38 is in the open state, the piston Fig.29 When the piston moves to the right, the working fluid in the working chamber 1 is easily pushed to the discharge port 7 through the electric control valve 38, and the power consumption of the pushing action is relatively small; Fig.29 When the center moves to the left, the electric control valve 38 is in an open state, and the suction valve 8 is kept in a closed state due to the high opening pressure, so the working fluid (or air) in the discharge port 7 can be easily extracted from the opened electric control valve 38 to the working chamber 1, and the power consumption of the extraction action is also small. This is equivalent to at least partially disconnecting the working load of the diaphragm 3. Therefore, in this process, part of the output power provided by the motor 5 is used to complete the aforementioned pushing and extraction actions, and the other part is used to work on the flywheel 24, so that the flywheel 24 speeds up and stores energy.

[0371] Therefore, this embodiment provides the following briefly introduced control method which is basically the same as that of the seventh embodiment. The detailed control method can refer to the content of the seventh embodiment.

[0372] S401, during the operation of the motor 5, the electrically controlled valve 38 is controlled to be alternately opened and closed at a first frequency.

[0373] Preferably, when it is determined that the rotation speed of the motor 5 is within a set first rotation speed range, the electrically controlled valve 38 is controlled to be alternately opened and closed at a first frequency.

[0374] S402. During the process of controlling the electric control valve 38 to open and close alternately at a first frequency in S401, if it is detected that the rotation speed of the motor 5 decreases continuously within a first time period, the electric control valve 38 is controlled to open and close alternately at a third frequency; wherein the ratio of the closing time to the opening time of the electric control valve 38 in each cycle of the third frequency is less than the ratio of the closing time to the opening time of the electric control valve 38 in each cycle of the first frequency.

[0375] S403, in the process of controlling the electric control valve 38 to open and close alternately at the third frequency in S402, if it is detected that the rotation speed of the motor 5 decreases continuously within the second time period, the electric control valve 38 is controlled to open and close alternately at a fourth frequency. The ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the fourth frequency is less than the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the third frequency.

[0376] S404, in the process of controlling the electric control valve 38 to open and close alternately at the third frequency in S402, if it is detected that the rotation speed of the motor 5 increases continuously within the third time period, the electric control valve 38 is controlled to open and close alternately at the fifth frequency. The ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the first frequency is greater than the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the fifth frequency, and the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the third frequency.

[0377] S405. During the process of controlling the electric control valve 38 to open and close alternately at a first frequency at S401, if it is detected that the rotation speed of the motor 5 increases continuously within a fourth time period, the electric control valve 38 is controlled to open and close alternately at a sixth frequency; wherein the ratio of the closing time to the opening time of the electric control valve 38 in each cycle of the sixth frequency is greater than the ratio of the closing time to the opening time of the electric control valve 38 in each cycle of the first frequency.

[0378] S406, in the process of controlling the electric control valve 38 to open and close alternately at the sixth frequency in S405, if it is detected that the speed of the motor 5 increases continuously within the fifth duration, the electric control valve 38 is controlled to open and close alternately at the seventh frequency. The ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the seventh frequency is greater than the ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the sixth frequency.

[0379] S407, in the process of controlling the electric control valve 38 to alternately open and close at the sixth frequency in S405, if it is detected that the speed of the motor 5 decreases continuously within the sixth duration, the electric control valve 38 is controlled to alternately open and close at the eighth frequency. The ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the sixth frequency is greater than the ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the eighth frequency and greater than the ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the first frequency.

[0380] S408: If it is detected that the rotation speed of the motor 5 is less than a first relatively small rotation speed threshold, the electronically controlled valve 38 is controlled to be continuously opened.

[0381] S409, if it is detected that the speed of the motor 5 is greater than the second speed threshold, the electronically controlled valve 38 is controlled to be continuously closed; wherein the second speed threshold is not less than the first speed threshold in S408. Preferably, the second speed threshold is greater than the upper limit of the first speed range in S401.

[0382] Embodiment nine:

[0383] Fig.32The ninth diaphragm pump is shown, which is also applicable to the situation described in the eighth embodiment: the extraction force for extracting the working fluid from the inlet 6 to the working chamber 1 is much greater than the thrust for pushing the working fluid from the working chamber to the outlet 7, and the power consumption for extracting the working fluid is much greater than the power consumption for pushing the working fluid. For example, the diaphragm pump is arranged at a high place to extract water from a low place to the high place.

[0384] The structure of the diaphragm pump is similar to that of the eighth embodiment, except that: in this embodiment, no additional electric control valve is added between the working chamber 1 and the discharge port 7, but the discharge valve 9 is set as an electric control one-way valve that is connected to the controller 35 for communication. Fig.33 .

[0385] It is known that the main difference between an electric-controlled one-way valve and an ordinary mechanical one-way valve is that an ordinary mechanical one-way valve directly senses the pressure to open or close, and cannot achieve reverse flow of the fluid. An electric-controlled one-way valve has more functions and applications, mainly including two types: ⅰ, some electric-controlled one-way valves can open (or close) in response to an electric control signal while fully retaining the functions of ordinary mechanical one-way valves; ⅱ, some other electric-controlled one-way valves need to first convert the fluid pressure at the valve into an electric control signal, and then control the opening (or closing) of the valve through the electric control signal. Therefore, as long as the control command is intervened on the electric-controlled one-way valve, the reverse flow of the fluid can be achieved. For example, the Chinese invention patent application with publication number CN108825828A discloses an electric-controlled one-way valve that can actively open the one-way valve by electric control, thereby achieving reverse flow of the fluid.

[0386] Based on the same purpose as the eighth embodiment, this embodiment mainly implements the following control method for the diaphragm pump by writing computer instructions into the controller 35:

[0387] S501, during the operation of the motor 5, the discharge valve 9 is controlled to be open for an eighth time period at intervals of a seventh time period.

[0388] That is, during the operation of the motor 5, the discharge valve 9 is alternately opened for the eighth time period - the seventh time period is interval - the discharge valve 9 is opened for the eighth time period - the seventh time period is interval - the discharge valve 9 is opened for the eighth time period - the seventh time period is interval - the discharge valve 9 is opened for the eighth time period .... In effect, it is equivalent to the seventh and eighth embodiments: during the operation of the motor 5, the workload of the diaphragm 3 is alternately disconnected and connected at the first frequency.

[0389] The above-mentioned “opening the discharge valve 9 for the eighth time period” means that the discharge valve 9 is kept in the open state for the eighth time period. “interval for the seventh time period” means that during the seventh time period, the controller 35 does not actively intervene in the action of the discharge valve 9, and allows the discharge valve 9 to operate according to its original characteristics. For example, it is opened or closed according to physical pressure, or opened or closed according to the original electrical control strategy.

[0390] The above-mentioned “allowing the discharge valve 9 to operate according to its original characteristics” generally includes two situations:

[0391] 1) The discharge valve 9 opens or closes according to the physical pressure. In this case, the controller 35 completely removes the interference with the working state of the discharge valve 9, allowing the discharge valve 9 to directly sense the pressure on both sides and automatically open or close. That is, the controller 35 does nothing to the discharge valve 9, allowing the discharge valve 9 to open or close only by non-electrical mechanical force. This is more suitable for the above-mentioned type "i" electric control one-way valve.

[0392] 2) The discharge valve 9 is opened or closed according to the original electrical control strategy. In this case, the controller only needs to remove the above-mentioned active intervention on the discharge valve and adopt the traditional strategy to control the opening and closing of the discharge valve 9. "Adopting the traditional strategy to control the opening and closing of the discharge valve 9" usually means that the controller 35 mainly controls the discharge valve 9 to open or close according to the pressure at the discharge valve 9. This is more suitable for the above-mentioned "ii" type of electrically controlled one-way valve.

[0393] For example, during the operation of the motor, the controller 35 actively opens the discharge valve 9 intermittently in a manner of opening the discharge valve once every 4 seconds and keeping it open for 2 seconds each time. That is, the discharge valve is opened and kept open for 2 seconds - every 4 seconds - the discharge valve is opened and kept open for 2 seconds - every 4 seconds - the discharge valve is opened and kept open for 2 seconds - every 4 seconds - the discharge valve is opened and kept open for 2 seconds...

[0394] During the operation of the motor 5, the controller 35 actively opens the discharge valve 9 intermittently according to the set rhythm, so that the workload of the diaphragm 3 is alternately disconnected and connected according to the set first frequency. In turn, the flywheel 24 and the diaphragm 3 intermittently perform work in each cycle of the first frequency, and the motor 5 periodically stores energy in the flywheel 24. Generally, in each cycle (for example, 4+2=6 seconds in this embodiment), the energy provided by the continuously running motor 5 is balanced with the energy consumption of the diaphragm 3 performing normal work only in a part of the time period (for example, 4 seconds in this embodiment), so that the diaphragm pump can operate continuously and stably.

[0395] It can be understood that when the controller 35 actively controls the discharge valve 9 to open, the workload of the diaphragm 3 is disconnected, and the duration of the discharge valve 9 being actively opened = the disconnection duration of the workload of the diaphragm. When the controller 35 stops actively intervening in the discharge valve 9, the discharge valve 9 operates normally, the workload of the diaphragm 3 is connected, and the interval duration of the controller 35 actively controlling the discharge valve 9 to open = the connection duration of the workload of the diaphragm. For the convenience of description, in this embodiment, the connection duration of the workload of the diaphragm, that is, the interval duration of the controller 35 actively controlling the discharge valve 9 to open, is referred to as the "connection duration of the workload", and the disconnection duration of the workload of the diaphragm is referred to as the "disconnection duration of the workload".

[0396] It is not appropriate to adopt the control strategy of S501 when the speed of the motor 5 is very low (such as just started). Therefore, the control strategy of S501 can be adopted only when the speed of the motor 5 is in the set first speed interval. That is, during the operation of the motor 5, if it is determined that the speed of the motor 5 is in the first speed interval, then in response to the determination, the discharge valve 9 is controlled to open for the eighth time period every seventh time period, so that the workload of the diaphragm 3 is alternately disconnected and connected at the first frequency. It can be understood that the aforementioned first speed interval is preferably an interval near the rated speed of the motor 5. For example, if the rated speed of the motor 5 is 10,000 rpm, the first speed interval can be selected as the interval of 9,000-11,000 rpm.

[0397] Of course, the rhythm of actively opening the discharge valve 9 can also be adjusted when the motor 5 is in different speed ranges. For example, if it is determined that the speed of the motor 5 is in a second speed range that is different from and has no intersection with the first speed range and is smaller than the first speed range, the discharge valve 9 is controlled to be opened for the tenth time period every ninth time period. That is, if it is determined that the speed of the motor 5 is in the second speed range, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at the second frequency.

[0398] S502, in the process of controlling the discharge valve 9 to open for the eighth time period at intervals of the seventh time period in the above S501, if it is detected that the rotation speed of the motor 5 decreases continuously within the first time period, for example, within three minutes, then the discharge valve 9 is controlled to open for the twelfth time period at intervals of the eleventh time period; wherein, the ratio of the eleventh time period to the twelfth time period is less than the ratio of the seventh time period to the eighth time period.

[0399] That is, in the process of controlling the workload of the diaphragm 3 to alternately disconnect and connect the diaphragm 3 at the first frequency, if it is determined that the speed of the motor 5 decreases continuously within the first duration, the workload of the diaphragm 3 is controlled to alternately disconnect and connect at the third frequency. The ratio of the workload connection duration to the disconnection duration in each cycle of the third frequency is less than the ratio of the workload connection duration to the disconnection duration in each cycle of the first frequency.

[0400] S503, in the process of controlling the discharge valve 9 to open for the twelfth time period at every eleventh time period in the above S502, if it is detected that the rotation speed of the motor 5 continuously decreases within the second time period, the discharge valve 9 is controlled to open for the fourteenth time period at every thirteenth time period; wherein, the ratio of the thirteenth time period to the fourteenth time period is less than the ratio of the eleventh time period to the twelfth time period.

[0401] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at a third frequency, if it is determined that the rotational speed of the motor 5 continuously decreases within the second time period, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at a fourth frequency; wherein, the ratio of the connection duration to the disconnection duration of the workload in each cycle of the fourth frequency is less than the ratio of the connection duration to the disconnection duration of the workload in each cycle of the third frequency.

[0402] S504, in the process of controlling the discharge valve 9 to open for the twelfth time period at every eleventh time period in the above S502, if it is detected that the rotation speed of the motor 5 continuously increases within the third time period, the discharge valve 9 is controlled to open for the sixteenth time period at every fifteenth time period; wherein, the ratio of the seventh time period to the eighth time period>the ratio of the fifteenth time period to the sixteenth time period>the ratio of the eleventh time period to the twelfth time period.

[0403] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at a third frequency, if it is determined that the rotational speed of the motor 5 continuously increases within the third time length, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at a fifth frequency; wherein, the ratio of the connection time length to the disconnection time length in each cycle of the first frequency is greater than the ratio of the connection time length to the disconnection time length in each cycle of the fifth frequency is greater than the ratio of the connection time length to the disconnection time length in each cycle of the third frequency.

[0404] S505. In the process of controlling the discharge valve 9 to open for the eighth time period at intervals of the seventh time period in the above S501, if it is detected that the rotation speed of the motor 5 increases continuously within the fourth time period, the discharge valve 9 is controlled to open for the eighteenth time period at intervals of the seventeenth time period; wherein, the ratio of the seventeenth time period to the eighteenth time period is greater than the ratio of the seventh time period to the eighth time period.

[0405] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at a first frequency, if it is determined that the rotational speed of the motor 5 continuously increases within a fourth time period, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at a sixth frequency; wherein, the ratio of the connection duration to the disconnection duration of the workload in each cycle of the sixth frequency is greater than the ratio of the connection duration to the disconnection duration of the workload in each cycle of the first frequency.

[0406] S506, in the process of controlling the discharge valve 9 to open for the eighteenth time period at intervals of the seventeenth time period in the above S505, if it is detected that the speed of the motor 5 increases continuously within the fifth time period, the discharge valve 9 is controlled to open for the twentieth time period at intervals of the nineteenth time period. The ratio of the nineteenth time period to the twentieth time period is greater than the ratio of the seventeenth time period to the eighteenth time period.

[0407] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at the sixth frequency, if it is determined that the rotational speed of the motor 5 continues to increase within the fifth time period, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at the seventh frequency; wherein, the ratio of the connection duration to the disconnection duration of the workload in each cycle of the seventh frequency is greater than the ratio of the connection duration to the disconnection duration of the workload in each cycle of the sixth frequency.

[0408] S507, in the process of controlling the discharge valve 9 to open for the eighteenth time period at intervals of the seventeenth time period in the above S505, if it is detected that the speed of the motor 5 continuously decreases within the sixth time period, the discharge valve 9 is controlled to open for the twenty-second time period at intervals of the twenty-first time period. The ratio of the seventeenth time period to the eighteenth time period>the ratio of the twenty-first time period to the twenty-second time period>the ratio of the seventh time period to the eighth time period.

[0409] That is, in the process of controlling the workload of the diaphragm 3 to be alternately disconnected and connected at the sixth frequency, if it is determined that the rotational speed of the motor 5 continuously increases within the sixth time period, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at the eighth frequency; wherein, the ratio of the connected time period to the disconnected time period of the workload in each cycle of the sixth frequency is greater than the ratio of the connected time period to the disconnected time period of the workload in each cycle of the eighth frequency is greater than the ratio of the connected time period to the disconnected time period of the workload in each cycle of the first frequency.

[0410] S508, if it is detected that the rotation speed of the motor 5 is less than a first rotation speed threshold value which is relatively small, the discharge valve 9 is controlled to be continuously opened; wherein the first rotation speed threshold value is less than the lower limit of the first rotation speed range in S501.

[0411] S509, if it is detected that the speed of the motor 5 is greater than the second speed threshold, the above-mentioned active intervention of the controller 35 on the discharge valve 9 is removed; wherein the second speed threshold is not less than the first speed threshold in S508, and the second speed threshold is preferably greater than the upper limit of the first speed range in S501.

[0412] In other embodiments, the above strategies of S501-S507 may be abandoned, and only the strategies of S508 and S509 may be used to control the diaphragm pump:

[0413] That is, if it is determined that the speed of the motor 5 is less than the first speed threshold, the workload of the diaphragm 3 is controlled to be continuously disconnected; if it is determined that the speed of the motor 5 is greater than the second speed threshold, the workload of the diaphragm 3 is controlled to be continuously connected; wherein the second speed threshold is not less than the first speed threshold. In such a control mode, the second speed threshold can usually be equal to the first speed threshold.

[0414] The controller 35 includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor. When the computer instructions are executed by the processor, the control method is implemented.

[0415] Embodiment ten:

[0416] Fig.34 The tenth diaphragm pump is shown, which is also applicable to the situation described in the seventh embodiment: the extraction force for extracting the working fluid from the inlet 6 to the working chamber 1 is much smaller than the thrust for pushing the working fluid from the working chamber to the outlet 7, and the power consumption for extracting the working fluid is much smaller than the power consumption for pushing the working fluid. For example, the diaphragm pump is arranged at the water source to push the water from the low place to the high place. This is similar to the working situation of the diaphragm compressor, so it is also applicable to the diaphragm compressor.

[0417] The structure of the diaphragm pump is similar to that of the seventh embodiment, except that: in this embodiment, no additional electric-controlled valve is added between the working chamber 1 and the inlet 6, but the suction valve 8 is set as an electric-controlled one-way valve that is connected to the controller 35 for communication.

[0418] Based on the same purpose as the seventh embodiment, this embodiment mainly implements the following control method of the diaphragm pump, which is similar to the ninth embodiment, by writing computer instructions (codes) into the controller 35. The detailed control method can refer to the contents of the ninth embodiment.

[0419] S601, during the operation of the motor 5, the suction valve 8 is controlled to be open for an eighth time period at intervals of a seventh time period.

[0420] That is, during the operation of the motor 5, the suction valve 8 is alternately opened for the eighth time period - the interval is the seventh time period - the suction valve 8 is opened for the eighth time period - the interval is the seventh time period - the suction valve 8 is opened for the eighth time period - the interval is the seventh time period - the suction valve 8 is opened for the eighth time period .... In effect, it is equivalent to the following in the seventh, eighth and ninth embodiments: during the operation of the motor 5, the workload of the diaphragm 3 is alternately disconnected and connected at the first frequency.

[0421] Preferably, when it is determined that the rotation speed of the motor 5 is within the set first rotation speed range, the suction valve 8 is controlled to open for an eighth time period at intervals of a seventh time period.

[0422] S602, in the process of S601 controlling the suction valve 8 to open for the eighth time period at intervals of the seventh time period, if it is detected that the rotation speed of the motor 5 continuously decreases within the first time period, the suction valve 8 is controlled to open for the twelfth time period at intervals of the eleventh time period; wherein, the ratio of the eleventh time period to the twelfth time period is less than the ratio of the seventh time period to the eighth time period.

[0423] S603, in the process of controlling the suction valve 8 to open for the twelfth time period at every eleventh time period at S602, if it is detected that the speed of the motor 5 decreases continuously within the second time period, the suction valve 8 is controlled to open for the fourteenth time period at every thirteenth time period. The ratio of the thirteenth time period to the fourteenth time period is less than the ratio of the eleventh time period to the twelfth time period.

[0424] S604, in the process of controlling the suction valve 8 to open for the twelfth time period at intervals of the eleventh time period at S602, if it is detected that the speed of the motor 5 continuously increases within the third time period, the suction valve 8 is controlled to open for the sixteenth time period at intervals of the fifteenth time period. The ratio of the seventh time period to the eighth time period>the ratio of the fifteenth time period to the sixteenth time period>the ratio of the eleventh time period to the twelfth time period.

[0425] S605, in the process of S601 controlling the suction valve 8 to open for the eighth time period at intervals of the seventh time period, if it is detected that the rotation speed of the motor 5 continuously increases within the fourth time period, the suction valve 8 is controlled to open for the eighteenth time period at intervals of the seventeenth time period; wherein, the ratio of the seventeenth time period to the eighteenth time period is greater than the ratio of the seventh time period to the eighth time period.

[0426] S606, in the process of controlling the suction valve 8 to open for the eighteenth time period at every seventeenth time period in S605, if it is detected that the speed of the motor 5 increases continuously within the fifth time period, the suction valve 8 is controlled to open for the twentieth time period at every nineteenth time period. The ratio of the nineteenth time period to the twentieth time period is greater than the ratio of the seventeenth time period to the eighteenth time period.

[0427] S607, in the process of controlling the suction valve 8 to open for the eighteenth time period at intervals of the seventeenth time period in the above S605, if it is detected that the speed of the motor 5 continuously decreases within the sixth time period, the suction valve 8 is controlled to open for the twenty-second time period at intervals of the twenty-first time period. The ratio of the seventeenth time period to the eighteenth time period>the ratio of the twenty-first time period to the twenty-second time period>the ratio of the seventh time period to the eighth time period.

[0428] S608: If it is detected that the rotation speed of the motor 5 is less than a first relatively small rotation speed threshold, the suction valve 8 is controlled to be continuously opened.

[0429] S609, if it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold, the above-mentioned active intervention of the controller 35 on the suction valve 8 is removed; wherein the second rotation speed threshold is not less than the first rotation speed threshold in S608.

[0430] In other embodiments, the strategies of S601 to S607 described above may be abandoned, and only the strategies of S608 and S609 may be used to control the diaphragm pump.

[0431] Embodiment eleven:

[0432] Fig.36 The eleventh diaphragm pump is shown, and the structure of the diaphragm pump is similar to that of the first embodiment, and the main difference is that:

[0433] This embodiment is not equipped with a piston, but with a bladder 26 of a rotating body structure that can axially expand and contract. The expansion and contraction of the bladder 26 is used to push the power fluid in the power chamber 2 to drive the diaphragm 3 to deform, thereby squeezing the working fluid in the working chamber 1 to do work. The axis of the bladder 26 is Fig.38 The middle extends straightly in the left-right direction.

[0434] like Fig.37 And refer to Fig.36 As shown, a part of the power chamber 2 is formed inside the bladder 26, and the rest is located outside the bladder 26. When working, the power chamber 2 inside and outside the bladder 26 is filled with power fluid. The motor 5 is connected to the left end of the bladder 26 through a transmission system to drive the bladder to move in the axial direction ( Fig.37 The right end of the bladder 26 is fixed to the housing 33 of the diaphragm pump.

[0435] like Fig.39 And refer to Fig.38 and Fig.37 As shown, the transmission system in this embodiment has the same structure as the transmission system in the sixth embodiment, the only difference is that the push-pull rod in the sixth embodiment is connected to the piston, while the push-pull rod 16 in this embodiment is connected to the bladder 26. The transmission system is also equipped with a flywheel 24 connected in series between the motor 5 and the reducer 12. When working, the push-pull rod 16 drives the left end of the bladder 26 to move in a Fig.36 When the bladder 26 is axially contracted by the flywheel 24, if the valve 11 is in the open state, a part of the hydraulic oil in the power chamber 2 enters the power fluid storage chamber 10; if the valve 11 is in the closed state, the hydraulic oil in the power chamber 2 squeezes the diaphragm 3 to deform to the right, and works on the working fluid.

[0436] Obviously, the transmission system in this embodiment can also adopt the structure of embodiment 2 or embodiment 3.

[0437] The bladder 26 is made of rubber and has a certain thickness. The inner part can withstand strong radial pressure without deformation (no radial deformation). The structure is basically the same as the bladder structure configured for air spring shock absorbers used in the automotive field.

[0438] A plurality of pleated rings are integrally provided on the bladder 26 . The pleated rings are closely arranged along the axial direction of the bladder, and each pleated ring surrounds the periphery of the bladder axis to enhance the axial deformation capability of the bladder 26 .

[0439] For the convenience of explanation, the power chamber 2 is now divided into two parts. The power chamber 2 inside the bladder 26 is called the first half chamber 2a, and the power chamber 2 outside the bladder 26 is called the second half chamber 2b. Fig.37 .

[0440] Both the left and right ends of the bladder 26 are open structures, and the right end of the push-pull rod 16 blocks the opening at the left end of the bladder. The opening at the right end of the bladder 26 is used to connect the power chamber outside the bladder, that is, the second half chamber 2b, so that the power fluid b can flow between the power chambers inside and outside the bladder, that is, between the first half chamber 2a and the second half chamber 2b.

[0441] If the opening at the right end of the bladder 26 is not specially treated, when the diaphragm 3 deforms to the left, it will be excessively deformed at the opening position, shortening its service life. In this regard, in this embodiment, a barrier net 27 is fixedly arranged at the opening at the right end of the bladder 26 to prevent excessive deformation of the diaphragm 3. The first half cavity 2a and the second half cavity 2b are respectively located on the left and right sides of the barrier net 27, and the second half cavity 2b is formed between the diaphragm 3 and the barrier net 27.

[0442] Furthermore, the second half cavity 2b is a tapered cavity with its large end facing the diaphragm 3, and the baffle net 27 is arranged at the small end of the tapered cavity to better adapt to the leftward deformation of the diaphragm 3. When the diaphragm deforms to the left, it can be entirely attached to the cavity wall of the second half cavity 2b and the right side of the diaphragm 3. Similarly, the working chamber 1 is also arranged as a tapered cavity with its large end facing the diaphragm 3. When the diaphragm deforms to the right, it can also be attached to the cavity wall of the working chamber 1 over a large area. Obviously, the above-mentioned embodiments 1 to 7 also adopt a similar design.

[0443] When the bladder 26 is stretched to a certain length by the push-pull rod 16, the diaphragm 3 is deformed to the left and abuts against the wall of the second half chamber 2b and the side surface of the baffle net 27 facing the second half chamber 2b. When the bladder 26 is compressed to a certain length by the push-pull rod 16, the diaphragm 3 is deformed to the right and abuts against the wall of the working chamber 1.

[0444] The push-pull rod 16, the bladder 26 and the diaphragm 3 are coaxially arranged, and the baffle net 27 is arranged parallel to the diaphragm 3. The axis of the bladder 26 is perpendicular to the diaphragm 3, and the extension line of the axis of the bladder 26 passes through the center of the diaphragm 3.

[0445] As mentioned above, the main purpose of the operation of the motor 5 is to provide driving force for the diaphragm 3, so as to drive the diaphragm 3 to move and squeeze and extract the working fluid. The bladder 26 of this embodiment and the transmission system connecting the motor and the bladder are both arranged on the driving path for the motor 5 to transmit the driving force to the diaphragm 3, and the bladder 26 and the transmission system connecting the motor and the bladder are both components of the driving path for the motor 5 to the diaphragm 3.

[0446] The power fluid b filled in the power chamber 2 is also arranged on the driving path through which the motor 5 transmits the driving force to the diaphragm 3, and has the function of transmitting the driving force to the diaphragm 3. Therefore, the power fluid b filled in the power chamber 2 is also a component of the driving path from the motor 5 to the diaphragm 3.

[0447] Embodiment 12:

[0448] Fig.40 The twelfth diaphragm pump is shown. The diaphragm pump has a pump head added on the basis of the eleventh embodiment, so that it can do work on two parts of working fluid at the same time. The details are as follows:

[0449] like Fig.40 The diaphragm pump is equipped with two bladders 26. The motor 5 drives the two bladders 26 at the same time through a transmission system. Fig.40 The two push-pull rods in the fourth embodiment are respectively connected to the pistons on the left and right sides, while the two push-pull rods in the present embodiment are respectively connected to the bladders 26 on the left and right sides.

[0450] The structure of the transmission system in this embodiment is the same as that in the fifth embodiment, the only difference is that the push-pull rod is connected to the piston in the fifth embodiment, while the push-pull rod 16 is connected to the bladder 26 in this embodiment.

[0451] Obviously, the transmission system in this embodiment can also adopt the structure of embodiment 6.

[0452] Embodiment 13:

[0453] Fig.41 and Fig.42 A thirteenth diaphragm pump is shown, the structure of which is substantially the same as that of the twelfth embodiment, the main difference being that:

[0454] In this embodiment, the power chamber 2 is entirely formed inside the bladder 26, and the diaphragm 3 is arranged at the right end of the bladder 26. The oil path for connecting the power chamber 2 and the power fluid storage chamber 10 is led from the push-pull rod 16 on the left side of the bladder to the inside of the bladder 26.

[0455] In order to enhance the sealing and isolating capability of the diaphragm 3 to the power chamber 2 and the working chamber 1 and to facilitate the manufacture and installation of related components, the diaphragm 3 and the bladder 26 are made into an integral structure in this embodiment, and the two are integrally formed.

[0456] Embodiment 14:

[0457] Fig.43 A fourteenth diaphragm pump is shown, and its structure is basically the same as that of the thirteenth embodiment, with the main differences being:

[0458] The diaphragm 3 is arranged inside the bladder 26, thereby dividing the inner cavity of the bladder 26 into a power chamber 2 and a working chamber 1, and the power chamber 2 and the working chamber 1 are both formed inside the bladder 26. During operation, the push-pull rod 16 pushes the bladder 26 to the right to axially contract. On the one hand, the hydraulic oil in the power chamber 2 pushes the diaphragm 3 to the right to squeeze the working fluid in the working chamber 1. On the other hand, the working chamber 1 itself also contracts and deforms to squeeze the working fluid therein to do work. Compared with the twelfth embodiment, the deformation of the diaphragm 3 in this embodiment is smaller when squeezing the same volume of working fluid, which is conducive to extending the service life of the diaphragm pump, especially the diaphragm.

[0459] In order to ensure the sealing isolation of the power chamber 2 and the working chamber 1 by the diaphragm 3 and to facilitate the manufacture and installation of related components, the diaphragm 3 and the bladder 26 are made into an integral structure in this embodiment. The two are integrally formed.

[0460] Embodiment 15:

[0461] Fig.45 and Fig.46 A fifteenth diaphragm pump is shown, and its structure is similar to that of the fourteenth embodiment, and the main differences are:

[0462] like Fig.46 and Fig.47 As shown in the figure, a rigid ring sleeve 30 with a thin left side and a thick right side and a roughly trumpet-shaped shape is connected to the right side of the leather bag 26, and the rigid ring sleeve 30 has a small opening at the left end and a large opening at the right end. The opening at the right end of the leather bag 26 is directly connected to the opening at the left end of the rigid ring sleeve 30, and the diaphragm 3 is closed at the opening at the right end of the rigid ring sleeve 30. The right side of the diaphragm 3 is connected to an annular deformable flexible ring sheet 31. A part of the power chamber 2 is formed in the rigid ring sleeve 30, and the other part is formed in the leather bag 26.

[0463] When the diaphragm sheet 3 and the flexible ring sheet 31 are in Fig.46 and Fig.47In the natural state shown in FIG. 1 , both are substantially planar structures, and the two are arranged close to each other, and the volume of the working chamber is zero. Fig.47 When the diaphragm 3 moves to the left, the negative pressure formed in the power chamber 2 causes the diaphragm 3 to deform to the left. On the other hand, the rigid ring sleeve 30 follows the movement of the bladder 26 to the left, thereby driving the outer edge of the flexible ring 31 to deform to the left, so that the flexible ring 31 is roughly in a tapered structure with a thick left and a thin right. A working chamber 1 for absorbing working fluid is formed between the diaphragm 3 and the flexible ring 31. Fig.48 Moreover, at this time, the volume of the working chamber is positively correlated with the deformation of the diaphragm sheet 3 and the flexible ring sheet 31 .

[0464] It can be seen that during operation, the diaphragm 3 and the flexible ring 31 are deformed together to change the volume of the working chamber, thereby sucking the working fluid into the working chamber, or pushing out all the working fluid in the working chamber. Compared with the above-mentioned embodiments 1 to 9, the deformation of the diaphragm 3 in this embodiment is smaller when squeezing the same volume of working fluid, which is conducive to extending the service life of the diaphragm.

[0465] In order to improve the deformation adaptability of the diaphragm 3 and the flexible ring 31, and further to improve the service life of the diaphragm 3 and the flexible ring 31, the diaphragm 3 of the present embodiment is integrally formed with a circle of axially right-convex diaphragm deformation folds 3a, and the flexible ring 31 is integrally formed with a circle of axially right-convex flexible ring deformation folds 31a. The right side of the flexible ring 31 is provided with a pressure-bearing seat 32 fixed to the shell 33, and the pressure-bearing seat 32 has a supporting plane facing the flexible ring, and the supporting plane is provided with an annular groove 32a that is concave inward and adapted to the deformation folds 3a of the diaphragm and the deformation folds 31a of the flexible ring, so as to Fig.46 The diaphragm sheet 3 and the flexible ring sheet 31 are in a state where the deformed folds 3a and 31a of the diaphragm sheet are accommodated. Fig.46 and Fig.47 In the natural state, the parts except the deformed wrinkles are all planar structures, that is, the non-deformed wrinkle areas of the diaphragm sheet 3 and the flexible ring sheet 31 in the natural state are planar structures.

[0466] In addition, an oil passage cavity is arranged at the periphery of the bladder 26 , and an oil passage connecting the power chamber 2 and the power fluid storage chamber 10 passes through the oil passage cavity. The valve 11 is arranged on the rigid ring sleeve 30 .

[0467] Embodiment 16:

[0468] Fig.50 A sixteenth diaphragm pump is shown, and its structure is similar to that of the eleventh embodiment, except that this embodiment does not have a power fluid storage chamber communicated with the power chamber 2.

[0469] Embodiment 17:

[0470] Fig.51 A seventeenth diaphragm pump is shown, and its structure is similar to that of the twelfth embodiment, except that this embodiment does not have a power fluid storage chamber communicated with the power chamber 2.

[0471] Embodiment 18:

[0472] Fig.52 An eighteenth diaphragm pump is shown, and its structure is similar to that of the thirteenth embodiment, except that this embodiment does not have a power fluid storage chamber communicated with the power chamber 2.

[0473] Embodiment 19:

[0474] Fig.53 A nineteenth diaphragm pump is shown, and its structure is similar to that of the fourteenth embodiment, except that this embodiment is not provided with a power fluid storage chamber communicated with the power chamber 2.

[0475] Embodiment 20:

[0476] Fig.54 The twentieth diaphragm pump is shown, and its structure is similar to that of the fifteenth embodiment, except that the present embodiment does not have a power fluid storage chamber communicating with the power chamber 2 .

[0477] It is understandable that the structures of the above-mentioned embodiments are all applicable to diaphragm compressors for compressing working fluids, such as compressing low-pressure refrigerants into high-pressure states or even liquid states, and are particularly applicable to air-conditioning compressors.

[0478] Embodiment 21: Air conditioning system

[0479] Inspired by the above-mentioned seventh and tenth embodiments, this embodiment provides an air conditioning system capable of intermittent high-power work. Fig.55 As shown, the air conditioning system includes a compressor 100, a condenser 200, a throttle valve 300 and an evaporator 400 which are fluidly connected in sequence and form a closed loop. The air conditioning system is filled with refrigerant. When working, the refrigerant flows through the compressor, the condenser, the throttle valve and the evaporator in sequence, so that the air conditioning system can cool or heat the outside.

[0480] The main improvement of the air conditioning system is that the compressor 100 is a diaphragm compressor, and the structure of the diaphragm compressor is basically the same as that of the diaphragm pump in the sixth embodiment, and also includes a motor speed sensor 34 and a controller 35 that is communicatively connected to the motor speed sensor. The only difference is that the diaphragm compressor is not equipped with the clutch in the sixth embodiment. Fig.24 .

[0481] like Fig.56 And refer to Fig.55As shown, the throttle valve 300 is an electronically controlled throttle valve that is communicatively connected to the controller 35 .

[0482] It is known that the opening and closing actions of the electronically controlled throttle valve can be controlled by an electronically controlled signal. In a conventional air-conditioning system, the electronically controlled throttle valve usually controls the switch state mainly according to the pressure at the throttle valve. An ordinary mechanical throttle valve directly senses the pressure and opens (including the degree of opening) or closes. Similar to the electronically controlled one-way valve, the electronically controlled throttle valve also mainly includes two types: i. Some electronically controlled throttle valves can open and close in response to electronically controlled signals while fully retaining the functions of ordinary mechanical throttle valves; ii. Some electronically controlled throttle valves are completely controlled by electronically controlled signals to open and close.

[0483] Based on the same purpose as Example 7 and Example 10, this embodiment mainly implements the following briefly described control method for the air-conditioning system by writing computer instructions (codes) into the controller 35. The detailed control method can refer to the contents of Example 9 and Example 10.

[0484] S701, during the operation of the motor 5 of the diaphragm compressor, if it is determined that the speed of the motor is in the set first speed range, the throttle valve 300 is controlled to open for an eighth time period every seventh time period.

[0485] S702, during the process of S701 controlling the throttle valve 300 to open for the eighth time period at intervals of the seventh time period, if it is detected that the rotation speed of the motor decreases continuously within the first time period, the throttle valve 300 is controlled to open for the twelfth time period at intervals of the eleventh time period; wherein the ratio of the eleventh time period to the twelfth time period is less than the ratio of the seventh time period to the eighth time period.

[0486] S703, in the process of S702 controlling the throttle valve 300 to open for the twelfth time period at every eleventh time period, if it is detected that the rotation speed of the motor decreases continuously within the second time period, the throttle valve 300 is controlled to open for the fourteenth time period at every thirteenth time period; wherein, the ratio of the thirteenth time period to the fourteenth time period is less than the ratio of the eleventh time period to the twelfth time period.

[0487] S704, in the process of controlling the throttle valve 300 to open for the twelfth time period at every eleventh time period at S702, if it is detected that the speed of the motor increases continuously within the third time period, the throttle valve 300 is controlled to open for the sixteenth time period at every fifteenth time period. The ratio of the seventh time period to the eighth time period>the ratio of the fifteenth time period to the sixteenth time period>the ratio of the eleventh time period to the twelfth time period.

[0488] S705. During the process of S701 controlling the throttle valve 300 to open for the eighth time period at intervals of the seventh time period, if it is detected that the rotation speed of the motor increases continuously within the fourth time period, the throttle valve 300 is controlled to open for the eighteenth time period at intervals of the seventeenth time period; wherein the ratio of the seventeenth time period to the eighteenth time period is greater than the ratio of the seventh time period to the eighth time period.

[0489] S706, in the process of controlling the throttle valve 300 to open for the eighteenth time period at every seventeenth time period in S705, if it is detected that the speed of the motor increases continuously within the fifth time period, the throttle valve 300 is controlled to open for the twentieth time period at every nineteenth time period, wherein the ratio of the nineteenth time period to the twentieth time period is greater than the ratio of the seventeenth time period to the eighteenth time period.

[0490] S707, in the process of controlling the throttle valve 300 to open for the eighteenth time period at intervals of the seventeenth time period in S705, if it is detected that the speed of the motor decreases continuously within the sixth time period, the throttle valve 300 is controlled to open for the twenty-second time period at intervals of the twenty-first time period. The ratio of the seventeenth time period to the eighteenth time period>the ratio of the twenty-first time period to the twenty-second time period>the ratio of the seventh time period to the eighth time period.

[0491] S708: If it is detected that the rotation speed of the motor is less than a first relatively small rotation speed threshold, the throttle valve 300 is continuously opened.

[0492] S709, if it is detected that the speed of the motor 5 is greater than the second speed threshold, the above-mentioned active intervention of the controller 35 on the throttle valve 300 is removed, and the discharge valve 9 is allowed to operate according to its original characteristics; wherein the second speed threshold is not less than the first speed threshold in S708. "Allowing the discharge valve 9 to operate according to its original characteristics" generally includes two situations:

[0493] 1) The throttle valve 300 opens or closes according to physical pressure. In this case, the controller 35 completely stops interfering with the working state of the throttle valve 300, allowing the throttle valve 300 to directly sense the pressure on both sides and automatically open or close. That is, the controller 35 does nothing to the throttle valve 300, allowing the throttle valve 300 to open or close only by non-electrical mechanical force. This is more suitable for the above-mentioned type "i" of electronically controlled throttle valves.

[0494] 2) The throttle valve 300 is opened or closed according to the original electrical control strategy. In this case, the controller 35 only needs to remove the above-mentioned active intervention on the throttle valve 300 and adopt the traditional strategy to control the opening and closing of the throttle valve 300. "Adopting the traditional strategy to control the opening and closing of the throttle valve 300" usually means that the controller 35 mainly controls the opening or closing of the throttle valve 300 according to the fluid pressure at the throttle valve 300. This is more suitable for the above-mentioned "ii" type of electronically controlled throttle valve.

[0495] In some other embodiments, the above strategies of S701-S707 may be abandoned, and only the strategies of S708 and S709 may be used to simplify the control of the air conditioning system, as follows:

[0496] That is, if it is determined that the speed of the motor 5 is less than the first speed threshold, the throttle valve 300 is controlled to be continuously opened to continuously disconnect the workload of the diaphragm. If it is determined that the speed of the motor is greater than the second speed threshold, the active intervention of the controller 35 on the throttle valve 300 is removed to continuously connect the workload of the diaphragm 3; wherein the second speed threshold is not less than the first speed threshold. Under such a control method, the second speed threshold can usually be equal to the first speed threshold.

[0497] In the simplified control strategy described above, when the motor speed is low and the output power is insufficient, the throttle valve 300 is kept in an open state to reduce the load of the compressor, increase the motor speed, and store energy for the flywheel. When the motor speed is high enough and the flywheel energy is large enough, the throttle valve 300 is restored to its original state to allow the air conditioning system to work normally. The disadvantage is that the speed of the motor in the compressor 100 will be very unstable.

[0498] Those skilled in the art will understand that obtaining the speed information of the motor 5 in the diaphragm compressor is one of the conditions for successfully implementing the above-mentioned S701-S709 control method. For example, the speed of the motor 5 can be obtained in real time during the operation of the motor 5. Once it is determined that the motor speed meets a certain preset condition, the throttle valve 300 is controlled to make a corresponding response action - for example, when it is determined that the motor speed is in a set first speed range, the throttle valve 300 is controlled to open and close alternately at a first frequency.

[0499] Embodiment 22: Air conditioning system

[0500] Inspired by the above-mentioned eighth and ninth embodiments, this embodiment provides another air conditioning system capable of intermittent high-power work. Fig.57 And refer to Fig.58 As shown, the air conditioning system is provided with an electric control valve 38 connected between the condenser 200 and the evaporator 400 and in parallel with the throttle valve 300. The electric control valve 38 is in communication connection with a controller 35 which is in communication connection with a motor speed sensor 34, so that the controller 35 can control the working state of the electric control valve 38 according to the motor speed. The compressor 100 adopts the same structure as that of the twenty-first embodiment.

[0501] If the electric control valve 38 is kept in the closed state, the working mode of the air conditioning system is the same as that of the conventional air conditioning system. At this time, as long as the diaphragm compressor 100 has sufficient energy, it can pressurize the high-pressure fluid on the upstream side of the throttle valve 300 to the downstream side of the throttle valve 300. However, in some cases, the power consumption of the compressor 100 to compress the working fluid is very large, such as when carbon dioxide is used as a refrigerant. Therefore, when the speed of the motor 5 is low and the energy storage of the flywheel 24 is insufficient, the compressor 100 cannot work normally.

[0502] If the electric control valve 38 is kept in the open state, it is equivalent to "shorting" the throttle valve 300 and removing it from the circuit. The electric control valve 38 without the throttling expansion function allows the working fluid (refrigerant) to flow easily between the condenser 200 and the evaporator 400, and the workload of the compressor 100 is small. Of course, in this case, the air conditioning system has no cooling and heating effects.

[0503] Therefore, this embodiment provides the following control method of the air conditioning system of this variant, and its detailed control method can refer to the seventh embodiment and the eighth embodiment.

[0504] S801, during the operation of the motor of the diaphragm compressor 100, if it is detected that the speed of the motor is in a first speed range, the electrically controlled valve 38 is controlled to be alternately opened and closed at a first frequency.

[0505] Generally, the rated speed of the driving motor in the compressor 100 is within the above-mentioned first speed range.

[0506] Optionally, if it is detected that the speed of the motor is in a second speed interval that does not intersect with the first speed interval and is smaller than the first speed interval, the electric control valve 38 is alternately opened and closed at a second frequency different from the first frequency. The ratio of the opening time length to the closing time length of the electric control valve 38 in each cycle of the second frequency is ≠ the ratio of the opening time length to the closing time length of the electric control valve 38 in each cycle of the first frequency.

[0507] S802. During the process of controlling the electric control valve 38 to open and close alternately at a first frequency at S801, if it is detected that the rotation speed of the motor decreases continuously within a first time period, the electric control valve 38 is controlled to open and close alternately at a third frequency; wherein the ratio of the closing time to the opening time of the electric control valve 38 in each cycle of the third frequency is less than the ratio of the closing time to the opening time of the electric control valve 38 in each cycle of the first frequency.

[0508] S803, in the process of controlling the electric control valve 38 to alternately open and close at the third frequency in S802, if it is detected that the rotation speed of the motor decreases continuously within the second time period, the electric control valve 38 is controlled to alternately open and close at a fourth frequency, wherein the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the fourth frequency is less than the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the third frequency.

[0509] S804, in the process of controlling the electric control valve 38 to open and close alternately at the third frequency in S802, if it is detected that the rotation speed of the motor 5 increases continuously within the third time period, the electric control valve 38 is controlled to open and close alternately at the fifth frequency. The ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the first frequency is greater than the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the fifth frequency, and the ratio of the closing time period to the opening time period of the electric control valve 38 in each cycle of the third frequency.

[0510] S805. During the process of controlling the electric-controlled valve 38 to open and close alternately at a first frequency at S801, if it is detected that the rotation speed of the motor increases continuously within a fourth time period, the electric-controlled valve 38 is controlled to open and close alternately at a sixth frequency; wherein the ratio of the closing time to the opening time of the electric-controlled valve 38 in each cycle of the sixth frequency is greater than the ratio of the closing time to the opening time of the electric-controlled valve 38 in each cycle of the first frequency.

[0511] S806, in the process of controlling the electric control valve 38 to open and close alternately at the sixth frequency in S805, if it is detected that the speed of the motor increases continuously within the fifth duration, the electric control valve 38 is controlled to open and close alternately at the seventh frequency. The ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the seventh frequency is greater than the ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the sixth frequency.

[0512] S807, in the process of controlling the electric control valve 38 to open and close alternately at the sixth frequency in S805, if it is detected that the speed of the motor decreases continuously within the sixth duration, the electric control valve 38 is controlled to open and close alternately at the eighth frequency. The ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the sixth frequency is greater than the ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the eighth frequency and greater than the ratio of the closing duration to the opening duration of the electric control valve 38 in each cycle of the first frequency.

[0513] S808, if it is detected that the rotation speed of the motor 5 is less than a first relatively small rotation speed threshold, the electronically controlled valve 38 is controlled to be continuously opened; wherein the first rotation speed threshold is less than the lower limit of the first rotation speed range in S801.

[0514] S809, if it is detected that the speed of the motor 5 is greater than the second speed threshold, the electronically controlled valve 38 is controlled to remain closed. The second speed threshold is not less than the first speed threshold in S808, and is usually greater than the upper limit of the first speed range in S801.

[0515] In order to simplify control, the electric control valve 38 is preferably a normally closed valve or a normally open valve.

[0516] Fig.57 and Fig.58 The controller 35 in the embodiment includes a memory, a processor connected to the memory, and computer instructions stored in the aforementioned memory and executable by the aforementioned processor. When the computer instructions are executed by the processor, the above-mentioned control method in this embodiment can be implemented respectively.

[0517] Embodiment 23: Air conditioning system

[0518] like Fig.59 and Fig.60 As shown, the air conditioning system of this embodiment also includes a compressor 100, a condenser 200, a throttle valve 300 and an evaporator 400 which are fluidly connected in sequence and form a closed loop. The pressure sensor 39 is used to detect the internal pressure of the condenser 200, referred to as the condenser pressure.

[0519] In this embodiment, the compressor 100 is a diaphragm compressor, and its structure is basically the same as that of the first embodiment. Figure 2 As shown, the difference between the two is that the compressor of this embodiment is not equipped with a motor speed sensor, and the controller 35 which is in communication connection with the valve 11 is also in communication connection with the above-mentioned pressure sensor 39, so that the valve 11 can be opened or closed according to the pressure of the condenser 200.

[0520] This embodiment proposes the following control method for the air-conditioning system: during the operation of the motor of the diaphragm compressor 100, if it is detected that the pressure of the condenser 200 is in a first pressure range, the valve 11 in the diaphragm compressor is opened and closed alternately at a first frequency, that is, the driving path from the flywheel 24 in the compressor 100 to the diaphragm 3 in the compressor 100 is alternately disconnected and connected at the first frequency.

[0521] The greater the pressure of the condenser 200, the greater the opening pressure of the discharge valve 9 in the compressor 100, and the greater the load force that the diaphragm 3 needs to overcome. The smaller the pressure of the condenser 200, the smaller the opening pressure of the discharge valve 9 in the compressor 100, and the smaller the load force that the diaphragm 3 needs to overcome. Therefore, the upper limit of the first pressure interval should not be too large, otherwise the speed of the motor 5 and the flywheel 24 may drop suddenly due to insufficient output power of the compressor motor 5, and the compressor 100 may be seriously overloaded. The lower limit of the first pressure interval does not need to be very small, otherwise it will increase energy waste and reduce the cooling or heating efficiency of the air conditioner. When the pressure of the condenser 200 is in the first pressure range which is neither too high nor too low, the valve 11 connected between the power chamber 2 and the power fluid storage chamber 10 on the diaphragm compressor 100 is controlled to open and close alternately at a set first frequency. If, within each cycle time of the first frequency, the energy provided by the continuously running compressor motor 5 and the power consumption of the compressor diaphragm 3 which only works in part of the time can be balanced, then the diaphragm compressor 100 can operate continuously and stably and can work intermittently at high power.

[0522] In other embodiments, when it is detected that the pressure of the condenser 200 is in a second pressure range that has no intersection with the above-mentioned first pressure range, the valve 11 on the diaphragm compressor can be alternately opened and closed at a second frequency; wherein the lower limit of the second pressure range is greater than the upper limit of the first pressure range, and the ratio of the closing time to the opening time of the valve 11 in each cycle of the second frequency is less than the ratio of the closing time to the opening time of the valve 11 in each cycle of the first frequency, that is, the ratio of the engagement time to the disconnection time of the driving path (the driving path from the flywheel to the diaphragm in the diaphragm compressor) in each cycle of the second frequency is less than the ratio of the engagement time to the disconnection time of the driving path in each cycle of the first frequency.

[0523] In other embodiments, if it is detected that the pressure of the condenser 200 is greater than a first pressure threshold, the valve 11 in the diaphragm compressor is continuously opened, thereby keeping the driving path of the flywheel 24 to the diaphragm 3 in a disconnected state; wherein the first speed threshold is greater than the upper limit of the first pressure range.

[0524] When the pressure of the condenser 200 is greater than a value greater than the upper limit of the first pressure interval, it means that the load of the compressor is too high. If the compressor 100 is still allowed to work intermittently at this time, the speed of the motor 5 and the flywheel 24 may drop suddenly due to insufficient output power of the compressor motor 5. Therefore, the valve 11 can be continuously opened at this time to keep the drive path of the flywheel 24 to the diaphragm 3 in a disconnected state, and the air conditioning system stops cooling or heating. If the speed of the motor has not reached the rated speed at this time, the flywheel 24 can continue to store energy during the period of time when the valve 11 is continuously opened.

[0525] In other embodiments, if it is detected that the pressure of the condenser 200 is less than a second pressure threshold, the valve 11 in the diaphragm compressor is continuously closed, thereby maintaining the drive path of the flywheel 24 to the diaphragm 3 in an engaged state; wherein the second speed threshold is less than the lower limit of the first pressure range.

[0526] When the pressure of the condenser 200 is less than a value smaller than the lower limit of the first pressure range, it means that the load of the compressor is very small. If the compressor 100 is still allowed to work intermittently at this time, there is a waste of energy. Therefore, the valve 11 can be continuously closed at this time to keep the driving path of the flywheel 24 to the diaphragm 3 in an engaged state, so that the air conditioning system can continue to cool or heat.

[0527] Those skilled in the art will understand that obtaining the internal pressure information of the condenser 200 is one of the conditions for successfully implementing the above-mentioned control method. For example, the pressure of the condenser 200 can be obtained in real time during the operation of the compressor motor. Once it is determined that the condenser pressure meets a certain preset condition, the control valve 11 makes a corresponding response action - for example, when it is determined that the condenser pressure is in a set first pressure interval, the valve 11 is alternately opened and closed at a first frequency, and when it is determined that the condenser pressure is greater than a set first pressure threshold, the valve 11 is continuously opened.

[0528] It can also be understood that if the diaphragm compressor 100 of this embodiment is replaced with the structures of the above-mentioned embodiments 6, 7 and 10, the air conditioning system can also be controlled by a method similar to the aforementioned control method. For example, the clutch 37 is engaged or disengaged based on the pressure control of the condenser 200, the electric control valve connected in parallel with the suction valve is opened or closed based on the pressure control of the condenser 200, and the suction valve of the electric control one-way valve structure is actively opened continuously or intermittently based on the pressure control of the condenser 200. The specific scheme can refer to the sixth embodiment, the seventh embodiment, the tenth embodiment and the present embodiment 23, which will not be described in detail here.

Claims

1. A control method for an air conditioning system, the air conditioning system comprising a compressor (100) and a condenser (200) connected in a fluid manner, the compressor (100) being a diaphragm compressor, the compressor (100) comprising: Diaphragm (3), a flywheel (24) for providing driving force to the diaphragm, and A motor (5) for providing driving force for the flywheel; Characterized in that the control method comprises: Acquiring the pressure of the condenser (200) in real time; If it is determined that the pressure of the condenser (200) is in the first pressure interval, the driving path of the flywheel (24) to the diaphragm (3) is controlled to be alternately disconnected and connected at a first frequency.

2. The control method according to claim 1, characterized in that: The control method further comprises: If it is determined that the pressure of the condenser (200) is in a second pressure range that has no intersection with the first pressure range, the drive path is controlled to be alternately disconnected and engaged at a second frequency; wherein the lower limit of the second pressure range is greater than the upper limit of the first pressure range, and the ratio of the engagement time to the disconnection time of the drive path in each cycle of the second frequency is less than the ratio of the engagement time to the disconnection time of the drive path in each cycle of the first frequency.

3. The control method according to claim 1, characterized in that: The control method further comprises: If it is determined that the pressure of the condenser (200) is greater than a first pressure threshold, the driving path is controlled to be continuously disconnected; wherein the first pressure threshold is greater than an upper limit of the first pressure interval.

4. The control method according to claim 1, characterized in that: The control method further comprises: If it is determined that the pressure of the condenser (200) is less than a second pressure threshold, the driving path is controlled to be continuously engaged; wherein the second pressure threshold is less than a lower limit of the first pressure interval.

5. The control method according to any one of claims 1 to 4, characterized in that: The air conditioning system comprises: An electric control device is mechanically connected to the drive path of the flywheel (24) to the diaphragm (3), and the electric control device has a first state of connecting the drive path of the flywheel (24) to the diaphragm (3) and a second state of disconnecting the drive path of the flywheel (24) to the diaphragm (3); A pressure sensor, used to detect the pressure of the condenser (200); A control unit is communicatively connected with the electronic control device and the pressure sensor, so as to obtain the pressure of the condenser (200) from the pressure sensor, and control the electronic control device to selectively be in the first state or the second state based on the pressure.

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