CN115405499B

CN115405499B - Diaphragm pump or diaphragm compressor, control method and controller

Info

Publication number: CN115405499B
Application number: CN202110583519.7A
Authority: CN
Inventors: 高峰; 刘在祥; 陈艳凤; 蔡园丰; 王兵; 牛争艳
Original assignee: Shanghai Xingye Material Technology Co Ltd
Current assignee: Shanghai Xingye Material Technology Co Ltd
Priority date: 2021-05-27
Filing date: 2021-05-27
Publication date: 2024-08-02
Anticipated expiration: 2041-05-27
Also published as: CN115405499A

Abstract

The application relates to a diaphragm pump or a diaphragm compressor, a control method and a controller, wherein the diaphragm pump or the diaphragm compressor comprises: the working chamber, the power chamber, the diaphragm that seals and sets up between working chamber and power chamber, provide the motor of the driving force for the diaphragm; the method comprises the following steps: a flywheel provided on a driving path of the motor to the diaphragm to obtain a driving force from the motor and to supply the driving force to the diaphragm; a power fluid storage chamber in communication with the power chamber for receiving power fluid exhausted from the power chamber and providing power fluid to the power chamber; and the valve is arranged on the communication path between the power fluid storage cavity and the power cavity and is used for switching on and switching off the communication path between the power fluid storage cavity and the power cavity. The diaphragm pump or diaphragm compressor of the present application can intermittently provide large short-time power and/or large short-time power for a long time, which helps to accomplish a part of tasks that were otherwise difficult to accomplish.

Description

Diaphragm pump or diaphragm compressor, control method and controller

Technical Field

The application relates to a diaphragm pump or a diaphragm compressor, a control method and a controller.

Background

The diaphragm pump and the diaphragm compressor are similar in structure, and both include: the device comprises a working chamber, a power chamber, a diaphragm arranged between the working chamber and the power chamber, and a motor for providing power. When the working chamber works, the motor drives the diaphragm to move through the power transmission system, so that the diaphragm extrudes working fluid in the working chamber to do work.

However, in practical applications, for various reasons, for example, in a situation where the power supply is small (such as small photovoltaic power supply), and for example, in a situation where the space where the apparatus can be placed is very tight, a motor with very high power cannot be configured in the diaphragm pump or the diaphragm compressor, so that it cannot perform some work, for example, cannot transport water at a low place to a place with a height of hundreds of meters, cannot compress carbon dioxide as a refrigerant into a high-pressure state or even a liquid state, and the application field is greatly limited.

Disclosure of Invention

The application aims to solve the technical problems that: a diaphragm pump or a diaphragm compressor capable of intermittently supplying a large short-time power and/or a large short-time power for a long time is provided, which is helpful for accomplishing a part of tasks that are difficult to accomplish.

The technical scheme of the application is as follows:

In a first aspect, the present application proposes a diaphragm pump or a diaphragm compressor comprising:

the working chamber is provided with a plurality of working chambers,

The power chamber is provided with a power cavity,

A diaphragm provided in a sealed manner between the working chamber and the power chamber, and

A motor for providing driving force to the diaphragm;

Further comprises:

A flywheel provided on a driving path of the motor to the diaphragm to obtain a driving force from the motor and to supply the driving force to the diaphragm;

A motive fluid storage chamber in communication with the motive chamber for receiving motive fluid expelled from the motive chamber and providing motive fluid to the motive chamber;

and the valve is arranged on the communication path between the power fluid storage cavity and the power cavity and is used for conducting and cutting off the communication path between the power fluid storage cavity and the power cavity.

The valve is an electronically controlled valve communicatively coupled to a controller configured to: the valve is controlled to open or close.

The controlling the valve to open or close includes:

during operation of the motor, the valve is controlled to alternately open and close at a first frequency.

Further comprising a motor speed sensor for detecting a speed of the motor and communicatively coupled to the controller, the controller configured to: the rotation speed of the motor is obtained from the motor rotation speed sensor, and the valve is controlled to be opened or closed based on the rotation speed.

The controlling the valve to open or close based on the rotational speed includes:

If it is determined that the rotational speed is in a first rotational speed interval, controlling the valve to alternately close and open at a first frequency; wherein the rated rotational speed of the motor is in the first rotational speed interval.

The controlling the valve to open or close based on the rotational speed further includes:

if the rotational speed is determined to be less than a first rotational speed threshold, controlling the valve to be continuously opened; wherein the first rotational speed threshold is less than a lower limit of the first rotational speed interval.

If the rotational speed is determined to be greater than a second rotational speed threshold, controlling the valve to be continuously closed; wherein the second rotational speed threshold is greater than an upper limit of the first rotational speed interval.

And a speed reducer is arranged on a driving path from the flywheel to the diaphragm.

In a second aspect, the present application proposes a control method of a diaphragm pump or a diaphragm compressor, the diaphragm pump or the diaphragm compressor comprising:

the diaphragm sheet is provided with a plurality of grooves,

A flywheel for providing driving force to the diaphragm, and

A motor for providing driving force to the flywheel;

the control method comprises the following steps:

during operation of the motor, a drive path of the flywheel to the diaphragm is controlled to alternately disengage and engage at a first frequency.

Before the controlling the drive path of the flywheel to the diaphragm to alternately disconnect and engage at a first frequency, the control method further includes:

And determining that the rotating speed of the motor is in a first rotating speed interval.

The rated rotational speed of the motor is in the first rotational speed interval.

The control method further includes:

controlling the drive path to be alternately disconnected and engaged at a second frequency if it is determined that the rotational speed of the motor is in a second rotational speed interval that is non-intersecting with the first rotational speed interval; the ratio of the engagement duration to the disengagement duration of the driving path in each period of the second frequency is not equal to the ratio of the engagement duration to the disengagement duration of the driving path in each period of the first frequency.

In the controlling the driving paths to be alternately disconnected and connected at a first frequency, the controlling method further includes:

If it is determined that the rotational speed of the motor continuously decreases over a first period of time, controlling the drive path to alternately disconnect and engage at a third frequency; wherein a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the third frequency < a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the first frequency.

In controlling the drive path to be alternately disconnected and connected at a third frequency, the control method further includes:

If it is determined that the rotational speed of the motor continuously decreases for a second period of time, controlling the drive path to alternately disconnect and connect at a fourth frequency; wherein a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the fourth frequency < a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the third frequency.

In the controlling the driving paths to be alternately disconnected and connected at a third frequency, the controlling method further includes:

If it is determined that the rotational speed of the motor continuously increases for a third period of time, controlling the drive path to alternately disconnect and engage at a fifth frequency; the ratio of the engagement duration to the disengagement duration of the driving path in each period of the first frequency is greater than the ratio of the engagement duration to the disengagement duration of the driving path in each period of the fifth frequency is greater than the ratio of the engagement duration to the disengagement duration of the driving path in each period of the third frequency.

In the controlling the driving path of the flywheel to the diaphragm to be alternately disconnected and connected at a first frequency, the control method further includes:

If it is determined that the rotational speed of the motor continuously increases within a fourth time period, controlling the driving path to be alternately disconnected and engaged at a sixth frequency; wherein a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the sixth frequency > a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the first frequency.

In the controlling the driving paths to be alternately disconnected and connected at a sixth frequency, the controlling method further includes:

If it is determined that the rotational speed of the motor continuously decreases for a sixth period of time, controlling the drive path to alternately disconnect and connect at an eighth frequency; and the ratio of the engagement time length to the disconnection time length of the driving path in each period of the sixth frequency is greater than the ratio of the engagement time length to the disconnection time length of the driving path in each period of the sixth frequency.

The control method further includes:

If the rotating speed of the motor is determined to be smaller than a first rotating speed threshold value, controlling the driving path to be continuously disconnected; wherein the first rotational speed threshold is less than a lower limit of the first rotational speed interval.

The control method further includes:

Controlling the drive path to continue engagement if it is determined that the rotational speed of the motor is greater than a second rotational speed threshold; wherein the second rotational speed threshold is greater than an upper limit of the first rotational speed interval.

The diaphragm pump or diaphragm compressor includes:

an electronic control device mechanically connected to a drive path of the flywheel to the diaphragm, the electronic control device having a first state in which the flywheel is coupled to the drive path of the diaphragm and a second state in which the flywheel is decoupled from the drive path of the diaphragm;

and the control unit is in communication connection with the electric control device so as to control the electric control device to be selectively in the first state or the second state.

In a third aspect, the present application proposes a control method of a diaphragm pump or a diaphragm compressor, the diaphragm pump or the diaphragm compressor comprising:

the diaphragm sheet is provided with a plurality of grooves,

A flywheel for providing driving force to the diaphragm, and

A motor for providing driving force to the flywheel;

the control method comprises the following steps:

and if the rotating speed of the motor is determined to be smaller than a first rotating speed threshold value, controlling the flywheel to continuously disconnect the driving path to the diaphragm.

The control method further includes:

Controlling the drive path to continue engagement if it is determined that the rotational speed of the motor is greater than a second rotational speed threshold; wherein the second rotational speed threshold is not less than the first rotational speed threshold.

In the process of controlling the continuous engagement of the drive path, the control method further includes:

alternately disconnecting and engaging a drive path of the flywheel to the diaphragm at a first frequency if the rotational speed of the motor is determined to be within a first rotational speed interval; the lower limit of the first rotation speed interval is larger than the first rotation speed threshold value, and the second rotation speed threshold value is larger than the upper limit of the first rotation speed interval.

In a fourth aspect, the present application proposes a controller comprising:

The memory device is used for storing the data,

A processor coupled to the memory, and

Computer instructions stored in the memory and executable by the processor;

the control method according to the second or third aspect is implemented when the computer instructions are executed by the processor.

The application has at least the following beneficial effects:

The diaphragm pump or the diaphragm compressor of the present application is provided with a flywheel connected to a path from a motor to a diaphragm, and a power fluid storage chamber in fluid communication with a power chamber, and a valve is provided in a communication path between the flywheel and the power chamber. During the operation of the motor, the valve can be alternately opened and closed according to a set frequency, and then the driving path of the flywheel to the diaphragm is alternately disconnected and connected at the frequency, so that the flywheel and the diaphragm do work intermittently in each cycle time of the frequency, and the motor stores energy to the flywheel periodically. In general, in each cycle time of the frequency, the energy provided by the continuously operated motor is balanced with the acting energy consumption of the diaphragm which only acts in a partial period, so that the diaphragm pump or the diaphragm compressor can continuously and stably operate and can intermittently perform large-power and large-force work, thereby being beneficial to the diaphragm pump or the diaphragm compressor to complete partial tasks which are difficult to complete or cannot be completed originally, such as smoothly conveying working fluid to a required position or compressing the working fluid to a required state.

Drawings

Fig. 1 is a longitudinal sectional view of a diaphragm pump in accordance with a first embodiment of the present application.

Fig. 2 is a schematic external view of a diaphragm pump according to a first embodiment of the present application.

Fig. 3 is a schematic partial structure of a transmission system according to a first embodiment of the present application.

Fig. 4 is a partial cross-sectional view of a diaphragm pump in accordance with a first embodiment of the present application.

Fig. 5 is a schematic partial structure of a transmission system according to a first embodiment of the present application.

Fig. 6 is a transmission schematic diagram of a transmission system in accordance with a first embodiment of the present application.

Fig. 7 is a graph showing the relationship between the moving speed of the lower end of the first link and the included angle β in the first embodiment of the present application.

Fig. 8 is a graph of piston travel speed versus angle beta.

Fig. 9 is a variation of fig. 6.

Fig. 10 is a block diagram of the control system of fig. 1.

Fig. 11 is a schematic view showing a partial structure of a diaphragm pump according to the first embodiment of the present application.

Fig. 12 is a longitudinal cross-sectional view of fig. 11.

Fig. 13 is an exploded view of fig. 11.

Fig. 14 is a longitudinal sectional view of the diaphragm pump in the second embodiment of the present application in the first operating state.

Fig. 15 is a longitudinal sectional view of the diaphragm pump in the second working state in the second embodiment of the present application.

Fig. 16 is a schematic view showing a partial structure of a transmission system in the second embodiment of the present application.

Fig. 17 is a longitudinal sectional view of a diaphragm pump in a third embodiment of the present application.

Fig. 18 is a schematic view showing a partial structure of a transmission system in a third embodiment of the present application.

Fig. 19 is a schematic external view of a diaphragm pump in a fourth embodiment of the present application.

FIG. 20 is a longitudinal cross-sectional view of a diaphragm pump according to a fourth embodiment of the present application

Fig. 21 is a schematic partial structure of a transmission system in a fourth embodiment of the present application.

Fig. 22 is a longitudinal sectional view of a diaphragm pump in a fifth embodiment of the present application.

Fig. 23 is a schematic partial structure of a transmission system in a fifth embodiment of the present application.

Fig. 24 is a longitudinal sectional view of a diaphragm pump in a sixth embodiment of the present application.

Fig. 25 is a block diagram of the control system of the clutch of fig. 24.

Fig. 26 is a longitudinal sectional view of a diaphragm pump in a seventh embodiment of the present application.

Fig. 27 is an enlarged view of the portion X1 in fig. 26.

Fig. 28 is a block diagram of the control system of the electronic control valve of fig. 27.

Fig. 29 is a longitudinal sectional view of a diaphragm pump in an eighth embodiment of the present application.

Fig. 30 is an enlarged view of the portion X2 of fig. 29.

Fig. 31 is a block diagram of the control system of the electronic control valve of fig. 30.

Fig. 32 is a longitudinal cross-sectional view of a diaphragm pump according to a ninth embodiment of the present application.

Fig. 33 is a block diagram of the control system of the exhaust valve of fig. 32.

Fig. 34 is a longitudinal sectional view of a diaphragm pump in accordance with an embodiment ten of the present application.

Fig. 35 is a block diagram of the control system of the suction valve of fig. 34.

Fig. 36 is a longitudinal sectional view of a diaphragm pump in an eleventh embodiment of the present application.

Fig. 37 is an enlarged view of the portion X3 in fig. 36.

FIG. 38 is a transverse cross-sectional view of a diaphragm pump according to an eleventh embodiment of the application

Fig. 39 is a schematic diagram showing a partial structure of a transmission system in accordance with an eleventh embodiment of the present application.

Figure 40 is a longitudinal cross-sectional view of a diaphragm pump in accordance with a twelfth embodiment of the present application.

Figure 41 is a longitudinal cross-sectional view of a thirteenth embodiment of the present application.

Fig. 42 is a transverse cross-sectional view of a diaphragm pump in accordance with a thirteenth embodiment of the present application.

Fig. 43 is a longitudinal sectional view of a diaphragm pump in fourteen embodiments of the application.

Fig. 44 is a partially exploded view of a diaphragm pump in accordance with a fourteen embodiment of the present application.

Fig. 45 is a schematic external view of a diaphragm pump according to a fifteenth embodiment of the present application.

Fig. 46 is a longitudinal sectional view of a diaphragm pump in fifteen embodiments of the present application.

Fig. 47 is a partial enlarged view of fig. 46.

FIG. 48 is a schematic view of the portion of FIG. 47 after the push-pull rod has been moved left.

Fig. 49 is a transverse cross-sectional view of a diaphragm pump in accordance with an embodiment fifteen of the present application.

Fig. 50 is a longitudinal sectional view of a diaphragm pump in sixteen embodiments of the application.

Fig. 51 is a longitudinal sectional view of a diaphragm pump in seventeenth embodiment of the present application.

Fig. 52 is a longitudinal cross-sectional view of an eighteen diaphragm pump according to an embodiment of the application.

Fig. 53 is a longitudinal cross-sectional view of a nineteenth septum pump according to an embodiment of the present application.

Fig. 54 is a longitudinal cross-sectional view of a membrane pump in accordance with a twenty-first embodiment of the application.

Fig. 55 is a schematic structural diagram of an air conditioning system according to a twenty-first embodiment of the present application.

Fig. 56 is a block diagram of the control system of the throttle valve of fig. 55.

Fig. 57 is a schematic view of an air conditioning system according to a twenty-second embodiment of the present application.

Fig. 58 is a block diagram of the control system of the electronic control valve of fig. 57.

Fig. 59 is a schematic structural diagram of an air conditioning system according to a twenty-third embodiment of the present application.

Fig. 60 is a block diagram of the control system of the upper valve of the compressor of fig. 59.

In order to facilitate the reader to more clearly observe the structure of the diaphragm pump or the diaphragm compressor, part of the drawing specifically conceals the working fluid and the power fluid, and part of the drawing conceals the guide and movement seat.

Reference numerals illustrate:

a-working fluid, b-power fluid, pivot axis of the O-crankshaft;

1-working chamber, 2-power chamber, 2 a-first half-chamber, 2 b-second half-chamber, 3-diaphragm, 3 a-diaphragm deformation fold, 4-piston, 5-motor, 6-inlet port, 7-outlet port, 8-suction valve, 9-discharge valve, 10-power fluid storage chamber, 11-valve, 12-decelerator, 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, 21-sixth connecting rod, 22-pivot, 23-guide seat, 23 a-guide groove, 24-flywheel, 25-coupling, 26-bellows, 27-barrier net, 28-linear bearing, 29-hoop, 30-rigid collar, 31-flexible ring piece, 31a deformation fold of flexible ring piece, 32-bearing seat, 32 a-annular groove, 33-housing, 34-motor rotation speed sensor, 35-controller, 36-37-electric control valve, 39-electric control valve, and electronic control cover;

100-compressor, 200-condenser, 300-throttle valve, 400-evaporator.

Detailed Description

In the description of the present specification and claims, the terms "first," "second," and the like, if any, are used merely to distinguish between the described objects and do not have any sequential or technical meaning. Thus, an object defining "first," "second," etc. may explicitly or implicitly include one or more such objects. Also, the terms "a" or "an" and the like do not denote a limitation of quantity, but rather denote the presence of at least one, and "a plurality" of "are used to indicate no less than two. The term "plurality" as used herein means not less than two.

In the description of the present application and in the claims, the terms "connected," "mounted," "secured," and the like are to be construed broadly unless otherwise indicated. For example, "connected" may be connected in a split manner, or may be integrally connected; can be directly connected or indirectly connected through an intermediate medium; either non-detachably or detachably. The specific meaning of the aforementioned terms in the present application can be understood by those skilled in the art according to the specific circumstances.

In the description of the present specification and claims, if there is an azimuth or positional relationship indicated by terms such as "upper", "lower", "horizontal", etc., based on the azimuth or positional relationship shown in the drawings, it is only for convenience of clarity and simplicity to describe the present application, rather than to indicate or imply that the elements referred to must have a specific direction, be constructed and operated in a specific azimuth, these directional terms are relative concepts for relative description and clarity, and may be changed accordingly in accordance with the change in azimuth in which the components are placed in the drawings. For example, if the device is turned over in the figures, elements described as "below" other elements would then be oriented "above" the other elements.

In the description of the present specification and claims, the terms "based on," "according to," if any, are used to describe one or more factors that affect a determination. The term does not exclude additional factors affecting the determination. That is, the determination may be based solely on these factors or at least in part on these factors. For example, the phrase "B is determined based on A", in which case A is a factor affecting the determination of B, which phrase does not exclude that the determination of B may also be based on C.

In the description of the present specification and claims, the term "configured to" if present, is generally interchangeable with "having … capabilities", "designed to", "used for" or "capable of" depending on the context.

Embodiments of the present application will now be described with reference to the accompanying drawings.

Embodiment one:

Fig. 1 and 2 show a diaphragm pump, which, like some of the prior art diaphragm pumps, also includes an inlet port 6 and an outlet port 7 for a working fluid a, a working chamber 1 fluidly connected between the inlet port 6 and the outlet port 7, a power chamber 2, a diaphragm 3 hermetically disposed 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 provided between the inlet port 6 and the working chamber 1, and a discharge valve 9 is provided between the outlet port 7 and the working chamber 1. It will be appreciated that the construction of the diaphragm pump of this embodiment is equally applicable to diaphragm compressors.

The "diaphragm 3 disposed between the working chamber and the power chamber in a sealing manner" means that the diaphragm 3 is disposed not only between the working chamber 1 and the power chamber 2, but also seals the working chamber 1 and the power chamber 2 from each other, so that the working fluid a in the working chamber 1 does not enter the power chamber 2, and the power fluid b in the power chamber 2 does not enter the working chamber 1.

The suction valve 8 and the discharge valve 9 are both check valves. Referring to fig. 1, in use, the power chamber 2 is filled with a power fluid b. When the motor 5 drives the piston 4 to move leftward in fig. 1, the internal pressure of the power chamber 2 < the internal pressure of the working chamber 1, and the diaphragm 3 deforms leftward. The working chamber 1 increases in volume and decreases in internal pressure. At this time, the suction valve 8 is opened when the left pressure is smaller than the right pressure, and the discharge valve 9 is closed when the left pressure is smaller than the right pressure. The working fluid a flowing at the inlet 6 enters the working chamber 1 through the open suction valve 8. When the motor 5 drives the piston 4 to move by pushing the power fluid b rightward in fig. 1, the diaphragm 3 deforms rightward, and the volume of the working chamber 1 decreases. At this time, the suction valve 8 is closed when the left pressure is higher than the right pressure, and the discharge valve 9 is opened when the left pressure is higher than the right pressure. The working fluid a in the working chamber 1 is discharged to the discharge port 7 through the open discharge valve 9, and is discharged through the discharge port 7. The operating motor 5 reciprocates the piston 4 in the left and right directions in fig. 1, thereby continuously sucking the working fluid supplied to the inlet port 6 into the working chamber 1, and then discharging the working fluid a sucked into the working chamber 1 to the discharge port 7, and discharging from the discharge port 7. Thus, the working fluid a is continuously transported.

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 by virtue of the power fluid b filled in the power chamber, so that the working fluid a is pumped in and pushed out. The motor 5 is operated to drive the diaphragm 3 to perform work, and the 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 a driving path of the motor 5 to the diaphragm 3, and the driving path of the motor 5 to the diaphragm 3 comprises the transmission system, the piston 4 and the power fluid b filled in the power chamber.

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 purchased directly in the market, so that they will not be described in detail herein.

The power fluid b is usually hydraulic oil, the working fluid a is usually water, and a diaphragm pump is usually used for delivering water.

Referring again to fig. 1, the diaphragm pump is further provided with a power fluid storage chamber 10 and a third valve 11 in addition to the above-described suction valve 8 and discharge valve 9. Wherein the power fluid storage chamber 10 communicates with the power chamber 2 for receiving the power fluid b discharged from the power chamber 2 and supplying the power fluid b to the power chamber 2. A valve 11 is provided on the communication path of the power fluid storage chamber 10 and the power chamber 2 for switching on and off the communication path of the power fluid storage chamber 10 and the power chamber 2.

Furthermore, the diaphragm pump is provided with a flywheel 24 and a reduction gear 12 on the transmission path of the motor 5 and the piston 4, i.e. on the aforementioned transmission system. Wherein 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 speed reducer 12, and the power provided by the motor 5 is transmitted to the speed reducer 12 through the flywheel 24. The speed 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 speed reducer 12 to be transmitted to the downstream piston 4 and the diaphragm 3. The speed reducer 12 serves to reduce the gear ratio to raise the torque, and thus the driving force received by the piston 4 and the diaphragm 3. The flywheel 24 functions to store energy to provide sufficient driving power and force to the diaphragm 3.

The diaphragm pump of the present embodiment is provided with the power fluid storage chamber 10, the valve 11 and the flywheel 24, and can perform work to the outside intermittently with high power under the condition that the output power of the motor 5 is small. The specific analysis is as follows:

Reference is made to figure 1. In the starting stage of the motor 5, the rotation speed of the motor 5 and the flywheel 24 is low, the kinetic energy of the flywheel is low, and the motor 5 and the flywheel 24 cannot drive the diaphragm 3 to do work in a high power mode. At this time, the valve 11 is opened. When the piston 4 moves right, the hydraulic oil serving as the power fluid b in the power chamber 2 easily flows into the power fluid storage cavity 10 through the valve 11 under the thrust action of the piston 4, and the hydraulic oil in the power chamber 2 does not obviously push the diaphragm 3 with higher load to deform and do work. When the piston 4 moves to the left, the hydraulic oil of the power fluid storage chamber 10 is again easily drawn into the power chamber 2. It is clear that neither pushing hydraulic oil from the power chamber 2 into the power fluid storage chamber 10 nor drawing hydraulic oil from the power fluid storage chamber 10 into the power chamber 2 consumes more power. In the process, the motor 5 and the flywheel 24 provide less power for the piston 4, the motor 5 mainly applies work to 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 rotating speed of the flywheel 24 is higher and the kinetic energy is larger. Obviously, the rotational speed of the motor 5 is positively correlated with the rotational speed of the flywheel 24. In particular, in the present embodiment, the rotation speed ratio of the motor 5 to the flywheel 24 is 1, and the rotation speed ratio of the motor 5 to the flywheel 24 is 1. When the rotational speed of the motor 5 has risen to a set value, for example when the motor 5 reaches the rated rotational 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 of the power chamber 2 cannot enter the power fluid storage chamber 10. The piston 4 moving rightward can only push the hydraulic oil in the power chamber 2 to press the diaphragm 3 rightward, so that the diaphragm 3 deforms rightward to press the working fluid a in the working chamber 1 to do work. Even if the working load of the diaphragm pump is large, the flywheel 24 storing a large amount of kinetic energy can apply a large rightward pushing force to the piston 4, so that the hydraulic oil in the power chamber 2 can push the diaphragm 3 to deform rightward, and a large enough pressure is applied to the working fluid a in the working chamber 1, so that high-power work on the working fluid a, such as pushing water to hundreds of meters, is completed.

The power source of the diaphragm pump is a motor 5, and the motor 5 drives the diaphragm 3 to move through the flywheel 24 and the piston 4 which move in sequence to do work. Based on this, it is apparent that there is a power relationship: the motor 5 provides driving force to the flywheel 24, the piston 4 and the diaphragm 3, the flywheel 24 provides driving force to the piston 4 and the diaphragm 3, and the piston 4 provides driving force to the diaphragm 3.

If the valve 11 is kept in the closed state all the time during the operation of the motor 5. The motor 5 as a power source cannot supply energy for continuously applying large power to the diaphragm 3 because of its small power. The energy consumed by the diaphragm 3 to do work is derived from the conversion of the newly added electrical energy by the motor 5 and the kinetic energy originally stored in the flywheel 24. Therefore, in the case that the new energy continuously supplied by the motor 5 cannot meet the continuous work requirement of the diaphragm 3, the flywheel 24 supplies the supplementary energy for the work of the diaphragm 3. This results in a continuous decrease in the kinetic energy of the flywheel 24, with a decreasing rotational speed. This not only results in an unstable operating speed of the motor 5, but also eventually renders the diaphragm 3 inoperable due to insufficient energy supply. Thus, the present embodiment provides a diaphragm pump control method to solve the foregoing problems, the control method including:

S101, during operation of the motor 5, the valve 11 is controlled to alternately open and close at a first frequency.

That is, during operation of the motor 5, the valve 11 is alternately opened for a twenty-third period of time-closing for a twenty-fourth period of time-opening for a twenty-third period of time-closing for a twenty-fourth period of time … … at a set first frequency. That is, the drive 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 open period and a continuous close period, the values of which can be set as desired. It will be appreciated that the greater the ratio of the open duration to the closed duration of the valve 11, the greater the energy storage time duty cycle of the flywheel 24 during each cycle; the smaller the ratio of the open period to the closed period of the valve 11, the smaller the energy storage time duty ratio of the flywheel 24 in each cycle.

For example, during operation of the motor, the valve 11 is alternately opened and closed at a frequency of 10 times/minute and 2 seconds each for 4 seconds. Wherein 10 times/minute means that the valve is opened 10 times every 1 minute, the valve is closed 10 times, and the opening and closing are alternately performed. 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 … ….

During operation of the motor 5, the valve 11 is alternately opened and closed at a set first frequency, so that the driving path of the flywheel 24 to the diaphragm 3 is alternately disconnected and engaged, and the flywheel 24 and the diaphragm 3 are caused to intermittently perform work during each cycle time of the first frequency, and the motor 5 periodically stores energy to the flywheel 24. Typically, during each cycle time, for example, 2+4=6 seconds as described above, the energy provided by the continuously operating motor 5 is balanced with the energy consumed to perform work on the diaphragm 3 for only a portion of the period (e.g., 4 seconds as described above), so that the diaphragm pump can continue to operate stably.

It will be appreciated that when the valve 11 is closed, the flywheel 24 engages the drive path of the diaphragm 3, and the length of time the valve is closed = the length of time the flywheel engages the drive path of the diaphragm. When the valve 11 is opened, the flywheel 24 is disconnected from the drive path to the diaphragm 3, and the valve opening period=the flywheel disconnection period from the drive path to the diaphragm. For convenience of description, herein, the engagement time period of the flywheel 24 to the drive path of the diaphragm 3 is simply referred to as "engagement time period of the drive path", and the disconnection time period of the flywheel 24 to the drive path of the diaphragm 3 is simply referred to as "disconnection time period of the drive path".

If the control strategy of S101 is adopted when the rotational speed of the motor 5 is low (e.g. just started), it is not appropriate. Therefore, the control strategy of S101 may be adopted when it is determined that the rotation speed of the motor 5 is in the set first rotation speed section. That is, during operation of the motor 5, if it is determined that the current rotational speed of the motor 5 is in the first rotational speed interval, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the first frequency.

The first rotation speed range is preferably a range around the rated rotation speed of the motor 5. For example, if the rated rotational speed of the motor 5 is 10000 rpm, the first rotational speed section may be selected to be a 9000-11000 rpm section.

Of course, the switching frequency of the valve 11 may be adjusted correspondingly when the motor 5 is in different rotation speed intervals. For example if it is determined that the rotation speed of the motor 5 is in a second rotation speed interval different from and without intersection with the first rotation speed interval and smaller than the first rotation speed interval, the valve 11 is alternately opened and closed at a second frequency different from the first frequency. That is, if it is determined that the rotation speed of the motor 5 is in the second rotation speed section, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the second frequency. The second frequency differs from the first frequency mainly in that: the ratio of the engagement duration to the disengagement duration of the flywheel to the diaphragm drive path in each cycle of the second frequency is not equal to the ratio of the engagement duration to the disengagement duration of the flywheel to the diaphragm drive path in each cycle of the first frequency.

S102, in the process of alternately opening and closing the control valve 11 at the first frequency in S101 described above, if a continuous decrease in the rotation speed of the motor 5 is detected for a first period of time, the control valve 11 is alternately opened and closed at the third frequency; wherein the ratio of the closing time period to the opening time period of the valve 11 in each period of the third frequency < the ratio of the closing time period to the opening time period of the valve 11 in each period of the first frequency. The aforementioned first period is typically several to several tens times the single period of the first frequency.

That is, in the process of controlling the driving path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and connected at the first frequency at S101, if it is determined that the rotation speed of the motor 5 is continuously decreased for the first time period, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and connected at the third frequency. Wherein a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency < a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency.

During the operation of the motor 5, its rotational speed may vary due to certain factors, if it is detected that the rotational speed of the motor 5 decreases continuously over a set, longer first period of time, for example, two minutes, indicating that during this first period of time the energy provided by the motor 5 is less than the power consumption of the diaphragm 3. Therefore, it is necessary to reduce the work time duty of the diaphragm 3, or increase the dead time duty of the flywheel 24. Thus, upon detecting that the rotational speed of the motor 5 continuously decreases for the first period, the control valve 11 is alternately opened and closed at the third frequency. Wherein a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency < a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency.

Illustratively, the third frequency may be: valve 4 seconds open-valve 2 seconds close-valve 4 seconds close-valve 2 seconds … …, still cycling 10 times per minute. Of course, the third frequency may also be adjusted to cycle the switch 3 times, 6 or 20 times per minute, etc.

The person skilled in the art knows that determining whether the rotational speed of the motor 5 decreases continuously within a set first period of time may be achieved by: in the above-described process of alternately opening and closing the control valve 11 at the first frequency S101, the rotational speed of the motor 5 is periodically acquired, and if the N motor rotational speeds acquired in the consecutive N periods have a tendency to gradually decrease, and the total duration of the aforementioned N periods is equal to or greater than the first duration, it is indicated that the rotational speed of the motor 5 continuously decreases for the first duration. In some embodiments, a decrease threshold may also be set, the valve 11 being controlled to open and close alternately at the third frequency only if the rotational speed of the motor 5 decreases continuously over a first time period and the decrease value exceeds the set decrease threshold. Obviously, this control manner of setting the decrease threshold is included in the range of "if the rotation speed of the motor 5 is detected to decrease continuously for the first period, the control valve 11 is alternately opened and closed at the third frequency".

S103, in the process of alternately opening and closing the control valve 11 at the third frequency in S102 described above, if it is detected that the rotation speed of the motor 5 is continuously decreased for the second period of time, the control valve 11 is alternately opened and closed at the fourth frequency; wherein the ratio of the closing time period to the opening time period of the valve 11 in each period of the fourth frequency < the ratio of the closing time period to the opening time period of the valve 11 in each period of the third frequency.

That is, in the process of controlling the driving 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 rotation speed of the motor 5 is continuously decreased for the second period of time, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the fourth frequency; wherein a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the fourth frequency < a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the third frequency.

The rotation speed of the motor 5 is continuously reduced during the second period, which means that during this second period the energy supplied by the motor 5 is still less than the energy consumption of the work of the membrane 3. Therefore, it is necessary to further reduce the work time ratio of the diaphragm 3, or to further increase the dead time ratio of the flywheel 24. Thus, upon detecting that the rotational speed of the motor 5 continues to decrease continuously for the second period of time, the control valve 11 is alternately opened and closed at the above-described fourth frequency.

Illustratively, at this fourth frequency: valve 5 seconds open-valve 1 second close-valve 1 second … … cycles still 10 times per minute. Also exemplary, valve 10 seconds open-valve 2 seconds close-valve 2 seconds … ….

S104, in the process of alternately opening and closing the control valve 11 at the third frequency in S102 described above, if it is detected that the rotation speed of the motor 5 is continuously increased for the third period of time, the control valve 11 is alternately opened and closed at the fifth frequency; wherein the ratio of the closing time period to the opening time period of the valve 11 in each period of the first frequency > the ratio of the closing time period to the opening time period of the valve 11 in each period of the fifth frequency > the ratio of the closing time period to the opening time period of the valve 11 in each period of the third frequency.

That is, in the process of controlling the driving 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 rotation speed of the motor 5 is continuously increased for the third period of time, the driving 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 disengagement duration of the drive path in each cycle of the first frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the fifth frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency.

The rotation speed of the motor 5 increases continuously during a third period of time, which means that during this third period of time the energy provided by the motor 5 is greater than the energy consumed for the work of the membrane 3. Therefore, the work-doing time duty ratio of the diaphragm 3 can be properly increased, or the idle energy-storage time duty ratio of the flywheel 24 can be properly reduced, so as to improve the work-doing efficiency of the motor 5. Thus, upon detecting that the rotational speed of the motor 5 continuously increases for the third period of time, the control valve 11 is alternately opened and closed at the above-described fifth frequency.

Illustratively, at the fifth frequency: open valve 3.5 seconds-close valve 2.5 seconds-open valve 3.5 seconds-close valve 2.5 seconds … ….

S105, in the process of alternately opening and closing the control valve 11 at the first frequency in S101 described above, if it is detected that the rotation speed of the motor 5 continuously increases in the fourth time period, the control valve 11 is alternately opened and closed at the sixth frequency; wherein the ratio of the closing time period to the opening time period of the valve 11 in each period of the sixth frequency > the ratio of the closing time period to the opening time period of the valve 11 in each period of the first frequency.

That is, in the process of S101 controlling the driving path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and connected at the first frequency, if it is determined that the rotation speed of the motor 5 is continuously increased for the fourth time period, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and connected at the sixth frequency; wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the sixth frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency.

The rotation speed of the motor 5 decreases continuously during the fourth period, which means that during this fourth period the energy supplied by the motor 5 is greater than the energy consumption of the diaphragm 3. Therefore, the work time duty ratio of the diaphragm 3 can be increased, or the idle energy storage time duty ratio of the flywheel 24 can be shortened, so that the work efficiency of the motor 5 can be improved. Thus, upon detecting that the rotational speed of the motor 5 continuously decreases in the fourth time period, the control valve 11 is alternately opened and closed at the sixth frequency.

Illustratively, the sixth frequency may be: the valve was opened 4 seconds-closed valve 11 seconds-opened valve 4 seconds-closed valve 11 seconds … …, and the switch was cycled 4 times per minute.

S106, in the above-described process of S105 in which the control valve 11 is alternately opened and closed at the sixth frequency, if it is detected that the rotation speed of the motor 5 is continuously increased for the fifth period of time, the control valve 11 is alternately opened and closed at the seventh frequency. Wherein the ratio of the closing time period to the opening time period of the valve 11 in each period of the seventh frequency > the ratio of the closing time period to the opening time period of the valve 11 in each period of the sixth frequency.

That is, in the process of controlling the driving 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 rotation speed of the motor 5 is continuously increased for the fifth period of time, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the seventh frequency; wherein a ratio of an engagement time length to an off time length of the driving path in each period of the seventh frequency > a ratio of an engagement time length to an off time length of the driving path in each period of the sixth frequency.

The rotation speed of the motor 5 increases continuously during the fifth period, which means that during this fifth period the energy supplied by the motor 5 is still greater than the energy consumption of the work of the membrane 3. Therefore, the work time duty ratio of the diaphragm 3 can be further increased, or the idle energy storage time duty ratio of the flywheel 24 can be further reduced, so that the work efficiency of the motor 5 is further improved. Thus, upon detecting that the rotational speed of the motor 5 continues to continuously decrease for the fifth period, the control valve 11 is alternately opened and closed at the seventh frequency described above.

Illustratively, at the seventh frequency: open valve 4 seconds-close valve 12 seconds-open valve 4 seconds-close valve 12 seconds … ….

S107, in the above-described process of S105 in which the control valve 11 is alternately opened and closed at the sixth frequency, if it is detected that the rotation speed of the motor 5 is continuously decreased for the sixth 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 period of the sixth frequency > the ratio of the closing time period to the opening time period of the valve 11 in each period of the eighth frequency > the ratio of the closing time period to the opening time period of the valve 11 in each period of the first frequency.

That is, in the process of controlling the driving 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 rotation speed of the motor 5 is continuously increased for the sixth period of time, the driving 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 on-time to the off-time of the drive path in each cycle of the sixth frequency > the ratio of the on-time to the off-time of the drive path in each cycle of the eighth frequency > the ratio of the on-time to the off-time of the drive path in each cycle of the first frequency.

The rotation speed of the motor 5 decreases continuously during a sixth period, which means that during this sixth period the motor 5 provides less energy than the energy consumed for doing work by the membrane sheet 3. Therefore, the work time ratio of the diaphragm 3 can be appropriately reduced, or the dead time ratio of the flywheel 24 can be appropriately increased. Thus, upon detecting that the rotational speed of the motor 5 continuously increases for the sixth period, the control valve 11 is alternately opened and closed at the above-described eighth frequency.

Illustratively, at the eighth frequency: open valve 4 seconds-close valve 10 seconds-open valve 4 seconds-close valve 10 seconds … ….

S108, if it is detected that the rotational speed of the motor 5 is less than the first rotational speed threshold, the control valve 11 is continuously opened; wherein the first rotational speed threshold is less than the lower limit of the first rotational speed interval.

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

The first rotational speed threshold is a relatively small value that is less than the lower limit of the first rotational speed interval. When the rotational speed of the motor 5 is less than the first smaller rotational speed threshold, it is indicated that the energy of the motor 5 and the flywheel 24 is severely insufficient, so that the valve 11 can be continuously opened at this time, and the driving path of the flywheel 24 to the diaphragm 3 is kept in a disconnected state, so that the motor 5 is prevented from being severely overloaded.

S109, if it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold value in the process of continuously opening the control valve 11 in S108, the control valve 11 is continuously closed; wherein the second rotation speed threshold value is not smaller than the first rotation speed threshold value.

That is, if it is determined that the rotational speed of the motor 5 is greater than the second rotational speed threshold value during the continuous disconnection of the drive path of the flywheel 24 to the diaphragm 3, the drive path of the flywheel 24 to the diaphragm 3 is controlled to be continuously engaged; wherein the second rotational speed threshold is not less than the first rotational speed threshold.

It will be appreciated that after the execution of S108 described above, the flywheel 24 is always kept in an empty energy storage state, and the energy provided by the motor 5 is all converted into kinetic energy of the flywheel 24. When the rotational speed of the motor 5 and the flywheel 24 is sufficiently high and the kinetic energy is sufficiently high, there is a waste of energy if the valve 11 is still kept in an open state, and the diaphragm pump runs empty. Thus, when it is detected that the rotational speed of the motor 5 is greater than the second rotational speed threshold value, the valve 11 is switched from the continuously open state to the continuously closed state, so that the flywheel 24 is continuously engaged with the driving path of the diaphragm 3, and the flywheel 24 is continuously driven to apply work to the diaphragm 3.

It is to be understood that in the present application, "continuous" in "continuous open" and "continuous closed" is a relative concept with "alternating" in "alternately open and closed". Continuously open means holding the valve in an open state, and continuously closed means holding the valve in a closed state; and alternately opening and closing the valve, the valve preset time period and the valve preset time period are periodically opened and closed at a set frequency.

It is to be understood that the execution of S109 is not necessarily premised on S108. In other embodiments, the valve 11 may be controlled to continue to close whenever the rotational speed of the motor 5 is detected to be greater than the second rotational speed threshold, regardless of the operating state of the valve 11 at that time.

The second rotational speed threshold should not be smaller than the first rotational speed threshold, and the second rotational speed threshold is preferably a value that is not in the above-described first rotational speed section. More preferably, the second rotational speed threshold is a value greater than the upper limit of the first rotational speed interval.

Obviously, in the process of continuously closing the control valve 11 at S109 described above, if it is detected that the rotational speed of the motor 5 is returned to the aforementioned first rotational speed section, the controllable valve 11 continues to be alternately opened and closed at the first frequency.

In addition, we can also dispense with the above strategy of S101-S107, using the strategies of S108 and S109 alone to control the diaphragm pump:

That is, if it is determined that the rotational speed of the motor 5 is less than the first rotational speed threshold value, the flywheel 24 is controlled to continuously disconnect the drive path to the diaphragm 3. If the rotation speed of the motor 5 is determined to be greater than the second rotation speed threshold value, controlling the flywheel 24 to continuously engage with the driving path of the diaphragm 3; wherein the second rotational speed threshold is not less than the first rotational speed threshold. In this control scheme using the S108 and S109 strategies alone, the second rotational speed threshold may be generally equal to the first rotational speed threshold. The disadvantages are: the rotational speed of the motor 5 may be very unstable.

As shown in fig. 10, in order to better implement the control strategy of S101-S109 described above, the valve 11 of the present embodiment employs an electronically controlled valve that can be opened and closed electronically, and a motor speed sensor 34 for detecting the speed of the motor 5 is also provided, both the motor speed sensor 34 and the valve 11 being communicatively connected to the controller 35. The controller 35 is configured to acquire the rotation speed of the motor 5 from the motor rotation speed sensor 34 and control the opening and closing of the valve 11 based on the rotation speed to realize the control method described above. It is to be noted that the opening and closing of the control valve 11 may not be based on the rotation speed of the motor 5. In other embodiments of the present application, motor speed sensor 34 is eliminated and valve 11 "is controlled to alternately open and close at a first frequency using only controller 35 in communication with valve 11.

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, which when executed by the processor, implement the various control methods described above.

Such as:

During operation of the motor 5, the controller 35 acquires the rotational speed of the motor 5 from the motor rotational speed sensor 34;

if it is determined that the rotational speed of the motor 5 is in the first rotational speed interval, the controller 35 sends a control command to the electronically controlled valve 11 to control the valve 11 to alternately open and close at the first frequency.

And, for example:

if it is determined that the rotational speed of the motor 5 is less than the first rotational speed threshold, the controller 35 sends a command signal to the electronically controlled valve 11 to control the valve 11 to be continuously opened;

If it is determined that the rotational speed of the motor 5 is greater than the second rotational speed threshold, the controller 35 sends a different command signal to the electronically controlled valve 11 to control the valve 11 to continuously close; wherein the second rotation speed threshold value is not smaller than the first rotation speed threshold value.

For another example:

during operation of the motor 5, the controller 35 causes the valve 11 to alternately open and close at a first frequency by receiving a user command (e.g., depressing an operating button connected to the controller).

In the description of the control method described above, the "opening" of the valve 11 generally includes two cases: 1) If the valve 11 is originally in the closed state, the controller 35 sends a command signal to the valve 11 to control the valve 11 to switch to the open state. 2) If the valve 11 is already in an open state, for example, if the valve 11 is a normally open valve, the controller 35 may not operate the valve 11, or may send a command signal to the valve 11 to cause the valve 11 to open.

Similarly, for a "closed" valve 11, two situations are also generally included: 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 already in a closed state, such as if the valve 11 is a normally closed valve, the controller 35 may not act on the valve 11 or may send a command signal to the valve 11 to cause the valve 11 to close.

Thus, if the valve 11 is a normally closed valve, the "control valve 11 is alternately opened and closed at a first frequency", this can be achieved: the controller 35 alternately transmits and stops transmitting command signals for opening the valve to the valve 11 at a first frequency. When the controller 35 transmits a command signal for opening the valve 11, the valve 11 is opened; when the controller 35 stops sending the command signal for opening the valve 11, the valve 11 is automatically closed. The controller 35 stops sending the command signal for opening the valve 11 and causes the normally closed valve 11 to automatically close, and the term "control valve closing" as used herein is also included. The only thing is that it "controls" the valve 11 to close by stopping sending the relevant signal or what is called a non-acting way.

The valve 11 is typically a solenoid valve, and the valve 11 is preferably a normally closed valve or a normally open valve for simplicity of control.

Those skilled in the art will appreciate that: the acquisition of the rotation speed information of the motor 5 is one of the conditions that can smoothly implement the control method of S101-S109 described above, and for example, the rotation speed of the motor 5 may be acquired in real time during the operation of the motor 5, and once it is determined that the motor rotation speed satisfies the corresponding condition, the control valve 11 makes a corresponding response action, such as alternately opening and closing the control valve 11 at a first frequency when it is determined that the motor rotation speed is in a preset first rotation speed interval, and such as continuously opening the control valve 11 when it is determined that the motor rotation speed is greater than a preset second rotation speed threshold.

As described above, the motor 5 does work at high speed, and one reason is that the flywheel 24 is in a high-speed motion state at this time, and has large kinetic energy, so that the flywheel 24 with a large amount of kinetic energy stored therein can work at high speed. Therefore, by properly increasing the mass of the flywheel 24, preferably more than 5kg, the kinetic energy of the flywheel 24 in a high-speed state can be improved, and the mass of the flywheel 24 can be further improved to further improve the short-time power of the diaphragm pump.

The flywheel 24 is typically made of metal or carbon fiber.

Some motors 5 have smaller output power when starting or running at low speed, and only after the rotation speed of the motor 5 reaches a certain value, the motor has considerable output power, which is one of the reasons why we adopt the design.

It will be appreciated that even when the motor 5 is operating at high speed, its power is not significantly increased. As long as the kinetic energy of the flywheel 24 is sufficiently large at this time, large power can be applied to the outside only by the inertia of the flywheel 24. The kinetic energy of the flywheel 24 mainly comes from the speed thereof, and the upper speed limit of the flywheel 24 depends on the motor 5, so that the motor 5 can be selected as a high-speed motor with rated rotation speed not less than 10000 r/min. Of course, the speed of the transfer system and the piston 4 cannot be too fast, otherwise mechanical damage is easily caused. Therefore, when the rated rotational speed of the motor 5 is large, it is preferable to provide the speed reducer 12 in the transmission system, so that mechanical damage can be reduced, and the driving force applied to the diaphragm 3 can be raised.

The motor rotation speed sensor 34 may directly detect the rotation speed of the motor 5, or may indirectly detect the rotation speed of the motor 5 by detecting the speed of other elements in driving connection with the motor 5, for example, directly detect the rotation speed of the flywheel 24 or the speed reducer 12 or the crankshaft 13 described below. Even if the rotational speed of the motor 5 can be indirectly determined by detecting other physical quantities related to the rotational speed of the motor, the sensor can be regarded as a motor rotational speed sensor as long as the related physical quantity detected by the sensor has high correlation with the rotational speed of the motor 5. The motor rotation speed sensor 34 may directly or indirectly detect the rotation speed of the motor 5, which is not limited by the present application.

The present embodiment arranges the power fluid storage chamber 10 above the power chamber 2 so that when the valve 11 is in an open state, the power fluid b (hydraulic oil) in the power fluid storage chamber 10 automatically flows into the power chamber 2 with a larger volume (when the piston retreats) under the self-gravity, so that the transmission of the power fluid b between the power fluid storage chamber 10 and the power chamber 2 is more smooth.

The power fluid storage chamber 10 is formed in a square tank.

The above-mentioned transmission system for connecting the piston 4 and the motor 5 adopts a crankshaft connecting rod structure, and is specifically as follows:

Referring to fig. 1, 3 and 4, the transmission system includes the flywheel 24, the reduction gear 12, the crankshaft 13, the first connecting rod 14, the second connecting rod 15 and the push-pull rod 16, which are sequentially arranged in the transmission direction. The input shaft of the speed reducer 12 is connected with the output shaft of the motor 5 through a coupler 25, and the output shaft of the speed reducer 12 is connected with one end of the crankshaft 13 through the coupler 25. The other end of the crankshaft 13 is pivotally supported on a housing 33 of the diaphragm pump. One end of the first connecting rod 14 is pivotally connected to a curved portion of the crankshaft 13, and the other end is pivotally connected to one end of the second connecting rod 15 through a pivot 22. The other end of the second link 15 is pivotally connected to the push-pull rod 16 by a second pivot 22. The other end of the push-pull rod 16 is fixedly connected with the piston 4, but it is of course also possible to pivotally connect the other end of the push-pull rod 16 with the piston 4.

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 a housing 33. The push-pull rod 16 is a straight rod extending from side to side (i.e., extending straight along the direction of movement of the piston 4).

Referring again to fig. 1, in order to ensure that the pivot 22 pivotally connecting the second link 15 and the push-pull rod 16 can only move horizontally in the front-rear direction perpendicular to the paper surface in fig. 1 during operation, thereby better converting the rotational motion of the crankshaft 13 into the left-right motion of the push-pull rod 16, the present embodiment fixedly provides a guide seat 23 in the above-mentioned transmission chamber 17, a guide groove 23a extending in the front-rear direction perpendicular to the paper surface (perpendicular to the movement direction of the piston) is formed in the guide seat 23, and the pivot 22 pivotally connecting the second link 15 and the push-pull rod 16 is slidably disposed in the guide groove 23 a.

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, as shown in fig. 1 and 4. Of course, the guide 23 may be a separate component connected to the housing 33, as shown in fig. 5.

In operation, the motor 5 drives the crankshaft 13 to pivot about the pivot axis O via the reduction gear 12. The crankshaft 13 rotates (revolves) one end of the first connecting rod 14 about the pivot axis O of the crankshaft. The other end of the first link 14 drives one end of the second link 15 to reciprocate along the guide groove 23 a. The other end of the second connecting rod 15 drives the push-pull rod 16 to reciprocate in the left-right direction in fig. 1.

Obviously, the above structural design is equally applicable to diaphragm compressors for compressing working fluid.

In many application scenarios, the volume of the working chamber 1 is smaller and smaller during the movement of the piston 4 of the diaphragm pump or the diaphragm compressor in the direction of the diaphragm 3, and the internal pressure of the working chamber is larger and larger (especially when the gaseous fluid in the working chamber is compressed) when the working fluid a in the working chamber is not discharged or is not discharged in the process. The piston 4 is therefore subjected to a greater and greater reaction force exerted by the power fluid b in a direction away from the diaphragm 3, which requires that the push-pull rod 16 must have the capacity to provide a greater and greater thrust force to the piston 4 in order to ensure the proper functioning of the diaphragm pump or diaphragm compressor, which places a greater demand on the output power of the motor 5. It is ingenious that even if the output power, especially the output torque, of the motor 5 is not changed in this process, the driving force applied by the push-pull rod 16 to the piston 4 can be larger and larger in the process of right-shifting the piston 4, and the method is perfectly adapted to the application scenario, and specifically analyzed as follows:

As shown in fig. 6 and referring to fig. 4 and 5, an acute angle between the second connecting rod 15 and the push-pull rod 16 is set to be α, and an angle between the curved portion of the crankshaft 13 and the horizontal plane is set to be β=0 in fig. 5. When the crankshaft 13 rotates clockwise about the pivot axis O in fig. 6, the left end of the second link 15 is driven by the crankshaft 13 to move downward through the first link 14, so as to push the push-pull rod 16 to move rightward, and in this process, the included angle β gradually increases and the included angle α gradually decreases. When the reduction ratio of the speed reducer 12 is fixed, the transmission ratio of the motor 5 to the crankshaft 13 is a constant value, so that every time the motor 5 rotates by one angle, β changes by a corresponding angle value in the same proportion, and Δβ (i.e., a change value of β) is the same for any one of the equal short time periods. The estimation can be made by simple geometric analysis: during rotation of the curved portion of the crankshaft 13 from the state shown in fig. 5 to the downward vertical state. On the one hand, the angle β increases from zero to 90 ° (n/2) at a constant speed, and 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) is first gradually increased until the downward movement speed of the lower end of the first connecting rod 14 reaches the maximum when the first connecting rod 14 is substantially perpendicular to the curved portion of the crankshaft (i.e., the portion indicated by reference numeral 13 in fig. 6); then, in the second stage, the downward moving speed of the lower end of the first connecting rod 14 is smaller and smaller, when the first connecting rod 14 and the bent portion of the crankshaft are in a straight line in fig. 6, the instantaneous downward moving speed of the lower end of the first connecting rod 14 is reduced to zero, and at this time, the piston 4 moves to the right limit position; then, in the third stage, the lower end of the first connecting rod 14 moves upwards, driving the piston 4 to retract leftwards. It can be seen that the downward movement speed of the lower end of the first connecting rod 14 is smaller and smaller in the latter half period before the piston 4 moves right to the extreme position, that is, in the aforementioned second stage. On the other hand, in the first and second stages, the angle α is gradually reduced all the time, and correspondingly, even if the lower end of the first link 14 and the left end of the second link 15 move downward at a constant speed, the right moving speed of the push-pull rod 16 is inevitably gradually reduced when the angle α is smaller, and in the second stage, the downward moving speed of the left end of the second link 15 is gradually reduced, so that in the second stage, the right moving speed of the piston 4 is reduced, and the second stage is exactly the second half period of the right moving action of the piston 4.

For a more visual understanding of the above reasoning, reference is made again to fig. 6, in which fig. 6 the points O, A, B, C, D, E represent the pivot axis of the crankshaft 13, the point of rotation of the first connecting rod 14 with the crankshaft curve, the point of rotation of the first connecting rod 14 with the second connecting rod 15, the point of rotation of the second connecting rod 15 with the push-pull rod 16, the point of position on the guide groove 23a which is flush with the point of rotation of the second connecting rod with the push-pull rod in the direction of movement of the piston, and the point of position on the guide groove 23a which is flush with the pivot axis of the crankshaft in the direction of movement of the piston, respectively. OA is the known radial dimension of the upper curve of the crankshaft 13, i.e. the distance from the pivot point of the first connecting rod 14 to the crankshaft 13 to the crankshaft pivot axis O. AB is the length of the first link 14 as known. BC is the length of the second link 15, which is known. The DE length is known and the EO length is known.

Let the included angle between the curved part of the crankshaft 3 and the horizontal plane be beta.

The length of CD is known by geometric calculation as:

Deriving equation (1), it can be seen that the rate of change of CD length when β is in the range of 0 to n/2 is:

Assuming ao=2, e0=2, ab=8, bc=8, de=10, it can be seen from the above equation (2) that the change rate of the CD length, i.e. the velocity of the piston 4, is plotted against the angle β as shown in fig. 8, and it is easy to see from this fig. 8: as β increases gradually in the range of 0 to pi/2, the speed of CD lengthening becomes slower and slower, i.e. the transmission ratio of the motor 5 to the piston 4 becomes smaller (the reduction ratio becomes larger) and the right-moving speed of the piston 4 becomes slower and slower, and under the condition that the output power of the motor 5 is constant, the driving force received by the piston 4 becomes larger and larger, which proves the above conclusion. More subtly, as can be seen from fig. 8, the piston 4 remains at a very low running speed for a long period of time before reaching the right-hand limit position. This is perfectly adapted to many conditions in practical applications of diaphragm pumps or diaphragm compressors, in particular diaphragm compressors. Such as a diaphragm compressor of such a structure is applied to an air conditioning system to compress a gaseous refrigerant into a high pressure state or even a liquid state and then discharged from the discharge valve 9. Obviously, during the refrigerant discharge process, the diaphragm 3 only needs to provide a relatively stable pushing force to push out the refrigerant in the working chamber 1, the driving force applied by the push-pull rod 16 to the piston 4 does not need to be greatly increased, the working condition is perfectly matched with the curve of fig. 8, the final reduction ratio is not sharply reduced, but is reduced relatively gently, and the piston basically maintains a relatively reasonable and gentle speed. Therefore, the compressed refrigerant in the working chamber can be discharged faster without reducing the driving force of the piston, and the working efficiency is improved.

In addition, we also calculate the relationship between the velocity of the lower end of the first link 14 (i.e. point B) and the included angle β through geometric calculation as shown in fig. 7, it is easy to see that the running velocity of the lower end of the first link 14 increases first, decreases then moves up reversely, and also verifies the estimation.

In order to better exploit the above characteristics, in fig. 6, 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 transition of the second connecting rod to the push-pull rod (point C) when the crankshaft rotates 360 °, i.e. point B always moves on the same side of the straight line CD (including overlapping of point B with the straight line CD). The straight line CD is a straight line parallel to the movement direction of the piston 4 and passing through the point C. In other words, the point B always moves on the same side (upper side of fig. 9) of the straight line passing the point C and parallel to the movement direction of the piston 4.

It is apparent that the above-described function can be necessarily achieved if the sum of the radial dimension of the curved portion of the crankshaft 13 (the length A0 in fig. 6, i.e., the distance between the first connecting rod and the crankshaft adapter and the pivot axis) and the length dimension of the first connecting rod 14 is not greater than the length of ED.

It can be seen that the further the transmission system is in the rear section of the working action (rightward movement in fig. 1) of the piston 4, the larger the reduction ratio is, the larger the rightward driving force to which the piston 4 is subjected is in the rear section of the working action, and the driving force to which the piston 4 is subjected can be kept at a (relatively stable) large value for a long period of time before the piston reaches the working limit position, which is perfectly adapted to many working conditions of the diaphragm pump and the diaphragm compressor in practical application.

Further, in the present embodiment, the guide groove 23a and the pivot axis O are disposed in the same plane and perpendicular to each other, i.e. the distance between the point E and the point O in fig. 6 is zero. Thus, when the point of rotation of the first connecting rod 14 and the crankshaft 13 is rotated to the lowest point in fig. 9, the first connecting rod 14 and the curved portion of the crankshaft 13 are just in line. Further, the sum of the radial dimension of the crankshaft curve and the length of the first connecting rod 14 in fig. 9 may also be set equal to the vertical spacing of the pivot axis from the second connecting rod and the push-pull rod pivot point. Thus, when the curved portion of the crankshaft 13 rotates in the direction of the second connecting rod 15 to be in the same straight line as the first connecting rod 14 (vertical straight line in fig. 9), the first connecting rod 14 is just perpendicular to the second connecting rod 15, and the second connecting rod 15 is just parallel to the movement direction of the piston 4. This helps to improve the compactness of the transmission system.

In order to improve the adaptability of the diaphragm 3 to left and right deformation and further improve the service life of the diaphragm 3, the diaphragm 3 of this embodiment is integrally provided with an annular deformation fold 3a protruding rightward in the thickness direction of the diaphragm.

The main purpose of the operation of the motor 5 is to provide a driving force to the diaphragm 3 to drive the movement of the diaphragm 3 and thereby squeeze and draw the working fluid. The piston 4 and the transmission system connecting the motor and the piston, including the flywheel 24, are all arranged on the driving path of the motor 5 for transmitting driving force to the diaphragm 3, and 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. Wherein the crankshaft 13 is located on the transmission downstream side of the speed 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.

The motive fluid b filled in the motive chamber 2 is also provided in a driving path of the motor 5 for transmitting driving force to the diaphragm 3, and has a function of transmitting driving force to the diaphragm 3, so that the motive fluid b filled in the motive chamber 2 is also a component of the driving path of the motor 5 (or the flywheel 24, or the piston 4) to the diaphragm 3.

Further, the deformation pleat 3a has a circular ring-shaped structure to accommodate the leftward and rightward deformation characteristics of the diaphragm 3. The diaphragm 3 is constituted by a first portion housed inside the working chamber 1 and the power chamber 2, and a second portion located outside the working chamber 1 and the power chamber 2, and the deformed fold 3a is specifically formed on the first portion.

The deformed pleat 3a is arranged close to the outer edge of the first part of the diaphragm, so that the enclosing area of the deformed pleat 3a is as large as possible, and the purpose of the arrangement is to promote the deformation of the diaphragm 3 to the left and right, and further promote the extrusion amount of the working fluid.

The enclosed area of the deformed pleat 3a is preferably not less than 80% of the area of the first portion of the membrane sheet.

Embodiment two:

Fig. 14 and 15 show a second type of diaphragm pump having substantially the same structure as the first embodiment, with the following main differences:

This embodiment further optimizes the structure of the transmission system. As shown in fig. 14 and 15, the transmission system includes a flywheel, a speed reducer, a crankshaft 13, two links (first link 14 and second link 15, respectively), parallel four links, and a push-pull rod 16, which are not shown in the drawing, and are arranged in this order in the transmission direction (or power transmission direction). Wherein: the input shaft of the speed reducer is connected with the output shaft of the motor through a coupler, and the output shaft of the speed reducer is connected with one end of the crankshaft 13 through the coupler. The other end of the crankshaft 13 is pivotally supported on a housing 33 of the diaphragm pump. The parallel four links are constituted by a third link 18, a fourth link 19, a fifth link 20 and a sixth link 21 which are pivotally connected end to end in this order in the circumferential direction. The joint (i.e., the pivot connection) between the third link 18 and the fourth link 19, the joint between the fourth link 19 and the fifth link 20, the joint between the fifth link 20 and the sixth link 21, and the joint between the sixth link 21 and the third link 18 form four vertex angles of the parallel four links, respectively. 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 an adapter 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 the other curved portion of the crankshaft 13, and the other end is connected to the adapter portion of the fifth connecting rod 20 and the sixth connecting rod 21. One end of the push-pull rod 16 is connected with the switching part of the fourth connecting rod 19 and the fifth connecting rod 20, and the other end is connected with the piston 4.

In operation, the motor 5 drives the crankshaft 13 to rotate through the speed reducer. The crankshaft 13 rotates (revolves) one end of the first connecting rod 14 and the second connecting rod 15 about 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 vertex angles of the parallel four-bar linkage to periodically approach and separate in fig. 14, the horizontal dimension of the parallel four-bar linkage in fig. 14 periodically stretches and shortens, and then the piston 4 is driven to reciprocate in the left-right direction in fig. 14 through the push-pull rod 16.

Referring again to fig. 16, 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 pivotally connected by respective pivots 22. The "other end" of the first link 14 is in particular connected to the pivot 22 pivotally connecting the third link 18 and the fourth link 19, the "other end" of the second link 15 is in particular connected to the pivot 22 pivotally connecting 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 connecting the fourth link 19 and the fifth link 20.

It will be appreciated that during operation, the vertical component of the pushing or pulling force of the fourth link 19 on the push-pull rod 16 is always opposite to the vertical component of the pushing or pulling force of the fifth link 20 on the push-pull rod 16. The total vertical force exerted by the parallel four-bar linkage on the push-pull rod 16 is small and even zero, so that the radial external force exerted by the push-pull rod 16 on the piston 4 is reduced, the service life of the piston 4 and a piston cylinder sleeve (in the embodiment, the piston cylinder sleeve is a main component for forming a power chamber) shown in fig. 14 and 15 and not labeled is further prolonged, and the possibility or severity of oil leakage at the position where the piston 4 is matched with the power chamber 2 is reduced.

In order to ensure that the vertical component force of the pushing force or the pulling force of the fourth connecting rod 19 on the push-pull rod 16 always and the vertical component force of the fifth connecting rod 20 on the pushing force or the pulling force of the push-pull rod 16 are completely counteracted to be zero in the working process, so that the driving force born by the piston 4 is always parallel to the inner wall surface of the power chamber, 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, the parallel four connecting rods are in a diamond structure, and one diagonal line of the diamond parallel four connecting rods is parallel to the moving direction of the piston 4.

Further, the first link 14 and the second link 15 have the same length so that the parallel four-bar linkage operates more smoothly.

It will be understood that the structural combination of the crankshaft 13, the first connecting rod 14, the fourth connecting rod 19 and the push-pull rod 16 in the transmission system of this embodiment is substantially the same as that of the first embodiment shown in fig. 6 or fig. 9, and the motion trail during operation is also substantially the same, so that the transmission system of this embodiment also has the same transmission characteristics as the transmission system of the first embodiment: the larger the reduction ratio of the motor 5 to the piston 4 is, the larger the driving force received by the piston 4 is, the further the piston 4 moves rightward to perform work.

In addition, the present embodiment further provides a linear bearing 28 sleeved outside the push-pull rod 16, the linear bearing 28 is fixed with a housing 33 of the diaphragm pump, and the linear bearing 28 supports and guides the reciprocating motion of the push-pull rod 16, so as to further improve the service life of the piston 4.

To better convert the rotational movement of the crankshaft 13 into a side-to-side translation of the push-pull rod 16, the present embodiment fixedly (or pivotally) connects the pivot 22 pivotally connecting the third and sixth links 18, 21 to the housing 33 of the diaphragm pump. When the crankshaft 13 is unfolded and folded by the parallel four-bar linkage driven by the first and second connecting bars 14 and 15, the pivot 22 pivotally connecting the third and sixth connecting bars 18 and 21 is always unchanged in relative position with the housing 33, so that the pivot 22 pivotally connecting the fourth and fifth connecting bars 19 and 20 is translated left or right, thereby driving the piston 4 to translate left or right as shown in fig. 14 and 15.

Embodiment III:

The diaphragm pump of this embodiment differs from that of the second embodiment only in the structure of the transmission system, and is specifically as follows:

as shown in fig. 17 and 18, the transmission system of the diaphragm pump of the present embodiment includes: a flywheel and a decelerator, which are not shown in the drawings, 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 speed reducer is connected with an output shaft of a motor, not shown in the figure, through a coupling, and the output shaft of the speed reducer is connected with one end of the crankshaft 13 through the coupling. The other end of the crankshaft 13 is pivotally supported on a housing 33 of the diaphragm pump. One end of the first connecting rod 14, i.e., the upper end in fig. 18, is pivotally connected to the curved portion of the crankshaft 13, and the other end, i.e., the lower end in fig. 18, is pivotally connected to one end of the third connecting rod 18, i.e., the left end in fig. 18, through a pivot 22. One end of the second connecting rod 15, i.e., the upper end in fig. 18, is pivotally connected to another curved portion of the crankshaft 13, and the other end, i.e., the lower end in fig. 18, is pivotally connected to one end of the fourth connecting rod 19, i.e., the left end in fig. 16, through a pivot 22. The other end of the third link 18, i.e. the right end in fig. 16, is pivotally connected to the other end of the fourth link 19, i.e. the right end in fig. 16, by a pivot 22. One end of the push-pull rod 16 is connected to the pivot 22 pivotally connecting the third link 18 and the fourth link 19 and the other end is connected to the piston 4. In order to convert the rotary motion of the crankshaft 13 into a lateral translation of the push-pull rod 16, a guide seat 23 is also provided, which is fixed (with the housing 33) in the transmission space. The guide seat 23 is formed with a vertically extending guide groove 23a as shown in 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 slidably disposed in the foregoing guide groove 23a such that the two pivots 22 can move only up and down (toward or away from each other) along the guide groove 23 a.

In operation, the motor drives the crankshaft 13 to rotate through the speed reducer. The crankshaft 13 drives the upper ends of the first and second connecting rods 14, 15 to rotate about 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 far away from each other, and further the push-pull rod 16 and the piston 4 move left and right.

It will be appreciated that during operation, the direction of the vertical component of the pushing force or pulling force of the third connecting rod 18 on the push-pull rod 16 is always opposite to the direction of the vertical component of the pushing force or pulling force of the fourth connecting rod 19 on the push-pull rod 16, and the total vertical force applied to the push-pull rod 16 is smaller or even zero, so that the radial acting force applied to the piston 4 by the push-pull rod 16 is reduced, the service lives of the piston 4 and a piston cylinder sleeve (in the embodiment, the piston cylinder sleeve is a main component for forming a power chamber) shown in fig. 17 but not labeled are further prolonged, and the oil leakage problem at the matched position of the piston 4 and the power chamber 2 is reduced.

In order to ensure that the vertical component of the pushing force or the pulling force of the third connecting rod 18 on the push-pull rod 16 is always completely offset to be zero with the vertical component of the pushing force or the pulling force of the fourth connecting rod 19 on the push-pull rod 16 in the working process, so that the driving force born by 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 the embodiment.

Further, the first link 14 and the second link 15 also have the same length, so that the link transmission structure operates more smoothly.

It will be appreciated that the structural combination of 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 substantially the same as the structural combination of fig. 6 or 9 of the first embodiment, and the movement track during operation is also substantially the same. Therefore, the transmission system in this embodiment also has the same transmission characteristics as the transmission system in the first embodiment: the larger the reduction ratio of the motor 5 to the piston 4 is, the larger the driving force received by the piston 4 is, the further the piston 4 moves rightward to perform work.

In addition, the present embodiment also provides a linear bearing 28 fixed in the housing 33 and sleeved outside the push-pull rod 16, and the linear bearing 28 supports and guides the reciprocating motion of the push-pull rod 16, so as to further improve the service life of the piston 4.

It will be seen that the transmission system of this embodiment corresponds to the transmission system in which the third link and the sixth link of the second embodiment are removed, and a guide seat 23 for restricting the lower end portions of the first link and the second link to move vertically is provided.

Embodiment four:

fig. 19 and 20 show a fourth diaphragm pump, which has one pump head added to the first embodiment, so that work can be performed on two portions of working fluid at the same time. The method comprises the following steps:

The diaphragm pump is provided with two working chambers 1, two power chambers 2, two diaphragm plates 3 and two pistons 4. The motor 5 drives the two pistons 4 to reciprocate in the left-right direction in fig. 19 through a set of transmission system at the same time, so as to drive the left and right diaphragm 3 to do work on the working fluid a of the left and right working chambers 1 respectively.

As shown in fig. 21 and referring to fig. 20, the structure of the transmission system in the diaphragm pump of the present embodiment is similar to that of the first embodiment, except that the present embodiment is provided with two second links 15 and two push-pull rods 16 in common. Two push-pull rods 16 are respectively connected with the two pistons 4 at the left side and the right side. One end of the two second connecting rods 15 is pivotally connected with the lower end of the first connecting rod 14 through a pivot 22, and the other ends of the two second connecting rods 15 are respectively pivotally connected with the two push-pull rods 16 on the left side and the right side through other pivots.

When the motor 5 drives the crankshaft 13 to rotate, the crankshaft 13 drives the first connecting rod 14 to move, and no matter where the lower end of the first connecting rod 14 moves, the at least one push-pull rod 16 is necessarily driven to move left and right, so that the at least one piston 4 is driven to move. However, in order to ensure that the pivot 22 pivotally connecting the first link 14 and the two second links 15 can only move horizontally in the front-rear direction perpendicular to the paper surface in fig. 20 during operation, thereby allowing both pistons 4 to move left and right, the present embodiment is provided with a guide seat 23 fixed in the transmission chamber 17 (fixed to the housing of the diaphragm pump), the guide seat 23 is formed with a guide groove 23a extending in the front-rear direction perpendicular to the paper surface in fig. 20, and the pivot 22 pivotally connecting the second link 15 and the push-pull rod 16 is slidably disposed in the guide groove 23 a.

Further, in this embodiment, the lengths of the two second connecting rods 15 are equal, so that when the crankshaft 13 rotates, the two push-pull rods 16 are synchronously separated or synchronously close in the left-right direction, and further, the working steps of the left pump head and the right pump head are consistent.

In operation, the motor 5 drives the crankshaft 13 to rotate through the speed reducer 12. The crankshaft 13 rotates (revolves) the upper end of the first connecting rod 14 about the pivot axis of the crankshaft. The lower ends of the first connecting rods 14 simultaneously drive one ends of the two second connecting rods 15 to reciprocate along the guiding grooves 23a, so that the other ends of the second connecting rods 15 drive the push-pull rods 16 to reciprocate along the left-right direction in fig. 20.

In this embodiment, the guide seat 23 is a separate member that is connected to the housing of the diaphragm pump separately. Of course, the guide seat 23 and the housing may be integrally formed as in the first embodiment.

It will be understood that the structural combination of the crankshaft 13, the first connecting rod 14, the second connecting rod 15 and the push-pull rod 16 in the transmission system of the present embodiment is substantially the same as the structure and the movement track of the structural combination in fig. 6 or 9 of the first embodiment, so that the transmission system of the present embodiment also has the same transmission characteristics as the transmission system of the first embodiment: the larger the reduction ratio of the motor 5 to the piston 4 is, the larger the driving force received by the piston 4 is, the further the piston 4 moves rightward to perform work.

Fifth embodiment:

fig. 22 shows a fifth diaphragm pump which, like in the fourth embodiment, has two pump heads so that work can be performed on two portions of the working fluid simultaneously. The difference between this embodiment and the fourth embodiment is the structure of the transmission system, which is as follows:

As shown in fig. 22 and 23, the transmission system for connecting the motor and the piston in the present embodiment includes, in order along the transmission direction: a flywheel, a speed reducer, a crankshaft 13, two connecting rods (a first connecting rod 14 and a second connecting rod 15 respectively), parallel four connecting rods and two push-pull rods 16, which are not shown in the figure. Wherein: the input shaft of the speed reducer is connected with the output shaft of the motor through a coupler, and the output shaft of the speed reducer is connected with one end of the crankshaft 13 through the coupler. The other end of the crankshaft 13 is pivotally supported on a housing 33 of the diaphragm pump. The parallel four links are constituted by a third link 18, a fourth link 19, a fifth link 20 and a sixth link 21 which are pivotally connected end to end in this order in the circumferential direction. One end of the first connecting rod 14 is pivotally connected to one curved portion of the crankshaft 13, and the other end is connected to the junction 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 the other curved portion of the crankshaft 13, and the other end is connected to the adapter portion of the fifth connecting rod 20 and the sixth connecting rod 21. One end of the right push rod 16 is connected to the joint between the fourth link 19 and the fifth link 20, and the other end is connected to the right piston 4. One end of the left push rod 16 is connected to the joint between the third link 18 and the sixth link 21, and the other end is connected to the left piston 4.

Specifically, as shown in fig. 23 and referring to fig. 22, 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 pivotally connected by respective pivots 22. The "other end" of the first link 14 is specifically connected to the pivot 22 that pivotally connects the third link 18 and the fourth link 19. The "other end" of the second link 15 is connected to the pivot 22 which pivotally connects the fifth link 20 and the sixth link 21. One end of the right push-pull rod 16 is connected to the pivot 22 that pivotally connects the fourth link 19 and the fifth link 20. One end of the left push-pull rod 16 is connected to the pivot 22 that pivotally connects the third link 18 and the sixth link 21.

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, the parallel four connecting rods are inevitably driven to deform, and then the at least one push-pull rod 16 is driven to move left and right, so that the at least one piston 4 moves left and right.

However, in order to ensure that both pistons 4 are operational during operation, the present embodiment provides a transfer seat 23 in the transmission chamber 17, which is fixed directly or indirectly to the diaphragm pump housing 33. The guide seat 23 is formed with a guide groove 23a extending up and down in parallel to the paper surface in fig. 23, and slidably arranges in the guide groove 23a the pivot 22 pivotally connecting the third link 18 and the fourth link 19 and the pivot 22 pivotally connecting the fifth link 20 and the sixth link 21. This allows the two pivots 22 to move up and down (toward or away from each other) only along the guide grooves 23a, thereby ensuring that the crankshaft 13 rotating during operation simultaneously moves the pistons 4 on both sides left and right.

In operation, the motor 5 drives the crankshaft 13 to rotate through the speed reducer. The crankshaft 13 rotates one end of the first connecting rod 14 and one end of the second connecting rod 15 about 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 vertex angles of the parallel four-bar linkage to periodically approach and separate in fig. 22. The horizontal dimension of the parallel four-bar linkage in fig. 22 is periodically lengthened and shortened, and the pistons 4 on the left and right sides are driven to reciprocate in the left and right directions in fig. 22 by the left and right push-pull rods 16, respectively.

It will be appreciated that during operation, the vertical component of the pushing force or pulling force of the fourth link 19 on the left push-pull rod 16 is always opposite to the vertical component of the pushing force or pulling force of the fifth link 20 on the right push-pull rod 16, the vertical component of the pushing force or pulling force of the third link 18 on the right push-pull rod 16 is always opposite to the vertical component of the pushing force or pulling force of the sixth link 21 on the right push-pull rod 16, and the vertical forces applied to the two push-pull rods 16 are smaller or even zero, so that the radial acting force applied by the push-pull rods 16 to the piston 4 is reduced, the service lives of the piston 4 and a piston cylinder sleeve (the piston cylinder sleeve is a main component for forming a power chamber in the embodiment) shown in fig. 22 are further improved, and the oil leakage problem at the position where the piston 4 is matched with the power chamber 2 is reduced.

Further, in order to ensure that during the working process, the vertical component force of the pushing force or the pulling force of the fourth connecting rod 19 to the right push rod 16 is always completely offset to be zero with the vertical component force of the pushing force or the pulling force of the fifth connecting rod 20 to the right push rod 16, the vertical component force of the pushing force or the pulling force of the third connecting rod 18 to the left push rod 16 is always completely offset to be zero with the vertical component force of the pushing force or the pulling force of the sixth connecting rod 21 to the left push rod 16, so that the driving forces received by the two pistons 4 are always parallel to the inner wall surface of the power chamber 2, 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, and the parallel four connecting rods are in a diamond structure.

Further, the first link 14 and the second link 15 also have the same length, so that the parallel four-bar linkage structure operates more smoothly.

Obviously, by adopting the design of the diamond four-bar linkage, the two push-pull rods 16 can be ensured to be always symmetrically far away or symmetrically close in the running process, so that the working steps of the left pump head and the right pump head are consistent.

It will be appreciated that the structural combination of the crankshaft 13, the first connecting rod 14, the third connecting rod 18 and the push-pull rod 16 in the transmission system of the present embodiment is substantially the same as the structural combination of the crankshaft 13, the first connecting rod 14, the fourth connecting rod 19 and the push-pull rod 16 in the first embodiment, and the movement track during operation is substantially the same as that of the structural combination of fig. 6 or 9. Therefore, the transmission system in this embodiment also has the same transmission characteristics as the transmission system in the first embodiment: the larger the reduction ratio between the motor 5 and the two pistons 4 is, the larger the driving force received by the two pistons 4 is, the more the left piston 4 moves leftwards and the right piston 4 moves rightwards to do work.

Example six:

fig. 24 shows a sixth diaphragm pump which is similar in structure to the first embodiment, except that:

in this embodiment, instead of providing a power fluid storage chamber in communication with the power chamber and a valve in the communication path, a clutch 37 is provided on the flywheel 24 to piston 4 transmission system-the clutch 37 is connected in series between the flywheel 24 and the piston 4. It is obvious that the clutch 37 is provided on the driving path of the motor 5 to the diaphragm 3, and that the clutch 37 also belongs to the component of the driving path of the motor 5 to the diaphragm 3.

The clutch 37 is operatively disengaged and engaged. When the clutch 37 is in the disengaged state, the drive path from the flywheel 24 to the diaphragm 3 is disconnected; when the clutch 37 is in the engaged state, the drive path of the flywheel 24 to the diaphragm 3 is engaged. It can be seen that this clutch 37 has the same function as the power fluid storage chamber 10 and valve 11 of the first embodiment.

As shown in fig. 25, in order to enable the clutch 37 to be automatically engaged or disengaged according to the rotational speed of the motor 5, the clutch 37 employs an electrically-controlled clutch that can be electrically engaged and disengaged, and a motor rotational speed sensor 34 that detects the rotational speed of the motor 5 and a controller 35 that is communicatively connected to the motor rotational speed sensor 34 and the clutch 37 are provided. The controller 35 is configured to acquire the rotational speed of the motor 5 from the motor rotational speed sensor 34, and control the engagement and disengagement of the clutch 37 based on the rotational speed, to realize the control method substantially the same as that of the first embodiment described below:

the embodiment provides a control method of the diaphragm pump, which comprises the following steps:

s201, during operation of the motor 5, the control clutch 37 is alternately disengaged and engaged at the first frequency.

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

Preferably, during operation of the motor 5, if it is determined that the rotational speed of the motor 5 is in a set first rotational speed interval, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at a first frequency.

In other embodiments, the motor speed sensor 34 may not be configured, and the controller 35 may control the clutch 37 to be alternately disengaged and engaged at the first frequency only by a user command applied to the controller 35.

S202 of controlling the clutch 37 to be alternately released and engaged at the third frequency if it is detected that the rotation speed of the motor 5 is continuously decreased for the first period in the process of controlling the clutch 37 to be alternately released and engaged at the first frequency at S201 described above; wherein the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the third frequency < the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the first frequency.

That is, in the process of controlling the driving path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and connected at the first frequency, if it is determined that the rotation speed of the motor 5 is continuously decreased for the first time period, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and connected at the third frequency. Wherein the ratio of the engagement duration to the disengagement duration of each cycle of the third frequency (the driving path of the flywheel 24 to the diaphragm 3) is < the ratio of the engagement duration to the disengagement duration of the driving path in each cycle of the first frequency.

S203, in the above-described process of S202 of controlling the clutch 37 to be alternately released and engaged at the third frequency, if it is detected that the rotation speed of the motor 5 is continuously decreased for the second period of time, the clutch 37 is controlled to be alternately released and engaged at the fourth frequency. Wherein the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the fourth frequency < the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the third frequency.

That is, in the process of controlling the driving path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and connected at the third frequency, if it is determined that the rotation speed of the motor 5 is continuously decreased for the second period of time, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and connected at the fourth frequency. Wherein a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the fourth frequency < a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the third frequency.

S204 of controlling the clutch 37 to be alternately released and engaged at the fifth frequency if it is detected that the rotation speed of the motor 5 is continuously increased for the third period of time in the process of controlling the clutch 37 to be alternately released and engaged at the third frequency at the above-described S202; wherein the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the first frequency > the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the fifth frequency > the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the third frequency.

That is, in the process of controlling the driving 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 increased for the third period of time, the driving 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 disengagement duration of the drive path in each cycle of the first frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the fifth frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency.

S205 of controlling the clutch 37 to be alternately released and engaged at the sixth frequency if it is detected that the rotation speed of the motor 5 is continuously increased for the fourth time period in the process of controlling the clutch 37 to be alternately released and engaged at the first frequency at S201 described above; wherein the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the sixth frequency > the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the first frequency.

That is, in the process of controlling the driving path of the flywheel 24 to the diaphragm 3 to be alternately disconnected and connected at the first frequency, if it is determined that the rotation speed of the motor 5 is continuously increased for the fourth time period, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and connected at the sixth frequency; wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the sixth frequency > the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency.

S206, in the above-described process of S205 of controlling the clutch 37 to be alternately released and engaged at the sixth frequency, if it is detected that the rotation speed of the motor 5 is continuously increased for the fifth period of time, the clutch 37 is controlled to be alternately released and engaged at the seventh frequency. Wherein the ratio of the engagement duration to the disengagement duration of the clutch 37 in each period of the seventh frequency > the ratio of the engagement duration to the disengagement duration of the clutch 37 in each period of the sixth frequency.

That is, in the course of controlling the driving 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 is continuously increased for the fifth period of time, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be alternately disconnected and engaged at the seventh frequency; wherein a ratio of an engagement time length to an off time length of the driving path in each period of the seventh frequency > a ratio of an engagement time length to an off time length of the driving path in each period of the sixth frequency.

S207, in the above-described process of S205 of controlling the clutch 37 to be alternately disengaged and engaged at the sixth frequency, if it is detected that the rotation speed of the motor 5 is continuously decreased for the sixth period, the clutch 37 is controlled to be alternately opened and closed at the eighth frequency. Wherein the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the sixth frequency > the ratio of the closing duration to the opening duration of the valve in each cycle of the eighth frequency > the ratio of the engagement duration to the disengagement duration of the clutch 37 in each cycle of the first frequency.

That is, in the process of controlling the driving 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 is continuously increased for the sixth period of time, the driving 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 length to the disengagement time length of the driving path in each period of the sixth frequency > the ratio of the engagement time length to the disengagement time length of the driving path in each period of the eighth frequency > the ratio of the engagement time length to the disengagement time length of the driving path in each period of the first frequency

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

That is, if it is determined that the rotational speed of the motor 5 is less than a relatively small first rotational speed threshold value, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be continuously disconnected; wherein the first rotational speed threshold is less than the lower limit of the first rotational speed interval. To avoid severe overload of the motor 5.

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

That is, in the process of controlling the continuous disconnection of the flywheel 24 to the drive path of the diaphragm 3, if it is determined that the rotational speed of the motor 5 is greater than the second rotational speed threshold value, the flywheel 24 is controlled to be continuously engaged to the drive path of the diaphragm 3; wherein the second rotational speed threshold is not less than the first rotational speed threshold.

Preferably, the second rotation speed threshold is greater than the upper limit of the first rotation speed section in S201.

In other embodiments, the strategy of S201-S207 described above may be omitted, and only the strategies of S208 and S209 are used to control the diaphragm pump:

That is, if it is determined that the rotational speed of the motor 5 is less than the first rotational speed threshold value, the driving path of the flywheel 24 to the diaphragm 3 is controlled to be continuously disconnected. If it is determined that the rotational speed of the motor 5 is greater than the second rotational speed threshold, controlling the flywheel 24 to continuously engage the drive path to the diaphragm 3; wherein the second rotational speed threshold is not less than the first rotational speed threshold. In such a control manner, the second rotational speed threshold value may be generally equal to the first rotational speed threshold value. The disadvantages are: the rotational speed of the motor 5 may be very unstable.

The controller 35 provided in the diaphragm pump of the present embodiment also includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor, which when executed by the processor, implement the control method described above.

To ensure a longer service life of the clutch 37, a flexible clutch may be used for the clutch 37. Moreover, the flexible clutch is preferably connected in series between the flywheel 24 and the speed reducer 12, rather than on the downstream side of the speed reducer 12, to reduce the stress of the flexible clutch.

Embodiment seven:

Fig. 26 shows a seventh diaphragm pump which is particularly suitable for this case: the fluid pressure of the inlet port 6 is much smaller than the fluid pressure of the outlet port 7, the extraction force for extracting the working fluid from the inlet port 6 to the working chamber 1 is much smaller than the thrust force 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 smaller than the power consumption for pushing the working fluid. For example, a diaphragm pump is disposed at the water source to push the water at a low level to a high level. This is similar to the operation of a diaphragm compressor and is therefore also particularly applicable to diaphragm compressors.

The diaphragm pump is similar to the sixth embodiment in structure, and the difference is that:

As shown in fig. 26, 27 and 28, the present embodiment is not provided with a clutch, but an electric control valve 38 is additionally provided in parallel with the suction valve 8 between the inlet port 6 and the working chamber 1, the electric control valve 38 being communicatively connected to the controller 35 so that the operating state of the electric control valve 38 can be controlled by the controller 35.

It can be seen that this embodiment is provided with an electrically controlled valve 38 between the working chamber 1 and the inlet port 6 in addition to the suction valve 8 which a conventional diaphragm pump would have.

The suction valve 8 in this embodiment is a mechanical one-way valve, and the opening and closing of the electrically controlled valve 38 may be controlled by an electrical signal independent of pressure, unlike the suction valve 8 which is automatically opened and closed by sensing pressure. In other embodiments, the suction valve 8 may also be an electronically controlled one-way valve. The differences between the mechanical check valve and the electrically controlled check valve are further described below.

If the electrically controlled valve 38 is in the closed state, the pump head of the diaphragm pump is not different from the conventional pump head, and the working fluid of the inlet 6 can be pumped to the working chamber 1 and then pushed to the outlet 7 as long as the diaphragm pump has enough energy. However, as already described above, the power consumption of the diaphragm pump for pushing the working fluid is large, so that the diaphragm pump cannot push the working fluid in the working chamber 1 to the discharge port 7 in a sufficient amount when the rotation speed of the motor 5 is low and the energy storage of the flywheel 24 is insufficient.

If the electrically controlled valve 38 is in the open state, when the piston 4 moves to the left in fig. 26, the working fluid in the inlet port 6 is easily pumped to the working chamber 1 through the open electrically controlled valve 38, and the power consumption of the action is small; when the piston moves to the right in fig. 26, since the electric control valve 38 is in the open state and the discharge valve 9 is kept in the closed state due to the large opening pressure, the working fluid in the working chamber 1 is discharged back from the open electric control valve 38 to the inlet port 6, and at this time the working fluid in the working chamber is discharged from the inlet port 6, and the power consumption of this action is also small. Corresponding to the (at least partial) disconnection of the operating load of the membrane 3. In this process, one part of the output power provided by the motor 5 is used for completing the extraction and back-discharge actions, and the other part is used for acting on the flywheel 24, so that the flywheel 24 can accelerate and store energy.

It is specifically noted that the term "opening the diaphragm work load" as used in the present specification and claims is not limited to adjusting the diaphragm work load to zero, but includes "opening only the diaphragm work load partially", that is, includes "reducing" the diaphragm work load.

Thus, the present embodiment provides the following control method of the diaphragm pump:

s301, during operation of the motor 5, the electrically controlled valve 38 is controlled to alternately open and close at a first frequency.

That is, during operation of the motor 5, the electronically controlled valve 38 is alternately opened for a twenty-third time period-closed for a twenty-fourth time period-opened for a twenty-third time period-closed for a twenty-fourth time period … … at a set first frequency. That is, during operation of the motor 5, the workload of the diaphragm 3 is controlled to be alternately disconnected and connected at a first frequency. And in each cycle of the first frequency, the electronically controlled valve 38 has a continuous open duration and a continuous closed duration, the ratio of the open duration to the closed duration being set as desired. It will be appreciated that the greater the ratio of the open duration to the closed duration of the electronically controlled valve 38, the greater the energy storage time duty cycle of the flywheel 24 during each cycle; the smaller the ratio of the open duration to the closed duration of the electronically controlled valve 38, the smaller the energy storage time duty cycle of the flywheel 24 during each cycle.

For example, during operation of the motor, the electronically controlled valve 38 is alternately opened and closed at a frequency of 10 times/minute and 2 seconds each for 4 seconds. Wherein 10 times/minute means that the valve is opened 10 times every 1 minute, the valve is closed 10 times, and the opening and closing are alternately performed. Specifically, the electronic control valve is opened for 2 seconds, the electronic control valve is closed for 4 seconds, the electronic control valve is opened for 2 seconds, and the electronic control valve is closed for 4 seconds … ….

During operation of the motor 5, the electrically controlled valve 38 is controlled to alternately open and close at a set first frequency, thereby alternately disconnecting and connecting the operating load of the diaphragm 3. In turn, the flywheel 24 and diaphragm 3 perform work intermittently during each cycle time of the first frequency. The motor 5 periodically charges the flywheel 24. If the motor 5, which is continuously operated (e.g., 2 seconds as described above), is energized in balance with the energy consumed by the diaphragm 3 to normally perform work only for a portion of the time period (e.g., 4 seconds as described above) during each cycle, the diaphragm pump can be continuously operated in a steady state.

It will be appreciated that when the electrically controlled valve 38 is closed, the diaphragm 3 is engaged in service, and the duration of the closing of the electrically controlled valve 38 = the duration of the engagement of the diaphragm in service. When the electronically controlled valve 38 is open, the work load of the diaphragm 3 is disconnected, and the open time period of the electronically controlled valve 38=the disconnection time period of the work load of the diaphragm. For convenience of description, in this embodiment, the access duration of the diaphragm workload is abbreviated as "access duration of the workload" and the disconnection duration of the diaphragm workload is abbreviated as "disconnection duration of the workload".

If the control strategy of S301 is adopted when the rotational speed of the motor 5 is low (e.g. just started), it is not appropriate. Therefore, the control strategy of S301 may be adopted when the rotation speed of the motor 5 is in the set first rotation speed section. That is, during operation of the motor 5, if it is determined that the rotational speed of the motor 5 is in the first rotational speed interval, the operating load of the diaphragm 3 is controlled to be alternately disconnected and connected at the first frequency. It is understood that the aforementioned first rotation speed section is preferably a section around the rated rotation speed of the motor 5. For example, if the rated rotational speed of the motor 5 is 10000 rpm, the first rotational speed section may be selected to be a 9000-11000 rpm section.

Of course, the switching frequency of the electrically controlled valve 38 may also be adjusted when the motor 5 is in different rotational speed intervals. If, for example, it is determined that the rotational speed of the motor 5 is in a second rotational speed interval that is different from and not intersecting the first rotational speed interval and that is smaller than the first rotational speed interval, the electronically controlled valve 38 is controlled to alternately open and close at a second frequency that is different from the first frequency. That is, if it is determined that the rotational speed of the motor 5 is in the second rotational speed interval, the operating load of the diaphragm 3 is controlled to be alternately turned off and on at the second frequency.

In other embodiments, motor speed sensor 34 may not be configured to control electronically controlled valve 38 to alternately disengage and engage at a first frequency by user command to controller 35 by a user.

S302 of controlling the electronically controlled valve 38 to alternately open and close at the third frequency if it is detected that the rotation speed of the motor 5 is continuously reduced for the first period in the process of controlling the electronically controlled valve 38 to alternately open and close at the first frequency at the above S301; wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the third frequency < the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency.

That is, in controlling the work load of the diaphragm 3 to be alternately turned off and on at the first frequency, if it is determined that the rotation speed of the motor 5 is continuously decreased for a first period of time, for example, for one minute, the work load of the diaphragm 3 is controlled to be alternately turned off and on at the third frequency; wherein the ratio of the on-time to the off-time of the workload in each period of the third frequency is less than the ratio of the on-time to the off-time of the workload in each period of the first frequency.

The rotation speed of the motor 5 is continuously reduced during a set first period of time, for example, during two minutes, which means that the energy supplied by the motor 5 is less than the work energy consumption of the diaphragm 3 during this first period of time. Therefore, it is necessary to reduce the work time duty of the diaphragm 3, or increase the dead time duty of the flywheel 24. Thus, upon detecting a continuous decrease in the rotational speed of the motor 5 over the first time period, the electronically controlled valve 38 is controlled to alternately open and close at a third frequency different from the first frequency. Wherein the ratio of the on-time to the off-time of the workload in each period of the third frequency < the ratio of the on-time to the off-time in each period of the first frequency.

Illustratively, the third frequency may be: the electronic control valve is opened for 4 seconds, the electronic control valve is closed for 2 seconds, the electronic control valve is opened for 4 seconds, the electronic control valve is closed for 2 seconds … …, and the switch is still cycled 10 times per minute. Of course, the third frequency may also be adjusted to cycle the switch 3 times, 6 or 20 times per minute, etc.

S303, in the process of controlling the electronically controlled valve 38 to be alternately opened and closed at the third frequency in S302 described above, if it is detected that the rotation speed of the motor 5 is continuously decreased for the second period, the electronically controlled valve 38 is controlled to be alternately opened and closed at the fourth frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the fourth frequency < the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the third frequency.

That is, in the process of controlling the work load of the diaphragm 3 to be alternately turned off and on at the third frequency, if it is determined that the rotation speed of the motor 5 is continuously decreased for the second period of time, the work load of the diaphragm 3 is controlled to be alternately turned off and on at the fourth frequency. Wherein the ratio of the on-time to the off-time of the workload in each period of the fourth frequency is less than the ratio of the on-time to the off-time of the workload in each period of the third frequency.

The rotation speed of the motor 5 is continuously reduced during the second period, which means that during this second period the energy supplied by the motor 5 is still less than the energy consumption of the work of the membrane 3. Therefore, it is necessary to further reduce the time duty of the normal operation of the diaphragm 3, or to further increase the dead time duty of the flywheel 24. Thus, upon detecting that the rotational speed of the motor 5 continues to decrease continuously for the second period, the electronically controlled valve 38 is controlled to open and close alternately at the fourth frequency described above.

Illustratively, at this fourth frequency: the cycle still 10 times per minute was performed by opening the electronic control valve 5 seconds-closing the electronic control valve 1 second-opening the electronic control valve 5 seconds-closing the electronic control valve 1 second … ….

S304, in the above-described process of S302 controlling the electronic control valve 38 to be alternately opened and closed at the third frequency, if it is detected that the rotation speed of the motor 5 is continuously increased for the third period of time, the electronic control valve 38 is controlled to be alternately opened and closed at the fifth frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the fifth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the third frequency.

That is, in controlling the work load of the diaphragm 3 to alternately disconnect and connect the work load of the diaphragm 3 at the third frequency, if it is determined that the rotation speed of the motor 5 continuously increases for the third period of time, the work load of the diaphragm 3 is controlled to alternately disconnect and connect the work load of the diaphragm 3 at the fifth frequency; wherein the ratio of the on-time to the off-time in each period of the first frequency > the ratio of the on-time to the off-time in each period of the fifth frequency > the ratio of the on-time to the off-time in each period of the third frequency.

The rotation speed of the motor 5 increases continuously during a third period of time, which means that during this third period of time the energy provided by the motor 5 is greater than the energy consumed for the work of the membrane 3. Therefore, the normal duty cycle of the diaphragm 3 can be appropriately increased, or the dead time duty cycle of the flywheel 24 can be appropriately reduced. Thus, upon detecting a continuous increase in the rotational speed of the motor 5 over the third period of time, the electronically controlled valve 38 is controlled to alternately open and close at the fifth frequency described above.

Illustratively, at the fifth frequency: opening the electronic control valve for 3.5 seconds-closing the electronic control valve for 2.5 seconds-opening the electronic control valve for 3.5 seconds-closing the electronic control valve for 2.5 seconds … ….

S305 of controlling the electronically controlled valve 38 to alternately open and close at the sixth frequency if it is detected that the rotation speed of the motor 5 continuously increases during the fourth time period in the process of controlling the electronically controlled valve 38 to alternately open and close at the first frequency at the above-described S301; wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the sixth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency.

That is, in controlling the work load of the diaphragm 3 to be alternately disconnected and connected to the work load of the diaphragm 3 at the first frequency, if it is determined that the rotation speed of the motor 5 is continuously increased for the fourth time period, the work load of the diaphragm 3 is controlled to be alternately disconnected and connected to the work load of the diaphragm 3 at the sixth frequency; wherein the ratio of the on-time to the off-time of the workload in each period of the sixth frequency > the ratio of the on-time to the off-time of the workload in each period of the first frequency.

The rotation speed of the motor 5 decreases continuously during the fourth period, which means that during this fourth period the energy supplied by the motor 5 is greater than the energy consumption of the diaphragm 3. Therefore, the time duty of the normal work of the diaphragm 3 can be increased, or the idle energy storage time duty of the flywheel 24 can be shortened. Thus, upon detecting that the rotational speed of the motor 5 continuously decreases in the fourth time period, the electronically controlled valve 38 is controlled to alternately open and close at the sixth frequency.

Illustratively, the sixth frequency may be: the electronic control valve is opened for 4 seconds, the electronic control valve is closed for 11 seconds, the electronic control valve is opened for 4 seconds, the electronic control valve is closed for 11 seconds … …, and the switch is cycled 4 times per minute.

S306, in the above-described process of S305 controlling the electronically controlled valve 38 to alternately open and close at the sixth frequency, if it is detected that the rotation speed of the motor 5 is continuously increased for the fifth period, the electronically controlled valve 38 is controlled to alternately open and close at the seventh frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the seventh frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the sixth frequency.

That is, in controlling the work load of the diaphragm 3 to alternately disconnect and connect the work load of the diaphragm 3 at the sixth frequency, if it is determined that the rotation speed of the motor 5 is continuously increased for the fifth period of time, the work load of the diaphragm 3 is controlled to alternately disconnect and connect the work load of the diaphragm 3 at the seventh frequency; wherein the ratio of the on-time to the off-time of the work load in each period of the seventh frequency > the ratio of the on-time to the off-time of the work load in each period of the sixth frequency.

The rotation speed of the motor 5 increases continuously during the fifth period, which means that during this fifth period the energy supplied by the motor 5 is still greater than the energy consumption of the work of the membrane 3. Therefore, the time duty ratio of the normal work of the diaphragm 3 can be further increased, or the idle energy storage time duty ratio of the flywheel 24 can be further reduced. Thus, upon detecting that the rotational speed of the motor 5 continues to decrease continuously for the fifth period, the electronically controlled valve 38 is controlled to open and close alternately at the seventh frequency described above.

Illustratively, at the seventh frequency: opening the electronic control valve 4 seconds-closing the electronic control valve 12 seconds-opening the electronic control valve 4 seconds-closing the electronic control valve 12 seconds … ….

S307, in the above-described process of S305 controlling the electronically controlled valve 38 to alternately open and close at the sixth frequency, if it is detected that the rotation speed of the motor 5 continuously decreases for the sixth period, the electronically controlled valve 38 is controlled to alternately open and close at the eighth frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the sixth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the eighth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency.

That is, in controlling the work load of the diaphragm 3 to alternately disconnect and connect the work load of the diaphragm 3 at the sixth frequency, if it is determined that the rotation speed of the motor 5 is continuously decreased for the sixth period of time, the work load of the diaphragm 3 is controlled to alternately disconnect and connect the work load of the diaphragm 3 at the eighth frequency; the ratio of the on time and the off time of the working load in each period of the sixth frequency is greater than the ratio of the on time and the off time of the working load in each period of the eighth frequency.

The rotation speed of the motor 5 decreases continuously during a sixth period, which means that during this sixth period the motor 5 provides less energy than the energy consumed for doing work by the membrane sheet 3. Therefore, the time duty of the normal work of the diaphragm 3 can be appropriately reduced, or the dead time duty of the flywheel 24 can be appropriately increased. Thus, upon detecting that the rotational speed of the motor 5 is continuously increased for the sixth period, the electronically controlled valve 38 is controlled to alternately open and close at the eighth frequency described above.

Illustratively, at the eighth frequency: opening the electronic control valve 4 seconds-closing the electronic control valve 10 seconds-opening the electronic control valve 4 seconds-closing the electronic control valve 10 seconds … ….

S308, if the rotating speed of the motor 5 is detected to be smaller than a first rotating speed threshold value, the electric control valve 38 is controlled to be continuously opened; wherein the first rotational speed threshold is less than the lower limit of the first rotational speed interval in S301.

That is, if it is determined that the rotational speed of the motor 5 is less than a relatively small first rotational speed threshold, the operating load of the control diaphragm 3 is continuously turned off.

The first rotation speed threshold value is a relatively small value that is smaller than the lower limit of the first rotation speed section described above in the present embodiment. When the rotational speed of the motor 5 is less than this very small first rotational speed threshold, which means that the energy of the motor 5 and the flywheel 24 is already severely insufficient, the electronically controlled valve 38 can be continuously opened so that the operating load of the diaphragm 3 remains in an off state, in order to avoid a severe overload of the motor 5.

S309, if the rotating speed of the motor 5 is detected to be greater than the second rotating speed threshold value, the electric control 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.

That is, during the continuous disconnection of the work load of the diaphragm 3, if it is determined that the rotation speed of the motor 5 is greater than the second rotation speed threshold value, the work load of the diaphragm 3 is continuously connected.

It will be appreciated that during the duration of S308 when the electrically controlled valve 38 is continuously opened, the flywheel 24 remains in the idle state, and the energy provided by the motor 5 is fully converted into kinetic energy of the flywheel 24. When the rotational speed of the motor 5 and the flywheel 24 is sufficiently high and the kinetic energy is sufficiently high, the diaphragm pump as a whole runs empty, with a waste of energy, if the electrically controlled valve 38 is still kept in an open state. Therefore, in this embodiment, when the rotation speed of the motor 5 is detected to be greater than the second rotation speed threshold, the electronic control valve 38 is switched from the card punching state to the closing state, and the working load of the diaphragm 3 is accessed, so that the diaphragm 3 normally works.

The second rotation speed threshold should not be smaller than the first rotation speed threshold in S301, and is preferably a value larger than the upper limit of the first rotation speed section.

Obviously, we can also dispense with the above strategy of S301-S307, using only the strategies of S308 and S309 to control the membrane pump:

That is, if it is determined that the rotational speed of the motor 5 is less than the first rotational speed threshold, the operating load of the diaphragm 3 is controlled to be continuously turned off. If the rotating speed of the motor 5 is determined to be larger than the second rotating speed threshold value, the work load of the diaphragm 3 is controlled to be continuously connected; wherein the second rotational speed threshold is not less than the first rotational speed threshold. In such a control manner, the second rotational speed threshold value may be generally equal to the first rotational speed threshold value. The disadvantages are: the rotational speed of the motor 5 may be very unstable.

The controller 35 disposed in the diaphragm pump also includes a memory, a processor coupled to the memory, and computer instructions stored in the memory and executable by the processor, which when executed by the processor, implement the control method.

Example eight:

fig. 29 shows an eighth diaphragm pump which is particularly suitable for this case: the extraction force of the working fluid from the inlet port 6 to the working chamber 1 is much greater than the thrust of the working fluid from the working chamber out to the outlet port 7, the power consumption of extracting the working fluid being much greater than the power consumption of pushing the working fluid. For example, a diaphragm pump is arranged at a high place to which water at a low place is pumped.

The diaphragm pump is similar in structure to the seventh embodiment, except that:

in this embodiment, an electronically controlled valve 38 in communication with the controller 35 is disposed between the working chamber 1 and the outlet port 7 and in parallel with the outlet valve 9, rather than being connected between the working chamber 1 and the inlet port 6.

It can be seen that this embodiment is additionally provided with an electrically controlled valve 38 between the working chamber 1 and the discharge opening 7, in addition to the discharge valve 9 which is inherent in conventional diaphragm pumps.

The discharge valve 9 in this embodiment is a mechanical check valve, and the opening and closing of the electric control valve 38 may be controlled by an electric signal independent of pressure, unlike the discharge valve 9 which is automatically opened and closed by sensing pressure. In other embodiments, the discharge valve 9 may also be an electronically controlled one-way valve.

If the electrically controlled valve 38 is in the closed state, the pump head of the diaphragm pump is not different from the conventional pump head in operation, and at this time, as long as the diaphragm pump has enough energy, the working fluid of the inlet port 6 can be pumped to the working chamber 1 and then pushed to the outlet port 7. However, as described above, the power consumption of the diaphragm pump for pumping the working fluid is very high, so that the diaphragm pump cannot pump the working fluid in the inlet 6 to the working chamber 1 in a sufficient amount when the rotation speed of the motor 5 is low and the energy storage of the flywheel 24 is insufficient. The working fluid or air in the outlet 7 can be pumped to the working chamber 1 with less power consumption, so that the electrically controlled valve 38 can be opened at this time, reducing the load of the diaphragm 3 deforming to the left in fig. 29.

If the electric control valve 38 is in the open state, when the piston moves rightward in fig. 29, 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 small; when the piston moves leftward in fig. 29, the electric control valve 38 is in an open state, and the suction valve 8 is kept in a closed state due to a large opening pressure, so that the working fluid (or air) in the discharge port 7 is easily drawn from the open electric control valve 38 to the working chamber 1, and the power consumption of the drawing action is also small. Corresponding to at least partially disconnecting the operating load of the membrane 3. Therefore, in this process, a part of the output power provided by the motor 5 is used for completing the pushing and extracting actions, and the other part is used for acting on the flywheel 24, so that the flywheel 24 can accelerate and store energy.

Thus, the present embodiment provides the following control method, which is basically the same as that of embodiment seven and the detailed control method thereof can be referred to the content of embodiment seven.

S401, during operation of the motor 5, the electrically controlled valve 38 is controlled to alternately open and close at a first frequency.

Preferably, in case it is determined that the rotational speed of the motor 5 is in the set first rotational speed interval, the electronically controlled valve 38 is controlled to be alternately opened and closed at the first frequency.

S402 of controlling the electronically controlled valve 38 to alternately open and close at a third frequency if it is detected that the rotation speed of the motor 5 is continuously reduced for a first period of time in the process of controlling the electronically controlled valve 38 to alternately open and close at the first frequency S401; wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the third frequency < the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency.

S403, in the process of controlling the electronically controlled valve 38 to alternately open and close at the third frequency at S402, if it is detected that the rotation speed of the motor 5 continuously decreases for the second period of time, the electronically controlled valve 38 is controlled to alternately open and close at the fourth frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the fourth frequency < the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the third frequency.

S404, in the process of controlling the electronically controlled valve 38 to be alternately opened and closed at the third frequency at S402, if it is detected that the rotation speed of the motor 5 is continuously increased for the third period of time, the electronically controlled valve 38 is controlled to be alternately opened and closed at the fifth frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the fifth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the third frequency.

S405, in the process of controlling the electronic control valve 38 to be alternately opened and closed at the first frequency at S401, if it is detected that the rotation speed of the motor 5 is continuously increased for the fourth time period, controlling the electronic control valve 38 to be alternately opened and closed at the sixth frequency; wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the sixth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency.

S406, in the process of controlling the electronic control valve 38 to alternately open and close at the sixth frequency at S405, if it is detected that the rotation speed of the motor 5 is continuously increased for the fifth period of time, the electronic control valve 38 is controlled to alternately open and close at the seventh frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the seventh frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the sixth frequency.

S407, in the process of controlling the electronic control valve 38 to alternately open and close at the sixth frequency at S405, if it is detected that the rotation speed of the motor 5 continuously decreases for the sixth period, the electronic control valve 38 is controlled to alternately open and close at the eighth frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the sixth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the eighth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency.

If it is detected that the rotational speed of the motor 5 is less than a first relatively small rotational speed threshold, the electronically controlled valve 38 is controlled to continue to open S408.

S409, if the rotation speed of the motor 5 is detected to be larger than the second rotation speed threshold value, the electric control valve 38 is controlled to be continuously closed; wherein the second rotational speed threshold is not less than the first rotational speed threshold in S408. Preferably, the second rotation speed threshold is greater than the upper limit of the first rotation speed section in S401.

Example nine:

Fig. 32 shows a ninth diaphragm pump, which is also applicable to the case described in embodiment eight: the extraction force of the working fluid from the inlet port 6 to the working chamber 1 is much greater than the thrust of the working fluid from the working chamber out to the outlet port 7, the power consumption of extracting the working fluid being much greater than the power consumption of pushing the working fluid. For example, a diaphragm pump is arranged at a high place to which water at a low place is pumped.

The diaphragm pump is similar to the eighth embodiment in structure, except that: in this embodiment, an electronically controlled valve is not additionally provided between the working chamber 1 and the discharge port 7, but the discharge valve 9 is provided as an electronically controlled check valve in communication with the controller 35. As in fig. 33.

It is known that an electronically controlled check valve differs from a conventional mechanical check valve mainly in that: the common mechanical check valve directly senses the pressure to open or close, and can not realize the reverse flow of the fluid. The electric control one-way valve has more functions and application modes and mainly comprises two types: some electronically controlled check valves are also capable of opening (or closing) in response to an electronic control signal, while fully retaining the function of a conventional mechanical check valve; ii), some electric control check valves are required to convert the fluid pressure at the valve into an electric control signal, and then the valve is controlled to be opened (or closed) by the electric control signal. Therefore, the reverse flow of the fluid can be realized by only applying the intervention of the control command to the electric control one-way valve. For example, chinese patent application CN108825828a discloses an electronically controlled check valve which can be opened actively by an electronic control method to realize reverse flow of fluid.

For the same purpose as in the eighth embodiment, the present embodiment realizes the following control method for the diaphragm pump mainly by writing the computer instructions of the controller 35:

S501, during the operation of the motor 5, the discharge valve 9 is controlled to open for an eighth period every seventh period.

That is, during the operation of the motor 5, the discharge valve 9 eighth period-the seventh period-the discharge valve 9 eighth period … … is alternately opened. In effect, it corresponds to those in the seventh and eighth embodiments: during operation of the motor 5, the operating load of the diaphragm 3 is alternately disconnected and connected at a first frequency.

The above-described "opening the discharge valve 9 for the eighth period" means that the discharge valve 9 is kept in the open state for the eighth period. By "interval of the seventh period of time" is meant that during this seventh period of time, the controller 35 does not actively interfere with the action of the discharge valve 9, allowing the discharge valve 9 to operate in accordance with its own original characteristics. Such as: on or off according to physical pressure or on or off according to an otherwise electrical control strategy.

The above-described "letting the discharge valve 9 operate as it is" generally includes two cases:

1) The discharge valve 9 is opened or closed according to the physical pressure. In this case, the controller 35 completely releases the intervention on the operating state of the discharge valve 9, and allows the discharge valve 9 to directly sense the pressure on both sides thereof to automatically open or close. That is, the controller 35 does not act at all on the discharge valve 9, and allows the discharge valve 9 to be opened or closed by only a non-electric mechanical force. This is suitably applied to the electrically controlled one-way valve of the type "i" described above.

2) The discharge valve 9 is opened or closed according to an original electrical control strategy. In this case, the controller only has to remove the above-described active intervention on the discharge valve and control the opening and closing of the discharge valve 9 using conventional strategies. "opening and closing of the discharge valve 9 is controlled by a conventional strategy", typically: the controller 35 controls the discharge valve 9 to be opened or closed mainly according to the pressure at the discharge valve 9. This is suitably applied to an electrically controlled one-way valve of the type "ii" described above.

For example, during operation of the motor, the controller 35 actively opens the discharge valve 9 intermittently, once every 4 seconds, and for 2 seconds each time the discharge valve is kept open. That is, the drain valve is opened and held for 2 seconds-4 seconds apart-the drain valve is opened and held for 2 seconds … ….

During operation of the motor 5, the controller 35 actively opens the discharge valve 9 intermittently at a set cadence, so that the operating load of the diaphragm 3 is alternately switched off and on at a set first frequency. And thus the flywheel 24 and the diaphragm 3 do work intermittently during each cycle time of the first frequency, and the motor 5 periodically stores energy to the flywheel 24. Typically, during each cycle time (e.g., 4+2=6 seconds in this embodiment), the continuously operating motor 5 provides energy in balance with the energy consumed by the diaphragm 3 to normally perform work only during a portion of the period (e.g., 4 seconds in this embodiment), so that the diaphragm pump can continue to operate stably.

It will be appreciated that when the controller 35 actively controls the discharge valve 9 to open, the operating load of the diaphragm 3 is disconnected and the duration of the active opening of the discharge valve 9 = the duration of the disconnection of the diaphragm operating load. When the controller 35 stops the active intervention on the discharge valve 9, the discharge valve 9 operates normally, the work load of the diaphragm 3 is switched on, and the controller 35 actively controls the interval duration of the discharge valve 9 opening=the switching-on duration of the work load of the diaphragm. For convenience of description, in this embodiment, the on period of the diaphragm workload, that is, the interval period during which the controller 35 actively controls the discharge valve 9 to be opened is simply referred to as "on period of the workload", and the off period of the diaphragm workload is simply referred to as "off period of the workload".

If the control strategy of S501 is adopted when the rotational speed of the motor 5 is low (e.g. just started), it is not appropriate. Therefore, the control strategy of S501 may be adopted when the rotation speed of the motor 5 is in the set first rotation speed section. That is, during the operation of the motor 5, if it is determined that the rotational speed of the motor 5 is in the first rotational speed interval, the discharge valve 9 is controlled to open for an eighth period of time every seventh period of time in response to the determination, so that the work load of the diaphragm 3 is alternately disconnected and connected at the first frequency. It is understood that the aforementioned first rotation speed section is preferably a section around the rated rotation speed of the motor 5. For example, if the rated rotational speed of the motor 5 is 10000 rpm, the first rotational speed section may be selected to be a 9000-11000 rpm section.

Of course, the rhythm of the active opening of the discharge valve 9 may be adjusted when the motor 5 is in different rotational speed intervals. For example, if it is determined that the rotation speed of the motor 5 is in a second rotation speed section different from and not intersecting the first rotation speed section and smaller than the first rotation speed section, the discharge valve 9 is controlled to open for a tenth period every ninth period. That is, if it is determined that the rotational speed of the motor 5 is in the second rotational speed interval, the operating load of the diaphragm 3 is controlled to be alternately turned off and on at the second frequency.

S502 of controlling the discharge valve 9 to open for a twelfth period of time every eleventh period of time if it is detected that the rotation speed of the motor 5 is continuously reduced for a first period of time, for example, three minutes, in the process of controlling the discharge valve 9 to open for the eighth period of time every seventh period of time at S501 described above; 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.

That is, in controlling the first frequency of the work load of the diaphragm 3 to alternately turn off and on the diaphragm 3, if it is determined that the rotation speed of the motor 5 is continuously decreased for the first time period, the work load of the diaphragm 3 is controlled to alternately turn off and on at the third frequency. Wherein the ratio of the on-time to the off-time of the workload in each period of the third frequency is less than the ratio of the on-time to the off-time of the workload in each period of the first frequency.

S503 of controlling the discharge valve 9 to open for a fourteenth period every thirteenth period if it is detected that the rotation speed of the motor 5 is continuously decreased for the second period in the process of controlling the discharge valve 9 to open for the twelfth period every eleventh period at S502 described above; wherein the ratio of the thirteenth time period to the fourteenth time period < the ratio of the eleventh time period to the twelfth time period.

That is, during the operation of controlling the diaphragm 3 to be alternately disconnected and connected at the third frequency, if it is determined that the rotation speed of the motor 5 is continuously decreased for the second period of time, the operation of controlling the diaphragm 3 to be alternately disconnected and connected at the fourth frequency; wherein the ratio of the on-time to the off-time of the workload in each period of the fourth frequency is less than the ratio of the on-time to the off-time of the workload in each period of the third frequency.

S504 of controlling the discharge valve 9 to open for a sixteenth period of time every fifteenth period of time if it is detected that the rotation speed of the motor 5 is continuously increased for a third period of time in the process of controlling the discharge valve 9 to open for the twelfth period of time every eleventh period of time at S502 described above; 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.

That is, in the process of controlling the work load of the diaphragm 3 to be alternately turned off and on at the third frequency, if it is determined that the rotation speed of the motor 5 is continuously increased for the third period of time, the work load of the diaphragm 3 is controlled to be alternately turned off and on at the fifth frequency; wherein the ratio of the on-time to the off-time in each period of the first frequency > the ratio of the on-time to the off-time in each period of the fifth frequency > the ratio of the on-time to the off-time in each period of the third frequency.

S505 of controlling the discharge valve 9 to open for an eighteenth period of time every seventeenth period of time if it is detected that the rotation speed of the motor 5 is continuously increased during the fourth period of time in the above-described process of controlling the discharge valve 9 to open for an eighth period of time every seventh period of time at S501; wherein the ratio of the seventeenth time period to the eighteenth time period > the ratio of the seventh time period to the eighth time period.

That is, in the process of controlling the first frequency of the work load of the diaphragm 3 to be alternately turned off and on, if it is determined that the rotation speed of the motor 5 is continuously increased for the fourth time period, the work load of the diaphragm 3 is controlled to be alternately turned off and on at the sixth frequency; wherein the ratio of the on-time to the off-time of the workload in each period of the sixth frequency > the ratio of the on-time to the off-time of the workload in each period of the first frequency.

S506, in the above-described process of S505 of controlling the discharge valve 9 to open for the eighteenth period every seventeenth period, if it is detected that the rotation speed of the motor 5 is continuously increased for the fifth period, the discharge valve 9 is controlled to open for the twentieth period every nineteenth period. Wherein the ratio of the nineteenth time period to the twentieth time period > the ratio of the seventeenth time period to the eighteenth time period.

That is, in the course of controlling the sixth frequency of the work load of the diaphragm 3 to be alternately turned off and on, if it is determined that the rotation speed of the motor 5 is continuously increased for the fifth period of time, the work load of the diaphragm 3 is controlled to be alternately turned off and on at the seventh frequency; wherein the ratio of the on-time to the off-time of the work load in each period of the seventh frequency > the ratio of the on-time to the off-time of the work load in each period of the sixth frequency.

S507, in the above-described process of S505 of controlling the discharge valve 9 to open for the eighteenth period every seventeenth period, if it is detected that the rotation speed of the motor 5 is continuously decreased for the sixth period, the discharge valve 9 is controlled to open for the twenty-second period every twenty-first period. Wherein 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.

That is, in the course of controlling the sixth frequency of the work load of the diaphragm 3 to be alternately turned off and on, if it is determined that the rotation speed of the motor 5 is continuously increased for the sixth period of time, the work load of the diaphragm 3 is controlled to be alternately turned off and on at the eighth frequency; the ratio of the on time and the off time of the working load in each period of the sixth frequency is greater than the ratio of the on time and the off time of the working load in each period of the eighth frequency.

S508, if it is detected that the rotation speed of the motor 5 is less than a first rotation speed threshold value, controlling the discharge valve 9 to be continuously opened; wherein the first rotation speed threshold is smaller than the lower limit of the first rotation speed section in S501.

S509, if it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold, removing the above-mentioned active intervention of the controller 35 on the discharge valve 9; wherein the second rotational speed threshold is not less than the first rotational speed threshold in S508, and the second rotational speed threshold is preferably a value greater than the upper limit of the first rotational speed section in S501.

In other embodiments, the strategy of S501-S507 described above may be omitted, with the strategy of S508 and S509 only being used to control the diaphragm pump:

That is, if it is determined that the rotational speed of the motor 5 is less than the first rotational speed threshold, the operating load of the diaphragm 3 is controlled to be continuously turned off; if the rotating speed of the motor 5 is determined to be larger than the second rotating speed threshold value, the work load of the diaphragm 3 is controlled to be continuously connected; wherein the second rotational speed threshold is not less than the first rotational speed threshold. In such a control manner, the second rotational speed threshold value may be generally equal to the first rotational speed threshold value.

The controller 35 includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor, which when executed by the processor, implement the control method.

Example ten:

fig. 34 shows a tenth diaphragm pump, which is also applicable to the case described in embodiment seven: the extraction force for extracting the working fluid from the inlet port 6 to the working chamber 1 is much smaller than the thrust for pushing the working fluid out of the working chamber to the outlet port 7, and the power consumption for extracting the working fluid is much smaller than the power consumption for pushing the working fluid. For example, a diaphragm pump is disposed at the water source to push the water at a low level to a high level. This is similar to the operation of a diaphragm compressor and is therefore also applicable to diaphragm compressors.

The diaphragm pump is similar in structure to the seventh embodiment, except that: in this embodiment, an electrically controlled valve is not additionally provided between the working chamber 1 and the inlet port 6, but the suction valve 8 is provided as an electrically controlled one-way valve in communication with the controller 35.

For the same purpose as in the seventh embodiment, this embodiment realizes the following control method of the diaphragm pump, similar to that of the ninth embodiment, mainly by writing the computer instructions (codes) of the controller 35, and the detailed control method thereof can be referred to the content of the foregoing ninth embodiment.

S601, during operation of the motor 5, the suction valve 8 is controlled to open for an eighth period of time every seventh period of time.

That is, during the operation of the motor 5, the suction valve 8 is alternately opened for the eighth period-the seventh period-the suction valve 8 is opened for the eighth period … …. In effect, it corresponds to the seventh, eighth and ninth embodiments: during operation of the motor 5, the operating load of the diaphragm 3 is alternately disconnected and connected at a first frequency.

Preferably, in the case where it is determined that the rotation speed of the motor 5 is in the set first rotation speed section, the suction valve 8 is controlled to be opened for an eighth period every seventh period.

S602 of controlling the suction valve 8 to open for a twelfth period of time every eleventh period of time if it is detected that the rotation speed of the motor 5 is continuously reduced for the first period of time in the process of controlling the suction valve 8 to open for the eighth period of time every seventh period of time at S601; 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.

S603, in the process of controlling the suction valve 8 to open for the twelfth period every eleventh period at S602, if it is detected that the rotation speed of the motor 5 decreases continuously for the second period, the suction valve 8 is controlled to open for the fourteenth period every thirteenth period. Wherein the ratio of the thirteenth time period to the fourteenth time period < the ratio of the eleventh time period to the twelfth time period.

S604, in the process of controlling the suction valve 8 to open for the twelfth period every eleventh period at S602, if it is detected that the rotation speed of the motor 5 is continuously increased for the third period, the suction valve 8 is controlled to open for the sixteenth period every fifteenth period at S602. 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.

S605, in the process of controlling the suction valve 8 to open for the eighth period every seventh period of time at S601, if it is detected that the rotation speed of the motor 5 is continuously increased in the fourth period of time, controlling the suction valve 8 to open for the eighteenth period of time every seventeenth period of time; wherein the ratio of the seventeenth time period to the eighteenth time period > the ratio of the seventh time period to the eighth time period.

S606, in the above-described process of S605 controlling the suction valve 8 to be opened for the eighteenth period every seventeenth period, if it is detected that the rotation speed of the motor 5 is continuously increased for the fifth period, the suction valve 8 is controlled to be opened for the twentieth period every nineteenth period. Wherein the ratio of the nineteenth time period to the twentieth time period > the ratio of the seventeenth time period to the eighteenth time period.

S607, in the above-described process of S605 controlling the suction valve 8 to open for the eighteenth period every seventeenth period, if it is detected that the rotation speed of the motor 5 is continuously decreased for the sixth period, controlling the suction valve 8 to open for the twenty-second period every twenty-first period. Wherein 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.

S608, if it is detected that the rotational speed of the motor 5 is less than a first relatively small rotational speed threshold, the suction valve 8 is controlled to be continuously opened.

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

In other embodiments, the strategy of S601-S607 described above may be omitted, with only the strategies of S608 and S609 being used to control the diaphragm pump.

Example eleven:

fig. 36 shows an eleventh diaphragm pump which is similar in structure to the first embodiment, and differs mainly in that:

In this embodiment, the piston is not provided, but a bellows 26 of a rotary structure is provided which is axially elastically deformable. The power fluid in the power chamber 2 is pushed to drive the diaphragm 3 to deform by using the telescopic deformation of the leather bag 26, so that the working fluid in the working chamber 1 is extruded to do work. The axis of the bellows 26 extends straight in the left-right direction in fig. 38.

As shown in fig. 37 and with reference to fig. 36, a portion of the power chamber 2 is formed inside the bellows 26, and the remaining portion is located outside the bellows 26. In operation, the power chamber 2, both inside and outside the bellows 26, is filled with a power fluid. The motor 5 is connected to the left end portion of the bellows 26 through a transmission system to drive the bellows to deform in an axial direction (left-right direction in fig. 37). The right end of the bellows 26 is fixed to a housing 33 of the diaphragm pump.

As shown in fig. 39 and referring to fig. 38 and 37, the transmission system in this embodiment has the same structure as that of the transmission system in the sixth embodiment, except that the push-pull rod in the sixth embodiment is connected to the piston, and the push-pull rod 16 in this embodiment is connected to the bellows 26. The transmission system is also provided with a flywheel 24 connected in series between the motor 5 and the reduction gear 12. In operation, the push-pull rod 16 drives the left end of the leather bag 26 to move left and right in fig. 36, so that the leather bag 26 axially stretches and deforms. When the bellows 26 is axially contracted under the drive of the flywheel 24, if the valve 11 is in an open state, a part of hydraulic oil in the power chamber 2 enters the power fluid storage chamber 10; when the valve 11 is in a closed state, the hydraulic oil in the power chamber 2 presses the diaphragm 3 to deform rightward, and work is done on the working fluid.

It is apparent that the transmission system in this embodiment may also adopt the structure of the second embodiment or the third embodiment.

The bellows 26 is made of rubber, has a certain thickness, and can bear strong radial pressure inside without deformation (radial deformation), and has basically the same structure as the bellows configured by the air spring shock absorber used in the automobile field.

The bellows 26 is integrally provided with a plurality of bellows rings, the bellows rings are closely arranged along the axis direction of the bellows, and each bellows ring surrounds the periphery of the bellows axis to promote the axial deformation capability of the bellows 26.

For ease of illustration, the power chamber 2 is now divided into two parts, the power chamber 2 within the bellows 26 being referred to as a first half-chamber 2a and the power chamber 2 outside the bellows 26 being referred to as a second half-chamber 2b, as shown in fig. 37.

The left end and the right end of the leather bag 26 are both in an opening structure, and the opening at the left end of the leather bag is plugged by the right end of the push-pull rod 16. The opening at the right end of the bellows 26 is adapted to communicate with the power chamber outside the bellows, the second half-chamber 2b, so that the power fluid b can flow between the power chambers inside and outside the bellows, i.e. between the first half-chamber 2a and the second half-chamber 2b.

If the opening at the right end of the bellows 26 is not specially treated, when the diaphragm 3 is deformed leftward, excessive deformation occurs at the opening position, and the service life is shortened. In this regard, in this embodiment, a barrier net 27 is fixedly provided at the opening of the right end of the bellows 26 to block excessive deformation of the diaphragm 3. The first half chamber 2a and the second half chamber 2b are located on the left and right sides of the barrier net 27, respectively, and the second half chamber 2b is formed between the diaphragm 3 and the barrier net 27.

Further, the second half chamber 2b is a conical chamber with a large end facing the diaphragm 3, and the baffle net 27 is arranged at a small end of the conical chamber to better adapt to the leftward deformation of the diaphragm 3, and can be integrally abutted against the chamber wall of the second half chamber 2b and the right side surface of the diaphragm 3 when the diaphragm is deformed leftward. Similarly, the working chamber 1 is also provided as a conical cavity with a large end facing the diaphragm 3, which also can rest over a large area against the wall of the working chamber 1 when the diaphragm is deformed to the right. Obviously, similar designs are also used for the first to seventh embodiments.

When the bellows 26 is stretched to a certain length by the push-pull rod 16, the diaphragm 3 is deformed to the left and is placed against the wall of the second half-chamber 2b and against the side surface of the barrier net 27 facing the second half-chamber 2 b. When the bellows 26 is compressed to a certain length by the push-pull rod 16, the diaphragm 3 deforms rightward and is arranged to abut against the wall surface of the working chamber 1.

The push-pull rod 16, the leather bag 26 and the diaphragm 3 are coaxially arranged, and the baffle net 27 is parallel to the diaphragm 3. The axis of the bellows 26 is perpendicular to the diaphragm 3, and an extension of the axis of the bellows 26 passes through the center of the diaphragm 3.

As mentioned above, the main purpose of the operation of the motor 5 is to provide a driving force to the diaphragm 3 to drive the movement of the diaphragm 3 to squeeze and draw the working fluid. The bellows 26 and the transmission system connecting the motor and the bellows are both disposed on the driving path of the motor 5 for transmitting the driving force to the diaphragm 3, and the bellows 26 and the transmission system connecting the motor and the bellows are both members of the driving path of the motor 5 to the diaphragm 3.

The motive fluid b filled in the motive chamber 2 is also provided in a driving path along which the motor 5 transmits driving force to the diaphragm 3, and has a function of transmitting driving force to the diaphragm 3, so that the motive fluid b filled in the motive chamber 2 is also a component of the driving path along which the motor 5 transmits driving force to the diaphragm 3.

Embodiment twelve:

fig. 40 shows a twelfth diaphragm pump, which has one pump head added to the eleventh embodiment, so that work can be performed on two portions of working fluid at the same time. The method comprises the following steps:

As shown in fig. 40, the diaphragm pump is provided with two bellows 26 in total. The motor 5 drives the two bellows 26 to deform in a stretching manner in the left-right direction in fig. 40 through a set of transmission system, so as to drive the left diaphragm 3 and the right diaphragm 3 to do work on the working fluid a in the corresponding working chamber 1. The structure of the transmission system is the same as that of the fourth embodiment, except that two push-pull rods in the fourth embodiment are respectively connected with pistons at the left side and the right side, and the two push-pull rods in the fourth embodiment are respectively connected with leather bags 26 at the left side and the right side.

The structure of the transmission system in this embodiment is the same as that of the fifth embodiment, except that the push-pull rod is connected to the piston in the fifth embodiment, and the push-pull rod 16 is connected to the bellows 26 in this embodiment.

Obviously, the transmission system in this embodiment may also adopt the structure of the sixth embodiment.

Embodiment thirteen:

Fig. 41 and 42 show a thirteenth diaphragm pump having substantially the same structure as the twelfth embodiment, with the main difference that:

In this embodiment, the power chamber 2 is entirely formed inside the bellows 26, and the diaphragm 3 is disposed at the right end of the bellows 26, so that an oil path for communicating the power chamber 2 and the power fluid storage chamber 10 leads from the push-pull rod 16 on the left side of the bellows to the inside of the bellows 26.

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

Fourteen examples:

fig. 43 shows a fourteenth diaphragm pump which is basically identical in structure to the thirteenth embodiment, with the main difference that:

The diaphragm 3 is arranged inside the leather bag 26, so that the inner cavity of the leather bag 26 is divided into a power chamber 2 and a working chamber 1, and the power chamber 2 and the working chamber 1 are formed in the leather bag 26. During operation, the push-pull rod 16 pushes the leather bag 26 to shrink axially rightwards, hydraulic oil in the power chamber 2 pushes the diaphragm 3 to squeeze working fluid in the working chamber 1 rightwards, and on the other hand, the working chamber 1 also generates shrinkage deformation to squeeze the working fluid therein to do work. The diaphragm 3 in this embodiment is deformed less than in the twelve-way embodiment by squeezing the same volume of working fluid, which is advantageous for extending the service life of the diaphragm pump, in particular the diaphragm.

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

Example fifteen:

Fig. 45 and 46 show a fifteenth diaphragm pump similar in structure to the fourteenth embodiment, with the main difference that:

As shown in fig. 46 and 47, a rigid collar 30 having a generally horn shape with thin left and thick right is attached to the right side of the bellows 26, the rigid collar 30 having 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 communicated with the opening at the left end of the rigid annular sleeve 30, and the diaphragm 3 is sealed at the opening at the right end of the rigid annular sleeve 30. The right side of the diaphragm 3 is connected to an annular deformable flexible ring 31. One part of the power chamber 2 is formed in the rigid collar 30 and the other part is formed in the bladder 26.

When the diaphragm 3 and the flexible ring 31 are in the natural state shown in fig. 46 and 47, both are substantially planar structures and are placed against each other with the working chamber volume being zero. When the push-pull rod 16 moves the left end of the bellows 26 to the left in fig. 47. The negative pressure formed in the power chamber 2 deforms the diaphragm 3 leftwards, and the rigid ring sleeve 30 moves leftwards along with the leather bag 26, so that the outer edge of the flexible ring piece 31 is driven to deform leftwards, and the flexible ring piece 31 is approximately in a conical structure with thick left and thin right. A working chamber 1 for sucking up working fluid is formed between the diaphragm 3 and the flexible ring 31 as shown in fig. 48. And the volume of the working chamber is now positively correlated with the amount of deformation of the diaphragm 3 and the flexible ring 31.

It can be seen that during operation the diaphragm 3 and the flexible ring 31 deform together to change the volume of the working chamber and thereby draw working fluid into the working chamber or push the working fluid out of the working chamber altogether. The deformation amount of the diaphragm 3 is smaller in this embodiment than in the above embodiments one to nine, which contributes to the prolongation of the service life of the diaphragm, by pressing the same volume of working fluid.

In order to improve the deformation adaptability of the diaphragm 3 and the flexible ring 31, and further improve the service lives of the diaphragm 3 and the flexible ring 31, a circle of deformation folds 3a protruding rightwards are integrally formed on the diaphragm 3 in this embodiment, and a circle of deformation folds 31a protruding rightwards are integrally formed on the flexible ring 31. The right side of the flexible ring piece 31 is provided with a bearing seat 32 fixed with the shell 33, the bearing seat 32 is provided with a bearing plane facing the flexible ring piece, and an annular groove 32a which is concave inwards and is matched with the deformation fold 3a and the second deformation fold 31a is formed on the bearing plane so as to accommodate the deformation fold 3a and the second deformation fold 31a in the state of fig. 46. When the membrane sheet 3 and the flexible ring sheet 31 are in the natural state of fig. 46 and 47, the portions other than the deformed wrinkles are both planar structures, that is, the non-deformed wrinkles of the membrane sheet 3 and the flexible ring sheet 31 in the natural state are planar structures.

Furthermore, the bellows 26 is provided with an oil passage chamber at its periphery, and an oil passage that communicates the power chamber 2 and the power fluid storage chamber 10 passes through the oil passage chamber, and the valve 11 is provided on the rigid collar 30.

Example sixteen:

Fig. 50 shows a sixteenth diaphragm pump which is similar in structure to the eleventh embodiment except that the present embodiment is not provided with a motive fluid reservoir communicating with the motive chamber 2.

Example seventeenth:

Fig. 51 shows a seventeenth diaphragm pump which is similar in structure to the twelfth embodiment, except that the present embodiment is not provided with a motive fluid reservoir communicating with the motive chamber 2.

Example eighteenth:

Fig. 52 shows an eighteenth diaphragm pump which is similar in structure to the thirteenth embodiment except that the present embodiment is not provided with a motive fluid reservoir communicating with the motive chamber 2.

Example nineteenth:

Fig. 53 shows a nineteenth diaphragm pump having a structure similar to that of the fourteenth embodiment except that the present embodiment is not provided with a motive fluid reservoir communicating with the motive chamber 2.

Example twenty:

Fig. 54 shows a twentieth diaphragm pump which is similar in construction to fifteen embodiments, except that this embodiment has no motive fluid reservoir communicating with the motive chamber 2.

It will be appreciated that the structures of the various embodiments described above are applicable to diaphragm compressors for compressing working fluid. Such as compressing low pressure refrigerant to a high pressure state or even to a liquid state, and is particularly suitable for use as an air conditioning compressor.

Example twenty-one: air conditioning system

Inspired by the seventh and tenth embodiments described above, the present embodiment provides an air conditioning system capable of intermittently performing high-power work. As shown in fig. 55, the air conditioning system includes a compressor 100, a condenser 200, a throttle valve 300, and an evaporator 400, which are sequentially fluidly connected and constitute a closed circuit. The air conditioning system is filled with a refrigerant. During operation, the refrigerant flows through the compressor, the condenser, the throttle valve and the evaporator in sequence, so that the air conditioning system can refrigerate or heat outwards.

The main improvement of the air conditioning system is that the compressor 100 is a diaphragm compressor, and the diaphragm compressor has substantially the same structure as the diaphragm pump of the sixth embodiment, and also includes a motor rotation speed sensor 34 and a controller 35 communicatively connected to the motor rotation speed sensor, except that the diaphragm compressor is not provided with the clutch of the sixth embodiment, and reference is made to fig. 24.

As shown in fig. 56 and with reference to fig. 55, the throttle valve 300 is an electronically controlled throttle valve in communication with the controller 35.

As is known, the opening and closing actions of an electrically controlled throttle valve can be controlled by an electrical control signal, and in conventional air conditioning systems, the electrically controlled throttle valve generally controls the on-off state mainly based on the pressure at the throttle valve. A common mechanical throttle valve directly senses pressure to open (including degree of opening) or close. Like electrically controlled check valves, electrically controlled throttle valves also mainly include two types: some electrically controlled throttle valves can also be opened and closed in response to an electrical control signal on the basis of fully retaining the function of a common mechanical throttle valve; ii, some electric control throttle valves are completely controlled to be opened and closed by electric control signals.

For the same purpose as in the seventh and tenth embodiments, the present embodiment realizes the control method of the air conditioning system described briefly below mainly by writing computer instructions (codes) in the controller 35, and the detailed control method thereof can be referred to in the ninth and tenth embodiments.

S701, if it is determined that the rotation speed of the motor is in the set first rotation speed interval during the operation of the motor 5 of the diaphragm compressor, the throttle valve 300 is controlled to be opened for an eighth period every seventh period.

S702, in the process of controlling the throttle valve 300 to open for an eighth time period every seventh time period in S701, if the rotation speed of the motor is detected to continuously decrease in the first time period, controlling the throttle valve 300 to open for a twelfth time period every 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.

S703 of controlling the throttle valve 300 to open for a fourteenth period every thirteenth period if it is detected that the rotation speed of the motor is continuously decreased for the second period in the process of controlling the throttle valve 300 to open for the twelfth period every eleventh period at S702; wherein the ratio of the thirteenth time period to the fourteenth time period < the ratio of the eleventh time period to the twelfth time period.

S704, in the process of controlling the throttle valve 300 to open for the twelfth time period every eleventh time period at S702, if it is detected that the rotation speed of the motor continuously increases for the third time period, the throttle valve 300 is controlled to open for the sixteenth time period 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.

S705 of controlling the throttle valve 300 to open for an eighteenth period of time every seventeenth period of time if it is detected that the rotation speed of the motor continuously increases during the fourth period of time in the process of controlling the throttle valve 300 to open for the eighth period of time every seventh period of time at S701; wherein the ratio of the seventeenth time period to the eighteenth time period > the ratio of the seventh time period to the eighth time period.

S706, in the process of controlling the throttle valve 300 to open for the eighteenth period every seventeenth period of time at S705, if it is detected that the rotation speed of the motor continuously increases for the fifth period of time, the throttle valve 300 is controlled to open for the twentieth period of time every nineteenth period of time. Wherein the ratio of the nineteenth time period to the twentieth time period > the ratio of the seventeenth time period to the eighteenth time period.

S707, in the process of controlling the throttle valve 300 to open for the eighteenth period every seventeenth period of time at S705, if it is detected that the rotation speed of the motor continuously decreases for the sixth period of time, the throttle valve 300 is controlled to open for the twenty-second period of time every twenty-first period of time at intervals. Wherein 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.

S708, if it is detected that the rotational speed of the motor is less than a first relatively small rotational speed threshold, the throttle valve 300 is continuously opened.

S709, if it is detected that the rotation speed of the motor 5 is greater than the second rotation speed threshold, removing the above-mentioned active intervention of the controller 35 on the throttle valve 300, and allowing the discharge valve 9 to operate according to its own original characteristics; wherein the second rotational speed threshold is not less than the first rotational speed threshold in S708. The "letting the discharge valve 9 operate as it is" generally includes two cases:

1) The throttle valve 300 is opened or closed according to the physical pressure. In this case, the controller 35 completely releases the intervention on the operation state of the throttle valve 300, and allows the throttle valve 300 to directly sense the pressure on both sides thereof to automatically open or close. That is, the controller 35 does not act at all on the throttle valve 300, allowing the throttle valve 300 to open or close solely by means of non-electrical mechanical forces. This is suitably applied to an electrically controlled throttle valve of the type "i" described above.

2) The throttle valve 300 is opened or closed according to an otherwise electrical control strategy. In this case, the controller 35 need only remove the above-described active intervention on the throttle valve 300 and control the opening and closing of the throttle valve 300 using a conventional strategy. "opening and closing of the throttle valve 300 is controlled using a conventional strategy", typically: the controller 35 controls the throttle valve 300 to open or close mainly according to the fluid pressure at the throttle valve 300. This is suitably applied to an electrically controlled throttle valve of the type "ii" described above.

In other embodiments, the policies of S701-S707 described above may be omitted, and the air conditioning system may be controlled simply using only the policies of S708 and S709, as follows:

That is, if it is determined that the rotational speed of the motor 5 is less than the first rotational speed threshold, the throttle valve 300 is controlled to be continuously opened to continuously disconnect the work load of the diaphragm. If it is determined that the rotational speed of the motor is greater than the second rotational speed threshold, removing the active intervention of the controller 35 on the throttle valve 300 to continue to engage the workload of the diaphragm 3; wherein the second rotational speed threshold is not less than the first rotational speed threshold. In such a control manner, the second rotational speed threshold value may be generally equal to the first rotational speed threshold value.

In the simplified control strategy, under the condition of low motor rotation speed and insufficient output power, the throttle valve 300 is kept in an open state so as to reduce the load of the compressor, raise the rotation speed of the motor and store energy for the flywheel. Under the conditions that the motor rotation speed is high enough and the flywheel energy is large enough, the throttle valve 300 is restored to the original state, and the air conditioning system works normally. The disadvantages are: the rotational speed of the motor in the compressor 100 may be very unstable.

Those skilled in the art will appreciate that: the obtaining of the rotational speed information of the motor 5 in the diaphragm compressor is one of conditions that can smoothly implement the control method of S701-S709 described above, for example, the rotational speed of the motor 5 may be obtained in real time during the operation of the motor 5, and once it is determined that the rotational speed of the motor meets a certain preset condition, the throttle valve 300 is controlled to perform a corresponding response action, such as controlling the throttle valve 300 to be alternately opened and closed at the first frequency when it is determined that the rotational speed of the motor is in the set first rotational speed interval.

Example twenty two: air conditioning system

In addition, the present embodiment provides another air conditioning system capable of intermittently performing high-power work. As shown in fig. 57 and with reference to fig. 58, the air conditioning system is provided with an electronically controlled valve 38 connected between the condenser 200 and the evaporator 400 in parallel with the throttle valve 300. The electrically controlled valve 38 is in communication with the controller 35 which is in communication with the motor speed sensor 34, so that the operating state of the electrically controlled valve 38 can be controlled by the controller 35 in accordance with the motor speed. The compressor 100 adopts the same structure as that of the twenty-first embodiment.

If the electrically controlled valve 38 is maintained in the closed state, the air conditioning system operates in a manner that is not different from that of a conventional air conditioning system. At this time, as long as the diaphragm compressor 100 has sufficient energy, the high-pressure fluid on the upstream side of the throttle valve 300 can be pressure-fed 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 significant, such as when carbon dioxide is used as the refrigerant. Therefore, when the rotation speed of the motor 5 is low and the energy storage of the flywheel 24 is insufficient, the compressor 100 cannot work normally.

If the electrically controlled valve 38 is kept in the open state, which corresponds to "shorting" the throttle valve 300, removing it from the circuit, the electrically controlled valve 38 without the throttle expansion function allows the working fluid (refrigerant) to flow easily between the condenser 200 and the evaporator 400, and the working load of the compressor 100 is small. Of course, in this case, the air conditioning system has no cooling and heating effects.

Thus, the present embodiment provides the following control method of the air conditioning system of this modification, and the detailed control method thereof can be implemented with reference to the seventh and eighth embodiments.

S801, if it is detected that the rotational speed of the motor is in the first rotational speed interval during the operation of the motor of the diaphragm compressor 100, the electronic control valve 38 is controlled to be alternately opened and closed at the first frequency.

In general, the rated rotation speed of the driving motor in the compressor 100 is in the first rotation speed section.

Alternatively, if it is detected that the rotational speed of the motor is in a second rotational speed interval that is not intersected by and smaller than the first rotational speed interval, the electronically controlled valve 38 is alternately opened and closed at a second frequency different from the first frequency. The ratio of the open time period to the close time period of the electrically controlled valve 38 in each period of the second frequency is not equal to the ratio of the open time period to the close time period of the electrically controlled valve 38 in each period of the first frequency.

S802 of controlling the electronically controlled valve 38 to alternately open and close at a third frequency if it is detected that the rotational speed of the motor continuously decreases for a first period of time in the process of controlling the electronically controlled valve 38 to alternately open and close at the first frequency at S801; wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the third frequency < the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency.

S803, in the process of controlling the electronic control valve 38 to alternately open and close at the third frequency at S802, if it is detected that the rotation speed of the motor continuously decreases for the second period of time, the electronic control valve 38 is controlled to alternately open and close at the fourth frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the fourth frequency < the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the third frequency.

S804, in the process of controlling the electronic control valve 38 to alternately open and close at the third frequency at S802, if it is detected that the rotation speed of the motor 5 is continuously increased for the third period of time, the electronic control valve 38 is controlled to alternately open and close at the fifth frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the fifth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the third frequency.

S805 of controlling the electronically controlled valve 38 to alternately open and close at the sixth frequency if it is detected that the rotation speed of the motor continuously increases for the fourth time period in the process of controlling the electronically controlled valve 38 to alternately open and close at the first frequency at S801; wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the sixth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency.

S806, in the process of controlling the electronic control valve 38 to alternately open and close at the sixth frequency at S805, if it is detected that the rotation speed of the motor continuously increases for the fifth period of time, the electronic control valve 38 is controlled to alternately open and close at the seventh frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the seventh frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the sixth frequency.

S807, in the process of controlling the electronic control valve 38 to alternately open and close at the sixth frequency at S805, if it is detected that the rotation speed of the motor continuously decreases for the sixth period, the electronic control valve 38 is controlled to alternately open and close at the eighth frequency. Wherein the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the sixth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the eighth frequency > the ratio of the closing time period to the opening time period of the electrically controlled valve 38 in each period of the first frequency.

S808, if it is detected that the rotation speed of the motor 5 is less than a first relatively small rotation speed threshold, controlling the electronic control valve 38 to be continuously opened; wherein the first rotation speed threshold is smaller than the lower limit of the first rotation speed section in S801.

S809, if it is detected that the rotational speed of the motor 5 is greater than the second rotational speed threshold, the electronic control valve 38 is controlled to be continuously closed. The second rotation speed threshold is not smaller than the first rotation speed threshold in S808, and is generally larger than the upper limit value of the first rotation speed section in S801.

For ease of control, the electrically controlled valve 38 is preferably a normally closed valve or a normally open valve.

The controller 35 in fig. 57 and 58 includes a memory, a processor connected to the memory, and computer instructions stored in the aforementioned memory and executable by the aforementioned processor, respectively, which when executed by the processor can implement the aforementioned control methods in the present embodiment, respectively.

Example twenty-three: air conditioning system

As shown in fig. 59 and 60, the air conditioning system of the present embodiment also includes a compressor 100, a condenser 200, a throttle valve 300, and an evaporator 400, which are sequentially fluidly connected and constitute a closed circuit. The pressure sensor 39 is used to detect the internal pressure of the condenser 200, simply referred to as the condenser pressure.

In this embodiment, the compressor 100 is a diaphragm compressor, and the structure is basically the same as that of the first embodiment, and reference is made to fig. 2, and the difference between them is only that: the compressor of the present embodiment is not provided with a motor rotation speed sensor, and the controller 35 communicatively connected to the valve 11 is also communicatively connected to the above-described pressure sensor 39, so that the valve 11 can be opened or closed according to the pressure of the condenser 200.

The present embodiment proposes a control method for the air conditioning system as follows: during operation of the motor of the diaphragm compressor 100, if the pressure of the condenser 200 is detected to be in the first pressure interval, the valve 11 in the diaphragm compressor is alternately opened and closed at the first frequency, i.e., the driving path of the flywheel 24 in the compressor 100 to the diaphragm 3 in the compressor 100 is alternately opened and engaged at the first frequency.

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 the diaphragm 3 needs to overcome. Therefore, the upper limit of the first pressure interval should not be too large, otherwise the rotation speed of the motor 5 and the flywheel 24 may be suddenly reduced due to insufficient output power of the compressor motor 5, and the compressor 100 is severely overloaded. The lower limit of the first pressure interval is not required to be very small, otherwise, the energy waste is increased, and the refrigerating or heating efficiency of the air conditioner is reduced. When the pressure of the condenser 200 is in the first pressure interval which is not excessively large nor excessively small, the valve 11 connected between the power chamber 2 and the power fluid storage chamber 10 on the diaphragm compressor 100 is controlled to be alternately opened and closed according to the set first frequency, and if the energy provided by the continuously operated compressor motor 5 is balanced with the work energy consumption of the compressor diaphragm 3 which works only for a part of the period of time during each cycle time of the first frequency, the diaphragm compressor 100 can continuously and stably operate and can intermittently perform high-power work.

In other embodiments, the valve 11 on the diaphragm compressor may also be alternately opened and closed at a second frequency upon detecting that the pressure of the condenser 200 is in a second pressure interval that is non-intersecting with the first pressure interval described above; wherein the lower limit of the second pressure interval is greater than the upper limit of the first pressure interval, and the ratio of the closing time period to the opening time period of the valve 11 in each period of the second frequency is less than the ratio of the closing time period to the opening time period of the valve 11 in each period of the first frequency, that is, the ratio of the engaging time period to the opening time period of the driving path (the driving path of the flywheel to the diaphragm in the diaphragm compressor) in each period of the second frequency is less than the ratio of the engaging time period to the opening time period of the driving path in each period of the first frequency.

In other embodiments, if the pressure of the condenser 200 is detected to be greater than the first pressure threshold, the valve 11 in the diaphragm compressor is continuously opened, thereby maintaining the driving path of the flywheel 24 to the diaphragm 3 in a disconnected state; wherein the first rotational speed threshold is greater than an upper limit of the first pressure interval.

When the pressure of the condenser 200 is greater than a value greater than the upper limit of the first pressure interval, it is indicated that the load of the compressor is too high, and if the compressor 100 is still intermittently operated, the rotation speed of the motor 5 and the flywheel 24 may be suddenly reduced due to insufficient output power of the motor 5. Thus, the valve 11 can be continuously opened at this time to keep the drive path of the flywheel 24 to the diaphragm 3 in the off state, and the air conditioning system stops cooling or heating. If the rotational speed of the motor has not reached the nominal rotational speed at this time, the flywheel 24 can be continuously charged for a period of time during which the valve 11 is continuously open.

In other embodiments, if the pressure of the condenser 200 is detected to be less than the second pressure threshold, the valve 11 in the diaphragm compressor is continuously closed, thereby maintaining the driving path of the flywheel 24 to the diaphragm 3 in an engaged state; wherein the second rotational speed threshold is less than the lower limit of the first pressure interval.

When the pressure of the condenser 200 is less than a value smaller than the lower limit of the first pressure interval, the load of the compressor is small, and if the compressor 100 is also intermittently operated, energy is wasted. Thus, the valve 11 can be continuously closed at this time to keep the driving path of the flywheel 24 to the diaphragm 3 in the engaged state, so that the air conditioning system can continuously perform cooling or heating.

Those skilled in the art will appreciate that: the acquisition of the internal pressure information of the condenser 200 is one of the conditions under which the above-mentioned control method can be smoothly implemented, and for example, the pressure of the condenser 200 may be acquired in real time during the operation of the compressor motor, and upon determining that the condenser pressure satisfies a certain preset condition, the control valve 11 performs a corresponding response action, such as alternately opening and closing the valve 11 at a first frequency when the condenser pressure is determined to be in a set first pressure interval, and such as continuously opening the valve 11 when the condenser pressure is determined to be in a pressure greater than a set first pressure threshold.

It is also understood that if the diaphragm compressor 100 of the present embodiment is replaced with the structure of the above-described embodiment six, embodiment seven, embodiment ten or embodiment eleven, the air conditioning system can be controlled similarly to the control method described above. Such as controlling engagement or disengagement of the clutch 37 based on the pressure of the condenser 200, such as controlling opening or closing of an electronically controlled valve in parallel with the suction valve based on the pressure of the condenser 200, and such as controlling the suction valve of an electronically controlled check valve structure to actively continue to open or intermittently open based on the pressure of the condenser 200. The specific solution may refer to the sixth embodiment, the seventh embodiment, the tenth embodiment and the twenty-third embodiment, and will not be described herein.

The above is only an exemplary embodiment of the present application and is not intended to limit the scope of the present application, which is defined by the appended claims.

Claims

1. A diaphragm pump or diaphragm compressor comprising:

A working chamber (1),

A power chamber (2),

A diaphragm (3) sealingly disposed between the working chamber and the power chamber, and

A motor (5) for supplying a driving force to the diaphragm;

Characterized by further comprising:

A flywheel (24) provided on a drive path of the motor (5) to the diaphragm (3) to acquire a drive force from the motor (5) and to supply the drive force to the diaphragm (3);

A power fluid storage chamber (10) in communication with the power chamber (2) for receiving power fluid (b) discharged from the power chamber (2) and providing power fluid (b) to the power chamber (2);

A valve (11) provided on a communication path between the power fluid storage chamber (10) and the power chamber (2) for switching on and off the communication path between the power fluid storage chamber (10) and the power chamber (2), the valve (11) being controlled to be alternately opened and closed at a first frequency during operation of the motor (5), a driving path of the flywheel (24) to the diaphragm (3) being disconnected when the valve (11) is switched on; when the valve (11) is cut off, the flywheel (24) is engaged with the drive path of the diaphragm (3).

2. The diaphragm pump or diaphragm compressor of claim 1, wherein the valve (11) is an electrically controlled valve communicatively connected to a controller (35), the controller (35) being configured to: controlling the valve (11) to open or close;

a speed reducer (12) is arranged on a driving path of the flywheel (24) to the diaphragm (3).

3. The diaphragm pump or diaphragm compressor of claim 2, further comprising a motor speed sensor (34) for detecting a speed of the motor (5) and communicatively connected to the controller (35), the controller (35) being configured to: -acquiring the rotational speed of the motor (5) from the motor rotational speed sensor (34), -controlling the valve (11) to open or close based on the rotational speed.

4. A diaphragm pump or a diaphragm compressor according to claim 3, wherein said controlling the valve (11) to open or close based on the rotational speed comprises:

-controlling the valve (11) to alternately close and open at a first frequency if it is determined that the rotational speed is in a first rotational speed interval; wherein the rated rotational speed of the motor (5) is in the first rotational speed interval.

5. The diaphragm pump or diaphragm compressor according to claim 4, wherein said controlling the valve (11) to open or close based on the rotational speed further comprises:

-if it is determined that the rotational speed is less than a first rotational speed threshold, controlling the valve (11) to continue to open; wherein the first rotational speed threshold is less than a lower limit of the first rotational speed interval.

6. A diaphragm pump or a diaphragm compressor according to claim 4 or 5, wherein said controlling the valve (11) to open or close based on the rotational speed further comprises:

-if it is determined that the rotational speed is greater than a second rotational speed threshold, controlling the valve (11) to be continuously closed; wherein the second rotational speed threshold is greater than an upper limit of the first rotational speed interval.

7. A control method of a diaphragm pump or a diaphragm compressor, adapted to the diaphragm pump or the diaphragm compressor according to any one of claims 1 to 6;

The control method is characterized by comprising the following steps:

During operation of the motor (5), the drive path of the flywheel (24) to the diaphragm (3) is alternately disconnected and engaged at a first frequency by controlling the valve (11) to be turned on and off.

8. The control method according to claim 7, characterized in that before said controlling the drive path of the flywheel (24) to the diaphragm (3) to alternately disconnect and engage at a first frequency, the control method further comprises:

determining that the rotational speed of the motor (5) is in a first rotational speed interval.

9. A control method according to claim 8, characterized in that the rated rotational speed of the motor (5) is in the first rotational speed interval.

10. The control method according to claim 8 or 9, characterized in that the control method further comprises:

Controlling the drive path to be alternately disconnected and engaged at a second frequency if it is determined that the rotational speed of the motor (5) is in a second rotational speed interval that is non-intersecting with the first rotational speed interval; the ratio of the engagement duration to the disengagement duration of the driving path in each period of the second frequency is not equal to the ratio of the engagement duration to the disengagement duration of the driving path in each period of the first frequency.

11. The control method according to claim 7 or 8 or 9, characterized in that in the process of controlling the drive path to be alternately disconnected and connected at a first frequency, the control method further comprises:

if it is determined that the rotational speed of the motor (5) decreases continuously over a first period of time, controlling the drive path to alternately disconnect and connect at a third frequency; wherein a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the third frequency < a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the first frequency.

12. The control method according to claim 11, wherein in controlling the drive path to be alternately disconnected and connected at a third frequency, the control method further comprises:

If it is determined that the rotational speed of the motor (5) decreases continuously for a second period of time, controlling the drive path to alternately disconnect and connect at a fourth frequency; wherein a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the fourth frequency < a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the third frequency.

13. The control method according to claim 11, characterized in that in the process of controlling the drive path to be alternately disconnected and connected at a third frequency, the control method further comprises:

If it is determined that the rotational speed of the motor (5) continuously increases for a third period of time, controlling the drive path to alternately disconnect and connect at a fifth frequency; the ratio of the engagement duration to the disengagement duration of the driving path in each period of the first frequency is greater than the ratio of the engagement duration to the disengagement duration of the driving path in each period of the fifth frequency is greater than the ratio of the engagement duration to the disengagement duration of the driving path in each period of the third frequency.

14. The control method according to claim 7 or 8 or 9, characterized in that during said controlling the drive path of the flywheel (24) to the diaphragm (3) to be alternately disconnected and engaged at a first frequency, the control method further comprises:

If it is determined that the rotational speed of the motor (5) continuously increases within a fourth time period, controlling the drive path to alternately disconnect and connect at a sixth frequency; wherein a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the sixth frequency > a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the first frequency.

15. The control method according to claim 14, characterized in that in the process of controlling the drive path to be alternately disconnected and connected at a sixth frequency, the control method further comprises:

If it is determined that the rotational speed of the motor (5) decreases continuously for a sixth period of time, controlling the drive path to be alternately disconnected and engaged at an eighth frequency; and the ratio of the engagement time length to the disconnection time length of the driving path in each period of the sixth frequency is greater than the ratio of the engagement time length to the disconnection time length of the driving path in each period of the sixth frequency.

16. The control method according to claim 8, characterized in that the control method further comprises:

If the rotating speed of the motor (5) is determined to be smaller than a first rotating speed threshold value, controlling the driving path to be continuously disconnected; wherein the first rotational speed threshold is less than a lower limit of the first rotational speed interval.

17. The control method according to claim 8 or 16, characterized in that the control method further comprises:

Controlling the drive path to continue engagement if it is determined that the rotational speed of the motor (5) is greater than a second rotational speed threshold; wherein the second rotational speed threshold is greater than an upper limit of the first rotational speed interval.

18. The control method according to claim 7, wherein the diaphragm pump or diaphragm compressor includes:

an electronic control device mechanically connected to a drive path of the flywheel (24) to the diaphragm (3), and having a first state in which the flywheel (24) is coupled to the drive path of the diaphragm (3) and a second state in which the flywheel (24) is decoupled from the drive path of the diaphragm (3);

19. A control method of a diaphragm pump or a diaphragm compressor, adapted to any one of claims 1 to 6;

The control method is characterized by comprising the following steps:

the rotational speed of the motor (5) is acquired, and if the rotational speed of the motor (5) is determined to be smaller than a first rotational speed threshold value, the continuous conduction of the valve (11) is controlled to control the continuous disconnection of the driving path of the flywheel (24) to the diaphragm (3).

20. The control method according to claim 19, characterized in that the control method further comprises:

controlling the drive path to continue engagement if it is determined that the rotational speed of the motor (5) is greater than a second rotational speed threshold; wherein the second rotational speed threshold is not less than the first rotational speed threshold.

21. The control method according to claim 20, characterized in that in the process of controlling the continuous engagement of the drive path, the control method further comprises:

-if it is determined that the rotational speed of the motor (5) is in a first rotational speed interval, alternately disconnecting and engaging the drive path of the flywheel (24) to the diaphragm (3) at a first frequency; the lower limit of the first rotation speed interval is larger than the first rotation speed threshold value, and the second rotation speed threshold value is larger than the upper limit of the first rotation speed interval.

22. A controller, comprising:

The memory device is used for storing the data,

A processor coupled to the memory, and

Computer instructions stored in the memory and executable by the processor;

the control method of any of claims 7-21 when executed by the processor.