CN215062965U - Air conditioning system - Google Patents

Abstract

The present application relates to an air conditioning system to more fully compress a refrigerant. The air conditioning system comprises a compressor, a condenser, a throttle valve and an evaporator which are sequentially in fluid connection and form a closed loop; the compressor is a diaphragm compressor comprising: the diaphragm, the motor providing the driving force for the diaphragm, the flywheel arranged on the driving path from the motor to the diaphragm, and the motor speed sensor for detecting the speed of the motor; an electric control valve which is connected with the throttle valve in parallel and is in communication connection with the motor speed sensor is arranged between the condenser and the evaporator, and the electric control valve is configured to: on or off based on the rotational speed of the motor detected by the motor rotational speed sensor.

Description

Air conditioning system

Technical Field

The present application relates to an air conditioning system.

Background

An air conditioning compressor is a core component of an air conditioning system, and plays a role of compressing a driving refrigerant in an air conditioning refrigerant circuit. The air conditioner compressor extracts the refrigerant from a low-pressure area, compresses the refrigerant and sends the compressed refrigerant to a high-pressure area for cooling and condensation, heat is emitted into air through the radiating fins, the refrigerant is changed from a gas state into a liquid state, and the pressure is increased.

The power of the air conditioner compressor is derived from the motor. The output power of the motor is a major factor determining the operating capacity of the compressor. The power of the motor is typically relatively large in order to adequately compress the refrigerant. If carbon dioxide is used as the refrigerant, a higher-power compressor needs to be disposed.

However, in practical applications, for various reasons, for example, in the case of small power supply (such as small photovoltaic power supply), for example, in the case of a very restricted space where equipment can be placed, the condition of configuring an ultra-high power motor in the compressor is not provided, so that the compressor cannot sufficiently compress the refrigerant, for example, the carbon dioxide refrigerant cannot be compressed into a high-pressure state or even a liquid state, and the application scenarios are greatly limited.

Disclosure of Invention

The technical problem that this application will solve is: an air conditioning system is provided to more fully compress a refrigerant.

The technical scheme of the application is as follows:

an air conditioning system is provided, comprising a compressor, a condenser, a throttle valve and an evaporator which are sequentially and fluidly connected and form a closed loop;

the compressor is a diaphragm compressor, which includes:

the membrane sheet is provided with a plurality of membrane sheets,

a motor for providing a driving force to the diaphragm,

a flywheel provided in a drive path of the motor to the diaphragm, an

A motor rotation speed sensor for detecting a rotation speed of the motor;

an electric control valve which is connected with the throttle valve in parallel and is in communication connection with the motor speed sensor is arranged between the condenser and the evaporator.

In an alternative design, the electrically controlled valve is configured to: on or off based on the rotational speed of the motor detected by the motor rotational speed sensor.

In an alternative embodiment, the communication connection of the electric control valve to the motor speed sensor is realized by means of a controller which is in communication connection with the electric control valve and the motor speed sensor, respectively.

In an alternative design, the controller is configured to: and acquiring the rotating speed of the motor from the motor rotating speed sensor, and controlling the electric control valve to be opened or closed based on the rotating speed.

In an alternative design, the controlling the electronically controlled valve to open or close based on the rotational speed includes:

in response to determining that the speed is in a first speed interval, controlling the electrically controlled valve to alternately open and close at a first frequency; wherein the rated rotating speed of the motor is in the first rotating speed interval.

The application has at least the following beneficial effects:

an air conditioning compressor of the air conditioning system is provided with a flywheel and a motor rotating speed sensor for detecting the rotating speed of a driving motor, and is in fluid connection with an electric control valve connected with a throttling valve in parallel between a condenser and an evaporator. Therefore, when the diaphragm pump or the diaphragm compressor is in work, the electric control valve can be intermittently and actively opened according to the set frequency, and then the working load of the diaphragm sheet of the compressor is alternately disconnected and connected at the frequency, so that the flywheel intermittently applies work and stores energy in each period time of the frequency, the diaphragm pump or the diaphragm compressor can stably and intermittently compress refrigerant fluid in the working chamber greatly, and the diaphragm compressor provided with a low-power motor, particularly a low-power motor adopting household photovoltaic power supply, can also fully compress the refrigerant.

2, this application air conditioning system's compressor can also keep opening electric control valve when the rotational speed of motor is lower to the work load of continuous disconnection diaphragm, and then make the motor only do work to the flywheel, make the rotational speed and the kinetic energy of flywheel promote steadily. And after the rotating speed of the motor is increased to a certain value, the active intervention on the electric control valve is removed, so that the kinetic energy stored in the flywheel is utilized to do work on the refrigerant, and the refrigerant can be fully compressed.

3, the compressor among this application air conditioning system is used for diaphragm compressor, and during operation, the refrigerant that flows through diaphragm compressor is sealed strictly by the diaphragm, can not cluster inside the compressor.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings of the embodiments will be briefly introduced below, and it is apparent that the drawings in the following description only relate to some embodiments of the present application and are not limiting on the present application.

Fig. 1 is a longitudinal sectional view of a diaphragm pump according to an embodiment of the present invention.

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

Fig. 3 is a partial schematic structural diagram of a transmission system in an embodiment of the present application.

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

Fig. 5 is a partial schematic structural diagram of a transmission system in an embodiment of the present application.

Fig. 6 is a block diagram of a control system of the valve of fig. 1.

Fig. 7 is a longitudinal sectional view of a diaphragm pump according to a second embodiment of the present application.

Fig. 8 is a block diagram of a control system of the clutch of fig. 7.

Fig. 9 is a schematic structural diagram of an air conditioning system in a third embodiment of the present application.

Fig. 10 is a block diagram showing a control system of the throttle valve of fig. 9.

In order to facilitate a reader to clearly observe the structure of the diaphragm pump or the diaphragm compressor, part of the attached drawings are specially hidden from working fluid and power fluid, and part of the attached drawings are hidden from a guide seat.

Description of reference numerals:

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

1-a working chamber, 2-a power chamber, 3-a diaphragm, 3 a-a deformation fold of the diaphragm, 4-a piston, 5-a motor, 6-an inlet, 7-an outlet, 8-an inlet valve, 9-an outlet valve, 10-a power fluid storage chamber, 11-a valve, 12-a reducer, 13-a crankshaft, 14-a first connecting rod, 15-a second connecting rod, 16-a push-pull rod, 17-a transmission chamber, 22-a pivot, 23-a guide seat, 23 a-a guide groove, 24-a flywheel, 25-a coupler, 33-a shell, 34-a motor speed sensor, 35-a controller, 37-a clutch and 38-an electric control valve;

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

Detailed Description

In the description of the present application and claims, the terms "first," "second," and the like, if any, are used solely to distinguish one from another as between described objects and not necessarily in any sequential or technical sense. Thus, an object defined as "first," "second," etc. may explicitly or implicitly include one or more of the object. Also, the use of the terms "a" or "an" and the like, do not denote a limitation of quantity, but rather denote the presence of at least one of the two, and "a plurality" denotes no less than two. As used herein, the term "plurality" 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 used broadly, unless otherwise indicated. For example, "connected" may be a separate connection or may be integrally connected; can be directly connected or indirectly connected through an intermediate medium; may be non-detachably connected or may be detachably connected. The specific meaning of the foregoing terms in the present application can be understood by those skilled in the art as appropriate.

In the description of the present application and in the claims, if there is an orientation or positional relationship indicated by the terms "upper", "lower", "horizontal", etc. based on the orientation or positional relationship shown in the drawings, it is only for the convenience of clearly and simply describing the present application, and it is not indicated or implied that the elements referred to must have a specific direction, be constructed and operated in a specific orientation, and these directional terms are relative concepts for the sake of description and clarification and may be changed accordingly according to the change of orientation in which the elements in the drawings are placed. For example, if the device in the figures is turned over, elements described as "below" other elements would then be oriented "above" the other elements.

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

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

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

The first embodiment is as follows:

fig. 1 and 2 show a diaphragm pump, which is similar to some existing diaphragm pumps, and which 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 sealingly 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 via a transmission system to drive the piston to reciprocate. An intake valve 8 is provided between the inlet port 6 and the working chamber 1, and an exhaust valve 9 is provided between the exhaust port 7 and the working chamber 1. It can be understood that the structure of the diaphragm pump of the present embodiment is also applicable to the diaphragm compressor.

The term "diaphragm 3 sealingly disposed between the working chamber and the power chamber" means that the diaphragm 3 is not only disposed between the working chamber 1 and the power chamber 2, but also seals and separates the working chamber 1 and the power chamber 2, so that the working fluid a in the working chamber 1 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 figure 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 the internal pressure decreases. At this time, the suction valve 8 is opened because the left side pressure is lower than the right side pressure, and the discharge valve 9 is closed because the left side pressure is lower than the right side pressure. The working fluid a in flow at the inlet port 6 enters the working chamber 1 through the open suction valve 8. When the motor 5 drives the piston 4 to push the power fluid b to move rightwards in fig. 1, the diaphragm 3 deforms rightwards, and the volume of the working chamber 1 is reduced. 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 drives the piston 4 to reciprocate in the left-right direction in fig. 1, thereby continuously sucking the working fluid supplied to the inlet port 6 into the working chamber 1, and discharging the working fluid a sucked into the working chamber 1 to the outlet port 7 and out of the outlet port 7. The working fluid a is continuously fed in this way.

The motor 5 indirectly drives the piston 4 to reciprocate through a 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 operates to drive the diaphragm 3 to do work, 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 from the motor 5 to the diaphragm 3, and the driving path from 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 directly purchased in the market, and thus will not be described herein.

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

Referring again to fig. 1, the diaphragm pump is also provided with a power fluid storage chamber 10 and a third valve 11 in addition to the suction valve 8 and the discharge valve 9 described above. Wherein the motive fluid storage chamber 10 communicates with the motive chamber 2 for receiving the motive fluid b discharged from the motive chamber 2 and for providing the motive fluid b to the motive chamber 2. A valve 11 is provided in the communication path between the motive fluid storage chamber 10 and the motive chamber 2 for opening and closing the communication path between the motive fluid storage chamber 10 and the motive chamber 2.

In addition, the diaphragm pump is provided with a flywheel 24 and a speed reducer 12 in a transmission path between the motor 5 and the piston 4, that is, in 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 needs to be 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 reducer 12 functions to reduce the gear ratio to raise the torque and thus the driving force to which the piston 4 and the diaphragm 3 are subjected. The flywheel 24 serves to store energy and provide sufficient driving power and driving force to the diaphragm 3.

The diaphragm pump of the present embodiment is provided with the above-described power fluid storage chamber 10, valve 11 and flywheel 24, and can intermittently apply work to the outside with a large power in a case where the output power of the motor 5 itself is small. The specific analysis is as follows:

as shown with reference to fig. 1. In the starting stage of the motor 5, the rotating 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 at high power. At this time, the valve 11 is opened. When the piston 4 moves to the right, the hydraulic oil in the power chamber 2 as the power fluid b easily flows into the power fluid storage chamber 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 to do work. When the piston 4 moves to the left, the hydraulic oil in the power fluid storage chamber 10 is easily drawn into the power chamber 2 again. It is clear that neither pushing hydraulic oil from the power chamber 2 into the power fluid storage chamber 10 nor pumping hydraulic oil from the power fluid storage chamber 10 into the power chamber 2 consumes much power. In the process, the power provided by the motor 5 and the flywheel 24 to the piston 4 is small, 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 higher, and the kinetic energy is larger and larger. Obviously, the rotation speed of motor 5 is positively correlated with the rotation speed of flywheel 24. Specifically, in the present embodiment, the rotation speed ratio of motor 5 to flywheel 24 is 1. When the rotational speed of the motor 5 is raised to a set value, for example, when the motor 5 reaches a rated rotational speed, the valve 11 is closed. The communication path of the motive fluid storage chamber 10 with the motive chamber 2 is cut off, and the hydraulic oil of the motive chamber 2 cannot enter the motive fluid storage chamber 10. The piston 4 moving to the right can only push the hydraulic oil in the power chamber 2 to press the diaphragm 3 to the right, so that the diaphragm 3 deforms to the right 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 thrust to the piston 4, so that the diaphragm 3 is pushed to deform rightwards by the hydraulic oil in the power chamber 2, and a sufficient pressure is applied to the working fluid a in the working chamber 1, so that a large-power work on the working fluid a, such as pushing water to hundreds of meters high altitude, is completed.

The power source of the diaphragm pump is a motor 5, and the motor 5 drives the diaphragm 3 to move sequentially through a moving flywheel 24 and a piston 4 to do work. Based on this, it is clear that such a dynamic relationship exists: the motor 5 provides driving force for the flywheel 24, the piston 4 and the diaphragm 3, the flywheel 24 provides driving force for the piston 4 and the diaphragm 3, and the piston 4 provides driving force for the diaphragm 3.

If the valve 11 is kept closed during operation of the motor 5. The motor 5 as a power source cannot provide energy for the diaphragm 3 to work continuously with high power because of low power. The energy consumed by diaphragm 3 to do work is derived from the conversion of the new electric energy by motor 5 and the kinetic energy originally stored in flywheel 24. Therefore, under the condition that the newly added energy continuously provided by the motor 5 cannot meet the requirement of continuously doing work on the diaphragm 3, the flywheel 24 provides the supplementary energy for the work of the diaphragm 3. This results in a continuous decrease in kinetic energy of flywheel 24 and a smaller and smaller rotational speed. This not only results in an unstable operating speed of the motor 5, but ultimately renders the diaphragm 3 inoperable because of insufficient energy supply. Thus, the present embodiment provides the following diaphragm pump control method to solve the foregoing problems, the control method including:

s101, during the operation of the motor 5, controlling the valve 11 to open and close alternately at a first frequency.

That is, during operation of the motor 5, the valve 11 is alternately opened for a twenty-third period-closed for a twenty-fourth period-opened for a twenty-third period-closed for a twenty-fourth period … … at the set first frequency. That is, the drive path (or drive force transmission path) of the control flywheel 24 to the diaphragm 3 is alternately disconnected and engaged at the first frequency. In each cycle of this first frequency, the valve 11 has a continuous open duration and a continuous closed duration, the values of which can be set as desired. It will be appreciated that the greater the ratio of the opening duration to the closing duration of valve 11, the greater the proportion of flywheel 24 that is charged in each cycle; the smaller the ratio of the opening period to the closing period of the valve 11, the smaller the energy charging time ratio of the flywheel 24 in each cycle.

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

During the operation of the electric motor 5, the valve 11 is opened and closed alternately according to a set first frequency, so that the driving path of the flywheel 24 to the diaphragm 3 is opened and closed alternately, and the flywheel 24 and the diaphragm 3 do work intermittently in each cycle time of the first frequency, and the electric motor 5 periodically charges the flywheel 24 with energy. Generally, in each cycle time, for example, 2+4 ═ 6 seconds, the energy provided by the motor 5 which is continuously operated is balanced with the energy consumption of the diaphragm 3 which only works for a part of the time (for example, 4 seconds), and then the diaphragm pump can be continuously and stably operated.

It will be appreciated that with the valve 11 closed, the flywheel 24 is engaged in the drive path of the diaphragm 3, and the valve is closed for as long as the flywheel is engaged in 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 is the disconnection period of the flywheel from the drive path to the diaphragm. For convenience of description, herein, the engagement period of the flywheel 24 to the drive path of the diaphragm 3 is simply referred to as "the engagement period of the drive path", and the disconnection period of the flywheel 24 to the drive path of the diaphragm 3 is simply referred to as "the disconnection period of the drive path".

It is not appropriate to adopt this control strategy of S101 if the rotation speed of the motor 5 is low (e.g., just started). Therefore, the control strategy of S101 may be adopted only 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 drive 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 interval may be selected to be an interval of 9000-.

Of course, the switching frequency of the valve 11 may be adjusted correspondingly when the motor 5 is in different rotational speed intervals. For example, if it is determined that the speed of the electric motor 5 is in a second speed interval, different from and not intersecting the first speed interval, and smaller than the first 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 by: and the ratio of the engaging time length of the flywheel to the diaphragm driving path to the disconnecting time length in each period of the second frequency is not equal to the ratio of the engaging time length of the flywheel to the diaphragm driving path to the disconnecting time length in each period of the first frequency.

S102, in the process of the control valve 11 alternately opening and closing at the first frequency in the above S101, if it is detected that the rotation speed of the motor 5 is continuously decreased for the first time period, the control valve 11 alternately opens and closes at the third frequency; wherein the ratio of the closing period to the opening period of the valve 11 in each cycle of the third frequency < the ratio of the closing period to the opening period of the valve 11 in each cycle of the first frequency. The aforementioned first duration is typically several times to tens of times the single period of the first frequency.

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

During operation of the motor 5, the speed of rotation may vary due to certain factors, and if it is detected that the speed of rotation of the motor 5 decreases continuously over a first set longer period of time, for example two minutes, this means that the energy supplied by the motor 5 is less than the energy consumed by the diaphragm 3 to do work. Therefore, it is necessary to reduce the duty ratio of the working time of the diaphragm 3 or increase the duty ratio of the dead time of the flywheel 24. Thus, when it is detected that the rotation 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 the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency < the 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: open valve 4 seconds-close valve 2 seconds … …, still cycling on and off 10 times per minute. Of course, the third frequency could be adjusted to cycle on and off 3, 6 or 20 times per minute, etc.

It is known to those skilled in the art that the determination of whether the rotation speed of the motor 5 is continuously decreasing for the set first period of time may be performed by: in the process of the above-mentioned S101 control valve 11 alternately opening and closing at the first frequency, the rotation speed of the motor 5 is periodically acquired, and if the N motor rotation speeds acquired in the consecutive N cycles have a tendency to gradually decrease and the total time period of the aforementioned N cycles is equal to or greater than the first time period, it is said that the rotation speed of the motor 5 continuously decreases for the first time period. In some embodiments, a reduction threshold may also be provided, and the control valve 11 may be alternately opened and closed at the third frequency only when the rotation speed of the motor 5 is continuously reduced for the first period and the reduction value exceeds the set reduction threshold. Obviously, this control manner of setting the reduction threshold is included in the range of "if the rotation speed of the motor 5 is detected to be continuously reduced 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 the above S102, 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 period to the opening period of the valve 11 in each cycle of the fourth frequency < the ratio of the closing period to the opening period of the valve 11 in each cycle of the third frequency.

That is, in the process of controlling the flywheel 24 to alternately open and engage the drive path to the diaphragm 3 at the third frequency in S102, if it is determined that the rotation speed of the motor 5 continuously decreases for the second period of time, the flywheel 24 is controlled to alternately open and engage the drive path to the diaphragm 3 at the fourth frequency; wherein the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the fourth frequency < the ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency.

The rotational speed of the motor 5 is continuously reduced during a second period of time, which means that the energy supplied by the motor 5 is still less than the energy consumed by the diaphragm 3. Therefore, it is necessary to further reduce the duty ratio of the working time of the diaphragm 3 or further increase the duty ratio of the dead time of the flywheel 24. Thus, when it is detected that the rotation speed of the motor 5 continuously decreases for the second period, the control valve 11 is alternately opened and closed at the above-described fourth frequency.

Illustratively, at the fourth frequency: open valve 5 seconds-close valve 1 seconds-close valve 5 seconds-close valve 1 second … …, still cycling 10 times per minute. Also illustratively, valve open 10 seconds-valve closed 2 seconds … ….

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

That is, in the process of controlling the flywheel 24 to alternately open and engage the drive path to the diaphragm 3 at the third frequency in S102, if it is determined that the rotation speed of the motor 5 continuously increases for the third period of time, the flywheel 24 is controlled to alternately open and engage the drive path to the diaphragm 3 at the fifth frequency; wherein a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the fifth frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency.

The rotational speed of the motor 5 is continuously increased during a third period of time, which means that the energy supplied by the motor 5 is greater than the energy consumed by the diaphragm 3. Therefore, the working time ratio of the diaphragm 3 can be properly increased, or the no-load energy storage time ratio of the flywheel 24 can be properly reduced, so as to improve the working efficiency of the motor 5. Thus, upon detecting a continuous increase in the rotational speed of the motor 5 for the third period of time, the control valve 11 is alternately opened and closed at the above-described fifth frequency.

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

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

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

The rotational speed of the motor 5 is continuously reduced during a fourth period of time, which means that the energy supplied by the motor 5 is greater than the energy consumed by the diaphragm 3. Therefore, the working time ratio of the diaphragm 3 can be increased, or the no-load energy storage time ratio of the flywheel 24 can be shortened, so as to improve the working efficiency of the motor 5. Thus, when it is detected that the rotation speed of the motor 5 continuously decreases for the fourth period, the control valve 11 is alternately opened and closed at the sixth frequency.

Illustratively, the sixth frequency may be: open valve 4 seconds-close valve 11 seconds … …, cycle on and off 4 times per minute.

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

That is, in the process of controlling the flywheel 24 to alternately open and engage the drive path to the diaphragm 3 at the sixth frequency in S105, if it is determined that the rotation speed of the motor 5 continuously increases in the fifth period, the flywheel 24 is controlled to alternately open and engage the drive path to the diaphragm 3 at the seventh frequency; wherein a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the seventh frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the sixth frequency.

The rotational speed of the electric motor 5 is continuously increased during a fifth period of time, which means that the energy supplied by the electric motor 5 is still greater than the work energy consumed by the diaphragm 3 during this fifth period of time. Therefore, the working time ratio of the diaphragm 3 can be further increased, or the dead-time energy storage ratio of the flywheel 24 can be further reduced, so that the working efficiency of the motor 5 can be further improved. Thus, when it is detected that the rotation speed of the motor 5 continuously decreases for the fifth period, the control valve 11 is alternately opened and closed at the above-described seventh frequency.

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

S107, in the process of the above S105 where 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 in the sixth period, the control valve 11 is alternately opened and closed at the eighth frequency; wherein the ratio of the closing period to the opening period of the valve 11 in each cycle of the sixth frequency > the ratio of the closing period to the opening period of the valve 11 in each cycle of the eighth frequency > the ratio of the closing period to the opening period of the valve 11 in each cycle of the first frequency.

That is, in the process of controlling the flywheel 24 to alternately open and engage the drive path to the diaphragm 3 at the sixth frequency in S105, if it is determined that the rotation speed of the motor 5 continuously increases in the sixth period, the flywheel 24 is controlled to alternately open and engage the drive path to the diaphragm 3 at the eighth frequency; wherein a ratio of the engaging duration to the disengaging duration of the drive path in each cycle of the sixth frequency > a ratio of the engaging duration to the disengaging duration of the drive path in each cycle of the eighth frequency > a ratio of the engaging duration to the disengaging duration of the drive path in each cycle of the first frequency.

The rotational speed of the motor 5 is continuously reduced during a sixth period of time, which means that the energy supplied by the motor 5 is less than the energy consumed by the diaphragm 3. Therefore, the duty ratio of diaphragm 3 can be appropriately reduced, or the dead time ratio of flywheel 24 can be appropriately increased. Thus, when it is detected that the rotation speed of the motor 5 is continuously increased in the sixth period, the control valve 11 is alternately opened and closed at the above-described eighth frequency.

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

S108, if the rotation speed of the motor 5 is detected to be smaller than the first rotation speed threshold value, the control valve 11 is continuously opened; wherein the first rotating speed threshold value is smaller than the lower limit of the first rotating speed interval.

I.e. if it is determined that the rotational speed of the motor 5 is less than a relatively small first rotational speed threshold, the drive path of the flywheel 24 towards the diaphragm 3 is controlled to be continuously interrupted.

The first rotational speed threshold is a relatively small value which is smaller than the lower limit of the first rotational speed interval. When the rotation speed of the motor 5 is less than the first smaller rotation speed threshold, it indicates that the energy of the motor 5 and the flywheel 24 is already seriously insufficient, so that the valve 11 can be continuously opened at this time to keep the driving path of the flywheel 24 to the diaphragm 3 in a disconnected state, so as to avoid serious overload of the motor 5.

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

That is, in the process of controlling the flywheel 24 to continuously disconnect from the drive path 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, controlling the flywheel 24 to continuously engage with the drive path of the diaphragm 3; and the second rotating speed threshold value is not less than the first rotating speed threshold value.

It is understood that after executing S108, flywheel 24 is always maintained in the idle energy storage state, and the energy provided by motor 5 is completely converted into the kinetic energy of flywheel 24. When the rotational speed of motor 5 and flywheel 24 is high enough and the kinetic energy is large enough, the diaphragm pump operates idle and there is a waste of energy if valve 11 is still kept open. Thus, when it is detected that the rotation speed of the motor 5 is greater than the second rotation 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 drive path of the diaphragm 3, and the flywheel 24 continuously drives the diaphragm 3 to apply work.

It is to be understood that "continuously" in "continuously open" and "continuously closed" and "alternately" in "alternately open and closed" are relative concepts in the present application. Continuously open means that the valve is kept in an open state, and continuously closed means that the valve is kept in a closed state; and alternately opening and closing the valve means periodically opening the valve for a preset period of time and closing the valve for a preset period of time at a set frequency.

It is to be understood that the execution of S109 is not necessarily premised on S108. In other embodiments, regardless of the operating state of the valve 11, the valve 11 may be controlled to be continuously closed as long as the rotation speed of the motor 5 is detected to be greater than the second rotation speed threshold.

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

Obviously, during the above-mentioned process of S109, if it is detected that the rotation speed of the motor 5 returns to the aforementioned first rotation speed interval, the valve 11 may be controlled to continue to open and close alternately at the first frequency.

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

that is, if it is determined that the rotation speed of motor 5 is less than the first rotation speed threshold value, flywheel 24 is controlled to be continuously disconnected from the drive path to diaphragm 3. Controlling flywheel 24 to continue engaging the drive path of diaphragm 3 if it is determined that the speed of rotation of motor 5 is greater than the second speed threshold; and the second rotating speed threshold value is not less than the first rotating speed threshold value. In this control scheme using the strategies S108 and S109 alone, the second rotational speed threshold may be generally equal to the first rotational speed threshold. The disadvantages are that: the rotation speed of the motor 5 may be unstable.

As shown in fig. 10, in order to better implement the control strategy of S101-S109, the valve 11 of the present embodiment employs an electrically-controlled valve that can be opened and closed electrically, and a motor speed sensor 34 for detecting the rotation speed of the motor 5 is further provided, and both the motor speed sensor 34 and the valve 11 are connected in communication with 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 implement the above-described control method. It is to be noted that the opening and closing of the control valve 11 may also not be based on the rotational speed of the motor 5. In other embodiments of the present application, the motor speed sensor 34 is removed and the valve 11 is controlled to "alternately open and close at the first frequency" using only the controller 35 in communicative connection with the 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, and when the computer instructions are executed by the processor, the various control methods are implemented.

Such as:

during the operation of the motor 5, the controller 35 acquires the rotation speed of the motor 5 from the motor rotation speed sensor 34;

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

For another example:

during the operation of the motor 5, the controller 35 acquires the rotation speed of the motor 5 from the motor rotation speed sensor 34;

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

if it is determined that the speed of rotation of the electric motor 5 is greater than the second speed threshold, the controller 35 sends different command signals to the electrically controlled valve 11 to control the valve 11 to close continuously; and the second rotating speed threshold value is not less than the first rotating 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 above, the "opening" of the valve 11 generally includes two situations: 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 the 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 open the valve 11.

Similarly, two situations are generally also included for the "closed" valve 11: 1) if the valve 11 is originally in the open state, the controller 35 sends a command signal to the valve 11 to control the valve 11 to switch to the closed state. 2) If the valve 11 is already closed, for example, if the valve 11 is normally closed, the controller 35 may not act on the valve 11, or may send a command signal to the valve 11 to close the valve 11.

Thus, if the valve 11 is a normally closed valve, the "control valve 11 alternately opens and closes at a first frequency" may be implemented such that: the controller 35 alternately sends and stops sending command signals to the valve 11 at a first frequency to cause the valve to open. When the controller 35 sends a command signal to open the valve 11, the valve 11 opens; when the controller 35 stops sending the command signal to open the valve 11, the valve 11 is automatically closed. It is also within the scope of the present application to control valve closure that controller 35 stops sending command signals to open valve 11, causing normally closed valve 11 to close automatically. In particular only in that it "controls" the valve 11 to close, by stopping the transmission of the relevant signal or in what is called a non-functioning way.

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

Those skilled in the art will understand that: the obtaining of the rotation speed information of the motor 5 is one of the conditions for smoothly implementing the control methods of S101 to S109, for example, the rotation 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 rotation speed of the motor satisfies the corresponding conditions, the control valve 11 may perform corresponding response actions, such as the control valve 11 alternately opening and closing at a first frequency when the rotation speed of the motor is determined to be in a preset first rotation speed interval, and the control valve 11 continuously opening when the rotation speed of the motor is determined to be greater than a preset second rotation speed threshold.

As mentioned above, the motor 5 does work outwards only when running at a high speed, one reason is that the flywheel 24 is also in a high-speed motion state and has a large kinetic energy, and the flywheel 24 running at a high speed and storing a large amount of kinetic energy can do work outwards with a large power. Therefore, the mass of flywheel 24 can be increased by increasing the mass of flywheel 24, preferably by 5kg or more, to increase the kinetic energy of flywheel 24 at high speed, and the mass of flywheel 24 can further increase the short-term power of the diaphragm pump.

Flywheel 24 is typically made of metal or carbon fiber.

The output power of some motors 5 is small when the motors are started or run at low speed, and considerable output power is obtained only after the rotating speed of the motors 5 reaches a certain value, which is also one of the reasons for adopting 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 flywheel 24 is large enough, it can do work with large power outwards only by means of the inertia of flywheel 24. The kinetic energy of flywheel 24 is mainly derived from its speed, and the upper speed limit of flywheel 24 is determined by motor 5, so that motor 5 can be selected as a high-speed motor with a rated rotation speed not less than 10000 r/min. Of course, the speed of the transfer system and the piston 4 must not be too high, otherwise mechanical damage is easily caused. Therefore, when the rated rotation speed of the motor 5 is large, it is preferable to arrange the speed reducer 12 in the transmission system, so that the mechanical damage can be reduced, and the driving force to which the diaphragm 3 is subjected can be raised.

It should be noted that the motor speed sensor 34 may directly detect the speed of the motor 5, or may indirectly detect the speed of the motor 5 by detecting the speed of other elements in transmission connection with the motor 5, such as the flywheel 24 or the speed reducer 12 or the crankshaft 13 described below. Even the rotation speed of the motor 5 can be indirectly judged by detecting other physical quantities related to the rotation speed of the motor, and the related physical quantities detected by such sensors can be regarded as the motor rotation speed sensors as long as the related physical quantities are highly related to the rotation speed of the motor 5. The detection of the rotation speed of the motor 5 by the motor rotation speed sensor 34 may be direct or indirect, and the present application is not limited thereto.

The present embodiment arranges the power fluid storage chamber 10 above the power chamber 2 so that when the valve 11 is in the open state, the power fluid b (hydraulic oil) in the power fluid storage chamber 10 automatically flows into the power chamber 2 with the increased volume (when the piston is retracted) under its own weight, 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 oil tank.

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

referring to fig. 1, 3 and 4, the transmission system includes the flywheel 24, the reducer 12, the crankshaft 13, the first connecting rod 14, the second connecting rod 15 and the push-pull rod 16, which are arranged in this order along the transmission direction. An input shaft of the speed reducer 12 is connected with an output shaft of the motor 5 through a coupling 25, and an output shaft of the speed reducer 12 is connected with one end of the crankshaft 13 through the coupling 25. The other end of the crankshaft 13 is pivotally supported on the housing 33 of the diaphragm pump. The first link 14 has one end pivotally connected to the curved portion of the crankshaft 13 and the other end pivotally connected to one end of the second link 15 via 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 to the piston 4, although it is also possible to pivotally connect the other end of the push-pull rod 16 to 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 the housing 33. The push-pull rod 16 is a linear rod extending left and right, i.e., linearly along the direction of movement of the piston 4.

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

In this embodiment, the guide seat 23 is integrally connected to 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 holder 23 may be a separate member separately 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 reducer 12. The crankshaft 13 rotates (revolves) one end of the first connecting rod 14 about a 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 link 15 drives the push-pull rod 16 to reciprocate in the left-right direction in fig. 1.

Obviously, the above-described structural design is equally applicable to a diaphragm compressor for compressing a working fluid.

In order to improve the adaptability of the diaphragm 3 to deform leftwards and rightwards and further improve the service life of the diaphragm 3, the diaphragm 3 of the present embodiment is integrally provided with annular deformation wrinkles 3a protruding rightwards in the thickness direction of the diaphragm.

The primary 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 working fluid. The piston 4 and the transmission system connecting the motor and the piston, including the flywheel 24, are all arranged in a drive path of the motor 5 to the diaphragm 3, and the piston 4 and the transmission system connecting the motor and the piston are all part of the drive path of the motor 5 to the diaphragm 3. 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 force chamber 2 is also provided in a driving path through which the motor 5 transmits a driving force to the diaphragm 3, and has a function of transmitting the driving force to the diaphragm 3, so that the motive fluid b filled in the motive force chamber 2 is also a component of the driving path through which the motor 5 (or the flywheel 24, or the piston 4) transmits the driving force to the diaphragm 3.

Further, the deformed pleats 3a have a circular ring shape to accommodate the leftward and rightward deformation characteristics of the diaphragm 3. The diaphragm 3 is composed of 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 wrinkles 3a are formed specifically on the first portion.

The deformation fold 3a is arranged close to the outer edge of the first part of the diaphragm, so that the enclosed area of the deformation fold 3a is as large as possible, and the purpose of the arrangement is to promote the leftward and rightward deformation of the diaphragm 3, and further promote the extrusion amount of the working fluid.

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

Example two:

fig. 7 shows a second type of diaphragm pump, which is similar in structure to the first embodiment except that:

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 in the flywheel 24 to piston 4 transmission, the clutch 37 being connected in series between the flywheel 24 and piston 4. Obviously, the clutch 37 is arranged in the drive path from the motor 5 to the diaphragm 3, and the clutch 37 also forms part of the drive path from 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; with the clutch 37 engaged, the drive path from the flywheel 24 to the diaphragm 3 is engaged. It can be seen that the clutch 37 has the same function as the power fluid storage chamber 10 and valve 11 of the first embodiment.

As shown in fig. 8, in order to enable the clutch 37 to be automatically engaged or disengaged according to the rotation speed of the motor 5, the clutch 37 is an electrically controlled clutch that can be electrically controlled to be engaged or disengaged, and a motor rotation speed sensor 34 that detects the rotation speed of the motor 5 and a controller 35 that is connected to the motor rotation speed sensor 34 and the clutch 37 in communication are provided. The controller 35 is configured to acquire the rotation speed of the motor 5 from the motor rotation speed sensor 34, and control the engagement and disengagement of the clutch 37 based on the rotation speed, so as to implement the following control method substantially the same as the first embodiment:

the embodiment provides the following control method of the diaphragm pump:

s201, during operation of the electric machine 5, the clutch 37 is controlled to be alternately disengaged and engaged at a 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 a first frequency.

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

In other embodiments, motor speed sensor 34 may not be provided, and controller 35 may be caused to control clutch 37 to alternately disengage and engage at the first frequency simply by a user command applied to controller 35.

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

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

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

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

S204, in the process of controlling the clutch 37 to be alternately disengaged and engaged at the third frequency in the above S202, if it is detected that the rotation speed of the electric motor 5 is continuously increased for the third period, controlling the clutch 37 to be alternately disengaged and engaged at the fifth frequency; wherein the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the first frequency > the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the fifth frequency > the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the third frequency.

That is, in the process of controlling the flywheel 24 to alternately open and engage the drive path to 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 flywheel 24 is controlled to alternately open and engage the drive path to the diaphragm 3 at the fifth frequency; wherein a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the first frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the fifth frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the third frequency.

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

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

S206, in the process of controlling the clutch 37 to be alternately disengaged and engaged at the sixth frequency in S205 described above, if it is detected that the rotation speed of the electric motor 5 is continuously increased in the fifth period, the clutch 37 is controlled to be alternately disengaged and engaged at the seventh frequency. Wherein the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle of the seventh frequency > the ratio of the engaging duration to the disengaging duration of the clutch 37 in each cycle 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, if it is determined that the rotation speed of the motor 5 continuously increases in the fifth period, 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 the engagement duration to the disengagement duration of the drive path in each cycle of the seventh frequency > a ratio of the engagement duration to the disengagement duration of the drive path in each cycle of the sixth frequency.

S207, in the process of controlling the clutch 37 to be alternately disengaged and engaged at the sixth frequency in S205 described above, if it is detected that the rotation speed of the electric motor 5 is continuously decreased in the sixth period, the clutch 37 is controlled to be alternately opened and closed at the eighth frequency. Wherein the ratio of the engaging duration to the disengaging 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 engaging duration to the disengaging 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 continuously increases 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 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 eighth frequency > a ratio of an engagement duration to a disengagement duration of the drive path in each cycle of the first frequency

S208, if the rotation speed of the motor 5 is detected to be less than the first rotation speed threshold value, controlling the clutch 37 to be continuously disengaged; wherein the first rotation speed threshold is smaller than the lower limit of the first rotation speed interval in S201.

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

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

That is, in the process of controlling the flywheel 24 to continuously disconnect the drive path to 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 flywheel 24 is controlled to continuously engage the drive path to the diaphragm 3; and the second rotating speed threshold value is not less than the first rotating speed threshold value.

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

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

that is, if it is determined that the rotation speed of motor 5 is less than the first rotation speed threshold value, flywheel 24 is controlled to be continuously disconnected from the drive path to diaphragm 3. Controlling flywheel 24 to continue to engage the drive path of diaphragm 3 if it is determined that the speed of rotation of motor 5 is greater than the second speed threshold; and the second rotating speed threshold value is not less than the first rotating speed threshold value. In such a control mode, the second rotational speed threshold may generally be equal to the first rotational speed threshold. The disadvantages are that: the rotation speed of the motor 5 may be unstable.

The controller 35 configured 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, wherein the computer instructions, when executed by the processor, implement the control method.

To ensure a long service life of the clutch 37, a flexible clutch may be used for the clutch 37. Also, it is preferable to connect the flexible clutch in series between the flywheel 24 and the reducer 12, not on the downstream side of the reducer 12, to reduce the stress of the flexible clutch.

Example three: air conditioning system

Fig. 9 shows an air conditioning system capable of intermittently performing high power work. The air conditioning system includes a compressor 100, a condenser 200, a throttle valve 300, and an evaporator 400 fluidly connected in sequence and forming a closed circuit. The air conditioning system is charged with a refrigerant. When the air conditioner works, the refrigerant flows through the compressor, the condenser, the throttle valve and the evaporator in sequence, so that the air conditioner 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 structure of the diaphragm compressor is substantially the same as that of the diaphragm pump in the second embodiment, and the air conditioning system also includes a motor speed sensor 34 and a controller 35 communicatively connected to the motor speed sensor, except that the diaphragm compressor is not equipped with the clutch in the second embodiment, and refer to fig. 7.

In addition, the air conditioning system is provided with an electrically 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 such that the controller 35 controls the operating state of the electrically controlled valve 38 based on the rotational speed of the motor.

If the electrically controlled valve 38 is kept closed, the air conditioning system operates in the same manner as 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 large, such as when carbon dioxide is used as the refrigerant. Therefore, when the rotation speed of the motor 5 is low and the energy stored in the flywheel 24 is insufficient, the compressor 100 cannot work normally.

If the electronic control valve 38 is kept in the open state, which corresponds to "short-circuiting" the throttle valve 300 and removing it from the circuit, the electronic control valve 38 having no 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. In this case, of course, 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 the modification:

s301, during the operation of the motor of the diaphragm compressor 100, if the rotation speed of the motor is detected to be in the first rotation speed interval, the electronically controlled valve 38 is controlled to be alternately opened and closed at the first frequency.

For example, during operation of the motor, the electronically controlled valve 38 is alternately opened and closed at a frequency of 10 times per minute, and 2 seconds and 4 seconds of closure each time. Wherein 10 times/minute means that the valve is opened 10 times and the valve is closed 10 times every 1 minute, and the opening and closing are alternately performed. Specifically, the electric control valve is opened for 2 seconds, the electric control valve is closed for 4 seconds, the electric control valve is opened for 2 seconds, and the electric control valve is closed for 4 seconds … …. It will be appreciated that the greater the ratio of the open duration to the closed duration of electronically controlled valve 38, the greater the percentage of flywheel 24 energy storage time in each cycle; the smaller the ratio of the open duration to the closed duration of electronically controlled valve 38, the smaller the energy storage time fraction of flywheel 24 in each cycle.

During the operation of the electric motor 5, the electronically controlled valve 38 is controlled to alternately open and close at a set first frequency, thereby causing the flywheel 24 and the diaphragm 3 to intermittently perform work during each cycle time of the first frequency. Motor 5 periodically charges flywheel 24 with energy. If the energy supplied by the motor 5 during continuous operation (e.g. 2 seconds as described above) is balanced with the energy consumed by the diaphragm 3 during normal work only for a part of the period (e.g. 4 seconds as described above) during each cycle, the diaphragm pump can continue to operate stably.

It is not appropriate to adopt the control strategy of S301 if the rotation speed of the motor 5 is low (e.g., just started). Therefore, the control strategy of S301 may be adopted only when the rotation speed of the motor 5 is in the first rotation speed range set as described above. The first rotational speed range is preferably a range around the rated rotational speed of the motor 5. For example, if the rated rotational speed of the motor 5 is 10000 rpm, the first rotational speed interval may be selected to be an interval of 9000-.

Of course, the switching frequency of the electronically controlled valve 38 can also be adjusted when the electric motor 5 is in different speed ranges. For example, if it is determined that the speed of the electric machine 5 is in a second speed interval, different from and not intersecting the first speed interval, and smaller than the first speed interval, the electronically controlled valve 38 is controlled to alternately open and close at a second frequency different from the first frequency. I.e. if it is determined that the rotational speed of the motor 5 is in the second rotational speed interval, the working load of the diaphragm 3 is controlled to be alternately switched off and on at the second frequency.

S302, in the process of controlling the electric control valve 38 to be opened and closed alternately at the first frequency in S301, if the rotation speed of the motor is detected to be continuously reduced within the first time period, controlling the electric control valve 38 to be opened and closed alternately at the third frequency; wherein the ratio of the closing duration to the opening duration of the electrically controlled valve 38 in each cycle of the third frequency < the ratio of the closing duration to the opening duration of the electrically controlled valve 38 in each cycle of the first frequency.

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

S304, in the process of controlling the electronically controlled valve 38 to alternately open and close at the third frequency in S302, if it is detected that the rotation speed of the motor 5 continuously increases in the third period, the electronically controlled valve 38 is controlled to alternately open and close at the fifth frequency. Wherein, the ratio of the closing duration to the opening duration of the electronic control valve 38 in each period of the first frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each period of the fifth frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each period of the third frequency.

S305, in the process of controlling the electronic control valve 38 to be opened and closed alternately at the first frequency in S301, if the rotation speed of the motor is detected to be continuously increased within the fourth time period, controlling the electronic control valve 38 to be opened and closed alternately at the sixth frequency; wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the sixth frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the first frequency.

S306, in the process of controlling the electronic control valve 38 to alternately open and close at the sixth frequency in S305, if it is detected that the rotation speed of the motor continuously increases in the fifth period, the electronic control valve 38 is controlled to alternately open and close at the seventh frequency. Wherein the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the seventh frequency > the ratio of the closing duration to the opening duration of the electronically controlled valve 38 in each cycle of the sixth frequency.

S307, in the process of S305 controlling the electronic control valve 38 to be alternately opened and closed at the sixth frequency, if it is detected that the rotation speed of the motor is continuously decreased in the sixth period, the electronic control valve 38 is controlled to be alternately opened and closed at the eighth frequency. Wherein, the ratio of the closing duration to the opening duration of the electronic control valve 38 in each cycle of the sixth frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each cycle of the eighth frequency > the ratio of the closing duration to the opening duration of the electronic control valve 38 in each cycle of the first frequency.

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

And S309, if the rotation speed of the motor 5 is detected to be greater than the second rotation speed threshold value, controlling the electronic control valve 38 to be continuously closed. The second rotation speed threshold is not less than the first rotation speed threshold in S308, and is generally greater than the upper limit value of the first rotation speed section in S301.

The electrically controlled valve 38 is preferably a normally closed valve or a normally open valve for simplicity of control.

The controller 35 in fig. 10 includes a memory, a processor connected to the memory, and computer instructions stored in the memory and executable by the processor, and when the computer instructions are executed by the processor, the control method in the embodiment can be implemented.

Claims (5)

1. An air conditioning system includes a compressor (100), a condenser (200), a throttle valve (300), and an evaporator (400) that are fluidly connected in sequence and form a closed circuit;

it is characterized in that the preparation method is characterized in that,

the compressor (100) is a diaphragm compressor comprising:

a membrane sheet (3),

a motor (5) for providing a driving force to the diaphragm,

a flywheel (24) arranged in the drive path of the motor to the diaphragm, and

a motor rotational speed sensor (34) for detecting a rotational speed of the motor;

an electric control valve (38) which is connected with the throttle valve (300) in parallel and is in communication connection with the motor rotating speed sensor (34) is arranged between the condenser (200) and the evaporator (400).

2. Air conditioning system according to claim 1, characterized in that the electrically controlled valve (38) is configured to: is turned on or off based on the rotation speed of the motor (5) detected by the motor rotation speed sensor (34).

3. Air conditioning system according to claim 1 or 2, characterized in that the communication connection of the electrically controlled valve (38) with the motor speed sensor (34) is realized by means of a controller (35) which is in communication connection with the electrically controlled valve (38) and the motor speed sensor (34), respectively.

4. The air conditioning system of claim 3, wherein the controller is configured to: the rotating speed of the motor (5) is obtained from the motor rotating speed sensor (34), and the electronic control valve (38) is controlled to be opened or closed based on the rotating speed.

5. The air conditioning system of claim 4, wherein said controlling the electronically controlled valve (38) to open or close based on the rotational speed comprises:

in response to determining that the rotational speed is in a first rotational speed interval, controlling the electronically controlled valve (38) to alternately open and close at a first frequency; wherein the rated speed of the motor (5) is in the first speed range.

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