CN112556227A - Air conditioning unit, frequency converter cooling system and control method thereof - Google Patents

Air conditioning unit, frequency converter cooling system and control method thereof Download PDF

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Publication number
CN112556227A
CN112556227A CN202011530013.1A CN202011530013A CN112556227A CN 112556227 A CN112556227 A CN 112556227A CN 202011530013 A CN202011530013 A CN 202011530013A CN 112556227 A CN112556227 A CN 112556227A
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China
Prior art keywords
temperature difference
target temperature
value
evaporator
compressor
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Pending
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CN202011530013.1A
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Chinese (zh)
Inventor
李家新
梅正茂
姜智博
郭晓迪
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Priority to CN202011530013.1A priority Critical patent/CN112556227A/en
Publication of CN112556227A publication Critical patent/CN112556227A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02M—APPARATUS FOR CONVERSION BETWEEN AC AND AC, BETWEEN AC AND DC, OR BETWEEN DC AND DC, AND FOR USE WITH MAINS OR SIMILAR POWER SUPPLY SYSTEMS; CONVERSION OF DC OR AC INPUT POWER INTO SURGE OUTPUT POWER; CONTROL OR REGULATION THEREOF
    • H02M1/00—Details of apparatus for conversion
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
    • H05K7/00—Constructional details common to different types of electric apparatus
    • H05K7/20—Modifications to facilitate cooling, ventilating, or heating
    • H05K7/2089—Modifications to facilitate cooling, ventilating, or heating for power electronics, e.g. for inverters for controlling motor
    • H05K7/20936—Liquid coolant with phase change

Abstract

The disclosure relates to an air conditioning unit, a frequency converter cooling system and a control method thereof. The frequency converter cooling system includes: the air conditioner comprises a compressor, a condenser and at least two refrigerating paths, wherein the condenser is communicated with an exhaust port of the compressor, each refrigerating path is provided with a throttling element and an evaporator which are connected in series, the evaporators in the at least two refrigerating paths are respectively configured to cool a plurality of modules in the frequency conversion cabinet, and the at least two refrigerating paths are connected between the condenser and an air suction port of the compressor in a parallel mode. The embodiment of the disclosure can optimize the cooling mode of the frequency converter.

Description

Air conditioning unit, frequency converter cooling system and control method thereof
Technical Field
The disclosure relates to the field of refrigeration, in particular to an air conditioning unit, a frequency converter cooling system and a control method thereof.
Background
The frequency converter belongs to an AC electric transmission system, and is a power electronic converter which converts an AC power frequency power supply into a variable voltage and frequency and is suitable for AC motor speed regulation. The high-power frequency converter can generate a large amount of heat in the working process, and the frequency converter and other components are possibly burnt out due to overlarge heat productivity. In some prior art, the cooling of the frequency converter is performed by providing a dedicated cooling device. The cooling method comprises air cooling, water cooling, refrigerant cooling and the like.
Disclosure of Invention
The inventor finds that the air cooling mode in the related art needs to occupy the internal space of the frequency conversion cabinet, dirt easily enters the frequency conversion cabinet along with air flow, and the temperature control is unstable, so that the air cooling mode is difficult to be applied to a high-power frequency converter; the water cooling mode in the related art is difficult to be applied to areas lacking water resources, and the risk of circuit breaking of electronic devices in the frequency conversion cabinet due to water leakage exists; the cooling medium cooling mode in the related art is difficult to realize independent and accurate temperature control on each plate inside the frequency conversion cabinet.
In view of this, the embodiments of the present disclosure provide an air conditioning unit, an inverter cooling system and a control method thereof, which can optimize an inverter cooling method.
In one aspect of the present disclosure, there is provided an inverter cooling system comprising: the air conditioner comprises a compressor, a condenser and at least two refrigerating paths, wherein the condenser is communicated with an air outlet of the compressor, each refrigerating path is provided with a throttling element and an evaporator which are connected in series, the evaporators in the at least two refrigerating paths are respectively configured to cool a plurality of modules in a frequency conversion cabinet, and the at least two refrigerating paths are connected between the condenser and an air suction port of the compressor in a parallel mode.
In some embodiments, the at least two refrigeration circuits include a first refrigeration circuit including, in series and in series from the condenser to the suction port of the compressor, a first throttling element, a first evaporator and an evaporating pressure regulator, the first evaporator having a saturation temperature corresponding to its own rated evaporating pressure that is higher than the saturation temperature corresponding to its own rated evaporating pressure of the evaporators of the other of the at least two refrigeration circuits, the evaporating pressure regulator being configured to maintain the operating evaporating pressure of the first evaporator within a preset pressure range.
In some embodiments, the first evaporator comprises a cold plate evaporator, and the corresponding module of the cold plate evaporator comprises at least one of a rectification module and an inversion module in the inverter cabinet.
In some embodiments, the at least two refrigeration circuits further include a second refrigeration circuit, the second refrigeration circuit includes a second throttling element, a second evaporator and a first check valve which are connected in series in sequence from the condenser to the suction port of the compressor, and the saturation temperature corresponding to the self-rated evaporation pressure of the second evaporator is lower than the saturation temperature corresponding to the self-rated evaporation pressure of the evaporator of the other refrigeration circuit in the at least two refrigeration circuits.
In some embodiments, the second evaporator comprises a dehumidification evaporator, and the corresponding module of the dehumidification evaporator comprises a dehumidification module in the inverter cabinet.
In some embodiments, the at least two refrigeration circuits further include a third refrigeration circuit including a third throttling element, a third evaporator and a second check valve connected in series in sequence from the condenser to the suction port of the compressor, and a saturation temperature corresponding to a self-rated evaporating pressure of the third evaporator is lower than a saturation temperature corresponding to a self-rated evaporating pressure of the first evaporator and higher than a saturation temperature corresponding to a self-rated evaporating pressure of the second evaporator.
In some embodiments, the third evaporator comprises a reactive evaporator, and the corresponding module of the reactive evaporator comprises a reactive module in the frequency conversion cabinet.
In some embodiments, the first throttling element and the second throttling element each comprise an electronic expansion valve and the third throttling element comprises a capillary tube.
In some embodiments, each of the at least two refrigeration circuits further includes a first shut-off valve and a second shut-off valve, the evaporators in the refrigeration circuits being connected in series between the first shut-off valve and the second shut-off valve.
In one aspect of the disclosure, an air conditioning unit is provided, which comprises the inverter cooling system.
In an aspect of the present disclosure, there is provided a control method of the aforementioned frequency converter cooling system, including:
detecting the temperature of each module in the frequency conversion cabinet;
calculating a first target temperature difference, wherein the first target temperature difference is a result of subtracting a preset first temperature threshold from the temperature of a module corresponding to the first evaporator, and the preset first temperature threshold is a saturation temperature corresponding to the self rated evaporation pressure of the first evaporator;
calculating a second target temperature difference, wherein the second target temperature difference is a result of subtracting a preset second temperature threshold from the temperature of a module corresponding to the second evaporator, and the preset second temperature threshold is a saturation temperature corresponding to the self-rated evaporation pressure of the second evaporator;
and controlling the compressor and the evaporation pressure regulator according to the value ranges corresponding to the first target temperature difference and the second target temperature difference respectively.
In some embodiments, the step of controlling the compressor and the evaporation pressure regulator according to the value ranges corresponding to the first target temperature difference and the second target temperature difference respectively comprises:
when the first target temperature difference and the second target temperature difference are both larger than the positive tolerance value, enabling the compressor to run at full frequency, and enabling the evaporation pressure regulator to be opened so as to reduce the working evaporation pressure of the first evaporator;
when the first target temperature difference is larger than the positive tolerance value, and the second target temperature difference is larger than or equal to 0 ℃ and smaller than or equal to the positive tolerance value, enabling the compressor to run at full frequency, and enabling the evaporation pressure regulator to be opened so as to reduce the working evaporation pressure of the first evaporator;
and when the first target temperature difference is larger than the positive tolerance value and the second target temperature difference is smaller than 0 ℃, enabling the compressor to run at full frequency and enabling the evaporation pressure regulator to be opened so as to reduce the working evaporation pressure of the first evaporator.
In some embodiments, the step of controlling the compressor and the evaporation pressure regulator according to the value ranges corresponding to the first target temperature difference and the second target temperature difference respectively comprises:
when the first target temperature difference is smaller than a negative tolerance value and the second target temperature difference is larger than a positive tolerance value, enabling the compressor to run at full frequency and the evaporation pressure regulator to be closed and set to be not triggerable;
when the first target temperature difference is less than a negative tolerance value and the second target temperature difference is less than 0 ℃, enabling the compressor to run at the lowest frequency and enabling the evaporation pressure regulator to be closed and set to be triggerable;
and when the first target temperature difference is smaller than a negative tolerance value, and the second target temperature difference is greater than or equal to 0 ℃ and less than or equal to a positive tolerance value, enabling the compressor to operate at a frequency which is less than a full frequency and greater than a lowest frequency, and enabling the evaporation pressure regulator to be closed and set to be triggerable.
In some embodiments, the step of controlling the compressor and the evaporation pressure regulator according to the value ranges corresponding to the first target temperature difference and the second target temperature difference respectively comprises:
and when the first target temperature difference is greater than or equal to a negative tolerance value and less than or equal to a positive tolerance value, and the second target temperature difference is greater than the positive tolerance value, enabling the compressor to run at full frequency, enabling the evaporation pressure regulator to be closed, and setting the saturation temperature corresponding to the opening trigger value of the evaporation pressure regulator as a result of subtracting the temperature variable from the preset first temperature threshold.
In some embodiments, the control method further comprises at least one of:
detecting whether a first condition that the first target temperature difference is continuously increased within a preset first time length is met, if the first condition is met, increasing the value of the temperature variable, and if not, maintaining the value of the temperature variable;
and detecting whether a second condition that the first target temperature difference is continuously greater than a tolerance intermediate value within a preset second time length is met, wherein the tolerance intermediate value is greater than 0 ℃ and smaller than the tolerance positive value, if the second condition is met, the value of the temperature variable is increased, and if the second condition is not met, the value of the temperature variable is maintained.
In some embodiments, the step of controlling the compressor and the evaporation pressure regulator according to the value ranges corresponding to the first target temperature difference and the second target temperature difference respectively comprises:
and when the first target temperature difference is greater than or equal to a negative tolerance value and less than or equal to a positive tolerance value, and the second target temperature difference is greater than or equal to 0 ℃ and less than or equal to a positive tolerance value, the compressor is operated at a frequency which is less than a full frequency and greater than a lowest frequency, the evaporation pressure regulator is closed, and the saturation temperature corresponding to the opening trigger value of the evaporation pressure regulator is set as a result of subtracting a temperature variable from a preset first temperature threshold value.
In some embodiments, the control method further comprises at least one of:
detecting whether a first condition that the first target temperature difference is continuously increased within a preset first time length is met, if the first condition is met, increasing the value of the temperature variable, and if not, maintaining the value of the temperature variable;
detecting whether a second condition that the first target temperature difference is continuously greater than a tolerance intermediate value within a preset second duration is met, wherein the tolerance intermediate value is greater than 0 ℃ and smaller than the tolerance positive value, if the second condition is met, increasing the value of the temperature variable, and if not, maintaining the value of the temperature variable;
and detecting whether a third condition that the second target temperature difference is continuously increased within a preset third time period is met, and if the third condition is met, increasing the operating frequency of the compressor.
In some embodiments, the step of controlling the compressor and the evaporation pressure regulator according to the value ranges corresponding to the first target temperature difference and the second target temperature difference respectively comprises:
and when the first target temperature difference is greater than or equal to a negative tolerance value and less than or equal to a positive tolerance value, and the second target temperature difference is less than 0 ℃, enabling the compressor to operate at a frequency which is less than a full frequency and greater than a lowest frequency, enabling the evaporation pressure regulator to be closed, and setting a saturation temperature corresponding to an opening trigger value of the evaporation pressure regulator as a result of subtracting a temperature variable from a preset first temperature threshold value.
In some embodiments, the control method further comprises at least one of:
detecting whether a first condition that the first target temperature difference is continuously increased within a preset first time length is met, if the first condition is met, increasing the value of the temperature variable, and if not, maintaining the value of the temperature variable;
detecting whether a second condition that the first target temperature difference is continuously greater than a tolerance intermediate value within a preset second duration is met, wherein the tolerance intermediate value is greater than 0 ℃ and smaller than the tolerance positive value, if the second condition is met, increasing the value of the temperature variable, and if not, maintaining the value of the temperature variable;
and detecting whether a fourth condition that the second target temperature difference is continuously less than 0 ℃ within a preset fourth time period is met, and reducing the operating frequency of the compressor if the fourth condition is met.
In some embodiments, the temperature variable has a value greater than 0 ℃ and less than or equal to 15 ℃.
Therefore, according to the embodiment of the disclosure, the evaporators in at least two refrigeration paths are used for respectively cooling the modules in the frequency conversion cabinet, and the working evaporation pressures of the evaporators in different refrigeration paths are adjusted as required, so as to maintain stable refrigeration output, reduce temperature fluctuation and improve the stability and accuracy of temperature control of the corresponding modules in the frequency conversion cabinet.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description, serve to explain the principles of the disclosure.
The present disclosure may be more clearly understood from the following detailed description, taken with reference to the accompanying drawings, in which:
FIG. 1 is a schematic block diagram of some embodiments of an inverter cooling system according to the present disclosure;
FIG. 2 is a schematic flow diagram of some embodiments of a control method of an inverter cooling system according to the present disclosure.
It should be understood that the dimensions of the various parts shown in the figures are not drawn to scale. Further, the same or similar reference numerals denote the same or similar components.
Detailed Description
Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and is in no way intended to limit the disclosure, its application, or uses. The present disclosure may be embodied in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art. It should be noted that: the relative arrangement of parts and steps, the composition of materials, numerical expressions and numerical values set forth in these embodiments are to be construed as merely illustrative, and not as limitative, unless specifically stated otherwise.
The use of "first," "second," and similar terms in this disclosure is not intended to indicate any order, quantity, or importance, but rather are used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that the element preceding the word covers the element listed after the word, and does not exclude the possibility that other elements are also covered. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.
In the present disclosure, when a specific device is described as being located between a first device and a second device, there may or may not be intervening devices between the specific device and the first device or the second device. When a particular device is described as being coupled to other devices, that particular device may be directly coupled to the other devices without intervening devices or may be directly coupled to the other devices with intervening devices.
All terms (including technical or scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs unless specifically defined otherwise. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate.
FIG. 1 is a schematic block diagram of some embodiments of an inverter cooling system according to the present disclosure. Referring to FIG. 1, in some embodiments, an inverter cooling system includes: a compressor 10, a condenser 20 and at least two refrigeration circuits. The condenser 20 communicates with the discharge port of the compressor 10. Each refrigeration circuit has a throttling element and an evaporator in series. The evaporators of at least two refrigeration circuits, which are connected in parallel between the condenser 20 and the suction port of the compressor 10, are respectively configured to cool a plurality of modules within the inverter cabinet.
In fig. 1, the at least two refrigeration circuits include a first refrigeration circuit R1. The first refrigeration path R1 includes a first throttling element 31, a first evaporator 32, and an evaporating pressure regulator 33 connected in series in this order in a direction from the condenser 20 to a suction port of the compressor 10. The saturation temperature corresponding to the self-rated evaporating pressure of the first evaporator 32 is higher than the saturation temperature corresponding to the self-rated evaporating pressure of the evaporator of the other refrigerating circuit of the at least two refrigerating circuits, and the evaporating pressure regulator 33 is configured to maintain the working evaporating pressure of the first evaporator 32 within a preset pressure range.
The rated evaporating pressure here is an evaporating pressure suitable for the evaporator in the refrigeration circuit in normal steady operation. The rated evaporating pressure can be determined by the actual ambient temperature or the required evaporating pressure of the module corresponding to the evaporator. The modules can be respectively positioned in different frequency conversion cabinets. In some embodiments, multiple modules may also be located in the same inverter cabinet.
This embodiment is right respectively through the evaporimeter in two at least refrigeration ways a plurality of modules in the inverter cabinet cool off to adjust the work evaporating pressure of the evaporimeter in the refrigeration way that the evaporimeter saturation temperature is the highest through evaporating pressure regulator, in order to maintain stable refrigeration output, reduce temperature fluctuation improves corresponding module temperature control's in the inverter cabinet stability and accuracy nature.
In some embodiments, the first evaporator 32 comprises a cold plate evaporator, and the corresponding module of the cold plate evaporator comprises at least one of a rectifier module and an inverter module within the inverter cabinet. The cold plate evaporator adopts a mode that the plate-shaped evaporator is attached to the surface of the module. The working environment temperature of the cold plate evaporator is generally about 30-50 ℃, and the saturation temperature corresponding to the rated evaporation pressure of the cold plate evaporator is generally maintained at 20-30 ℃.
The evaporation pressure regulator is arranged at the downstream of the cold plate evaporator with higher working environment temperature in the refrigerant circulation direction, so that the working evaporation pressure of the cold plate evaporator can be effectively maintained, and the working evaporation pressure of the cold plate evaporator is maintained at a corresponding saturation temperature of 20-30 ℃ in most of the normal operation time of the unit. When work evaporating pressure is too high or low, accessible evaporating pressure regulator with work evaporating pressure adjust to the settlement scope, maintain stable refrigeration output, reduce the temperature fluctuation, avoid the high or low temperature of cold plate evaporator to lead to rectifier module and contravariant module efficiency to reduce or even damage to ensure rectifier module and contravariant module full play and function.
Referring to fig. 1, in some embodiments, the at least two refrigeration circuits further include a second refrigeration circuit R2. The second refrigeration passage R2 includes a second throttling element 41, a second evaporator 42, and a first check valve 43 connected in series in this order in a direction from the condenser 20 to the suction port of the compressor 10. The saturation temperature corresponding to the rated evaporation pressure of the second evaporator 42 is lower than the saturation temperature corresponding to the rated evaporation pressure of the evaporator of the other refrigeration circuit of the at least two refrigeration circuits.
The operating evaporating pressure of the second evaporator 42 in the second refrigerant circuit R2 can be adjusted by adjusting the frequency of the compressor. The self-rated evaporating pressure of the second evaporator 42 is smaller than the self-rated evaporating pressure of the first evaporator 32, so that the first check valve 43 can prevent the second refrigerating circuit with lower working evaporating pressure from generating refrigerant backflow under the action of pressure difference when the evaporating pressure regulator 33 regulates the higher working evaporating pressure of the first evaporator 32, thereby avoiding the influence of the high-pressure refrigerating circuit (such as the first refrigerating circuit R1) and maintaining the lower working evaporating pressure of the second evaporator 43.
In some embodiments, the second evaporator 42 comprises a dehumidification evaporator, and the corresponding modules of the dehumidification evaporator comprise dehumidification modules in the inverter cabinet. The dehumidifying evaporator maintains a low working evaporating pressure to achieve a sufficient dehumidifying effect. The dehumidifying evaporator may take the form of a fan + radiating fins. The working environment temperature of the dehumidification evaporator is low, the rated evaporation pressure is low, and the corresponding saturation temperature is generally kept at 5-10 ℃.
Referring to fig. 1, in some embodiments, the at least two refrigeration circuits further include a third refrigeration circuit R3. The third refrigeration path R3 includes a third throttling element 51, a third evaporator 52, and a second check valve 53 connected in series in this order in a direction from the condenser 20 to a suction port of the compressor 10. The saturation temperature of the third evaporator 52 corresponding to the rated evaporation pressure thereof is lower than the saturation temperature of the first evaporator 32 corresponding to the rated evaporation pressure thereof and higher than the saturation temperature of the second evaporator 42 corresponding to the rated evaporation pressure thereof.
The operating evaporating pressure of the third evaporator 52 in the third refrigerant circuit R3 can also be adjusted by adjusting the frequency of the compressor. The third evaporator 52 has a lower self-rated evaporating pressure than the first evaporator 32, so that the second check valve 53 prevents the refrigerant from flowing backwards in the third cooling circuit with a lower working evaporating pressure under the action of the pressure difference when the evaporating pressure regulator 33 adjusts the higher working evaporating pressure of the first evaporator 32, thereby preventing the refrigerant from being influenced by the high-pressure cooling circuit (e.g., the first cooling circuit R1), and maintaining the lower working evaporating pressure of the third evaporator 53. Thus, the stability and the accuracy of temperature control of each module are improved.
In some embodiments, the third evaporator 52 comprises a reactive evaporator, and the corresponding modules of the reactive evaporator comprise reactive modules in the inverter cabinet. The reactance evaporator can adopt a fan plus a radiating fin form. The working environment temperature of the reactance evaporator is between the working environment temperature of the cold plate evaporator and the dehumidifying evaporator, and the saturation temperature corresponding to the rated evaporating pressure is generally maintained at 15-25 ℃.
In the above embodiments, the first throttling element 31 and the second throttling element 41 may each comprise an electronic expansion valve. The opening degree of the electronic expansion valve included in the first throttle element 31 is adjustable according to the variation of the load, and the fluctuation of the working evaporation pressure caused by the adjustment of the opening degree is suppressed by the evaporation pressure regulator 33. The opening degree of the electronic expansion valve included in the second throttling element 41 can be adjusted according to the variation of the load, and the fluctuation of the working evaporation pressure caused by the adjustment of the opening degree can be suppressed by the adjustment of the frequency of the compressor.
It is contemplated that in some embodiments, the reactive evaporator may not need to be precisely controlled in operating evaporating pressure, and that the third throttling element 51 may comprise a capillary tube. This is beneficial to reducing the system cost and the control difficulty.
In fig. 1, each of the at least two refrigeration circuits further includes a first shutoff valve and a second shutoff valve. The evaporator in the refrigeration circuit may be connected in series between the first and second shutoff valves. For example, the first evaporator 32 is connected in series between the first cutoff valve 34 and the second cutoff valve 35, the second evaporator 42 is connected in series between the first cutoff valve 44 and the second cutoff valve 45, and the third evaporator 52 is connected in series between the first cutoff valve 54 and the second cutoff valve 55. The first stop valve and the second stop valve can control the on-off and flow of the refrigeration path where the first stop valve and the second stop valve are located so as to meet the working requirements of corresponding modules.
Valve 71, valve 72 and gas-liquid separator 60 may also be included in fig. 1. The valve 71 may be positioned between the at least two refrigeration paths and the condenser 20, the valve 72 and the gas-liquid separator 60 may be disposed in series between the at least two refrigeration paths and the suction port of the compressor 10, and the gas-liquid separator 60 is positioned between the valve 72 and the compressor 10. In fig. 1, the inside and the outside of the frequency conversion cabinet are divided by dotted lines.
FIG. 2 is a schematic flow diagram of some embodiments of a control method of an inverter cooling system according to the present disclosure. Based on the foregoing embodiments of the inverter cooling system, the present disclosure also provides a control method of the inverter cooling system, which includes steps 100-400. In step 100, the temperature of each module in the frequency conversion cabinet is detected. In this step, the temperature may be detected by a temperature sensor.
In step 200, a first target temperature difference Δ T1 is calculated, where the first target temperature difference Δ T1 is the temperature T1 of the module corresponding to the first evaporator 32 minus a preset first temperature threshold TTH1The result of (1), i.e., Δ T1 ═ T1-TTH1. The preset first temperature threshold value TTH1Is the saturation temperature corresponding to the self-rated evaporating pressure of the first evaporator 32.
In step 300, a second target temperature difference Δ T2 is calculated, where the second target temperature difference Δ T2 is the temperature T2 of the module corresponding to the second evaporator 42 minus a preset second temperature threshold TTH2The result of (1), i.e., Δ T2 ═ T2-TTH2. The preset second temperature threshold value TTH2The saturation temperature is corresponding to the rated evaporation pressure of the second evaporator 42.
In step 400, the compressor 10 and the evaporation pressure regulator 33 are controlled according to the value ranges corresponding to the first target temperature difference Δ t1 and the second target temperature difference Δ t2, respectively.
In some embodiments, step 400 may include:
at the first target temperature difference Δ t1The second target temperature difference Deltat 2 is greater than the tolerance positive value TOLPAt this time, the compressor 10 is operated at full frequency, and the evaporation pressure regulator 33 is opened to reduce the working evaporation pressure of the first evaporator 32;
when the first target temperature difference delta t1 is larger than the tolerance positive value TOLPThe second target temperature difference Δ t2 is greater than or equal to 0 ℃ and less than or equal to the tolerance positive value TOLPAt this time, the compressor 10 is operated at full frequency, and the evaporation pressure regulator 33 is opened to reduce the working evaporation pressure of the first evaporator 32;
when the first target temperature difference delta t1 is larger than the tolerance positive value TOLPWhen the second target temperature difference Δ t2 is less than 0 ℃, the compressor 10 is operated at full frequency, and the evaporation pressure regulator 33 is opened to lower the operating evaporation pressure of the first evaporator 32.
Greater than TOL at Δ t1PIn this case, the requirement of the lowest evaporating pressure in the plurality of refrigeration paths can be satisfied by operating the compressor at full frequency, and the evaporating pressure of the refrigeration path having the highest evaporating pressure can be adjusted by opening the evaporating pressure regulator 33 through the evaporating pressure regulator 33.
In some embodiments, step 400 may include:
when the first target temperature difference delta t1 is smaller than the negative tolerance TOLNAnd the second target temperature difference Δ t2 is greater than the tolerance positive value TOLPAt that time, the compressor 10 is operated at full frequency, and the evaporating pressure regulator 33 is closed and set to be non-triggerable;
when the first target temperature difference delta t1 is smaller than the negative tolerance TOLNAnd the second target temperature difference Δ t2 is less than 0 ℃, operating the compressor 10 at the lowest frequency and the evaporating pressure regulator 33 closed and set to be triggerable;
when the first target temperature difference delta t1 is smaller than the negative tolerance TOLNAnd the second target temperature difference Deltat 2 is greater than or equal to 0 ℃ and less than or equal to the tolerance positive value TOLPWhile, the compressor 10 is operated at a frequency less than the full frequency and greater than the lowest frequency, and the steam is evaporatedThe pressure regulator 33 is closed and set to be non-triggerable.
Less than TOL at Δ t1NWhen the evaporation pressure regulator 33 is closed and is not triggerable, the vapor pressure does not need to be adjusted by the evaporation pressure regulator 33. According to Δ t2 and 0 ℃ and TOLPTo adjust the operating frequency of the compressor.
In some embodiments, step 400 may include:
when the first target temperature difference delta t1 is greater than or equal to a negative tolerance TOLNAnd less than or equal to the positive tolerance TOLPThe second target temperature difference Δ t2 is greater than the tolerance positive value TOLPAt the same time, the compressor 10 is operated at full frequency, the evaporation pressure regulator 33 is closed, and the opening trigger value P of the evaporation pressure regulator 33 is settrThe corresponding saturation temperature is set as a preset first temperature threshold TTH1The result of the temperature variable x is subtracted.
Accordingly, the control method further comprises the following step or at least one of these steps.
And detecting whether a first condition that the first target temperature difference delta t1 is continuously increased within a preset first time length is met, if the first condition is met, increasing the value of the temperature variable x, and if not, maintaining the value of the temperature variable x. For the case where Δ t1 continues to rise, P can be decreased by increasing the value of xtrSo that the evaporating pressure regulator 33 is actuated earlier to decrease at 1.
Detecting whether the first target temperature difference delta t1 is met and continuously exceeds the tolerance intermediate value TOL within a preset second time periodMSecond condition of (2), said tolerance intermediate value TOLMGreater than 0 ℃ and less than the positive tolerance value TOLPIf the second condition is met, increasing the value of the temperature variable x, otherwise, maintaining the value of the temperature variable x. For the case that the delta t1 does not meet the requirement for a long time, the value of x can be increased to reduce PtrSo that the evaporating pressure regulator 33 is actuated earlier to decrease at 1.
In some embodiments, step 400 may include:
at the first stageA target temperature difference Δ t1 greater than or equal to the negative tolerance TOLNAnd less than or equal to the positive tolerance TOLPThe second target temperature difference Δ t2 is greater than or equal to 0 ℃ and less than or equal to the tolerance positive value TOLPWhen the compressor 10 is operated at a frequency less than the full frequency and greater than the lowest frequency, and the evaporation pressure regulator 33 is closed, and the opening trigger value P of the evaporation pressure regulator 33 is settrCorresponding preset first temperature threshold TTH1The result of the temperature variable x is subtracted.
Accordingly, the control method further comprises the following step or at least one of these steps.
Detecting whether a first condition that the first target temperature difference delta t1 continuously increases within a preset first time (for example, 3-10 seconds, and may be specifically 5 seconds) is met, if the first condition is met, increasing the value of the temperature variable x, otherwise, maintaining the value of the temperature variable x. For the case where Δ t1 continues to rise, P can be decreased by increasing the value of xtrSo that the evaporating pressure regulator 33 is actuated earlier to decrease at 1.
Detecting whether the first target temperature difference delta t1 is met and continuously exceeds the tolerance intermediate value TOL within a preset second time length (for example, 20-40 seconds, and may be specifically 30 seconds)MSecond condition of (2), said tolerance intermediate value TOLMGreater than 0 ℃ and less than the positive tolerance value TOLPIf the second condition is met, increasing the value of the temperature variable x, otherwise, maintaining the value of the temperature variable x. For the case that the delta t1 does not meet the requirement for a long time, the value of x can be increased to reduce PtrSo that the evaporating pressure regulator 33 is actuated earlier to decrease at 1.
And detecting whether a third condition that the second target temperature difference delta t2 continuously increases within a preset third time (for example, 3-10 seconds, and may be specifically 5 seconds) is met, and if the third condition is met, increasing the operating frequency of the compressor 10. In the event that compressor 10 is not operating at full or lowest frequency, for continued increases in Δ t2, the evaporating pressure may be reduced by increasing the operating frequency of compressor 10, thereby reducing the temperature of the second evaporator.
In some embodiments, step 400 may include:
when the first target temperature difference delta t1 is greater than or equal to a negative tolerance TOLNAnd less than or equal to the positive tolerance TOLPWhen the second target temperature difference Δ t2 is less than 0 ℃, the compressor 10 is operated at a frequency less than the full frequency and greater than the lowest frequency, the evaporating pressure regulator 33 is closed, and the opening trigger value P of the evaporating pressure regulator 33 is settrCorresponding preset first temperature threshold TTH1The result of the temperature variable x is subtracted.
Accordingly, the control method further comprises the following step or at least one of these steps.
Detecting whether a first condition that the first target temperature difference delta t1 continuously increases within a preset first time (for example, 3-10 seconds, and may be specifically 5 seconds) is met, if the first condition is met, increasing the value of the temperature variable x, otherwise, maintaining the value of the temperature variable x. For the case where Δ t1 continues to rise, P can be decreased by increasing the value of xtrSo that the evaporating pressure regulator 33 is actuated earlier to decrease at 1.
Detecting whether the first target temperature difference delta t1 is met and continuously exceeds the tolerance intermediate value TOL within a preset second time length (for example, 20-40 seconds, and may be specifically 30 seconds)MSecond condition of (2), said tolerance intermediate value TOLMGreater than 0 ℃ and less than the positive tolerance value TOLPIf the second condition is met, increasing the value of the temperature variable x, otherwise, maintaining the value of the temperature variable x. For the case that the delta t1 does not meet the requirement for a long time, the value of x can be increased to reduce PtrSo that the evaporating pressure regulator 33 is actuated earlier to decrease at 1.
Detecting whether a fourth condition that the second target temperature difference Δ t2 is continuously less than 0 ℃ for a preset fourth time (for example, 20 to 40 seconds, and may be specifically 30 seconds) is met, and if the fourth condition is met, reducing the operating frequency of the compressor 10. When the compressor 10 is not operated at the full frequency or the lowest frequency, if Δ t2 is less than 0 ℃ for a long time, frosting of the second evaporator may be caused, and thus the temperature of the second evaporator is increased by increasing the evaporation pressure by lowering the operation frequency of the compressor 10.
In the above embodiments, the TOL can be set according to actual conditionsPNegative tolerance value TOLNA first temperature threshold TTH1A second temperature threshold TTH2TOL, the tolerance intermediate valueMEqual parameters, e.g. setting of positive tolerance TOLPAt 5 ℃ and a negative tolerance TOLNIs-5 deg.C, a first temperature threshold TTH1At 5 ℃ and a second temperature threshold TTH2At 5 ℃ and a tolerance intermediate value TOLMIs 2 ℃. In some embodiments, the temperature variable x can be made to have a value greater than 0 ℃ and less than or equal to 15 ℃.
Thus, various embodiments of the present disclosure have been described in detail. Some details that are well known in the art have not been described in order to avoid obscuring the concepts of the present disclosure. It will be fully apparent to those skilled in the art from the foregoing description how to practice the presently disclosed embodiments.
Although some specific embodiments of the present disclosure have been described in detail by way of example, it should be understood by those skilled in the art that the foregoing examples are for purposes of illustration only and are not intended to limit the scope of the present disclosure. It will be understood by those skilled in the art that various changes may be made in the above embodiments or equivalents may be substituted for elements thereof without departing from the scope and spirit of the present disclosure. The scope of the present disclosure is defined by the appended claims.

Claims (20)

1. An inverter cooling system, comprising: the air conditioner comprises a compressor (10), a condenser (20) communicated with an air outlet of the compressor (10), and at least two refrigerating paths, wherein each refrigerating path is provided with a throttling element and an evaporator which are connected in series, the evaporators in the at least two refrigerating paths are respectively configured to cool a plurality of modules in an inverter cabinet, and the at least two refrigerating paths are connected between the condenser (20) and an air inlet of the compressor (10) in a parallel mode.
2. Frequency converter cooling system according to claim 1, characterized in that said at least two refrigeration circuits comprise a first refrigeration circuit (R1), said first refrigeration circuit (R1) comprising, in succession, in a direction from said condenser (20) to the suction of said compressor (10), a first throttling element (31), a first evaporator (32) and an evaporation pressure regulator (33), the first evaporator (32) having a saturation temperature corresponding to its own nominal evaporation pressure higher than the saturation temperature corresponding to its own nominal evaporation pressure of the evaporators of the other of said at least two refrigeration circuits, said evaporation pressure regulator (33) being configured to maintain the operating evaporation pressure of said first evaporator (32) within a preset pressure range.
3. Inverter cooling system according to claim 2, wherein the first evaporator (32) comprises a cold plate evaporator, the corresponding module of which comprises at least one of a rectifier module and an inverter module within the inverter cabinet.
4. Frequency converter cooling system according to claim 3, characterized in that said at least two refrigeration circuits further comprise a second refrigeration circuit (R2), said second refrigeration circuit (R2) comprising, in series in succession in the direction from said condenser (20) to the suction of said compressor (10), a second throttling element (41), a second evaporator (42) and a first non-return valve (43), said second evaporator (42) having a saturation temperature corresponding to its own nominal evaporation pressure lower than the saturation temperature corresponding to its own nominal evaporation pressure of the evaporators of the other of said at least two refrigeration circuits.
5. Inverter cooling system according to claim 5, characterized in that the second evaporator (42) comprises a dehumidifying evaporator, the corresponding module of which comprises a dehumidifying module in the inverter cabinet.
6. Inverter cooling system according to claim 5, characterised in that said at least two refrigeration circuits further comprise a third refrigeration circuit (R3), said third refrigeration circuit (R3) comprising, in series in succession, in the direction from the condenser (20) to the suction of the compressor (10), a third throttling element (51), a third evaporator (52) and a second non-return valve (53), the third evaporator (52) having a saturation temperature corresponding to its own rated evaporation pressure lower than the saturation temperature corresponding to its own rated evaporation pressure of the first evaporator (32) and higher than the saturation temperature corresponding to its own rated evaporation pressure of the second evaporator (42).
7. Frequency converter cooling system according to claim 6, wherein the third evaporator (52) comprises a reactive evaporator, the corresponding modules of which comprise reactive modules within the frequency converter cabinet.
8. Frequency converter cooling system according to claim 7, wherein the first throttling element (31) and the second throttling element (41) each comprise an electronic expansion valve and the third throttling element (51) comprises a capillary tube.
9. Frequency converter cooling system according to any one of claims 1 to 8, wherein each of the at least two refrigeration circuits further comprises a first shut-off valve (34, 44, 54) and a second shut-off valve (35, 45, 55), the evaporators of the refrigeration circuits being connected in series between the first shut-off valve (34, 44, 54) and the second shut-off valve (35, 45, 55).
10. An air conditioning assembly, comprising:
a frequency converter cooling system as claimed in any one of claims 1 to 9.
11. A control method of the inverter cooling system according to any one of claims 4 to 8, comprising:
detecting the temperature of each module in the frequency conversion cabinet;
calculating a first target temperature difference (Δ T1), the first target temperature difference (Δ T1) being the temperature of the module to which the first evaporator (32) corresponds minus a preset first temperature threshold (T)TH1) As a result of the preset first temperatureThreshold value (T)TH1) A saturation temperature corresponding to the self rated evaporation pressure of the first evaporator (32);
calculating a second target temperature difference (Δ T2), the second target temperature difference (Δ T2) being the temperature of the module corresponding to the second evaporator (42) minus a preset second temperature threshold (T)TH2) As a result of said preset second temperature threshold (T)TH2) A saturation temperature corresponding to the rated self-evaporation pressure of the second evaporator (42);
and controlling the compressor (10) and the evaporation pressure regulator (33) according to the value ranges corresponding to the first target temperature difference (delta t1) and the second target temperature difference (delta t 2).
12. The control method according to claim 11, characterized in that the step of controlling the compressor (10) and the evaporation pressure regulator (33) according to the respective ranges of values of the first target temperature difference (Δ t1) and the second target temperature difference (Δ t2) comprises:
when the first target temperature difference (delta t1) and the second target temperature difference (delta t2) are both greater than a positive tolerance value (TOL)P) When the compressor (10) is operated at full frequency, and the evaporation pressure regulator (33) is opened to reduce the working evaporation pressure of the first evaporator (32);
when the first target temperature difference (Δ t1) is greater than the tolerance positive value (TOL)P) The second target temperature difference (Δ t2) is equal to or greater than 0 ℃ and equal to or less than the positive tolerance value (TOL)P) When the compressor (10) is operated at full frequency, and the evaporation pressure regulator (33) is opened to reduce the working evaporation pressure of the first evaporator (32);
when the first target temperature difference (Δ t1) is greater than the tolerance positive value (TOL)P) -operating the compressor (10) at full frequency and opening the evaporation pressure regulator (33) to reduce the working evaporation pressure of the first evaporator (32) when the second target temperature difference (Δ t2) is less than 0 ℃.
13. The control method according to claim 11, characterized in that the step of controlling the compressor (10) and the evaporation pressure regulator (33) according to the respective ranges of values of the first target temperature difference (Δ t1) and the second target temperature difference (Δ t2) comprises:
when the first target temperature difference (delta t1) is less than the negative tolerance value (TOL)N) And the second target temperature difference (Δ t2) is greater than the positive tolerance value (TOL)P) -at full frequency operating the compressor (10) and closing the evaporation pressure regulator (33) and setting it to be non-triggerable;
when the first target temperature difference (delta t1) is less than the negative tolerance value (TOL)N) And the second target temperature difference (Δ t2) is less than 0 ℃, operating the compressor (10) at the lowest frequency and the evaporating pressure regulator (33) closed and set to be non-triggerable;
when the first target temperature difference (delta t1) is less than the negative tolerance value (TOL)N) And the second target temperature difference (Δ t2) is equal to or greater than 0 ℃ and equal to or less than the positive tolerance value (TOL)P) -operating the compressor (10) at a frequency less than the full frequency and greater than the lowest frequency, and-closing the evaporation pressure regulator (33) and setting it to be non-triggerable.
14. The control method according to claim 11, characterized in that the step of controlling the compressor (10) and the evaporation pressure regulator (33) according to the respective ranges of values of the first target temperature difference (Δ t1) and the second target temperature difference (Δ t2) comprises:
when the first target temperature difference (delta t1) is greater than or equal to a negative tolerance value (TOL)N) And is less than or equal to the positive tolerance value (TOL)P) Said second target temperature difference (Δ t2) being greater than said tolerance positive value (TOL)P) When the compressor (10) is operated at full frequency, and the evaporation pressure regulator (33) is closed, and the opening trigger value (P) of the evaporation pressure regulator (33) is settr) The corresponding saturation temperature is set to a preset first temperature threshold (T)TH1) The result of the temperature variable (x) is subtracted.
15. The control method according to claim 14, characterized by further comprising at least one of the following steps:
detecting whether a first condition that the first target temperature difference (delta t1) is continuously increased within a preset first time length is met, if the first condition is met, increasing the value of the temperature variable (x), otherwise, maintaining the value of the temperature variable (x);
detecting whether the first target temperature difference (delta t1) is met and continuously exceeds the tolerance intermediate value (TOL) within a preset second time periodM) The intermediate tolerance value (TOL)M) Greater than 0 ℃ and less than the positive tolerance value (TOL)P) If the second condition is met, increasing the value of the temperature variable (x), otherwise, maintaining the value of the temperature variable (x).
16. The control method according to claim 11, characterized in that the step of controlling the compressor (10) and the evaporation pressure regulator (33) according to the respective ranges of values of the first target temperature difference (Δ t1) and the second target temperature difference (Δ t2) comprises:
when the first target temperature difference (delta t1) is greater than or equal to a negative tolerance value (TOL)N) And is less than or equal to the positive tolerance value (TOL)P) The second target temperature difference (Δ t2) is equal to or greater than 0 ℃ and equal to or less than the positive tolerance value (TOL)P) When the pressure is low, the compressor (10) is operated at a frequency less than the full frequency and greater than the lowest frequency, the evaporation pressure regulator (33) is closed, and the opening trigger value (P) of the evaporation pressure regulator (33) is settr) The corresponding saturation temperature is set to a preset first temperature threshold (T)TH1) The result of the temperature variable (x) is subtracted.
17. The control method according to claim 16, characterized by further comprising at least one of the following steps:
detecting whether a first condition that the first target temperature difference (delta t1) is continuously increased within a preset first time length is met, if the first condition is met, increasing the value of the temperature variable (x), otherwise, maintaining the value of the temperature variable (x);
detecting whether the first target temperature difference (delta t1) is met and continuously exceeds the tolerance intermediate value (TOL) within a preset second time periodM) The intermediate tolerance value (TOL)M) Greater than 0 ℃ and less than the positive tolerance value (TOL)P) If the second condition is met, increasing the value of the temperature variable (x), otherwise, maintaining the value of the temperature variable (x);
detecting whether a third condition that the second target temperature difference (Δ t2) is continuously increased for a preset third time period is satisfied, the satisfaction of the third condition increasing the operating frequency of the compressor (10).
18. The control method according to claim 11, characterized in that the step of controlling the compressor (10) and the evaporation pressure regulator (33) according to the respective ranges of values of the first target temperature difference (Δ t1) and the second target temperature difference (Δ t2) comprises:
when the first target temperature difference (delta t1) is greater than or equal to a negative tolerance value (TOL)N) And is less than or equal to the positive tolerance value (TOL)P) -when the second target temperature difference (Δ t2) is less than 0 ℃, operating the compressor (10) at a frequency less than the full frequency and greater than the lowest frequency, and closing the evaporation pressure regulator (33) and setting an opening trigger value (P) of the evaporation pressure regulator (33)tr) The corresponding saturation temperature is set to a preset first temperature threshold (T)TH1) The result of the temperature variable (x) is subtracted.
19. The control method according to claim 18, further comprising at least one of:
detecting whether a first condition that the first target temperature difference (delta t1) is continuously increased within a preset first time length is met, if the first condition is met, increasing the value of the temperature variable (x), otherwise, maintaining the value of the temperature variable (x);
detecting whether the first target temperature difference (delta t1) is met and continuously exceeds the tolerance intermediate value (TOL) within a preset second time periodM) The intermediate tolerance value (TOL)M) Greater than 0 ℃ and less than the positive tolerance value (TOL)P) If the second condition is met, increasing the value of the temperature variable (x), otherwise, maintaining the value of the temperature variable (x);
detecting whether a fourth condition that the second target temperature difference (Δ t2) is continuously less than 0 ℃ for a preset fourth time period is met, the fourth condition being met, and reducing the operating frequency of the compressor (10).
20. The control method according to any one of claims 14 to 19, wherein the temperature variable (x) has a value greater than 0 ℃ and less than or equal to 15 ℃.
CN202011530013.1A 2020-12-22 2020-12-22 Air conditioning unit, frequency converter cooling system and control method thereof Pending CN112556227A (en)

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