CN111520873B - Air conditioning system and condensation prevention control method of variable-frequency radiating pipe of air conditioning system - Google Patents
Air conditioning system and condensation prevention control method of variable-frequency radiating pipe of air conditioning system Download PDFInfo
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- CN111520873B CN111520873B CN202010449736.2A CN202010449736A CN111520873B CN 111520873 B CN111520873 B CN 111520873B CN 202010449736 A CN202010449736 A CN 202010449736A CN 111520873 B CN111520873 B CN 111520873B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/41—Defrosting; Preventing freezing
- F24F11/42—Defrosting; Preventing freezing of outdoor units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/64—Electronic processing using pre-stored data
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/88—Electrical aspects, e.g. circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
- F24F2110/12—Temperature of the outside air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/20—Humidity
- F24F2110/22—Humidity of the outside air
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- Air Conditioning Control Device (AREA)
Abstract
The invention discloses an air conditioning system, which is used for calculating and determining the corresponding air dew point temperature X based on the real-time acquired environment temperature T4 and environment humidity T5; acquiring a copper pipe temperature T6 and a copper pipe temperature T7, and calculating and comparing a lowest value A between the copper pipe temperature T6 and the copper pipe temperature T7; and adjusting the on/off state of the air conditioning system, the on/off state of the first electromagnetic valve, the opening degree of the indoor electromagnetic valve, the opening degree of the main electronic expansion valve and the opening degree of the auxiliary electronic expansion valve according to the difference between the lowest value A and the air dew point temperature X calculated in the step S1 and by combining the operation mode of the air conditioning system. The effect of utilizing the refrigerant to cool the frequency conversion module in a heat dissipation manner is guaranteed, the safety risk of not condensing dew in the cooling process is also guaranteed, the air conditioning system can obtain better supercooling degree, and the influence of heat dissipation and cooling on the heating or refrigerating work of the air conditioning system is reduced.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to an air conditioning system and an anti-condensation control method for a variable-frequency radiating pipe of the air conditioning system.
Background
In the existing inverter air conditioning system, the current of an inverter (inverter module) for driving an inverter compressor in the running process of the compressor can generate a large amount of heat, and if the heat cannot be dissipated timely, the temperature of the inverter can be very high, so that the inverter is burnt.
It is a common practice to mount the inverter on an aluminum plate, which may have fins, and to form air flow around the aluminum plate by the operation of the outdoor unit fan, and to dissipate heat due to the radiation heat transfer property of the aluminum plate itself, thereby maintaining the compressor inverter to operate at a reliable temperature.
With the development of industrial technologies, the capacity of the inverter compressor is larger and larger, and the inverter compressor is developed from 5 in the early stage to 20 in the present stage, and the larger capacity of the compressor means that the power of a driving module of the inverter compressor is larger and larger, so that the heat dissipation of the high-power inverter cannot be met by the heat dissipation of an air-cooled aluminum plate in the early stage.
The method for radiating the frequency converter by using the refrigerant of the air conditioning system adopted in the air conditioning industry at present is characterized in that a copper pipe is implanted into an aluminum plate, and the refrigerant in the system is introduced, and the temperature of the introduced refrigerant is controlled to reach a reasonable state, so that the heat of the frequency converter of the frequency conversion compressor can be radiated.
However, there is a problem that if the temperature of the refrigerant introduced into the copper pipe in the refrigerant heat sink is too low, when the temperature of the refrigerant is lower than the dew point temperature of the air around the refrigerant heat sink, the air will be condensed into condensed water on the surface of the refrigerant heat sink (the dew point temperature of the air is determined by the temperature and the relative humidity of the air, and the dew point temperatures under different temperatures and humidities are different, for example, when the temperature of the air is 27 ℃ and the relative humidity is 80%, the dew point temperature is 23 ℃, that is, the dew point temperature is lower than 23 ℃, that is, the dew point temperature is lower than 23 ℃, if the dew point water is condensed on the refrigerant heat sink, the serious accidents such as burning of the components in the electrical control box, fire, and the.
In an air conditioning system, the lower the supercooling degree of a refrigerant in a liquid pipe is, the better the capacity and energy efficiency of the system are generally, and the lower the supercooling degree of the system is generally required to be.
Therefore, how to control the refrigerant temperature of the refrigerant cooling fins well is a very big subject for the design of the air conditioning system, not only ensuring the best supercooling degree of the system, but also ensuring that the refrigerant cooling fins do not condense and condense water and can keep the effective heat dissipation of the frequency converter.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide an indoor unit refrigerant distribution control method of a multi-split system, which can solve the problem of refrigerant distribution among different indoor units.
In order to achieve the purpose, the air conditioning system provided by the invention comprises a compressor, a four-way valve, a multi-connected indoor unit, an outdoor heat exchanger, a variable frequency radiating pipe for cooling a variable frequency module, a throttling assembly and a subcooler; four interfaces of the four-way valve are respectively connected with an exhaust port of the compressor, a return air port of the compressor, one end of the outdoor heat exchanger and one end of the multi-connected indoor unit; the two ends of the throttling assembly are respectively connected with the other end of the outdoor heat exchanger and one end of the variable-frequency radiating pipe, wherein the throttling assembly comprises a main electronic expansion valve, a first electromagnetic valve and a one-way valve, and the first electromagnetic valve is connected with the one-way valve in series and then connected with the main electronic expansion valve in parallel; two ends of a main flow path of the subcooler are respectively connected with the other end of the variable-frequency radiating pipe and the other end of the multi-connected indoor unit, one end of a subcooling branch of the subcooler is connected between the main flow path and the multi-connected indoor unit in a bypass mode, and the other end of the subcooling branch is connected with a gas return port of the compressor; an auxiliary electronic expansion valve is arranged at the inlet of the supercooling branch; the multi-connected indoor unit consists of a plurality of indoor units connected in parallel, and each indoor unit is provided with an indoor electromagnetic valve; the outdoor environment temperature detection device further comprises an environment temperature detection unit, a humidity detection unit, a first temperature detection unit and a second temperature detection unit, wherein the environment temperature detection unit and the humidity detection unit are respectively used for acquiring the environment temperature T4 and the environment humidity T5 of the outdoor environment; first temperature detecting element and second temperature detecting element establish respectively at the both ends of frequency conversion cooling tube and are used for acquireing the copper pipe temperature T6 and the copper pipe temperature T7 at frequency conversion cooling tube both ends.
An anti-condensation control method for a variable frequency heat dissipation pipe in an air conditioning system comprises the following steps:
s1, calculating and determining a corresponding air dew point temperature X based on the environment temperature T4 and the environment humidity T5 which are obtained in real time;
s2, obtaining the temperature T6 of the copper pipe and the temperature T7 of the copper pipe, and calculating and comparing the lowest value A between the temperature T6 of the copper pipe and the temperature T7 of the copper pipe;
and S3, correspondingly adjusting the on/off state of the air conditioning system, the on/off state of the first electromagnetic valve, the opening degree of the indoor electromagnetic valve, the opening degree of the main electronic expansion valve and the opening degree of the auxiliary electronic expansion valve according to the difference between the lowest value A and the air dew point temperature X calculated in the step S1 and by combining the operation mode of the air conditioning system.
Further, the air conditioning system is in a heating mode, four-stage heating executing actions are set according to the difference condition of the lowest value A and the air dew point temperature X, wherein when A-X is less than or equal to delta T1 ℃, the first-stage heating executing action is started; when the temperature is more than delta T1 and less than or equal to delta T2 ℃, starting a second-stage heating execution action; when the temperature is more than delta T2 and less than or equal to delta T3 ℃, starting a third-level heating execution action; and when A-X is equal to or more than T3 ℃, enabling the fourth-level heating execution action.
Further, the first level heating performs the actions of: the air conditioning system is immediately stopped until the air conditioning system is stopped for a rated time and then restarted for operation; the second level heating execution action: immediately closing the auxiliary electronic expansion valve, and increasing the opening degree of an indoor expansion valve of the indoor unit in an opening state; and the third-stage heating execution action: immediately closing the auxiliary electronic expansion valve, and performing the fourth-stage heating execution action: and immediately adjusting the auxiliary electronic expansion valve to a rated opening degree.
Further, during any one of the second heating execution operation, the third heating execution operation, and the fourth heating execution operation, if the difference between the minimum value a and the air dew point temperature X is a rated difference value maintaining a rated length, the operation state is switched back to the operation state before the execution operation.
Further, the air conditioning system is in a refrigeration mode, five-stage refrigeration executing actions are set according to the difference condition of the lowest value A and the air dew point temperature X, wherein when A-X is less than or equal to delta T1' ° C, the first-stage refrigeration executing action is started; enabling a second stage refrigeration performing action when Δ T1 '< A-X ≦ Δ T2' ° C; when the delta T2 '< A-X ≦ delta T3' ° C, enabling third-stage refrigeration to perform actions; enabling fourth stage refrigeration to perform actions when delta T3 '< A-X ≦ delta T4' ° C; and when A-X is equal to or more than delta T4' ° C, starting the fifth-stage refrigeration to execute the action.
Further, the first stage refrigeration performs the acts of: the air conditioning system is immediately stopped until the air conditioning system is stopped for a rated time and then restarted for operation; the second stage refrigeration performs the actions of: immediately closing the auxiliary electronic expansion valve, opening the main electronic expansion valve to the maximum opening degree and opening the first electromagnetic valve until the difference value between the lowest value A and the air dew point temperature X is a rated difference value and maintaining the rated time length, and then recovering the normal operation state; the third stage refrigeration performs the actions of: immediately closing the auxiliary electronic expansion valve, and opening the main electronic expansion valve to the maximum opening degree; the fourth stage refrigeration performing action: immediately closing the auxiliary electronic expansion valve; the fifth stage refrigeration performs the actions of: and immediately adjusting the auxiliary electronic expansion valve to a rated opening degree.
Further, during any one of the second-stage refrigeration executing operation, the third-stage refrigeration executing operation, the fourth-stage refrigeration executing operation, and the fifth-stage refrigeration executing operation, if the difference between the minimum value a and the air dew point temperature X is a rated difference and remains a rated time, the operation state is switched back to the operation state before the execution operation.
Further, in the second-stage heating execution action, after the opening degree of the indoor expansion valve of the indoor unit is adjusted and increased for the first time and the indoor unit is continuously operated for 1 minute, the difference condition between the real-time minimum value A and the air dew point temperature X is judged, wherein if the minimum value A is smaller than the air dew point temperature X, the opening degree of the indoor expansion valve of the indoor unit is increased again and real-time judgment is carried out again, and the second-stage heating execution action is repeated circularly until the minimum value A is larger than the air dew point temperature X.
Further, when the expansion valve of the indoor unit after being adjusted for many times reaches the maximum opening, the lowest value A is still judged to be less than the air dew point temperature X in real time, and then abnormity is prompted.
The invention adopts the scheme, and has the beneficial effects that: the effect of utilizing the refrigerant to cool the frequency conversion module in a heat dissipation manner is guaranteed, the safety risk of not condensing dew in the cooling process is also guaranteed, the air conditioning system can obtain better supercooling degree, and the influence of heat dissipation and cooling on the heating or refrigerating work of the air conditioning system is reduced.
Drawings
Fig. 1 is a schematic diagram of the composition of the air conditioning system of the present invention.
Fig. 2 is a flowchart of an anti-condensation control method of the present invention.
The system comprises a compressor 1, a four-way valve 2, a 3-multi-connected indoor unit, an indoor unit 31, an indoor unit 32, an indoor electromagnetic valve 4, an outdoor heat exchanger 41, an ambient temperature detection unit 42, a humidity detection unit 5, a variable-frequency radiating pipe 51, a first temperature detection unit 52, a second temperature detection unit 52, a throttling assembly 6, a main electronic expansion valve 61, a first electromagnetic valve 62, a one-way valve 63, a subcooler 7 and an auxiliary electronic expansion valve 71.
Detailed Description
To facilitate an understanding of the invention, the invention is described more fully below with reference to the accompanying drawings. Preferred embodiments of the present invention are shown in the drawings. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. These embodiments are provided so that this disclosure will be thorough and complete.
Referring to the attached drawing 1, the air conditioning system comprises a compressor 1, a four-way valve 2, a multi-connected indoor unit 3, an outdoor heat exchanger 4, a variable-frequency radiating pipe 5, a throttling assembly 6 and a subcooler 7, wherein the four-way valve 2 comprises four interfaces of e, f, g and h, the interface e of the four-way valve 2 is connected with an exhaust port of the compressor 1 through an oil separator, the interface f is connected with one end of the multi-connected indoor unit 3, the interface g is connected with one end of the outdoor heat exchanger 4, and the interface h is connected with a return air port of the compressor 1 through a gas-liquid. Two ends of the throttling assembly 6 are respectively connected with the other end of the outdoor heat exchanger 4 and one end of the variable-frequency radiating pipe 5, wherein the throttling assembly 6 comprises a main electronic expansion valve 61, a first electromagnetic valve 62 and a one-way valve 63, the first electromagnetic valve 62 is connected with the one-way valve 63 in series and then connected with the main electronic expansion valve 61 in parallel, namely, two ends after being connected in parallel are used as two ends of the throttling assembly 6, and two ends are respectively connected with the other end of the outdoor heat exchanger 4 and one end of the variable-frequency radiating pipe 5. The subcooler 7 comprises a main flow path and a subcooling branch, wherein two ends of the main flow path of the subcooler 7 are respectively connected with the other end of the variable-frequency radiating pipe 5 and the other end of the multi-connected indoor unit 3, one end of the subcooling branch of the subcooler 7 is connected between the main flow path and the multi-connected indoor unit 3 in a bypassing manner, the other end of the subcooling branch is connected with a return air port of the compressor 1, and an auxiliary electronic expansion valve 71 is arranged at an inlet of the process branch. The frequency conversion radiating pipe 5 is used for radiating and cooling a frequency conversion module of the air conditioning system. The multiple indoor unit group 3 is constituted by a plurality of indoor units 31 connected in parallel by branch pipes, and each indoor unit 31 is provided with an indoor electromagnetic valve 32.
In the present embodiment, the outdoor environment temperature detection device further includes an ambient temperature detection unit 41, a humidity detection unit 42, a first temperature detection unit 51, a second temperature detection unit 52, wherein the ambient temperature detection unit 41 and the humidity detection unit 42 are respectively used for acquiring an ambient temperature T4 and an ambient humidity T5 of the outdoor environment; the ambient temperature detecting unit 41 is disposed on the outdoor heat exchanger 4, and the humidity detecting unit 42 may be disposed near the ambient temperature detecting unit 41, or may be disposed outside the heat sink of the variable-frequency heat dissipating pipe 5. The first temperature detecting unit 51 and the second temperature detecting unit 52 are respectively arranged at two ends of the variable-frequency radiating pipe 5 and are used for acquiring the copper pipe temperature T6 and the copper pipe temperature T7 at two ends of the variable-frequency radiating pipe 5.
Based on the air conditioning system, further explanation is made by combining a specific anti-condensation control method of the variable-frequency radiating pipe 5.
Referring to fig. 2, in the present embodiment, the method for controlling condensation prevention of the variable frequency radiating pipe 5 of the air conditioning system includes the following steps:
s1, calculating and determining the corresponding air dew point temperature X based on the environment temperature T4 and the environment humidity T5 which are obtained in real time.
Specifically, during the operation of the air conditioning system, the ambient temperature T4 and the ambient humidity T5 are respectively detected and obtained in real time by the ambient temperature detection unit 41 and the humidity detection unit 42, and the corresponding air dew point temperature X is calculated and determined based on the obtained current ambient temperature T4 and ambient humidity T5 (the air dew point temperature X can be calculated according to the existing public standard data lookup table).
And S2, acquiring the temperature T6 of the copper pipe and the temperature T7 of the copper pipe, and calculating and comparing the lowest value A between the temperature T6 of the copper pipe and the temperature T7 of the copper pipe.
Specifically, the first temperature detection unit 51 and the second temperature detection unit 52 respectively detect and acquire the copper pipe temperature T6 and the copper pipe temperature T7 at the two ends of the variable-frequency radiating pipe 5, and determine the minimum value between the two as the minimum value a, so if T6 > T7, T7 is taken as the minimum value a, otherwise, if T6 < T7, T6 is taken as the minimum value a.
And S3, correspondingly adjusting the on/off state of the air conditioning system, the on/off state of the first electromagnetic valve 62, the opening degree of the indoor electromagnetic valve 32, the opening degree of the main electronic expansion valve 61 and the opening degree of the auxiliary electronic expansion valve 71 according to the difference between the minimum value A and the air dew point temperature X calculated in the step S1 and the operation mode of the air conditioning system.
In particular, the air conditioning system is adjusted accordingly based on the difference between a-X, and for ease of understanding, the adjustments are further explained below.
In this embodiment, four stages of heating execution actions are set according to the difference between the minimum value a and the air dew point temperature X when the air conditioning system is in the heating mode:
1) when A-X ≦ Δ T1 deg.C (Δ T1 is-1 deg.C, A-X ≦ -1 deg.C), enabling a first stage heating performing action, wherein the first stage heating performing action: the air conditioning system is immediately stopped until the air conditioning system is restarted for running after the air conditioning system is stopped for a rated time (preferably 10 min).
2) When Δ T1 < A-X ≦ Δ T2 ℃ (- Δ T2 is 2 ℃, -1 < A-X ≦ 2 ℃), enabling a second stage heating performing action, wherein the second stage heating performing action: the auxiliary electronic expansion valve 71 is immediately closed (adjusted to 0 pulse), and the indoor expansion valve opening degree of the indoor unit 31 in the open state is increased.
3) Enabling a third stage heating execution action when delta T2 < A-X ≦ delta T3 ℃, wherein the third stage heating execution action: the auxiliary electronic expansion valve 71 is immediately closed.
4) When A-X ≧ Δ T3 ℃, a fourth level heating execution action is enabled, wherein the fourth level heating execution action: the auxiliary electronic expansion valve 71 is immediately adjusted to a rated opening degree (the rated opening degree is preferably 56 pulses, and can be adaptively adjusted according to actual requirements).
Further, in the second-stage heating execution action, after the opening degree of the indoor expansion valve of the indoor unit 31 is adjusted and increased for the first time and the indoor expansion valve is continuously operated for 1 minute, the difference condition between the real-time minimum value a and the air dew point temperature X is judged, if the minimum value a is still smaller than the air dew point temperature X, the opening degree of the indoor expansion valve of the indoor unit 31 is continuously increased, the operation is repeated in a circulating mode until the minimum value a is larger than the air dew point temperature X (when a is larger than X, the current opening degree is kept continuously operated), and if the expansion valve of the indoor unit 31 after being adjusted for multiple times reaches the maximum opening degree, the minimum value a is still smaller than the air dew point temperature X, an abnormal alarm is prompted to remind a user of a fault.
Further, in the second-stage heating execution operation, the opening degree of the indoor expansion valve is adjusted to be increased by 16 pulses each time.
Further, during any one of the second stage heating execution operation, the third stage heating execution operation, and the fourth stage heating execution operation, if the difference between the minimum value a and the air dew point temperature X is a rated difference and is maintained for a rated time (preferably, a-X =2 ℃ for 5min, which is assumed to be satisfactory), the operation state before the execution operation is switched back, that is, both the auxiliary electronic expansion valve 71 and the indoor expansion valve are returned to be freely adjustable, and are freely adjusted according to the preset operation state.
The normal refrigerant flow path in the heating mode is as follows: the high-temperature and high-pressure refrigerant sent by the compressor 1 flows into each indoor unit 31 in the running state through the interfaces e-f of the four-way valve 2 to be condensed and released, the refrigerant after releasing heat flows to the subcooler 7 through the indoor expansion valve (at this time, the refrigerant is divided into two parts, one part flows into a subcooling branch of the subcooler 7 through the auxiliary electronic expansion valve 71 and directly flows back to an air return port of the compressor 1, the other part flows into a main flow path of the subcooler 7), the refrigerant sent out from the main flow path of the subcooler 7 flows through the variable-frequency radiating pipe 5 and the main electronic expansion valve 61 and then enters the outdoor unit to be evaporated and absorbed, the refrigerant after absorbing heat flows back to the compressor 1 through the interfaces g-h of the four-way valve 2, and in the refrigerant circulation flow path in the heating mode, wherein in the second-stage heating execution action and the third-stage heating execution action, after the auxiliary electronic expansion valve 71 is closed, all the main flow path of the, the supercooling branch at this time is not passed (supercooling process is not performed any more).
In this embodiment, for the air conditioning system in the cooling mode, five cooling execution actions are set according to the difference between the minimum value a and the air dew point temperature X:
1) when A-X ≦ Δ T1 '° C (Δ T1' is-1 ℃, A-X ≦ -1 ℃), enabling a first stage refrigeration performing action, wherein the first stage refrigeration performing action: the air conditioning system is immediately stopped until the air conditioning system is stopped for a rated time and then restarted for operation;
2) when Δ T1 ' < A-X < [ Δ T2 ' ° C ([ Δ T2 ' is 1 ℃, -1 < A-X ≦ 1 ℃), enabling second stage refrigeration performing action, wherein the second stage refrigeration performing action: immediately closing the auxiliary electronic expansion valve 71, opening the main electronic expansion valve 61 to the maximum opening degree and opening the first electromagnetic valve 62 until the difference value between the lowest value A and the air dew point temperature X is a rated difference value and the rated time is maintained, and then recovering to the normal operation state;
3) when Δ T2 ' < A-X < [ Δ T3 ' ° C ([ Δ T3 ' is 2 ℃, -1 < A-X ≦ 2 ℃), enabling third stage refrigeration performing action, wherein the third stage refrigeration performing action: immediately closing the auxiliary electronic expansion valve 71, and opening the main electronic expansion valve 61 to the maximum opening degree;
4) and when the delta T3 ' < A-X < [ delta T4 ' ° C (delta T4 ' is 3 ℃, 2 < A-X ≦ 2 ℃), enabling a fourth stage refrigeration performing action, wherein the fourth stage refrigeration performing action: immediately closing the auxiliary electronic expansion valve 71;
5) and when A-X is not less than delta T4' ° C (A-X is not less than 3 ℃), starting a fifth-stage refrigeration execution action, wherein the fifth-stage refrigeration execution action comprises the following steps: the auxiliary electronic expansion valve 71 is immediately adjusted to a rated opening degree (the rated opening degree is preferably 56 pulses, and can be adaptively adjusted according to actual requirements).
The normal refrigerant flow path in the refrigeration mode is as follows: high-temperature and high-pressure refrigerant sent by the compressor 1 flows into an outdoor unit to release heat through interfaces e-g of the four-way valve 2, the refrigerant after heat release flows through the variable-frequency radiating pipe 5 and a main flow path of the subcooler 7 after being throttled by the main electronic expansion valve 61 (one part of the refrigerant at this time is two, one part of the refrigerant flows back to a gas return port of the compressor 1 after flowing through a subcooling branch of the subcooler 7 through the auxiliary electronic expansion valve 71, and the other part of the refrigerant flows into the indoor unit 31 through the indoor expansion valve), the refrigerant flowing into the indoor unit 31 is sent out after being evaporated and absorbed heat and flows back to the gas return port of the compressor 1 through; the circulation flow of the refrigerant in the cooling mode is completed.
Further, in the second-stage cooling operation, when the sub-electronic expansion valve 71 is closed, all of the refrigerant flowing out of the main flow path of the subcooler 7 is sent to the indoor unit 31 in the operating state, the subcooling branch of the subcooler 7 is not passed, and the first solenoid valve 62 and the main electronic expansion valve 61 are opened to the maximum opening degree, so that the refrigerant flowing out of the outdoor unit simultaneously flows through the flow path of the main electronic expansion valve 61 and the flow path of the first solenoid valve 62 and the check valve 63, and the flow rate of the refrigerant flowing out of the outdoor unit is maximized.
Further, in the third-stage cooling execution operation, when the sub electronic expansion valve 71 is closed, all of the refrigerant flowing out of the main flow path of the subcooler 7 is sent to the indoor unit 31 in the operating state, the subcooling branch of the subcooler 7 is not passed, and the main electronic expansion valve 61 is opened to the maximum opening degree, thereby increasing the flow rate of the refrigerant flowing out of the outdoor unit.
Further, in the four-stage cooling execution operation, when the sub-electronic expansion valve 71 is closed, all of the refrigerant flowing out of the main flow path of the subcooler 7 is sent to the indoor unit 31 in the operating state, and the subcooling branch of the subcooler 7 is not passed through.
Further, during any one of the second-stage refrigeration executing operation, the third-stage refrigeration executing operation, the fourth-stage refrigeration executing operation, and the fifth-stage refrigeration executing operation, if the difference between the minimum value a and the air dew point temperature X is a rated difference and is maintained for a specified time (preferably, a-X =2 ℃ for 10min, it is determined that the requirement is met), the operation state before the execution operation is switched and recovered, that is, the auxiliary electronic expansion valve 71, the indoor expansion valve, the main expansion valve, and the first solenoid valve 62 are all recovered to be freely adjustable, and are freely adjusted according to the preset operation state.
In conclusion, the air conditioning system detects and judges the heating mode and the cooling mode, so that the effect of heat dissipation and cooling of the frequency conversion module by using the refrigerant can be ensured, the safety risk of no condensation water in the cooling process is also ensured, the air conditioning system can obtain better supercooling degree, and the influence of heat dissipation and cooling on the heating or cooling work of the air conditioning system is reduced.
The above-described embodiments are merely preferred embodiments of the present invention, which is not intended to limit the present invention in any way. Those skilled in the art can make many changes, modifications, and equivalents to the embodiments of the invention without departing from the scope of the invention as set forth in the claims below. Therefore, equivalent changes made according to the spirit of the present invention should be covered within the protection scope of the present invention without departing from the contents of the technical scheme of the present invention.
Claims (10)
1. An air conditioning system characterized by: the multi-split air conditioner comprises a compressor (1), a four-way valve (2), a multi-split indoor unit (3), an outdoor heat exchanger (4), a variable frequency radiating pipe (5) for cooling a variable frequency module, a throttling assembly (6) and a subcooler (7); four interfaces of the four-way valve (2) are respectively connected with an exhaust port of the compressor (1), an air return port of the compressor (1), one end of the outdoor heat exchanger (4) and one end of the multi-connected indoor unit (3); the two ends of the throttling assembly (6) are respectively connected with the other end of the outdoor heat exchanger (4) and one end of the variable-frequency radiating pipe (5), wherein the throttling assembly (6) comprises a main electronic expansion valve (61), a first electromagnetic valve (62) and a one-way valve (63), and the first electromagnetic valve (62) is connected with the one-way valve (63) in series and then connected with the main electronic expansion valve (61) in parallel; two ends of a main flow path of the subcooler (7) are respectively connected with the other end of the variable-frequency radiating pipe (5) and the other end of the multi-connected indoor unit (3), one end of a subcooling branch path of the subcooler (7) is connected between the main flow path and the multi-connected indoor unit (3) in a bypass mode, and the other end of the subcooling branch path is connected with a return air port of the compressor (1); an auxiliary electronic expansion valve (71) is arranged at the inlet of the supercooling branch; the multi-connected indoor unit (3) is composed of a plurality of indoor units (31) which are connected in parallel, and each indoor unit (31) is provided with an indoor electromagnetic valve (32); the outdoor environment temperature detection device further comprises an environment temperature detection unit (41), a humidity detection unit (42), a first temperature detection unit (51) and a second temperature detection unit (52), wherein the environment temperature detection unit (41) and the humidity detection unit (42) are respectively used for acquiring the environment temperature T4 and the environment humidity T5 of the outdoor environment; the first temperature detection unit (51) and the second temperature detection unit (52) are respectively arranged at two ends of the variable-frequency radiating pipe (5) and are used for obtaining the copper pipe temperature T6 and the copper pipe temperature T7 at two ends of the variable-frequency radiating pipe (5).
2. A condensation prevention control method of a frequency conversion heat radiation pipe (5) in an air conditioning system according to claim 1, characterized in that: the anti-condensation control method comprises the following steps:
s1, calculating and determining a corresponding air dew point temperature X based on the environment temperature T4 and the environment humidity T5 which are obtained in real time;
s2, obtaining the temperature T6 of the copper pipe and the temperature T7 of the copper pipe, and calculating and comparing the lowest value A between the temperature T6 of the copper pipe and the temperature T7 of the copper pipe;
and S3, correspondingly adjusting the on/off of the air conditioning system, the on/off of the first electromagnetic valve (62), the opening degree of the indoor electromagnetic valve (32), the opening degree of the main electronic expansion valve (61) and the opening degree of the auxiliary electronic expansion valve (71) according to the difference between the minimum value A and the air dew point temperature X calculated in the step S1 and the operation mode of the air conditioning system.
3. The condensation prevention control method of a frequency conversion heat dissipation pipe (5) in an air conditioning system according to claim 2, characterized in that: when the air conditioning system is in a heating mode, four-stage heating executing actions are set according to the difference condition of the lowest value A and the air dew point temperature X, wherein when A-X is less than or equal to delta T1 ℃, the first-stage heating executing action is started; when the temperature is more than delta T1 and less than or equal to delta T2 ℃, starting a second-stage heating execution action; when the temperature is more than delta T2 and less than or equal to delta T3 ℃, starting a third-level heating execution action; and when A-X is equal to or more than T3 ℃, enabling the fourth-level heating execution action.
4. The condensation prevention control method of a frequency conversion heat dissipation pipe (5) in an air conditioning system according to claim 3, characterized in that:
the first level heating execution action: the air conditioning system is immediately stopped until the air conditioning system is stopped for a rated time and then restarted for operation;
the second level heating execution action: immediately closing the auxiliary electronic expansion valve (71), and increasing the opening degree of the indoor expansion valve of the indoor unit (31) in an open state;
and the third-stage heating execution action: immediately closing the auxiliary electronic expansion valve (71),
the fourth stage heating execution action: immediately adjusting the auxiliary electronic expansion valve (71) to a rated opening degree.
5. The condensation prevention control method of a frequency conversion heat dissipation pipe (5) in an air conditioning system according to claim 4, characterized in that: and switching to return to the operating state before the execution operation if the difference between the minimum value a and the air dew point temperature X is a rated difference maintaining rated time during any one of the second-stage heating execution operation, the third-stage heating execution operation, and the fourth-stage heating execution operation.
6. The condensation prevention control method of a frequency conversion heat dissipation pipe (5) in an air conditioning system according to claim 2, characterized in that: when the air conditioning system is in a refrigeration mode, five-stage refrigeration executing actions are set according to the difference condition of the lowest value A and the air dew point temperature X, wherein when A-X is less than or equal to delta T1' ° C, the first-stage refrigeration executing action is started; enabling a second stage refrigeration performing action when Δ T1 '< A-X ≦ Δ T2' ° C; when the delta T2 '< A-X ≦ delta T3' ° C, enabling third-stage refrigeration to perform actions; enabling fourth stage refrigeration to perform actions when delta T3 '< A-X ≦ delta T4' ° C; and when A-X is equal to or more than delta T4' ° C, starting the fifth-stage refrigeration to execute the action.
7. The condensation prevention control method of a frequency conversion heat dissipation pipe (5) in an air conditioning system according to claim 6, characterized in that:
the first stage refrigeration performs the actions: the air conditioning system is immediately stopped until the air conditioning system is stopped for a rated time and then restarted for operation;
the second stage refrigeration performs the actions of: immediately closing the auxiliary electronic expansion valve (71), opening the main electronic expansion valve (61) to the maximum opening degree and opening the first electromagnetic valve (62) until the difference value between the lowest value A and the air dew point temperature X is a rated difference value and the normal running state is recovered after the rated time is maintained;
the third stage refrigeration performs the actions of: immediately closing the auxiliary electronic expansion valve (71), and opening the main electronic expansion valve (61) to the maximum opening degree;
the fourth stage refrigeration performing action: immediately closing the auxiliary electronic expansion valve (71);
the fifth stage refrigeration performs the actions of: immediately adjusting the auxiliary electronic expansion valve (71) to a rated opening degree.
8. The condensation prevention control method of a frequency conversion heat dissipation pipe (5) in an air conditioning system according to claim 7, characterized in that: and during any one of the second-stage refrigeration executing action, the third-stage refrigeration executing action, the fourth-stage refrigeration executing action and the fifth-stage refrigeration executing action, if the difference between the minimum value A and the air dew point temperature X is a rated difference and is maintained for a long time, switching to recover the running state before the executing action.
9. The condensation prevention control method of a frequency conversion heat dissipation pipe (5) in an air conditioning system according to claim 4, characterized in that: and in the second-stage heating execution action, after the opening degree of the indoor expansion valve of the indoor unit (31) is adjusted and increased for the first time and the indoor heating execution action is continuously operated for 1 minute, judging the difference condition between the real-time minimum value A and the air dew point temperature X, if the minimum value A is less than the air dew point temperature X, increasing the opening degree of the indoor expansion valve of the indoor unit (31) again and judging the difference condition in real time again, and circularly repeating the action until the minimum value A is more than the air dew point temperature X.
10. The condensation prevention control method of a frequency conversion heat dissipation pipe (5) in an air conditioning system according to claim 9, characterized in that: when the expansion valve of the indoor unit (31) after being adjusted for many times reaches the maximum opening degree, the lowest value A is still judged to be less than the air dew point temperature X in real time, and then abnormity is prompted.
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| CN112432397B (en) * | 2020-11-18 | 2021-10-08 | 珠海格力电器股份有限公司 | Air conditioning system and frequency converter condensation prevention control method thereof |
| CN112460763B (en) * | 2020-11-27 | 2021-11-09 | 珠海格力电器股份有限公司 | Air conditioner control method and device, storage medium and air conditioner |
| CN112432333B (en) * | 2020-12-04 | 2021-11-09 | 珠海格力电器股份有限公司 | Control method and device of air conditioning system, storage medium and air conditioner |
| CN113251496B (en) * | 2021-04-25 | 2023-02-17 | 广东Tcl智能暖通设备有限公司 | Air conditioning system and refrigerant heat dissipation method thereof |
| CN114777352A (en) * | 2022-03-23 | 2022-07-22 | 浙江中广电器集团股份有限公司 | Fluorine cooling variable frequency drive control module unit and control method thereof |
| CN115682283A (en) * | 2022-10-29 | 2023-02-03 | 珠海格力电器股份有限公司 | Air conditioner condensation prevention control method and device, air conditioner and medium |
| CN115773613A (en) * | 2022-11-11 | 2023-03-10 | 宁波奥克斯电气股份有限公司 | Condensation prevention control method and device for heat pump system and heat pump system |
| CN118066617A (en) * | 2022-11-22 | 2024-05-24 | 广东美的制冷设备有限公司 | Anti-condensation control method, device, equipment and storage medium |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20060100795A (en) * | 2005-03-18 | 2006-09-21 | 주식회사 대우일렉트로닉스 | Over cooling structure for heat pump type air conditioner |
| JP2008309478A (en) * | 2008-09-29 | 2008-12-25 | Sanyo Electric Co Ltd | Supercooling device |
| EP2876385A2 (en) * | 2013-11-26 | 2015-05-27 | Mitsubishi Heavy Industries, Ltd. | Air conditioner |
| CN105115065A (en) * | 2015-09-24 | 2015-12-02 | 芜湖美智空调设备有限公司 | Air conditioner control method |
| CN107270487A (en) * | 2017-07-10 | 2017-10-20 | 珠海格力电器股份有限公司 | Control the methods, devices and systems of air-conditioning driving plate radiating |
| CN110686390A (en) * | 2019-09-12 | 2020-01-14 | 珠海格力电器股份有限公司 | Control method and system for preventing mainboard condensation of frequency converter and air conditioner |
| CN110701690A (en) * | 2019-09-02 | 2020-01-17 | 格力电器（合肥）有限公司 | Control system, method and device for electric control cooling and condensation prevention of outdoor unit of air conditioner |
| CN110822564A (en) * | 2019-11-26 | 2020-02-21 | 广东美的制冷设备有限公司 | Heat dissipation assembly, air conditioning system and heat dissipation control method of air conditioning system |
-
2020
- 2020-05-25 CN CN202010449736.2A patent/CN111520873B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20060100795A (en) * | 2005-03-18 | 2006-09-21 | 주식회사 대우일렉트로닉스 | Over cooling structure for heat pump type air conditioner |
| JP2008309478A (en) * | 2008-09-29 | 2008-12-25 | Sanyo Electric Co Ltd | Supercooling device |
| EP2876385A2 (en) * | 2013-11-26 | 2015-05-27 | Mitsubishi Heavy Industries, Ltd. | Air conditioner |
| CN105115065A (en) * | 2015-09-24 | 2015-12-02 | 芜湖美智空调设备有限公司 | Air conditioner control method |
| CN107270487A (en) * | 2017-07-10 | 2017-10-20 | 珠海格力电器股份有限公司 | Control the methods, devices and systems of air-conditioning driving plate radiating |
| CN110701690A (en) * | 2019-09-02 | 2020-01-17 | 格力电器（合肥）有限公司 | Control system, method and device for electric control cooling and condensation prevention of outdoor unit of air conditioner |
| CN110686390A (en) * | 2019-09-12 | 2020-01-14 | 珠海格力电器股份有限公司 | Control method and system for preventing mainboard condensation of frequency converter and air conditioner |
| CN110822564A (en) * | 2019-11-26 | 2020-02-21 | 广东美的制冷设备有限公司 | Heat dissipation assembly, air conditioning system and heat dissipation control method of air conditioning system |
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