CN106969524B - Air conditioner differential pressure balancing system and air conditioner differential pressure balancing method - Google Patents

Air conditioner differential pressure balancing system and air conditioner differential pressure balancing method Download PDF

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Publication number
CN106969524B
CN106969524B CN201611242146.2A CN201611242146A CN106969524B CN 106969524 B CN106969524 B CN 106969524B CN 201611242146 A CN201611242146 A CN 201611242146A CN 106969524 B CN106969524 B CN 106969524B
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China
Prior art keywords
valve
port
heat exchanger
compressor
switching
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CN201611242146.2A
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CN106969524A (en
Inventor
程威
刘树清
许永锋
梁伯启
蒋运鹏
李华勇
马进
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Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
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Midea Group Co Ltd
GD Midea Heating and Ventilating Equipment Co Ltd
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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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves

Abstract

The invention provides an air conditioner differential pressure balancing system and an air conditioner differential pressure balancing method, wherein the air conditioner differential pressure balancing system comprises: outdoor unit circulation subassembly, indoor set circulation subassembly and the switching subassembly of connecting outdoor unit circulation subassembly and indoor set circulation subassembly, wherein, outdoor unit circulation subassembly includes: compressor, cross valve, outdoor heat exchanger and vapour and liquid separator, off-premises station circulation subassembly still includes: the oil separator, the first pipeline, the first valve, the second valve and at least one gear electromagnetic valve are arranged on the pipeline connecting the four-way valve and the outdoor heat exchanger, and each gear electromagnetic valve is connected with each part of the heat exchanger of the outdoor heat exchanger in series. By the technical scheme, the valve body in the existing system can be utilized, the control on the action of the valve body before starting is increased, effective pressure equalization before starting of the compressor is realized, the starting reliability of the compressor is ensured, and the running stability of the compressor is further ensured.

Description

Air conditioner differential pressure balancing system and air conditioner differential pressure balancing method
Technical Field
The invention relates to the technical field of household appliances, in particular to an air conditioner differential pressure balancing system and an air conditioner differential pressure balancing method.
Background
In the starting process of a compressor in an air conditioning system, in order to ensure the reliability of the starting operation of the compressor, the pressure of the exhaust side and the pressure of the return side are required to be basically consistent before the compressor is started so as to ensure that the compressor is started without pressure difference. The multi-split air conditioning system is complex in pipeline structure, the time interval from shutdown to restart of the compressor is short, and in the period, the system is difficult to completely balance high pressure and low pressure, so that the pressure difference between an exhaust side and an air return side is too large when the compressor is started again, potential safety hazards exist when the compressor is started, and faults can occur in serious cases.
Therefore, in the case that the time interval between the on and off of the air conditioner is short, how to balance the high-low pressure difference of the air conditioning system and make the air conditioning compressor start without pressure difference is needed to ensure the reliability of the start of the air conditioning compressor, which is a technical problem to be solved urgently.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art or the related art.
To this end, an object of the present invention is to provide an air conditioner differential pressure balancing system.
Another object of the present invention is to provide a method for balancing the differential pressure of an air conditioner.
To achieve the above object, according to a first aspect of the present invention, there is provided an air conditioner differential pressure balancing system, comprising: outdoor unit circulation subassembly, indoor set circulation subassembly and the switching subassembly of connecting outdoor unit circulation subassembly and indoor set circulation subassembly, wherein, outdoor unit circulation subassembly includes: compressor, cross valve, outdoor heat exchanger and vapour and liquid separator, off-premises station circulation subassembly still includes: the oil separator is arranged between the first valve port of the four-way valve and the compressor, the first port of the oil separator is connected with the exhaust port of the compressor, and the second port of the oil separator is connected with the first valve port; the first pipeline is connected with the air outlet of the air-liquid separator and the return air port of the compressor; one end of the first valve is connected with the fourth port of the oil separator through a pipeline, and the other end of the first valve is connected to the first pipeline through a pipeline; one end of the second valve is connected with the second port of the oil separator through a pipeline, and the other end of the second valve is connected to the first pipeline through a pipeline; and the at least one gear electromagnetic valve is arranged on a pipeline connecting the four-way valve and the outdoor heat exchanger, and each gear electromagnetic valve is connected with each partial heat exchanger of the outdoor heat exchanger in series.
According to the air conditioner differential pressure balancing system of the technical scheme of the invention, on the basis of the existing valve body in the existing system, the control valve body is added to realize the control of the valve body action before starting, the gears of the heat exchangers can be controlled and switched to meet different combined load requirements, effective pressure equalization before the compressor is started is realized, meanwhile, at least one gear electromagnetic valve is arranged on a pipeline between a third valve port and an outdoor heat exchanger, each gear electromagnetic valve is connected with each part of the heat exchangers of the outdoor heat exchanger in series, in the refrigeration, heating and mixed heating modes, all the gear electromagnetic valves are opened, in the mixed refrigeration mode, the opening number of the gear electromagnetic valves is determined according to the load, so that the refrigerant flowing out through the gear electromagnetic valve and the outdoor heat exchanger is a gas-liquid mixture to enhance the refrigeration effect, through the technical scheme, before the compressor is started or after the compressor is closed, all the control valve bodies are opened, so that the starting reliability of the compressor is ensured, and the running stability of the compressor is further ensured.
According to the above technical solution of the present invention, preferably, the outdoor unit circulation assembly is connected to the switching assembly through a first stop valve and a second stop valve, wherein the first stop valve is connected to the outdoor heat exchanger, the second stop valve is connected to a third port of the four-way valve through a first check valve, and the second stop valve is connected to the outdoor heat exchanger through a second check valve; in a refrigeration mode, the refrigerant flows out of the switching assembly through the second stop valve, flows to the third valve port through the first check valve and enters the gas-liquid separator; in the heating mode, the refrigerant flows out of the second stop valve and flows into the outdoor heat exchanger through the second one-way valve and the at least one gear electromagnetic valve.
In the technical scheme, the first stop valve and the second stop valve are arranged between the outdoor unit circulating assembly and the switching assembly, so that the connected pipelines can be forcibly sealed and cut off in the process of disassembling and assembling the indoor unit and the outdoor unit, the stability of fluid movement in the pipelines is ensured, and the effective switching of the air conditioner among various working modes is further ensured.
According to the above technical solution of the present invention, preferably, a first port of the four-way valve is connected to the compressor, a second port of the four-way valve is connected to the first cut-off valve, a third port of the four-way valve is connected to the first end of the outdoor heat exchanger, and a fourth port of the four-way valve is connected to the air inlet of the gas-liquid separator.
In the technical scheme, each valve port of the four-way valve is connected with different elements, and the four-way valve is controlled to be communicated with different pipelines, so that the flow direction of a refrigerant in a system pipeline is changed, and further the air conditioner is switched between a refrigerating mode and a heating mode.
According to the above technical solution of the present invention, preferably, the outdoor unit circulation assembly further includes: the second pipeline is communicated with the first valve port and the second port; the first capillary tube is connected with the first valve in series between the first pipeline and the fourth port; and a second capillary tube connected in series with the second valve between the first and second lines.
In the technical scheme, the first capillary tube and the first capillary tube control the flow of the refrigerant in the corresponding pipeline, so that the flow speed and the pressure of the refrigerant in the corresponding pipeline can be controlled, the use efficiency of the air conditioning system is improved, and a better heat exchange effect is achieved. In order to achieve better air return when the air-conditioning compressor is started, the second pipeline is communicated with the first pipeline through a pipeline, the second pipeline is a pipeline for communicating the first valve port with the second port, a second valve is arranged in the middle of the pipeline to control the communication and disconnection of the second pipeline and the first pipeline, high-pressure oil coming out of the second pipeline is decompressed through a second capillary tube, and then enters an air return port of the compressor in a low-pressure air mode. Through the pressure relief of the first capillary tube and the second capillary tube, high-pressure oil and high-pressure air return to the air return side, the pressure difference between the exhaust side and the air return side of the compressor can be made up, so that the pressure difference is overlarge when the compressor is operated, and the possibility of accidents can be effectively reduced.
According to the above technical solution of the present invention, preferably, the outdoor unit circulation assembly further includes: one end of the oil return pipeline is connected with an air return port of the compressor, and the other end of the oil return pipeline is connected with a third port of the oil separator; and the oil in the oil separator is discharged from the third port and flows back to the compressor from the air return port through the oil return capillary tube.
In the technical scheme, when the air conditioner is started, and the compressor is in a working state, high-temperature and high-pressure gas-oil mixture discharged by the exhaust port passes through the oil separator, high-pressure oil is filtered into the oil separator, in order to maintain the oil supply circulation of the compressor, high-pressure oil in the oil separator flows out of a third port in the oil separator, flows into the oil return pipeline, passes through an oil return capillary tube on the oil return pipeline, becomes low-pressure oil, and flows back to a return port of the compressor, so that the high-pressure oil can be recycled by the compressor.
According to the above technical solution of the present invention, preferably, the outdoor unit circulation assembly further includes: and the third one-way valve is arranged on a pipeline which is communicated with the second valve port and a main line consisting of each branch of the at least one gear electromagnetic valve, and the refrigerant flows out of the second valve port, passes through the third one-way valve and the at least one gear electromagnetic valve and flows into the outdoor heat exchanger.
In the technical scheme, the third one-way valve can prevent the refrigerant flowing into the outdoor heat exchanger from flowing reversely in the heating mode, so that the running stability of the air conditioning system is ensured, and the service life of the air conditioner is prolonged.
According to the above technical solution of the present invention, preferably, the outdoor unit circulation assembly further includes: the fourth check valve is arranged on a pipeline communicated with the outlet of the outdoor heat exchanger and the second valve port, and in the heating mode, the refrigerant flows out of the outdoor heat exchanger and flows to the second valve port through the fourth check valve; and the fifth one-way valve is arranged on a pipeline communicated with the outlet of the outdoor heat exchanger and the first stop valve, and the refrigerant flows out of the outdoor heat exchanger in the refrigeration mode and flows to the first stop valve through the fifth one-way valve.
In the technical scheme, in a heating mode, a refrigerant flows out of the outdoor heat exchanger, flows to a second valve port of the four-way valve through a fourth one-way valve, flows into the gas-liquid separator from the second valve port through the fourth valve port, and flows out of the gas-liquid separator to flow back to a return port of the compressor; in the cooling mode, the refrigerant flows out of the outdoor heat exchanger, flows into the first stop valve through the fifth one-way valve, flows into the indoor heat exchanger through the first stop valve to achieve the effect of cooling, the counter flow of the refrigerant in the cooling mode can be prevented by selecting the fourth one-way valve, and the counter flow of the refrigerant in the heating mode can be prevented by the fifth one-way valve.
According to the above technical solution of the present invention, preferably, the outdoor unit circulation assembly further includes: and the sixth one-way valve is arranged in a pipeline for communicating the third valve port with the first stop valve, and in the heating mode, the refrigerant flows out of the third valve port and flows to the first stop valve through the sixth one-way valve.
In the technical scheme, in the heating mode, the refrigerant flows out of the third valve and flows to the first stop valve through the sixth one-way valve, and when the first stop valve is closed, the sixth one-way valve can prevent the refrigerant in the pipeline from flowing back to the four-way valve, so that the stability of the air conditioning system is ensured, and other components are prevented from being damaged.
According to any one of the above technical solutions of the present invention, preferably, the switching component includes: the switching separator is connected with the first stop valve through a pipeline, and the refrigerant flows into the switching separator from a liquid inlet of the switching separator through the first stop valve; the first part of the first heat exchanger is connected with a liquid outlet of the switching separator; the second heat exchanger is connected with the first heat exchanger in series, and the refrigerant flows through the first heat exchanger from the liquid outlet and flows into the second heat exchanger; the third valve is arranged on a pipeline connecting the first part of the second heat exchanger with the first part of the first heat exchanger; wherein, first heat exchanger and second heat exchanger are plate heat exchanger.
In the technical scheme, the gaseous refrigerant flows to the upper gaseous outlet after passing through the switching separator, the liquid refrigerant flows to the lower liquid outlet after passing through the switching separator, and the switching separator has the function of separating gas and liquid in the refrigerant; the refrigerant needs to realize thermal exchange through the heat exchanger, and plate-type heat exchanger can guarantee the abundant contact of refrigerant and heat exchanger, and simultaneously, the heat exchanger divide into first heat exchanger and second heat exchanger, sets up the third valve between the two, when having liquid to flow out from switching the separator in refrigeration and mixed refrigeration mode, the circulation of liquid in the switching separator can be controlled to opening and closing of third valve, and liquid flows to the first portion of second heat exchanger from the first portion of first heat exchanger through the third valve.
According to the above technical solution of the present invention, preferably, the switching component further includes: the fourth valve and the fifth valve are connected in parallel to form a throttling assembly, one end of the throttling assembly is connected to the second portion of the second heat exchanger, and the other end of the throttling assembly is connected to a pipeline extending through the first portion of the second heat exchanger.
In the technical scheme, the throttling assembly formed by connecting the fourth valve and the fifth valve in parallel can quickly adjust the flow rate of the refrigerant flowing out of the second heat exchanger so as to ensure the effective operation of the air-conditioning system.
According to the above technical solution of the present invention, preferably, in the cooling mode, the refrigerant flows out from the liquid outlet of the switching separator, and after passing through the first heat exchanger and the third valve, a part of the refrigerant flows back to the second stop valve through the second heat exchanger and the throttling assembly, and another part of the refrigerant flows back to the second stop valve after flowing to the indoor unit circulating assembly; in the heating mode, the refrigerant flows out from the air outlet of the switching separator and flows out through the indoor unit circulation assembly, after passing through the second heat exchanger, a part of the refrigerant flows back to the second stop valve through the throttling assembly, and the other part of the refrigerant flows back to the second stop valve after flowing to the indoor unit circulation assembly.
In the technical scheme, during refrigeration cycle, one part of refrigerant flows back to the second stop valve through the second heat exchanger and the throttling assembly, and the other part of refrigerant flows back to the second stop valve after flowing to the indoor unit circulating assembly, so that the refrigerant in the pipeline is further subcooled, and the refrigeration effect of the air conditioning system is effectively improved. During the heating circulation, after the refrigerant passes through the second heat exchanger, a part of the refrigerant flows back to the second stop valve through the throttling assembly, heat exchange is carried out through the first heat exchanger and the second heat exchanger again, the service efficiency of the system is improved, the other part of the refrigerant flows to the indoor unit circulation assembly, sufficient heat exchange is carried out through the indoor heat exchanger, and a good heating effect is achieved.
According to one technical scheme of the invention, preferably, in a mixed mode, when the outdoor heat exchanger condenses, the refrigerant is a gas-liquid mixed refrigerant, wherein the gas refrigerant enters at least one first indoor heat exchanger in the indoor unit circulation assembly through the gas outlet, exchanges heat through the at least one first indoor heat exchanger and flows into the second heat exchanger, the liquid refrigerant sequentially passes through the first heat exchanger and the third valve, a part of liquid refrigerant flows back to the second stop valve through the second heat exchanger and the throttling assembly, and the other part of liquid refrigerant flows back to the second stop valve after flowing to the at least one second indoor heat exchanger; when the outdoor heat exchanger evaporates, the refrigerant flows into the at least one second indoor heat exchanger through the air outlet to perform primary heat exchange, the refrigerant flowing out of the at least one second indoor heat exchanger passes through the second heat exchanger, one part of the refrigerant flows to the second stop valve through the throttling assembly, and the other part of the refrigerant flows to the second stop valve after passing through the at least one first indoor heat exchanger.
In the technical scheme, after gas-liquid mixed refrigerant enters a switching separator and is separated, gas refrigerant enters at least one first indoor heat exchanger for heat exchange, then further heat exchange is carried out between the gas refrigerant and the first heat exchanger through a second heat exchanger, the gas refrigerant flows into an outdoor unit assembly, after the liquid refrigerant sequentially passes through the first heat exchanger and a third valve, a part of liquid refrigerant flows back to the outdoor unit assembly through the second heat exchanger and a throttling assembly, and the other part of liquid refrigerant flows back to the outdoor unit assembly after flowing to at least one second indoor heat exchanger; when the outdoor heat exchanger is evaporated, the refrigerant flows into the at least one second indoor heat exchanger through the air outlet to perform primary heat exchange, the refrigerant flowing out of the at least one second indoor heat exchanger passes through the second heat exchanger, one part of the refrigerant flows to the second stop valve through the throttling assembly, the other part of the refrigerant flows to the second stop valve after passing through the at least one first indoor heat exchanger, and better heat exchange effect is realized, by the proposal, the matching of the gear electromagnetic valve and the switching separator and the shunting of the gas-liquid mixture realize the indoor mixed mode, in addition, the existing valve body in the prior system is fully utilized, the effective pressure equalizing before the compressor is started is realized by increasing the control on the action of the valve body before the compressor is started, meanwhile, the gears of the heat exchangers can be controlled and switched to meet different combined load requirements, the starting reliability of the compressor is ensured, and the stable operation of the compressor is further ensured.
According to a second aspect of the present invention, there is provided an air-conditioning differential pressure balancing method for an air-conditioning differential pressure balancing system according to any one of the first aspect of the present invention, comprising: receiving an adjusting signal, and adjusting the operation mode of the air conditioner according to the adjusting signal; receiving a control signal for controlling the start or stop of the air conditioner; and controlling the opening and closing of the first valve, the second valve and each gear electromagnetic valve of the outdoor circulation assembly in the air conditioner and the opening and closing of the switching valve of the switching assembly connected with the outdoor circulation assembly according to the control signals.
According to the air conditioner differential pressure balancing method, the air conditioner can be switched to the corresponding operation mode according to the adjusting signal, then the existing valve body in the existing system is utilized, effective pressure equalizing before the compressor is started is realized by increasing the control on the action of the valve body before starting, and meanwhile, the gears of the heat exchanger can be controlled and switched to meet different combined load requirements, so that the starting reliability of the compressor is ensured, and the stable operation of the compressor is further ensured.
According to the above technical solution of the present invention, preferably, when the adjustment signal received by the air conditioner is a refrigeration signal, the air conditioner is switched to a refrigeration mode, the first valve port and the second valve port of the four-way valve are communicated, and the third valve port and the fourth valve port of the four-way valve are communicated; if the control signal is a starting signal, opening the first valve, the second valve, the switching valve and each gear electromagnetic valve; when the first delay time after the first valve, the second valve, the switching valve and each gear electromagnetic valve are opened is longer than a first preset time, the first valve, the second valve, the switching valve and each gear electromagnetic valve are closed, and the compressor is started; and if the control signal is a stop signal, closing the compressor, and opening the first valve, the second valve, the switching valve and each gear electromagnetic valve when second delay time after the compressor is closed is greater than second preset time.
In the technical scheme, during refrigeration cycle, a first valve port of a four-way valve is communicated with a second valve port, a third valve port of the four-way valve is communicated with a fourth valve port, before a compressor is started, a first valve, a second valve, a switching valve and each gear electromagnetic valve are opened to rapidly balance the high-low pressure difference of a system, when the opening duration reaches a first preset time, the first valve, the second valve, the switching valve and each gear electromagnetic valve are closed, then the compressor is started, the compressor is started without pressure difference, and after the compressor is started, all the valves operate according to normal control logic. After the compressor is closed, if the duration is longer than a second preset time, the first valve, the second valve, the switching valve and the electromagnetic valve of each gear are controlled to be opened, so that effective pressure equalization before the compressor is opened is realized, and the reliability of starting the compressor is ensured.
According to one embodiment of the present invention, preferably, when the adjustment signal received by the air conditioner is a heating signal, the air conditioner is switched to a heating mode, the first port of the four-way valve is communicated with the third port, and the second port of the four-way valve is communicated with the fourth port; if the control signal is a starting signal, opening the first valve, the second valve, the switching valve and each gear electromagnetic valve; when the first delay time after the first valve, the second valve, the switching valve and each gear electromagnetic valve are opened is longer than a first preset time, the first valve, the second valve, the switching valve and each gear electromagnetic valve are closed, and the compressor is started; and if the control signal is a stop signal, closing the compressor, determining second delay time after the compressor is closed, and opening the first valve, the second valve, the switching valve and each gear electromagnetic valve when the second delay time is greater than second preset time.
In the technical scheme, during heating circulation, a first valve port of a four-way valve is communicated with a third valve port, a second valve port of the four-way valve is communicated with a fourth valve port, before a compressor is started, a first valve, a second valve, a switching valve and each gear electromagnetic valve are opened to quickly balance the high-low pressure difference of a system, when the opening duration reaches a first preset time, the first valve, the second valve, the switching valve and each gear electromagnetic valve are closed, then the compressor is started to be started without pressure difference, and after the compressor is started, all the valves operate according to normal control logic. After the compressor is closed, if the duration time is longer than a second preset time, the first valve, the second valve, the switching valve and the electromagnetic valve of each gear are controlled to be opened so as to quickly balance the high-low pressure difference of the system and enable the compressor to be started without pressure difference.
According to one technical scheme of the invention, preferably, when the adjusting signal received by the air conditioner is a mixed refrigeration signal, the air conditioner is switched to a mixed refrigeration mode, the first valve port and the second valve port of the four-way valve are communicated, and the third valve port and the fourth valve port of the four-way valve are communicated; if the control signal is a starting signal, opening the first valve, the second valve, the switching valve and each gear electromagnetic valve; when the first delay time after the first valve, the second valve, the switching valve and each gear electromagnetic valve are opened is longer than a first preset time, the first valve, the second valve, the switching valve and each gear electromagnetic valve are closed, and the compressor is started; and if the control signal is a stop signal, closing the compressor, and opening the first valve, the second valve, the switching valve and the at least one gear electromagnetic valve when second delay time after the compressor is closed is greater than second preset time, wherein the number of the gear electromagnetic valves which are opened is less than the total number of the gear electromagnetic valves.
In the technical scheme, during mixed refrigeration circulation, a first valve port and a second valve port of a four-way valve are communicated, a third valve port and a fourth valve port of the four-way valve are communicated, before a compressor is started, a first valve, a second valve, a switching valve and each gear electromagnetic valve are opened to rapidly balance the high-low pressure difference of a system, when the opening duration reaches a first preset time, the first valve, the second valve, the switching valve and each gear electromagnetic valve are closed, then the compressor is started to be started without pressure difference, and after the compressor is started, all the valves operate according to normal control logic. After the compressor is closed, if the duration time is longer than the second preset time, the first valve, the second valve, the switching valve and the partial gear electromagnetic valves are controlled to be opened, so that effective pressure equalization before the compressor is opened is realized, the reliability of starting of the compressor is ensured, the number of the opened gear electromagnetic valves is smaller than the total number of the gear electromagnetic valves, the operation efficiency of the system is improved, and the mixed refrigeration effect is better achieved.
According to one embodiment of the present invention, preferably, when the adjustment signal received by the air conditioner is a mixed heating signal, the air conditioner is switched to the mixed heating mode, and the first valve port and the third valve port of the four-way valve are communicated, and the second valve port and the fourth valve port of the four-way valve are communicated; if the control signal is a starting signal, opening the first valve, the second valve, the switching valve and each gear electromagnetic valve; when the first delay time after the first valve, the second valve, the switching valve and each gear electromagnetic valve are opened is longer than a first preset time, the first valve, the second valve, the switching valve and each gear electromagnetic valve are closed, and the compressor is started; and if the control signal is a stop signal, closing the compressor, determining second delay time after the compressor is closed, and opening the first valve, the second valve, the switching valve and each gear electromagnetic valve when the second delay time is greater than second preset time.
In the technical scheme, during a hybrid heating cycle, a first valve port and a third valve port of a four-way valve are communicated, a second valve port and a fourth valve port of the four-way valve are communicated, before a compressor is started, a first valve, a second valve, a switching valve and each gear electromagnetic valve are opened to quickly balance the high-low pressure difference of a system, when the opening duration reaches a first preset time, the first valve, the second valve, the switching valve and each gear electromagnetic valve are closed, then the compressor is started to enable the compressor to be started without pressure difference, and after the compressor is started, all the valves are operated according to normal control logic. After the compressor is closed, if the duration time is longer than the second preset time, the first valve, the second valve, the switching valve and the partial gear electromagnetic valves are controlled to be opened, so that effective pressure equalization before the compressor is opened is achieved, the reliability of starting of the compressor is ensured, the number of the opened gear electromagnetic valves is smaller than the total number of the gear electromagnetic valves, the system operation efficiency is improved, and the mixed heating effect is better achieved.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
Fig. 1 shows a schematic view of a refrigeration cycle system according to an embodiment of the present invention;
fig. 2 is a schematic flow chart illustrating a method for balancing air conditioning differential pressure according to an embodiment of the present invention;
FIG. 3 shows a schematic view of a heating cycle system according to an embodiment of the invention;
FIG. 4 shows a schematic diagram of a hybrid refrigeration cycle system according to yet another embodiment of the present invention;
fig. 5 shows a schematic diagram of a hybrid heating cycle system according to yet another embodiment of the invention.
102 indoor unit circulation module, 104 switching module, 106 outdoor unit circulation module, 108 compressor, 110 four-way valve, 112 outdoor heat exchanger, 114 gas-liquid separator, 116 oil separator, 118 first valve, 120 second valve, 122 third valve, 124 fourth valve, 126 fifth valve, 128 first check valve, 130 second check valve, 132 third check valve, 134 fourth check valve, 136 fifth check valve, 138 sixth check valve, 140 first capillary tube, 142 second capillary tube, 144 return capillary tube, 146 first stop valve, 148 second stop valve, 150-step solenoid valve, 152 first heat exchanger, 154 second heat exchanger, 156 switching separator, a first port, b second port, c third port, d fourth port.
Detailed Description
In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited to the specific embodiments disclosed below.
The air conditioner differential pressure equalizing system according to the embodiment of the present invention will be described in detail with reference to fig. 1 to 5.
As shown in fig. 1, according to an embodiment of a first aspect of the present invention, there is provided an air conditioner differential pressure balancing system, including: an outdoor unit circulation component 106, an indoor unit circulation component 102, and a switching component 104 connecting the outdoor unit circulation component 106 and the indoor unit circulation component 102, wherein the outdoor unit circulation component 106 includes: compressor 108, four-way valve 110, outdoor heat exchanger 112 and gas-liquid separator 114, and outdoor unit circulation module 106 further includes:
an oil separator 116 provided between the first port a of the four-way valve 110 and the compressor 108, a first port of the oil separator 116 being connected to an exhaust port of the compressor 108, and a second port of the oil separator 116 being connected to the first port a; a first conduit connecting the outlet of the gas-liquid separator 114 to the return port of the compressor 108; a first valve 118, one end of the first valve 118 being connected to the fourth port of the oil separator 116 via a pipe, the other end of the first valve 118 being connected to the first pipe via a pipe; a second valve 120, one end of the second valve 120 being connected to the second port of the oil separator 116 through a pipe, the other end of the second valve 120 being connected to the first pipe through a pipe; and at least one gear solenoid valve disposed on a pipeline connecting the four-way valve 110 and the outdoor heat exchanger 112, wherein each gear solenoid valve is connected in series with each partial heat exchanger of the outdoor heat exchanger 112.
According to the air conditioner differential pressure balancing system of the embodiment of the invention, on the basis of the existing valve body in the existing system, the control valve body is added to realize the control of the valve body action before starting, the gears of the heat exchangers can be controlled and switched to meet different combined load requirements, effective pressure equalization before the compressor is started is realized, meanwhile, at least one gear electromagnetic valve is arranged on a pipeline between a third valve port and an outdoor heat exchanger, each gear electromagnetic valve is connected with each part of the heat exchangers of the outdoor heat exchanger in series, in the refrigeration, heating and mixed heating modes, all the gear electromagnetic valves are opened, in the mixed refrigeration mode, the opening number of the gear electromagnetic valves is determined according to the load, so that the refrigerant flowing out through the gear electromagnetic valve and the outdoor heat exchanger is a gas-liquid mixture to enhance the refrigeration effect, by the technical scheme, before the compressor is started or after the compressor is closed, all the control valve bodies are opened, so that the starting reliability of the compressor is ensured, and the running stability of the compressor is further ensured.
Specifically, when the compressor 108 is stopped, the system needs to be restarted, the external unit receives a starting command, is in a standby mode, and starts the compressor 108, the standby time is defined as T0, the first valve 118 to the fifth valve 126 and the gear position solenoid valve 150 are opened within the time T0, and the pressure of the system is equalized before the compressor 108 is started. That is, the outdoor unit receives the power-on command, the first valve 118 to the fifth valve 126 and the gear position electromagnetic valve 150 are opened, and after the compressor 108 is started, the first valve 118 to the fifth valve 126 and the gear position electromagnetic valve 150 are controlled according to the logic after power-on. When the outer unit receives the shutdown command, the compressor 108 is stopped, the first to fifth valves 118 to 126 and the shift position solenoid valve 150 are opened, and the opening time of the first to fifth valves 118 to 126 and the shift position solenoid valve 150 is defined as T1.
According to the above-mentioned embodiment of the present invention, preferably, the outdoor unit circulation module 106 is connected to the switching module 104 through the first cut-off valve 146 and the second cut-off valve 148, wherein the first cut-off valve 146 is connected to the outdoor heat exchanger 112, the second cut-off valve 148 is connected to the third port c of the four-way valve 110 through the first check valve 128, and the second cut-off valve 148 is connected to the outdoor heat exchanger 112 through the second check valve 130; in the cooling mode, the refrigerant flows out of the switching assembly 104 through the second stop valve 148, flows to the third valve port c through the first check valve 128, and enters the gas-liquid separator 114; in the heating mode, the refrigerant flows out of the second stop valve 148, passes through the second check valve 130 and the at least one shift position solenoid valve, and flows into the outdoor heat exchanger 112.
In this embodiment, by providing the first stop valve 146 and the second stop valve 148 between the outdoor unit circulation assembly 106 and the switching assembly 104, the connected pipes can be forcibly sealed and cut off in the process of assembling and disassembling the indoor unit and the outdoor unit, thereby ensuring the stability of the fluid movement in the pipes and further ensuring the effective switching of the air conditioner between various working modes.
The second stop valve is a low-pressure stop valve, only low-pressure fluid is allowed to pass through the second stop valve, high-pressure fluid is stopped, the refrigerant passing through the second stop valve can only flow into the third valve port through the first check valve in a one-way mode and flows into the outdoor heat exchanger through the second check valve in a one-way mode, when a user uses an air conditioner for refrigeration, the refrigerant flows through the second stop valve, the low-pressure refrigerant in the refrigerant flows out of the second stop valve, flows to the third valve port of the four-way valve through the first check valve, and flows back to the air return port of the compressor after passing through the gas-liquid.
According to the above-described embodiment of the present invention, it is preferable that the first port a of the four-way valve 110 is connected to the compressor 108, the second port b of the four-way valve 110 is connected to the first cut-off valve 146, the third port c of the four-way valve 110 is connected to the first end of the outdoor heat exchanger 112, and the fourth port d of the four-way valve 110 is connected to the air inlet of the gas-liquid separator 114.
In this embodiment, each valve port of the four-way valve 110 is connected to different components, and the four-way valve 110 is controlled to communicate with different pipelines, so as to change the flow direction of the refrigerant in the system pipeline, thereby realizing the interconversion between the cooling and heating modes of the air conditioner.
When a user needs air-conditioning refrigeration, the user sends a refrigeration instruction, a first valve port a and a fourth valve port d in the four-way valve are communicated, and a second valve port b and a third valve port c are communicated; when a user needs to heat, the first valve port a of the four-way valve is communicated with the second valve port b, and the third valve port c is communicated with the fourth valve port d.
According to the above embodiment of the present invention, preferably, the outdoor unit circulation module 106 further includes: the second pipeline is communicated with the first valve port a and the second port; a first capillary 140 in series with the first valve 118 between the first line and the fourth port; and a second capillary 142 in series with the second valve 120 between the first and second lines.
In this embodiment, the first capillary tube 140 and the second capillary tube 142 control the flow rate of the refrigerant in the corresponding pipeline, so as to control the flow rate and pressure of the refrigerant in the corresponding pipeline, thereby improving the utilization efficiency of the air conditioning system and achieving a better heat exchange effect. In order to achieve better air return when the air-conditioning compressor is started, the second pipeline is communicated with the first pipeline through a pipeline, wherein the second pipeline is a pipeline for communicating the first valve port with the second port, a second valve 120 is arranged in the middle of the pipeline to control the communication and disconnection of the second pipeline and the first pipeline, high-pressure oil from the second pipeline is decompressed through a second capillary tube, and then enters an air return port of the compressor in a low-pressure air mode. Through the pressure relief of the first capillary tube and the second capillary tube, high-pressure oil and high-pressure air return to the air return side, the pressure difference between the exhaust side and the air return side of the compressor can be made up, so that the pressure difference is overlarge when the compressor is operated, and the possibility of accidents can be effectively reduced.
According to the above embodiment of the present invention, preferably, the outdoor unit circulation module 106 further includes: one end of the oil return pipeline is connected with an air return port of the compressor 108, and the other end of the oil return pipeline is connected with the third port; and an oil return capillary tube 144 provided in the oil return line, wherein the oil in the oil separator 116 is discharged from the third port, and flows back to the compressor 108 from the oil return port through the oil return capillary tube 144.
In this embodiment, when the air conditioner is turned on and the compressor 108 is in operation, the high-temperature and high-pressure gas-oil mixture discharged from the exhaust port passes through the oil separator, the high-pressure oil is filtered into the oil separator, and in order to maintain the oil supply cycle of the compressor, the high-pressure oil in the oil separator flows out from the third port in the oil separator, flows into the oil return line, passes through the oil return capillary tube 144 on the oil return line, becomes low-pressure oil, and flows back to the return port of the compressor 108, so that the oil can be reused by the compressor 108.
According to the above embodiment of the present invention, preferably, the outdoor unit circulation module 106 further includes: and a third check valve 132 disposed on a pipe line connecting the second valve port b and a main line formed by each branch of the at least one shift solenoid valve, wherein the refrigerant flows out from the second valve port b, passes through the third check valve 132 and the at least one shift solenoid valve, and flows into the outdoor heat exchanger 112.
In this embodiment, the third check valve 132 can prevent the refrigerant flowing into the outdoor heat exchanger 112 from flowing backward in the heating mode, so as to ensure the stability of the operation of the air conditioning system, and further improve the service life of the air conditioner.
According to the above embodiment of the present invention, preferably, the outdoor unit circulation module 106 further includes: a fourth check valve 134, which is disposed on a pipeline communicating the outlet of the outdoor heat exchanger 112 and the second valve b, and in the heating mode, the refrigerant flows out of the outdoor heat exchanger 112 and flows to the second valve b through the fourth check valve 134; and a fifth check valve 136 disposed on a pipeline connecting the outlet of the outdoor heat exchanger 112 and the first cutoff valve 146, wherein the refrigerant flows out of the outdoor heat exchanger 112 through the fifth check valve 136 to the first cutoff valve 146 in the cooling mode.
In this embodiment, in the heating mode, the refrigerant flows out of the outdoor heat exchanger 112, flows to the second port b of the four-way valve through the fourth check valve 134, flows from the second port b to the gas-liquid separator through the fourth port d, flows out of the gas-liquid separator, and flows back to the return port of the compressor; in the cooling mode, the refrigerant flows out of the outdoor heat exchanger 112, flows into the first stop valve 146 through the fifth check valve 136, flows into the indoor heat exchanger through the first stop valve 146, and reaches the effect of cooling, the refrigerant can be prevented from flowing backwards in the cooling mode by selecting the fourth check valve 134, and the refrigerant can be prevented from flowing backwards in the heating mode by the fifth check valve 136.
According to the above embodiment of the present invention, preferably, the outdoor unit circulation module 106 further includes: and a sixth check valve 138 provided in a pipe line connecting the third port c and the first shutoff valve 146, and allowing the refrigerant to flow out of the third port c and to flow to the first shutoff valve 146 through the sixth check valve 138 in the heating mode.
In this embodiment, in the heating mode, the refrigerant flows out of the third port c and flows to the first stop valve 146 through the sixth check valve 138, and when the first stop valve 146 is closed, the sixth check valve 138 can prevent the refrigerant in the pipeline from flowing back into the four-way valve 110, thereby ensuring the stability of the air conditioning system and avoiding damaging other components.
According to any of the above embodiments of the present invention, preferably, the switching component 104 includes: a switching separator 156 connected to the first cutoff valve 146 through a pipe, and the refrigerant flows into the switching separator 156 through the first cutoff valve 146 from a liquid inlet of the switching separator 156; a first heat exchanger 152, a first part of the first heat exchanger 152 being connected to the liquid outlet of the switching separator 156; the second heat exchanger 154 is connected with the first heat exchanger 152 in series, and the refrigerant flows through the first heat exchanger 152 from the liquid outlet and flows into the second heat exchanger 154; a third valve 122 provided on a line connecting the first portion of the second heat exchanger 154 and the first portion of the first heat exchanger 152; the first heat exchanger 152 and the second heat exchanger 154 are both plate heat exchangers.
In this embodiment, the third valve 122 is used to control the flow rate, pressure and flow rate of the refrigerant flowing out of the switching separator 156, so as to improve the utilization efficiency of the air conditioning system, and further achieve a better heat exchange effect. The plate heat exchanger is a high-efficiency heat exchanger formed by stacking a series of metal sheets with certain corrugated shapes, thin rectangular channels are formed among various plates, heat exchange is carried out through the plates, and the plate heat exchanger is high in heat exchange efficiency, small in heat loss, compact and light in structure, small in occupied area, wide in application and long in service life.
According to the above embodiment of the present invention, preferably, the switching component 104 further includes: a fourth valve 124 with adjustable valve port size and a fifth valve 126 capable of being opened and closed, wherein the fourth valve 124 and the fifth valve 126 are connected in parallel to form a throttling assembly, one end of the throttling assembly is connected to the second part of the second heat exchanger 154, and the other end of the throttling assembly is connected to a pipeline extending through the first part of the second heat exchanger 154.
In this embodiment, in the cooling and mixed cooling mode, the refrigerant flows into the throttling assembly after flowing out of the indoor heat exchanger, wherein the fourth valve is closed, the fifth valve is opened, and the refrigerant enters the second portion of the second heat exchanger after passing through the switching valve; in the heating and mixed heating mode, after flowing out of the indoor heat exchanger, the refrigerant flows into the switching valve, the fourth valve is opened, the fifth valve is opened, the refrigerant is decompressed by the switching valve and enters the second part of the second heat exchanger, and the throttling valve in the switching assembly can ensure the circulation of the refrigerant and also can perform the decompression function on the refrigerant.
According to the above embodiment of the present invention, preferably, in the cooling mode, after the refrigerant flows out from the liquid outlet of the switching separator 156 and passes through the first heat exchanger 152 and the third valve 122, a part of the refrigerant flows back to the second stop valve 148 through the second heat exchanger 154 and the throttling assembly, and another part of the refrigerant flows back to the second stop valve 148 after flowing to the indoor unit circulation assembly 102; in the heating mode, the refrigerant flows out from the air outlet of the switching separator 156, flows out through the indoor unit circulation assembly 102, passes through the second heat exchanger 154, and then flows back to the second stop valve 148 through the throttling assembly, and flows back to the second stop valve 148 after flowing to the indoor unit circulation assembly 102.
In this embodiment, during the refrigeration cycle, a portion of the refrigerant flows back to the second stop valve 148 through the second heat exchanger 154 and the throttling assembly, and another portion of the refrigerant flows back to the second stop valve 148 after flowing to the indoor unit circulation assembly 102, so as to further subcool the refrigerant in the pipeline, thereby effectively improving the refrigeration effect of the air conditioning system. During the heating cycle, after the refrigerant passes through the second heat exchanger 154, a part of the refrigerant flows back to the second stop valve 148 through the throttling assembly, and heat exchange is carried out through the first heat exchanger 152 and the second heat exchanger 154 again, so that the service efficiency of the system is improved, and the other part of the refrigerant flows to the indoor unit circulation assembly 102, and fully exchanges heat through the indoor heat exchanger, so that a good heating effect is achieved.
According to an embodiment of the present invention, preferably, in the mixed mode, when the outdoor heat exchanger 112 condenses, the refrigerant is a gas-liquid mixed refrigerant, wherein the gas-phase refrigerant enters at least one first indoor heat exchanger in the indoor unit circulation assembly 102 through the gas outlet, exchanges heat with at least one first indoor heat exchanger, and flows into the second heat exchanger 154, after the liquid-phase refrigerant sequentially passes through the first heat exchanger 152 and the third valve 122, a portion of the liquid-phase refrigerant flows back to the second stop valve 148 through the second heat exchanger 154 and the throttling assembly, and another portion of the liquid-phase refrigerant flows back to the second stop valve 148 after flowing to at least one second indoor heat exchanger; when the outdoor heat exchanger 112 is used for evaporation, the refrigerant flows into the at least one second indoor heat exchanger through the air outlet for primary heat exchange, the refrigerant flowing out of the at least one second indoor heat exchanger passes through the second heat exchanger 154, a part of the refrigerant flows to the second stop valve 148 through the throttling assembly, and the other part of the refrigerant flows to the second stop valve 148 after passing through the at least one first indoor heat exchanger.
In this embodiment, after the gas-liquid mixed refrigerant enters the switching separator 156 and is separated, the gas refrigerant enters at least one first indoor heat exchanger for heat exchange, and then further exchanges heat with the first heat exchanger 152 through the second heat exchanger 154 and flows into the outdoor unit assembly, after the liquid refrigerant sequentially passes through the first heat exchanger 152 and the third valve 122, a part of the liquid refrigerant flows back to the outdoor unit assembly through the second heat exchanger 154 and the throttling assembly, and another part of the liquid refrigerant flows back to the outdoor unit assembly after flowing to at least one second indoor heat exchanger; when the outdoor heat exchanger 112 is evaporating, the refrigerant flows into at least one second indoor heat exchanger through the air outlet to perform primary heat exchange, the refrigerant flowing out of the at least one second indoor heat exchanger passes through the second heat exchanger 154, a part of the refrigerant flows to the second stop valve 148 through the throttling component, the other part of the refrigerant flows to the second stop valve 148 through at least one first indoor heat exchanger, and a good heat exchange effect is realized, through the scheme, through the matching of the gear electromagnetic valve and the switching separator, the gas-liquid mixture is divided, an indoor mixed mode is realized, in addition, the existing valve body in the existing system is fully utilized, through increasing the control on the action of the valve body before starting, the effective pressure equalizing before starting the compressor 108 is realized, meanwhile, the gear positions of the heat exchangers can be controlled and switched, so as to meet different combined load requirements, and ensure the starting reliability of, thereby ensuring that the compressor 108 operates stably.
As shown in fig. 2, according to an embodiment of the second aspect of the present invention, there is provided an air-conditioning pressure difference balancing method, which is used in the air-conditioning pressure difference balancing system of any one of the embodiments of the first aspect of the present invention, and includes:
step S202, receiving an adjusting signal, and adjusting the operation mode of the air conditioner according to the adjusting signal;
step S204, receiving a control signal for controlling the start or stop of the air conditioner;
in step S206, the first valve 118, the second valve 120, and each shift position solenoid valve of the outdoor circulation module in the air conditioner are controlled to open and close, and the switching valve of the switching module 104 connected to the outdoor circulation module is controlled to open and close, according to the control signal.
According to the air conditioner differential pressure balancing method provided by the embodiment of the invention, the air conditioner can be switched to the corresponding operation mode according to the adjusting signal, then the effective pressure equalization before the compressor 108 is started is realized by increasing the control on the valve body action before starting by utilizing the existing valve body in the existing system, and meanwhile, the gear of the heat exchanger can be controlled and switched to meet the requirements of different combined loads, ensure the starting reliability of the compressor 108 and further ensure the stable operation of the compressor 108.
When a user uses the air conditioner, the air conditioner is turned on or off by using a remote controller, before the air conditioner is turned on or turned off, the control signal is firstly converted into an adjusting signal, and an operation mode to be performed by the air conditioner is prepared, such as the adjustment of the opening and closing of a first valve, a second valve and each gear electromagnetic valve of an outdoor circulation assembly in the air conditioner and the control of the opening and closing of a switching valve in a switching assembly connected with the outdoor circulation assembly, so that a stable and reliable environment is provided for the opening and closing of the air conditioner.
As shown in fig. 1, according to the above embodiment of the present invention, preferably, when the adjustment signal received by the air conditioner is a cooling signal, the air conditioner is switched to a cooling mode, the first port a of the four-way valve 110 is communicated with the second port b, and the third port c of the four-way valve 110 is communicated with the fourth port d; if the control signal is the start signal, opening the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve; when the first delay time after the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve are opened is greater than a first preset time, closing the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve, and opening the compressor 108; if the control signal is the stop signal, the compressor 108 is turned off, and when a second delay time after the compressor 108 is turned off is greater than a second preset time, the first valve 118, the second valve 120, the switching valve, and each gear electromagnetic valve are opened.
In this embodiment, during a refrigeration cycle, the first port a of the four-way valve 110 is communicated with the second port b, the third port c of the four-way valve 110 is communicated with the fourth port d, before the compressor 108 is started, the first valve 118, the second valve 120, the switching valve and each gear solenoid valve are opened to rapidly balance the high-low pressure difference of the system, when the duration of the opening reaches a first preset time, the first valve 118, the second valve 120, the switching valve and each gear solenoid valve are closed, then the compressor 108 is started to prevent the compressor 108 from pressure difference, and after the compressor 108 is started, all the above valves are operated according to a normal control logic. After the compressor 108 is turned off, if the duration is longer than a second preset time, the first valve 118, the second valve 120, the switching valve and the solenoid valve of each gear are controlled to be opened, so that effective pressure equalization before the compressor 108 is turned on is realized, and the reliability of starting the compressor 108 is ensured.
As shown in fig. 3, according to an embodiment of the present invention, preferably, when the adjustment signal received by the air conditioner is a heating signal, the air conditioner is switched to a heating mode, the first port a of the four-way valve 110 is communicated with the third port c, and the second port b of the four-way valve 110 is communicated with the fourth port d; if the control signal is a start signal, opening the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve; when the first delay time after the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve are opened is greater than a first preset time, closing the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve, and opening the compressor 108; if the control signal is the stop signal, the compressor 108 is turned off, a second delay time after the compressor 108 is turned off is determined, and when the second delay time is greater than a second preset time, the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve are opened.
In this embodiment, during a heating cycle, the first port a of the four-way valve 110 is communicated with the third port c, the second port b of the four-way valve 110 is communicated with the fourth port d, before the compressor 108 is started, the first valve 118, the second valve 120, the switching valve and each gear solenoid valve are opened to rapidly balance the high-low pressure difference of the system, when the duration of the opening reaches a first preset time, the first valve 118, the second valve 120, the switching valve and each gear solenoid valve are closed, then the compressor 108 is started to prevent the compressor 108 from being started with pressure difference, and after the compressor 108 is started, all the valves are operated according to a normal control logic. After the compressor 108 is turned off, if the duration time is longer than a second preset time, the first valve 118, the second valve 120, the switching valve and the solenoid valve of each gear are controlled to be opened so as to quickly balance the high-low pressure difference of the system, the compressor 108 is started without pressure difference, the refrigerant absorbs energy in the outdoor circulation assembly, and releases energy in the indoor circulation assembly, so that the indoor heating effect is achieved.
As shown in fig. 4, according to an embodiment of the present invention, preferably, when the adjustment signal received by the air conditioner is a mixed cooling signal, the air conditioner is switched to a mixed cooling mode, the first port a and the second port b of the four-way valve 110 are communicated, and the third port c and the fourth port d of the four-way valve 110 are communicated; if the control signal is a start signal, opening the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve; when the first delay time after the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve are opened is greater than a first preset time, closing the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve, and opening the compressor 108; if the control signal is a stop signal, the compressor 108 is turned off, and when a second delay time after the compressor 108 is turned off is longer than a second preset time, the first valve 118, the second valve 120, the switching valve and at least one gear electromagnetic valve are opened, wherein the number of the opened gear electromagnetic valves is smaller than the total number of the gear electromagnetic valves.
In this embodiment, during a hybrid refrigeration cycle, the first port a and the second port b of the four-way valve 110 are communicated, the third port c and the fourth port d of the four-way valve 110 are communicated, before the compressor 108 is started, the first valve 118, the second valve 120, the switching valve and each gear solenoid valve are opened to rapidly balance the high-low pressure difference of the system, when the duration of the opening reaches a first preset time, the first valve 118, the second valve 120, the switching valve and each gear solenoid valve are closed, then the compressor 108 is started to prevent the compressor 108 from pressure difference, and after the compressor 108 is started, all the above valves are operated according to a normal control logic. After the compressor 108 is closed, if the duration is longer than a second preset time, the first valve 118, the second valve 120, the switching valve and the partial gear electromagnetic valves are controlled to be opened, so that effective pressure equalization before the compressor 108 is opened is achieved, and the reliability of starting the compressor 108 is ensured, wherein the number of the opened gear electromagnetic valves is smaller than the total number of the gear electromagnetic valves, the system operation efficiency is improved, the refrigerant releases a part of energy in the outdoor circulation assembly, and absorbs a part of energy in the indoor space and releases a part of energy by switching the shunting of the separator, so that mixed refrigeration is achieved.
As shown in fig. 5, according to an embodiment of the present invention, preferably, when the adjustment signal received by the air conditioner is a mixed heating signal, the air conditioner is switched to the mixed heating mode to communicate the first port a and the third port c of the four-way valve 110, and to communicate the second port b and the fourth port d of the four-way valve 110; if the control signal is a start signal, opening the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve; when the first delay time after the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve are opened is greater than a first preset time, closing the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve, and opening the compressor 108; if the control signal is the stop signal, the compressor 108 is turned off, a second delay time after the compressor 108 is turned off is determined, and when the second delay time is greater than a second preset time, the first valve 118, the second valve 120, the switching valve and each gear electromagnetic valve are opened.
In this embodiment, during a hybrid heating cycle, the first port a and the third port c of the four-way valve 110 are communicated, the second port b and the fourth port d of the four-way valve 110 are communicated, before the compressor 108 is started, the first valve 118, the second valve 120, the switching valve and each gear solenoid valve are opened to rapidly balance the high-low pressure difference of the system, when the duration of the opening reaches a first preset time, the first valve 118, the second valve 120, the switching valve and each gear solenoid valve are closed, then the compressor 108 is started to prevent the compressor 108 from being started with pressure difference, and after the compressor 108 is started, all the valves are operated according to a normal control logic. After the compressor 108 is closed, if the duration is longer than a second preset time, the first valve 118, the second valve 120, the switching valve and the partial gear electromagnetic valves are controlled to be opened, so that effective pressure equalization before the compressor 108 is opened is achieved, and the reliability of starting the compressor 108 is ensured, wherein the number of the opened gear electromagnetic valves is smaller than the total number of the gear electromagnetic valves, the system operation efficiency is improved, the refrigerant releases a part of energy in the outdoor circulation assembly, and the refrigerant absorbs a part of energy in a room and releases a part of energy through switching the shunting of the separator, so that the mixed heating effect is achieved.
The technical scheme of the invention is explained in detail above, and the invention provides the air conditioner differential pressure balancing system which can utilize the existing valve body in the existing system to increase the control on the action of the valve body before starting, realize effective pressure balancing before starting the compressor, ensure the starting reliability of the compressor and ensure the stable operation of the compressor.
In the description of the present specification, the terms "first", "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; the terms "connected," "mounted," "secured," and the like are to be construed broadly and include, for example, fixed connections, removable connections, or integral connections; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description of the present specification, the description of the term "one embodiment" or the like means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (15)

1. An air conditioner differential pressure equalizing system comprising: an outdoor unit circulation component (106), an indoor unit circulation component (102), and a switching component (104) connecting the outdoor unit circulation component (106) and the indoor unit circulation component (102), wherein the outdoor unit circulation component (106) comprises: a compressor (108), a four-way valve (110), an outdoor heat exchanger (112), and a gas-liquid separator (114), wherein the outdoor unit circulation unit (106) further comprises:
an oil separator (116) disposed between a first valve port (a) of the four-way valve (110) and the compressor (108), a first port of the oil separator (116) being connected to an exhaust port of the compressor (108), a second port of the oil separator (116) being connected to the first valve port (a);
a first pipeline for communicating the gas outlet of the gas-liquid separator (114) with the return gas port of the compressor (108);
a first valve (118), one end of the first valve (118) is connected with the fourth port of the oil separator (116) through a pipeline, and the other end of the first valve (118) is connected with the first pipeline through a pipeline;
a second valve (120), one end of the second valve (120) is connected with the second port of the oil separator (116) through a pipeline, and the other end of the second valve (120) is connected with the first pipeline through a pipeline;
at least one gear electromagnetic valve (150) arranged on a pipeline connecting the four-way valve (110) and the outdoor heat exchanger (112), wherein each gear electromagnetic valve (150) is connected with each partial heat exchanger of the outdoor heat exchanger (112) in series;
the outdoor unit circulation assembly (106) is connected with the switching assembly (104) through a first stop valve (146) and a second stop valve (148);
the switching component (104) comprises:
a switching separator (156) connected to the first shut-off valve (146) via a pipe, wherein the refrigerant flows into the switching separator (156) from a liquid inlet of the switching separator (156) via the first shut-off valve (146);
a first heat exchanger (152), a first part of the first heat exchanger (152) being connected to the liquid outlet of the switching separator (156);
a second heat exchanger (154) connected in series with the first heat exchanger (152), wherein the refrigerant flows through the first heat exchanger (152) from the liquid outlet and flows into the second heat exchanger (154);
a third valve (122) provided on a line connecting the first portion of the second heat exchanger (154) and the first portion of the first heat exchanger (152);
wherein the first heat exchanger (152) and the second heat exchanger (154) are both plate heat exchangers;
the switching assembly (104) further comprises: a fourth valve (124) with adjustable valve port size and a fifth valve (126) capable of opening and closing,
wherein the fourth valve (124) and the fifth valve (126) are connected in parallel to form a throttling assembly, one end of the throttling assembly being connected to the second portion of the second heat exchanger (154), the other end of the throttling assembly being connected to a conduit extending through the first portion of the second heat exchanger (154);
in the cooling mode, the refrigerant flows out of the liquid outlet of the switching separator (156), passes through the first heat exchanger (152) and the third valve (122), a part of the refrigerant flows back to the second stop valve (148) through the second heat exchanger (154) and the throttling assembly, and another part of the refrigerant flows back to the second stop valve (148) after flowing to the indoor unit circulation assembly (102).
2. The differential pressure equalizing system for an air conditioner according to claim 1,
the first stop valve (146) is connected with the outdoor heat exchanger (112), the second stop valve (148) is connected with the third valve port (c) of the four-way valve (110) through a first check valve (128), and the second stop valve (148) is connected with the outdoor heat exchanger (112) through a second check valve (130);
in a cooling mode, the refrigerant flows out of the switching assembly (104) through the second stop valve (148), flows to the third valve port (c) through the first check valve (128), and enters the gas-liquid separator (114);
in the heating mode, the refrigerant flows out of the second stop valve (148), passes through the second check valve (130) and the at least one shift solenoid valve (150), and flows into the outdoor heat exchanger (112).
3. The air conditioner differential pressure equalizing system according to claim 2, wherein a first port (a) of the four-way valve (110) is connected to the compressor (108), a second port (b) of the four-way valve (110) is connected to the first cut-off valve (146), a third port (c) of the four-way valve (110) is connected to a first end of the outdoor heat exchanger (112), and a fourth port (d) of the four-way valve (110) is connected to an air inlet of the gas-liquid separator (114).
4. The differential pressure equalizing system for air conditioners as claimed in claim 3, wherein the outdoor unit circulating assembly (106) further comprises:
a second pipeline, which communicates the first valve port (a) and the second port;
a first capillary (140) in series with the first valve (118) between the first line and the fourth port; and
a second capillary (142) in series with the second valve (120) between the first and second lines.
5. The differential pressure equalizing system for air conditioners as claimed in claim 4, wherein the outdoor unit circulating assembly (106) further comprises:
one end of the oil return pipeline is connected with an air return port of the compressor (108), and the other end of the oil return pipeline is connected with a third port of the oil separator (116);
and the oil return capillary tube (144) is arranged on the oil return pipeline, and the oil in the oil separator (116) is discharged from the third port and flows back to the compressor (108) from the air return port through the oil return capillary tube (144).
6. The differential pressure equalizing system for air conditioners as claimed in claim 5, wherein the outdoor unit circulating assembly (106) further comprises:
and the third check valve (132) is arranged on a pipeline of a main line which is communicated with the second valve port (b) and is formed by each branch of the at least one gear electromagnetic valve (150), and the refrigerant flows out from the second valve port (b), passes through the third check valve (132) and the at least one gear electromagnetic valve (150) and flows into the outdoor heat exchanger (112).
7. The differential pressure equalizing system for air conditioners as claimed in claim 6, wherein the outdoor unit circulating assembly (106) further comprises:
the fourth check valve (134) is arranged on a pipeline communicated with the outlet of the outdoor heat exchanger (112) and the second valve port (b), and the refrigerant flows out of the outdoor heat exchanger (112) and flows to the second valve port (b) through the fourth check valve (134) in the heating mode;
and the fifth check valve (136) is arranged on a pipeline communicated with the outlet of the outdoor heat exchanger (112) and the first stop valve (146), and the refrigerant flows out of the outdoor heat exchanger (112) and flows to the first stop valve (146) through the fifth check valve (136) in the refrigeration mode.
8. The differential pressure equalizing system for air conditioners as claimed in claim 7, wherein the outdoor unit circulating assembly (106) further comprises:
and the sixth check valve (138) is arranged in a pipeline which communicates the third valve port (c) with the first stop valve (146), and the refrigerant flows out from the third valve port (c) and flows to the first stop valve (146) through the sixth check valve (138) in the heating mode.
9. The differential pressure equalizing system for an air conditioner according to claim 1,
in the heating mode, the refrigerant flows out from the air outlet of the switching separator (156), flows out through the indoor unit circulation assembly (102), passes through the second heat exchanger (154), then flows back to the second stop valve (148) through the throttling assembly, and flows back to the second stop valve (148) after flowing to the indoor unit circulation assembly (102).
10. The differential pressure equalizing system for an air conditioner according to claim 1, wherein, in the mixing mode,
when the outdoor heat exchanger (112) condenses, the refrigerant is a gas-liquid mixed refrigerant, wherein a gaseous refrigerant enters at least one first indoor heat exchanger in the indoor unit circulation assembly (102) through the gas outlet, exchanges heat with the at least one first indoor heat exchanger and flows into the second heat exchanger (154), a liquid refrigerant sequentially passes through the first heat exchanger (152) and the third valve (122), a part of the liquid refrigerant flows back to the second stop valve (148) through the second heat exchanger (154) and the throttling assembly, and the other part of the liquid refrigerant flows back to the second stop valve (148) after flowing to the at least one second indoor heat exchanger;
when the outdoor heat exchanger (112) is used for evaporation, the refrigerant flows into the at least one second indoor heat exchanger through the air outlet to perform primary heat exchange, the refrigerant flowing out of the at least one second indoor heat exchanger passes through the second heat exchanger (154), a part of the refrigerant flows to the second stop valve (148) through the throttling assembly, and the other part of the refrigerant flows to the second stop valve (148) after passing through the at least one first indoor heat exchanger.
11. A method for balancing a differential pressure of an air conditioner, which is used in the differential pressure balancing system of any one of claims 1 to 10, comprising:
receiving an adjusting signal, and adjusting the operation mode of the air conditioner according to the adjusting signal;
receiving a control signal for controlling the start or stop of the air conditioner;
and controlling the opening and closing of a first valve (118), a second valve (120), each gear position electromagnetic valve (150) of an outdoor circulation assembly in the air conditioner and the opening and closing of a switching valve in a switching assembly (104) connected with the outdoor circulation assembly according to the control signals.
12. The method for balancing air conditioning pressure difference according to claim 11, wherein when the adjustment signal received by the air conditioner is a cooling signal, the air conditioner is switched to a cooling mode, the first port (a) and the second port (b) of the four-way valve (110) are communicated, and the third port (c) and the fourth port (d) of the four-way valve (110) are communicated;
if the control signal is an activation signal, opening the first valve (118), the second valve (120), the switching valve and each gear electromagnetic valve (150);
when a first delay time after the first valve (118), the second valve (120), the switching valve and each gear position electromagnetic valve (150) are opened is greater than a first preset time, closing the first valve (118), the second valve (120), the switching valve and each gear position electromagnetic valve (150), and opening a compressor (108);
if the control signal is a stop signal, the compressor (108) is closed, and when a second delay time after the compressor (108) is closed is longer than a second preset time, the first valve (118), the second valve (120), the switching valve and each gear electromagnetic valve (150) are opened.
13. The method for balancing air conditioning pressure difference according to claim 11, wherein when the adjustment signal received by the air conditioner is a heating signal, the air conditioner is switched to a heating mode, the first port (a) of the four-way valve (110) is communicated with the third port (c), and the second port (b) of the four-way valve (110) is communicated with the fourth port (d);
if the control signal is an activation signal, opening the first valve (118), the second valve (120), the switching valve, and each of the gear solenoid valves (150);
when a first delay time after the first valve (118), the second valve (120), the switching valve and each gear position electromagnetic valve (150) are opened is greater than a first preset time, closing the first valve (118), the second valve (120), the switching valve and each gear position electromagnetic valve (150), and opening a compressor (108);
if the control signal is a stop signal, the compressor (108) is closed, a second delay time after the compressor (108) is closed is determined, and when the second delay time is greater than a second preset time, the first valve (118), the second valve (120), the switching valve and each gear electromagnetic valve (150) are opened.
14. The method for balancing air conditioning pressure difference according to claim 11, wherein when the adjustment signal received by the air conditioner is a mixed cooling signal, the air conditioner is switched to a mixed cooling mode, the first port (a) and the second port (b) of the four-way valve (110) are communicated, and the third port (c) and the fourth port (d) of the four-way valve (110) are communicated;
if the control signal is an activation signal, opening the first valve (118), the second valve (120), the switching valve, and each of the gear solenoid valves (150);
when a first delay time after the first valve (118), the second valve (120), the switching valve and each gear position electromagnetic valve (150) are opened is greater than a first preset time, closing the first valve (118), the second valve (120), the switching valve and each gear position electromagnetic valve (150), and opening a compressor (108);
if the control signal is a stop signal, the compressor (108) is closed, and when a second delay time after the compressor (108) is closed is longer than a second preset time, the first valve (118), the second valve (120), the switching valve and the at least one gear electromagnetic valve (150) are opened, wherein the number of the opened gear electromagnetic valves (150) is smaller than the total number of the gear electromagnetic valves (150).
15. The method of balancing a differential pressure between air conditioners according to claim 11, wherein when the adjustment signal received by the air conditioner is a mixed heating signal, the air conditioner is switched to a mixed heating mode, the first port (a) and the third port (c) of the four-way valve (110) are communicated, and the second port (b) and the fourth port (d) of the four-way valve (110) are communicated;
if the control signal is an activation signal, opening the first valve (118), the second valve (120), the switching valve, and each of the gear solenoid valves (150);
when a first delay time after the first valve (118), the second valve (120), the switching valve and each gear position electromagnetic valve (150) are opened is greater than a first preset time, closing the first valve (118), the second valve (120), the switching valve and each gear position electromagnetic valve (150), and opening a compressor (108);
if the control signal is a stop signal, the compressor (108) is closed, a second delay time after the compressor (108) is closed is determined, and when the second delay time is greater than a second preset time, the first valve (118), the second valve (120), the switching valve and each gear electromagnetic valve (150) are opened.
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