CN110953755B - Air conditioning system capable of adjusting temperature and dehumidifying and control method thereof - Google Patents

Air conditioning system capable of adjusting temperature and dehumidifying and control method thereof Download PDF

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Publication number
CN110953755B
CN110953755B CN201911051672.4A CN201911051672A CN110953755B CN 110953755 B CN110953755 B CN 110953755B CN 201911051672 A CN201911051672 A CN 201911051672A CN 110953755 B CN110953755 B CN 110953755B
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China
Prior art keywords
heat exchanger
port
valve
indoor
communicated
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CN201911051672.4A
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Chinese (zh)
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CN110953755A (en
Inventor
王宝龙
石文星
刘兆濡
陈琪
吴纯凌
杨子旭
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Tsinghua University
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Tsinghua University
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Classifications

    • 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
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0003—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station characterised by a split arrangement, wherein parts of the air-conditioning system, e.g. evaporator and condenser, are in separately located units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • 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
    • 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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

The invention relates to the field of air conditioners, and provides an air conditioning system capable of adjusting temperature and dehumidifying and a control method thereof. The system comprises a compressor unit, an outdoor heat exchanger and an indoor large and small heat exchanger; the outdoor heat exchanger, the indoor large heat exchanger, the exhaust port of the compressor unit and the air suction port of the large cylinder are communicated with a first reversing valve, and the first reversing valve is used for controlling the outdoor heat exchanger to be communicated with one of the exhaust port of the compressor unit and the air suction port of the large cylinder and the indoor large heat exchanger to be communicated with the air suction port of the large cylinder and the air suction port of the compressor unit; the indoor small heat exchanger, the air suction port of the compressor unit, the air exhaust port of the compressor unit and the first reversing valve are all communicated with the second reversing valve, and the second reversing valve is used for controlling the outdoor heat exchanger or the indoor large heat exchanger to be selectively communicated with the air suction port of the small cylinder through the first reversing valve, and the indoor small heat exchanger is communicated with the air suction port of the small cylinder, the air suction port of the compressor unit and the air exhaust port of the compressor unit. The invention can meet the requirements of summer, winter and transitional seasons.

Description

Air conditioning system capable of adjusting temperature and dehumidifying and control method thereof
Technical Field
The invention relates to the technical field of air conditioners, in particular to an air conditioning system capable of adjusting temperature and dehumidifying and a control method thereof.
Background
The temperature and humidity control air conditioning system based on the high and low temperature double cold sources is a double-temperature air conditioning system for short, and is characterized in that two cold sources with different evaporating temperatures are arranged in the same air conditioning system to respectively bear indoor cold load and humidity load, so that independent control of indoor temperature and humidity is realized.
The dual-temperature air conditioning system mainly comprises the following advantages: 1. the separation of temperature and humidity control equipment is realized, so that the temperature limitation on the main cold source of the air conditioner is released. 2. Through the arrangement of the high-low temperature double cold sources, more than 85% of the total air conditioning load in summer is borne by the high-temperature cold source with the refrigerating efficiency of more than 8.0, and the energy-saving effect is remarkable.
At present, a dual-temperature air conditioning system is usually adopted in summer and winter cold areas in China, but the existing dual-temperature air conditioning system cannot realize working condition switching, can only be applied to summer working conditions but cannot be applied to winter and transitional seasons, or an additional water system is required for realizing temperature adjustment and dehumidification in transitional seasons, so that the cost is increased.
Disclosure of Invention
The present invention aims to solve at least one of the technical problems existing in the prior art or related art. Therefore, the invention provides the air conditioning system with the temperature adjustment and dehumidification functions and the control method thereof, which are simple in structure and convenient to operate, so that the requirements of three working conditions of summer, winter and transitional seasons in summer, winter and cold areas are met, the energy consumption of a building is reduced, and the energy conservation and emission reduction are realized.
The invention also provides a control method of the air conditioning system capable of adjusting temperature and dehumidifying.
According to an embodiment of the first aspect of the invention, the temperature-adjustable dehumidification air conditioning system comprises a compressor unit, an outdoor heat exchanger, an indoor large heat exchanger, an indoor small heat exchanger, a first reversing valve, a second reversing valve and an indoor fan, wherein the compressor unit comprises a large cylinder and a small cylinder; the second end of the outdoor heat exchanger is respectively communicated with the first end of the indoor large heat exchanger and the first end of the second throttle valve through the first throttle valve, and the second end of the second throttle valve is communicated with the first end of the indoor small heat exchanger;
The first end of the outdoor heat exchanger, the second end of the indoor large heat exchanger, the exhaust port of the compressor unit and the air suction port of the large cylinder are all communicated with the first reversing valve, and the first reversing valve is used for controlling the first end of the outdoor heat exchanger to be communicated with one of the exhaust port of the compressor unit and the air suction port of the large cylinder and controlling the second end of the indoor large heat exchanger to be communicated with the air suction port of the large cylinder and the air suction port of the compressor unit;
The second end of the indoor small heat exchanger, the air suction port of the compressor unit, the air exhaust port of the compressor unit and the first reversing valve are all communicated with the second reversing valve, and the second reversing valve is used for controlling the first end of the outdoor heat exchanger or the second end of the indoor large heat exchanger to be selectively communicated with the air suction port of the small cylinder through the first reversing valve and controlling the second end of the indoor small heat exchanger to be selectively communicated with the air suction port of the small cylinder, the air suction port of the compressor unit and the air exhaust port of the compressor unit; the air inlets of the compressor unit are the air inlets of the large cylinder and the small cylinder, and the air outlets of the compressor unit are the air outlets of the large cylinder and the small cylinder.
According to the temperature-adjustable dehumidification air conditioning system provided by the embodiment of the invention, the requirements of three working conditions of summer, winter and transitional seasons in summer, winter and cold areas can be met, the energy consumption of a building is reduced, and energy conservation and emission reduction are realized.
In addition, the air conditioning system capable of adjusting temperature and dehumidifying according to the embodiment of the invention can also have the following additional technical characteristics:
According to one embodiment of the invention, the system further comprises a flash tank, wherein the first throttle valve is communicated with the indoor large heat exchanger and the second throttle valve through the flash tank respectively.
According to one embodiment of the invention, the heat exchanger further comprises an intermediate heat exchanger and a third throttle valve, the second end of the first throttle valve is communicated with the second throttle valve through the high temperature side of the intermediate heat exchanger, and the second end of the first throttle valve is communicated with the indoor large heat exchanger through the third throttle valve and the low temperature side of the intermediate heat exchanger in sequence.
According to one embodiment of the invention, the second reversing valve comprises a first valve, a second valve and a third valve which are two-way valves, the second end of the indoor small heat exchanger is respectively communicated with the first port of the first valve and the first port of the second valve, the second port of the first valve is communicated with the exhaust port of the compressor unit, the second port of the second valve is respectively communicated with the air suction port of the small cylinder and the first port of the third valve, and the second port of the third valve is respectively communicated with the air suction port of the large cylinder and the first reversing valve.
According to one embodiment of the invention, the second reversing valve comprises a pneumatic two-way valve, a pneumatic three-way valve and an electromagnetic pilot valve, wherein a first port of the pneumatic two-way valve is respectively communicated with the first reversing valve and the air suction port of the large cylinder, and a second port of the pneumatic two-way valve and a first port of the pneumatic three-way valve are respectively communicated with the air suction port of the small cylinder; the second port of the pneumatic three-way valve is communicated with the second end of the indoor small heat exchanger, and the third port of the pneumatic three-way valve is communicated with the exhaust port of the compressor unit; the first signal pipe and the second signal pipe of the electromagnetic pilot valve are respectively communicated with the third port and the first port of the pneumatic three-way valve; the two side chambers of the pneumatic three-way valve are respectively communicated with the third signal pipe and the fourth signal pipe of the electromagnetic pilot valve, and the two side chambers of the pneumatic two-way valve are respectively communicated with the third signal pipe and the fourth signal pipe of the electromagnetic pilot valve.
According to one embodiment of the invention, the compressor unit is a double-cylinder parallel compressor; or the compressor unit comprises a first compressor and a second compressor which are mutually connected in parallel, wherein the first compressor is configured with the large cylinder, and the second compressor is configured with the small cylinder.
According to one embodiment of the invention, the air duct further comprises an air duct, wherein the air duct is provided with an air inlet, a first air outlet and a second air outlet; the air inlet is arranged close to the indoor fan, the indoor large heat exchanger is arranged in the air supply direction of the first air outlet, the indoor large heat exchanger and the indoor small heat exchanger are sequentially arranged in the air supply direction of the second air outlet, and the indoor large heat exchanger is positioned between the second air outlet and the indoor small heat exchanger;
Or the indoor large heat exchanger and the indoor small heat exchanger are sequentially arranged along the air supply direction of the indoor fan, and the indoor large heat exchanger is positioned between the indoor fan and the indoor small heat exchanger.
According to one embodiment of the invention, the first reversing valve is a four-way valve, a first port of the four-way valve is communicated with an exhaust port of the compressor unit, a second port of the four-way valve is communicated with the outdoor heat exchanger, a third port of the four-way valve is respectively communicated with an air suction port of the large cylinder and the second reversing valve, and a fourth port of the four-way valve is communicated with the indoor large heat exchanger.
According to one embodiment of the present invention, the first reversing valve includes a first two-way valve, a second two-way valve, a third two-way valve, and a fourth two-way valve, wherein the first port of the first two-way valve and the first port of the second two-way valve are both communicated with the exhaust port of the compressor unit, the second port of the second two-way valve and the first port of the third two-way valve are both communicated with the first end of the outdoor heat exchanger, the second port of the third two-way valve and the first port of the fourth two-way valve are both communicated with the air suction port of the large cylinder and the second reversing valve, and the second port of the fourth two-way valve and the second port of the first two-way valve are both communicated with the indoor large heat exchanger.
According to a second aspect of the present invention, a control method of an air conditioning system capable of temperature-adjustable dehumidification includes the steps of:
Indoor high humidity working condition in summer:
adjusting the first reversing valve to communicate a first end of the outdoor heat exchanger with an exhaust port of the compressor unit and a second end of the indoor large heat exchanger with an intake port of the large cylinder;
the second reversing valve is regulated so as to disconnect the second end of the indoor large heat exchanger from the air suction port of the small cylinder and to communicate the second end of the indoor small heat exchanger with the air suction port of the small cylinder;
Winter working conditions:
adjusting the first reversing valve to communicate a first end of the outdoor heat exchanger with the suction port of the large cylinder and a second end of the indoor large heat exchanger with the exhaust port of the compressor unit;
the second reversing valve is regulated so as to enable the first end of the outdoor heat exchanger to be communicated with the air suction port of the small cylinder through the first reversing valve and enable the second end of the indoor small heat exchanger to be communicated with the air discharge port of the compressor unit;
and (5) working conditions in transitional seasons:
Adjusting a first reversing valve to communicate a first end of the outdoor heat exchanger with an exhaust port of the compressor unit and a second end of the indoor large heat exchanger with an air suction port of the large cylinder;
And adjusting a second reversing valve to communicate the second end of the indoor large heat exchanger with the air suction port of the small cylinder through the first reversing valve and communicate the second end of the indoor small heat exchanger with the air discharge port of the compressor unit.
According to one embodiment of the invention, the method further comprises the steps of:
indoor low humidity condition in summer:
adjusting the first reversing valve to communicate a first end of the outdoor heat exchanger with an exhaust port of the compressor unit and a second end of the indoor large heat exchanger with an intake port of the large cylinder;
And the second reversing valve is regulated so as to enable the second end of the indoor large heat exchanger to be communicated with the air suction port of the small cylinder through the first reversing valve and enable the second end of the indoor small heat exchanger to be communicated with the air suction port of the compressor unit.
According to one embodiment of the invention, the step of adjusting the first reversing valve to communicate the first end of the outdoor heat exchanger with the exhaust port of the compressor unit and the second end of the indoor large heat exchanger with the intake port of the large cylinder comprises: a first port and a second port of the four-way valve are communicated, and a third port and a fourth port of the four-way valve are communicated;
The step of adjusting the first reversing valve to communicate the first end of the outdoor heat exchanger with the suction port of the large cylinder and the second end of the indoor large heat exchanger with the discharge port of the compressor unit, includes: and communicating the second port and the third port of the four-way valve, and communicating the first port and the fourth port of the four-way valve.
According to one embodiment of the invention, the step of adjusting the second reversing valve to disconnect the second end of the indoor large heat exchanger from the suction port of the small cylinder and to communicate the second end of the indoor small heat exchanger with the suction port of the small cylinder comprises: opening the second valve, and closing the first valve and the third valve;
The step of adjusting the second reversing valve to communicate the second end of the indoor large heat exchanger with the suction port of the small cylinder through the first reversing valve and to communicate the second end of the indoor small heat exchanger with the suction port of the compressor unit includes: opening the second valve and the third valve, and closing the first valve;
The step of adjusting the second reversing valve to communicate the first end of the outdoor heat exchanger with the suction port of the small cylinder through the first reversing valve and to communicate the second end of the indoor small heat exchanger with the discharge port of the compressor unit includes: opening the first valve and the third valve, and closing the second valve.
According to one embodiment of the invention, the step of adjusting the second reversing valve to disconnect the second end of the indoor large heat exchanger from the suction port of the small cylinder and to communicate the second end of the indoor small heat exchanger with the suction port of the small cylinder comprises: powering off the electromagnetic pilot valve to enable the first port and the second port of the pneumatic two-way valve to be closed and the first port and the second port of the pneumatic three-way valve to be communicated;
The step of adjusting the second reversing valve to communicate the first end of the outdoor heat exchanger with the suction port of the small cylinder through the first reversing valve and to communicate the second end of the indoor small heat exchanger with the discharge port of the compressor unit includes: electrifying and sucking the electromagnetic pilot valve to open the pneumatic two-way valve, and communicating a second port and a third port of the pneumatic three-way valve;
The step of adjusting the second reversing valve to communicate the second end of the indoor large heat exchanger with the suction port of the small cylinder through the first reversing valve and to communicate the second end of the indoor small heat exchanger with the exhaust port of the compressor unit includes: electrifying and sucking the electromagnetic pilot valve to open the pneumatic two-way valve, and communicating a second port and a third port of the pneumatic three-way valve;
The third signal pipe of the electromagnetic pilot valve is communicated with a chamber adjacent to the second port of the pneumatic three-way valve, and the fourth signal pipe of the electromagnetic pilot valve is communicated with a chamber far away from the second port of the pneumatic three-way valve; the two-side chambers of the pneumatic two-way valve are a first chamber and a second chamber respectively, and the first chamber and the second chamber are sequentially arranged along the closing direction of the sliding valve of the pneumatic two-way valve; and a third signal pipe of the electromagnetic pilot valve is communicated with the second chamber, and a fourth signal pipe of the electromagnetic pilot valve is communicated with the first chamber.
The above technical solutions in the embodiments of the present invention have at least one of the following technical effects:
The temperature-adjustable dehumidifying air conditioning system can meet the requirements of three working conditions of summer, winter and transitional seasons in summer, winter and cold areas by adjusting the first reversing valve and the second reversing valve: in summer, the exhaust gas of the indoor large heat exchanger and the indoor small heat exchanger respectively flow into the large cylinder and the small cylinder to be independently compressed, meanwhile, the inlet liquid of the indoor large heat exchanger is throttled once, and the inlet liquid of the indoor small heat exchanger is throttled twice to realize independent treatment of cold load and wet load, namely, the indoor large heat exchanger and the indoor small heat exchanger are respectively used as a high-temperature evaporator and a low-temperature evaporator to realize indoor double evaporation temperature, the indoor large heat exchanger is used for bearing indoor sensible heat cold load to realize cooling, and the indoor small heat exchanger is used for bearing indoor latent heat wet load to realize dehumidification. The exhaust gas of the compressor unit respectively enters the indoor large heat exchanger and the indoor small heat exchanger in winter, so that the convection air supply and heating of the indoor double condensers can be realized, the total indoor condenser area can be increased, the condensation temperature can be reduced, the energy efficiency ratio of the system can be improved, and the indoor temperature can be more uniform and the comfort of a user can be improved by adopting two condensers, namely the indoor large heat exchanger and the indoor small heat exchanger to realize the double-position air supply and heating. The indoor large heat exchanger and the indoor small heat exchanger are respectively communicated with the air suction port and the air discharge port of the compressor unit in transitional seasons, that is, the indoor large heat exchanger is used as an evaporator to realize indoor cooling and dehumidification, and the indoor small heat exchanger is used as a condenser to realize reheating of dehumidified air, so that cold caused by pure cooling and dehumidification in transitional seasons can be avoided, and reheat energy consumption can be saved.
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
In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings used in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are some embodiments of the invention, and other drawings can be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of an air conditioning system with temperature and humidity adjustment according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of another temperature-adjustable dehumidification air conditioning system in accordance with an embodiment of the present disclosure;
FIG. 3 is a schematic view of an air conditioning system with temperature and humidity adjustment according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of an air conditioning system with temperature and humidity adjustable in summer under high humidity conditions in the summer according to an embodiment of the present invention;
FIG. 5 is a schematic diagram of an air conditioning system with temperature and humidity adjustment in winter conditions according to an embodiment of the present invention;
FIG. 6 is a schematic diagram of an air conditioning system with temperature adjustment and dehumidification in a transitional season operation in accordance with an embodiment of the present invention;
FIG. 7 is a schematic diagram of an air conditioning system with temperature and humidity adjustable in summer under low humidity conditions in the summer according to an embodiment of the present invention;
FIG. 8 is a schematic diagram of a second reversing valve according to an embodiment of the present invention;
FIG. 9 is a schematic diagram of another temperature-adjustable dehumidification air conditioning system under a summer indoor high humidity condition in accordance with an embodiment of the present invention;
fig. 10 is a schematic structural diagram of another air conditioning system with temperature adjustment and dehumidification function under winter conditions according to an embodiment of the present invention.
Reference numerals:
1.1: a large cylinder; 1.2: a small cylinder; 2: a four-way valve; 3: an outdoor heat exchanger;
4: a first throttle valve; 5: a flash tank; 6: a second throttle valve;
7.1: an indoor large heat exchanger; 7.2: an indoor small heat exchanger; 8.1: a first valve;
8.2: a second valve; 8.3: a third valve; 9: an indoor fan;
10: a pneumatic two-way valve; 10.1, a first port of a pneumatic two-way valve;
10.2, a second port of the pneumatic two-way valve; 11: a pneumatic three-way valve;
11.1: a first port of the pneumatic three-way valve; 11.2: a second port of the pneumatic three-way valve;
11.3: a third port of the pneumatic three-way valve; 12: an electromagnetic pilot valve;
12.1: a first signal pipe; 12.2: a second signal tube; 12.3: a third signal tube;
12.4: a fourth signal tube; 13: an intermediate heat exchanger; 14: and a third throttle valve.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be clearly described below with reference to the accompanying drawings, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments. All other embodiments, based on the embodiments of the invention, which would be apparent to one of ordinary skill in the art without making any inventive effort are intended to be within the scope of the invention.
In the description of the embodiments of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the embodiments of the present invention and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the embodiments of the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In describing embodiments of the present invention, it should be noted that, unless explicitly stated and limited otherwise, the terms "coupled," "coupled," and "connected" should be construed broadly, and may be either a fixed connection, a removable connection, or an integral connection, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in embodiments of the present invention will be understood in detail by those of ordinary skill in the art.
In embodiments of the invention, unless expressly specified and limited otherwise, a first feature "up" or "down" on a second feature may be that the first and second features are in direct contact, or that the first and second features are in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., 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 embodiments of the present invention. In this specification, schematic representations of the above terms are not necessarily directed 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. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.
As shown in fig. 1, the embodiment of the invention provides an air conditioning system capable of adjusting temperature and dehumidifying, which comprises a compressor unit, an outdoor heat exchanger 3, an indoor large heat exchanger 7.1, an indoor small heat exchanger 7.2, a first reversing valve, a second reversing valve and an indoor fan 9, wherein the compressor unit comprises a large air cylinder 1.1 and a small air cylinder 1.2; the second end of the outdoor heat exchanger 3 is respectively communicated with the first end of the indoor large heat exchanger 7.1 and the first end of the second throttle valve 6 through the first throttle valve 4, and the second end of the second throttle valve 6 is communicated with the first end of the indoor small heat exchanger 7.2; the first end of the outdoor heat exchanger 3, the second end of the indoor large heat exchanger 7.1, the air outlet of the compressor unit and the air inlet of the large cylinder 1.1 are all communicated with a first reversing valve, and the first reversing valve is used for controlling the first end of the outdoor heat exchanger 3 to be communicated with the air outlet of the compressor unit and the air inlet of the large cylinder 1.1 in a selected manner and controlling the second end of the indoor large heat exchanger 7.1 to be communicated with the air inlet of the large cylinder 1.1 and the air outlet of the compressor unit in a selected manner; the second end of the indoor small heat exchanger 7.2, the air suction port of the compressor unit, the air exhaust port of the compressor unit and the first reversing valve are all communicated with the second reversing valve, the second reversing valve is used for controlling the first end of the outdoor heat exchanger 3 or the second end of the indoor large heat exchanger 7.1 to be selectively communicated with the air suction port of the small cylinder 1.2 through the first reversing valve, that is, the second reversing valve is used for controlling the first end of the outdoor heat exchanger 3 to be communicated with or disconnected from the air suction port of the small cylinder 1.2 through the first reversing valve, or controlling the second end of the indoor large heat exchanger 7.1 to be communicated with or disconnected from the air suction port of the small cylinder 1.2 through the first reversing valve; in addition, the second reversing valve is also used for controlling the second end of the indoor small heat exchanger 7.2 to be communicated with the air suction port of the small cylinder 1.2, the air suction port of the compressor unit and the air discharge port of the compressor unit; the air suction port of the compressor unit is the air suction port of the large cylinder 1.1 and the air suction port of the small cylinder 1.2, and the air discharge port of the compressor unit is the air discharge port of the large cylinder 1.1 and the air discharge port of the small cylinder 1.2. It should be noted that, the compressor unit may be a single double-cylinder parallel compressor, or may include a first compressor and a second compressor connected in parallel, where the first compressor is configured with a large cylinder 1.1, and the second compressor is configured with a small cylinder 1.2.
The following describes a control method of the air conditioning system capable of adjusting temperature and dehumidifying in summer, winter and transitional seasons in the embodiment of the invention:
High humidity and high pressure ratio working condition in summer: adjusting the first reversing valve to communicate the first end of the outdoor heat exchanger 3 with the exhaust port of the compressor unit and the second end of the indoor large heat exchanger 7.1 with the air suction port of the large cylinder 1.1; the second reversing valve is adjusted to disconnect the second end of the indoor large heat exchanger 7.1 from the suction port of the small cylinder 1.2 and to communicate the second end of the indoor small heat exchanger 7.2 with the suction port of the small cylinder 1.2. Under the working condition, the outdoor heat exchanger 3 serves as a condenser, the indoor large heat exchanger 7.1 serves as a high-temperature evaporator, and the indoor small heat exchanger 7.2 serves as a low-temperature evaporator. The system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit, namely the large cylinder 1.1 and the small cylinder 1.2, flows into the outdoor heat exchanger 3 through the first reversing valve to release heat to the outside, and the gaseous refrigerant after releasing heat and reducing temperature is converted into liquid refrigerant to flow into the first throttle valve 4 from the outdoor heat exchanger 3. The liquid refrigerant is divided into two paths after being throttled and cooled by the first throttle valve 4, one path directly flows into the indoor large heat exchanger 7.1 to absorb heat to indoor air, and the other path flows into the indoor small heat exchanger 7.2 to absorb heat to indoor air after being throttled and cooled again by the second throttle valve 6. In the process, indoor air sucked by the indoor fan 9 is firstly blown to the indoor large heat exchanger 7.1, and the air cooled by the indoor large heat exchanger 7.1 flows to the indoor small heat exchanger 7.2 for cooling and dehumidifying. The liquid refrigerant flowing through the indoor large heat exchanger 7.1 absorbs heat and rises temperature to be converted into gaseous refrigerant and then flows into the air suction port of the large cylinder 1.1 again through the first reversing valve, and meanwhile, the liquid refrigerant flowing through the indoor small heat exchanger 7.2 absorbs heat and rises temperature to be converted into gaseous refrigerant and then flows into the air suction port of the small cylinder 1.2 again through the second reversing valve.
Winter working conditions: adjusting the first reversing valve to communicate the first end of the outdoor heat exchanger 3 with the air suction port of the large cylinder 1.1 and the second end of the indoor large heat exchanger 7.1 with the air discharge port of the compressor unit; the second reversing valve is adjusted to communicate the first end of the outdoor heat exchanger 3 with the suction opening of the small cylinder 1.2 via the first reversing valve and to communicate the second end of the indoor small heat exchanger 7.2 with the discharge opening of the compressor block. In this operating mode, the outdoor heat exchanger 3 serves as an evaporator, and the indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2 serve as condensers. The system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit, namely the large cylinder 1.1 and the small cylinder 1.2, is divided into two paths, one path of the gaseous refrigerant flows into the indoor large heat exchanger 7.1 through the first reversing valve to release heat indoors, and the other path of gaseous refrigerant flows into the indoor small heat exchanger 7.2 through the second reversing valve to release heat indoors. In the process, indoor air sucked by the indoor fan 9 is firstly blown to the indoor large heat exchanger 7.1, is heated by the indoor large heat exchanger 7.1, and then flows to the indoor small heat exchanger 7.2 for heating. At this time, the second throttle valve 6 is fully opened, the liquid refrigerant flowing out of the indoor small heat exchanger 7.2 passes through the second throttle valve 6, then is mixed with the liquid refrigerant flowing out of the indoor large heat exchanger 7.1, and enters the first throttle valve 4, the low-temperature liquid refrigerant throttled and cooled by the first throttle valve 4 flows into the outdoor heat exchanger 3 to absorb heat from the outdoor, the liquid refrigerant in the outdoor heat exchanger 3 absorbs heat and rises in temperature to be converted into gaseous refrigerant, and then flows into the air inlets of the compressor units, namely the large air cylinder 1.1 and the small air cylinder 1.2 again through the first reversing valve.
And (5) working conditions in transitional seasons: adjusting the first reversing valve to communicate the first end of the outdoor heat exchanger 3 with the exhaust port of the compressor unit and the second end of the indoor large heat exchanger 7.1 with the air suction port of the large cylinder 1.1; the second reversing valve is adjusted to communicate the second end of the indoor large heat exchanger 7.1 with the suction port of the small cylinder 1.2 through the first reversing valve and to communicate the second end of the indoor small heat exchanger 7.2 with the discharge port of the compressor unit. Under the working condition, the outdoor heat exchanger 3 and the indoor small heat exchanger 7.2 are both used as condensers, and the indoor large heat exchanger 7.1 is used as an evaporator. The system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit, namely the large cylinder 1.1 and the small cylinder 1.2, is divided into two paths, one path of the gaseous refrigerant flows into the outdoor heat exchanger 3 through the first reversing valve to release heat outdoors, and the other path of gaseous refrigerant flows into the indoor small heat exchanger 7.2 through the second reversing valve to release heat indoors. The gaseous refrigerant flowing through the outdoor heat exchanger 3 is converted into liquid refrigerant by heat release and temperature reduction, and then flows into the first throttle valve 4. At the same time, the gaseous refrigerant flowing through the indoor small heat exchanger 7.2 releases heat, cools down and changes into liquid refrigerant and then flows into the second throttle valve 6. The liquid refrigerant throttled and cooled by the first throttle valve 4 and the second throttle valve 6 is mixed and flows into the indoor large heat exchanger 7.1 to absorb heat indoors. In the process, indoor air sucked by the indoor fan 9 is firstly blown to the indoor large heat exchanger 7.1, and the air cooled and dehumidified by the indoor large heat exchanger 7.1 flows to the indoor small heat exchanger 7.2 for heating. The liquid refrigerant flowing through the indoor large heat exchanger 7.1 absorbs heat and rises temperature to be converted into gaseous refrigerant, then the gaseous refrigerant is divided into two paths through the first reversing valve, one path of the gaseous refrigerant directly flows into the air suction port of the large cylinder 1.1 again, and the other path of gaseous refrigerant flows into the air suction port of the small cylinder 1.2 again through the second reversing valve.
Therefore, the air conditioning system with the temperature adjustable and dehumidification functions can meet the requirements of three working conditions of summer, winter and transitional seasons in summer, winter and winter cold areas by adjusting the first reversing valve and the second reversing valve: in summer, the exhaust gas of the indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2 respectively flow into the large cylinder 1.1 and the small cylinder 1.2 to be compressed independently, meanwhile, the inlet liquid of the indoor large heat exchanger 7.1 is throttled once, and the inlet liquid of the indoor small heat exchanger 7.2 is throttled twice to realize independent treatment of cold load and wet load, namely, the indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2 are respectively used as a high-temperature evaporator and a low-temperature evaporator to realize indoor double evaporation temperature. Therefore, the indoor large heat exchanger 7.1 can be used for bearing indoor sensible heat and cold load to realize cooling, and the indoor small heat exchanger 7.2 can be used for bearing indoor latent heat and wet load to realize dehumidification. The exhaust gas of the compressor unit respectively enters the indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2 in winter, so that the indoor double-condenser convection air supply heating can be realized, the indoor total condenser area can be increased, the condensing temperature can be reduced, the energy efficiency ratio of the system can be improved, and the two condensers, namely the indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2, are adopted to realize the double-position air supply heating, so that the indoor temperature can be more uniform, and the comfort of a user can be improved. The indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2 are respectively communicated with the air suction port and the air discharge port of the compressor unit in transitional seasons, that is, the indoor large heat exchanger 7.1 is used as an evaporator to realize indoor cooling and dehumidification, and the indoor small heat exchanger 7.2 is used as a condenser to realize reheating of dehumidified air, so that cold caused by pure cooling and dehumidification in transitional seasons can be avoided, and reheat energy consumption can be saved.
In addition, considering that the conditions of low humidity and small pressure ratio also occur in the summer room, the control method of the temperature-adjustable dehumidification air conditioning system in the embodiment of the invention further comprises the following steps:
Indoor low humidity in summer, little pressure ratio operating mode: adjusting the first reversing valve to communicate the first end of the outdoor heat exchanger 3 with the exhaust port of the compressor unit and the second end of the indoor large heat exchanger 7.1 with the air suction port of the large cylinder 1.1; the second reversing valve is adjusted to communicate the second end of the indoor large heat exchanger 7.1 with the suction port of the small cylinder 1.2 through the first reversing valve and to communicate the second end of the indoor small heat exchanger 7.2 with the suction port of the compressor unit. In this operating mode, the outdoor heat exchanger 3 serves as a condenser, and the indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2 serve as evaporators. The system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit, namely the large cylinder 1.1 and the small cylinder 1.2, flows into the outdoor heat exchanger 3 through the first reversing valve to release heat to the outside, and the gaseous refrigerant after releasing heat and reducing temperature is converted into liquid refrigerant to flow into the first throttle valve 4 from the outdoor heat exchanger 3. The liquid refrigerant is divided into two paths after being throttled and cooled by the first throttle valve 4, one path directly flows into the indoor large heat exchanger 7.1 to absorb heat to indoor air, and the other path flows into the indoor small heat exchanger 7.2 to absorb heat to indoor air after being throttled and cooled again by the second throttle valve 6. The liquid refrigerant flowing through the indoor large heat exchanger 7.1 absorbs heat and rises temperature to be converted into gaseous refrigerant, and then is divided into two paths through the first reversing valve, one path of the gaseous refrigerant directly flows into the air suction port of the large cylinder 1.1 again, and the other path of the gaseous refrigerant flows into the air suction port of the small cylinder 1.2 again through the second reversing valve. At the same time, the liquid refrigerant passing through the indoor small heat exchanger 7.2 absorbs heat and rises temperature to be converted into gaseous refrigerant, and then flows into the air inlets of the large cylinder 1.1 and the small cylinder 1.2 again through the second reversing valve.
Therefore, under the working conditions of low indoor humidity and low pressure ratio in summer, the system can realize double-cylinder parallel operation of the compressor unit by adjusting the first reversing valve and the second reversing valve to enable the indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2 to be communicated with the air suction port of the compressor unit. The evaporation temperatures of the large indoor heat exchanger 7.1 and the small indoor heat exchanger 7.2 are substantially the same due to the small indoor pressure ratio. And at low pressure ratios, the energy efficiency of the system is higher than that of an air conditioning system employing dual evaporators.
In addition, in order to improve the system efficiency, as shown in fig. 2, the system further comprises a flash tank 5, wherein the second end of the first throttle valve 4 is respectively communicated with the second throttle valve 6 and the indoor large heat exchanger 7.1 through the flash tank 5, that is, the second end of the first throttle valve 4 is communicated with the first port of the flash tank 5, the second port of the flash tank 5 is communicated with the second throttle valve 6, and the third port of the flash tank 5 is communicated with the indoor large heat exchanger 7.1.
The working principle of the flash tank 5 is described below by taking the working condition of high indoor humidity and high pressure ratio in summer as an example:
When the system operates, high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit flows into the outdoor heat exchanger 3 through the first reversing valve to release heat to the outside, the released and cooled gaseous refrigerant is converted into liquid refrigerant, and the liquid refrigerant flows into the first throttle valve 4 from the outdoor heat exchanger 3. The liquid refrigerant flows into the flash tank 5 after being throttled and cooled by the first throttle valve 4, and flashes saturated gas and saturated liquid. The saturated liquid generated in the flash tank 5 directly flows into the second throttle valve 6 for throttling and cooling and finally enters the indoor small heat exchanger 7.2, and the gas-liquid two-phase refrigerant generated in the flash tank 5 flows into the indoor large heat exchanger 7.1. Since the refrigerant flowing into the indoor small heat exchanger 7.2 is entirely saturated liquid, the refrigerating capacity per unit mass of the refrigerant is higher.
Of course, as shown in fig. 3, in order to improve the system efficiency, in addition to the flash tank 5, an intermediate heat exchanger 13 and a third throttle valve 14 may be provided, specifically, the second end of the first throttle valve 4 communicates with the second throttle valve 6 through the high temperature side of the intermediate heat exchanger 13, and at the same time, the second end of the first throttle valve 4 communicates with the indoor large heat exchanger 7.1 through the third throttle valve 14 and the low temperature side of the intermediate heat exchanger 13 in order. Wherein the first throttle valve 4, the second throttle valve 6 and the third throttle valve 14 may be, but are not limited to, expansion valves.
The working principle of the intermediate heat exchanger 13 is explained below:
Indoor low humidity in summer, little pressure ratio operating mode: the first throttle valve 4 is fully opened, and the second throttle valve 6 and the third throttle valve 14 are adjusted to the opening degrees having the same supercooling degree. When the system operates, high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit flows into the outdoor heat exchanger 3 through the first reversing valve to release heat to the outside, the released and cooled gaseous refrigerant is converted into liquid refrigerant, and the liquid refrigerant flows into the first throttle valve 4 from the outdoor heat exchanger 3. The liquid refrigerant is divided into two paths after passing through the first throttle valve 4, one path directly flows into the high temperature side of the intermediate heat exchanger 13, and the other path flows into the low temperature side of the intermediate heat exchanger 13 after being throttled and cooled by the third throttle valve 14. The refrigerant flowing through the high temperature side of the intermediate heat exchanger 13 is continuously subjected to heat exchange with the refrigerant flowing through the low temperature side of the intermediate heat exchanger 13, the refrigerant enters the second throttle valve 6 to be throttled again after being cooled and cooled at the high temperature side of the intermediate heat exchanger 13, and the refrigerant directly flows into the indoor large heat exchanger 7.1 after absorbing heat at the low temperature side of the intermediate heat exchanger 13. The two paths of refrigerant are kept at the same pressure when flowing through the large indoor heat exchanger 7.1 and the small indoor heat exchanger 7.2, respectively.
High humidity and high pressure ratio working condition in summer: the first throttle valve 4 is fully opened, and the second throttle valve 6 and the third throttle valve 14 are adjusted to the opening degrees having the same supercooling degree. The system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit flows into the outdoor heat exchanger 3 through the first reversing valve to release heat to the outside, and the gaseous refrigerant after releasing heat and reducing temperature is converted into liquid refrigerant to flow into the first throttle valve 4 from the outdoor heat exchanger 3. The liquid refrigerant is throttled and cooled by the first throttle valve 4 and then is divided into two paths, one path directly flows into the high-temperature side of the intermediate heat exchanger 13, and the other path flows into the low-temperature side of the intermediate heat exchanger 13 after being throttled and cooled by the third throttle valve 14. The refrigerant flowing through the high temperature side of the intermediate heat exchanger 13 is continuously subjected to heat exchange with the refrigerant flowing through the low temperature side of the intermediate heat exchanger 13, the refrigerant enters the second throttle valve 6 to be throttled again after being cooled and cooled at the high temperature side of the intermediate heat exchanger 13, and the refrigerant directly flows into the indoor large heat exchanger 7.1 after absorbing heat at the low temperature side of the intermediate heat exchanger 13. And (5) working conditions in transitional seasons: the first throttle valve 4 and the second throttle valve 6 are fully opened, and the third throttle valve 14 is adjusted to a certain opening degree. Winter working conditions: the second throttle valve 6 and the third throttle valve 14 are fully opened, and the first throttle valve 4 is adjusted to a certain opening degree. The operation process of the system under the three working conditions is the same as the above, and is not repeated here.
It should be noted that the first reversing valve in the embodiment of the present invention may be, but is not limited to, the four-way valve 2 or the combination valve. For example, when the first reversing valve is the four-way valve 2: the first port of the four-way valve 2 is communicated with an exhaust port of the compressor unit, the second port of the four-way valve 2 is communicated with the outdoor heat exchanger 3, the third port of the four-way valve 2 is respectively communicated with an air suction port of the large cylinder 1.1 and the second reversing valve, and the fourth port of the four-way valve 2 is communicated with the indoor large heat exchanger 7.1. When the first reversing valve is a combined valve, the first reversing valve comprises a first two-way valve, a second two-way valve, a third two-way valve and a fourth two-way valve, wherein the first port of the first two-way valve and the first port of the second two-way valve are communicated with an exhaust port of the compressor unit, the second port of the second two-way valve and the first port of the third two-way valve are communicated with the first end of the outdoor heat exchanger 3, the second port of the third two-way valve and the first port of the fourth two-way valve are communicated with an air suction port of the large cylinder 1.1 and the second reversing valve, and the second port of the fourth two-way valve and the second port of the first two-way valve are communicated with the indoor large heat exchanger 7.1.
Similarly, the second reversing valve in the embodiments of the present invention may be, but is not limited to, a two-way combination valve as follows.
Form one: the second reversing valve comprises a first valve 8.1, a second valve 8.2 and a third valve 8.3 which are two-way valves, the second end of the indoor small heat exchanger 7.2 is respectively communicated with the first port of the first valve 8.1 and the first port of the second valve 8.2, the second port of the first valve 8.1 is communicated with the exhaust port of the compressor unit, the second port of the second valve 8.2 is respectively communicated with the air suction port of the small cylinder 1.2 and the first port of the third valve 8.3, and the second port of the third valve 8.3 is respectively communicated with the air suction port of the large cylinder 1.1 and the first reversing valve.
Form two: as shown in fig. 8, the second reversing valve comprises a pneumatic two-way valve 10, a pneumatic three-way valve 11 and an electromagnetic pilot valve 12, wherein a first port 10.1 of the pneumatic two-way valve is respectively communicated with the first reversing valve and the air suction port of the large cylinder 1.1, and a second port 10.2 of the pneumatic two-way valve and a first port 11.1 of the pneumatic three-way valve are respectively communicated with the air suction port of the small cylinder 1.2; the second port 11.2 of the pneumatic three-way valve is communicated with the second end of the indoor small heat exchanger 7.2, and the third port 11.3 of the pneumatic three-way valve is communicated with the exhaust port of the compressor unit; the first signal tube 12.1 and the second signal tube 12.2 of the electromagnetic pilot valve 12 are respectively communicated with the third port 11.3 of the pneumatic three-way valve and the first port 11.1 of the pneumatic three-way valve; the chambers on two sides of the pneumatic three-way valve 11 are respectively communicated with a third signal pipe 12.3 and a fourth signal pipe 12.4 of the electromagnetic pilot valve 12, and the chambers on two sides of the pneumatic two-way valve are respectively communicated with the third signal pipe 12.3 and the fourth signal pipe 12.4 of the electromagnetic pilot valve 12.
It should be noted that the solenoid pilot valve 12 may be connected to the two chambers of the pneumatic three-way valve 11 and the pneumatic two-way valve 10 in various manners, for example: the first mode is that a third signal pipe 12.3 of the electromagnetic pilot valve 12 is communicated with a chamber adjacent to a second port of the pneumatic three-way valve 11, and a fourth signal pipe 12.4 of the electromagnetic pilot valve 12 is communicated with a chamber far away from the second port of the pneumatic three-way valve 11; the two side chambers of the pneumatic two-way valve 10 are a first chamber and a second chamber respectively, and the first chamber and the second chamber are sequentially arranged along the closing direction of the slide valve of the pneumatic two-way valve 10; the third signal tube 12.3 of the solenoid pilot valve 12 communicates with the second chamber and the fourth signal tube 12.4 of the solenoid pilot valve 12 communicates with the first chamber. The third signal tube 12.3 of the electromagnetic pilot valve 12 is communicated with a chamber far away from the second port in the pneumatic three-way valve 11, and the fourth signal tube 12.4 of the electromagnetic pilot valve 12 is communicated with a chamber near the second port in the pneumatic three-way valve 11; the two side chambers of the pneumatic two-way valve 10 are a first chamber and a second chamber respectively, and the first chamber and the second chamber are sequentially arranged along the closing direction of the sliding valve in the pneumatic two-way valve 10; the third signal tube 12.3 of the solenoid pilot valve 12 communicates with the first chamber and the fourth signal tube 12.4 of the solenoid pilot valve 12 communicates with the second chamber.
The following describes a control method of the air conditioning system with temperature adjustment and dehumidification in summer, winter and transitional seasons in the embodiment of the invention by taking a first reversing valve as a four-way valve 2 and a second reversing valve as a combined valve adopting a first form as an example:
As shown in fig. 4, the working condition of high humidity and high pressure ratio in the summer room: the first port and the second port of the four-way valve 2 are communicated, the third port and the fourth port of the four-way valve 2 are communicated, the second valve 8.2 is opened, and the first valve 8.1 and the third valve 8.3 are closed; the system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit flows into the outdoor heat exchanger 3 through the first port and the second port of the four-way valve 2 in sequence to release heat to the outside, and the gaseous refrigerant after releasing heat and reducing temperature is converted into liquid refrigerant to flow into the first throttle valve 4 from the outdoor heat exchanger 3. The liquid refrigerant enters the flash tank 5 after being throttled and cooled by the first throttle valve 4, the gas-liquid two-phase refrigerant generated by the flash tank 5 flows into the indoor large heat exchanger 7.1, and the saturated liquid of the refrigerant generated by the flash tank 5 flows into the indoor small heat exchanger 7.2 after being throttled and cooled again by the second throttle valve 6. The liquid refrigerant flowing through the indoor large heat exchanger 7.1 absorbs heat and rises temperature to be converted into gaseous refrigerant, and then flows into the air suction port of the large cylinder 1.1 directly through the fourth port and the third port of the four-way valve 2 in sequence. At the same time, the liquid refrigerant flowing through the indoor small heat exchanger 7.2 absorbs heat and rises in temperature to be converted into gaseous refrigerant, and then flows into the air suction port of the small cylinder 1.2 again through the second valve 8.2.
As shown in fig. 7, the low humidity and low pressure ratio conditions in the summer room: the first port and the second port of the four-way valve 2 are communicated, and the third port and the fourth port of the four-way valve 2 are communicated; the second valve 8.2 and the third valve 8.3 are opened and the first valve 8.1 is closed. The system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit flows into the outdoor heat exchanger 3 through the first port and the second port of the four-way valve 2 in sequence to release heat to the outside, and the gaseous refrigerant after releasing heat and reducing temperature is converted into liquid refrigerant to flow into the first throttle valve 4 from the outdoor heat exchanger 3. The liquid refrigerant enters the flash tank 5 after being throttled and cooled by the first throttle valve 4, the gas-liquid two-phase refrigerant generated by the flash tank 5 flows into the indoor large heat exchanger 7.1, and the saturated liquid of the refrigerant generated by the flash tank 5 flows into the indoor small heat exchanger 7.2 after being throttled and cooled again by the second throttle valve 6. After the liquid refrigerant flowing through the indoor large heat exchanger 7.1 absorbs heat and is converted into gaseous refrigerant, the gaseous refrigerant sequentially passes through a fourth port and a third port of the four-way valve 2 and is divided into two paths, one path of the gaseous refrigerant directly flows into the air suction port of the large cylinder 1.1, and the other path of the gaseous refrigerant flows into the air suction port of the small cylinder 1.2 through the third valve 8.3. Meanwhile, after the liquid refrigerant is converted into gaseous refrigerant through the heat absorption and temperature rise of the indoor small heat exchanger 7.2, the gaseous refrigerant is divided into two paths through the second valve 8.2, one path of the gaseous refrigerant directly flows into the air suction port of the small cylinder 1.2, and the other path of the gaseous refrigerant flows into the air suction port of the large cylinder 1.1 through the third valve 8.3.
As shown in fig. 5, winter conditions: the second port and the third port of the four-way valve 2 are communicated, and the first port and the fourth port of the four-way valve 2 are communicated; the first valve 8.1 and the third valve 8.3 are opened and the second valve 8.2 is closed. The system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit is divided into two paths, one path of the gaseous refrigerant flows into the indoor large heat exchanger 7.1 to release heat indoors through the first port and the fourth port of the four-way valve 2 in sequence, and the other path of the gaseous refrigerant flows into the indoor small heat exchanger 7.2 to release heat indoors through the first valve 8.1. The liquid refrigerant flowing out of the indoor small heat exchanger 7.2 passes through the second throttle valve 6 and then flows into the flash tank 5 with the liquid refrigerant flowing out of the indoor large heat exchanger 7.1 for mixing. At this time, the flash tank 5 is equivalent to a liquid storage tank, the liquid refrigerant in the flash tank 5 enters the first throttle valve 4, the low-temperature liquid refrigerant throttled and cooled by the first throttle valve 4 flows into the outdoor heat exchanger 3 to absorb heat from the outside, the liquid refrigerant in the outdoor heat exchanger 3 absorbs heat and rises temperature to be converted into gaseous refrigerant, and then the gaseous refrigerant sequentially passes through the second port and the third port of the four-way valve 2 and is divided into two paths, one path directly flows into the air suction port of the large cylinder 1.1, and the other path directly flows into the air suction port of the small cylinder 1.2 through the third valve 8.3.
As shown in fig. 6, the transitional season operation: the first port and the second port of the four-way valve 2 are communicated, and the third port and the fourth port of the four-way valve 2 are communicated; the first valve 8.1 and the third valve 8.3 are opened and the second valve 8.2 is closed. The system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit is divided into two paths, one path of the gaseous refrigerant flows into the outdoor heat exchanger 3 to release heat outdoors through the first port and the second port of the four-way valve 2 in sequence, and the other path of the gaseous refrigerant flows into the indoor small heat exchanger 7.2 to release heat indoors through the first valve 8.1. The gaseous refrigerant flowing through the outdoor heat exchanger 3 is converted into liquid refrigerant by heat release and temperature reduction, and then flows into the first throttle valve 4. At the same time, the gaseous refrigerant flowing through the indoor small heat exchanger 7.2 releases heat, cools down and changes into liquid refrigerant and then flows into the second throttle valve 6. The liquid refrigerant throttled and cooled by the first throttle valve 4 and the second throttle valve 6 flows into the indoor large heat exchanger 7.1 through the flash tank 5 to absorb heat indoors. After the liquid refrigerant flowing through the indoor large heat exchanger 7.1 absorbs heat and is converted into gaseous refrigerant, the gaseous refrigerant sequentially passes through the second port and the third port of the four-way valve 2 and is divided into two paths, one path of the gaseous refrigerant directly flows into the air suction port of the large cylinder 1.1, and the other path of the gaseous refrigerant flows into the air suction port of the small cylinder 1.2 through the third valve 8.3.
The control method of the air conditioning system with temperature adjustment and dehumidification in summer and winter in the embodiment of the invention is described below by taking the first reversing valve as the four-way valve 2 and the second reversing valve as the combined valve adopting the second form as an example, and other working conditions are similar and are not repeated here: wherein the third signal tube 12.3 of the electromagnetic pilot valve 12 is communicated with a chamber adjacent to the second port of the pneumatic three-way valve 11, and the fourth signal tube 12.4 of the electromagnetic pilot valve 12 is communicated with a chamber far away from the second port of the pneumatic three-way valve 11; the two side chambers of the pneumatic two-way valve 10 are a first chamber and a second chamber respectively, and the first chamber and the second chamber are sequentially arranged along the closing direction of the sliding valve in the pneumatic two-way valve 10; the third signal tube 12.3 of the solenoid pilot valve 12 communicates with the second chamber and the fourth signal tube 12.4 of the solenoid pilot valve 12 communicates with the first chamber.
As shown in fig. 9, the high humidity and high pressure ratio conditions in the summer room: the first port and the second port of the four-way valve 2 are communicated, the third port and the fourth port of the four-way valve 2 are communicated, and the electromagnetic pilot valve 12 is powered off. Because the solenoid pilot valve 12 is in the de-energized state at this time, the slide bowl of the solenoid pilot valve 12 moves to the left, the first signal tube 12.1 communicates with the fourth signal tube 12.4, and the second signal tube 12.2 communicates with the third signal tube 12.3. Meanwhile, since the third port 11.3 of the pneumatic three-way valve and the first port 11.1 of the pneumatic three-way valve are respectively communicated with the exhaust port of the compressor unit and the suction port of the small cylinder 1.2, and the first signal pipe 12.1 and the second signal pipe 12.2 are respectively communicated with the third port 11.3 of the pneumatic three-way valve and the first port 11.1 of the pneumatic three-way valve, the pressure of the first chamber of the pneumatic three-way valve 10 and the chamber of the pneumatic three-way valve 11 far away from the second port thereof is close to the exhaust pressure of the compressor unit, and the pressure of the second chamber of the pneumatic three-way valve 10 and the chamber of the pneumatic three-way valve 11 near the second port thereof is close to the suction pressure of the small cylinder 1.2, so that the slide valves in the pneumatic two-way valve 10 and the pneumatic three-way valve 11 slide towards the left under the pressure difference of the two-side chambers, and the pneumatic two-way valve 10 is closed, namely the first port 10.1 of the pneumatic two-way valve and the second port 10.2 of the pneumatic three-way valve are disconnected, and the second port 11.2 of the pneumatic three-way valve is communicated.
The system operates as follows: the high-temperature and high-pressure gaseous refrigerant discharged by the compressor unit flows into the outdoor heat exchanger 3 through the first port and the second port of the four-way valve 2 in sequence to release heat to the outside, and the gaseous refrigerant after releasing heat and reducing temperature is converted into liquid refrigerant to flow into the first throttle valve 4 from the outdoor heat exchanger 3. The liquid refrigerant enters the flash tank 5 after being throttled and cooled by the first throttle valve 4, the gas-liquid two-phase refrigerant generated by the flash tank 5 flows into the indoor large heat exchanger 7.1, and the saturated liquid of the refrigerant generated by the flash tank 5 flows into the indoor small heat exchanger 7.2 after being throttled and cooled again by the second throttle valve 6. The liquid refrigerant flowing through the indoor large heat exchanger 7.1 absorbs heat and rises temperature to be converted into gaseous refrigerant, and then flows into the air suction port of the large cylinder 1.1 directly through the fourth port and the third port of the four-way valve 2 in sequence. At the same time, the liquid refrigerant flowing through the indoor small heat exchanger 7.2 absorbs heat and rises temperature to be converted into gaseous refrigerant, and then flows into the air suction port of the small cylinder 1.2 again through the second port 11.2 of the pneumatic three-way valve and the first port 11.1 of the pneumatic three-way valve in sequence.
As shown in fig. 10, winter conditions: the second port and the third port of the four-way valve 2 are communicated, and the first port and the fourth port of the four-way valve 2 are communicated; the solenoid pilot valve 12 is electrically energized. Because the electromagnetic pilot valve 12 is in the power-on attraction state at this time, the slide bowl of the electromagnetic pilot valve 12 moves rightward, so that the first signal tube 12.1 and the third signal tube 12.3 are communicated, and the second signal tube 12.2 and the fourth signal tube 12.4 are communicated. Meanwhile, since the third port 11.3 of the pneumatic three-way valve and the first port 11.1 of the pneumatic three-way valve are respectively communicated with the exhaust port of the compressor unit and the suction port of the small cylinder 1.2, and the first signal pipe 12.1 and the second signal pipe 12.2 are respectively communicated with the third port 11.3 of the pneumatic three-way valve and the first port 11.1 of the pneumatic three-way valve, the pressure of the second chamber of the pneumatic two-way valve 10 and the chamber adjacent to the second port of the pneumatic three-way valve 11 is close to the exhaust pressure of the compressor unit, and the pressure of the first chamber of the pneumatic two-way valve 10 and the chamber far away from the second port of the pneumatic three-way valve 11 is close to the suction pressure of the small cylinder 1.2, so that the sliding valves in the pneumatic two-way valve 10 and the pneumatic three-way valve 11 slide towards the right under the pressure difference of the two-side chambers, and the pneumatic two-way valve 10 is opened, namely the first port 10.1 of the pneumatic two-way valve and the second port 10.2 of the pneumatic two-way valve are communicated, and the third port 11.3 of the pneumatic three-way valve are communicated.
The system operates as follows: the high-temperature high-pressure gaseous refrigerant discharged by the compressor unit is divided into two paths, one path of the gaseous refrigerant flows into the indoor large heat exchanger 7.1 through the first port and the fourth port of the four-way valve 2 in sequence to release heat indoors, and the other path of the gaseous refrigerant flows into the indoor small heat exchanger 7.2 through the third port 11.3 of the pneumatic three-way valve and the second port 11.2 of the pneumatic three-way valve in sequence to release heat indoors. The liquid refrigerant flowing out of the indoor small heat exchanger 7.2 passes through the second throttle valve 6 and then flows into the flash tank 5 with the liquid refrigerant flowing out of the indoor large heat exchanger 7.1 for mixing. At this time, the flash tank 5 is equivalent to a liquid storage device, the refrigerant in the tube of the flash tank 5 enters the first throttle valve 4, the low-temperature liquid refrigerant throttled and cooled by the first throttle valve 4 flows into the outdoor heat exchanger 3 to absorb heat from the outside, the liquid refrigerant in the outdoor heat exchanger 3 absorbs heat and is heated to be converted into gaseous refrigerant, and then the gaseous refrigerant sequentially passes through the second port and the third port of the four-way valve 2 and is divided into two paths, one path directly flows into the air suction port of the large cylinder 1.1, and the other path sequentially passes through the first port 10.1 of the pneumatic two-way valve and the second port 10.2 of the pneumatic two-way valve and flows into the air suction port of the small cylinder 1.2.
In all the above working conditions, the air sucked from the room by the indoor fan 9 may be all blown to the indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2 in sequence, but of course, part of the air sucked from the room by the indoor fan 9 may be blown to the indoor large heat exchanger 7.1 to cool and then blown to the indoor small heat exchanger 7.2 to dehumidify, and the rest is blown to the indoor large heat exchanger 7.1 only, and the air is mixed and then sent into the room. For the first case, the indoor large heat exchanger 7.1 and the indoor small heat exchanger 7.2 may be sequentially disposed along the air supply direction of the indoor fan 9, and the indoor large heat exchanger 7.1 is disposed between the indoor fan 9 and the indoor small heat exchanger 7.2. For the second case, the system further comprises an air duct, wherein the air duct is provided with an air inlet, a first air outlet and a second air outlet; the air intake of wind channel is close to indoor fan 9 setting, and indoor big heat exchanger 7.1 locates in the air supply direction of first air outlet, and indoor big heat exchanger 7.1 and indoor little heat exchanger 7.2 set gradually in the air supply direction of second air outlet, and indoor big heat exchanger 7.1 is located between second air outlet and the indoor little heat exchanger 7.2.
Finally, it should be noted that: the above embodiments are only for illustrating the technical scheme of the invention, and are not limiting; although the invention has been described in detail with reference to the foregoing embodiments, it will be appreciated by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the invention.

Claims (14)

1. The air conditioning system capable of adjusting temperature and dehumidifying is characterized by comprising a compressor unit, an outdoor heat exchanger, an indoor large heat exchanger, an indoor small heat exchanger, a first reversing valve, a second reversing valve and an indoor fan, wherein the compressor unit comprises a large cylinder and a small cylinder; the second end of the outdoor heat exchanger is respectively communicated with the first end of the indoor large heat exchanger and the first end of the second throttle valve through the first throttle valve, and the second end of the second throttle valve is communicated with the first end of the indoor small heat exchanger;
The first end of the outdoor heat exchanger, the second end of the indoor large heat exchanger, the exhaust port of the compressor unit and the air suction port of the large cylinder are all communicated with the first reversing valve, and the first reversing valve is used for controlling the first end of the outdoor heat exchanger to be communicated with one of the exhaust port of the compressor unit and the air suction port of the large cylinder and controlling the second end of the indoor large heat exchanger to be communicated with the air suction port of the large cylinder and the air suction port of the compressor unit;
The second end of the indoor small heat exchanger, the air suction port of the compressor unit, the air exhaust port of the compressor unit and the first reversing valve are all communicated with the second reversing valve, and the second reversing valve is used for controlling the first end of the outdoor heat exchanger or the second end of the indoor large heat exchanger to be selectively communicated with the air suction port of the small cylinder through the first reversing valve and controlling the second end of the indoor small heat exchanger to be selectively communicated with the air suction port of the small cylinder, the air suction port of the compressor unit and the air exhaust port of the compressor unit; the air inlets of the compressor unit are the air inlets of the large cylinder and the small cylinder, and the air outlets of the compressor unit are the air outlets of the large cylinder and the small cylinder;
The indoor high humidity working condition in summer, the first end of the outdoor heat exchanger is communicated with the exhaust port of the compressor unit, the second end of the indoor large heat exchanger is communicated with the air suction port of the large cylinder, and the second end of the indoor large heat exchanger is disconnected with the air suction port of the small cylinder;
The indoor low humidity operating mode in summer, the first end of outdoor heat exchanger communicates with the gas vent of compressor unit, and the second end of indoor big heat exchanger communicates with the induction port of big cylinder, and the second end of indoor big heat exchanger communicates with the induction port of little cylinder through first switching-over valve, and the second end of indoor little heat exchanger communicates with the induction port of compressor unit.
2. An air conditioning system with temperature adjustable dehumidification as recited in claim 1, further comprising a flash tank through which the first throttle valve communicates with the indoor large heat exchanger and the second throttle valve, respectively.
3. An air conditioning system with temperature and humidity adjustment function according to claim 1 further comprising an intermediate heat exchanger and a third throttle valve, wherein the second end of the first throttle valve is communicated with the second throttle valve through the high temperature side of the intermediate heat exchanger, and the second end of the first throttle valve is communicated with the indoor large heat exchanger through the third throttle valve and the low temperature side of the intermediate heat exchanger in sequence.
4. The temperature-adjustable dehumidification air conditioning system according to claim 1, wherein the second reversing valve comprises a first valve, a second valve and a third valve which are two-way valves, the second end of the indoor small heat exchanger is respectively communicated with the first valve and the first port of the second valve, the second port of the first valve is communicated with the exhaust port of the compressor unit, the second port of the second valve is respectively communicated with the air suction port of the small cylinder and the first port of the third valve, and the second port of the third valve is respectively communicated with the air suction port of the large cylinder and the first reversing valve.
5. The temperature-adjustable dehumidification air conditioning system according to claim 1, wherein the second reversing valve comprises a pneumatic two-way valve, a pneumatic three-way valve and an electromagnetic pilot valve, a first port of the pneumatic two-way valve is respectively communicated with the first reversing valve and the air suction port of the large cylinder, and a second port of the pneumatic two-way valve and a first port of the pneumatic three-way valve are respectively communicated with the air suction port of the small cylinder; the second port of the pneumatic three-way valve is communicated with the second end of the indoor small heat exchanger, and the third port of the pneumatic three-way valve is communicated with the exhaust port of the compressor unit; the first signal pipe and the second signal pipe of the electromagnetic pilot valve are respectively communicated with the third port and the first port of the pneumatic three-way valve; the two side chambers of the pneumatic three-way valve are respectively communicated with the third signal pipe and the fourth signal pipe of the electromagnetic pilot valve, and the two side chambers of the pneumatic two-way valve are respectively communicated with the third signal pipe and the fourth signal pipe of the electromagnetic pilot valve.
6. The temperature-adjustable dehumidification air conditioning system according to claim 1, wherein the compressor unit is a double-cylinder parallel compressor; or the compressor unit comprises a first compressor and a second compressor which are mutually connected in parallel, wherein the first compressor is configured with the large cylinder, and the second compressor is configured with the small cylinder.
7. The temperature-adjustable dehumidification air conditioning system of claim 1, further comprising an air duct having an air inlet, a first air outlet, and a second air outlet; the air inlet is arranged close to the indoor fan, the indoor large heat exchanger is arranged in the air supply direction of the first air outlet, the indoor large heat exchanger and the indoor small heat exchanger are sequentially arranged in the air supply direction of the second air outlet, and the indoor large heat exchanger is positioned between the second air outlet and the indoor small heat exchanger;
Or the indoor large heat exchanger and the indoor small heat exchanger are sequentially arranged along the air supply direction of the indoor fan, and the indoor large heat exchanger is positioned between the indoor fan and the indoor small heat exchanger.
8. The temperature-adjustable dehumidification air conditioning system according to any one of claims 1 to 7, wherein the first reversing valve is a four-way valve, a first port of the four-way valve is communicated with an exhaust port of the compressor unit, a second port of the four-way valve is communicated with the outdoor heat exchanger, a third port of the four-way valve is respectively communicated with an air suction port of the large cylinder and the second reversing valve, and a fourth port of the four-way valve is communicated with the indoor large heat exchanger.
9. The temperature-adjustable dehumidification air conditioning system according to any one of claims 1 to 7, wherein the first reversing valve comprises a first two-way valve, a second two-way valve, a third two-way valve and a fourth two-way valve, wherein a first port of the first two-way valve and a first port of the second two-way valve are both communicated with an exhaust port of the compressor unit, wherein a second port of the second two-way valve and a first port of the third two-way valve are both communicated with a first end of the outdoor heat exchanger, wherein a second port of the third two-way valve and a first port of the fourth two-way valve are both communicated with an air suction port of the large cylinder and the second reversing valve, and wherein a second port of the fourth two-way valve and a second port of the first two-way valve are both communicated with the indoor large heat exchanger.
10. A control method of an air conditioning system based on temperature-adjustable dehumidification according to any one of claims 1 to 9, characterized by comprising the steps of:
Indoor high humidity working condition in summer:
adjusting the first reversing valve to communicate a first end of the outdoor heat exchanger with an exhaust port of the compressor unit and a second end of the indoor large heat exchanger with an intake port of the large cylinder;
the second reversing valve is regulated so as to disconnect the second end of the indoor large heat exchanger from the air suction port of the small cylinder and to communicate the second end of the indoor small heat exchanger with the air suction port of the small cylinder;
Winter working conditions:
adjusting the first reversing valve to communicate a first end of the outdoor heat exchanger with the suction port of the large cylinder and a second end of the indoor large heat exchanger with the exhaust port of the compressor unit;
the second reversing valve is regulated so as to enable the first end of the outdoor heat exchanger to be communicated with the air suction port of the small cylinder through the first reversing valve and enable the second end of the indoor small heat exchanger to be communicated with the air discharge port of the compressor unit;
and (5) working conditions in transitional seasons:
Adjusting a first reversing valve to communicate a first end of the outdoor heat exchanger with an exhaust port of the compressor unit and a second end of the indoor large heat exchanger with an air suction port of the large cylinder;
And adjusting a second reversing valve to communicate the second end of the indoor large heat exchanger with the air suction port of the small cylinder through the first reversing valve and communicate the second end of the indoor small heat exchanger with the air discharge port of the compressor unit.
11. The method of controlling a temperature-adjustable dehumidification air conditioning system according to claim 10, further comprising the steps of:
indoor low humidity condition in summer:
adjusting the first reversing valve to communicate a first end of the outdoor heat exchanger with an exhaust port of the compressor unit and a second end of the indoor large heat exchanger with an intake port of the large cylinder;
And the second reversing valve is regulated so as to enable the second end of the indoor large heat exchanger to be communicated with the air suction port of the small cylinder through the first reversing valve and enable the second end of the indoor small heat exchanger to be communicated with the air suction port of the compressor unit.
12. The method of controlling a temperature-adjustable dehumidification air conditioning system according to claim 10, wherein the step of adjusting the first reversing valve to communicate a first end of the outdoor heat exchanger with the exhaust port of the compressor unit and a second end of the indoor large heat exchanger with the suction port of the large cylinder comprises: a first port and a second port of the four-way valve are communicated, and a third port and a fourth port of the four-way valve are communicated;
The step of adjusting the first reversing valve to communicate the first end of the outdoor heat exchanger with the suction port of the large cylinder and the second end of the indoor large heat exchanger with the discharge port of the compressor unit, includes: and communicating the second port and the third port of the four-way valve, and communicating the first port and the fourth port of the four-way valve.
13. The method of controlling a temperature-adjustable dehumidification air conditioning system according to claim 10, wherein the step of adjusting the second reversing valve to disconnect the second end of the indoor large heat exchanger from the suction port of the small cylinder and to communicate the second end of the indoor small heat exchanger with the suction port of the small cylinder comprises: opening the second valve, and closing the first valve and the third valve;
The step of adjusting the second reversing valve to communicate the second end of the indoor large heat exchanger with the suction port of the small cylinder through the first reversing valve and to communicate the second end of the indoor small heat exchanger with the suction port of the compressor unit includes: opening the second valve and the third valve, and closing the first valve;
The step of adjusting the second reversing valve to communicate the first end of the outdoor heat exchanger with the suction port of the small cylinder through the first reversing valve and to communicate the second end of the indoor small heat exchanger with the discharge port of the compressor unit includes: opening the first valve and the third valve, and closing the second valve.
14. The method of controlling a temperature-adjustable dehumidification air conditioning system according to claim 10, wherein the step of adjusting the second reversing valve to disconnect the second end of the indoor large heat exchanger from the suction port of the small cylinder and to communicate the second end of the indoor small heat exchanger with the suction port of the small cylinder comprises: powering off the electromagnetic pilot valve to enable the first port and the second port of the pneumatic two-way valve to be closed and the first port and the second port of the pneumatic three-way valve to be communicated;
The step of adjusting the second reversing valve to communicate the first end of the outdoor heat exchanger with the suction port of the small cylinder through the first reversing valve and to communicate the second end of the indoor small heat exchanger with the discharge port of the compressor unit includes: electrifying and sucking the electromagnetic pilot valve to open the pneumatic two-way valve, and communicating a second port and a third port of the pneumatic three-way valve;
The step of adjusting the second reversing valve to communicate the second end of the indoor large heat exchanger with the suction port of the small cylinder through the first reversing valve and to communicate the second end of the indoor small heat exchanger with the exhaust port of the compressor unit includes: electrifying and sucking the electromagnetic pilot valve to open the pneumatic two-way valve, and communicating a second port and a third port of the pneumatic three-way valve;
The third signal pipe of the electromagnetic pilot valve is communicated with a chamber adjacent to the second port of the pneumatic three-way valve, and the fourth signal pipe of the electromagnetic pilot valve is communicated with a chamber far away from the second port of the pneumatic three-way valve; the two-side chambers of the pneumatic two-way valve are a first chamber and a second chamber respectively, and the first chamber and the second chamber are sequentially arranged along the closing direction of the sliding valve of the pneumatic two-way valve; and a third signal pipe of the electromagnetic pilot valve is communicated with the second chamber, and a fourth signal pipe of the electromagnetic pilot valve is communicated with the first chamber.
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CN111998565B (en) * 2020-08-13 2024-02-27 珠海格力电器股份有限公司 Double-temperature air conditioning system and control method thereof
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