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WO2013093966A1 - Appareil de conditionnement d'air - Google Patents

Appareil de conditionnement d'air Download PDF

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Publication number
WO2013093966A1
WO2013093966A1 PCT/JP2011/007144 JP2011007144W WO2013093966A1 WO 2013093966 A1 WO2013093966 A1 WO 2013093966A1 JP 2011007144 W JP2011007144 W JP 2011007144W WO 2013093966 A1 WO2013093966 A1 WO 2013093966A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
refrigerant
indoor
outdoor
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2011/007144
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English (en)
Japanese (ja)
Inventor
内藤　宏治
康孝 吉田
浦田　和幹
博之 川口
古田　裕貴
坪江　宏明
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Global Life Solutions Inc
Original Assignee
Hitachi Appliances Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hitachi Appliances Inc filed Critical Hitachi Appliances Inc
Priority to JP2013549949A priority Critical patent/JP5716102B2/ja
Priority to PCT/JP2011/007144 priority patent/WO2013093966A1/fr
Publication of WO2013093966A1 publication Critical patent/WO2013093966A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • F25B30/00—Heat pumps
    • F25B30/04—Heat pumps of the sorption type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/54—Heating and cooling, simultaneously or alternatively
    • 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
    • F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type
    • F25B17/08—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/007—Compression machines, plants or systems with reversible cycle not otherwise provided for three pipes connecting the outdoor side to the indoor side with multiple indoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02732—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two three-way 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0312—Pressure sensors near the indoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0313—Pressure sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to an air conditioner, and more particularly to a cooling and heating simultaneous multi-type air conditioner including a plurality of indoor units.
  • Patent Document 1 air conditioning is performed by controlling the capacity of the compressor and the rotational speed of the outdoor unit side blower from the discharge pressure and suction pressure of the compressor.
  • Patent Document 2 in order to adjust the capacity
  • the refrigerant pressure (liquid pipe pressure) on the outlet side of the indoor unit that performs the heating operation becomes equal to or higher than the refrigerant pressure (high pressure gas pipe pressure) on the inlet side, and the high pressure gas refrigerant flows through the indoor heat exchanger of the indoor unit. There is no fear.
  • the present invention aims to improve the heating capacity by allowing the refrigerant to flow into the indoor unit that performs the heating operation even in the case of the elevation difference construction in the simultaneous cooling and heating multi-type air conditioner. To do.
  • At least one outdoor unit, the first indoor unit and the second indoor unit are connected by a refrigerant pipe, and the outdoor unit exchanges heat with the compressor.
  • the first indoor unit includes a first indoor heat exchanger
  • the second indoor unit includes an air conditioner including a second indoor heat exchanger.
  • the refrigerant pipe is configured to flow to the first indoor heat exchanger, and the opening of the expansion valve disposed on the refrigerant outlet side of the outdoor heat exchanger is reduced, thereby reducing the first
  • the refrigerant pressure on the inlet side of the indoor heat exchanger is greater than the refrigerant pressure on the outlet side of the first indoor heat exchanger. And controlling so as to be higher.
  • Example 1 The refrigeration cycle system diagram of Example 1 is shown.
  • the Mollier diagram of Example 1 is shown. It is a figure which shows an example of the control flowchart of the outdoor expansion valve 15 of Example 1.
  • FIG. FIG. 3 is an excerpt of a part of the refrigeration cycle diagram of Example 1. It is a figure for demonstrating the outdoor expansion valve control flowchart of Example 2.
  • FIG. 6 is a diagram for explaining a refrigeration cycle structure of Example 4.
  • FIG. It is a figure for demonstrating the control flowchart of the outdoor expansion valve of Example 5.
  • FIG. 6 is a system diagram of a refrigeration cycle in Example 6.
  • FIG. 6 is a system diagram of a refrigeration cycle in Example 6.
  • FIG. 1 is a system diagram of the refrigeration cycle of the air conditioner of the first embodiment.
  • This air conditioner is composed of one outdoor unit 10 installed on the roof and indoor units 40a and 40b used for air conditioning on the lower floor with a refrigerant high / low pressure gas pipe 31, a low pressure gas pipe 32, and a liquid main pipe 33. Connected and configured.
  • One outdoor unit 10 or a plurality of outdoor units 10 may be connected in parallel.
  • Two indoor units (40a, 40b) may be connected or a plurality of indoor units may be connected.
  • each indoor unit in the present embodiment is that the indoor unit 40a performs heating operation and the indoor unit 40b performs cooling operation, and is in a state of simultaneous cooling and heating operation. Further, assuming that the cooling load is greater than the heating load, the outdoor heat exchanger 14 is a condenser.
  • the refrigerant flow in the cooling main mode (cooling load> heating load state) in the simultaneous cooling and heating operation will be described. First, a case where the height difference between the outdoor unit 10 and the indoor units (40a, 40b) is equal to or less than a predetermined value (in the case of current product specifications) will be described.
  • the high-pressure gas refrigerant compressed by the compressor 11 is discharged to the high-low pressure switching four-way valve 12 and the heat exchanger switching four-way valve 13.
  • the high-pressure gas refrigerant sent to the high-low pressure switching four-way valve 12 is sent through the high-low pressure gas pipe 31 to the indoor unit 40 a that performs heating operation.
  • the high pressure side opening / closing mechanism 51a is opened and the low pressure side opening / closing mechanism 52a is closed on the gas pipe side of the indoor unit 40a
  • the high pressure gas refrigerant flowing from the high / low pressure gas pipe 31 is sent to the indoor heat exchanger 41a, It exchanges heat with the indoor air, condenses into high-pressure liquid refrigerant, and is sent to the indoor expansion valve 42a and the liquid branch pipe 35a.
  • the high-pressure gas refrigerant discharged to the heat exchanger switching four-way valve 13 is condensed by the outdoor heat exchanger 14 to become high-pressure liquid refrigerant, and is slightly throttled by the outdoor expansion valve 15 and sent to the liquid blocking valve 23 and the liquid main pipe 33. It is done. Then, it merges with the high-pressure liquid refrigerant sent from the indoor unit 40a via the liquid branch pipe 35a, and is sent via the liquid branch pipe 35b to the indoor unit 40b performing the cooling operation.
  • the high-pressure liquid refrigerant sent to the indoor unit 40b is throttled and depressurized by the indoor expansion valve 42b, evaporates by exchanging heat with the indoor air in the indoor heat exchanger 41b, becomes a low-pressure gas refrigerant, and the high-pressure side opening / closing mechanism 51b is closed. Since the side opening / closing mechanism 52b is opened, it is sent to the low-pressure gas pipe 32 and returns to the compressor 11 to circulate again.
  • the outdoor unit 10 and the indoor unit 40b that performs cooling operation have the same refrigerant flow, and the description will be limited to the vicinity of the indoor unit 40a that performs heating operation.
  • the refrigerant pressure (gas pipe side pressure) on the inlet side of the indoor heat exchanger 41a of the indoor unit 40a is the same as that of the high and low pressure gas pipe 31 because the high pressure side opening / closing mechanism 51a is opened and the low pressure side opening / closing mechanism 52a is closed. .
  • the refrigerant pressure (gas pipe side pressure) on the inlet side of the indoor heat exchanger 41a of the indoor unit 40a is substantially the discharge pressure of the compressor 11.
  • the refrigerant pressure (liquid pipe side pressure) on the outlet side of the indoor heat exchanger 41a of the indoor unit 40a will be described in order.
  • the liquid blocking valve 23 with respect to the discharge pressure of the compressor 11 is connected to the outdoor heat exchanger 14 and The pressure is reduced by the pressure loss of the outdoor expansion valve 15.
  • the pressure increases as it goes downward.
  • the pressure may increase to be equal to or higher than the discharge pressure of the compressor 11.
  • the indoor unit 40a As the refrigerant flow of the indoor unit 40a, if the refrigerant pressure (liquid pipe side pressure) on the outlet side is not larger than the refrigerant pressure (gas pipe side pressure) on the inlet side of the indoor heat exchanger 41a, Since the high-pressure gas refrigerant does not flow into the indoor unit 40a, the indoor unit 40a cannot generate heating capacity.
  • the high-pressure gas refrigerant from the high-low pressure gas pipe 31 can be flowed to the indoor unit 40a that performs the heating operation by narrowing the opening of the outdoor expansion valve 15. More specifically, in the air conditioner of the present embodiment, at least one outdoor unit 10, the first indoor unit 40a and the second indoor unit 40b are connected by a refrigerant pipe, and the outdoor unit 10 is compressed.
  • the first indoor unit 40a includes a first indoor heat exchanger 41a
  • the second indoor unit 40b includes a second indoor heat exchanger 41b. Yes.
  • the refrigerant from the compressor 11 is While flowing to the outdoor heat exchanger 14, the refrigerant pipe is configured to flow to the first indoor heat exchanger 41a. Further, by reducing the opening of the expansion valve (outdoor expansion valve 15) arranged on the refrigerant outlet side of the outdoor heat exchanger 14, the refrigerant pressure on the inlet side of the first indoor heat exchanger 41a is changed to the first indoor heat. It controls so that it may become higher than the refrigerant
  • the first indoor heat exchanger 41a acts as a condenser, and the refrigerant from the outdoor heat exchanger 14 is combined with the refrigerant flowing from the first indoor heat exchanger 41a to generate the second indoor heat. It flows to the exchanger 41b.
  • the outdoor unit 10 is on the upper side and the indoor unit 40a is on the lower side. Even if there is a difference, the refrigerant from the high / low pressure gas pipe 31 can be allowed to flow through the indoor unit 40a, and the heating capacity of the indoor unit 40a can be exhibited.
  • the control target is where the liquid pipe pressure connected to the heating indoor unit is lower than the discharge pressure, and a pressure sensor may be attached to the liquid pipe side of the heating indoor unit.
  • a pressure sensor may be attached to the liquid pipe side of the heating indoor unit.
  • the heating capacity of the heating indoor unit when the heating capacity of the heating indoor unit is not generated, it may be estimated that the liquid pipe pressure is higher than the discharge pressure, and the outdoor expansion valve may be throttled until the heating capacity is generated.
  • the presence or absence of the heating capacity may be estimated from the difference between the air intake and blow-out temperature of the indoor unit.
  • the saturation temperature estimated from the discharge pressure and the gas pipe temperature are compared, and a predetermined superheat level is obtained in the refrigerant in the gas pipe section. You may estimate by whether or not.
  • the pressure loss at the outdoor expansion valve may be estimated from the outdoor expansion valve flow rate characteristics and the appropriate liquid main pipe flow rate, and the pressure loss corresponding to the separately obtained height difference head may be given by narrowing the outdoor expansion valve in advance.
  • the height difference may be estimated from the operating pressure and the refrigerant circulation rate, the indoor expansion valve flow rate characteristic, and the outdoor expansion valve flow rate characteristic.
  • the connection pipe may be constituted by one liquid pipe and two gas pipes, or may be constituted by two gas pipes.
  • this control is a multi-cooling simultaneous multi-unit, when the outdoor heat exchanger is a condenser, the indoor unit performing cooling operation and the indoor unit performing heating operation coexist, and both indoor units start operation. Instead of starting the control, control may be performed to throttle the outdoor expansion valve when the heating indoor unit liquid pipe pressure is higher than the discharge pressure during operation or when the capacity of the heating indoor unit is insufficient.
  • FIG. 2 shows a Mollier diagram of this example. 2 is a simplified diagram of the refrigeration cycle diagram of FIG.
  • heating operation and cooling operation are mixed in the indoor units (40a, 40b)
  • the outdoor heat exchanger 14 of the outdoor unit 10 acts as a condenser
  • the outdoor unit 10 is connected to the indoor unit ( 40a, 40b) is a case where construction is performed with a height difference of a predetermined value or more installed on the lower side.
  • FIG. 2-1 shows a Mollier diagram when the outdoor expansion valve 15 of this embodiment is not controlled.
  • the refrigerant passes through the outdoor heat exchanger 14, the specific enthalpy decreases, and the pressure drops slightly due to the pressure loss of the outdoor heat exchanger 14.
  • the differential pressure ⁇ Pvo before and after the outdoor expansion valve 15 is small because control for reducing the expansion valve opening degree is not performed.
  • the state from the outlet side of the outdoor heat exchanger 14 to the outdoor liquid blocking valve ( ⁇ ) hardly changes and enters the liquid main pipe 33.
  • the specific enthalpy of the refrigerant remains unchanged, the head ⁇ PH is applied, and the refrigerant pressure rises, resulting in a state of the heater liquid pipe (liquid branch pipe 35a) ( ⁇ ) of the indoor unit 40a that performs the heating operation.
  • the pressure of the gas pipe of the indoor unit 40a that performs the heating operation that is, the pressure of the gas pipe flowing from the high / low pressure gas pipe 31 to the indoor unit 40a (pressure of the heating machine gas pipe) is PGih
  • the pressure PLih ⁇ the pressure PGih of the heater gas pipe, the refrigerant does not flow into the indoor unit 40a that performs the heating operation.
  • FIG. 2-2 shows a Mollier diagram when the outdoor expansion valve 15 of this embodiment is controlled.
  • the refrigerant passes through the outdoor heat exchanger 14, the specific enthalpy decreases, and the pressure drops slightly due to the pressure loss of the outdoor heat exchanger 14.
  • the opening degree of the outdoor expansion valve 15 is controlled at the outlet of the outdoor heat exchanger 14, the front-rear differential pressure ⁇ Pvo of the outdoor expansion valve 15 is increased.
  • the pressure from the outlet side of the outdoor heat exchanger 14 to the outdoor liquid blocking valve ( ⁇ ) is lower than that in FIG. 2-1, so the pressure in the heater liquid pipe (liquid branch pipe 35a) ( ⁇ ) is also the same.
  • Fig. 2-1 shows a Mollier diagram when the outdoor expansion valve 15 of this embodiment is controlled.
  • the refrigerant flows into the heater (indoor unit 40a), and the refrigerant condensed in the heater (indoor unit 40a) becomes the outdoor heat exchanger 14. Then, the refrigerant is condensed with the refrigerant and sent to the indoor unit 40b that performs the cooling operation. And the pressure reduction and heat exchange are made in the indoor unit 40b, and it sends to the compressor 11 again, and a refrigerating cycle is formed.
  • FIG. 3 is a diagram showing an example of a control flowchart of the outdoor expansion valve 15 of the present embodiment.
  • the control proceeds to the outdoor expansion valve 15.
  • the outdoor expansion valve 15 when the refrigerant pressure on the discharge side of the compressor 11 is higher than the refrigerant pressure in the liquid branch pipe 35a (in the case of True in FIG. 3), the outdoor expansion valve 15 is not particularly operated, and the compressor 11 When the refrigerant pressure on the discharge side becomes equal to or lower than the refrigerant pressure in the liquid branch pipe 35a, the outdoor expansion valve is throttled.
  • coolant pressure of the liquid branch pipe 35a here, you may use the refrigerant
  • the control shown in FIG. 3 is event-like control in the specific case described above.
  • the operation mode changes (such as when the indoor unit operation state changes), or when a predetermined condition is satisfied (discharge pressure> liquid pipe pressure).
  • discharge pressure> liquid pipe pressure When the refrigerant circulation amount, the outdoor fan air amount, etc. change, the throttle valve opening degree that has been throttled may be restored to the original state as appropriate.
  • the opening degree of the outdoor expansion valve 15 may be controlled so that the differential pressure between the discharge pressure and the liquid pipe pressure is within a predetermined range.
  • FIG. 4 is an excerpt from a part of the refrigeration cycle diagram of Example 1, in which pressure sensors (71, 72, 73) are attached to the liquid main pipe 33, the liquid branch pipe 35a, or 35b of the indoor unit.
  • the pressure sensor on the indoor unit side allows the liquid pipe pressure to be controlled by the outdoor expansion valve 15 when the outdoor unit 10 and the indoor units (40a, 40b) are installed with a height difference of a predetermined value or more. It becomes easy.
  • the mounting position of the pressure sensor may be the same indoor liquid pipe assembly (a part of the liquid main pipe 33) as the floor where the indoor unit is located, as in the pressure sensor 71, and the liquid branch pipes (35a, 35b) of the indoor unit.
  • a pressure sensor may be attached to the liquid pipe inside the indoor unit.
  • the 1st indoor unit 40a performs heating operation and the 2nd indoor unit 40b performs cooling operation.
  • the outdoor heat exchanger 14 acts as a condenser, and the detected pressure on the discharge side of the compressor 11 becomes equal to or lower than the detected pressure of the pressure sensor 72, the refrigerant outlet of the outdoor heat exchanger 14
  • the refrigerant pressure on the inlet side of the first indoor heat exchanger 41a becomes higher than the refrigerant pressure on the outlet side of the first indoor heat exchanger 41a by reducing the opening of the outdoor expansion valve 15 arranged on the side.
  • the high-pressure gas refrigerant from the high-low pressure gas pipe 31 can flow through the indoor heat exchanger 41a.
  • FIG. 5 is a diagram for explaining an outdoor expansion valve control flowchart of this embodiment.
  • the difference from FIG. 3 of the first embodiment is that the outdoor expansion valve 15 is throttled when the temperature difference between the intake air temperature and the blown air temperature of the indoor unit 40a that performs the heating operation becomes equal to or less than a set value. is there.
  • the indoor unit 40a includes a first temperature sensor that detects the temperature on the air suction side and a second temperature sensor that detects the temperature on the air blowing side.
  • the outdoor expansion valve 15 is opened.
  • the refrigerant pressure on the inlet side of the indoor heat exchanger 41a is controlled to be higher than the refrigerant pressure on the outlet side of the indoor heat exchanger 41a.
  • the temperature difference between the intake air temperature and the blown air temperature of the indoor unit 40a that performs heating operation is an index for determining the heating capacity of the indoor unit 40a, but the set value here may be as small as 2K or 3K. What is to be determined here is whether or not high-pressure gas is flowing through the indoor unit 40a that performs heating operation, and does not control the outdoor expansion valve 15 in order to further increase the heating capacity that has already been generated. Different from expansion valve control.
  • the heating capacity is generally controlled by controlling the outdoor fan 19.
  • the outdoor expansion valve 15 may be controlled so that the temperature difference between the intake air temperature and the blown air temperature of the indoor unit 40a falls within a predetermined range.
  • FIG. 6 is a diagram for explaining an outdoor expansion valve control flowchart of this embodiment.
  • the difference from FIG. 3 of the first embodiment and FIG. 5 of the second embodiment is that the outdoor expansion valve 15 is throttled when the gas pipe temperature of the indoor unit 40a that performs the heating operation becomes lower than the set value. It is. More specifically, when the temperature difference between the refrigerant temperature on the inlet side of the indoor unit 40a and the saturation temperature in the refrigerant pressure on the discharge side of the compressor 11 is equal to or less than a set value, the opening degree of the outdoor expansion valve 15 is set.
  • the refrigerant pressure on the inlet side of the indoor heat exchanger 41a is controlled to be higher than the refrigerant pressure on the outlet side of the indoor heat exchanger 41a. Thereby, the heating capability of the indoor unit 40a can be exhibited similarly to the first embodiment.
  • the outdoor expansion valve 15 is throttled.
  • the outdoor expansion valve may be controlled so that the gas pipe temperature falls within a predetermined range.
  • FIG. 7 is a diagram for explaining the refrigeration cycle structure of the present embodiment.
  • the liquid pipe pressure of the indoor unit 40a that performs the heating operation is lowered by restricting the outdoor expansion valve 15, but in FIG. 7, the liquid refrigerant in the liquid pipe that causes the liquid head is reduced.
  • an increase in the liquid pipe pressure is suppressed.
  • FIG. 7 shows the state of the liquid main pipe 33 and the low-pressure gas pipe 32 in normal operation.
  • the vertical pipe portions of the low-pressure gas pipe 32 and the liquid main pipe 33 are shown in cross-section and the internal refrigerant state is described.
  • the low-pressure gas pipe 32 is used as a gas single phase
  • the liquid main pipe 33 is used as a liquid single phase.
  • the head in the liquid single phase can be obtained by liquid density ⁇ L ⁇ height difference ⁇ H ⁇ gravity acceleration.
  • the right figure in FIG. 7 shows an example in which the liquid head is reduced.
  • a part of the refrigerant in the liquid main pipe 33 is moved to the low-pressure gas pipe 32 by opening the indoor expansion valve 42b of the indoor unit 40b that performs the cooling operation with respect to the left figure. Since the low-pressure gas pipe 32 has a larger volume than the liquid main pipe 33, such a movement of the refrigerant can be easily performed. Further, the refrigerant may be moved to an auxiliary device such as an accumulator or a receiver.
  • the two-phase head density ⁇ GL ⁇ liquid density ⁇ L By setting the refrigerant in the liquid main pipe 33 in the two-phase state in this manner, the two-phase head density ⁇ GL ⁇ liquid density ⁇ L, so that the head ⁇ GL ⁇ ⁇ H ⁇ g in the two-phase state can be reduced. It is also possible to generate heating capacity during simultaneous operation.
  • FIG. 8 is a view for explaining a control flowchart of the outdoor expansion valve of the present embodiment.
  • the outdoor expansion valve 15 is used to restrict the pressure loss of the difference in height between the outdoor unit 10 and the indoor units (40a, 40b) in advance.
  • the indoor / outdoor height difference may be stored in the control circuit by the contractor, or may be estimated from an operating state such as a trial operation.
  • the degree of opening of the outdoor expansion valve 15 to be throttled is determined by determining the pressure applied to the liquid main pipe 33 in consideration of the refrigerant physical properties with respect to the height difference, and then the amount of refrigerant circulating through the outdoor heat exchanger 14 acting as a condenser, It is determined from the state (liquid single phase or two phase) and expansion valve flow rate characteristics. For example, in order to generate an equivalent pressure loss, the expansion valve opening degree is opened when the refrigerant circulation amount is large, and when the condenser outlet state is two-phase, the expansion valve opening degree is opened and the expansion valve aperture is For small models, it is recommended to open the expansion valve opening. The obtained opening is always taken into account when calculating the outdoor expansion valve.
  • FIG. 9 is a system diagram of the refrigeration cycle of Example 6.
  • the number of outdoor units 10 and indoor units 40a and 40b is the same as in Example 1, but the number of connecting pipes is only two (low pressure gas pipe 32 and high pressure gas pipe 34) corresponding to gas pipes, and the liquid pipe is a gas pipe. Omitted by flowing refrigerant along with gas in the tube.
  • a gas-liquid separator 61 for separating the two-phase refrigerant sent to the indoor units 40a and 40b into liquid and gas
  • a first decompression mechanism 62 for adjusting the refrigerant pressure of the liquid refrigerant after separation
  • the gas refrigerant There is a second pressure reducing mechanism 63 that adjusts the refrigerant pressure.
  • the refrigerant flow in the cooling main mode (cooling load> heating load state) in the cooling and heating simultaneous operation will be described. Since the outdoor expansion valve 15 does not normally exist in this product form, the case where there is no outdoor expansion valve 15 and the height difference is about the current product specification below a predetermined value will be described first.
  • the high-pressure gas refrigerant compressed by the compressor 11 is discharged to the heat exchanger switching four-way valve 13 and flows to the outdoor heat exchanger 14.
  • the refrigerant is appropriately condensed by the outdoor fan 19 to become a high-pressure two-phase refrigerant, and is sent to the high-pressure gas pipe 34 and the gas-liquid separator 61 through the check valve.
  • the liquid refrigerant separated here is controlled so as to be maintained at an appropriate pressure between the indoor expansion valves 42a of the indoor unit 40a that performs the cooling operation after passing through the first pressure reducing mechanism 62.
  • the proper pressure is to make the pressure between the first decompression mechanism 62 and the indoor expansion valve 42a lower than the pressure of the gas-liquid separator 61, and to this, the saturated gas refrigerant is supplied to the indoor unit 40b that performs the heating operation. Begins to flow.
  • the saturated gas refrigerant separated by the gas-liquid separator 61 is condensed by being sent to the indoor unit 40b that is operated for heating, and is sent to the indoor expansion valve 42b as a high-pressure liquid refrigerant. Moreover, it joins between the 1st pressure reduction mechanism 62 and the indoor expansion valve 42a via the liquid branch pipe 35b.
  • the liquid refrigerant thus joined is throttled and depressurized by the indoor expansion valve 42a, and is evaporated to become low-pressure gas refrigerant by exchanging heat with indoor air in the indoor heat exchanger 41a.
  • the high-pressure side opening / closing mechanism 52a is closed and the low-pressure side opening / closing mechanism 51a is opened, the high-pressure side opening / closing mechanism 51a is opened and sent to the low-pressure gas pipe 32. .
  • the height difference between the outdoor unit 10 and the indoor units (40a, 40b) is greater than or equal to a predetermined value (when expanded beyond the current product specifications) will be described.
  • the refrigerant flow is the same for the vicinity of the outdoor unit 10 and the indoor unit 40b that performs cooling operation, and the description will focus on the state of the indoor unit 40b and gas-liquid separator 61 that perform heating operation.
  • the amount of outdoor heat exchange is the same, if the height difference is large, the liquid refrigerant accumulates in the gas-liquid separator 61 and becomes full, and the gas refrigerant cannot be sent to the indoor unit 40b that performs the heating operation.
  • the air volume of the outdoor fan 19 must be reduced, the outdoor heat exchange amount must be reduced, and the gas-liquid separator 61 must be in a two-phase state.
  • the gas-liquid separator 61 is an indoor unit that performs heating operation while being full. There is a possibility that the gas refrigerant cannot be sent to 40b and the heating capacity cannot be generated.
  • the outdoor unit 10 is provided with the outdoor expansion valve 15, and by controlling the outdoor expansion valve 15, the heating capacity of the indoor unit 40b is exhibited.
  • the amount of heat exchange in the outdoor heat exchanger 14 can be slightly reduced by reducing the opening of the outdoor expansion valve 15 in the above case.
  • the refrigerant changes from a liquid single phase to a two-phase. As a result, a saturated gas refrigerant is produced in the gas-liquid separator 61, and heating capacity can be generated.
  • the outdoor expansion valve 15 when the temperature difference between the intake air temperature and the blown air temperature of the indoor unit 40a that performs the heating operation becomes equal to or less than a set value as shown in the flowchart of FIG. You may make it squeeze. By squeezing, it is possible to create a state in which the gas-liquid separator 61 has two phases.
  • the gas pipe temperature of the indoor unit 40a performing the heating operation illustrated in FIG. 6 is equal to or lower than the set value, only the saturated gas flows through the heater during the cooling main operation, so the reference temperature is set to the gas pipe saturation temperature. It is good.
  • the pressure loss of the difference in height may be previously throttled by the outdoor expansion valve 15.

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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

La présente invention a pour objectif d'améliorer la performance de chauffage en permettant à un fluide frigorigène de s'écouler jusqu'à un module intérieur qui effectue une opération de chauffage, même quand une construction ayant une différence de hauteur est utilisée avec un appareil de conditionnement d'air du type multiple à refroidissement/chauffage simultané. Avec cet appareil de conditionnement d'air, au moins un module extérieur, un premier module intérieur, et un second module intérieur sont raccordés par le biais de conduits de fluide frigorigène ; le module extérieur est équipé d'un compresseur et d'un échangeur de chaleur extérieur ; le premier module intérieur est équipé d'un premier échangeur de chaleur intérieur ; et le second module intérieur est équipé d'un second échangeur de chaleur intérieur. Les conduits de fluide frigorigène sont construits de sorte que, quand le premier module intérieur effectue une opération de chauffage et quand le second module intérieur effectue une opération de refroidissement et que l'échangeur de chaleur extérieur fonctionne tel un condensateur, le fluide frigorigène provenant du compresseur s'écoule jusqu'à l'échangeur de chaleur extérieur et s'écoule jusqu'au premier échangeur de chaleur intérieur. De plus, en limitant le degré d'ouverture d'une vanne de détente agencée sur le côté sortie de fluide frigorigène de l'échangeur de chaleur extérieur, la pression du fluide frigorigène du côté admission du premier échangeur de chaleur intérieur est régulée de manière à être supérieure à la pression du fluide frigorigène du côté sortie du premier échangeur de chaleur intérieur.
PCT/JP2011/007144 2011-12-21 2011-12-21 Appareil de conditionnement d'air Ceased WO2013093966A1 (fr)

Priority Applications (2)

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JP2013549949A JP5716102B2 (ja) 2011-12-21 2011-12-21 空気調和機
PCT/JP2011/007144 WO2013093966A1 (fr) 2011-12-21 2011-12-21 Appareil de conditionnement d'air

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016205772A (ja) * 2015-04-28 2016-12-08 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 空気調和機
WO2017183308A1 (fr) * 2016-04-19 2017-10-26 日立ジョンソンコントロールズ空調株式会社 Climatiseur
CN110906503A (zh) * 2019-11-07 2020-03-24 珠海格力电器股份有限公司 空调制热控制方法、装置及空调
CN113646596A (zh) * 2019-03-29 2021-11-12 大金工业株式会社 冷冻装置用单元、热源单元以及冷冻装置
CN117404823A (zh) * 2023-12-15 2024-01-16 北京环都拓普空调有限公司 一种高落差直膨机

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08189717A (ja) * 1995-01-11 1996-07-23 Matsushita Refrig Co Ltd ヒートポンプ式空気調和機
JP2716559B2 (ja) * 1990-03-02 1998-02-18 三菱電機株式会社 冷暖混在型多室空気調和装置
JPH11294871A (ja) * 1998-04-14 1999-10-29 Toshiba Corp 空気調和機
WO2008090927A1 (fr) * 2007-01-23 2008-07-31 Daikin Industries, Ltd. Dispositif de climatisation
JP2011112233A (ja) * 2009-11-24 2011-06-09 Mitsubishi Electric Corp 空気調和装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2716559B2 (ja) * 1990-03-02 1998-02-18 三菱電機株式会社 冷暖混在型多室空気調和装置
JPH08189717A (ja) * 1995-01-11 1996-07-23 Matsushita Refrig Co Ltd ヒートポンプ式空気調和機
JPH11294871A (ja) * 1998-04-14 1999-10-29 Toshiba Corp 空気調和機
WO2008090927A1 (fr) * 2007-01-23 2008-07-31 Daikin Industries, Ltd. Dispositif de climatisation
JP2011112233A (ja) * 2009-11-24 2011-06-09 Mitsubishi Electric Corp 空気調和装置

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016205772A (ja) * 2015-04-28 2016-12-08 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 空気調和機
WO2017183308A1 (fr) * 2016-04-19 2017-10-26 日立ジョンソンコントロールズ空調株式会社 Climatiseur
JP2017194202A (ja) * 2016-04-19 2017-10-26 日立ジョンソンコントロールズ空調株式会社 空気調和機
CN109073264A (zh) * 2016-04-19 2018-12-21 日立江森自控空调有限公司 空气调节装置
CN109073264B (zh) * 2016-04-19 2021-09-21 日立江森自控空调有限公司 空气调节装置
CN113646596A (zh) * 2019-03-29 2021-11-12 大金工业株式会社 冷冻装置用单元、热源单元以及冷冻装置
EP3940315A4 (fr) * 2019-03-29 2022-04-20 Daikin Industries, Ltd. Unité de dispositif de réfrigération, unité source de chaleur, et dispositif de réfrigération
US12352477B2 (en) 2019-03-29 2025-07-08 Daikin Industries, Ltd. Refrigeration apparatus-use unit, heat source unit, and refrigeration apparatus
CN110906503A (zh) * 2019-11-07 2020-03-24 珠海格力电器股份有限公司 空调制热控制方法、装置及空调
CN117404823A (zh) * 2023-12-15 2024-01-16 北京环都拓普空调有限公司 一种高落差直膨机
CN117404823B (zh) * 2023-12-15 2024-03-29 北京环都拓普空调有限公司 一种高落差直膨机

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