EP0482629B1 - Appareil de conditionnement d'air - Google Patents

Appareil de conditionnement d'air Download PDF

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Publication number
EP0482629B1
EP0482629B1 EP91118140A EP91118140A EP0482629B1 EP 0482629 B1 EP0482629 B1 EP 0482629B1 EP 91118140 A EP91118140 A EP 91118140A EP 91118140 A EP91118140 A EP 91118140A EP 0482629 B1 EP0482629 B1 EP 0482629B1
Authority
EP
European Patent Office
Prior art keywords
coolant
heat exchanger
indoor heat
air
indoor
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.)
Expired - Lifetime
Application number
EP91118140A
Other languages
German (de)
English (en)
Other versions
EP0482629A1 (fr
Inventor
Kazuo Suzuki
Tetsuo Sano
Yasunori Oyabu
Katsuaki Yamagishi
Hiroichi Yamaguchi
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.)
Toshiba Corp
Original Assignee
Toshiba Corp
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
Priority claimed from JP2285855A external-priority patent/JPH04161750A/ja
Priority claimed from JP2290708A external-priority patent/JPH04165248A/ja
Priority claimed from JP33410990A external-priority patent/JPH04203853A/ja
Application filed by Toshiba Corp filed Critical Toshiba Corp
Publication of EP0482629A1 publication Critical patent/EP0482629A1/fr
Application granted granted Critical
Publication of EP0482629B1 publication Critical patent/EP0482629B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • F24F3/065—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units with a plurality of evaporators or condensers
    • 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
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/50—Load
    • 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

Definitions

  • the present invention relates to a multiple-system air-conditioning apparatus that air-conditions a plurality of living spaces (see for example EP-A-0 188 630).
  • Figure 1 shows another conventional multiple-system air-conditioning apparatus for air-conditioning two rooms.
  • numeral 1 denotes a compressor, 2 a four-way valve, and 3 an outdoor heat exchanger.
  • the compressor 1 and outdoor heat exchanger 3 constitute an outdoor unit to which two indoor units for rooms A and B are connected in parallel.
  • the indoor unit for the room A comprises an expansion valve 4 serving as a flow control valve, an indoor heat exchanger 5, and an open-close valve 13.
  • the indoor unit for the room B comprises an expansion valve 7 serving as a flow control valve, an indoor heat exchanger 8, and an open-close valve 14.
  • coolant is supplied in a direction indicated with continuous arrow marks, and for heating the rooms, in a direction indicated with dotted arrow marks.
  • the expansion valves 4 and 7 disposed on the liquid coolant side (the coolant inlet side during the cooling operation) of the indoor heat exchangers 5 and 8 are opened or closed in response to an increase or a decrease in air-conditioning loads of the indoor units, to adjust flow rates of the coolant to the indoor heat exchangers 5 and 8.
  • the open-close valves 13 and 14 disposed on the gaseous coolant side (the coolant outlet side during the cooling operation) of the heat exchangers 5 and 8 block the coolant from entering the heat exchangers 5 and 8 while they are out of operation, and have no function of adjusting the flows of the coolant.
  • the expansion valve 4 for the room A is opened to a full extent to feed the coolant at a maximum flow rate, and the expansion valve 7 for the room B is adjusted to feed the coolant to the room B at a flow rate of 10% of the maximum flow rate.
  • the flow rate of the coolant in the indoor unit for the room B is very small compared with its maximum capacity, so that the liquid coolant may exist only partly around the inlet of the indoor heat exchanger 8, and the remaining part of the heat exchanger 8 may be occupied with superheated vapor.
  • the inside of the indoor heat exchanger 8 may involve a part 17 where the liquid coolant exists and a part 16 where the superheated vapor exists.
  • Room air that passes through the part 7 where the liquid coolant exists is cooled and dehumidified to provide dry air "a”
  • room air that passes through the part 16 where the superheated vapor exists is substantially not cooled or dehumidified to provide damp air "b”.
  • These air portions "a” and “b” are mixed together and supersaturated in the indoor unit 15, thereby forming dew "c" over structural components such as a casing, a nose, and a blow port disposed inside the indoor unit 15.
  • the indoor heat exchanger 8 for the room B may excessively condense the coolant and hold a large amount of liquid coolant in the piping thereof. This may cause a shortage of the coolant in a refrigeration cycle of the air-conditioning apparatus, and thus deteriorating the performance of the compressor 1 and overheating and breaking the compressor 1. To avoid this trouble, a ratio between the operating capacities of the indoor heat exchangers 5 and 8 must not be increased too large.
  • the conventional multiple-system air-conditioning apparatus has a problem that, if there is a big difference between loads required for the indoor units when cooling rooms, the structural components disposed inside the indoor unit operating under a light loads are bedewed. There is another problem that, when heating the rooms with the same large difference existing between loads required for the indoor units, an excessive quantity of liquid coolant stays in the piping of the indoor heat exchanger operating under a light load. The latter problem causes a shortage of coolant in the refrigeration cycle of the apparatus, thereby deteriorating, overheating, and breaking the compressor.
  • the conventional air-conditioning apparatus adjusts the opening of each flow control valve to control the flow rate of coolant supplied to a corresponding room.
  • the capacity of the outdoor unit is sometimes designed to be smaller than a total of capacities of the indoor units, to reduce the cost of the air-conditioning apparatus. This is made on an assumption that rooms to be air-conditioned will not simultaneously require a full load each. The outdoor unit, therefore, will be in a shortage of capacity if all rooms simultaneously require a full load each. If this happens, the conventional air-conditioning apparatus cannot deal with this situation.
  • a ratio between capacities (air-conditioning loads) required for the two rooms in Fig. 1 involves a big difference, for example, 1:9
  • a ratio between flow rates of coolant supplied to the indoor units will not always be 1:9 even if a ratio between the openings of the flow control valves is set to 1:9.
  • a ratio between actual performances of the indoor units will not be 1:9 so that a user may not obtain required air-conditioning performances.
  • the air-conditioning apparatus of Fig. 1 for air-conditioning a plurality of rooms has only one outdoor heat exchanger with which heat of the coolant is discharged to atmosphere for cooling the rooms, or heat of atmosphere is absorbed by the coolant for heating the rooms.
  • the single outdoor heat exchanger is able to carry out only one of the heat exchanging actions, and if the cooling and heating requirements simultaneously occur, it responds to only one of them.
  • An object of the invention is to provide an air-conditioning apparatus that does not produce dew over structural components disposed inside on indoor unit operating under a light load during a cooling operation, nor holds an excessive amount of coolant inside the piping of an indoor heat exchanger of an indoor unit operating under a light load during a heating operation, thereby improving the efficiency and reliability of a refrigeration cycle of the apparatus and comfortably air-conditioning a plurality of rooms without fluctuating room temperatures even under light loads.
  • Another object of the invention is to provide an air-conditioning apparatus that accurately controls performances of a plurality of indoor units of the apparatus according to a ratio between air-conditioning loads required for the indoor units, and even if a total of capacities of the indoor units is greater than the capacity of an outdoor unit, properly controls the performances of the indoor units according to the required air-conditioning load ratio.
  • Still another object of the invention is to provide an air-conditioning apparatus that correctly responds to a simultaneous occurrence of opposing cooling an heating requirements.
  • a first aspect of the invention as defined in claim 1 provides an air-conditioning apparatus involving an outdoor unit having a compressor and an outdoor heat exchanger, and a plurality of indoor units connected to the outdoor unit in parallel and each having an indoor heat exchanger.
  • the air-conditioning apparatus comprises flow control means disposed between each of the indoor heat exchangers and the compressor, for adjusting the flow rate of coolant.
  • the flow control means reduces the flow rate of coolant to a corresponding one of the indoor heat exchangers according to at least one of a decrease in an evaporation temperature in the indoor heat exchanger, the degree of superheat of the coolant at an outlet of the coolant, and an increase in the temperature or humidity of air in the room.
  • the flow control means adjusts the flow rate of coolant to a corresponding indoor heat exchanger according to a load on the indoor heat exchanger.
  • the corresponding flow control means adjusts the flow rate of coolant to a required small value at the outlet of the coolant.
  • the evaporation capacity of the indoor heat exchanger is reduced, and liquid coolant is uniformly distributed through the indoor heat exchanger to equalize a temperature in the indoor heat exchanger, thereby equalizing the temperature and humidity of air passing through the indoor heat exchanger, without producing dew over structural components disposed in the indoor unit.
  • the coolant is adjusted to the required small flow rate at an inlet of the coolant of the corresponding indoor heat exchanger.
  • a condensation temperature in the indoor heat exchanger acting as a condenser is reduced to weaken the heat exchanging capacity thereof, so that the coolant may not be excessively condensed, nor held inside the indoor heat exchanger, thereby stabilizing a refrigeration cycle of the air-conditioning apparatus.
  • the coolant is supplied to a plurality of the indoor units in a time sharing manner according to, for example, a time ratio corresponding to a ratio between air-conditioning loads required for the indoor units. Even if the ratio between the air-conditioning loads required for the indoor units is relatively large, the coolant is properly and accurately distributed to the indoor units according to the air-conditioning load ratio.
  • the coolant is properly distributed to the indoor units according to the air-conditioning load ratio.
  • a second aspect of the invention as defined in claim 11 provides an air-conditioning apparatus involving a plurality of indoor heat exchangers connected to a coolant path in parallel.
  • the air-conditioning apparatus alternately carries out cooling and heating operations, and supplies coolant to the indoor heat exchangers according to the cooling and heating requirements in synchronism of the alternate cooling and heating operations.
  • This arrangement alternately carries out the cooling and heating operations in a time sharing manner when the cooling and heating requirements simultaneously occur. During the cooling operation, this arrangement supplies coolant only to the indoor heat exchangers that have issued cooling requests, and during the heating operation, only to the indoor heat exchangers that have issued heating requests.
  • FIG. 3 shows an air-conditioning apparatus according to the first embodiment of the invention. This air-conditioning apparatus is used for air-conditioning two rooms.
  • Figs. 3 through Fig. 19 the same reference numerals as those shown in Fig. 1 represent like parts whose explanations will not be repeated.
  • the air-conditioning apparatus comprises flow control devices 6 and 9 connected to indoor heat exchangers 5 and 8 for rooms A and B, respectively.
  • Each of the flow control devices 6 and 9 serves as flow control means for adjusting the flow rate of coolant and is disposed between the corresponding indoor heat exchanger and a compressor 1.
  • the flow control device 6 (9) is at an outlet of gaseous coolant during a cooling operation.
  • the flow control device 6 (9) comprises an open-close valve 6a (9a) and a thin pipe 6b (9b) that are connected in parallel with each other.
  • Each of the open-close valves 6a and 9a has a function of simply opening and closing a flow of the coolant between a 100% opened state and a 0% opened state.
  • each of the thin pipes 6b and 9b has a function of reducing the flow of the coolant to, for example, 20%. This reduction radio of the coolant flow by the thin pipe 6b or 9b is properly designed.
  • the flow control device 6 (9) is 100% open when the open-close valve 6a (9a) is opened, and reduces the flow of the coolant to, for example, 20% when the open-close valve 6a (9a) is closed.
  • the expansion valve 7 is controlled to reduce the flow of the coolant to 50%, while the flow control device 9 is adjusted to reduce the flow to 20%, thereby adjusting the flow rate of the coolant passing through the indoor heat exchanger 8 for the room B to 10% in total.
  • the indoor unit for the room A is required to operate at 100% capacity and the indoor unit for the room B at 10% capacity.
  • the expansion valve 4 for the room A is fully opened, and the open-close valve 6a of the flow control device 6 is also fully opened, so that the indoor heat exchanger 5 for the room A may receive coolant at the maximum flow rate.
  • the expansion valve 7 for the room B is opened 50%, and the open-close valve 9s of the flow control device 9 is closed to control the flow rate of the coolant to 20%.
  • the indoor heat exchanger 8 for the room B may receive the coolant at the flow rate of 10% in total. In this way, when reducing the flow rate of the coolant in the indoor unit for the room B, the flow control device 9 disposed at the outlet of the coolant more predominantly acts than the expansion valve 7 disposed at the inlet of the coolant.
  • this embodiment Compared with the conventional technique of adjusting the flow rate of the coolant to 10% only with the expansion valve 7, this embodiment increases the quantity of liquid coolant supplied to the indoor heat exchanger 8 for the room B. As a result, the evaporation capacity of the indoor heat exchanger 8 is reduced, and the liquid coolant is uniformly distributed through the indoor heat exchanger 8 to equalize a temperature in the indoor heat exchanger 8. Unlike the conventional air-conditioning apparatus, the apparatus of this embodiment never causes unevenness in the temperature and humidity of air passing through the indoor heat exchanger 8, nor produces dew in the indoor unit.
  • the flow control device 9 of the indoor unit for the room B reduces the flow rate of coolant at an inlet of the coolant in front of the indoor heat exchanger 8, so that the heat exchanging capacity of the indoor heat exchanger 8 serving as a condenser decreases due to a decrease in a condensation temperature.
  • the coolant is not excessively condensed and held inside the indoor heat exchanger 8. This stabilizes a refrigeration cycle of the air-conditioning apparatus.
  • Figure 4 shows an air-conditioning apparatus according to a modification of the first embodiment.
  • This modification has flow control valves 11 and 12 serving as flow control means for linearly adjusting the flow rate of coolant.
  • the flow control valves 11 and 12 are disposed between the compressor 1 and the indoor heat exchangers 5 and 8 for the rooms A and B, respectively.
  • the opening of the flow control valve 11 (12) is adjusted by a control circuit 45 and an opening control circuit 52 (53) according to at least one of the evaporation temperature of the indoor heat exchanger 5 (8), the degree of superheat of coolant detected by a heat exchanger sensor 34 (39) at an outlet of the coolant, and the temperature and humidity of air in the room A (B) detected by a room temperature sensor 33 (38) and a humidity sensor 60, as shown in Fig. 5.
  • the opening of the flow control valve 11 (12) is controlled according to at least one of a decrease in the evaporation temperature of the indoor heat exchanger 5 (8), the degree of superheat of the coolant at the outlet of the coolant, and an increase in the temperature or humidity of air in the room A (B).
  • the flow of the coolant to the indoor heat exchanger 5 (8) is reduced in response to a capacity required for the corresponding indoor unit.
  • the flow rate of the coolant to the indoor heat exchanger of the indoor unit whose required load is smaller is adjustable only through a corresponding one of the flow control valves 11 and 12, so that the modification is more effective in producing no dew over structural components disposed inside the indoor unit of the smaller load during the cooling operation, and in holding no excessive liquid coolant in the piping of the indoor heat exchanger of the smaller load during the heating operation.
  • the first embodiment of the invention arranges flow control means on the compressor side of an indoor heat exchanger of each indoor unit, for adjusting the flow rate to coolant.
  • the flow rate of coolant for the indoor heat exchanger of the indoor unit that requires a smaller cooling load is adjusted to a required small value at an outlet of the coolant.
  • the evaporation capacity to the indoor heat exchanger is reduced, and the liquid coolant is uniformly distributed through the indoor heat exchanger to equalize a temperature in the heat exchanger.
  • the temperature and humidity of air passing through the heat exchanger is equalized without producing dew over structural components disposed inside the indoor unit.
  • the flow rate of coolant to the indoor heat exchanger of the indoor unit that requires a light load is adjusted to a required small value at an inlet of the coolant, so that the condensation temperature of the indoor heat exchanger is reduced to reduce the heat exchanging capacity of the indoor heat exchanger acting as a condenser, and condensed liquid does not excessively stay inside the heat exchanger.
  • a refrigeration cycle of the air-conditioning apparatus is stabilized to increase the efficiency thereof, an overheat of the compressor prevented, the reliability of the apparatus improved.
  • the embodiment Compared with the conventional air-conditioning apparatus that repeatedly starts and stops an indoor unit that requires a small load, the embodiment remarkably reduces fluctuations in a room temperature, thereby comfortably air-conditioning a room.
  • Figures 6 through 13 show an air-conditioning apparatus according to a preferred embodiment of the invention.
  • a coolant is supplied in a time sharing manner.
  • numeral 1 denotes a compressor, which is connected to an outdoor heat exchanger 3 through coolant piping and a four-way valve 2.
  • the coolant piping extending from the outdoor heat exchanger 3 is divided into a plurality of paths (two in the figure) through a flow divider 23.
  • the divided piping is connected to pressure reduction devices, e.g., flow control valves (electronic expansion valves) 4 and 7, indoor heat exchangers 5 and 8, and flow control valves 11 and 12 for rooms A and B.
  • the piping is then collected by a flow divider 21 and connected again to the compressor 1 through the four-way valve 2, thereby completing a heat-pump-type refrigeration cycle.
  • Figure 7 is a block diagram showing a control circuit according to the second embodiment.
  • an operation control portion 32 for the room A is manipulated by a user to issue a start or stop instruction, a required room temperature, or a required wind volume.
  • This operation control portion 32 comprises, for example, a remote control unit.
  • a room temperature sensor 33 measures the temperature of the room A, and a heat exchanger sensor 34 measures the temperature of the indoor heat exchanger 5. These sensors 33 and 34 are used for, for example, preventing a cold wind during a heating operation.
  • a fan motor 35 blows a wind for cooling or heating the room A.
  • a difference between the room temperature measured by the room temperature sensor 33 and a temperature set through the operation control portion 32 is calculated in a temperature difference calculation circuit 36 and transferred to an air-conditioning load calculation circuit 42.
  • the room B has an operation control portion 37, a room temperature sensor 38, a heat exchanger sensor 39, and a fan motor 40. Functions of these components are the same as those for the room A.
  • a difference between the room temperature of the room B and a set temperature is calculated in a temperature difference calculation circuit 41 and transferred to an air-conditioning load calculation circuit 43.
  • the air-conditioning load calculation circuits 42 and 43 provide information to an air-conditioning load ratio calculation circuit 44, which calculates a ratio between air-conditioning loads of the rooms A and B.
  • the air-conditioning load of each room is determined according to the difference between the room temperature and the set temperature for the room, an ambient temperature outside the room, insulation of the room, etc. If these conditions except the temperature difference are substantially identical for all rooms, the air-conditioning load may be calculated according to only the temperature difference.
  • a signal corresponding to an ambient temperature provided by an ambient temperature sensor 57 may be used to calculate the air-conditioning load.
  • a time sharing control circuit 46 for time-sharing coolant flow rates drives opening control circuits 50, 51, 52, and 53 for the rooms A and B. Namely, the openings of the flow control valves 4 and 11 for the room A and of the flow control valves 7 and 12 for the room B are controlled in a time sharing manner according to the air-conditioning load ratio.
  • a total of capacities of the rooms A and B is prepared by changing the rotational speed of a compressor motor 1M with a frequency variable circuit 47. Cooling and heating operations are switched from one to another by turning ON and OFF the four-way valve 2 with a switching circuit 48.
  • a fan motor 54 is employed for an outdoor heat exchanger 3.
  • a current sensor 55 detects a current flowing to the compressor motor 1M and controls not to supply an over-curret thereto.
  • a discharge temperature sensor 56 measures a coolant discharge temperature, and reduces an operation frequency of the compressor if the discharge temperature is too high, thereby protecting a coil of the compressor.
  • a suction temperature sensor 58 and a suction pressure sensor 59 detect the degree of superheat of the coolant. Controlling the degree of superheat is important for safely and efficiently operating the refrigeration cycle but not particularly explained here.
  • Figure 8 shows a first example of the time sharing control.
  • the air-conditioning apparatus air-conditions two rooms A and B in which coolant is supplied to one of the rooms and not supplied to the other according to the time sharing control.
  • a ratio between air-conditioning loads of the rooms A and B calculated in the air-conditioning load ratio calculation circuit 44 is supposed to be 2:1.
  • the time sharing control circuit 46 controls the flow control valves 4 and 11 for the room A and the flow control valves 7 and 12 for the room B in a time sharing manner as shown in Fig. 8.
  • the flow control valves 4 and 11 for the room A are fully opened, while the flow control valves 7 and 12 for the room B are kept completely closed. This is done for a period of 2T which is two times a unit period T. After this period, the flow control valves 4 and 11 for the room A are completely closed, while the flow control valves 7 and 12 for the room B are fully opened. This is done for the unit period T. As a result, the coolant is distributed at the ratio of 2:1 corresponding to the air-conditioning load ratio for the rooms A and B.
  • Figure 9 shows a second example of the time sharing control, which is a modification of the first example. While the flow control valves for one room are fully opened, those for the other room are not completely closed but slightly opened to pass a small quantity of coolant. In this case, if the room A receives the coolant, the openings of the flow control valves 4 and 11 are controlled as explained in the first embodiment.
  • the second example also distributes the coolant to the indoor units at the ratio of 2:1 corresponding to the air-conditioning load ratio for the rooms A and B.
  • Figure 10 shows a third example of the time sharing control.
  • a ratio between air-conditioning loads of the indoor units is relatively large, for example, 8:1.
  • the openings of the flow control valves for the indoor unit of larger air-conditioning load are kept at predetermined extent, while the openings of the flow control valves for the indoor unit of smaller air-conditioning load are controlled in a time sharing manner to precisely distribute the coolant according to the air-conditioning load ratio.
  • the coolant is properly distributed to the rooms only by adjusting the openings of the flow control valves. While the ratio becomes 8:1, the coolant is hardly distributed by only adjusting the openings of the flow control valves.
  • a ratio between the openings of the flow control valves 4 and 11 for the room A to the openings of the flow control valves 7 and 12 is firstly set to 8:2 for a period of 4T.
  • the flow control valves 7 and 12 for the room B are closed.
  • a ratio between flow rates of the coolant for the rooms A and B for a total period of 8T becomes 8:1.
  • Figure 11 shows a fourth example of the time sharing control, which is a modification of the third example.
  • the flow control valves 7 and 12 for the room B are opened and closed alternately every unit time T.
  • the coolant is supplied for 4T and not supplied for 4T to provide the same result as in the third example.
  • Figure 12 shows a fifth example of the time sharing control.
  • This example controls three rooms A, B and C at an air-conditioning load ratio of 2:1:3.
  • Time sharing control is carried out by supplying coolant to the indoor unit of the room A for a period of twice (2T) a unit time T, to the indoor unit of the room B for the unit time (1T), and to the indoor unit of the room C for a period of three times (3T) the unit time.
  • the coolant is supplied to the rooms A, B and C according to the required air-conditioning load ratio of 2:1:3.
  • FIG 13 shows a sixth example of the time sharing control, which is a modification of the fifth example. Coolant is sequentially supplied to each of the rooms A, B, and C for a unit time T. Since it is necessary to supply the coolant to the room A for a period of 2T, the coolant is further supplied to the room A for another unit time T. As a result, the room A receives the coolant for a period of 2T in total. At this time, the coolant is not supplied to the room B because the room B requires the coolant only for the unit time T. Since the room C requires the coolant for a period of 3T, the coolant is further supplied to the room C for another unit time T.
  • the rooms A and B have already received necessary quantities of the coolant, so that only the room C receives the coolant for the unit time T, i.e., for a period of 3T in total.
  • the rooms A, B and C receive the coolant at the time ratio of 2:1:3 similar to the fifth example.
  • the closed flow control valves may receive a small quantity of coolant as in the second example.
  • the second embodiment has a flow control valve on each side of each indoor heat exchanger.
  • this embodiment of the invention carries out time sharing control when supplying coolant to a plurality of indoor units according to a required air-conditioning load ratio. Even if this ratio is relatively large, the coolant is properly and precisely distributed to the indoor units according to the ratio. Even if a total of capacities of a plurality of the indoor units is greater than the capacity of an outdoor unit, the coolant is properly distributed to the indoor units according to the ratio.
  • This embodiment alternately carries out cooling and heating operations to deal with cooling out heating requirements that simultaneously occur.
  • Figure 14 shows an air-conditioning apparatus according to the second aspect of the invention.
  • numeral 1 denotes a compressor; 3 an outdoor heat exchanger; 70 an expansion valve; 71, 73 and 75 indoor heat exchangers disposed for rooms A, B and C, respectively; 77, 79 and 81 operation portions each for setting a cooling or heating request and a target temperature for the corresponding room; 83, 85, 87, 89, 91, and 93 two-way valves for controlling the supply of coolant to the indoor heat exchangers 71, 73, and 75; and 2 a four-way valve for changing the flow of coolant in a coolant path and thus changing cooling and heating operations from one to another.
  • Numeral 97 is a control circuit for controlling an overall operation of the air-conditioning apparatus.
  • the control circuit 97 controls the four-way valve 2 to guide gaseous coolant of high temperature from the compressor 1 toward the indoor heat exchangers 71, 73, and 75.
  • the gaseous coolant passes through the indoor heat exchangers 71, 73, and 75 to discharge heat to air in the rooms, thereby heating the rooms and reducing the temperature of the gaseous coolant.
  • the coolant then passes through the expansion valve 70 and the outdoor heat exchanger 3 to absorb heat from air outside the rooms.
  • control circuit 97 controls the four-way valve 2 to guide the gaseous coolant from the compressor 1 toward the outdoor heat exchanger 3, which discharges heat of the coolant to outside air, thereby liquefying the coolant.
  • the liquid coolant is fed to the indoor heat exchangers 71, 73, and 75 in which the coolant absorbs heat from air in the rooms to cool the rooms.
  • Figure 15 is a time chart showing an operation of the second aspect which deals with simultaneous cooling and heating requests.
  • the indoor heat exchangers 71, 73 and 75 air-condition the rooms A, B, and C, respectively.
  • the control circuit 97 then switches the four-way valve 2 to alternately carry out cooling and heating operations in a time sharing manner for a period t2.
  • the two-way valves 83 and 85 of the indoor heat exchanger 71 for the room A and the two-way valves 87 and 89 of the indoor heat exchanger 73 for the room B are alternately opened end closed.
  • the room A is cooled, and the room B is heated.
  • the numbers of rooms cooled and heated are each one so that a time ratio between cooling and heating operations (A:B) is 1:1.
  • the room C issues a heating request.
  • the number of rooms to be heated then becomes twice the number of rooms to be cooled. Namely, the time ratio between the cooling and heating operations becomes 1:2, and with this time ratio, the alternating operations are continued for a period t3.
  • this embodiment alternately carries out heating and cooling operations according to a time ratio corresponding to the numbers of cooled and heated rooms, to deal with simultaneous cooling and heating requests. Unlike the conventional air-conditioning apparatus, this embodiment can deal with all of such simultaneous cooling and heating requests.
  • the time ratio between the alternating operations is changed when the numbers of rooms to be cooled and heated are changed, thereby properly air-conditioning the rooms.
  • a modification shown in Fig. 16 changes the rotational speed of the compressor 1 with the time ratio (A:B) being unchanged.
  • Figure 17 is a time chart showing another modification to the second aspect of the invention. According to this modification, the alternating cooling and heating operations are carried out according to not only the time ratio based on the numbers of rooms to be cooled and heated but also differences between target temperatures and room temperatures as well as an ambient temperature.
  • the cooling and heating operations are alternately carried out at a time ratio of 1:1 for a period t4.
  • the time ratio (A:B) is changed to 2 for cooling and 1 for heating, and the cooling and heating operations are alternately carried out for a period t5.
  • the control circuit 97 may store a data table shown in Fig. 18 containing various time ratios. According to this table, a proper time ratio is selected to more precisely air-conditioning the individual rooms.
  • the time ratio (A:B) between the alternating operations is changed to properly air-condition the individual rooms according to the numbers of rooms to be cooled and heated, differences between target temperatures and room temperatures, and a change in an ambient temperature. It is possible to change the rotational speed for the compressor 1 with the time ratio (A:B) being unchanged, as shown in Fig. 19.
  • this second aspect also has a flow control valve on each side of each indoor heat exchanger.
  • the second aspect of the invention alternately carries out cooling and heating operations in a time sharing manner to deal with simultaneous cooling and heating requests.
  • coolant is supplied only to indoor heat exchangers that have issued the cooling requests, and during the heating operation, only to indoor exchangers that have issued the heating requests. In this way, correct air-conditioning of individual rooms is ensured even if rooms simultaneously issue opposing cooling and heating requests.

Claims (17)

  1. Appareil de conditionnement d'air, comportant:
    a) une unité extérieure (1, 2, 3) comprenant un compresseur (1) et un échangeur de chaleur extérieur (3) relié en série au dit compresseur (1);
    b) plusieurs unités intérieures (A; B) branchées en parallèle sur ladite unité extérieure (1, 2, 3) et comprenant chacune un échangeur de chaleur intérieur (5; 8); et
    c) des premiers moyens de commande d'écoulement (4; 7) prévus respectivement entre chaque échangeur de chaleur intérieur (5; 8) et ledit échangeur de chaleur extérieur (3), pour ajuster sur un premier côté respectif desdits échangeurs de chaleur intérieurs (5; 8) le débit d'écoulement de fluide réfrigérant entre lesdits échangeurs de chaleur intérieurs (5; 8) et ledit échangeur de chaleur extérieur (3);
    caractérisé par
    d) des seconds moyens de commande d'écoulement (6, 6a, 6b, 11; 9, 9a, 9b, 12) respectivement prévus entre chaque échangeur de chaleur intérieur (5; 8) et ledit compresseur (1), pour ajuster entre un état complètement ouvert et un état partiellement fermé, sur un second côté respectif desdits échangeurs de chaleur intérieurs (5; 8), le débit d'écoulement de fluide réfrigérant entre lesdits échangeurs de chaleur intérieurs (5; 8) et ledit compresseur (1).
  2. Appareil de conditionnement d'air selon la revendication 1, caractérisé en ce que lesdits seconds moyens de commande d'écoulement (6, 6a, 6b, 11; 9, 9a, 9b, 12) sont respectivement prévus pour ajuster linéairement le débit d'écoulement de fluide réfrigérant.
  3. Appareil de conditionnement d'air selon la revendication 1, caractérisé en ce que ledit état complètement ouvert correspond à un débit d'écoulement de fluide réfrigérant de 100%, et ledit état partiellement fermé à un débit d'écoulement de fluide réfrigérant de 10%.
  4. Appareil selon la revendication 1, caractérisé en ce que lesdits premiers moyens de commande d'écoulement (4, 5) sont des soupapes de détente.
  5. Appareil selon la revendication 1, caractérisé en ce qu'une vanne à quatre voies (2) est disposée entre ledit compresseur (1) et ledit échangeur de chaleur extérieur (3), pour commander le débit dudit fluide réfrigérant.
  6. Appareil selon la revendication 1, caractérisé en ce que lorsque l'échangeur de chaleur intérieur (5, 8) d'une quelconque (B) desdites unités intérieures (A, B) est requis de fonctionner à une faible capacité (10%) pendant un fonctionnement en refroidissement, un moyen correspondant (9) parmi lesdits seconds moyens de commande d'écoulement (6, 9) ajuste, à une sortie du fluide réfrigérant, le débit d'écoulement du fluide réfrigérant pour l'échangeur de chaleur intérieur (8) concerné à une faible valeur requise (20%), réduisant ainsi la capacité d'évaporation de l'échangeur de chaleur intérieur (8), distribuant uniformément le fluide réfrigérant liquide à travers l'échangeur de chaleur intérieur (8), équilibrant une température dans l'échangeur de chaleur intérieur (8) ainsi que la température et l'humidité de l'air passant à travers l'échangeur de chaleur intérieur (8), et ne produisant pas de rosée sur des composants structurels disposes à l'intérieur de l'unité intérieure (B) correspondante.
  7. Appareil selon la revendication 1, caractérisé en ce que lorsque l'échangeur de chaleur intérieur (5, 8) d'une quelconque (B) desdites unités intérieures (A, B) est requis de fonctionner à une faible capacité (10%) pendant un fonctionnement en chauffage, un moyen correspondant (9) desdits seconds moyens de commande d'écoulement (6, 9) ajuste, sur une entrée du fluide réfrigérant, le débit d'écoulement du fluide réfrigérant pour l'échangeur de chaleur intérieur concerné à une faible valeur requise (20%), réduisant ainsi la température de condensation et la capacité d'échange de chaleur de l'échangeur de chaleur intérieur (8) agissant comme condenseur, ne retenant pas une quantité excessive de fluide réfrigérant condensé à l'intérieur de l'échangeur de chaleur intérieur (8), et stabilisant un cycle de refroidissement de l'appareil de conditionnement d'air.
  8. Appareil selon la revendication 1, caractérisé en ce que pour un fonctionnement en refroidissement, ledit moyen de commande d'écoulement (6,) réduit le débit d'écoulement du fluide réfrigérant vers l'échangeur de chaleur intérieur (8 ou 9) correspondant, en fonction d'au moins un des éléments suivants: une diminution de la température d'évaporation dans l'échangeur de chaleur intérieur, le degré de surchauffe du fluide réfrigérant à une sortie du fluide réfrigérant, détecté par une sonde d'échangeur de chaleur (34, 39), et une augmentation de la température ou de l'humidité de l'air du local (8, 9), détectée par une sonde de température (33, 38).
  9. Appareil selon la revendication 1, caractérisé en ce que pour un fonctionnement en chauffage, ledit second moyen de commande d'écoulement (8, 9) réduit le débit d'écoulement du fluide réfrigérant lorsqu'une charge de chauffage sur l'échangeur de chaleur intérieur (8, 9) correspondant a diminué.
  10. Appareil selon la revendication 1, caractérisé en ce que des moyens de commande à partage de temps (46) sont prévus pour commander lesdits premiers et lesdits seconds moyens de commande d'écoulement (4, 7; 6, 6a, 6b, 11, 9, 9a, 9b, 12) de manière partagée dans le temps, du fluide réfrigérant étant fourni auxdites unités intérieures (A; B) suivant un rapport de temps entre les charges de conditionnement d'air appliquées sur les unités intérieures (A; B).
  11. Appareil de conditionnement d'air, comportant:
    a) une unité extérieure (1, 2, 3) comprenant un compresseur (1) et un échangeur de chaleur extérieur (3) relié en série au dit compresseur (1);
    b) plusieurs unités intérieures (A, B, C) comprenant chacune un échangeur de chaleur intérieur (71, 73, 75) branché en parallèle sur ledit échangeur de chaleur extérieur (3);
    c) des premiers moyens de commande d'écoulement (83, 87, 91) prévus respectivement entre chaque échangeur de chaleur intérieur (71, 73, 75) et ledit échangeur de chaleur extérieur (3), pour ajuster sur un premier côté respectif desdits échangeurs de chaleur intérieurs (71, 73, 75) un débit d'écoulement de fluide réfrigérant entre ledit échangeur de chaleur extérieur (3) et lesdits échangeurs de chaleur intérieurs (71, 73, 79);
    d) ledit compresseur (1) étant doté d'un moyen à vanne (2) connecté entre ledit échangeur de chaleur extérieur (3) et un second côté respectif desdits échangeurs de chaleur intérieurs (71, 73, 75), et agencé de manière à comprimer ledit fluide réfrigérant provenant desdits échangeurs de chaleur intérieurs (71, 73, 75), et à transférer ledit fluide réfrigérant audit échangeur de chaleur extérieur (3) dans un mode de refroidissement, et de manière à comprimer ledit fluide réfrigérant provenant dudit échangeur de chaleur extérieur (3) et à transférer ledit fluide réfrigérant vers lesdits échangeurs de chaleur intérieurs (71, 73, 75) dans un mode de chauffage;
    e) des seconds moyens de commande d'écoulement (85, 89, 93) respectivement prévus entre chaque échangeur de chaleur intérieur (71, 73, 75) et ledit moyen à vanne (2), pour ajuster le débit d'écoulement de fluide réfrigérant sur les dits seconds côtés respectifs desdits échangeurs de chaleur intérieurs (71, 73, 75);
    caractérisé en ce que
    f) lesdits échangeurs de chaleur intérieurs (71, 73, 75) sont dotés de parties fonctionnelles (77, 79, 81) par l'intermédiaire desquelles le chauffage ou le refroidissement, respectivement, requis dans lesdites unités intérieures (A, B, C), est réglé;
    g) il existe un circuit de commande (97) relié audit compresseur (1), audit moyen à vanne (2), auxdits premiers et seconds moyens de commande d'écoulement (83, 87, 91; 85, 89, 93) et auxdites parties fonctionnelles (77, 79, 81); et
    h) ledit circuit de commande (97) est adapté pour commander ledit compresseur (1), ledit moyen à vanne (2) et lesdits premiers et seconds moyens de commande d'écoulement (83, 87, 91; 85, 89, 93) lorsque du chauffage et du refroidissement sont réglés simultanément par les parties fonctionnelles (77, 79, 81) individuelles desdits échangeurs de chaleur intérieurs (71, 73, 75), de manière à faire passer le fluide réfrigérant alternativement à travers lesdits échangeurs de chaleur intérieurs (71, 73, 75), et à entraîner ledit appareil en alternance et périodiquement dans le mode de chauffage et dans le mode de refroidissement, de manière partagée dans le temps, et en synchronisme, pour satisfaire les demandes simultanées de chauffage et de refroidissement dans lesdites unités intérieures (A, B, C) respectives.
  12. Appareil selon la revendication 11, caractérisé en ce que ledit moyen à vanne (2) est une vanne à quatre voies.
  13. Appareil selon la revendication 11, caractérisé en ce que lesdits seconds moyens de commande d'écoulement (85, 89, 93) sont des vannes d'arrêt présentant un état complètement fermé et un état complètement ouvert.
  14. Appareil selon la revendication 11, caractérisé en ce que lesdits premiers et seconds moyens de commande d'écoulement (6; 8; 83, 87, 91; 85, 89, 93) comprennent des vannes à deux voies.
  15. Appareil selon la revendication 14, caractérisé en ce que lesdites vannes (83, 87, 91) desdits premiers moyens de commande d'écoulement sont prévues entre une soupape de détente (70) et les échangeurs de chaleur intérieurs (71, 73, 75) respectifs.
  16. Appareil selon la revendication 11, caractérisé en ce que ledit circuit de commande (97) commande la capacité dudit compresseur (1) en synchronisme avec le fonctionnement alterné en chauffage et en refroidissement, selon les capacités respectivement requises en chauffage et en refroidissement.
  17. Appareil selon la revendication 14, caractérisé en ce que ledit circuit de commande (97) commande ledit compresseur (1), ledit moyen à vanne (2) et lesdites différentes vannes (83, 87, 91;85, 89, 93) de manière que le rapport de durée du refroidissement au chauffage corresponde à des capacités respectivement requises en refroidissement et en chauffage.
EP91118140A 1990-10-25 1991-10-24 Appareil de conditionnement d'air Expired - Lifetime EP0482629B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP285855/90 1990-10-25
JP2285855A JPH04161750A (ja) 1990-10-25 1990-10-25 空気調和方式
JP290708/90 1990-10-30
JP2290708A JPH04165248A (ja) 1990-10-30 1990-10-30 空気調和装置
JP334109/90 1990-11-30
JP33410990A JPH04203853A (ja) 1990-11-30 1990-11-30 空気調和機

Publications (2)

Publication Number Publication Date
EP0482629A1 EP0482629A1 (fr) 1992-04-29
EP0482629B1 true EP0482629B1 (fr) 1995-12-13

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Application Number Title Priority Date Filing Date
EP91118140A Expired - Lifetime EP0482629B1 (fr) 1990-10-25 1991-10-24 Appareil de conditionnement d'air

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EP (1) EP0482629B1 (fr)
KR (1) KR950012148B1 (fr)
DE (1) DE69115434T2 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2232994T3 (es) * 1993-11-12 2005-06-01 Sanyo Electric Co., Ltd. Aparato de aire acondicionado.
EP1422483B1 (fr) 2002-11-21 2015-10-14 LG Electronics Inc. Appareil de conditionnement d'air
KR100599081B1 (ko) 2004-05-27 2006-07-13 삼성전자주식회사 포토레지스트 조성물 및 이를 사용한 패턴 형성방법
JP4797727B2 (ja) * 2006-03-22 2011-10-19 ダイキン工業株式会社 冷凍装置
KR101275561B1 (ko) * 2006-09-05 2013-06-20 엘지전자 주식회사 기지국의 공조 시스템 및 그 제어방법
CN113686049B (zh) * 2021-07-28 2023-02-21 广东芬尼克兹节能设备有限公司 一种室温协同控制热泵机组方法及装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4644756A (en) * 1983-12-21 1987-02-24 Daikin Industries, Ltd. Multi-room type air conditioner
MY104902A (en) * 1988-04-25 1994-06-30 Matsushita Electric Ind Co Ltd Air conditioning system.

Also Published As

Publication number Publication date
KR950012148B1 (ko) 1995-10-14
EP0482629A1 (fr) 1992-04-29
DE69115434D1 (de) 1996-01-25
KR920008426A (ko) 1992-05-28
DE69115434T2 (de) 1996-05-30

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