EP2034261A1 - Klimaanlage - Google Patents

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Info

Publication number: EP2034261A1
Authority: EP; European Patent Office
Prior art keywords: refrigerant; communication pipe; circuit; volume; pipe
Prior art date: 2006-06-26
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 Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.): Withdrawn

Application number

EP07767400A

Other languages

English (en)

French (fr)

Other versions

EP2034261A4 (de

Inventor

Tadafumi Nishimura

Shinichi Kasahara

Takahiro 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.)

Daikin Industries Ltd

Original Assignee

Daikin Industries Ltd

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.)

2006-06-26

Filing date

2007-06-22

Publication date

2009-03-11

2007-06-22 Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd

2009-03-11 Publication of EP2034261A1 publication Critical patent/EP2034261A1/de

2014-07-30 Publication of EP2034261A4 publication Critical patent/EP2034261A4/de

Status Withdrawn legal-status Critical Current

Images

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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- 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
- F25B45/00—Arrangements for charging or discharging refrigerant
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/005—Arrangement or mounting of control or safety devices of safety devices
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
- 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
- F25B2500/00—Problems to be solved
- F25B2500/19—Calculation of parameters
- 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
- F25B2600/21—Refrigerant outlet evaporator temperature
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/04—Refrigerant level

Definitions

the present invention relates to a function to judge the adequacy of the refrigerant quantity in a refrigerant circuit of an air conditioner. More specifically, the present invention relates to a function to judge the adequacy of the refrigerant quantity in a refrigerant circuit of an air conditioner configured by the interconnection of a heat source unit and a utilization unit via a refrigerant communication pipe.
An object of the present invention is to minimize the labor of inputting information on a refrigerant communication pipe before operating a separate type air conditioner, and at the same time, to enable a highly accurate judgment of the adequacy of the refrigerant quantity in a refrigerant circuit.
An air conditioner includes a refrigerant circuit configured by the interconnection of a heat source unit and a utilization unit via a refrigerant communication pipe, and a pipe volume calculating means.
the pipe volume calculating means calculates the volume of the refrigerant communication pipe based on an additional charging quantity that is a refrigerant quantity to be additionally charged after the refrigerant circuit is configured by the interconnection of the heat source unit and the utilization unit via the refrigerant communication pipe.
the volume of the refrigerant communication pipe is calculated based on the additional charging quantity that is the refrigerant quantity to be additionally charged after the refrigerant circuit is configured by the interconnection of the heat source unit and the utilization unit via the refrigerant communication pipe.
the volume of the refrigerant communication pipe is unknown, it is possible to calculate the volume of the refrigerant communication pipe by inputting a value of the additional charging quantity. Accordingly, it is possible to determine the volume of the refrigerant communication pipe while minimizing the labor of inputting information on the refrigerant communication pipe. As a result, it is possible to judge the adequacy of the refrigerant quantity in the refrigerant circuit with high accuracy.
An air conditioner according to a second aspect of the present invention is the air conditioner according to the first aspect of the present invention, further including a refrigerant quantity judging means to judge whether or not the refrigerant quantity charged in the refrigerant circuit has reached a target charging quantity based on an operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit in an automatic refrigerant charging operation in which the refrigerant is additionally charged into the refrigerant circuit.
the additional charging quantity is the refrigerant quantity additionally charged into the refrigerant circuit in the automatic refrigerant charging operation.
An air conditioner includes a refrigerant circuit configured by the interconnection of a heat source unit and a utilization unit via a refrigerant communication pipe, and a pipe volume calculating means.
the pipe volume calculating means calculates the volume of the refrigerant communication pipe based on a communication pipe refrigerant quantity that is a refrigerant quantity in the refrigerant communication pipe.
the communication pipe refrigerant quantity is determined by subtracting an inside-unit refrigerant quantity that is a refrigerant quantity in the refrigerant circuit excluding the refrigerant communication pipe from a total charged refrigerant quantity that is a refrigerant quantity in the entire refrigerant circuit after the refrigerant is additionally charged thereinto.
the volume of the refrigerant communication pipe is calculated based on the communication pipe refrigerant quantity that is the refrigerant quantity in the refrigerant communication pipe.
the communication pipe refrigerant quantity is determined by subtracting the inside-unit refrigerant quantity that is the refrigerant quantity in the refrigerant circuit excluding the refrigerant communication pipe from the total charged refrigerant quantity that is the refrigerant quantity in the entire refrigerant circuit after the refrigerant is additionally charged thereinto.
An air conditioner according to a fourth aspect of the present invention is the air conditioner according to the second aspect of the present invention, further including a refrigerant quantity calculating means to calculate an inside-unit refrigerant quantity that is a refrigerant quantity in the refrigerant circuit excluding the refrigerant pipe from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit in the automatic refrigerant charging operation.
the pipe volume calculating means determines a total charged refrigerant quantity that is a refrigerant quantity in the entire refrigerant circuit immediately after the automatic refrigerant charging operation, by adding the additional charging quantity to an initial charging quantity that is a refrigerant quantity charged in the refrigerant circuit before the automatic refrigerant charging operation.
the pipe volume calculating means determines a communication pipe refrigerant quantity that is a refrigerant quantity in the refrigerant communication pipe by subtracting the inside-unit refrigerant quantity from the total charged refrigerant quantity, and calculates a density of the refrigerant flowing through the refrigerant communication pipe from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit. Then, the pipe volume calculating means calculates the volume of the refrigerant communication pipe based on the communication pipe refrigerant quantity and the density.
the communication pipe refrigerant quantity present with high accuracy during the automatic refrigerant charging operation by subtracting the inside-unit refrigerant quantity calculated based on the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit in the automatic refrigerant charging operation, from the total charged refrigerant quantity determined by adding the additional charging quantity to the initial charging quantity.
the volume of the refrigerant communication pipe can be calculated with high accuracy.
An air conditioner according to a fifth aspect of the present invention is the air conditioner according to the fourth aspect of the present invention, wherein the refrigerant communication pipe includes a liquid refrigerant communication pipe and a gas refrigerant communication pipe.
the pipe volume calculating means calculates a liquid refrigerant density that is a density of liquid refrigerant flowing through the liquid refrigerant communication pipe and a gas density that is a density of gas refrigerant flowing through the gas refrigerant communication pipe.
the pipe volume calculating means calculates the volume of the liquid refrigerant communication pipe and the volume of the gas refrigerant communication pipe based on the communication pipe refrigerant quantity, a volume ratio between the liquid refrigerant communication pipe and the gas refrigerant communication pipe, the liquid refrigerant density, and the gas refrigerant density.
the liquid refrigerant communication pipe and the gas refrigerant communication pipe are provided so as to interconnect the utilization unit and the heat source unit, so that these pipes have substantially the same pipe length but different pipe diameters, i.e., different flow passage cross-sectional areas, due to the different densities of the refrigerant flowing through the pipes. Therefore, the volume ratio between the liquid refrigerant communication pipe and the gas refrigerant communication pipe will substantially correspond to a flow passage cross-sectional area ratio between these pipes, and furthermore, this volume ratio will be within a certain range because the flow passage cross-sectional area ratio is predetermined based on the capacities and models of the utilization unit and the heat source unit.
the volume ratio between the liquid refrigerant communication pipe and the gas refrigerant communication pipe is known, it will be possible to calculate both the volume of the liquid refrigerant communication pipe and the volume of the gas refrigerant communication pipe, because a total value obtained by adding a value of the multiplication between the volume of the liquid refrigerant communication pipe and the liquid refrigerant density to a value of the multiplication between the volume of the gas refrigerant communication pipe and the gas refrigerant density will be equal to the communication pipe refrigerant quantity.
this air conditioner it is possible to easily calculate both the volume of the liquid refrigerant communication pipe and the volume of the gas refrigerant communication pipe by predetermining the volume ratio between the liquid refrigerant communication pipe and the gas refrigerant communication pipe.
An air conditioner according to a sixth aspect of the present invention is the air conditioner according to the fourth or fifth aspect of the present invention, wherein the refrigerant quantity calculating means calculates a total calculated refrigerant quantity that is a refrigerant quantity in the entire refrigerant circuit based on the volume of the refrigerant communication pipe calculated by the pipe volume calculating means and based on the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit in a refrigerant leak detection operation in which whether or not there is a refrigerant leak from the refrigerant circuit is judged.
the refrigerant quantity judging means judges whether or not there is a refrigerant leak from the refrigerant circuit by comparing the total calculated refrigerant quantity with a reference refrigerant quantity that serves as a reference for judging whether or not there is a refrigerant leak from the refrigerant circuit.
the pipe volume calculating means can calculate the volume of the refrigerant communication pipe, so that even if the volume of the refrigerant communication pipe is unknown, it is possible to calculate the refrigerant quantity in the refrigerant circuit in the refrigerant leak detection operation using the volume of the refrigerant communication pipe calculated by the pipe volume calculating means. Accordingly, it is possible to determine, with high accuracy, whether or not there is a refrigerant leak from the refrigerant circuit while minimizing the labor of inputting information on the refrigerant communication pipe.
An air conditioner according to a seventh aspect of the present invention is the air conditioner according to the second aspect of the present invention, wherein the pipe volume calculating means calculates a density of the refrigerant flowing through the refrigerant communication pipe from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit, and calculates the volume of the refrigerant communication pipe based on the additional charging quantity and the density.
the refrigerant whose quantity is substantially equal to an inside-unit refrigerant quantity that is a refrigerant quantity in the refrigerant circuit excluding the refrigerant communication pipe and that is present when the refrigerant quantity in the refrigerant circuit is reached the target charging quantity by the automatic refrigerant charging operation is charged as an initial charging quantity into the refrigerant circuit before the automatic refrigerant charging operation is performed, and thereby the refrigerant quantity to be additionally charged into the refrigerant circuit in the automatic refrigerant charging operation can be regarded as a refrigerant quantity corresponding to the refrigerant quantity present in the refrigerant communication pipe. Accordingly, it is possible to calculate the volume of the refrigerant communication pipe with high accuracy based on the additional charging quantity and the density.
An air conditioner according to an eighth aspect of the present invention is the air conditioner according to the seventh aspect of the present invention, wherein the refrigerant communication pipe includes a liquid refrigerant communication pipe and a gas refrigerant communication pipe.
the pipe volume calculating means calculates a liquid refrigerant density that is a density of liquid refrigerant flowing through the liquid refrigerant communication pipe and a gas refrigerant density that is a density of gas refrigerant flowing through the gas refrigerant communication pipe.
the pipe volume calculating means calculates the volume of the liquid refrigerant communication pipe and the volume of the gas refrigerant communication pipe based on the additional charging quantity, a volume ratio between the liquid refrigerant communication pipe and the gas refrigerant communication pipe, the liquid refrigerant density, and the gas refrigerant density.
the liquid refrigerant communication pipe and the gas refrigerant communication pipe are provided so as to interconnect the utilization unit and the heat source unit, so that these pipes have substantially the same pipe length but different pipe diameters, i.e., different flow passage cross-sectional areas, due to the different densities of the refrigerant flowing through the pipes. Therefore, the volume ratio between the liquid refrigerant communication pipe and the gas refrigerant communication pipe substantially corresponds to a flow passage cross-sectional area ratio between these pipes, and further more, this volume ratio will be within a certain range because the flow passage cross-sectional area ratio is predetermined based on the capacities and models of the utilization unit and the heat source unit.
the volume ratio between the liquid refrigerant communication pipe and the gas refrigerant communication pipe is known, it will be possible to calculate both the volume of the liquid refrigerant communication pipe and the volume of the gas refrigerant communication pipe because a total value obtained by adding a value of the multiplication between the volume of the liquid refrigerant communication pipe and the liquid refrigerant density to a value of the multiplication between the volume of the gas refrigerant communication pipe and the gas refrigerant density will be equal to the additional charging quantity.
this air conditioner it is possible to easily calculate both the volume of the liquid refrigerant communication pipe and the volume of the gas refrigerant communication pipe by predetermining the volume ratio between the liquid refrigerant communication pipe and the gas refrigerant communication pipe.
An air conditioner according to a ninth aspect of the present invention is the air conditioner according to the seventh or eighth aspect of the present invention, further including a refrigerant quantity calculating means to calculate a total calculated refrigerant quantity that is a refrigerant quantity in the entire refrigerant circuit based on the volume of the refrigerant communication pipe calculated by the pipe volume calculating means and based on the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit in a refrigerant leak detection operation in which whether or not there is a refrigerant leak from the refrigerant circuit is judged,
the refrigerant quantity judging means judges whether or not there is a refrigerant leak from the refrigerant circuit by comparing the total calculated refrigerant quantity with a reference refrigerant quantity that serves as a reference for judging whether or not there is a refrigerant leak from the refrigerant circuit.
the pipe volume calculating means can calculate the volume of the refrigerant communication pipe, so that even when the volume of the refrigerant communication pipe is unknown, it is possible to calculate the refrigerant quantity in the refrigerant circuit in the refrigerant leak detection operation using the volume of the refrigerant communication pipe calculated by the pipe volume calculating means. Accordingly, it is possible to determine, with high accuracy, whether or not there is a refrigerant leak from the refrigerant circuit while minimizing the labor of inputting information on the refrigerant communication pipe.
FIG. 1 is a schematic configuration view of an air conditioner 1 according to an embodiment of the present invention.
the air conditioner 1 is a device that is used to cool and heat a room in a building and the like by performing a vapor compression-type refrigeration cycle operation.
the air conditioner 1 mainly includes one outdoor unit 2 as a heat source unit, indoor units 4 and 5 as a plurality (two in the present embodiment) of utilization units connected in parallel thereto, and a liquid refrigerant communication pipe 6 and a gas refrigerant communication pipe 7 as refrigerant communication pipes which interconnect the outdoor unit 2 and the indoor units 4 and 5.
the vapor compression-type refrigerant circuit 10 of the air conditioner 1 in the present embodiment is configured by the interconnection of the outdoor unit 2, the indoor units 4 and 5, and the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7.
the indoor units 4 and 5 are installed by being embedded in or hung from a ceiling of a room in a building and the like or by being mounted or the like on a wall surface of a room.
the indoor units 4 and 5 are connected to the outdoor unit 2 via the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7, and configure a part of the refrigerant circuit 10.
the indoor unit 4 mainly includes an indoor side refrigerant circuit 10a (an indoor side refrigerant circuit 10b in the case of the indoor unit 5) that configures a part of the refrigerant circuit 10.
the indoor side refrigerant circuit 10a mainly includes an indoor expansion valve 41 as an expansion mechanism and an indoor heat exchanger 42 as a utilization side heat exchanger.
the indoor expansion valve 41 is an electrically powered expansion valve connected to a liquid side of the indoor heat exchanger 42 in order to adjust the flow rate or the like of the refrigerant flowing in the indoor side refrigerant circuit 10a.
the indoor heat exchanger 42 is a cross fin-type fin-and-tube type heat exchanger configured by a heat transfer tube and numerous fins, and is a heat exchanger that functions as an evaporator for the refrigerant during a cooling operation to cool the room air and functions as a condenser for the refrigerant during a heating operation to heat the room air.
the indoor unit 4 includes an indoor fan 43 as a ventilation fan for taking in room air into the unit, causing the air to heat exchange with the refrigerant in the indoor heat exchanger 42, and then supplying the air to the room as supply air.
the indoor fan 43 is a fan capable of varying an air flow rate Wr of the air which is supplied to the indoor heat exchanger 42, and in the present embodiment, is a centrifugal fan, multi-blade fan, or the like, which is driven by a motor 43a comprising a DC fan motor.
a liquid side temperature sensor 44 that detects the temperature of the refrigerant i.e., the refrigerant temperature corresponding to a condensation temperature Tc during the heating operation or an evaporation temperature Te during the cooling operation
a gas side temperature sensor 45 that detects a temperature Teo of the refrigerant is disposed at a gas side of the indoor heat exchanger 42.
a room temperature sensor 46 that detects the temperature of the room air that flows into the unit i.e., a room temperature Tr
a room temperature Tr is disposed at a room air intake side of the indoor unit 4.
the liquid side temperature sensor 44, the gas side temperature sensor 45, and the room temperature sensor 46 comprise thermistors.
the indoor unit 4 includes an indoor side controller 47 that controls the operation of each portion constituting the indoor unit 4.
the indoor side controller 47 includes a microcomputer and a memory and the like disposed in order to control the indoor unit 4, and is configured such that it can exchange control signals and the like with a remote controller (not shown) for individually operating the indoor unit 4 and can exchange control signals and the like with the outdoor unit 2 via a transmission line 8a.
the outdoor unit 2 is installed outside of a building and the like, is connected to the indoor units 4 and 5 via the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7, and configures the refrigerant circuit 10 with the indoor units 4 and 5.
the outdoor unit 2 mainly includes an outdoor side refrigerant circuit 10c that configures a part of the refrigerant circuit 10.
This outdoor side refrigerant circuit 10c mainly includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23 as a heat source side heat exchanger, an outdoor expansion valve 38 as an expansion mechanism, an accumulator 24, a subcooler 25 as a temperature adjustment mechanism; a liquid side stop valve 26, and a gas side stop valve 27.
the compressor 21 is a compressor whose operation capacity can be varied, and in the present embodiment, is a positive displacement-type compressor driven by a motor 21a whose rotation frequency Rm is controlled by an inverter. In the present embodiment, only one compressor 21 is provided, but it is not limited thereto, and two or more compressors may be connected in parallel according to the number of connected units of indoor units and the like.
the four-way switching valve 22 is a valve for switching the direction of the flow of the refrigerant such that, during the cooling operation, the four-way switching valve 22 is capable of connecting a discharge side of the compressor 21 and a gas side of the outdoor heat exchanger 23 and connecting a suction side of the compressor 21 (specifically, the accumulator 24) and the gas refrigerant communication pipe 7 (see the solid lines of the four-way switching valve 22 in Figure 1 ) to cause the outdoor heat exchanger 23 to function as a condenser for the refrigerant compressed in the compressor 21.
the four-way switching valve 22 is capable of connecting the discharge side of the compressor 21 and the gas refrigerant communication pipe 7 and connecting the suction side of the compressor 21 and the gas side of the outdoor heat exchanger 23 (see the dotted lines of the four-way switching valve 22 in Figure 1 ) to cause the indoor heat exchangers 42 and 52 to function as condensers for the refrigerant compressed in the compressor 21 and to cause the outdoor heat exchanger 23 to function as an evaporator for the refrigerant condensed in the indoor heat exchangers 42 and 52.
the outdoor heat exchanger 23 is a cross-fin type fin-and-tube type heat exchanger configured by a heat transfer tube and numerous fins, and is a heat exchanger that functions as a condenser for the refrigerant during the cooling operation and as an evaporator for the refrigerant during the heating operation.
the gas side of the outdoor heat exchanger 23 is connected to the four-way switching valve 22, and the liquid side thereof is connected to the liquid refrigerant communication pipe 6.
the outdoor expansion valve 38 is an electrically powered expansion valve connected to a liquid side of the outdoor heat exchanger 23 in order to adjust the pressure, flow rate, or the like of the refrigerant flowing in the outdoor side refrigerant circuit 10c.
the outdoor unit 2 includes an outdoor fan 28 as a ventilation fan for taking in outdoor air into the unit, causing the air to exchange heat with the refrigerant in the outdoor heat exchanger 23, and then exhausting the air to the outside.
the outdoor fan 28 is a fan capable of varying an air flow rate Wo of the air which is supplied to the outdoor heat exchanger 23, and in the present embodiment, is a propeller fan or the like driven by a motor 28a comprising a DC fan motor.
the accumulator 24 is connected between the four-way switching valve 22 and the compressor 21, and is a container capable of accumulating excess refrigerant generated in the refrigerant circuit 10 in accordance with the change in the operation load of the indoor units 4 and 5 and the like.
the subcooler 25 is a double tube heat exchanger, and is disposed to cool the refrigerant sent to the indoor expansion valves 41 and 51 after the refrigerant is condensed in the outdoor heat exchanger 23.
the subcooler 25 is connected between the outdoor expansion valve 38 and the liquid side stop valve 26.
a bypass refrigerant circuit 61 as a cooling source of the subcooler 25 is disposed. Note that, in the description below, a portion corresponding to the refrigerant circuit 10 excluding the bypass refrigerant circuit 61 is referred to as a main refrigerant circuit for convenience sake.
the bypass refrigerant circuit 61 is connected to the main refrigerant circuit so as to cause a portion of the refrigerant sent from the outdoor heat exchanger 23 to the indoor expansion valves 41 and 51 to branch from the main refrigerant circuit and return to the suction side of the compressor 21.
the bypass refrigerant circuit 61 includes a branch circuit 61 a connected so as to branch a portion of the refrigerant sent from the outdoor expansion valve 38 to the indoor expansion valves 41 and 51 at a position between the outdoor heat exchanger 23 and the subcooler 25, and a merging circuit 61b connected to the suction side of the compressor 21 so as to return a portion of refrigerant from an outlet on a bypass refrigerant circuit side of the subcooler 25 to the suction side of the compressor 21.
the branch circuit 61a is disposed with a bypass expansion valve 62 for adjusting the flow rate of the refrigerant flowing in the bypass refrigerant circuit 61.
the bypass expansion valve 62 comprises an electrically operated expansion valve.
the refrigerant sent from the outdoor heat exchanger 23 to the indoor expansion valves 41 and 51 is cooled in the subcooler 25 by the refrigerant flowing in the bypass refrigerant circuit 61 which has been depressurized by the bypass expansion valve 62.
performance of the subcooler 25 is controlled by adjusting the opening degree of the bypass expansion valve 62.
the liquid side stop valve 26 and the gas side stop valve 27 are valves disposed at ports connected to external equipment and pipes (specifically, the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7).
the liquid side stop valve 26 is connected to the outdoor heat exchanger 23.
the gas side stop valve 27 is connected to the four-way switching valve 22.
various sensors are disposed in the outdoor unit 2.
an suction pressure sensor 29 that detects a suction pressure Ps of the compressor 21
a discharge pressure sensor 30 that detects a discharge pressure Pd of the compressor 21
a suction temperature sensor 31 that detects a suction temperature Ts of the compressor 21
a discharge temperature sensor 32 that detects a discharge temperature Td of the compressor 21.
the suction temperature sensor 31 is disposed at a position between the accumulator 24 and the compressor 21.
a heat exchanger temperature sensor 33 that detects the temperature of the refrigerant flowing through the outdoor heat exchanger 23 (i.e., the refrigerant temperature corresponding to the condensation temperature Tc during the cooling operation or the evaporation temperature Te during the heating operation) is disposed in the outdoor heat exchanger 23.
a liquid side temperature sensor 34 that detects a refrigerant temperature Tco is disposed at the liquid side of the outdoor heat exchanger 23.
a liquid pipe temperature sensor 35 that detects the temperature of the refrigerant i.e., a liquid pipe temperature T1p
T1p liquid pipe temperature
the merging circuit 61b of the bypass refrigerant circuit 61 is disposed with a bypass temperature sensor 63 for detecting the temperature of the refrigerant flowing through the outlet on the bypass refrigerant circuit side of the subcooler 25.
An outdoor temperature sensor 36 that detects the temperature of the outdoor air that flows into the unit (i.e., an outdoor temperature Ta) is disposed at an outdoor air intake side of the outdoor unit 2.
the suction temperature sensor 31, the discharge temperature sensor 32, the heat exchanger temperature sensor 33, the liquid side temperature sensor 34, the liquid pipe temperature sensor 35, the outdoor temperature sensor 36, and the bypass temperature sensor 63 comprise thermistors.
the outdoor unit 2 includes an outdoor side controller 37 that controls the operation of each portion constituting the outdoor unit 2.
the outdoor side controller 37 includes a microcomputer and a memory disposed in order to control the outdoor unit 2, an inverter circuit that controls the motor 21a. and the like, and is configured such that it can exchange control signals and the like with the indoor side controllers 47 and 57 of the indoor units 4 and 5 via the transmission line 8a.
a controller 8 that performs the operation control of the entire air conditioner 1 is configured by the indoor side controllers 47 and 57, the outdoor side controller 37, and the transmission line 8a that interconnects the controllers 37, 47, and 57.
the controller 8 is connected so as to be able to receive detection signals of sensors 29 to 36, 44 to 46, 54 to 56, and 63 and also to be able to control various equipment and valves 21, 22, 24, 28a, 38, 41, 43a, 51, 53a, and 62 based on these detection signals and the like.
the controller 8 is provided with an input unit 9a such that a set value for each type of control can be input and changed and such that the total charged refrigerant quantity including the refrigerant quantity additionally charged into the refrigerant circuit 10 in an automatic refrigerant charging operation (described later) and an initial charging quantity can be input.
a display 9b comprising LEDs and the like is connected to the controller 8.
the display 9b is configured to indicate that additional charging is completed in the automatic refrigerant charging operation (described later) and that a refrigerant leak is detected in a refrigerant leak detection operation (described later).
Figure 2 is a control block diagram of the air conditioner 1.
the input unit 9a is not limited to the one provided to the controller 8, but may be the one that is connected to the controller 8 as needed when inputting the additional charging quantity and the total charged refrigerant quantity.
the refrigerant communication pipes 6 and 7 are refrigerant pipes that are arranged on site when installing the air conditioner 1 at an installation site such as a building.
pipes having various lengths and diameters are used according to the installation conditions such as an installation site, combination of an outdoor unit and an indoor unit, and the like. Accordingly, for example, when installing a new air conditioner, in order to calculate the additional charging quantity of the refrigerant, it is necessary to obtain accurate information regarding the lengths, diameters and the like of the refrigerant communication pipes 6 and 7. However, such information management and the calculation itself of the refrigerant quantity are difficult.
information regarding the lengths, diameters and the like of the refrigerant communication pipes 6 and 7 may have been lost in some cases.
the refrigerant circuit 10 of the air conditioner 1 is configured by the interconnection of the indoor side refrigerant circuits 10a and 10b, the outdoor side refrigerant circuit 10c, and the refrigerant communication pipes 6 and 7.
this refrigerant circuit 10 is configured by the bypass refrigerant circuit 61 and the main refrigerant circuit excluding the bypass refrigerant circuit 61.
the controller 8 constituted by the indoor side controllers 47 and 57 and the outdoor side controller 37 allows the air conditioner 1 in the present embodiment to switch and operate between the cooling operation and the heating operation by the four-way switching valve 22 and to control each equipment of the outdoor unit 2 and the indoor units 4 and 5 according to the operation load of each of the indoor units 4 and 5.
the operation modes of the air conditioner 1 in the present embodiment include: a normal operation mode where control of constituent equipment of the outdoor unit 2 and the indoor units 4 and 5 is performed according to the operation load of each of the indoor units 4 and 5; a test operation mode where a test operation is performed after installation of constituent equipment of the air conditioner 1 is performed (specifically, it is not limited to after the first installation of equipment: it also includes, for example, after modification by adding or removing constituent equipment such as an indoor unit, after repair of damaged equipment); and a refrigerant leak detection operation mode where, after the test operation is finished and the normal operation has started, whether or not there is a refrigerant leak from the refrigerant circuit 10 is judged.
the normal operation mode mainly includes the cooling operation for cooling the room and the heating operation for heating the room.
the test operation mode mainly includes the automatic refrigerant charging operation to charge refrigerant into the refrigerant circuit 10, and a pipe volume calculation process to calculate the volumes of the refrigerant communication pipes 6 and 7.
the four-way switching valve 22 is in the state represented by the solid lines in Figure 1 , i.e., a state where the discharge side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23 and also the suction side of the compressor 21 is connected to the gas sides of the indoor heat exchangers 42 and 52 via the gas side stop valve 27 and the gas refrigerant communication pipe 7.
the outdoor expansion valve 38 is in a fully opened state.
the liquid side stop valve 26 and the gas side stop valve 27 are in an opened state.
the opening degree of each of the indoor expansion valves 41 and 51 is adjusted such that a superheat degree SHr of the refrigerant at the outlets of the indoor heat exchangers 42 and 52 (i.e., the gas sides of the indoor heat exchangers 42 and 52) becomes constant at a target superheat degree SHrs.
the superheat degree SHr of the refrigerant at the outlet of each of the indoor heat exchangers 42 and 52 is detected by subtracting the refrigerant temperature (which corresponds to the evaporation temperature Te) detected by the liquid side temperature sensors 44 and 54 from the refrigerant temperature detected by the gas side temperature sensors 45 and 55, or is detected by converting the suction pressure Ps of the compressor 21 detected by the suction pressure sensor 29 to saturated temperature corresponding to the evaporation temperature Te, and subtracting this saturated temperature of the refrigerant from the refrigerant temperature detected by the gas side temperature sensors 45 and 55.
a temperature sensor that detects the temperature of the refrigerant flowing through each of the indoor heat exchangers 42 and 52 may be disposed such that the superheat degree SHr of the refrigerant at the outlet of each of the indoor heat exchangers 42 and 52 is detected by subtracting the refrigerant temperature corresponding to the evaporation temperature Te which is detected by this temperature sensor from the refrigerant temperature detected by the gas side temperature sensors 45 and 55.
the opening degree of the bypass expansion valve 62 is adjusted such that a superheat degree SHb of the refrigerant at the outlet on the bypass refrigerant circuit side of the subcooler 25 becomes a target superheat degree SHbs.
the superheat degree SHb of the refrigerant at the outlet on the bypass refrigerant circuit side of the subcooler 25 is detected by converting the suction pressure Ps of the compressor 21 detected by the suction pressure sensor 29 to saturated temperature corresponding to the evaporation temperature Te, and subtracting this saturated temperature of the refrigerant from the refrigerant temperature detected by the bypass temperature sensor 63.
a temperature sensor may be disposed at an inlet on the bypass refrigerant circuit side of the subcooler 25 such that the superheat degree SHb of the refrigerant at the outlet on the bypass refrigerant circuit side of the subcooler 25 is detected by subtracting the refrigerant temperature detected by this temperature sensor from the refrigerant temperature detected by the bypass temperature sensor 63.
the refrigerant flowing from the outlet of the bypass expansion valve 62 of the bypass refrigerant circuit 61 toward the suction side of the compressor 21 passes through the subcooler 25 and exchanges heat with high-pressure liquid refrigerant sent from the outdoor heat exchanger 23 on the main refrigerant circuit side to the indoor units 4 and 5.
the high-pressure liquid refrigerant that has become subcooled is sent to the indoor unites 4 and 5 via the liquid side stop valve 26 and the liquid refrigerant communication pipe 6.
the high-pressure liquid refrigerant sent to the indoor units 4 and 5 is depressurized close to the suction pressure Ps of the compressor 21 by the indoor expansion valves 41 and 51, becomes refrigerant in a low-pressure gas-liquid two-phase state, is sent to the indoor heat exchangers 42 and 52, exchanges heat with the room air in the indoor heat exchangers 42 and 52, and is evaporated into low-pressure gas refrigerant.
This low-pressure gas refrigerant is sent to the outdoor unit 2 via the gas refrigerant communication pipe 7, and flows into the accumulator 24 via the gas side stop valve 27 and the four-way switching valve 22. Then, the low-pressure gas refrigerant that flowed into the accumulator 24 is again sucked into the compressor 21.
the four-way switching valve 22 is in a state represented by the dotted lines in Figure 1 , i.e., a state where the discharge side of the compressor 21 is connected to the gas sides of the indoor heat exchangers 42 and 52 via the gas side stop valve 27 and the gas refrigerant communication pipe 7 and also the suction side of the compressor 21 is connected to the gas side of the outdoor heat exchanger 23.
the opening degree of the outdoor expansion valve 38 is adjusted so as to be able to depressurize the refrigerant that flows into the outdoor heat exchanger 23 to a pressure where the refrigerant can evaporate (i.e., evaporation pressure Pe) in the outdoor heat exchanger 23.
the liquid side stop valve 26 and the gas side stop valve 27 are in an opened state.
the opening degree of the indoor expansion valves 41 and 51 is adjusted such that a subcooling degree SCr of the refrigerant at the outlets of the indoor heat exchangers 42 and 52 becomes constant at the target subcooling degree SCrs.
a subcooling degree SCr of the refrigerant at the outlets of the indoor heat exchangers 42 and 52 is detected by converting the discharge pressure Pd of the compressor 21 detected by the discharge pressure sensor 30 to saturated temperature corresponding to the condensation temperature Tc, and subtracting the refrigerant temperature detected by the liquid side temperature sensors 44 and 54 from this saturated temperature of the refrigerant.
a temperature sensor that detects the temperature of the refrigerant flowing through each of the indoor heat exchangers 42 and 52 may be disposed such that the subcooling degree SCr of the refrigerant at the outlets of the indoor heat exchangers 42 and 52 is detected by subtracting the refrigerant temperature corresponding to the condensation temperature Tc which is detected by this temperature sensor from the refrigerant temperature detected by the liquid side temperature sensors 44 and 54.
the bypass expansion valve 62 is closed.
the high-pressure gas refrigerant sent to the indoor units 4 and 5 exchanges heat with the room air in the indoor heat exchangers 42 and 52 and is condensed into high-pressure liquid refrigerant. Subsequently, it is depressurized according to the opening degree of the indoor expansion valves 41 and 51 when passing through the indoor expansion valves 41 and 51.
the refrigerant that passed through the indoor expansion valves 41 and 51 is sent to the outdoor unit 2 via the liquid refrigerant communication pipe 6, is further depressurized via the liquid side stop valve 26, the subcooler 25, and the outdoor expansion valve 38, and then flows into the outdoor heat exchanger 23. Then, the refrigerant in a low-pressure gas-liquid two-phase state that flowed into the outdoor heat exchanger 23 exchanges heat with the outdoor air supplied by the outdoor fan 28, is evaporated into low-pressure gas refrigerant, and flows into the accumulator 24 via the four-way switching valve 22. Then, the low-pressure gas refrigerant that flowed into the accumulator 24 is again sucked into the compressor 21.
Such operation control as described above in the normal operation mode is performed by the controller 8 (more specifically, the indoor side controllers 47 and 57, the outdoor side controller 37, and the transmission line 8a that connects between the controllers 37, 47 and 57) that functions as a normal operation controlling means to perform the normal operation that includes the cooling operation and the heating operation.
the controller 8 more specifically, the indoor side controllers 47 and 57, the outdoor side controller 37, and the transmission line 8a that connects between the controllers 37, 47 and 57
Figure 3 is a flowchart of the test operation mode.
the test operation mode first, the automatic refrigerant charging operation in Step 51 is performed, and subsequently, the pipe volume calculation process in Step 52 is performed.
the outdoor unit 2 in which the refrigerant is charged in advance and the indoor units 4 and 5 are installed at an installation site such as a building, and the outdoor unit 2, the indoor units 4, 5 are interconnected via the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 to configure the refrigerant circuit 10, and subsequently additional refrigerant is charged into the refrigerant circuit 10 whose refrigerant quantity is insufficient according to the volumes of the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7.
the liquid side stop valve 26 and the gas side stop valve 27 of the outdoor unit 2 are opened and the refrigerant circuit 10 is filled with the refrigerant that is charged in the outdoor unit 2 in advance.
FIG. 4 is a flowchart of the automatic refrigerant charging operation.
the refrigerant circuit 10 When a command to start the automatic refrigerant charging operation is issued, the refrigerant circuit 10, with the four-way switching valve 22 of the outdoor unit 2 in the state represented by the solid lines in Figure 1 , becomes a state where the indoor expansion valves 41 and 51 of the indoor units 4 and 5 and the outdoor expansion valve 38 are opened. Then, the compressor 21, the outdoor fan 28, and the indoor fans 43 and 53 are started, and the cooling operation is forcibly performed in all of the indoor units 4 and 5 (hereinafter referred to as "all indoor unit operation").
the high-pressure gas refrigerant compressed and discharged in the compressor 21 flows along a flow path from the compressor 21 to the outdoor heat exchanger 23 that functions as a condenser (see the portion from the compressor 21 to the outdoor heat exchanger 23 in the hatching area indicated by the diagonal line in Figure 5 ); the high-pressure refrigerant that undergoes phase-change from a gas state to a liquid state by heat exchange with the outdoor air flows in the outdoor heat exchanger 23 that functions as a condenser (see the portion corresponding to the outdoor heat exchanger 23 in the hatching area indicated by the diagonal line and the black-lacquered hatching area in Figure 5 ); the high-pressure liquid refrigerant flows along a flow path from the outdoor heat exchanger 23 to the indoor expansion valves 41 and 51 including the outdoor expansion valve 38, the portion corresponding to the main refrigerant circuit side of the subcooler 25 and the liquid refrigerant communication pipe 6, and a flow path from the outdoor heat exchange
the indoor expansion valves 41 and 51 are controlled such that the superheat degree SHr of the indoor heat exchangers 42 and 52 that function as evaporators becomes constant (hereinafter referred to as "super heat degree control”); the operation capacity of the compressor 21 is controlled such that an evaporation pressure Pe becomes constant (hereinafter referred to as “evaporation pressure control”); the air flow rate Wo of outdoor air supplied to the outdoor heat exchanger 23 by the outdoor fan 28 is controlled such that a condensation pressure Pc of the refrigerant in the outdoor heat exchanger 23 becomes constant (hereinafter referred to as “condensation pressure control”); the operation capacity of the subcooler 25 is controlled such that the temperature of the refrigerant sent from the subcooler 25 to the indoor expansion valves 41 and 51 becomes constant (hereinafter referred to as "liquid pipe temperature control”); and the air flow rate Wr of room air supplied to the
the reason to perform the evaporation pressure control is that the evaporation pressure Pe of the refrigerant in the indoor heat exchangers 42 and 52 that function as evaporators is greatly affected by the refrigerant quantity in the indoor heat exchangers 42 and 52 where low-pressure refrigerant flows while undergoing a phase change from a gas-liquid two-phase state to a gas state as a result of heat exchange with the room air (see the portions corresponding to the indoor heat exchangers 42 and 52 in the area indicated by the lattice hatching and hatching indicated by the diagonal line in Figure 5 , which is hereinafter referred to as "evaporator portion C").
the control of the evaporation pressure Pe by the compressor 21 in the present embodiment is achieved in the following manner: the refrigerant temperature (which corresponds to the evaporation temperature Te) detected by the liquid side temperature sensors 44 and 54 of the indoor heat exchangers 42 and 52 is converted to saturation pressure; the operation capacity of the compressor 21 is controlled such that the saturation pressure becomes constant at a target low pressure Pes (in other words, the control to change the rotation frequency Rm of the motor 21a is performed); and then a refrigerant circulation flow rate Wc flowing in the refrigerant circuit 10 is increased or decreased.
the refrigerant temperature which corresponds to the evaporation temperature Te
the operation capacity of the compressor 21 is controlled such that the saturation pressure becomes constant at a target low pressure Pes (in other words, the control to change the rotation frequency Rm of the motor 21a is performed)
a refrigerant circulation flow rate Wc flowing in the refrigerant circuit 10 is increased or decreased.
the operation capacity of the compressor 21 may be controlled such that the suction pressure Ps of the compressor 21 detected by the suction pressure sensor 29, which is the operation state quantity equivalent to the pressure of the refrigerant at the evaporation pressure Pe of the refrigerant in the indoor heat exchangers 42 and 52, becomes constant at the target low pressure Pes, or the saturation temperature (which corresponds to the evaporation temperature Te) corresponding to the suction pressure Ps becomes constant at a target low pressure Tes.
the operation capacity of the compressor 21 may be controlled such that the refrigerant temperature (which corresponds to the evaporation temperature Te) detected by the liquid side temperature sensors 44 and 54 of the indoor heat exchangers 42 and 52 becomes constant at the target low pressure Tes.
gas refrigerant distribution portion D the state of the refrigerant flowing in the refrigerant pipes from the indoor heat exchangers 42 and 52 to the compressor 21 including the gas refrigerant communication pipe 7 and the accumulator 24 (see the portion from the indoor heat exchangers 42 and 52 to the compressor 21 in the hatching area indicated by the diagonal line in Figure 5 , which is hereinafter referred to as "gas refrigerant distribution portion D") becomes stabilized, creating a state where the refrigerant quantity in the gas refrigerant distribution portion D changes mainly by the evaporation pressure Pe (i.e., the suction pressure Ps), which is the operation state quantity equivalent to the pressure of the refrigerant in the gas refrigerant distribution portion D.
the evaporation pressure Pe i.e., the suction pressure Ps
the reason to perform the condensation pressure control is that the condensation pressure Pc of the refrigerant is greatly affected by the refrigerant quantity in the outdoor heat exchanger 23 where high-pressure refrigerant flows while undergoing a phase change from a gas state to a liquid state as a result of heat exchange with the outdoor air (see the portions corresponding to the outdoor heat exchanger 23 in the area indicated by the diagonal line hatching and the black hatching in Figure 5 , which is hereinafter referred to as "condenser portion A").
the condensation pressure Pc of the refrigerant in the condenser portion A greatly changes due to the effect of the outdoor temperature Ta.
the air flow rate Wo of the room air supplied from the outdoor fan 28 to the outdoor heat exchanger 23 is controlled by the motor 28a, and thereby the condensation pressure Pc of the refrigerant in the outdoor heat exchanger 23 is maintained constant and the state of the refrigerant flowing in the condenser portion A is stabilized, creating a state where the refrigerant quantity in condenser portion A changes mainly by a subcooling degree SCo at the liquid side of the outdoor heat exchanger 23 (hereinafter regarded as the outlet of the outdoor heat exchanger 23 in the description regarding the refrigerant quantity judging operation).
the discharge pressure Pd of the compressor 21 detected by the discharge pressure sensor 30, which is the operation state quantity equivalent to the condensation pressure Pc of the refrigerant in the outdoor heat exchanger 23, or the temperature of the refrigerant flowing through the outdoor heat exchanger 23 (i.e., the condensation temperature Tc) detected by the heat exchanger temperature sensor 33 is used.
the high-pressure liquid refrigerant flows along a flow path from the outdoor heat exchanger 23 to the indoor expansion valves 41 and 51 including the outdoor expansion valve 38, the portion on the main refrigerant circuit side of the subcooler 25, and the liquid refrigerant communication pipe 6 and a flow path from the outdoor heat exchanger 23 to the bypass expansion valve 62 of the bypass refrigerant circuit 61; the pressure of the refrigerant in the portions from the outdoor heat exchanger 23 to the indoor expansion valves 41 and 51 and to the bypass expansion valve 62 (see the area indicated by the black hatching in Figure 5 , which is hereinafter referred to as "liquid refrigerant distribution portion B") also becomes stabilized; and the liquid refrigerant distribution portion B is sealed by the liquid refrigerant, thereby becoming a stable state.
the reason to perform the liquid pipe temperature control is to prevent a change in the density of the refrigerant in the refrigerant pipes from the subcooler 25 to the indoor expansion valves 41 and 51 including the liquid refrigerant communication pipe 6 (see the portion from the subcooler 25 to the indoor expansion valves 41 and 51 in the liquid refrigerant distribution portion B shown in Figure 5 ).
Performance of the subcooler 25 is controlled by increasing or decreasing the flow rate of the refrigerant flowing in the bypass refrigerant circuit 61 such that the refrigerant temperature Tlp detected by the liquid pipe temperature sensor 35 disposed at the outlet on the main refrigerant circuit side of the subcooler 25 becomes constant at a target liquid pipe temperature Tlps, and by adjusting the quantity of heat exchange between the refrigerant flowing through the main refrigerant circuit side and the refrigerant flowing through the bypass refrigerant circuit side of the subcooler 25.
the flow rate of the refrigerant flowing in the bypass refrigerant circuit 61 is increased or decreased by adjustment of the opening degree of the bypass expansion valve 62. In this way, the liquid pipe temperature control is achieved in which the refrigerant temperature in the refrigerant pipes from the subcooler 25 to the indoor expansion valves 41 and 51 including the liquid refrigerant communication pipe 6 becomes constant.
the reason to perform the superheat degree control is because the refrigerant quantity in the evaporator portion C greatly affects the quality of wet vapor of the refrigerant at the outlets of the indoor heat exchangers 42 and 52.
the superheat degree SHr of the refrigerant at the outlets of the indoor heat exchangers 42 and 52 is controlled such that the superheat degree SHr of the refrigerant at the gas sides of the indoor heat exchangers 42 and 52 (hereinafter regarded as the outlets of the indoor heat exchangers 42 and 52 in the description regarding the refrigerant quantity judging operation) becomes constant at the target superheat degree SHrs (in other words, the gas refrigerant at the outlets of the indoor heat exchangers 42 and 52 is in a superheat state) by controlling the opening degree of the indoor expansion valves 41 and 51, and thereby the state of the refrigerant flowing in the evaporator portion C is stabilized.
the state of the refrigerant circulating in the refrigerant circuit 10 becomes stabilized, and the distribution of the refrigerant quantity in the refrigerant circuit 10 becomes constant. Therefore, when refrigerant starts to be charged into the refrigerant circuit 10 by additional refrigerant charging, which is subsequently performed, it is possible to create a state where a change in the refrigerant quantity in the refrigerant circuit 10 mainly appears as a change of the refrigerant quantity in the outdoor heat exchanger 23 (hereinafter this operation is referred to as "refrigerant quantity judging operation").
Such operation control as described above is performed as the process in Step S11 by the controller 8 (more specifically, the indoor side controllers 47, 57, the outdoor side controller 37, and the transmission line 8a that connects between the controllers 37, 47 and 57) that functions as a normal operation controlling means to perform the refrigerant quantity judging operation.
the controller 8 more specifically, the indoor side controllers 47, 57, the outdoor side controller 37, and the transmission line 8a that connects between the controllers 37, 47 and 57
Step S 12 additional refrigerant is charged into the refrigerant circuit 10 during performing the above described refrigerant quantity judging operation.
the controller 8 that functions as refrigerant quantity calculating means calculates the refrigerant quantity in the refrigerant circuit 10 from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10 during additional refrigerant charging in Step S 12.
the refrigerant quantity calculating means divides the refrigerant circuit 10 into a plurality of portions, calculates the refrigerant quantity for each divided portions, and thereby calculates the refrigerant quantity in the refrigerant circuit 10. More specifically, a relational expression between the refrigerant quantity in each portion and the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10 is set for each divided portion, and the refrigerant quantity in each portion can be calculated by using these relational expressions.
the refrigerant circuit 10 is divided into the following portions and a relational expression is set for each portion: a portion corresponding to the compressor 21 and a portion from the compressor 21 to the outdoor heat exchanger 23 including the four-way switching valve 22 (not shown in Figure 5 ) (hereinafter referred to as "high-pressure gas pipe portion E"); a portion corresponding to the outdoor heat exchanger 23 (i.e., the condenser portion A); a portion from the outdoor heat exchanger 23 to the subcooler 25 and an inlet side half of the portion corresponding to the main refrigerant circuit side of the subcooler 25 in the liquid ref
the volume Vog1 of the high-pressure gas pipe portion E is a value that is known prior to installation of the outdoor unit 2 at the installation site and is stored in advance in the memory of the controller 8.
a density ⁇ d of the refrigerant in the high-pressure gas pipe portion E is obtained by converting the discharge temperature Td and the discharge pressure Pd.
the compressor discharge superheat degree SHm is a superheat degree of the refrigerant at the discharge side of the compressor, and is obtained by converting the discharge pressure Pd to refrigerant saturation temperature and subtracting this refrigerant saturation temperature from the discharge temperature Td.
a saturated liquid density ⁇ c of the refrigerant is obtained by converting the condensation temperature Tc.
a density ⁇ co of the refrigerant at the outlet of the outdoor heat exchanger 23 is obtained by converting the condensation pressure Pc which is obtained by converting the condensation temperature Tc and the refrigerant temperature Tco.
the volume Vol1 of the high-pressure liquid pipe portion B1 is a value that is known prior to installation of the outdoor unit 2 at the installation site and is stored in advance in the memory of the controller 8.
the volume Vol2 of the low temperature liquid pipe portion B2 is a value that is known prior to installation of the outdoor unit 2 at the installation site and is stored in advance in the memory of the controller 8.
the density ⁇ lp of the refrigerant in the low temperature liquid pipe portion B2 is the density of the refrigerant at the outlet of the subcooler 25, and is obtained by converting the condensation pressure Pc and the refrigerant temperature Tlp at the outlet of the subcooler 25.
the parameters kr1 to kr5 in the above described relational expression are derived from a regression analysis of results of tests and detailed simulations and are stored in advance in the memory of the controller 8.
the relational expression for the refrigerant quantity Mr is set for each of the two indoor units 4 and 5, and the total refrigerant quantity in the indoor unit portion F is calculated by adding the refrigerant quantity Mr in the indoor unit 4 to the refrigerant quantity Mr in the indoor unit 5.
relational expressions in each portion having parameters kr1 to kr5 with different values will be used when the indoor unit 4 and the indoor unit 5 are different in terms of the model and the capacity.
the density pgp of the refrigerant in the gas refrigerant communication pipe portion G is an average value between a density ps of the refrigerant at the suction side of the compressor 21 and a density peo of the refrigerant at the outlets of the indoor heat exchangers 42 and 52 (i.e., the inlet of the gas refrigerant communication pipe 7).
the density ps of the refrigerant is obtained by converting the suction pressure Ps and the suction temperature Ts
a density peo of the refrigerant is obtained by converting the evaporation pressure Pe, which is a converted value of the evaporation temperature Te, and the outlet temperature Teo of the indoor heat exchangers 42 and 52.
the volume Vog2 of the low-pressure gas pipe portion H is a value that is known prior to shipment to the installation site and is stored in advance in the memory of the controller 8.
the volume Vob of the bypass circuit portion I is a value that is known prior to installation of the outdoor unit 2 at the installation site and is stored in advance in the memory of the controller 8.
the saturated liquid density pe at the portion corresponding to the bypass circuit side of the subcooler 25 is obtained by converting the suction pressure Ps or the evaporation temperature Te.
one outdoor unit 2 is provided.
the refrigerant quantity in the outdoor unit such as Mog1, Mc, Mol1, Mol2, Mog2, and Mob
the relational expression for the refrigerant quantity in each portion is set for each of the plurality of outdoor units, and the entire refrigerant quantity in the outdoor units is calculated by adding the refrigerant quantity in each portion of the plurality of the outdoor units.
the refrigerant quantity in each portion is calculated from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10 in the refrigerant quantity judging operation, and thereby the refrigerant quantity in the refrigerant circuit 10 can be calculated.
the refrigerant quantity in each portion is calculated from the operation state quantity during refrigerant charging by using the relational expressions for each portion in the refrigerant circuit 10. More specifically, a refrigerant quantity Mo in the outdoor unit 2 and the refrigerant quantity Mr in each of the indoor units 4 and 5 (i.e., the refrigerant quantity in each portion in the refrigerant circuit 10 excluding the refrigerant communication pipes 6 and 7) necessary for judgment of the adequacy of the refrigerant quantity in the below described Step S 13 are calculated.
the refrigerant quantity Mo in the outdoor unit 2 is calculated by adding Mog1, Mc, Mol1, Mol2, Mog2, and Mob described above, each of which is the refrigerant quantity in each portion in the outdoor unit 2.
Step S12 is performed by the controller 8 that functions as the refrigerant quantity calculating means for calculating the refrigerant quantity in each portion in the refrigerant circuit 10 from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10 in the automatic refrigerant charging operation.
the refrigerant quantity in the refrigerant circuit 10 gradually increases.
the refrigerant quantity that should be charged into the refrigerant circuit 10 after additional refrigerant charging cannot be prescribed as a total charging refrigerant quantity Mt that is a refrigerant quantity in the entire refrigerant circuit 10.
additional refrigerant can be charged by the following manner: a refrigerant quantity that satisfies these optimal refrigerant quantities is stored in advance in the memory of the controller 8 as a target charging value Ms; the refrigerant quantity Mo in the outdoor unit 2 and the refrigerant quantities Mr in the indoor units 4 and 5 are calculated from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10 in the automatic refrigerant charging operation by using the above described relational expressions; and additional refrigerant is charged until a value (hereinafter referred to as an inside-unit refrigerant quantity Mu) of the refrigerant quantity obtained by adding the refrigerant quantity Mo to the refrigerant quantities Mr (i.e., the refrigerant quantity in the refrigerant circuit 10 excluding the refrigerant communication pipes 6 and 7) reaches the target charging value Ms.
a refrigerant quantity that satisfies these optimal refrigerant quantities is stored in advance in the memory of the controller 8
Step S13 is a process to judge the adequacy of the refrigerant quantity charged in the refrigerant circuit 10, by additional refrigerant charging by judging whether or not the inside-unit refrigerant quantity Mu in the automatic refrigerant charging operation has reached the target charging value Ms.
Step S13 when a value of the inside-unit refrigerant quantity Mu is smaller than the target charging value Ms and additional refrigerant charging has not been completed, the process in Step S13 is repeated until the target charging value Ms is reached.
the display 9b displays a message indicating that the additional refrigerant charging is completed, the refrigerant supply from the refrigerant cylinder is stopped, and Step S 1 as the automatic refrigerant charging operation process is completed.
Step S 13 the process in Step S 13 is performed by the controller 8 that functions as an automatic refrigerant charging judging means which is one of the refrigerant quantity judging means to judge the adequacy of the refrigerant quantity in the refrigerant circuit 10 in the refrigerant quantity judging operation of the automatic refrigerant charging operation (i.e., to judge whether or not the refrigerant quantity has reached the target charging value Ms). Then, by this automatic refrigerant charging operation, a state is reached where the total charged refrigerant quantity Mt is charged in the refrigerant circuit 10.
the total charged refrigerant quantity Mt is the refrigerant quantity obtained by adding an additional charging quantity Ma that is a refrigerant quantity additionally charged to an initial charging quantity Mi that is a refrigerant quantity that has been charged into the refrigerant circuit 10 before the automatic refrigerant charging operation (i.e., the refrigerant quantity charged in the outdoor unit 2 in advance).
Step S2 the process proceeds to the pipe volume calculation process in Step S2.
the process from Steps S21 to S24 shown in Figure 6 is performed by the controller 8 that functions as a pipe volume calculating means that calculates the volumes of the refrigerant communication pipes 6 and 7 based on the additional charging quantity Ma.
Figure 6 is a flowchart of the pipe volume calculation process.
Step S21 the operation data from the above described automatic refrigerant charging operation is stored in the memory of the controller 8 such that the density of the refrigerant flowing through the refrigerant communication pipes 6 and 7 can be calculated in the below described Step S23.
the data stored in the memory of the controller 8 includes: condensation pressure Pc and temperature Tlp of the refrigerant at the outlet of the subcooler 25 required for the calculation of the density ⁇ lp of the refrigerant in the liquid refrigerant communication pipe portion B3; suction pressure Ps, suction temperature Ts, evaporation pressure Pe, and outlet temperature Teo required for the calculation of the density pgp of the refrigerant in the gas refrigerant communication pipe portion H; and the inside-unit refrigerant quantity Mu at the time of completion of the automatic refrigerant charging operation.
Step S22 a value of the additional charging quantity Ma or a value of the total charged refrigerant quantity Mt including the additional charging quantity Ma is input in the memory of the controller 8 through the input unit 9a.
the additional charging quantity Ma is a value of the refrigerant quantity obtained from the change in the weight of the refrigerant cylinder and the like in the automatic refrigerant charging operation.
the additional charging quantity Ma may be manually input in the memory of the controller 8 through the input unit 9a provided in the controller 8 by an operator or the like who performs additional charging, or may be automatically input in the memory of the controller 8 by connecting a scale for measuring the change in the weight of the refrigerant cylinder as the input unit 9a to the controller 8.
Steps S21 and S22 are performed in the process of the pipe volume calculation, however, the process may be performed in the process of the above described automatic refrigerant charging operation.
Step S23 first, the total charged refrigerant quantity Mt, which is the refrigerant quantity in the entire refrigerant circuit 10 immediately after the automatic refrigerant charging operation, is obtained by adding the additional charging quantity Ma input in the controller 8 in Step S22 to the initial charging quantity Mi that is the refrigerant quantity that has been charged in the refrigerant circuit 10 before the automatic refrigerant charging operation.
the initial charging quantity Mi is stored in the memory of the controller 8.
the inside-unit refrigerant quantity Mu (or the target charging quantity Ms) stored in the controller 8 in Step S21 is subtracted from the total charged refrigerant quantity Mt, and thereby the communication pipe refrigerant quantity Mp that is the refrigerant quantity in the refrigerant communication pipes 6 and 7 is determined.
Step S23 based on the condensation pressure Pc and the temperature Tlp of the refrigerant at the outlet of the subcooler 25 stored in the controller 8 in Step S21, the density ⁇ lp of liquid refrigerant flowing through the liquid refrigerant communication pipe portion B3 (i.e., the liquid refrigerant communication pipe 6) during the automatic refrigerant charging operation is determined.
the density pgp of gas refrigerant flowing through the gas refrigerant communication pipe portion H i.e., the gas refrigerant communication pipe 7 during the automatic refrigerant charging operation is determined (note that the calculation of these densities ⁇ lp and pgp is the same as the calculation of the densities ⁇ lp and pgp for the calculation of the refrigerant quantity in Step S12 of the above described automatic refrigerant charging operation, and thus the description thereof is omitted here).
Step S24 the volumes of the refrigerant communication pipes 6 and 7 (more specifically, the volume Vlp of the liquid refrigerant communication pipe 6 and the volume Vgp of the gas refrigerant communication pipe) are calculated based on the communication pipe refrigerant quantity Mp and the densities ⁇ lp and pgp determined in Step S23.
the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 are provided so as to interconnect the indoor units 4 and 5 and the outdoor unit 2, so that these pipes have substantially the same pipe length but different pipe diameters, i.e., different flow passage cross-sectional areas, due to the different densities of the refrigerant flowing through the pipes.
the volume ratio between the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 (in the description below , a value of Vgp/Vlp in which the gas refrigerant communication pipe Vgp is divided by the volume Vlp of liquid refrigerant communication pipe 6 is referred to as a volume ratio Rv) will substantially correspond to the flow passage cross-sectional area ratio between these pipes, and furthermore, this volume ratio Rv will be within a certain range because the flow passage cross-sectional area ratio is predetermined based on the capacities and models of the indoor units 4 and 5 and the outdoor unit 2.
the volume ratio Rv between the liquid refrigerant communication pipe 6 and the gas refrigerant communication pipe 7 is stored in the memory of the controller 8 in advance as a value corresponding to the capacities and models of the indoor units 4, 5 and the outdoor unit 2, then the volumes of the refrigerant communication pipes 6 and 7 (more specifically, the volume Vlp of the liquid refrigerant communication pipe 6 and the volume Vgp of the gas refrigerant communication pipe) are calculated using the above described calculation equations, based on the communication pipe refrigerant quantity Mp, the densities ⁇ lp and pgp determined in Step S23 and the volume ratio Rv.
Figure 7 is a flowchart of the refrigerant leak detection operation mode.
the normal operation mode when operation in the normal operation mode such as the above described cooling operation and heating operation has gone on for a certain period of time (for example, half a year to a year), the normal operation mode is automatically or manually switched to the refrigerant leak detection operation mode, and as is the case with the refrigerant quantity judging operation of the initial refrigerant quantity detection operation, the refrigerant quantity judging operation, including the all indoor unit operation, condensation pressure control, liquid pipe temperature control, superheat degree control, and evaporation pressure control, is performed.
values that are the same as the target values in Step S11 of the refrigerant quantity judging operation of the automatic refrigerant charging operation are used for the target liquid pipe temperature Tlps in the liquid pipe temperature control, the target superheat degree SHrs in the superheat degree control, and the target low pressure Pes in the evaporation pressure control.
this refrigerant quantity judging operation is performed for each time the refrigerant leak detection operation is performed. Even when the refrigerant temperature Tco at the outlet of the outdoor heat exchanger 23 fluctuates due to the different operating conditions, for example, such as when the condensation pressure Pc is different or when there is a refrigerant leak, the refrigerant temperature Tlp in the liquid refrigerant communication pipe 6 is maintained constant at the same target liquid pipe temperature Tlps by the liquid pipe temperature control.
Step S31 the process in Step S31 is performed by the controller 8 that functions as the refrigerant quantity judging operation controlling means for performing the refrigerant quantity judging operation, including the all indoor unit operation, condensation pressure control, liquid pipe temperature control, superheat degree control, and evaporation pressure control.
the refrigerant quantity in the refrigerant circuit 10 is calculated from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10 in the refrigerant leak detection operation in Step S32 by the controller 8 that functions as the refrigerant quantity calculating means during performing the above described refrigerant quantity judging operation.
Calculation of the refrigerant quantity in the refrigerant circuit 10 is performed by using the above described relational expression between the refrigerant quantity in each portion in the refrigerant circuit 10 and the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10.
the volumes Vlp and Vgp of the refrigerant communication pipes 6 and 7, which were unknown at the time of after installation of constituent equipment of the air conditioner 1, have been calculated and the values thereof are known by the above described pipe volume calculation process.
the refrigerant quantities Mlp, Mgp in the refrigerant communication pipes 6 and 7 can be calculated, and further by adding the refrigerant quantity in each of the other portions (for the calculation of the refrigerant in each of other portions, see Step S12 of the automatic refrigerant charging operation), the refrigerant quantity in the entire refrigerant circuit 10 (hereinafter referred to as "tonal calculated refrigerant quantity M") can be calculated,
the refrigerant temperature Tlp in the liquid refrigerant communication pipe 6 is maintained constant at the target liquid pipe temperature Tlps by the liquid pipe temperature control. Therefore, regardless the difference in the operating conditions for the refrigerant leak detection operation, the refrigerant quantity Mlp in the liquid refrigerant communication pipe portion B3 will be maintained constant even when the refrigerant temperature Tco at the outlet of the outdoor heat exchanger 23 changes.
Step S32 the process in Step S32 is performed by the controller 8 that functions as the refrigerant quantity calculating means for calculating the refrigerant quantity at each portion in the refrigerant circuit 10 from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10 in the refrigerant leak detection operation.
the refrigerant quantity in the refrigerant circuit 10 decreases. Then, when the refrigerant quantity in the refrigerant circuit 10 decreases, mainly, a tendency of a decrease in the subcooling degree SC o at the outlet of the outdoor heat exchanger 23 appears. Along with this, the refrigerant quantity Mc in the outdoor heat exchanger 23 decreases, and the refrigerant quantities in other portions tend to be maintained substantially constant.
the total calculated refrigerant quantity M calculated in the above described Step S32 is smaller than the total charged refrigerant quantity Mt that is the refrigerant quantity in the entire refrigerant circuit 10 immediately after the automatic refrigerant charging operation is completed and that serves as a reference refrigerant quantity for judging whether or not there is a refrigerant leak; whereas when there is no refrigerant leak from the refrigerant circuit 10, the total calculated refrigerant quantity M has substantially the same value as the total charged refrigerant quantity Mt.
Step S33 whether or not there is a refrigerant leak is judged in Step S33.
Step S33 that there is no refrigerant leak from the refrigerant circuit 10
the refrigerant leak detection operation mode is finished.
Step S33 when it is judged in Step S33 that there is a refrigerant leak from the refrigerant circuit 10, the process proceeds to Step S34, and a warning indicating that a refrigerant leak is detected is displayed on the display 9b. Subsequently, the refrigerant leak detection operation mode is finished.
Steps S32 to S34 the process from Steps S32 to S34 is performed by the controller 8 that functions as the refrigerant leak detection means, which is one of the refrigerant quantity judging means, and which detects whether or not there is a refrigerant leak by judging the adequacy of the refrigerant quantity in the refrigerant circuit 10 during performing the refrigerant quantity judging operation in the refrigerant leak detection operation mode.
the controller 8 that functions as the refrigerant leak detection means, which is one of the refrigerant quantity judging means, and which detects whether or not there is a refrigerant leak by judging the adequacy of the refrigerant quantity in the refrigerant circuit 10 during performing the refrigerant quantity judging operation in the refrigerant leak detection operation mode.
the controller 8 functions as the refrigerant quantity judging operation means, the refrigerant quantity calculating means, the refrigerant quantity judging means, and the pipe volume calculating means, and thereby configures the refrigerant quantity judging system for judging the adequacy of the refrigerant quantity charged into the refrigerant circuit 10.
the air conditioner 1 in the present embodiment has the following characteristics.
the communication pipe refrigerant quantity Mp required for the calculation of the volumes of the refrigerant communication pipes 6 and 7 is determined by calculating the inside-unit refrigerant quantity Mu determined by the calculation above from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10 in the automatic refrigerant charging operation and subtracting the inside-unit refrigerant quantity Mu from the total charged refrigerant quantity Mt.
the refrigerant whose quantity is substantially equal to the inside-unit refrigerant quantity Mu that is present when the refrigerant quantity in the refrigerant circuit 10 is reached the target charging quantity Ms by the automatic refrigerant charging operation may be charged as the initial charging quantity Mi into the refrigerant circuit 10 before the automatic refrigerant charging operation (in other words, into the indoor units 4, 5 and the outdoor unit 2 to be shipped to the installation site) is performed.
the additional charging quantity Ma that is the refrigerant quantity to be additionally charged into the refrigerant circuit 10 in the automatic refrigerant charging operation can be regarded as being corresponding to the communication pipe refrigerant quantity Mp that is refrigerant quantity present in the refrigerant communication pipes 6 and 7. Therefore, unlike the above described embodiment, the need to calculate the communication pipe refrigerant quantity Mp using the inside-unit refrigerant quantity Mu and the total charged refrigerant quantity Mt will be eliminated, and thus the volumes of the refrigerant communication pipes 6 and 7 can be easily calculated.
the target charging quantity Ms by the automatic refrigerant charging operation is charged as the initial charging quantity Mi in the refrigerant circuit 10 before the automatic refrigerant charging operation (in other words, into the indoor units 4 and 5 and the outdoor unit 2 to be shipped to the installation site), in the above described embodiment, as described above, the inside-unit refrigerant quantity Mu is calculated from the operation state quantity of constituent equipment or refrigerant flowing in the refrigerant circuit 10 in the automatic refrigerant charging operation. Therefore, even under various conditions of the initial charging quantity Mi, it is possible to determine a correct value of the communication pipe refrigerant quantity Mp, and it is possible to calculate the volumes of the refrigerant communication pipes 6 and 7 with high accuracy.
the present invention is applied to an air conditioner capable of switching and performing the cooling operation and heating operation.
the present invention may be applied to different types of air conditioners such as a cooling only air conditioner and the like.
an example in which the present invention is applied to an air conditioner including a single outdoor unit is described.
the present invention may be applied to an air conditioner including a plurality of outdoor units.
the labor of inputting information on the refrigerant communication pipe before the operation of a separate type air conditioner is minimized, and at the same time, the adequacy of the refrigerant quantity in the refrigerant circuit can be judged with high accuracy.

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Engineering & Computer Science (AREA)
Physics & Mathematics (AREA)
Mechanical Engineering (AREA)
Thermal Sciences (AREA)
General Engineering & Computer Science (AREA)
Air Conditioning Control Device (AREA)

EP07767400.0A 2006-06-26 2007-06-22 Klimaanlage Withdrawn EP2034261A4 (de)

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
JP2006175083A JP4155313B2 (ja)	2006-06-26	2006-06-26	空気調和装置
PCT/JP2007/062589 WO2008001687A1 (fr)	2006-06-26	2007-06-22	Climatiseur

Publications (2)

Publication Number	Publication Date
EP2034261A1 true EP2034261A1 (de)	2009-03-11
EP2034261A4 EP2034261A4 (de)	2014-07-30

Family

ID=38845453

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP07767400.0A Withdrawn EP2034261A4 (de)	2006-06-26	2007-06-22	Klimaanlage

Country Status (7)

Country	Link
US (1)	US20090100849A1 (de)
EP (1)	EP2034261A4 (de)
JP (1)	JP4155313B2 (de)
KR (1)	KR101207004B1 (de)
CN (1)	CN101473177B (de)
AU (1)	AU2007264431B2 (de)
WO (1)	WO2008001687A1 (de)

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Also Published As

Publication number	Publication date
WO2008001687A1 (fr)	2008-01-03
US20090100849A1 (en)	2009-04-23
EP2034261A4 (de)	2014-07-30
KR20090027223A (ko)	2009-03-16
AU2007264431B2 (en)	2010-04-29
CN101473177B (zh)	2011-01-26
JP4155313B2 (ja)	2008-09-24
JP2008002786A (ja)	2008-01-10
CN101473177A (zh)	2009-07-01
KR101207004B1 (ko)	2012-11-30
AU2007264431A1 (en)	2008-01-03

Publication	Publication Date	Title
AU2007264431B2 (en)	2010-04-29	Air conditioner
EP1970655B1 (de)	2019-04-24	Klimaanlage
EP1970652B1 (de)	2019-03-27	Klimaanlage
EP1970653B1 (de)	2018-08-22	Klimaanlage
AU2007244357B2 (en)	2010-04-22	Air conditioner
AU2007208727B2 (en)	2010-03-04	Air conditioner
EP1983280B1 (de)	2018-12-26	Klimaanlage
EP1970654B1 (de)	2019-08-07	Klimaanlage
JP5104225B2 (ja)	2012-12-19	空気調和装置
JP2007187442A (ja)	2007-07-26	空気調和装置
JP2007163102A (ja)	2007-06-28	空気調和装置
JP4826247B2 (ja)	2011-11-30	空気調和装置

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