JP2010261715A - Air conditioning device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioning device for stably carrying out control of liquid equalization and excessive coolant treatment during heating. <P>SOLUTION: In the air conditioner having a plurality of outdoor units 1a, 1b composed of at least compressors 2a, 2b, outdoor heat exchangers 4a, 4b, and accumulators 5a, 5b, flow regulating valves 5a, 5b for regulating a coolant amount flowing into each outdoor unit 1a, 1b are respectively equipped between common liquid piping 11 and each outdoor heat exchanger 4a, 4b of each outdoor unit 1a, 1b. It includes a controller 14 determining whether or not degrees of superheat of outlet sides of the outdoor heat exchanger 4a, 4b of the outdoor units 1a, 1b are within a range wherein a certain value is an upper limit, determining whether degrees of discharge superheat of the compressors 2a, 2b are within a constant range, and regulating openings of the flow regulating valves 5a, 5b such that the degrees of superheat of outlet sides of the outdoor heat exchangers 4a, 4b are within the range and the degrees of discharge superheat of the compressors 2a, 2b are within the certain range on the basis of a combination of determination results. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an air conditioner configured by connecting a plurality of outdoor units and a plurality of indoor units with a common gas pipe and a common liquid pipe, and is particularly a problem in heating. The present invention relates to liquid / surplus refrigerant processing.

  2. Description of the Related Art Conventionally, an air conditioner that includes a plurality of outdoor units, a plurality of indoor units, a common gas pipe, and a common liquid pipe has been developed in order to meet the increase in capacity of the air conditioner. In this type of air conditioner, the accumulator (gas-liquid separator) of each outdoor unit is controlled by a liquid equalizing pipe by controlling the refrigerant circulation rate by means of the compressor rotation speed, fan rotation speed, opening degree of the external unit decompression device, etc. Since the liquid equalization / excess refrigerant processing during heating is performed without connection, there are some which are good in terms of workability and cost (for example, see Patent Document 1).

  In addition, in other conventional air conditioners, in order to perform liquid leveling and surplus refrigerant processing, there is also a device that controls the opening degree of the flow rate adjustment valve of the outdoor unit with the target of superheat in a compressor or the like (for example, Patent Documents). 2 and 3).

Japanese Patent Laid-Open No. 11-142010 (1-6, 10, 11 Mitsugu, FIGS. 1-8, 13) Japanese Patent Laid-Open No. 8-200809 (5-12 Mitsugu, Fig. 1) Japanese Patent Laying-Open No. 2005-121361 (4-9 Mitsugu, Fig. 1)

  In conventional air conditioners, for the treatment of liquid equalization and surplus refrigerant during heating, the flow distribution to multiple outdoor units is controlled by controlling the compressor rotation speed, fan rotation speed, outdoor unit decompression device opening, etc. In order to make the degree of superheat on the outlet side of the machine heat exchanger equal in each outdoor unit, there are the following problems.

  First, since the target value of the absolute value of the superheat degree is not set, the reliability of the compressor (outdoor unit) can be reduced by reducing the capacity due to high dryness or overflowing the refrigerant accumulated in the accumulator due to excessive moisture. There is a risk of damage. In addition, the refrigerant flow rate adjustment for adjusting the degree of superheat and the refrigerant flow rate control according to the load fluctuation on the indoor unit side cannot be taken, resulting in failure to follow up or taking time. In the worst case, all the excess refrigerant may be stored in one outdoor unit. Therefore, in order to prepare for this, it is necessary to sufficiently increase the volume of the accumulator of each outdoor unit.

  In the above air conditioner, the refrigerant flow rate is controlled by the liquid level detector provided in the accumulator. However, considering the cost, productivity and reliability of the liquid level detector, the volume of the accumulator is reduced. It is practical to make it sufficiently large so that the liquid refrigerant does not overflow. However, this is not consistent with the current situation where compactness and cost reduction are required.

  In other conventional air conditioners, the accumulator is used to protect the liquid back at the start-up even if the opening of the flow control valve of the outdoor unit is controlled. Since it is necessary to provide these together, it becomes expensive.

  In view of the above problems, an object of the present invention is to stably perform control of liquid equalization / excess refrigerant processing during heating.

  An air conditioner according to the present invention is an air conditioner having a plurality of outdoor units each including at least a compressor, an outdoor heat exchanger, and an accumulator, and is provided between a common liquid pipe and each outdoor heat exchanger of each outdoor unit. Each having a flow rate adjusting valve for adjusting the amount of refrigerant flowing into each outdoor unit, and the degree of superheat on the outlet side of the outdoor heat exchanger of each outdoor unit is within a range having a certain value as an upper limit. And whether or not the discharge superheat degree of the compressor is within a certain range, and the superheat degree on the outlet side of the outdoor heat exchanger is within the range based on the combination of the respective judgment results. And the control apparatus which adjusts the opening degree of each flow regulating valve so that the discharge superheat degree of a compressor may fall in a fixed range is provided.

  According to the present invention, the degree of opening of the flow rate adjustment valve is adjusted moderately, and on the outlet side of the outdoor heat exchanger, the degree of dryness is controlled to a low degree of superheat in the vicinity of 1, whereby the outdoor heat exchanger that is an evaporator is used. It is possible to operate stably in a substantially constant state while ensuring sufficiently high performance. In addition, by controlling the degree of discharge superheat of the compressor within a certain range, the liquid refrigerant does not overflow from the accumulator, and reliability can be ensured and stable operation can be achieved. And since control is performed so that the degree of superheat and the like is the same in each outdoor unit, the amount of refrigerant in each outdoor unit can be made substantially uniform. As a result, liquid leveling and surplus refrigerant processing can be performed by calculation in the control device without further equipment such as a receiver, and the volume of the accumulator is not changed according to the capacity of the entire air conditioner. Therefore, low cost and downsizing can be realized.

It is a block diagram which shows the air conditioning apparatus which concerns on Embodiment 1 of this invention. It is a figure which shows the structure of the control apparatus 14 in air_conditionaing | cooling operation. It is a figure which shows the structure of the control apparatus 14 in heating operation. It is a Mollier diagram which shows the refrigerant | coolant state of a part of this air conditioning apparatus. It is a figure showing the state of the outdoor unit when the opening degree of a flow regulating valve is changed. It is a figure showing the flowchart which the control apparatus 14 which concerns on this Embodiment performs. It is a figure showing the example of classification of the state of outdoor units 1a and 1b. It is a figure showing the flowchart at the time of comprising three outdoor units. It is a figure showing the other example of the arrangement | positioning position of temperature sensor 20e, 20f. FIG. 10 is a diagram illustrating a sensor arrangement position regarding a compressor according to a third embodiment. It is a figure showing the other example of the arrangement | positioning position of the sensor regarding a compressor. It is a figure showing the flowchart which the control apparatus 14 which concerns on Embodiment 4 performs.

Embodiment 1 FIG.
1 is a block diagram showing an air conditioner according to Embodiment 1 of the present invention. Embodiment 1 of the present invention will be described below. Here, it is assumed that two outdoor units and two indoor units are connected. In FIG. 1, 1a and 1b are outdoor units, 8p and 8q are indoor units, 22a and 22b are gas branch pipes exiting from each outdoor unit, 24p and 24q are gas branch pipes exiting from each indoor unit, and 7 is a gas branch pipe 22a. , 22b and the gas branch pipes 24p and 24q are connected to a common gas pipe, 13 is a connection point between the gas branch pipes 22a and 22b and the common gas pipe 7, and 23a and 23b are liquid branch pipes exiting from the outdoor units, 25p. , 25q is a liquid branch pipe coming out from each internal unit, 11 is a common liquid pipe connecting the liquid branch pipes 23a and 23b and the liquid branch pipes 25p and 25q, and 12 is a liquid pipe 11 common to the liquid branch pipes 23a and 23b. Connection point. In the present embodiment, a pipe through which a liquid (including a gas-liquid two-phase case) including the above pipes is referred to as a liquid pipe, and a pipe through which gas passes is referred to as a gas pipe.

  In the outdoor units 1a and 1b, 2a and 2b are compressors, and on the discharge side of the compressors 2a and 2b, 15a and 15b are oil separators, 3a and 3b are four-way valves that are flow rate switching valves, 4a, 4b is an outdoor heat exchanger, 17a and 17b are high and low pressure heat exchangers, and 5a and 5b are flow rate adjusting valves, which are sequentially connected to the liquid branch pipes 23a and 23b. The flow rate adjusting valves 5a and 5b may be connected between the heat exchangers 4a and 4b and the high and low pressure heat exchangers 17a and 17b. On the suction side of the compressors 2a and 2b, 6a and 6b are accumulators, which are sequentially connected to the four-way valves 3a and 3b and the gas branch pipes 22a and 22b. Reference numerals 16a and 16b denote oil return bypass circuits, one of which is connected to the lower inner side of the oil separators 15a and 15b and the other is connected to the suction side piping of the compressors 2a and 2b. Reference numerals 14a and 14b denote control devices (details will be described later).

  18a and 18b are flow rate adjusting valves, which branch from between the high and low pressure heat exchangers 17a and 17b and the liquid branch pipes 23a and 23b. The flow rate adjusting valves 18a and 18b, the high and low pressure heat exchangers 17a and 17b, the accumulator 6a, 6b and the four-way valves 3a and 3b are connected in order so as to join a pipe connecting the four-way valves 3a and 3b. 6c and 6d are oil return holes of the accumulators 6a and 6b, and are provided in the lower part of a U-shaped tube connected to the suction side of the compressors 2a and 2b.

  In the indoor units 8p and 8q, 9p and 9q are indoor heat exchangers, 10p and 10q are expansion valves, which are connected in order from the gas branch pipes 24p and 24q coming out of the indoor units 8p and 8q to the liquid branch pipe. The Reference numerals 14p and 14q denote control devices (details will be described later).

  Here, the compressors 2a and 2b have an inverter circuit, and the number of revolutions is controlled by the conversion of the power supply frequency by the inverter circuit, and the capacity control is performed. The flow rate adjusting valves 5a, 5b, 18a, 18b, and the expansion valves 10p, 10q are electronic expansion valves whose opening degree is controlled variably. These controls are performed by the control devices 14a, 14b, 14p and 14q described above.

  The pressure sensors in the outdoor units 1a and 1b are provided at 19a and 19b on the discharge side of the compressors 2a and 2b, and 19c and 19d on the suction side of the compressors 2a and 2b, respectively. Send a signal based on the measurement. As for the temperature sensors in the outdoor units 1a and 1b, 20a and 20b are the discharge sides of the compressors 2a and 2b, 20c and 20d are the suction sides of the compressors 2a and 2b, and 20e and 20f are the gases of the outdoor heat exchangers 4a and 4b. 20 g, 20 h are liquid side outlets of the outdoor heat exchangers 4 a, 4 b, 20 i, 20 j are 20 k between the high and low pressure heat exchangers 17 a, 17 b, the flow regulating valves 5 a, 5 b and the flow regulating valves 18 a, 18 b. , 20l are provided between the connecting pipes of the accumulators 6a and 6b and the four-way valves 3a and 3b and the high and low pressure heat exchangers 17a and 17b, respectively, and measure the temperature at the installation location. The temperature sensors 20m and 20n measure the ambient temperature of the outdoor units 1a and 1b, and transmit signals based on the measurements.

  The temperature sensors in the indoor units 8p and 8q are provided at 20p and 20q at the gas side outlet of the indoor heat exchangers 9p and 9q, and 20r and 20s at the liquid side outlet of the indoor heat exchangers 9p and 9q, respectively. Measure the temperature of the place.

  As described above, the outdoor units 1a and 1b and the indoor units 8p and 8q are respectively provided with the control devices 14a, 14b, 14p, and 14q configured by a microcomputer, for example, and the pressure sensor 19 and the temperature sensor 20 are provided. Based on the detected data, the operation content (load request) instruction from the user of the air conditioner, the operation of starting and stopping the compressors 2a and 2b, the flow switching of the four-way valves 3a and 3b, the outdoor heat The amount of heat exchange in the exchangers 4a and 4b, the opening degree of the expansion valves 10p and 10q, the opening degree of the flow rate adjusting valves 5a, 5b, 18a and 18b, and the like are controlled. And control device 14a, 14b, 14p, 14q shall be able to transmit / receive the communication containing various data etc., for example. In the following description, the control device 14 will be described when the entire control of each of the control devices 14a, 14b, 14p, and 14q is summarized. Here, although each control apparatus 14a, 14b, 14p, 14q is divided and installed in each outdoor unit 1a, 1b and indoor unit 8p, 8q, you may install collectively. Further, each device may be controlled by one device. The internal configuration for executing the function of the control device 14 will be described later.

  Next, the operation of the air conditioner will be described. First, the operation during the cooling operation will be described. In the four-way valves 3a and 3b, pipes are connected in the direction of the solid line in FIG. Further, the flow rate adjusting valves 5a and 5b are set to a fully closed state or almost fully opened state, the flow rate adjusting valves 18a and 18b are set to appropriate opening degrees, and the expansion valves 10p and 10q are set to appropriate opening degrees. The refrigerant flow in this case is as follows.

  The refrigerant of high-pressure and high-temperature gas discharged from the compressors 2a and 2b passes through the oil separators 15a and 15b. At this time, approximately most of the refrigerating machine oil mixed in the refrigerant is separated from the refrigerant, stored in the bottom of the inside, passes through the oil return bypass circuits 16a and 16b, and is returned to the suction pipes of the compressors 2a and 2b. Thereby, the refrigeration oil which flows out of the outdoor units 1a and 1b can be reduced, and the reliability of the compressor can be improved.

  On the other hand, the high-pressure and high-temperature refrigerant in which the ratio occupied by the refrigerating machine oil passes through the four-way valves 3a and 3b, is condensed and liquefied by the outdoor heat exchangers 4a and 4b, and passes through the high and low pressure heat exchangers 17a and 17b. One of the flows branched out of the high and low pressure heat exchangers 17a and 17b is moderately adjusted in flow rate by the flow rate adjusting valves 18a and 18b to become a low pressure and low temperature refrigerant, and the refrigerant flowing out of the outdoor heat exchangers 4a and 4b is high. Since heat is exchanged in the low-pressure heat exchangers 17a and 17b, the enthalpy is higher in the refrigerant state at the outlet side of the high- and low-pressure heat exchangers 17a and 17b than in the refrigerant state at the outlet side of the outdoor heat exchangers 4a and 4b. Lower. The low-pressure refrigerant passing through the flow rate adjusting valves 18a and 18b and exiting the high- and low-pressure heat exchangers 17a and 17b reaches a pipe connecting the accumulators 6a and 6b and the four-way valves 3a and 3b. Thereby, since the enthalpy difference increases, the required refrigerant flow rate in the case of the same capacity can be reduced, and there is an effect of performance improvement by reducing pressure loss. Here, the high pressure and the low pressure represent the relative relationship of the pressure in the refrigerant circuit (the same applies to the temperature).

  On the other hand, the high-pressure refrigerant that has exited the high-low pressure heat exchangers 17a and 17b passes through the flow rate adjusting valves 5a and 5b. However, since the flow rate adjusting valves 5a and 5b are fully opened, Supplied to the liquid pipe 11. Then, it enters into the indoor units 8p and 8q, is decompressed by the expansion valves 10p and 10q, becomes a low-pressure two-phase refrigerant, is evaporated and gasified by the indoor heat exchangers 9p and 9q, and is connected to the gas pipe 7, four-way valves 3a and 3b, accumulator. It passes through 6a and 6b and is sucked into the compressors 2a and 2b.

  Here, when the two-phase refrigerant flows into the accumulators 6a and 6b, the liquid refrigerant accumulates in the lower part of the container, and the gas-rich refrigerant flowing in from the upper opening of the U-shaped pipe is sucked into the compressors 2a and 2b. The liquid back of the compressors 2a and 2b can be temporarily prevented until the transient liquid or the two-phase refrigerant is accumulated in the accumulators 6a and 6b and overflows, and the effect of maintaining the reliability of the compressor is obtained. It is done.

  Also, the refrigeration oil that could not be separated by the oil separators 15a and 15b circulates in the refrigerant circuit and accumulates in the accumulators 6a and 6b. When a certain amount of refrigerating machine oil stays, it is returned to the compressors 2a and 2b through the U-shaped pipe return holes 6c and 6d located below the upper opening of the U-shaped pipe. Refrigerating machine oil staying in the accumulators 6a and 6b can be reduced, and an effect of improving the reliability of the compressor and improving the cost by reducing the oil amount of the refrigerating machine oil can be obtained. However, liquid refrigerant staying in the lower part or dissolved in the refrigerating machine oil is also sucked into the compressors 2a and 2b through the U-shaped pipe return holes 6c and 6d, but an appropriate U-shaped pipe return hole shape is set. Thus, it can have a function of returning only the refrigerating machine oil with an appropriate degree of suction dryness.

  FIG. 2 is a diagram illustrating a configuration of the control device 14 in the cooling operation. Next, the control operation performed by the control device 14 in this air conditioner will be described. In the cooling operation, the indoor heat exchangers 9p and 9q serve as an evaporator, and the evaporation temperature (two-phase refrigerant temperature of the evaporator) is set so that a predetermined heat exchange capability is exhibited here, and this evaporation temperature is realized. The pressure value to be set is set as the low pressure target value. The compressor control means 30 controls the rotation speed of the compressors 2a and 2b by an inverter circuit. The operating capacities of the compressors 2a and 2b are controlled so that the pressure measured by the pressure sensors 19c and 19d becomes a predetermined target value, for example, a pressure corresponding to a saturation temperature of 10 ° C. In addition, the condensing temperature (condenser two-phase refrigerant temperature) also changes due to the rotational speed control. To ensure performance and reliability, a certain range is set as the condensing temperature, and the pressure value that realizes this condensing temperature is set. Set as the high pressure target value. The number of rotations of the fan and the pump flow rate for conveying air or water as a heat transfer medium are determined in advance from the heat exchange amounts of the outdoor heat exchangers 4a and 4b and the heat exchange amounts of the indoor heat exchangers 9p and 9q. Originally, the pressure measured by the pressure sensors 19a and 19b is controlled to be within the target range by the compressor control means 30 and the outdoor heat exchange amount control means 31.

  Further, the expansion valve 10p, 10q is calculated by (temperature of the temperature sensor 20p) − (temperature of the temperature sensor 20r), (temperature of the temperature sensor 20q) − (temperature of the temperature sensor 20s) by the superheat degree control means 32. The opening degree is controlled so that the degree of superheat at the outlets of the indoor heat exchangers 9p and 9q becomes a target (temperature) value. As this target value, a predetermined target value, for example, 5 ° C. is used. By controlling to the target outlet superheat degree, the proportion of the refrigerant in the two-phase state in the indoor heat exchangers 9p and 9q can be maintained in a preferable state.

  The flow rate adjusting valves 5a and 5b are controlled by the flow rate control means 34 to a predetermined initial opening degree, for example, an opening degree close to or fully open. The flow rate adjusting valves 18a and 18b are controlled by the high / low pressure heat exchanger superheat degree control means 33 (temperature of the temperature sensor 20g) − (saturation temperature converted from the pressure measured by the pressure sensor 19c), (temperature sensor 20i). Of the low pressure side outlet through which the low pressure refrigerant of the high and low pressure heat exchangers 17a and 17b calculated by (the saturation temperature converted from the pressure measured by the pressure sensor 19d) is a predetermined target. The opening degree is controlled to be a value. Although the target value can be arbitrarily determined, for example, 2 ° C. is used here. Thereby, the heat exchange corresponding to the specification of the high-low pressure heat exchangers 17a and 17b can be realized. Here, the compressor control means 30, the outdoor heat exchange amount control means 31, the high and low pressure heat exchanger superheat degree control means 33, and the flow rate control means 34 are provided in the control means 14a and 14b in each of the outdoor units 1a and 1b. The superheat degree control means 32 is provided in the control means 14p, 14q of the indoor units 8p, 8q.

  Next, the heating operation will be described. In the four-way valves 3a and 3b, pipes are connected in the direction of broken lines in FIG. The flow rate adjusting valves 5a and 5b adjust the flow rate appropriately so that the refrigerant distribution state in the outdoor unit is the same in each outdoor unit, and the opening degree is such that an appropriate differential pressure is generated before and after the flow rate adjusting valves 5a and 5b. Is preset. The flow rate adjusting valves 18a and 18b are fully closed, and the expansion valves 10p and 10q are set to appropriate opening degrees.

  The refrigerant flow in this case is as follows. The refrigerant of the high-pressure high-temperature gas discharged from the compressors 2a and 2b flows into the gas pipe 7 through the oil separators 15a and 15b and the four-way valves 3a and 3b. The oil separators 15a and 15b perform the same operation as in the above cooling operation. The gas refrigerant supplied to the indoor unit 8 through the gas pipe 7 is condensed and liquefied by the indoor heat exchangers 9p and 9q in the indoor units 8p and 8q, and then depressurized by the expansion valves 10p and 10q. It becomes a two-phase refrigerant close to saturation. The intermediate-pressure refrigerant passes through the liquid pipe 11, is distributed to the outdoor units 1a and 1b, and flows into the outdoor units 1a and 1b. Since the refrigerant flow rates of the outdoor units 1a and 1b are appropriately adjusted by the flow rate adjusting valves 5a and 5b, the refrigerant passing through the flow rate adjusting valves 5a and 5b is in a low-pressure two-phase state. The refrigerant in the low-pressure two-phase state passes through the high- and low-pressure heat exchangers 17a and 17b, evaporates in the outdoor heat exchangers 4a and 4b, is gasified, passes through the accumulators 6a and 6b, and passes through the compressors 2a and 2b. Inhaled. The accumulators 6a and 6b perform the same operation as in the cooling operation described above. Since the flow rate adjusting valves 18a and 18b are fully closed and there is no flow, heat exchange between the refrigerants is not performed in the high and low pressure heat exchangers 17a and 17b. On the contrary, if there is a flow, the performance decreases as the heat is exchanged.

  Next, the control operation performed by the control device 14 in this air conditioner will be described. FIG. 3 shows a configuration of the control device 14 in the heating operation. In the heating operation, the indoor heat exchangers 9p and 9q are condensers, and therefore, the condensation temperature is set so that a predetermined heat exchange amount is exhibited, and the high pressure value that realizes the condensation temperature is set as the high pressure target value. Set as. The compressor control means 30 controls the rotational speed of the compressors 2a and 2b by an inverter circuit. The operating capacities of the compressors 2a and 2b are controlled so that the high pressure value measured by the pressure sensors 19a and 19b becomes a predetermined target value, for example, a pressure corresponding to a saturation temperature of 50 ° C. At the same time, the evaporation temperature of the outdoor heat exchangers 4a and 4b changes due to the rotational speed control, but a certain range is set to ensure capacity and reliability, and the pressure value that realizes this evaporation temperature is set as the low pressure target value. Set. By means of the compressor control means 30 and the outdoor heat exchange amount control means 31, the number of rotations of the fan and the pump flow rate for conveying the heat transfer medium such as air and water can be changed to the heat exchange amount of the outdoor heat exchangers 4 a and 4 b and the indoor heat. Based on a predetermined state based on the heat exchange amounts of the exchangers 9p and 9q, control is performed so that the low pressure value measured by the pressure sensors 19c and 19d is within the target range.

  Further, by the supercooling degree control means 35, the expansion valves 10p, 10q are (saturated temperature converted from the pressure measured by the pressure sensor 19p) − (temperature of the temperature sensor 20r), (pressure measured by the pressure sensor 19q). (Saturation temperature converted from) − (temperature of temperature sensor 20s), the degree of subcooling on the outlet side of indoor heat exchangers 9p and 9q (hereinafter referred to as indoor heat exchanger outlet subcooling degree) is a target value ( The opening degree is controlled to be (temperature). As this target value, a predetermined target value, for example, 10 ° C. is used. Further, the flow rate adjusting valves 18a and 18b are controlled to be fixed at an initial opening predetermined by the high / low pressure heat exchanger superheat degree control means 33, for example, an opening that is fully closed or close to being fully closed. Moreover, the flow control means 34 calculates the compressor discharge superheat degree and evaporator outlet superheat degree which are mentioned later, and controls the opening degree of the flow regulating valves 5a and 5b. Here, the compressor control means 30, the outdoor heat exchange amount control means 31, the high and low pressure heat exchanger superheat degree control means 33, and the flow rate control means 34 are provided in the control means 14a and 14b in each of the outdoor units 1a and 1b. The supercooling degree control means 35 is provided in the control means 14p, 14q of the indoor units 8p, 8q.

  Here, looking at the difference between the heating operation and the cooling operation, a high-pressure liquid refrigerant exists in the liquid pipe 11 in the cooling operation, whereas a two-phase refrigerant close to an intermediate-pressure liquid phase or saturated liquid in the liquid pipe 11 in the heating operation. Exists. Therefore, in the heating operation, the amount of refrigerant flowing in the liquid pipe 11 is smaller than in the cooling operation, and surplus refrigerant generated accordingly is accumulated as liquid refrigerant in the accumulators 6a and 6b. In the air conditioner having a large capacity, the common liquid pipe 11, liquid branch pipes 23a and 23b, and the liquid branch pipes 25p and 25q have increased pipe diameters and pipe lengths. The amount of surplus refrigerant will further increase.

  Therefore, the outdoor flow rate control means 34 performs an operation based on the pressure value from the pressure sensor 19 and the temperature value from the temperature sensor 20 to adjust the opening degree of the flow rate adjustment valves 5a and 5b, and the total amount of surplus refrigerant, It controls how much surplus refrigerant exists in the accumulators 6a and 6b of the outdoor units 1a and 1b. In general, the volume of the heat exchanger is larger in the outdoor heat exchangers 4a and 4b than in the indoor heat exchangers 9p and 9q. Since the indoor heat exchangers 9p and 9q are used as condensers during heating, the volume difference becomes an excess refrigerant in the heat exchanger during heating. The volume of the accumulators 6a and 6b is obtained by multiplying the sum of the surplus refrigerant in the heat exchanger and the surplus refrigerant in the liquid pipe by the safety factor. This safety factor includes that the air conditioner is conventionally configured as a single outdoor unit, the flow rate adjusting valves 5a and 5b are not present, and the surplus refrigerant in the liquid pipe is increased.

  Although there are various heat exchanger volumes, liquid pipe lengths, refrigerant charge amounts, etc., the air conditioner capacity combined with them is almost linear, and the surplus refrigerant amount is also based on the capacity of the air conditioner Can be estimated. When an air conditioner is configured by one outdoor unit, an accumulator having a volume corresponding to the capacity may be provided, and the capacity of the accumulator may be increased as the capacity increases. Here, when a large-capacity air conditioner is configured by a plurality of outdoor units and sufficient liquid leveling control is performed, each outdoor unit may have a capacity of an accumulator that matches the capacity of each outdoor unit. On the other hand, if liquid leveling control does not function sufficiently even with the same configuration, the accumulator of each outdoor unit must take into account the worst situation, and must have a capacity when an air conditioner having the same capacity is configured with one outdoor unit. . As described above, depending on whether the liquid leveling control is good or not, the total volume of the accumulator in the air conditioner varies greatly even if the amount of generated surplus refrigerant is the same, which affects cost and compactness. Therefore, in the present embodiment, control is performed so that liquid leveling control functions sufficiently.

  FIG. 4 is a Mollier diagram showing the refrigerant state from the condenser to the evaporator by changing the opening of the flow rate adjusting valve. Based on FIG. 4, the relationship between the opening degree of the flow regulating valves 5a and 5b and the amount of refrigerant in the liquid pipe will be described. Here, the evaporating pressure and the condensing pressure are approximately constant, and it is the expansion valve pressure loss, liquid pipe pressure loss, and flow rate adjustment valve pressure loss that occupy the high and low differential pressures. Originally, O, A, and B are on substantially the same enthalpy line, but are shifted to distinguish.

  In the state O on the Mollier diagram, when the opening degree of the flow rate adjusting valves 5a and 5b is decreased from this state, the state changes to the A side. At this time, the pressure difference between the refrigerant before and after passage through the flow rate adjusting valves 5a and 5b increases, and the difference in height is constant, so the pressure difference between the refrigerant before and after passage through the expansion valves 10p and 10q also decreases. The opening of 10p, 10q increases. Further, the density in the liquid pipe increases due to the increase in the liquid pipe pressure and the decrease in the dryness, and the amount of refrigerant existing in the liquid pipe increases. Furthermore, liquid pipe pressure loss is also reduced due to a decrease in dryness in the liquid pipe.

  Conversely, when the opening degree of the flow rate adjusting valves 5a, 5b is increased from the state O, the state on the Mollier diagram changes to the B side. At this time, the pressure difference between the refrigerant before and after passing through the flow rate adjusting valves 5a and 5b decreases and the difference in height is constant, so the pressure difference between the refrigerant before and after passage through the expansion valves 10p and 10q also increases. The opening degree of 10p and 10q decreases. Moreover, the density in a liquid pipe | tube reduces by the fall of a liquid pipe | tube pressure, and dryness increase, and the refrigerant | coolant amount which exists in a liquid pipe | tube reduces. Further, the liquid pipe pressure loss increases due to the increase in the dryness in the liquid pipe.

  FIG. 5 is a diagram illustrating state quantities in the outdoor units 1a and 1b when the opening degree of the flow rate adjusting valves 5a and 5b is changed. As shown in FIG. 4, when the opening degree of the flow rate adjusting valves 5a and 5b is decreased, the refrigerant amount in the liquid pipe is increased. Until the opening degree A in the figure, the amount of liquid refrigerant in the accumulators 6a and 6b decreases due to the increase in refrigerant in the liquid pipe. The refrigerant is present in the accumulators 6a and 6b, and the dryness on the suction side of the compressors 2a and 2b (hereinafter referred to as compressor suction dryness) is close to 1, and as a result, on the discharge side of the compressors 2a and 2b. The degree of superheat (hereinafter, referred to as compressor discharge superheat degree) slightly increases in the vicinity of a certain value, and the reliability of the compressors 2a and 2b is ensured. Further, there is no change in the refrigerant retention amount in the outdoor heat exchangers 4a and 4b, which are evaporators, and the outlet dryness (hereinafter referred to as evaporator outlet superheat degree) is close to 0, and the heat exchange performance is high.

  If the decrease in the opening degree of the flow rate adjusting valves 5a and 5b exceeds the opening degree A and no liquid refrigerant exists in the accumulators 6a and 6b, the refrigerant retention amount in the outdoor heat exchangers 4a and 4b is reduced, and the evaporator Outlet superheat increases. Since the heat exchange capacity of the outdoor heat exchangers 4a and 4b is lowered and the evaporation temperature is also lowered, the heating capacity is lowered and the performance (COP: coefficient of performance) is lowered. Further, the compressor discharge superheat degree and the compressor suction dryness greatly increase, and there is a risk that the temperature in the compressor rises and the reliability is impaired. Moreover, although it is necessary to increase the opening degree of the expansion valves 10p and 10q, it finally becomes a state of full open or nearly full open, and the indoor heat exchanger outlet subcooling degree of the indoor heat exchangers 9a and 9b which are condensers May exceed the target value, and the required heating capacity may not be exhibited. Further, it becomes impossible to distribute the refrigerant flow rate to the outdoor units 1a and 1b by controlling the opening of the expansion valves 10p and 10q.

  Conversely, when the opening degree of the flow rate adjusting valves 5a and 5b is increased, the amount of refrigerant in the liquid pipe decreases. Until the opening degree B in the figure, the amount of liquid refrigerant in the accumulators 6a and 6b increases due to the decrease in the refrigerant in the liquid pipe. For this reason, the liquid level in the accumulators 6a and 6b is increased, but the gas-liquid separation of the accumulators 6a and 6b is functioning, and the compressor suction dryness is close to 1. As a result, the compressor discharge superheat is close to a constant value. Therefore, the reliability of the compressors 2a and 2b is ensured. There is no change in the refrigerant retention amount of the outdoor heat exchangers 4a and 4b, the evaporator superheat degree is close to 0, and the heat exchange performance is high.

  Further, when the increase in the opening degree of the flow rate adjusting valves 5a and 5b exceeds the opening degree B and the gas-liquid distribution of the accumulators 6a and 6b stops functioning, the refrigerant is transferred to the outdoor heat exchangers 4a and 4b instead of the accumulators 6a and 6b. It begins to stay, and the degree of superheat of the evaporator outlet does not change, but the outlet side of the outdoor heat exchangers 4a and 4b enters a liquid back state. Furthermore, the compressor discharge superheat degree and the compressor suction dryness are greatly reduced, and the reliability of the compressors 2a and 2b may be impaired.

  As mentioned above, if the opening degree of the flow regulating valves 5a and 5b is adjusted within the range of the opening degree A and the opening degree B of FIG. 5 which is a preferable state, the evaporator superheat degree of the outdoor heat exchangers 4a and 4b is set. It is possible to control the degree of superheat in the vicinity of 1, and to control the compressor discharge superheat to a certain value or higher, or to control the compressor suction dryness in the vicinity of 1. Processing can be realized. This is not only due to the configuration of the two outdoor units 1a and 1b as in the present embodiment, but the same can be said for an air conditioner having three or more outdoor units.

  FIG. 6 is a diagram illustrating a flowchart regarding control processing performed by the control device 14 according to the present embodiment. Based on FIG. 6, the control performed by the control device 14 (particularly the control devices 14a and 14b), particularly the control of the opening degree of the flow rate adjusting valves 5a and 5b performed by the outdoor flow rate control means 34 will be described. First, in step S0, the compressors 2a, 2b, etc. are activated and the heating operation by the air conditioner is started. In step S1, each control means constituting the control device 14 sets a fixed value by initial setting according to the initial state detection of each sensor.

  Next, in step S2, it is determined whether or not a certain time (for example, 5 minutes, 10 minutes, etc.) has elapsed since the start of the operation of the air conditioner. Here, at the start of the heating operation, if the flow rate adjusting valves 5a and 5b are set to an opening degree at which a differential pressure is generated before and after the flow regulating valves 5a and 5b, the refrigerant becomes low pressure and forms frost, resulting in a decrease in capacity. There is a risk of starting failure such as it takes time to recover to the low pressure target value and further recovery is impossible. Therefore, for example, when the heating operation is started, the flow rate adjustment valves 5a and 5b are fully opened or close to full opening, so that the above-described deterioration in performance and startup failure can be prevented. Thereafter, the flow rate adjusting valves 5a and 5b are maintained in a fully opened state or a state close to a fully opened state until the control by the outdoor flow rate control unit 34 is performed.

  If it is determined that a certain period of time has elapsed after the start of operation in step S2, based on information (data) such as the usage status (load) of each pressure sensor 19 and temperature sensor 20 and indoor units 8p and 8q in step S3. Control means other than the outdoor flow rate control means 34 controls each control object. In step S4, the passage of time is determined based on the time interval for controlling the flow rate adjusting valves 5a and 5b. Here, the other flow rate control unit 34 is executed every time interval (for example, 1 minute) at which each control command is issued, whereas the outdoor flow rate control unit 34 has a sufficiently larger time interval (for example, 5 minutes). ), Steps S5a and S5b are executed to control the flow rate adjusting valves 5a and 5b. This is to prevent the occurrence of hunting and stabilize the control, as will be described later. In the following steps, the outdoor flow rate control means 34 controls the flow rate adjustment valves 5a and 5b, but the same control is not performed on both the flow rate adjustment valves 5a and 5b. Control is performed in accordance with the state of each device of the outdoor units 1a and 1b.

  As the contents of steps S5a and S5b performed by the outdoor flow rate control means 34, first, in steps S6a and S6b, the degree of superheat of the evaporator outlet in the outdoor heat exchangers 4a and 4b of the outdoor units 1a and 1b is determined (of the temperature sensor 20e). (Temperature)-(saturation temperature converted from pressure measured by pressure sensor 19c), (temperature of temperature sensor 20f)-(saturation temperature converted from pressure measured by pressure sensor 19d). Further, the compressor discharge superheat degree of the compressors 2a and 2b is expressed as (temperature of the temperature sensor 20a) − (saturation temperature converted from the pressure measured by the pressure sensor 19a), (temperature of the temperature sensor 20b) − (pressure sensor). (Saturation temperature converted from the pressure measured in 19b)). Here, regarding the saturation temperature, the control device 14 (outdoor flow rate control means 34) stores the data of the pressure-saturation temperature conversion table in the storage means (not shown), and based on the measured pressure value. Perform conversion.

  FIG. 7 is a diagram illustrating a classification example of the states of the outdoor units 1a and 1b, which are determination criteria for performing the opening operation of the flow rate adjusting valves 5a and 5b. On the basis of the compressor discharge superheat degree and the evaporator outlet superheat degree calculated in steps S7a and S7b, the state of the outdoor units 1a and 1b corresponds to any of the five states of state A to state E as shown in FIG. Judge whether to do. Here, one threshold value (for example, 30 ° C.) is provided for the compressor discharge superheat degree, and two threshold values (for example, 2 ° C. and 5 ° C.) are provided for the evaporator outlet superheat degree. Note that the equal sign is substantially meaningless and may belong to a classification of numerical values having a threshold value larger or smaller than that.

State A is
Compressor discharge superheat <30 ° C (threshold) and
0 ≦ Evaporator outlet superheat <2 ° C. (Threshold 1)
This is the state. The compressor suction state is the liquid back state, and this state will continue in the future.
State B is
Compressor discharge superheat <30 ° C (threshold) and
2 ° C (threshold 1) ≤ evaporator outlet superheat <5 ° C (threshold 2)
This is the state. The compressor inhalation state is damp, but the evaporator outlet dryness is high to some extent, so that the inhalation moist state may be eliminated over time.
State C is
Compressor discharge superheat <30 ° C (threshold) and
Evaporator outlet superheat> 5 ° C (threshold 2)
This is the state. Although the compressor inhalation state is damp, the evaporator outlet dryness is high, so that over time, the intake moist state may become a high dry state and performance may be degraded.
State D is
Compressor discharge superheat degree ≧ 30 ° C. (threshold) and
0 ≦ Evaporator outlet superheat <5 ° C. (Threshold 2)
This is the state. The performance can be ensured when the evaporator outlet dryness is almost zero, and the compressor suction state is good.
State E is
Compressor discharge superheat degree ≧ 30 ° C. (threshold) and
Evaporator outlet superheat> 5 ° C (threshold 2)
This is the state. In the state E, the compressor suction state is considerably dry, and there is no surplus refrigerant in the accumulators 6a and 6b, which may cause a decrease in performance.

Based on the determinations in steps S7a and S7b, it is determined whether the flow rate adjusting valves 5a and 5b are increased or decreased. The amount of change in the opening / closing increase / decrease is, for example, about 5% different from that before the change. here,
In the case of the state A, since the flow rate adjustment valve is too open, it is determined that the opening degree is to be decreased (steps S8a and S8b).
In the case of state B, it is determined that there is no need to change the opening degree of the flow control valve (steps S9a, S9b).
In the state C, it is determined that the opening degree is increased because the flow control valve is excessively throttled. (Steps S10a, S10b)
In the state D, it is determined that the opening degree of the flow rate control valve is a desirable state and is not changed (steps S9a and S9b).
In the case of the state E, since the flow rate adjustment valve is too narrowed, it is determined that the opening degree is to be increased (steps S10a and S10b).

  Next, in steps S11a and 11b, an upper limit value and a lower limit value of the opening degree of the flow rate adjusting valves 5a and 5b are obtained. The opening range of the flow rate adjusting valves 5a and 5b may be fixed. However, as will be described later, the preferable range of FIG. 5 is not uniquely determined, so the opening range of the flow rate adjusting valves 5a and 5b is adjusted. It is better to do it. Here, if step S11a, 11b is after step S3, you may make it calculate in the step before this. In steps S12a and 12b, it is determined whether the opening when increasing, decreasing, or maintaining is within the range defined by the upper limit value and the lower limit value. If not, the opening is corrected. If the opening is less than or equal to the lower limit, the opening is corrected to the lower limit (S13a, S13b). If the opening is equal to or greater than the upper limit, the opening is corrected to the upper limit (S14a, S14b). In steps S15a and S15b, a command is transmitted to the flow rate adjusting valves 5a and 5b, and the flow rate adjusting valves 5a and 5b are controlled to have the determined opening. And it returns to step S3 again and starts a process in order.

  The outdoor flow rate control means 34 controls the flow rate adjusting valves 5a and 5b as described above, and the compressor discharge superheat degree is set to a predetermined value or higher, so that the compressor suction dryness can be kept high. In order to improve the reliability of 2a and 2b, particularly to ensure the reliability of the bearing portion, there is an effect of ensuring the lubricating performance of the refrigerating machine oil necessary for the actual operation. Moreover, by setting the evaporator outlet superheat degree to a low superheat degree in the vicinity of 1, the heat exchange performance in the outdoor heat exchangers 4a and 4b can be kept high, and the performance of the entire air conditioner can be improved.

  Moreover, since a large capacity air conditioner is configured by the plurality of outdoor units 1a and 1b, it is necessary to increase the capacity of the accumulator in order to process a large amount of refrigerant and to treat surplus refrigerant. However, the opening degree of the flow rate adjusting valves 5a and 5b is controlled so that the compressor discharge superheat is a certain value or more and the evaporator outlet is in a low superheat state near the dryness 1 (state D described above). Thus, the refrigerant distribution state in each of the outdoor units 1a and 1b can be made to be the same (uniform) state, and the refrigerant can be distributed to the outdoor units 1a and 1b without significant deviation (surplus). For this reason, what is necessary is just to provide the accumulator 6a, 6b of the capacity | capacitance according to the capability of the outdoor unit in each outdoor unit 1a, 1b. Therefore, it is not necessary to divide the volume of the accumulator with an outdoor unit of the same capacity depending on whether it is used by one unit or a plurality of units, and the effects of productivity improvement and cost reduction can be obtained. In addition, the compressor discharge superheat degree strongly depends on the discharge and suction pressure during the compressor operation, in addition to the compressor suction dryness.

  Here, since it is known that the lower the compression ratio, the lower the compressor discharge superheat degree, the lower the threshold value for the compressor discharge superheat degree when operating in an environment where the outside air temperature is low such as during heating. You may correct | amend as follows.

  Next, a temporal change in the control of the flow rate adjusting valves 5a and 5b will be described. When the superheat degree of the evaporator outlet of the outdoor heat exchangers 4a and 4b changes, liquid refrigerant exists in the accumulators 6a and 6b, and when the liquid level changes, the U-tubes in the accumulators 6a and 6b change. Gas-liquid separation works, and the change in compressor suction dryness is small. On the other hand, when the liquid refrigerant does not exist in the accumulators 6a and 6b or overflows and the gas-liquid separation does not function, the compressor suction dryness greatly changes. As described above, the superheat degree at the outlet of the evaporator affects the dryness of the compressor, but a large change in the dryness of the suction of the compressor causes a time delay corresponding to the volume of the accumulators 6a and 6b.

  Further, as shown in FIG. 5, when the change in the compressor suction dryness is small, the change in the compressor discharge superheat is also small, but as the compressor suction dryness decreases from 1, the compressor discharge superheat degree The change of becomes larger. The change in the compressor discharge superheat is reflected in the change in the compressor suction dryness without causing a delay. When the state of the outdoor units 1a and 1b is within the preferable range shown in FIG. 5, the state change is small, and even if the control time interval of the flow rate adjusting valves 5a and 5b is large, sufficient control is possible. On the other hand, when it is out of the range of the preferable state or is likely to be out of the range, in the state of high humidity (right side from B) where the compressor suction dryness is low, the compressor discharge superheat is not delayed in time, and the compressor suction Even when the control time interval of the flow rate adjusting valves 5a and 5b is large by providing two threshold values for the evaporator outlet superheat degree in the state of the high dry side where the dryness is high (left side from A). Fully controllable.

  Further, the compressor capacity (operating frequency) control performed by the compressor control means 30 and the opening control of the expansion valves 10p, 10q performed by the indoor supercooling degree control means 35 as described above are the times when commands to be controlled are issued. The pipe pressure loss and the expansion valve differential pressure shown in FIG. 4 change at short time intervals in synchronization with the control. If the flow rate adjusting valves 5a and 5b are controlled in accordance with these time intervals, the differential pressure may also change in a short time, and these changes may affect each other, resulting in hunting and the like, and control may not be stable. There is. Therefore, the opening control of the flow rate adjusting valves 5a and 5b is performed with a command time interval larger than that of the capacity control of the compressors 2a and 2b and the opening control of the expansion valves 10p and 10q. Stable control can be realized by slowing the change and preventing the occurrence of hunting.

  Next, individual opening ranges of the flow rate adjusting valves 5a and 5b will be described. The range of the preferable state of FIG. 5 is not uniquely determined, and the opening ranges of the flow rate adjusting valves 5a and 5b are not necessarily constant. Although the opening range of the preferable state of FIG. 5 may be determined for each actual use condition, in reality, there are many factors that change the opening range and are complicated. Therefore, it is necessary to focus on specific factors. Here, since the state on the Mollier diagram does not change greatly even if the opening range is not constant, for example, the lower limit side is set to 0.5 MPa and the upper limit side is set to 1.4 MPa so that the differential pressure is as constant as possible. Determine. For this purpose, it is necessary to assume the refrigerant flow rate. Therefore, the capacity (load) required for the outdoor units 1a and 1b, the outside air temperature, the suction pressure, the refrigerant evaporation temperature, the compressor operating frequency, and the like are the factors for specifying the opening range. Become. Further, not only the opening range but also the opening may be corrected.

  Here, when the opening range of the margin is determined in consideration of various variations in the actual use conditions, it is the use outside the assumed actual use conditions that falls outside the opening range. Therefore, it can be determined that the operation should not be continued. Thus, the setting of the opening range has an effect of ensuring performance and reliability as a pawl for unexpected use. Moreover, the stable control can be implemented according to the change of actual use conditions by changing the opening of the flow control valves 5a and 5b according to the change of the opening range. The model configuration of the outdoor units 1a and 1b is usually similar to the rated capacity of the compressor, heat exchanger, accumulator, etc., so that it can be opened based on the required load capacity and outside air temperature regardless of the model. It is possible to set the degree range, to reduce the development load, and to improve the productivity by sharing the control specifications.

  As described above, according to the air conditioner of Embodiment 1, the outdoor flow rate control means 34 of the control device 14 is based on the physical quantity obtained from the measurement of the pressure sensor 19, the temperature sensor 20, etc. Calculating and calculating the compressor discharge superheat degree, determining whether the flow rate adjusting valves 5a and 5b are open or closed, and appropriately adjusting them, thereby adjusting the outdoor heat exchangers 4a and 4b in the outdoor units 1a and 1b. On the outlet side, the degree of dryness in the vicinity of a dryness of 1 is controlled so that the refrigerant present in the outdoor heat exchangers 4a and 4b can be stably operated while maintaining a sufficiently high performance in a substantially constant state. And by controlling the compressor discharge superheat degree of the compressors 2a and 2b within a certain range, the liquid refrigerant does not overflow from the accumulators 6a and 6b, and the operation of the outdoor unit is ensured and the operation is stable. Can be done. And since the evaporator outlet superheat degree and the compressor discharge superheat degree were made constant in the outdoor units 1a and 1b, the refrigerant amounts in the outdoor units 1a and 1b can be made substantially uniform. Furthermore, since liquid equalization and surplus refrigerant processing can be performed by calculation in the control device, it is not necessary to newly provide a device such as a receiver, so that low cost and the like can be realized.

  In addition, since the upper limit value and the lower limit value of the opening degree are provided, for example, unexpected use that exceeds the opening degree can be prevented, and reliability can be ensured. And since the opening degree and the opening degree range were correct | amended, the opening degree of the flow regulating valves 5a and 5b can be adjusted to a more preferable range. And, in the correction of the opening range and the opening degree, attention is paid to the refrigerant flow rate as many factors, and the correction is performed based on the data related to the refrigerant flow rate such as required capacity and outside air temperature. Even if a complicated opening degree range is not calculated using factors, it is possible to correct the opening range and the opening degree almost appropriately. And since the opening degree control of the flow control valves 5a and 5b as described above is performed and the refrigerant in each of the outdoor units 1a and 1b can be evenly distributed according to the capacity, the volume of the accumulators 6a and 6b Product costs and product sizes can be reduced without increasing the use and usage of multiple units in parallel, without changing specifications, etc., and productivity can be increased.

Embodiment 2. FIG.
FIG. 8 is a diagram illustrating a flowchart relating to control processing performed by the control device 14 in the case where three outdoor units are configured. Based on FIG. 8, control performed by the control device 14, particularly control of the opening degree of the flow rate adjusting valve performed by the outdoor flow rate control means 34 will be described. By configuring the air conditioner with a plurality of outdoor units, as described above, the opening range in a preferable state of FIG. 5 is not uniquely determined by each flow rate adjustment valve. And the opening range of each flow regulating valve also depends on the relative relationship between the opening of other flow regulating valves. The refrigerant in the gas-liquid two-phase state branched at the connection point 12 is unevenly distributed, and the calculated opening degree of the flow rate adjustment valve tends to exceed the range of the upper limit value and the lower limit value of the opening degree determined in advance. Even in this case, more optimal liquid equalization / surplus refrigerant processing can be performed by performing the following correction on the opening degree of each flow rate adjustment valve. Here, although not particularly illustrated, the third outdoor unit is assumed to be the outdoor unit 1c, and c is added to the reference numeral for each means in the outdoor unit 1c.

First, the processing from steps S20 to S30 is the same as the processing from steps S0 to S10 shown in FIG. After step S30, in steps S31a, S31b, and S31c, the outdoor flow rate control means 34 of the control devices 14a, 14b, and 14c calculates the upper limit value and the lower limit value of the opening degree for each of the flow rate adjustment valves 5a, 5b, and 5c. . In S32, an index for determining which outdoor unit the flow rate adjustment valve has the most protruding opening is obtained by calculation or the like. Any of the control devices 14a, 14b, and 14c may perform the process for obtaining the index. For example, the largest value of (the lower limit value L _{min of the} opening degree obtained for the flow rate adjusting valves 5a, 5b, 5c) − (the opening degree L of the flow rate adjusting valves 5a, 5b, 5c) is taken as the index δ _min . In addition, the largest value among (opening degree L of the flow rate adjusting valves 5a, 5b, 5c) − (upper limit value L _{max of the} opening degree obtained for the flow rate adjusting valves 5a, 5b, 5c) is set as an index δ _max .

In step S33, it is determined whether or not δ _min ≧ 0 (whether there is a flow rate adjusting valve that is going to exceed the lower limit value). If δ _min ≧ 0, the opening L of the flow rate regulating valves 5a, 5b, 5c determined in steps S34a, S34b, S34c is within the range between the lower limit value L _min and the upper limit value L _max , and FIG. Whether or not the state is in the state A indicated by 7 is determined. If it is determined that this condition is satisfied, in step S43, a command is transmitted to the flow rate adjusting valves 5a, 5b, and 5c, and the flow rate adjusting valves 5a, 5b, and 5c are controlled so that the obtained opening degree L is obtained. If it is determined that this condition is not satisfied, in steps S35a, S35b, and S35c, the opening degree obtained by adding δ _min to the opening degree L is corrected to the opening degree L again. Then, further steps S36a, S36b, in S36c, the corrected opening L is determined whether larger than the upper limit L _max, not greater, in step S43, and transmits the flow control valve 5a, 5b, an instruction to 5c The flow rate adjusting valves 5a, 5b, and 5c are controlled so that the corrected opening degree L is obtained. On the other hand, if the corrected angle L is greater than the upper limit value L _max, step S37a, S37b, and a correction to set the upper limit L _max on the opening L in S37c, in step S43, the flow control valve 5a, 5b, and 5c A command is transmitted to control the flow rate adjusting valves 5a, 5b, and 5c so that the corrected opening degree L (upper limit value L _max ) is obtained. After controlling the flow rate adjusting valves 5a, 5b, and 5c as described above, the process returns to step S23 and processing is started in order.

On the other hand, if it is determined in step S33 that δ _min ≧ 0, it is determined in step S38 whether δ _max ≧ 0 (whether there is a flow rate adjustment valve that exceeds the upper limit value). If δ _max ≧ 0, the opening degree L of the flow rate regulating valves 5a, 5b, 5c determined in steps S39a, S39b, S39c is within the range between the lower limit value L _min and the upper limit value L _max , and FIG. Whether the state is in the state C or E shown in FIG. If it is determined that this condition is satisfied, in step S43, a command is transmitted to the flow rate adjusting valves 5a, 5b, and 5c, and the flow rate adjusting valves 5a, 5b, and 5c are controlled so that the obtained opening degree L is obtained. If it is determined that this condition is not satisfied, in steps S40a, S40b, and S40c, the opening degree obtained by subtracting δ _max from the opening degree L is corrected to the opening degree L again. Further, in steps S41a, S41b, and S41c, it is determined whether or not the corrected opening degree L is larger than the lower limit L _min. If not, the command is transmitted to the flow rate adjusting valves 5a, 5b, and 5c in step S43. The flow rate adjusting valves 5a, 5b, and 5c are controlled so that the corrected opening degree L is obtained. On the other hand, if the corrected opening degree L is larger than the lower limit value L _min , the upper limit value L _max is corrected to the opening degree L in steps S42a, S42b, S42c, and in step S43, the flow rate adjusting valves 5a, 5b, 5c are changed. A command is transmitted, and the flow rate adjusting valves 5a, 5b, and 5c are controlled so that the corrected opening degree L (lower limit value L _min ) is obtained. After controlling the flow rate adjusting valves 5a, 5b, and 5c as described above, the process returns to step S23 and processing is started in order.

If it is determined in step S38 that δ _max ≧ 0, the flow rate adjusting valves 5a, 5b, and 5c are controlled so as to obtain the obtained opening degree L. After controlling the flow rate adjusting valves 5a, 5b, and 5c as described above, the process returns to step S23 and processing is started in order.

  For example, because of irregular factors such as the installation work of the air conditioner or the distribution of the liquid refrigerant before the start of operation, there is a connection point 13 between the liquid pipe that exits the outdoor unit and the common liquid pipe. In some cases, the two-phase refrigerant biased in the liquid rich state is distributed to the outdoor unit (for example, the outdoor unit 1a). At this time, for example, the outdoor flow rate control unit 34 may make an opening degree lower than a predetermined lower limit value by determining to reduce the opening degree of the flow rate adjustment valve 5a. At this time, in this embodiment, the opening amount exceeding the lower limit value is added to the opening amounts of the other flow rate adjustment valves, and the flow rate adjustment valve 5a is set to the lower limit value. Therefore, in each flow regulating valve 5a, 5b, 5c, the relative opening relationship between the flow regulating valves 5a, 5b, 5c is expanded and the total opening is reduced without departing from the opening range. As a result, the excess refrigerant is reduced, so that it is possible to deal with refrigerant distribution that is liquid-rich.

  Conversely, when the gas-rich two-phase refrigerant is distributed to a certain outdoor unit (for example, the outdoor unit 1a), the outdoor flow rate control unit 34 determines, for example, that the opening degree of the flow rate adjustment valve 5a is increased at this time. In some cases, the opening degree may exceed the predetermined upper limit value. At this time, in the present embodiment, the flow rate adjusting valve 5a is set to the opening upper limit value by subtracting the opening amount exceeding the upper limit value from the opening amounts of the other flow rate adjusting valves. Therefore, in each flow regulating valve 5a, 5b, 5c, the relative opening relationship between the flow regulating valves 5a, 5b, 5c is expanded and the total opening is increased without departing from the opening range. Therefore, it is possible to reduce the degree of dryness and deal with refrigerant distribution that is biased toward gas richness.

  FIG. 9 is a diagram illustrating another example of the arrangement positions of the temperature sensors 20e and 20f. In FIG. 1, in order to measure the degree of superheat of the evaporator outlet, the temperature sensors 20e and 20f are arranged on the pipes where the paths (piping etc.) passing through the outdoor heat exchangers 4a and 4b are gathered. Yes. Since the degree of superheat varies depending on each pass, the temperature based on the average degree of superheat at the outlet of the evaporator can be measured if it is disposed in a portion where the passes are gathered.

  On the other hand, in FIG. 9, the temperature sensors 20e and 20f are arranged in a path where the degree of superheat is likely to occur (the temperature is high). If such an arrangement is made, the temperature of the path with a high degree of superheat in the outdoor heat exchangers 4a and 4b will be measured, so even if the same temperature as the temperature arranged in the part where each path is gathered is measured. The average evaporator outlet superheat degree based on the temperature is low. Therefore, in the outdoor heat exchangers 4a and 4b, it can be dealt with after determining that the proportion of the two-phase refrigerant is large, so that there is an effect of maintaining high heat exchange performance.

  As described above, in the air conditioner of Embodiment 2, when the set opening range protrudes (exceeds) due to the opening control of the flow rate adjusting valves 5a, 5b, 5c, If the opening degree of the other flow rate control valve can be increased / decreased, the absolute value of the opening degree is not changed, and the outdoor units 1a, 1b, 1c are controlled. By adjusting the relative change between them and the sum of the opening degree of the flow rate adjusting valves 5a, 5b, and 5c, it is possible to perform the liquid equalization / surplus refrigerant processing with higher accuracy by cooperation.

Embodiment 3 FIG.
FIG. 10 is a diagram illustrating the positions of sensors related to the compressors 2a and 2b according to the third embodiment. In the above-described embodiment (particularly Embodiment 1), the compressor discharge superheat degree is calculated by subtracting the saturation temperature converted from the pressure measured by the pressure sensors 19a and 19b from the temperature of the temperature sensors 20a and 20b. . In the present embodiment, temperature sensors 20t and 20u are provided on the surface of the compressor shell where the refrigerating machine oil of the compressors 2a and 2b accumulates, and the flow rate adjusting valve 5a is determined by determining the degree of superheat of the compressor shell surface temperature in the compressor shell. The opening degree control of 5b is implemented.

  Here, about the pressure sensors 19c and 19d, if it is the suction | inhalation side of the outdoor units 1a and 1b, it is not necessary to be a specific location. As described above, the pressure value is converted into the saturation temperature based on the pressure-saturation temperature conversion table. The compressor shell surface temperature superheat degree is obtained based on the difference between the saturation temperature and the temperature value obtained by the temperature sensors 20t and 20u. As shown in FIG. 10, the pressure values measured by the pressure sensors 19 c and 19 d are used because the refrigerating machine oil is accumulated in the low-pressure spaces in the compressors 2 a and 2 b. When refrigerating machine oil is accumulated in the high-pressure space in the compressors 2a and 2b, the saturation temperature converted from the temperature value obtained by the temperature sensors 20t and 20u and the pressure measured by the pressure sensors 19a and 19b is calculated. To determine the shell surface temperature superheat.

  And the outdoor flow control means 34 controls the opening degree of the flow control valves 5a and 5b using the compressor shell surface temperature superheat degree instead of the compressor discharge superheat degree. Here, in FIG. 7, the threshold value of the compressor discharge superheat degree is set at 30 ° C., for example, but the threshold value of the compressor shell surface temperature superheat degree may be set at 10 ° C., for example.

  In securing the reliability of the compressors 2a and 2b, the lubricating performance of the refrigerating machine oil during actual operation particularly necessary for securing the bearing reliability has a correlation with the compressor discharge superheat degree. However, the correlation varies depending on the actual operating state of the compressors 2a and 2b, particularly the temperature distribution inside the compressor, depending on the refrigerant circulation amount. Moreover, recent compressors have low efficiency of compressor discharge superheat due to high efficiency such as DC brushless motors, and there is an error when judging the compressor suction dryness based on the compressor discharge superheat. Therefore, it is possible to realize liquid leveling and surplus refrigerant control with high accuracy by judging the factors of change and error in the correlation with the lubricant performance based on the compressor shell surface temperature superheat degree lower than the compressor discharge superheat degree. There is. Further, the reliability of the compressors 2a and 2b (particularly bearings) can be ensured.

  FIG. 11 is a diagram illustrating another example of the sensor arrangement positions related to the compressors 2a and 2b. In FIG. 11, instead of arranging the temperature sensors 20t and 20u on the surface of the compressor shell where the refrigerating machine oil accumulates, oil temperature sensors 21a and 21b that can directly measure the temperature of the refrigerating machine oil are used. Is. The degree of superheat of the refrigerating machine oil is obtained using the temperature value obtained by measurement by the oil temperature sensors 21a and 21b and the saturation temperature converted from the pressure measured by the pressure sensors 19a and 19b.

  And the outdoor flow control means 34 controls the opening degree of the flow control valves 5a and 5b using the superheat degree of refrigeration oil instead of the compressor discharge superheat degree. Here, in FIG. 7, the threshold value of the compressor discharge superheat degree is set at 30 ° C., for example, but the threshold value of the superheat degree of the refrigerating machine oil may be set at 5 ° C., for example.

  In order to ensure the bearing reliability of the compressors 2a and 2b, the required lubrication performance of the refrigeration oil during actual operation has a correlation with the degree of superheat of the compressor shell surface temperature. The correlation varies depending on the refrigerant flow inside the machine and the oil return to the compressor. By detecting the superheat degree of the refrigeration oil that is lower than the superheat degree of the compressor shell surface as a factor of change and error of the correlation with the lubricating oil performance, it is possible to realize liquid leveling and surplus refrigerant control with high accuracy. Further, the reliability of the compressors 2a and 2b (particularly bearings) can be ensured.

  As described above, according to the air conditioner of Embodiment 3, the compressor shell surface temperature superheat degree is calculated, and the flow rate adjusting valve 5a is calculated based on the compressor shell surface temperature superheat degree instead of the compressor discharge superheat degree. Since the opening control of 5b is performed, liquid leveling and surplus refrigerant control is performed more than the compressor discharge superheat degree, which may include an error in judgment due to the low superheat degree due to the high efficiency of the compressor. This can be realized with high accuracy, and the reliability of the compressors 2a and 2b (particularly bearings) can be ensured. Further, the effect can be further enhanced by controlling the opening of the flow rate adjusting valves 5a and 5b with the degree of superheat of the refrigeration oil that is less likely to contain an error than the degree of superheat of the compressor shell surface temperature. .

Embodiment 4 FIG.
FIG. 12 is a diagram illustrating a flowchart regarding control processing performed by the control device 14 according to the fourth embodiment. In the above-described embodiment (particularly Embodiment 1), for the purpose of distributing the surplus refrigerant in each outdoor unit 1a, 1b without unevenness, the compressor discharge superheat is set to a certain value or more, and the evaporator outlet superheat is The opening degree of the flow rate adjusting valves 5a and 5b is controlled so as to be close to zero. In the present embodiment, the flow rate adjusting valves 5a and 5b are used for the purpose of accumulating excess refrigerant in the accumulator 6a of one outdoor unit (for example, the outdoor unit 1a) and preventing the surplus refrigerant from accumulating in the remaining outdoor units. To control the opening degree. The basic configuration of the air conditioner is the same as that shown in FIG. 1, but the volume of the accumulator 6a of the outdoor unit 1a that is intended to store excess refrigerant is assumed to be large in proportion to the excess refrigerant that is to be stored.

  First, the processing from steps S50 to S54 is the same as the processing from steps S0 to S4 shown in FIG. After step S54, the outdoor flow rate control means 34 determines the opening degree of the flow rate adjustment valve 5a in the outdoor unit 1a that accumulates excess refrigerant, and the opening degree of the flow rate adjustment valve 5b in the other outdoor units. The determination is divided into step S55b to be performed.

  As contents of step S55a performed by the outdoor flow rate control means 34, first, in step S56a, the evaporator outlet superheat in the outdoor heat exchanger 4a of each outdoor unit 1a and the compressor discharge superheat degree of the compressor 2a are calculated. The calculation method is the same as described above.

  In step S57a, the state of the outdoor unit 1a is determined from the three classifications. When it is determined that the evaporator superheat degree is smaller than the lower limit value of a predetermined range (hereinafter referred to as the first range) or the compressor discharge superheat degree is smaller than a predetermined threshold value, In step S58a, it is determined that the opening degree of the flow rate adjustment valve 5a is to be decreased. In step S61a, a command is transmitted to the flow rate adjustment valve 5a, and the flow rate adjustment valve 5a is controlled to have the determined opening degree. If it is determined that the evaporator outlet superheat degree is within the first range, it is determined in step S59a that the opening degree of the flow rate adjustment valve 5a is maintained, and a command is transmitted to the flow rate adjustment valve 5a in step S61a. Then, the flow rate adjustment valve 5a is controlled to maintain the opening degree. If it is determined that the degree of superheat of the evaporator outlet is greater than the upper limit of the first range, it is determined in step S60a that the opening degree of the flow rate adjustment valve 5a is to be increased. In step S61a, a command is sent to the flow rate adjustment valve 5a. And the flow rate adjustment valve 5a is controlled to have the determined opening degree.

  On the other hand, as the content of step S55b performed by the outdoor flow rate control means 34, first, in step S56b, the evaporator outlet overheat in the outdoor heat exchanger 4b of each outdoor unit 1b is calculated. The calculation method is the same as described above.

  In step S57b, the state of the outdoor unit 1b is determined from the three classifications. If it is determined that the evaporator outlet superheat degree is smaller than the lower limit of a predetermined range (hereinafter referred to as the second range), it is determined in step S58b that the opening degree of the flow rate adjustment valve 5b is decreased, In step S61b, a command is transmitted to the flow rate adjusting valve 5b, and the flow rate adjusting valve 5b is controlled to have the determined opening. If it is determined that the evaporator outlet superheat degree is within the second range, it is determined in step S59b that the opening degree of the flow rate adjustment valve 5b is maintained, and a command is transmitted to the flow rate adjustment valve 5b in step S61b. Then, the flow rate adjustment valve 5b is controlled to maintain the opening degree. If it is determined that the degree of superheat of the evaporator outlet is larger than the upper limit value of the second range, it is determined in step S60b that the opening degree of the flow rate adjustment valve 5b is increased. In step S61b, a command is sent to the flow rate adjustment valve 5b. And the flow rate adjustment valve 5b is controlled to have the determined opening degree.

  Here, at least the upper limit value of the second range is larger than the upper limit value of the first range. For example, if the lower limit of the first range is 0 ° C. and the upper limit is 2 ° C., the lower limit of the second range is 2 ° C., and the upper limit is 5 ° C. Thereby, since the opening degree of the flow control valve 5a will increase compared with the opening degree of the flow control valve 5b, a refrigerant | coolant will flow into the outdoor unit 1a side. And by keeping the ranges from overlapping,

  As described above, according to the fourth embodiment, an outdoor unit that stores excess refrigerant is specified, and the upper limit value that serves as a reference for increasing the opening degree of the flow rate adjustment valve is determined for the outdoor unit based on the degree of superheat of the evaporator outlet. Lowering the flow rate adjustment valve makes it easier to increase the opening of the flow rate adjustment valve than the flow rate adjustment valve of other outdoor units that do not accumulate excess refrigerant, and it is possible to accumulate excess refrigerant in a specific outdoor unit. It is easy to grasp the behavior of the refrigerant and has an effect of improving the accuracy of control.

Embodiment 5 FIG.
Here, the air conditioner has been described. The present invention is an air-conditioning apparatus for both heating and cooling that can use the indoor heat exchangers 4a and 4b as an evaporator and a condenser, and is particularly effective in a situation where there is a difference in surplus refrigerant. It can use also for the heat pump etc. which use the apparatus 4a, 4b as an evaporator.

  1a, 1b Outdoor unit, 2a, 2b Compressor, 3a, 3b Four-way valve, 4a, 4b Outdoor heat exchanger, 5a, 5b Flow control valve, 6a, 6b Accumulator, 6c, 6d U-shaped pipe oil return hole in accumulator 7 common gas piping, 8p, 8q indoor unit, 9p, 9q indoor heat exchanger, 10p, 10q expansion valve, 11 common liquid piping, 12 connection point between liquid piping coming out of outdoor unit and common liquid piping, 13 Connection point between gas piping coming out of outdoor unit and common gas piping, 14, 14a, 14b, 14p, 14q Control device, 15a, 15b Oil separator, 16a, 16b Oil return bypass circuit, 17a, 17b High-low pressure heat exchange 18a, 18b Flow rate adjusting valve, 19a, 19b, 19c, 19d Pressure sensor, 20a, 20b, 20c, 20d, 20e, 20f, 20g, 20h, 20i, 20j, 20k, 20l, 20m, 20n, 20p, 20q, 20r, 20s, 20t, 20u Temperature sensor, 21a, 21b Oil temperature sensor, 22a, 22b Gas branch pipe, 23a, 23b Liquid branch pipe, 24p 24q gas branch pipe, 25p, 25q liquid branch pipe, 30 compressor control means, 31 outdoor heat exchange amount control means, 32 indoor superheat degree control means, 33 high / low pressure heat exchanger superheat degree control means, 34 outdoor flow rate control means , 35 Indoor supercooling degree control means.

Claims (10)

In an air conditioner having a plurality of outdoor units configured at least from a compressor, an outdoor heat exchanger, and an accumulator,
Between the common liquid pipe and each outdoor heat exchanger of each outdoor unit, each has a flow rate adjustment valve for adjusting the amount of refrigerant flowing into each outdoor unit,
Further, it is determined whether the degree of superheat on the outlet side of the outdoor heat exchanger of each outdoor unit is within a range with an upper limit, and whether the discharge superheat degree of the compressor is within a certain range. And determining the degree of superheat on the outlet side of the outdoor heat exchanger within the range and the discharge superheat degree of the compressor within a certain range based on a combination of the determination results. An air conditioner comprising a control device for adjusting the opening of each flow rate adjustment valve. The control device, instead of keeping the discharge superheat degree of the compressor within a certain range,
The opening degree of the flow rate adjusting valve is adjusted so that the superheat degree of the surface of the compressor shell of the staying portion with respect to the pressure conversion saturation temperature in the portion of the compressor where the refrigerating machine oil stays is within a certain range. The air conditioning apparatus according to claim 1. The control device, instead of keeping the discharge superheat degree of the compressor within a certain range,
The opening degree of the flow rate adjusting valve is adjusted so that the degree of superheat of the refrigeration oil in the stagnation part with respect to the pressure-converted saturation temperature in the part where the refrigeration oil stays in the compressor is within a certain range. The air conditioning apparatus according to claim 1.   The air conditioner according to any one of claims 1 to 3, wherein the control device presets an opening range of the flow regulating valve.   The air conditioner according to claim 4, wherein the control device corrects an opening range of the flow rate adjusting valve of each outdoor unit based on a refrigerant flow rate flowing through each outdoor unit.   The air conditioning according to any one of claims 1 to 3, wherein the control device corrects an opening degree of the flow rate adjustment valve of each outdoor unit based on a refrigerant flow rate flowing through each outdoor unit. apparatus.   The refrigerant flow rate flowing through each outdoor unit is calculated based on one or more values of suction pressure, evaporation temperature, compressor operating frequency, outside air temperature, and required capacity. Air conditioner.   When the controller determines that there is an increase or decrease in the opening degree of the flow rate adjustment valve and determines that there is the flow rate adjustment valve that exceeds the set opening degree range, the control device changes the opening degree of the flow rate adjustment valve to the opening range. Determining whether the opening degree of the flow rate adjustment valve that does not exceed the opening degree range can be increased or decreased, and determining that the opening degree can be increased or decreased, increase or decrease the opening degree of the flow rate adjustment valve that does not exceed the opening degree range. The air conditioner according to claim 4, wherein   The air conditioning apparatus according to any one of claims 1 to 8, wherein a control interval related to an opening degree of the flow regulating valve is made longer than a control interval of other devices of the air conditioning apparatus.   The air conditioner according to any one of claims 1 to 9, wherein the accumulator of each outdoor unit is configured based on a volume of the accumulator required when each outdoor unit is configured as a single unit.

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