WO2016151655A1 - Air conditioning device and method for determining performance of same - Google Patents

Abstract

Disclosed is an air conditioning device wherein: a compressor, an indoor heat exchanger, an outdoor heat exchanger, and pipes that connect the compressor, the indoor heat exchanger, and the outdoor heat exchanger to each other are provided; the indoor heat exchanger and/or the outdoor heat exchanger has a first refrigerant path region, a second refrigerant path region, a first fan for performing forced air-cooling of the first refrigerant path region, and a second fan for performing forced air-cooling of the second refrigerant path region; the first refrigerant path region has a first refrigerant flow rate adjustment valve, and a first temperature detector that detects the outlet temperature of a refrigerant; the second refrigerant path region has a second refrigerant flow rate adjustment valve, and a second temperature detector that detects the outlet temperature of the refrigerant; and a control is performed by adjusting the opening degree of each of the first refrigerant flow rate adjustment valve and the second refrigerant flow rate adjustment valve and/or the rotation number of each of the first fan and the second fan so that a difference between the refrigerant outlet temperature obtained by the first temperature detector and the refrigerant outlet temperature obtained by the second temperature detector becomes small.

Description

AIR CONDITIONER AND ITS PERFORMANCE DETERMINING METHOD

The present invention relates to an air conditioner.

Patent Document 1 discloses an air conditioner including an outdoor unit having a compressor and an outdoor heat exchanger, and another heat exchanger, in which the outdoor heat exchanger is divided to increase the frontal area. What is arrange | positioned at 4 surfaces of the outer peripheral side of an outdoor unit housing | casing is disclosed.

Patent No. 3710874 gazette

In the prior art described in Patent Document 1, there is no disclosure of technology relating to a control method of a refrigeration cycle for a specific air conditioning only by a proposal of a structure.

An object of the present invention is to reduce the difference in refrigerant outlet temperature between two refrigerant path regions in an air conditioner having two refrigerant path regions in the indoor heat exchanger or the outdoor heat exchanger.

An air conditioner according to the present invention comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger, and a pipe connecting these, and at least one of the indoor heat exchanger and the outdoor heat exchanger is First refrigerant path area, second refrigerant path area, first fan for forced air cooling of first refrigerant path area, and second fan for forced air cooling of second refrigerant path area A first refrigerant path region having a first refrigerant flow control valve and a first temperature detector for detecting an outlet temperature of the refrigerant; and a second refrigerant path region having a fan; , A second refrigerant flow control valve, and a second temperature detector for detecting the outlet temperature of the refrigerant, and the opening degree of the first refrigerant flow control valve and the second refrigerant flow control valve and the first By adjusting at least one of the number of rotations of the second fan and the second fan, the first temperature detector can Ri resulting refrigerant outlet temperature and the difference between the second coolant outlet temperature obtained by the temperature detector is controlled to be small.

According to the present invention, in an air conditioner having two refrigerant path regions in the indoor heat exchanger or the outdoor heat exchanger, the difference between the refrigerant outlet temperatures of the two refrigerant path regions can be reduced.

FIG. 2 is a schematic view showing the configuration of the air conditioning apparatus of the first embodiment and the flow of a refrigerant during a cooling operation. FIG. 2 is a schematic view showing the configuration of the air conditioning apparatus of Embodiment 1 and the flow of the refrigerant during heating operation. FIG. 7 is a top view showing a specific configuration of the outdoor unit of Example 1; It is the figure which looked at the housing | casing 50 of the outdoor unit 3 of FIG. 2 from the front. It is sectional drawing which shows an example of arrangement | positioning of the internal component of the housing | casing 50 of FIG. FIG. 6 is a flowchart showing control under heating conditions of the outdoor unit of the first embodiment. FIG. 6 is a flow chart showing control of the outdoor unit of the first embodiment under cooling conditions. It is a flowchart which shows the case where the rotation speed of the 1st fan 5a of FIG. 1A and the 2nd fan 5b is controlled on cooling conditions. It is the schematic which shows the flow of a refrigerant | coolant when the amount of heat exchange is small at the time of heating operation of an air conditioning apparatus. It is the schematic which shows the example in case an air conditioning apparatus has two indoor units. It is a top view which shows the two outdoor units installed adjacently which comprise the air conditioning apparatus of Example 2. FIG. When an outdoor unit is installed in proximity, it is a flow figure showing control which distinguishes the open space side of an outdoor unit.

BACKGROUND OF THE INVENTION Field of the Invention The present invention relates to an air conditioner, and more particularly to improvement of energy saving according to air conditioning load.

Hereinafter, the outdoor unit of the air conditioning apparatus according to the embodiment of the present invention will be described in detail with reference to the drawings.

FIG. 1A is a schematic view showing the structure of an air conditioner (hereinafter also referred to as “air conditioner”) and the flow of refrigerant during cooling operation.

The air conditioner 1 is roughly divided into an indoor heat exchanger 4 in the indoor unit 1a, a compressor 2 and an outdoor heat exchanger 3 in the outdoor unit 1b, expansion valves 6a, 6b and 6c, and a four-way valve 5 And consists of. Inside the outdoor unit 1b, a first fan 5a and a second fan 5b are provided.

The outdoor heat exchanger 3 is branched from the refrigerant flow path and has two refrigerant path areas, and has a first refrigerant path area 3a and a second refrigerant path area 3b. The first refrigerant path region 3a is cooled or heated by forced convection by the first fan 5a. On the other hand, the second refrigerant path region 3b is cooled or heated by forced convection by the second fan 5b. In other words, the first fan 5a and the second fan 5b are fans for cooling or heating the two refrigerant passage regions (the first refrigerant passage region 3a and the second refrigerant passage region 3b) respectively. is there.

An expansion valve 6a is connected to the first refrigerant path area 3a, and an expansion valve 6b is connected to the second refrigerant path area 3b. The expansion valves 6a and 6b are electronic and can adjust the opening degree so as to finely change the flow rate of the refrigerant (refrigerant flow rate adjustment valve). Also, temperature sensors 3a0 and 3a1 (temperature detectors) are attached to the end of the first refrigerant path area 3a, and temperature sensors 3b0 and 3b1 (temperature detectors) are attached to the end of the second refrigerant path area 3b. It is done. The temperature detector is a thermistor or the like, and is for detecting the temperature of the refrigerant. The signals from the temperature sensors 3b0 and 3b1 are received by the measuring unit 3ab0. On the other hand, the signals from the temperature sensors 3a1 and 3b1 are received by the measuring unit 3ab1. The first fan 5a is electrically connected to the control unit 5a1, and the second fan 5b is electrically connected to the control unit 5b1.

The indoor unit 1 a is provided with a fan 5 c for heating or cooling the indoor heat exchanger 4. The indoor air is supplied to the indoor heat exchanger 4 by the fan 5c, and cooling or heating of the air is performed so as to reach a preset room temperature.

An expansion valve 6c is connected to an end of the indoor heat exchanger 4 of the indoor unit 1a. The expansion valve 6 c may also be an electronic type, and may be capable of adjusting the opening degree so as to finely change the flow rate of the refrigerant.

An accumulator 21 is provided on the upstream side of the compressor 2. The accumulator 21 serves to separate the refrigerant into a gas and a liquid and to send only the gas refrigerant to the compressor 2. By providing the accumulator 21, it is possible to prevent liquid refrigerant from entering the compressor 2 and to prevent damage to the compressor 2. The pressure sensor 201 (compressor discharge pressure sensor) measures the discharge pressure Pd of the compressor 2, and the pressure sensor 202 (compressor suction pressure sensor) measures the suction pressure Ps of the compressor 2.

FIG. 1B is a schematic view showing the configuration of the air conditioning apparatus and the flow of the refrigerant during the heating operation.

The configuration of the air conditioner is the same as that of FIG. As shown in the drawing, in the heating operation, the direction of the flow of the refrigerant is reversed from that in the cooling operation by switching the four-way valve 5.

Next, the operation of the air conditioning apparatus of the present invention during the cooling operation will be described using FIG. 1A.

The flow direction of the refrigerant is indicated by an arrow in FIG. 1A. Specifically, it is as follows.

The refrigerant discharged from the compressor 2 and having a high temperature and a high pressure passes through the four-way valve 5, and the flow is divided by the branch of the piping, and the first refrigerant path region 3a of the outdoor heat exchanger 3 and the second refrigerant path It flows into the area 3b, radiates heat, and condenses and liquefies. In other words, during the cooling operation, the outdoor heat exchanger 3 acts as a condenser.

Then, the refrigerant that has passed through the first refrigerant path region 3a passes through the expansion valve 6a, and the refrigerant that has passed through the second refrigerant path region 3b passes through the expansion valve 6b, and then merges and passes through the expansion valve 6c. As a result, the low pressure and low temperature gas-liquid two-phase refrigerant is obtained by the pressure reducing action of the expansion valve 6c. Then, the refrigerant flows into the indoor heat exchanger 4 to cool the indoor air. In the indoor heat exchanger 4, the refrigerant absorbs heat from room air having a temperature higher than that of the refrigerant and gradually evaporates to increase the dryness. In other words, during the cooling operation, the indoor heat exchanger 4 acts as an evaporator.

The refrigerant that has passed through the indoor heat exchanger 4 passes through the four-way valve 5 and flows into the compressor 2.

The indoor cooling operation is performed by repeating the above series of operations.

Next, the operation at the time of heating operation will be described using FIG. 1B.

The flow direction of the refrigerant is indicated by an arrow in FIG. 1B. Specifically, it is as follows.

The refrigerant discharged from the compressor 2 and having a high temperature and a high pressure passes through the four-way valve 5 which has a different connection from that in the cooling operation, flows into the indoor heat exchanger 4, and heats the indoor air. At this time, the refrigerant condenses and liquefies. In other words, in the heating operation, the indoor heat exchanger 4 acts as a condenser.

The refrigerant that has passed through the indoor heat exchanger 4 passes through the expansion valve 6c and becomes a low-pressure, low-temperature gas-liquid two-phase refrigerant by the pressure reducing action of the expansion valve 6c. The refrigerant is sent to the outdoor unit 1b, and the flow is divided by branching of the piping. Then, the refrigerant that has passed through the expansion valve 6a flows into the first refrigerant path region 3a, and the refrigerant that has passed through the expansion valve 6b flows into the second refrigerant path region 3b. Then, the refrigerant absorbs heat from the outside air in the first refrigerant passage region 3a and the second refrigerant passage region 3b and gradually evaporates to increase the dryness. Thereafter, they merge, pass through the four-way valve 5, and flow into the compressor 2. In other words, during the heating operation, the outdoor heat exchanger 3 acts as an evaporator.

The indoor heating operation is performed by repeating the above series of operations.

FIG. 2 is a top view showing a specific configuration of the outdoor unit 3 of FIGS. 1A and 1B.

In the outdoor unit 1b, the first refrigerant passage region 3a and the second refrigerant passage region 3b (fin and tube type heat exchanger) are provided to face the four surfaces of the casing 50 in order to provide a large front area. It is arranged. In other words, each of the first refrigerant path region 3a and the second refrigerant path region 3b has three bent portions, can be accommodated in the outdoor unit 1b, and has a large front surface area for ventilation. It is as a structure.

In FIG. 2, the first fan 5 a and the second fan 5 b are provided on the top surface of the housing 50. The first fan 5 a discharges the air of the space surrounded by the first refrigerant path region 3 a to the outside of the housing 50. On the other hand, the second fan 5 b discharges the air of the space surrounded by the second refrigerant path region 3 b to the outside of the housing 50. As a result, the inside of the housing 50 has a negative pressure. Along with this, the outside air passes between the fins of the first refrigerant path region 3 a and the second refrigerant path region 3 b and is sucked into the inside of the housing 50. Arrows in the figure represent the flow of air passing between the fins of the first coolant passage region 3a and the second coolant passage region 3b.

FIG. 3 is a view of the case 50 of the outdoor unit 3 of FIG. 2 as viewed from the front (the suction surface of the first refrigerant path region 3a and the second refrigerant path region 3b).

The arrangement inside the housing 50 is clearly shown in FIG. The first fan 5a and the second fan 5b are disposed in the upper part of the housing 50 and above the first refrigerant path region 3a and the second refrigerant path region 3b. The electrical parts such as the control units 5a1 and 5b1 shown in FIG. 1 are accommodated in an electrical box 900 shown in FIG.

FIG. 4 shows an example of the arrangement of internal components of the case 50 of FIG.

In FIG. 4, the compressor 2 and the accumulator 21 are disposed in the housing 50 as relatively large parts. It is desirable that the compressor 2 and the accumulator 21 be disposed close to each other in order to reduce pressure loss when the refrigerant is caused to flow inside with the both connected. In addition, it is desirable to arrange the compressor 2 at a position close to the side surface portion of the housing 50 so as to be easily replaced in the case of failure.

Furthermore, it is desirable that the service port 7 for attaching a connection pipe to the indoor unit be disposed near the side surface portion of the housing 50 and at a position where the installer can easily work. Furthermore, for the installation and installation of the housing 50, it is desirable that the weight balance be equal on the left and right of the housing 50.

In order to satisfy the above requirements, as shown in FIG. 4, depending on the dimensions of the housing 50, the outdoor heat exchanger 3 (the second refrigerant path region 3b in FIG. 4) and the accumulator 21 etc. The parts must be in close proximity (dimension G in FIG. 4). As a result, it is difficult for the air to flow partially, and as shown by the size of the arrow in FIG. The side and the small side will occur. That is, even with the first refrigerant path area 3a and the second refrigerant path area 3b having a symmetrical shape formed by dividing the outdoor heat exchanger 3, exchange with an appropriate air volume depending on the arrangement of other components A difference may occur in the amount of heat.

Next, the flow of control will be described.

5A and 5B show the case of controlling the opening degree of the expansion valve.

FIG. 5A shows the flow of control under heating conditions. In this case, the outdoor heat exchanger acts as an evaporator.

Data on the refrigerant outlet temperature measured by the temperature sensors 3a0 and 3b0 shown in FIG. 1B are sent to the measuring unit 3ab0 (S101 in FIG. 5A). Both temperatures are compared (S102), and if the temperature difference is a target value (for example, 1 K or less), control is terminated. However, if the temperature difference is equal to or greater than the target value, control is performed such that the expansion operation of the expansion valve with the lower refrigerant outlet temperature (for example, symbol 6a in FIG. 1B) at S103 becomes smaller, ie, the opening degree of the expansion valve becomes smaller. Do. Then, the refrigerant outlet temperatures are compared again, and control is continued until the temperature difference becomes less than the target value.

Next, FIG. 5B shows a flow of control under the cooling condition. In this case, the outdoor heat exchanger acts as a condenser.

Data on the refrigerant outlet temperature measured by the temperature sensors 3a1 and 3b1 shown in FIG. 1A are sent to the measuring unit 3ab1 (S201 in FIG. 5B). Both temperatures are compared (S202), and if the temperature difference is a target value (for example, 1 K or less), control is terminated. However, if the temperature difference is equal to or greater than the target value, control is performed so that the expansion operation of the expansion valve (for example, symbol 6a in FIG. 1A) having the higher refrigerant outlet temperature becomes smaller at S103. Do. Then, the refrigerant outlet temperatures are compared again, and control is continued until the temperature difference becomes less than the target value.

In the case of cooling, it is desirable to control the two refrigerant outlet temperatures so as to be a subcool temperature at which the coefficient of performance (COP) of the air conditioner becomes the highest.

FIG. 6 shows a flow of control in the case of controlling the rotational speeds of the first fan 5a and the second fan 5b shown in FIG. 1A under the cooling condition.

In FIG. 6, data of the refrigerant outlet temperature measured by the temperature sensors 3a1 and 3b1 shown in FIG. 1A are sent to the measuring unit 3ab1 (S301 in FIG. 6). Both temperatures are compared (S302), and if the temperature difference is a target value (for example, 1 K or less), control is terminated. However, when the temperature difference is equal to or more than the target value, in S303, control is performed such that the number of rotations of the fan having the higher refrigerant outlet temperature (for example, the symbol 5a in FIG. Then, the refrigerant outlet temperatures are compared again, and control is continued until the temperature difference becomes less than the target value.

Next, control in the case where the required amount of heat exchange is small will be described.

FIG. 7 is a schematic view showing the configuration of the air conditioning apparatus and the flow of the refrigerant during the heating operation.

The blower (fan) has a minimum rotational speed that can be rotated, and has a small air conditioning load such as when the temperature difference between room temperature and the outside air is small, and when the amount of heat exchange is small, one heat exchange of the outdoor heat exchanger 3 It is desirable not to operate the vessel (the first refrigerant path area 3a and the second refrigerant path area 3b). In this case, as shown in FIG. 7, for example, the expansion valve 6a is completely closed and the first fan 5a is stopped to restrict the flow of the refrigerant and the air, and the amount of heat exchange from the outdoor heat exchanger 3 is obtained. It can be made smaller.

In addition, although the example which connected to one outdoor unit to one indoor unit was demonstrated in FIG. 1A-FIG. 7, as shown in FIG. 8, even when a plurality of indoor units are connected, the present invention The effect of is obtained.

In FIG. 8, the air conditioner 1 includes indoor units 81 a and 81 b. The indoor unit 81a has an indoor heat exchanger 41, a fan 5c1, and an expansion valve 6c1. The indoor unit 81b has an indoor heat exchanger 42, a fan 5c2, and an expansion valve 6c2. The refrigerant discharged from one compressor 2 is branched to flow into the indoor heat exchanger 41 and the indoor heat exchanger 42 respectively.

Control of the outdoor heat exchanger 3 is the same as in the case of FIGS. 1A and 1B.

The control unit can adjust the opening degrees of the two refrigerant flow control valves and the rotational speeds of the two fans independently of each other.

FIG. 9 is a top view showing a state in which the outdoor unit is installed in proximity.

As shown in the figure, the plurality of outdoor units 51, 53 are installed close to one another in order to reduce the installation space. In the outdoor unit 51, a first refrigerant path region 3a and a second refrigerant path region 3b constituting an outdoor heat exchanger are accommodated. The first refrigerant path region 3a is cooled or heated by forced convection by the first fan 5a. Further, the second refrigerant path region 3b is cooled or heated by forced convection by the second fan 5b. On the other hand, in the outdoor unit 53, a first refrigerant path region 3a 'and a second refrigerant path region 3b' constituting the outdoor heat exchanger are accommodated. The first refrigerant path region 3a 'is cooled or heated by forced convection by the first fan 5a'. In addition, the second refrigerant path region 3b is cooled or heated by forced convection by the second fan 5b '.

Since the outdoor units 51 and 53 are installed adjacent to each other, the air flow is reduced in the part 3bg of the second refrigerant path area 3b and the part 3a'g of the first refrigerant path area 3a ' Do. For this reason, the amount of heat exchange in this portion is small. As a result, the blowing power is increased and the energy saving performance is deteriorated.

Therefore, in order to increase the amount of heat exchange of the first refrigerant path region 3a of the outdoor unit 51 on the open space side and the second refrigerant path region 3b 'of the outdoor unit 53, the first fan 5a of the outdoor unit 51 and the outdoor By increasing the rotational speed of the second fan 5b 'of the machine 53 and increasing the air volume, power saving may be achieved in some cases. In this case, the rotational speeds of the second fan 5b of the outdoor unit 51 and the first fan 5a 'of the outdoor unit 53 may be maintained as it is or may be reduced.

As described above, it is desirable to adjust the refrigerant circulation amount by adjusting the rotational speed of the fan and changing the opening degree of the expansion valves 6a and 6b according to the air volume distribution. Adjustment of the opening degree of the expansion valves 6a, 6b can be achieved by using the control flow shown in FIGS. 5A and 5B.

Next, a method of automatically determining whether the heat exchanger is the open space side or the side adjacent to the outdoor unit when the outdoor unit is installed in proximity will be described with reference to FIG.

In this embodiment, at the time of installation and installation of the outdoor unit, a trial run is performed to determine the quality of the device. At this time, a control function for automatically determining is provided. In addition, the code | symbol in the following description uses what was described in FIG. 1A.

As shown in FIG. 10, for example, the operation is performed under the cooling condition, and first, the expansion valve 6b on the L side (left side) is fully closed. (S501) Then, the expansion valve 6a on the R side (right side) is opened appropriately, and the fan 5a is set to an appropriate rotational speed (S502). Then, the compressor 2 is started (S503). When the steady state is achieved, the discharge pressure (PdR) of the compressor 2 is measured by the pressure sensor 201 (S504).

Next, the flow path on the R side is closed (S505), the flow path on the L side is opened appropriately, and the fan 5b is set to an appropriate number of revolutions (S506). Then, similarly, the compressor 2 is started (S507), and when it is in a substantially steady state, the discharge pressure (PdL) of the compressor 2 is measured by the pressure sensor 201 (S508). The two discharge pressures PdR and PdL are compared (S509), and the side with a low pressure is determined as the open space heat exchanger that can easily obtain an exchange heat quantity with a large air volume. That is, when the PdR is low, it is determined that the R side is the open side (S510), and when the PdL is low, it is determined that the L side is the open side (S511).

Thus, the heat exchanger on the open space side can be determined. By incorporating a program that controls the heat exchanger to be mainly used during actual air conditioning operation, an air conditioning apparatus with excellent energy saving performance can be obtained.

In the present embodiment, the case where two outdoor units are disposed in proximity to each other has been described. However, even when three or more outdoor units are disposed in series and in proximity, it is possible to determine the heat exchanger on the open space side. it can. In this case, for the outdoor unit in which both sides are sandwiched by the outdoor units, that is, for the outdoor unit disposed between two outdoor units, any heat exchanger (refrigerant route region) is also on the open space side It is not determined.

The present invention is not limited to the embodiments described above, but includes various modifications. For example, the above-described embodiments are described in detail for easy understanding in the present invention, and are not necessarily limited to those having all the configurations described. Also, part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.

1: Air conditioner, 1a: indoor unit, 1b: outdoor unit, 2: compressor, 3: outdoor heat exchanger, 3a: first refrigerant path region, 3b: second refrigerant path region, 3a0, 3a1, 3b0, 3b1: temperature sensor, 4: indoor heat exchanger, 5: four-way valve, 5a: first fan, 5b: second fan, 5a1, 5b1: controller, 5c1, 5c2: fan, 6a, 6b, 6c: expansion valve, 21: accumulator, 201, 202: pressure sensor, 900: electrical box.

Claims (10)

A compressor, an indoor heat exchanger, an outdoor heat exchanger, and a pipe connecting these,
At least one of the indoor heat exchanger and the outdoor heat exchanger is a first refrigerant path area, a second refrigerant path area, and a first for performing forced air cooling of the first refrigerant path area. A fan and a second fan for forced air cooling of the second refrigerant passage area;
The first refrigerant path region has a first refrigerant flow control valve and a first temperature detector for detecting the outlet temperature of the refrigerant.
The second refrigerant path region includes a second refrigerant flow control valve and a second temperature detector that detects the outlet temperature of the refrigerant.
By adjusting at least one of the opening degree of the first refrigerant flow control valve and the second refrigerant flow control valve and the rotational speed of the first fan and the second fan, the first An air conditioner, which controls so that a difference between a refrigerant outlet temperature obtained by a temperature detector and a refrigerant outlet temperature obtained by the second temperature detector becomes small. The air conditioner according to claim 1, wherein the outdoor heat exchanger has the first refrigerant path region, the second refrigerant path region, the first fan, and the second fan. . The said indoor heat exchanger is a said 1st refrigerant | coolant path | route area | region, The said 2nd refrigerant | coolant path | route area | region, The said 1st fan, The said 2nd fan of Claim 1 or 2 Air conditioner. The air conditioner according to any one of claims 1 to 3, wherein the adjustment is performed independently. A compressor, an indoor heat exchanger, an outdoor heat exchanger, piping connecting these, and a control unit,
The outdoor heat exchanger includes a first refrigerant path area, a second refrigerant path area, a first fan for forced air cooling of the first refrigerant path area, and the second refrigerant path area. Have a second fan for forced air cooling,
The first refrigerant path region has a first refrigerant flow control valve and a first temperature detector for detecting the outlet temperature of the refrigerant.
The second refrigerant path region is an air conditioner having a second refrigerant flow control valve and a second temperature detector for detecting the outlet temperature of the refrigerant,
The control unit
One of the first refrigerant flow control valve and the second refrigerant flow control valve is fully closed, the other is open, and the refrigerant is supplied to the refrigerant passage area corresponding to the other refrigerant flow control valve. Cooling the refrigerant passage region with a fan and measuring the discharge pressure in a steady state of the compressor;
Thereafter, with the other refrigerant flow control valve fully closed and the refrigerant flowing to the refrigerant passage area corresponding to the fully closed refrigerant flow adjustment valve, the refrigerant passage area is cooled by a fan, Measure the discharge pressure in the steady state of the compressor,
An air conditioner, which determines whether or not the refrigerant passage region is disposed on the open space side from the difference between the two discharge pressures. The air conditioning apparatus according to claim 5, wherein the determination is performed by a test run when the outdoor unit is installed. The air conditioning apparatus according to claim 5, wherein the determination is automatically performed. A compressor, an indoor heat exchanger, an outdoor heat exchanger, and a pipe connecting these,
The outdoor heat exchanger includes a first refrigerant path area, a second refrigerant path area, a first fan for forced air cooling of the first refrigerant path area, and the second refrigerant path area. Have a second fan for forced air cooling,
The first refrigerant path region has a first refrigerant flow control valve and a first temperature detector for detecting the outlet temperature of the refrigerant.
The second refrigerant path region is a method of determining the performance of an air conditioner having a second refrigerant flow control valve and a second temperature detector for detecting the outlet temperature of the refrigerant,
One of the first refrigerant flow control valve and the second refrigerant flow control valve is fully closed, the other is open, and the refrigerant is supplied to the refrigerant passage area corresponding to the other refrigerant flow control valve. Cooling the refrigerant passage region with a fan and measuring the discharge pressure in a steady state of the compressor;
Thereafter, with the other refrigerant flow control valve fully closed and the refrigerant flowing to the refrigerant passage area corresponding to the fully closed refrigerant flow adjustment valve, the refrigerant passage area is cooled by a fan, Measure the discharge pressure in the steady state of the compressor,
A method of determining the performance of an air conditioner, which determines whether or not the refrigerant path region is disposed on the open space side from the difference between these two discharge pressures. The performance judgment method of the air conditioning apparatus according to claim 8, wherein the judgment is performed in a test run when the outdoor unit is installed. The performance judging method of the air conditioning apparatus according to claim 8 or 9, wherein the judgment is automatically performed.

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