CN111936792A - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN111936792A CN111936792A CN201980004700.9A CN201980004700A CN111936792A CN 111936792 A CN111936792 A CN 111936792A CN 201980004700 A CN201980004700 A CN 201980004700A CN 111936792 A CN111936792 A CN 111936792A
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- Prior art keywords
- heat exchanger
- row
- double
- indoor
- row heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
Abstract
The invention provides an air conditioner, which comprises an indoor unit and an outdoor unit, wherein the indoor unit is provided with an indoor heat exchanger, the outdoor unit is provided with an expansion valve, the indoor heat exchanger is provided with a double-row heat exchanger provided with two rows of heat transfer pipes and a single-row heat exchanger provided with one row of heat transfer pipes, and the expansion valve is connected to the single-row heat exchanger through at least one part of one row of the double-row heat exchanger and at least one part of the other row of the double-row heat exchanger.
Description
Technical Field
The present invention relates to an air conditioner having an indoor unit and an outdoor unit.
Background
The air conditioner includes an outdoor unit and an indoor unit, and the outdoor unit and the indoor unit each include a heat exchanger for exchanging heat between air and a refrigerant, and a blower device for generating an air flow. During the cooling operation, a low-temperature refrigerant flows through the inside of a heat exchanger provided in the indoor unit, and the air in the room flows through the outside of the heat exchanger, thereby cooling the air in the room. At this time, a part of the water vapor contained in the air in the room is cooled on the heat exchanger surface, and dew condensation occurs. The dew condensation water on the surface of the heat exchanger is discharged to the outside of the room from the drain pipe through the drain pan along the fins of the heat exchanger.
When the heat exchanger has a temperature distribution, a part of the air may be excessively cooled and a part of the air may be insufficiently cooled. When air having such a temperature difference is blown out from the heat exchanger, dew condensation may occur on the air flow path of the blowout part of the indoor unit. The problems that exist are that: the dew condensation on the air blowing path is blown out from the air outlet into the room and drips down along the air blowing path into the room. In contrast, patent document 1 discloses a technique of: in order to prevent condensation inside the indoor unit, a temperature sensor is provided in the heat exchanger of the indoor unit, and the expansion valve is controlled based on the measured temperature so that there is no temperature difference inside the heat exchanger. In addition, from the viewpoint of cost reduction and compactness, it is desirable to apply a heat exchanger composed of a single-row heat exchanger and a double-row heat exchanger.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 8-159538
Disclosure of Invention
Problems to be solved by the invention
However, in the heat exchanger including the single-row heat exchanger and the double-row heat exchanger, air flows more easily in the 1-row portion than in the 2-row portion. Therefore, there is a problem that the temperature of the air passing through the heat exchanger tends to be poor.
The present invention has been made in view of the above problems, and an object of the present invention is to prevent condensation inside an indoor unit while using a heat exchanger having a single-row heat exchanger and a double-row heat exchanger.
Means for solving the problems
The present invention is an air conditioner including an indoor unit and an outdoor unit, wherein the indoor unit includes an indoor heat exchanger, the outdoor unit includes an expansion valve, the indoor heat exchanger includes a double-row heat exchanger in which two rows of heat transfer pipes are arranged and a single-row heat exchanger in which one row of heat transfer pipes is arranged, and the expansion valve is connected to the single-row heat exchanger via at least a part of one row of the double-row heat exchanger and at least a part of the other row of the double-row heat exchanger.
ADVANTAGEOUS EFFECTS OF INVENTION
According to the present invention, condensation inside the indoor unit can be prevented while using a heat exchanger having a single-row heat exchanger and a double-row heat exchanger.
Drawings
Fig. 1 is a diagram showing a structure of an indoor unit.
Fig. 2 is a sectional view of an indoor heat exchanger.
Fig. 3 is a diagram showing a modification of the indoor heat exchanger.
Fig. 4 is an overall configuration diagram of the air conditioner.
Fig. 5 is a sectional view of an indoor heat exchanger of a second embodiment.
Fig. 6 is a sectional view of an indoor heat exchanger of a third embodiment.
Fig. 7 is a sectional view of an indoor heat exchanger of a fourth embodiment.
Fig. 8 is a diagram showing a heat exchanger of a comparative example.
Fig. 9 is a diagram showing a heat exchanger of a comparative example.
Detailed Description
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings, but the present invention is not limited to the embodiments below, and various modifications and application examples in the technical concept of the present invention are included in the scope thereof.
(first embodiment)
Fig. 1 is a diagram showing a structure of an indoor unit 100 of an air conditioner according to a first embodiment. Fig. 1 is a cross-sectional view perpendicular to the back surface 120 of the indoor unit 100 and parallel to the vertical direction of the indoor unit 100. Hereinafter, the x-axis direction (depth direction of the paper surface) of the three-dimensional coordinates shown in fig. 1 is set to the lateral direction of the indoor unit 100, the y-axis direction (longitudinal direction of the paper surface) is set to the vertical direction of the indoor unit 100 (upper side of the paper surface is the upper direction), and the z-axis direction (lateral direction of the paper surface) is set to the depth direction of the indoor unit 100.
The indoor unit 100 is provided near the ceiling of the room so that the rear surface 120 faces the wall a. In fig. 1, a room as an air-conditioned space is expanded to the lower left of the drawing, and an indoor unit 100 has a structure in which air flows so as to adjust the temperature of the room.
An indoor heat exchanger 110 and an indoor fan 102 are mounted inside the indoor unit 100. In the indoor heat exchanger 110, air is sent from the indoor fan 102 to perform heat exchange. The indoor unit 100 is further provided with a filter device 103, a rear casing 104, a front casing 105, louvers 106, and vertical louvers 107.
Air is taken into the indoor unit 100 from the upper side of fig. 1, that is, the upper side of the indoor unit 100, and large dust and the like are removed by the filter device 103 and pass through the indoor heat exchanger 110. The indoor fan 102 blows air to the indoor heat exchanger 110. The indoor fan 102 can use a cross flow fan. When the cross flow fan is used, a front nose 109 is provided on the front side of the indoor fan 102, and a rear nose 108 is provided on the rear side (rear surface 120 side). The air suction side and the air discharge side of the indoor fan 102 are separated by the front nose 109 and the rear nose 108, and the indoor fan 102 performs an air blowing function.
When air is sucked from above the indoor heat exchanger 110 and wind flows into the space below as shown in fig. 1, the indoor fan 102 rotates clockwise as viewed from the right in the depth direction as shown in fig. 1. After being blown out by the indoor fan 102, the air passes through an air passage formed by the front nose 109 and the rear case 104, and flows into the room while the blowing direction is controlled by the louvers 106 and the vertical louvers 107. The louver 106 controls the direction of the blown air in the vertical direction. The vertical louvers 107 control the wind direction in the lateral direction (left-right direction).
The indoor heat exchanger 110 includes heat transfer tubes through which the refrigerant flows and fins connected to the periphery of the heat transfer tubes. A plurality of circles 110a shown inside the indoor heat exchanger 110 in fig. 1 indicate heat transfer pipes. The heat transfer pipes extend in the depth direction and are connected to each other at the right or left end by a U-shaped pipe, thereby forming one flow path (single path) for the refrigerant. The fins are aluminum plates having a thickness of about 0.1mm, and are connected in the lateral direction of the indoor heat exchanger 110 at intervals of about 1 mm. The fins are in close contact with the heat transfer tube, and the refrigerant passes through the heat transfer tube.
In the cooling operation, a refrigerant having a temperature lower than the temperature of the indoor air is supplied from the outdoor unit 200 to the indoor heat exchanger 110. The temperature of the fins of the indoor heat exchanger 110 is close to the temperature of the supplied refrigerant. Warm air in the room flows by the indoor fan 102 and is cooled by the indoor heat exchanger 110. When the temperature of the fins of the indoor heat exchanger 110 is lower than the dew point of the indoor air flowing through the indoor heat exchanger 110, moisture in the air is condensed on the fin surfaces of the indoor heat exchanger 110. The condensed water flows down the indoor heat exchanger 110 along the fins and flows out to the outside along a drain passage provided in the casing. As described above, during the cooling operation, moisture in the air may condense in the indoor heat exchanger 110. The air passing through the indoor heat exchanger 110 is cooled in the indoor heat exchanger 110, and a part of the moisture is condensed, but the humidity is maintained at approximately 100% as the relative humidity.
Fig. 2 is a diagram showing the structure of the indoor heat exchanger 110. The indoor heat exchanger 110 includes a double-row heat exchanger 111, a front-side single-row heat exchanger 112, and a back-side single-row heat exchanger 113. The double row heat exchanger 111 is provided on the upper side of the front surface of the indoor unit 100 so as to arrange 2 rows of heat transfer pipes in the depth direction. In the double row heat exchanger 111, 2 rows of heat transfer pipes are arranged in the direction in which air flows when the indoor fan 102 is driven. The front surface side, i.e., the upwind side row of the double row heat exchanger 111 is referred to as an upwind row 1111. The rear side, i.e., the leeward side row of the double row heat exchanger 111 is referred to as a leeward row 1112. The front-surface-side single-row heat exchanger 112 is disposed so as to extend further downward from the lower side of the double-row heat exchanger 111. The rear-side single-row heat exchanger 113 is disposed so as to extend from the upper side of the double-row heat exchanger 111 to the rear side. The lowermost layer 111a of the double-row heat exchanger 111, which serves as an inlet port for the refrigerant during cooling operation, is connected to an expansion valve of the outdoor unit via a pipe. The lowermost layer 13b of the rear-face heat exchanger 113, which serves as an outlet for the refrigerant during the cooling operation, is connected to the four-way valve of the outdoor unit via a pipe.
The indoor heat exchanger 110 of the present embodiment has 1 column unit as described above. In many conventional heat exchangers, a double-row heat exchanger is used on both the front surface side and the back surface side. In contrast, in the indoor heat exchanger 110 of the present embodiment, a part of the front surface side and the back surface side are single-row heat exchangers, thereby reducing the material of the heat exchangers. This makes it possible to effectively utilize resources, and to maintain compactness and energy saving.
However, the degree of ventilation resistance of air at the same wind speed is doubly different in single and double rows. Therefore, simply considering the wind speed, it is considered that the amount of air passing through the single-row heat exchanger and the amount of air passing through the double-row heat exchanger are different by about 1.4 times. In addition, since air is actually sucked from the ceiling side (upper side) of the indoor unit 100, in the arrangement of the indoor heat exchanger 110 shown in fig. 2, it is more difficult to suck air into the front surface side single-row heat exchanger 112 located below the position of the double-row heat exchanger 111 located above. Therefore, the difference in air volume is considered to be smaller than 1.4 times. In the back-side single-row heat exchanger 113, the rear nose 108 may serve as a wall that blocks the flow from the back-side single-row heat exchanger 113 to the indoor fan 102. Therefore, the back-side single-row heat exchanger 113 is less likely to suck air than the double-row heat exchanger 111. That is, the double-row heat exchanger 111 has higher heat exchange efficiency than the front-side single-row heat exchanger 112 and the back-side single-row heat exchanger 113.
As described above, in the indoor heat exchanger 110 of the present embodiment, the refrigerant passage is a single passage that does not branch midway. This corresponds to the desire for a simple refrigerant passage in the heat exchanger and for a small number of brazed portions due to branching or the like, which reduces the risk of leakage when using a flammable refrigerant. As the flammable refrigerant, propane (R290) and the like can be cited. Examples of the slightly flammable refrigerant include difluoromethane (R32), 2, 3, and 3-tetrafluoropropene (R1234 yf).
Further, in the present embodiment, the heat transfer pipe is formed of aluminum or an aluminum alloy. In this way, when aluminum or an aluminum alloy is used for the heat transfer pipe, the brazeability is inferior to that of a copper pipe or the like. Therefore, the reduction of the brazed portion leads to an improvement in productivity of the heat exchanger. Aluminum is considered to be buried in a larger amount than copper, and replacement with aluminum is considered to be effective in order to achieve a sustainable society while minimizing the use of copper. Further, in a portion where the aluminum pipe and the copper pipe are joined, corrosion may occur if dew condensation occurs. Therefore, it is desirable that excessive condensation is not generated as much as possible. For the above reasons, the double-row heat exchanger 111 of the present embodiment employs a single passage.
In the cooling operation, the refrigerant is in a state of a large liquid phase near the inlet of the double-row heat exchanger 111, and when passing through the double-row heat exchanger 111, the liquid phase in the refrigerant evaporates, thereby cooling the air. Therefore, the gas phase in the refrigerant increases while passing through the double heat exchanger 111. Therefore, the velocity of the refrigerant is also increased in the flow path of the refrigerant in the double-row heat exchanger 111. In a conventional heat exchanger, a branch is provided in a pipe in the heat exchanger to divide and flow a refrigerant, thereby reducing a pressure loss of the refrigerant in the double-row heat exchanger. In contrast, in the double-row heat exchanger 111 of the present embodiment, since a single passage is used, acceleration of the refrigerant due to pressure loss becomes larger than in the case of using two passages. As the pressure loss increases, the pressure decreases in the second half of the flow path of the double-row heat exchanger 111 as compared with the first half, and the saturation temperature decreases accordingly. This increases the temperature difference of the refrigerant inside the heat exchanger. In contrast, the indoor heat exchanger 110 of the present embodiment can prevent condensation due to the temperature difference by the following configuration.
The arrows shown in fig. 2 indicate the flow of the refrigerant during the cooling operation. In the cooling operation, the refrigerant in the two-phase state reduced in pressure by the expansion valve of the outdoor unit described later and brought into a low temperature flows into the double-column heat exchanger 111 with the lowermost layer 111a of the upwind column 1111 of the double-column heat exchanger 111 as an inlet port. Thereafter, the refrigerant flows upward in the direction opposite to the direction of gravity in the windward row 1111, and flows into the subsequent leeward row 1112 when flowing to the uppermost layer 111 b. In the leeward row 1112, the refrigerant flows downward from the uppermost layer 111c, and when flowing to the lowermost layer 111d, flows into the uppermost layer 112a of the front-surface-side single-row heat exchanger 112. In the front-side single-row heat exchanger 112, the refrigerant flows downward, and flows into the rear-side single-row heat exchanger 113 when flowing to the lowermost layer 112 b. In the rear-side single-row heat exchanger 113, the refrigerant flows downward from the uppermost layer 113a to the lowermost layer 113b, and flows out of the lowermost layer 113b as an outlet.
In the above configuration, the refrigerant on the cooling inlet side of the indoor heat exchanger 110 exchanges heat with air in the double-row heat exchanger 111 having a large heat transfer area. Further, the refrigerant having passed through the double-row heat exchanger 111 and having a reduced temperature exchanges heat with air in the front-side single-row heat exchanger 112 and the back-side single-row heat exchanger 113, which have small heat transfer areas. This makes it possible to make the temperature of the air passing through the indoor heat exchanger 110 nearly uniform. That is, the occurrence of dew condensation in the air blowing passage in the rear layer of the indoor heat exchanger 110 can be suppressed.
The refrigerant flowing out of the double-row heat exchanger 111 preferably flows into the front-side single-row heat exchanger 112 and the back-side single-row heat exchanger 113 at positions as close to the double-row heat exchanger 111 as possible. From this viewpoint, in the present embodiment, the refrigerant is disposed in either one of the front-side single-row heat exchanger 112 and the back-side single-row heat exchanger 113 so as to flow into the uppermost layers 112a, 113 a.
Fig. 2 shows the flow of the refrigerant during the cooling operation, and the flow of the refrigerant during the heating operation is opposite to that during the cooling operation. During heating operation, the pipe that becomes the refrigerant inlet during cooling becomes the outlet. In the heating operation, the gas refrigerant flows into the indoor heat exchanger 110, heats the air, and is liquefied. At the heating outlet of the indoor heat exchanger 110, the refrigerant is cooled to become substantially liquid, and flows out at a temperature lower than the inlet. Therefore, in order to increase the heat transfer to the air by the temperature difference with the air as much as possible, the windward side in contact with the air that does not pass through the indoor heat exchanger 110 is preferable. Further, the passage on the heating outlet side flows from the upper layer to the lower layer by gravity, so that the liquid flows more easily, and the refrigerant can be prevented from being accumulated. From these viewpoints, the indoor heat exchanger 110 of the present embodiment is configured to flow upward by setting the inlet during cooling, which is the outlet during heating, as the lowermost layer 111a of the upwind row 1111 of the double-row heat exchanger 111.
Further, the lowermost layer 112b of the front-side single-row heat exchanger 112 and the uppermost layer 113a of the rear-side single-row heat exchanger 113 are connected by pipes. This piping is also a cause of pressure loss. Therefore, the pipe is thicker than the other pipes. Further, in order to avoid heat exchange other than the blown air, the air is covered with a heat insulator.
Fig. 8 is a diagram showing a heat exchanger 800 of a comparative example. The heat exchanger 800 includes a double-row heat exchanger 801, a front-side single-row heat exchanger 802, and a back-side single-row heat exchanger 803, as in the indoor heat exchanger 110 of the present embodiment. The front-side single-row heat exchanger 802 is provided below the double-row heat exchanger 801, and the back-side single-row heat exchanger 803 is provided on the back side so as to extend from the upper side of the double-row heat exchanger 801.
In heat exchanger 800, the refrigerant flows into heat exchanger 800 with lowermost layer 801a of upwind row 8011 of double-row heat exchanger 801 as an inflow port. Thereafter, the refrigerant flows upward in the windward row 8011, and flows into the uppermost layer 801b, and thereafter flows into the lowermost layer 802a of the front surface side single-row heat exchanger 802. The refrigerant flows upward from the lowermost layer 802a to the uppermost layer 802b, and then flows upward from the lowermost layer 801c to the uppermost layer 801d of the leeward row 8012 of the double-row heat exchanger 801. Thereafter, the refrigerant flows downward from the uppermost layer 803a to the lowermost layer 803b of the rear-side single-row heat exchanger 803.
In the above configuration, the temperature of the refrigerant near the cooling inlet side is not sufficiently lowered, and therefore sufficient heat exchange is not performed in the front-side single-row heat exchanger 802 in which only the refrigerant passing through 1 row of the double-row heat exchanger 801 flows, and cooling and dehumidification are insufficient. On the other hand, in the vicinity of the uppermost layer 801d of the leeward row 8012 of the double row heat exchanger 801, the refrigerant having a temperature lowered by 2 rows flows, and therefore, the temperature is remarkably lowered as compared with the other refrigerant. Therefore, cold air in the vicinity of the leeward row 8012 is mixed with warm air in the vicinity of the front surface side single-row heat exchanger 802, which may cause dew condensation in the air blowing passage.
In contrast, as shown in fig. 2, in the indoor heat exchanger 110 of the present embodiment, all of the heat exchangers pass through the double-row heat exchanger 111 and then flow into the front-side single-row heat exchanger 112. This allows the refrigerant on the cooling inlet side having a high temperature to flow into the double-row heat exchanger 111, which is likely to lower the temperature of the air. Then, the refrigerant having a reduced temperature flows into the front-side single-row heat exchanger 112 and the back-side single-row heat exchanger 113. This can reduce the difference in the air temperature of the entire indoor heat exchanger 110.
Fig. 3 is a diagram showing a modification of the indoor heat exchanger 110. Fig. 9 is a diagram showing a comparative example corresponding to the modification shown in fig. 3. In the example shown in fig. 3, the refrigerant flows through the double-row heat exchanger 111, flows through the front-side single-row heat exchanger 112, flows into the lowermost layer 113b of the rear-side single-row heat exchanger 113, and flows upward to the uppermost layer 113 a. In this way, the inlet of the refrigerant to the single-row heat exchanger does not have to be provided at the position closest to the double-row heat exchanger.
On the other hand, in the heat exchanger 900 of the comparative example shown in fig. 9, the refrigerant flows downward from the uppermost layer 901a to the lowermost layer 901b of the double-row heat exchanger 901, then enters the lowermost layer 902a of the front-surface-side single-row heat exchanger 902 before flowing downward, and flows upward to the uppermost layer 902 b. Thereafter, the refrigerant flows from the lowermost layer 901c on the leeward side of the double-row heat exchanger 901 to the uppermost layer 901d, and then flows from the uppermost layer 903a to the lowermost layer 903b of the back-side single-row heat exchanger 113.
In the indoor heat exchanger 110 of the modification shown in fig. 3, the cooling inlet temperature is 16.2 ℃, the temperature of the uppermost layer 111c of the double-row heat exchanger 111 is 15.7 ℃, the temperature of the lowermost layer 112b of the front-side single-row heat exchanger 112 is 14.5 ℃, and the temperature of the uppermost layer 113a, i.e., the outlet, of the back-side single-row heat exchanger 113 is 13.2 ℃ according to theoretical calculation under the cooling rated conditions. On the other hand, in the heat exchanger 900 of the comparative example shown in fig. 9, the cooling inlet temperature is 16.3 ℃, the temperature of the lowermost layer 902a of the front-side single-row heat exchanger 902 is 15.8 ℃, the temperature of the uppermost layer 902b is 15.3 ℃, the temperature of the uppermost layer 901d of the double-row heat exchanger 901 is 14.3 ℃, and the temperature of the lowermost layer 803b, i.e., the outlet, of the back-side single-row heat exchanger 903 is 13.1 ℃.
As described above, in the comparative example, the lowermost layer 902a of the front-side single-row heat exchanger 902 is insufficiently cooled and insufficiently dehumidified, whereas the uppermost layer 901d is excessively cooled. In contrast, in the indoor heat exchanger 110 according to the modification, the uppermost layer 112a of the front-surface-side single-row heat exchanger 112 is lower in temperature than the corresponding position (lowermost layer 902a) of the comparative example, and is sufficiently cooled. In the indoor heat exchanger 110 according to the modification, it is understood that the temperature of the uppermost layer 111c of the double-column heat exchanger 111 is higher than the corresponding position (the uppermost layer 901d) of the comparative example, and supercooling is eliminated. As described above, in the present embodiment, condensation inside the indoor unit 100 can be prevented while using the indoor heat exchanger 110 having a single-row heat exchanger and a double-row heat exchanger.
Fig. 4 is an overall configuration diagram of the air conditioner 10 including the indoor unit 100. The air conditioner 10 includes an indoor unit 100 and an outdoor unit 200. The indoor unit 100 and the outdoor unit 200 are connected by a refrigerant connection pipe. The outdoor unit 200 includes a four-way valve 201, a compressor 202, an accumulator 203, an expansion valve 204, an outdoor heat exchanger 205, and an outdoor fan 206.
The high-pressure liquid refrigerant is depressurized by the expansion valve 204 to be cooled to a low temperature, and becomes a gas-liquid two-phase flow. The low-pressure, low-temperature refrigerant reaches the outdoor heat exchanger 205. The outdoor air flows toward the outdoor heat exchanger 205 by the outdoor fan 206. Since the refrigerant is decompressed by the expansion valve 204 so that the temperature thereof becomes lower than that of the outside air, the refrigerant is heated by the outside air in the outdoor heat exchanger 205, and the liquid refrigerant is evaporated into a gas refrigerant.
The low-temperature, low-pressure refrigerant vaporized in the outdoor heat exchanger 205 reaches the four-way valve 201. At this time, the four-way valve 201 switches the valve so that the gas refrigerant flowing out of the outdoor heat exchanger 205 returns to the suction side of the compressor 202 via the accumulator 203. The low-temperature, low-pressure gas refrigerant reaches compressor 202 via accumulator 203 by way of four-way valve 201. The accumulator 203 has a function of preventing a large amount of liquid refrigerant from flowing into the compressor 202.
Arrow 11 indicates the flow of the refrigerant during cooling. The compressor 202 compresses a low-pressure and low-temperature refrigerant and discharges a high-temperature and high-pressure gas refrigerant. The high-temperature and high-pressure gas refrigerant discharged from the compressor 202 reaches the four-way valve 201. In the four-way valve 201, the valve is switched so that the gas refrigerant flowing from the compressor 202 flows to the outdoor heat exchanger 205 side. In the cooling operation, the high-temperature and high-pressure gas refrigerant flows into the outdoor heat exchanger 205. When outdoor air having a temperature lower than that of the gas refrigerant flows through the outdoor heat exchanger 205, the outdoor heat exchanger 205 cools and condenses the gas refrigerant, and the liquid refrigerant undergoes a phase change. In the outdoor heat exchanger 205, a part or all of the refrigerant liquefied by the gas refrigerant reaches the expansion valve 204, and is decompressed by the expansion valve 204. The pressure reduction causes a part of the refrigerant to vaporize, and the temperature of the refrigerant is lowered by the heat of vaporization. Then, the low-temperature refrigerant flows into the indoor unit 100 through the refrigerant connection pipe.
The amount of pressure reduction of the refrigerant in the expansion valve 204 can be adjusted by the opening degree of the valve inside the expansion valve 204, and when the opening degree is reduced, the amount of pressure reduction increases, and the refrigerant becomes lower in temperature. On the other hand, when the opening degree is increased, the decompression amount is decreased, and the temperature decrease of the refrigerant is decreased. Under the cooling operation condition, the opening degree of the expansion valve 204 is adjusted so that the temperature of the refrigerant reaching the indoor unit 100 becomes lower than the indoor air temperature.
As a first modification, the indoor heat exchanger 110 may be configured such that the refrigerant flows into the front-side single-row heat exchanger 112 or the back-side single-row heat exchanger 113 after passing through at least a part of the upwind row 1111 and at least a part of the downwind row 1112 of the double-row heat exchanger 111, and the piping state is not limited to the embodiment.
For example, the refrigerant may be configured to pass through a part of the upwind row 1111, pass through all the heat transfer tubes of the downwind row 1112, pass through the remaining flow paths of the upwind row 1111 again, and flow to the front surface side single-row heat exchanger 112 or the back surface side single-row heat exchanger 113. For example, the refrigerant may pass through the double-row heat exchanger 111, pass through the back-side single-row heat exchanger 113, and flow into the front-side single-row heat exchanger 112. For example, the refrigerant may flow into the front-side single-row heat exchanger 112 in a state where the uppermost layers 111b and 111c of the remaining two-row heat exchangers 111 are present, pass through the uppermost layers 111b and 111c of the two-row heat exchangers 111, and flow into the back-side single-row heat exchanger 113.
However, from the viewpoint of preventing dew condensation, the refrigerant needs to be sufficiently cooled when flowing from the double-row heat exchanger 111 into the front-surface-side single- row heat exchangers 112 and 113, and the refrigerant temperature is preferably cooled to a temperature close to the dew point temperature. Therefore, the indoor heat exchanger 110 is disposed with a flow path from the double-row heat exchanger to the single-row heat exchanger so that the connection between the front-surface-side single-row heat exchanger 112 and the double-row heat exchanger 111 is at a temperature determined by the dew-point temperature after passing through the double-row heat exchanger 111. Here, the connection portion is a region from the double-row heat exchanger 111d to the uppermost layer 112a of the single-row heat exchanger 112. The temperature determined by the dew point temperature may be the dew point temperature, or may be a value higher or lower by a predetermined temperature than the dew point temperature. The temperature determined according to the dew point temperature may have a predetermined temperature width.
From the viewpoint of preventing condensation, the expansion valve and the front-surface-side heat exchanger 112 may be connected to the flow passage of the double-column heat exchanger 111 at a distance of at least half of the total flow passage of the indoor heat exchanger 110 so that the refrigerant flows into the single-column heat exchanger after passing through at least half of the total flow passage of the indoor heat exchanger 110 in the double-column heat exchanger 111.
As a second modification, the indoor heat exchanger 110 may have a plurality of heat exchangers having different numbers of rows, and the combination of the numbers of rows is not limited to the embodiment. For example, the indoor heat exchanger 110 may have three-column heat exchangers and two-column heat exchangers. In this case, the indoor heat exchanger 110 may be arranged such that the refrigerant first passes through the heat exchangers having a larger number of rows, and after passing through a distance that is cooled to a temperature near the dew point temperature, the refrigerant flows into the heat exchangers having a smaller number of rows. Further, for example, a heat exchanger having three or more rows such as a three-row heat exchanger, a two-row heat exchanger, and a single-row heat exchanger may be used. In this case, the indoor heat exchanger 110 is arranged such that the refrigerant passes through the heat exchangers having the large number of columns in the order corresponding to the number of columns.
(second embodiment)
Next, the indoor heat exchanger 110 according to the second embodiment will be mainly described with respect to the differences from the indoor heat exchanger 110 according to the first embodiment. Fig. 5 is a sectional view of the indoor heat exchanger 110 of the second embodiment. In the indoor heat exchanger 110 of the second embodiment, the refrigerant flows into the double-column heat exchanger 111 in one flow path, and is branched into two flow paths (two-way paths) in the double-column heat exchanger 111. The expansion valve and the lowermost layer 111a of the double-column heat exchanger 111 are connected by a pipe, and as shown in fig. 5, the refrigerant flows into the lowermost layer 111a of the double-column heat exchanger 111. The flow path flowing upward from the lowest stage 111a branches into two flow paths in the third stage 111e from above in the windward row 1111. One flow path is as follows: after moving from the third floor 111e to the upper floor 111f and the uppermost floor 111b, the air flows to the second floor 111g from the top of the leeward row 1112, then to the uppermost floor 111c, and then flows from the uppermost floor 113a to the lowermost floor 113b of the rear-side single-row heat exchanger 113. The other flow path is as follows: the third layer 111e from the top of the upwind row 1111 flows to the third layer 111h from the top of the downwind row 1112, then flows downward in the downwind row 1112, and then flows from the uppermost layer 112a to the lowermost layer 112b of the front surface side single-row heat exchanger 112.
Thus, by using the two-path structure, the pressure loss of the refrigerant in the heat transfer tubes of the indoor heat exchanger 110 is reduced. However, since the pressure loss is not zero, the temperature of the refrigerant on the inlet side is high, and the temperature of the refrigerant on the outlet side is low. Therefore, in this dual channel structure, the following channels are also provided: the refrigerant first flows through the two-row heat exchanger 111, and then flows through the front-surface-side single-row heat exchanger 112 or the back-surface-side single-row heat exchanger 113. Thus, after branching into two paths, the refrigerant that has been sufficiently cooled can flow through both the front-side single-row heat exchanger 112 and the back-side single-row heat exchanger 113. Accordingly, it is possible to eliminate insufficient cooling of the air and reduce a temperature difference in the temperature of the air passing through the indoor heat exchanger 110.
As a modification of the second embodiment, the branching position and the branched flow path are not limited to the embodiments. Wherein the branching position is preferably within the double heat exchanger 111. It is preferable that the branching position is determined so that the distances of the respective paths after branching are equal. In the indoor heat exchanger 110 according to the second embodiment, the outlet of the indoor heat exchanger 110 is provided in the front-side single-row heat exchanger 112 or the rear-side single-row heat exchanger 113.
(third embodiment)
Next, the indoor heat exchanger according to the third embodiment will be mainly described with respect to points different from the indoor heat exchangers according to the other embodiments. Fig. 6 is a sectional view of an indoor heat exchanger 210 of the third embodiment. The indoor heat exchanger 210 according to the third embodiment includes a double-column heat exchanger 221 integrally provided from the upper portion to the lower portion of the front surface, instead of the double-column heat exchanger 111 and the front-surface-side single-column heat exchanger 112 of the indoor heat exchanger 110 according to the first embodiment.
In such a configuration, the refrigerant flowing into the indoor heat exchanger 210 during the cooling operation first passes through the double-row heat exchanger 221, and then flows into the rear-side single-row heat exchanger 222. The flow path of the refrigerant is a single passage. In the indoor heat exchanger 210 of the present embodiment, during cooling operation, the refrigerant first flows into the double-column heat exchanger 221 with the lowermost layer 221a of the upwind column 2211 of the double-column heat exchanger 221 as an inlet port. The refrigerant then flows upward from the lowermost layer 221a to the uppermost layer 221b, and then downward from the uppermost layer 221c to the lowermost layer 221d of the lower air column 2212. Thereafter, the refrigerant flows into the uppermost stage 222a of the back-side single-row heat exchanger 222, flows downward to the lowermost stage 222b, and flows out with the lowermost stage 222b as an outlet.
In the indoor heat exchanger 210 of the third embodiment, as in the indoor heat exchangers of the other embodiments, the refrigerant first flows into the double-row heat exchanger 221, passes through all the channels of the double-row heat exchanger 221, and then flows into the back-side single-row heat exchanger 222. That is, the sufficiently cooled refrigerant flows into the rear-side single-row heat exchanger 222. Accordingly, the temperature difference of the air passing through the indoor heat exchanger 210 can be reduced, and condensation can be prevented.
(fourth embodiment)
Next, the indoor heat exchanger 210 according to the fourth embodiment will be described only with respect to the points different from the indoor heat exchanger 210 according to the third embodiment. Fig. 7 is a sectional view of an indoor heat exchanger 210 of the fourth embodiment. In the indoor heat exchanger 210 according to the fourth embodiment, the refrigerant flows into the double-column heat exchanger 221 through one flow path, and the interior of the double-column heat exchanger 221 is divided into two flow paths.
As shown in fig. 7, the refrigerant flows into the fifth layer 221e from below of the upwind row 2211 of the double-row heat exchanger 221. The refrigerant flows upward from the fifth layer 221e to the uppermost layer 221 b. The channel branches into two channels at the uppermost layer 221 b. One flow path is as follows: the refrigerant flows from the uppermost layer 221b of the upwind row 2211 into the tenth layer 221f of the downwind row 2212 from above, flows upwind to the uppermost layer 221c, flows into the uppermost layer 222a of the rear-side single-row heat exchanger 222, and has the fourth layer 222c from above as an outlet port. The other flow path is as follows: the air flows from the uppermost layer 221b of the upwind row 2211 into the sixth layer 221g from below of the downwind row 2212, flows downward from the fourth layer 221i from below to the lowermost layer 221a of the upwind row 2211 through the 221h of the next layer, flows into the lowermost layer 222b of the back-face-side single-row heat exchanger 222, and has the fourth layer 222d from below as an outflow port.
As described in the second embodiment, in the two-pass structure, the difference in the temperature of the air passing through the indoor heat exchanger 210 can be reduced by first flowing the refrigerant to the double-row heat exchanger 221 and then flowing the refrigerant to the rear-side single-row heat exchanger 222. Further, in the present embodiment, the outlets of the passages are all provided in the back-side single-row heat exchanger 222. If one passage outlet is provided in the back-side single-row heat exchanger 222 and the other passage outlet is provided in the double-row heat exchanger 221, the refrigerant on the outlet side having a decreased temperature may pass through the double-row heat exchanger 221, and the air may be excessively cooled. In order to avoid such excessive cooling, in the present embodiment, as in the above-described embodiments, the outlets of the passages are provided in the rear-side single-row heat exchanger 222.
Description of the symbols
10-air conditioner, 100-indoor unit, 110-heat exchanger, 111-double-row heat exchanger, 112-front surface side single-row heat exchanger, 113-back surface side single-row heat exchanger.
The claims (modification according to treaty clause 19)
(modified) an air conditioner comprising an indoor unit and an outdoor unit,
the air conditioner is characterized in that the air conditioner is provided with a fan,
the indoor unit is provided with an indoor heat exchanger,
the outdoor unit is provided with an expansion valve,
the indoor heat exchanger includes a double-row heat exchanger having two rows of heat transfer tubes and a single-row heat exchanger having one row of heat transfer tubes,
the double-row heat exchanger is arranged on the front surface side of the indoor unit,
the single-row heat exchanger is disposed on the back side of the indoor unit,
in the cooling operation, the expansion valve is connected to the single-row heat exchanger via at least a part of one row of the double-row heat exchanger and at least a part of the other row of the double-row heat exchanger,
the flow path of the indoor heat exchanger is formed by a single passage.
(modified) an air conditioner comprising an indoor unit and an outdoor unit,
the air conditioner is characterized in that the air conditioner is provided with a fan,
the indoor unit is provided with an indoor heat exchanger,
the outdoor unit is provided with an expansion valve,
the indoor heat exchanger includes a double-row heat exchanger having two rows of heat transfer tubes and a single-row heat exchanger having one row of heat transfer tubes,
the double-row heat exchanger is arranged on the front surface side of the indoor unit,
the indoor heat exchanger has a first single-row heat exchanger and a second single-row heat exchanger,
the first single-row heat exchanger is disposed on the back surface side of the indoor unit,
the second single-row heat exchanger is disposed below the double-row heat exchanger,
in the cooling operation, the expansion valve is connected to the single-row heat exchanger via at least a part of one row of the double-row heat exchanger and at least a part of the other row of the double-row heat exchanger,
the flow path of the indoor heat exchanger is formed by a single passage.
(modified) the air conditioner according to claim 1 or 2,
the expansion valve is connected to at least a part of the other row via the entire one row.
(modified) the air conditioner according to any one of claims 1 to 3,
the expansion valve is connected to the single-row heat exchanger through all the flow paths in the double-row heat exchanger.
(modified) the air conditioner according to any one of claims 1 to 4,
the double-row heat exchanger is configured to be arranged such that the temperature of a connection portion between the single-row heat exchanger and the double-row heat exchanger is a temperature determined according to a dew-point temperature.
(modified) the air conditioner according to any one of claims 1 to 5,
the expansion valve is connected to the single-row heat exchanger through at least half of all the flow paths of the double-row heat exchanger in the double-row heat exchanger.
(modified) the air conditioner according to any one of claims 1 to 6,
the double-row heat exchanger is connected to a heat transfer pipe provided at a position closest to the double-row heat exchanger in the single-row heat exchanger.
(modified) the air conditioner according to any one of claims 1 to 7,
the one row of the double-row heat exchanger is arranged in a direction opposite to the direction of gravity from the expansion valve side.
(modified) the air conditioner according to any one of claims 1 to 8,
the one row is arranged on the windward side of the wind flowing into the double-row heat exchanger,
the other row is arranged on the leeward side of the wind flowing into the double-row heat exchanger.
(modified) the air conditioner according to any one of claims 1 to 9,
the outlet port for the cooling operation of the indoor heat exchanger is provided in the single-row heat exchanger.
(modified) the air conditioner according to any one of claims 1 to 10,
the heat transfer pipe of the indoor heat exchanger is formed of aluminum or an aluminum alloy.
(modified) an air conditioner comprising an indoor unit and an outdoor unit, characterized in that,
the indoor unit is provided with an indoor heat exchanger,
the outdoor unit is provided with an expansion valve,
the indoor heat exchanger includes a double-row heat exchanger having two rows of heat transfer tubes and a single-row heat exchanger having one row of heat transfer tubes,
the double-row heat exchanger is arranged on the front surface side of the indoor unit,
the single-row heat exchanger is disposed on the back side of the indoor unit,
in the cooling operation, the expansion valve is connected to the first heat exchanger through at least a part of the double-row heat exchanger,
the double-row heat exchanger is configured such that the temperature of the connection portion between the single-row heat exchanger and the double-row heat exchanger is set to a temperature determined according to the dew-point temperature,
the flow path of the indoor heat exchanger is formed by a single passage.
(modified) an air conditioner comprising an indoor unit and an outdoor unit, characterized in that,
the outdoor unit is provided with an expansion valve,
the indoor heat exchanger includes a double-row heat exchanger having two rows of heat transfer tubes arranged therein, a first single-row heat exchanger having one row of heat transfer tubes arranged therein, and a second single-row heat exchanger having one row of heat transfer tubes arranged therein,
the double-row heat exchanger is arranged on the front surface side of the indoor unit,
the first single-row heat exchanger is disposed below the double-row heat exchanger,
the second single-row heat exchanger is disposed on the back surface side of the indoor unit,
in the cooling operation, the expansion valve is connected to the first single-row heat exchanger and the second single-row heat exchanger via at least a part of the double-row heat exchanger,
the double-row heat exchanger is configured so that the temperature of the connection portion between the double-row heat exchanger and the first single-row heat exchanger is set to a temperature determined according to the dew-point temperature,
the flow path of the indoor heat exchanger is formed by a single passage.
(modified) an air conditioner comprising an indoor unit and an outdoor unit, characterized in that,
the indoor unit is provided with an indoor heat exchanger,
the indoor heat exchanger includes a double-row heat exchanger having two rows of heat transfer tubes and a single-row heat exchanger having one row of heat transfer tubes,
the double-row heat exchanger is arranged on the front surface side of the indoor unit,
the single-row heat exchanger is disposed on the back side of the indoor unit,
the outdoor unit is provided with an expansion valve,
in the cooling operation, the expansion valve is connected to the single-row heat exchanger via at least half of all the flow paths of the double-row heat exchanger in the double-row heat exchanger,
the flow path of the indoor heat exchanger is formed by a single passage.
(modified) an air conditioner comprising an indoor unit and an outdoor unit, characterized in that,
the indoor unit is provided with an indoor heat exchanger,
the indoor heat exchanger includes a double-row heat exchanger having two rows of heat transfer tubes arranged therein, a first single-row heat exchanger having one row of heat transfer tubes arranged therein, and a second single-row heat exchanger having one row of heat transfer tubes arranged therein,
the double-row heat exchanger is arranged on the front surface side of the indoor unit,
the first single-row heat exchanger is disposed below the double-row heat exchanger,
the second single-row heat exchanger is disposed on the back surface side of the indoor unit,
the outdoor unit is provided with an expansion valve,
in the cooling operation, the expansion valve is connected to the first single-row heat exchanger and the second single-row heat exchanger via half or more of all the flow paths of the double-row heat exchanger in the double-row heat exchanger,
the flow path of the indoor heat exchanger is formed by a single passage.
(modified) an air conditioner comprising an indoor unit and an outdoor unit, characterized in that,
the indoor unit is provided with an indoor heat exchanger,
the outdoor unit is provided with an expansion valve,
the indoor heat exchanger includes m rows of heat exchangers in which m rows of heat transfer pipes are arranged and n rows of heat exchangers in which n rows of heat transfer pipes are arranged,
the m-row heat exchanger is arranged on the front surface side of the indoor unit,
the n rows of heat exchangers are disposed on the back side of the indoor unit,
in the cooling operation, the expansion valve is connected to the n-row heat exchangers via at least a part of the first row of the m-row heat exchangers and at least a part of the second row of the m-row heat exchangers,
the flow path of the indoor heat exchanger is formed of a single passage,
wherein m is an integer of 2 or more, and n is an integer of 1 or more and smaller than m.
(modified) an air conditioner comprising an indoor unit and an outdoor unit, characterized in that,
the indoor unit is provided with an indoor heat exchanger,
the outdoor unit is provided with an expansion valve,
the indoor heat exchanger includes an m-row heat exchanger in which m rows of heat transfer tubes are arranged, a first n-row heat exchanger in which n rows of heat transfer tubes are arranged, and a second n-row heat exchanger in which n rows of heat transfer tubes are arranged,
the m-row heat exchanger is arranged on the front surface side of the indoor unit,
the first n-row heat exchanger is arranged below the m-row heat exchanger,
the second n-row heat exchanger is disposed on the back surface side of the indoor unit,
in the cooling operation, the expansion valve is connected to the first n-row heat exchanger and the second n-row heat exchanger via at least a part of the first row of the m-row heat exchangers and at least a part of the second row of the m-row heat exchangers,
the flow path of the indoor heat exchanger is formed of a single passage,
wherein m is an integer of 2 or more, and n is an integer of 1 or more and smaller than m.
(deletion)
Claims (18)
1. An air conditioner is provided with an indoor unit and an outdoor unit,
the air conditioner is characterized in that the air conditioner is provided with a fan,
the indoor unit is provided with an indoor heat exchanger,
the outdoor unit is provided with an expansion valve,
the indoor heat exchanger includes a double-row heat exchanger having two rows of heat transfer tubes and a single-row heat exchanger having one row of heat transfer tubes,
the expansion valve is connected to the single-row heat exchanger via at least a part of one row of the double-row heat exchanger and at least a part of the other row of the double-row heat exchanger.
2. The air conditioner according to claim 1,
the expansion valve is connected to at least a part of the other row via the entire one row.
3. An air conditioner according to claim 1 or 2,
the expansion valve is connected to the single-row heat exchanger through all the flow paths in the double-row heat exchanger.
4. An air conditioner according to any one of claims 1 to 3,
the double-row heat exchanger is configured to be arranged such that the temperature of a connection portion between the single-row heat exchanger and the double-row heat exchanger is a temperature determined according to a dew-point temperature.
5. An air conditioner according to any one of claims 1 to 4,
the expansion valve is connected to the single-row heat exchanger through at least half of all the flow paths of the heat exchangers in the double-row heat exchanger.
6. An air conditioner according to any one of claims 1 to 5,
the double-row heat exchanger is connected to a heat transfer pipe provided at a position closest to the double-row heat exchanger in the single-row heat exchanger.
7. An air conditioner according to any one of claims 1 to 6,
the double-row heat exchanger is arranged on the front surface side of the indoor unit,
the single-row heat exchanger is disposed on the back surface side of the indoor unit.
8. An air conditioner according to any one of claims 1 to 6,
the double-row heat exchanger is arranged on the front surface side of the indoor unit,
the indoor heat exchanger has a first single-row heat exchanger and a second single-row heat exchanger,
the first single-row heat exchanger is disposed on the back surface side of the indoor unit,
the second single-row heat exchanger is disposed below the double-row heat exchanger.
9. An air conditioner according to any one of claims 1 to 8,
the one row of the double-row heat exchanger is arranged in a direction opposite to the direction of gravity from the expansion valve side.
10. An air conditioner according to any one of claims 1 to 9,
the one row is arranged on the windward side of the wind flowing into the double-row heat exchanger,
the other row is arranged on the leeward side of the wind flowing into the double-row heat exchanger.
11. An air conditioner according to any one of claims 1 to 10,
the outlet port for the cooling operation of the indoor heat exchanger is provided in the single-row heat exchanger.
12. An air conditioner according to any one of claims 1 to 11,
the flow path of the indoor heat exchanger is formed by a single passage.
13. An air conditioner according to any one of claims 1 to 11,
the flow path of the indoor heat exchanger is branched from the single path to the double path.
14. An air conditioner according to any one of claims 1 to 13,
the branch is arranged in the double-row heat exchanger.
15. An air conditioner according to any one of claims 1 to 14,
the heat transfer pipe of the indoor heat exchanger is formed of aluminum or an aluminum alloy.
16. An air conditioner comprising an indoor unit and an outdoor unit, characterized in that,
the indoor unit is provided with an indoor heat exchanger,
the outdoor unit is provided with an expansion valve,
the indoor heat exchanger includes a double-row heat exchanger having two rows of heat transfer tubes and a single-row heat exchanger having one row of heat transfer tubes,
the expansion valve is connected to the first heat exchanger through at least a part of the two-column heat exchanger,
the double-row heat exchanger is configured to be arranged such that the temperature of a connection portion between the single-row heat exchanger and the double-row heat exchanger is a temperature determined according to a dew-point temperature.
17. An air conditioner comprising an indoor unit and an outdoor unit, characterized in that,
the indoor unit is provided with an indoor heat exchanger,
the indoor heat exchanger includes a double-row heat exchanger having two rows of heat transfer tubes and a single-row heat exchanger having one row of heat transfer tubes,
the expansion valve is connected to the single-row heat exchanger through at least half of all the flow paths of the heat exchangers in the double-row heat exchanger.
18. An air conditioner comprising an indoor unit and an outdoor unit, characterized in that,
the indoor unit is provided with an indoor heat exchanger,
the outdoor unit is provided with an expansion valve,
the indoor heat exchanger includes m rows of heat exchangers in which m rows of heat transfer pipes are arranged and n rows of heat exchangers in which n rows of heat transfer pipes are arranged,
the expansion valve is connected to the n-row heat exchanger via at least a part of the first row of the m-row heat exchangers and at least a part of the second row of the m-row heat exchangers,
wherein m is an integer of 2 or more, and n is an integer of 1 or more and smaller than m.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2019/009993 WO2020183606A1 (en) | 2019-03-12 | 2019-03-12 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111936792A true CN111936792A (en) | 2020-11-13 |
| CN111936792B CN111936792B (en) | 2021-10-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980004700.9A Active CN111936792B (en) | 2019-03-12 | 2019-03-12 | Air conditioner |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6641070B1 (en) |
| CN (1) | CN111936792B (en) |
| TW (1) | TWI731588B (en) |
| WO (1) | WO2020183606A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022252681A1 (en) * | 2021-06-01 | 2022-12-08 | 广东美的暖通设备有限公司 | Wall-mounted air conditioner |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2020183606A1 (en) | 2020-09-17 |
| TW202033917A (en) | 2020-09-16 |
| JP6641070B1 (en) | 2020-02-05 |
| JPWO2020183606A1 (en) | 2021-04-01 |
| CN111936792B (en) | 2021-10-22 |
| TWI731588B (en) | 2021-06-21 |
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