Classifications

• • 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
  • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
  • F24F1/26—Refrigerant piping
  • F24F1/30—Refrigerant piping for use inside the separate outdoor units
• • 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
  • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
  • F24F1/46—Component arrangements in separate outdoor units
  • F24F1/48—Component arrangements in separate outdoor units characterised by air airflow, e.g. inlet or outlet airflow
  • F24F1/50—Component arrangements in separate outdoor units characterised by air airflow, e.g. inlet or outlet airflow with outlet air in upward direction
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
  • F24F11/00—Control or safety arrangements
  • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
  • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
  • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers

Definitions

• This disclosure relates to a top-flow type outdoor unit that constitutes an air conditioning system, and to the air conditioning system.
• Patent Document 1 Conventionally, outdoor units have been proposed that aim to suppress the decrease in heat exchange rate caused by uneven wind speed distribution of wind passing through the heat exchanger in top-flow outdoor units (see, for example, Patent Document 1).
• the outdoor unit of Patent Document 1 has a heat exchanger that includes an inlet header, an outlet header, multiple rooms separated by partitions inside the inlet header, multiple flat tubes arranged in parallel and connected to each room and the outlet header, a distributor provided in the refrigerant piping, and multiple branch pipes connected to each room and the distributor.
• the branch pipes are provided with branch sections between the rooms and the distributor according to the wind speed distribution, and the number of branch sections of the branch pipes connected to rooms connected to flat tubes located in areas with high wind speeds is configured to be smaller than the number of branch sections of the branch pipes connected to rooms connected to flat tubes passing through areas with low wind speeds.
• the outdoor unit of Patent Document 1 is equipped with a heat exchanger having heat transfer tubes extending horizontally, and realizes refrigerant distribution suitable for the wind speed distribution in the vertical direction of the housing.
• the outdoor unit needs to realize refrigerant distribution suitable for the wind speed distribution in the direction in which the heat transfer tubes are arranged in parallel, that is, the circumferential direction of the housing, rather than the vertical wind speed distribution.
• FIG. 4 is a refrigerant circuit diagram of a second modified example of the air conditioning apparatus according to Embodiment 1.
• FIG. 11 is a refrigerant circuit diagram of a third modified example of the air conditioning apparatus according to Embodiment 1.
• 11 is a conceptual diagram for explaining an example of a flow rate adjustment mechanism in an outdoor unit of an air-conditioning apparatus according to Embodiment 2.
• FIG. 13 is a conceptual diagram for explaining an example of a flow rate adjustment mechanism in an outdoor unit of an air-conditioning apparatus according to embodiment 3.
• FIG. 13 is a conceptual diagram for explaining an example of a flow rate adjustment mechanism in an outdoor unit of an air-conditioning apparatus according to embodiment 4.
• FIG. 11 is a refrigerant circuit diagram of a third modified example of the air conditioning apparatus according to Embodiment 1.
• 11 is a conceptual diagram for explaining an example of a flow rate adjustment mechanism in an outdoor unit of an air-conditioning apparatus according to Embodiment 2.
• FIG. 13 is a conceptual diagram for explaining an example
• Fig. 1 is a refrigerant circuit diagram showing an example of a basic configuration of an air-conditioning apparatus 1 according to embodiment 1. The air-conditioning apparatus 1 will be described with reference to Fig. 1. Note that Fig. 1 shows the circuit configuration of a refrigerant circuit 100, which will be described later, and the length of the flow path of a pipe 101 constituting the refrigerant circuit 100 differs from the actual length.
• the air conditioner 1 is a device that performs air conditioning by heating or cooling the room by transferring heat between the outside air and the indoor air via a refrigerant.
• the air conditioner 1 according to the first embodiment includes an outdoor unit 10 and an indoor unit 20 that is connected to the outdoor unit 10 by piping 101 that circulates the refrigerant, has an indoor heat exchanger 22, and performs heat exchange between the indoor air and the refrigerant flowing inside. Note that while FIG. 1 shows one outdoor unit 10 and one indoor unit 20, there may be more than one outdoor unit 10 and more than one indoor unit 20.
• the compressor 11 and the accumulator 16 are internal components 19 of the outdoor unit 10.
• the internal components 19 are components used in the operation of the outdoor unit 10 and the air conditioning device 1.
• the internal components 19 are components that occupy a large volume in the internal space 45 of the outdoor unit 10 (see FIG. 4). Note that if the outdoor unit 10 does not have an accumulator 16, the internal components 19 are the compressor 11.
• the internal components 19 are composed of either or both of the compressor 11 that compresses and discharges the refrigerant, or the accumulator 16 that stores liquid refrigerant inside the housing 40.
• Compressor 11 draws in low-temperature, low-pressure refrigerant, compresses it, and discharges high-temperature, high-pressure refrigerant.
• Compressor 11 is, for example, an inverter compressor whose capacity, which is the amount of refrigerant discharged per unit time, is controlled by changing the operating frequency.
• the flow path switching device 12 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the direction of refrigerant flow. During cooling operation, the flow path switching device 12 switches to connect the discharge side of the compressor 11 to the heat exchanger 30. During heating operation, the flow path switching device 12 switches to connect the discharge side of the compressor 11 to the indoor heat exchanger 22.
• the air conditioning device 1 can achieve cooling operation, heating operation, or defrost operation by switching the flow of refrigerant using the flow path switching device 12 based on instructions from a control device (not shown).
• the heat exchanger 30 exchanges heat between the outdoor air and the refrigerant.
• the heat exchanger 30 functions as a condenser that releases heat from the refrigerant to the outdoor air and condenses the refrigerant.
• the heat exchanger 30 absorbs heat from the outdoor air to evaporate the refrigerant, and functions as an evaporator that cools the outdoor air with the heat of vaporization.
• the outdoor unit 10 has three heat exchangers 30, namely, heat exchanger 30a, heat exchanger 30b, and heat exchanger 30c.
• the outdoor unit 10 has three heat exchangers 30, but the number of heat exchangers 30 mounted on the outdoor unit 10 is not limited to three.
• the outdoor unit 10 may have multiple heat exchangers 30, and may have, for example, two heat exchangers 30 or four heat exchangers 30.
• the flow rate control valve 13 is, for example, an electronic expansion valve that can adjust the throttle opening, and by adjusting the opening, the pressure of the refrigerant flowing into the heat exchanger 30 that functions as an evaporator is controlled.
• the outdoor unit 10 in the refrigerant circuit 100 of the air conditioning device 1 shown in Figure 1 the outdoor unit 10 has two flow rate control valves 13, a flow rate control valve 13a and a flow rate control valve 13b.
• the on-off valve 14 is a two-way valve that allows the flow of refrigerant when open and restricts the flow of refrigerant when closed, and is open during cooling operation and closed during heating operation.
• the check valve 15 prevents the refrigerant from flowing backwards and restricts the refrigerant to flow in only one direction. Note that a two-way valve may be provided instead of the check valve 15.
• the temperature sensor 17 is, for example, a thermistor, and is provided in the pipe 101a between the heat exchanger 30c and the flow control valve 13b to detect the temperature of the refrigerant flowing through the pipe 101a. As will be described later, this temperature sensor 17 is provided only in the pipe 101a on the outlet side of the heat exchanger 30c, which is downstream during cooling operation and defrost operation.
• the pipe 101a is part of the multiple pipes 101 that make up the refrigerant circuit 100.
• the indoor unit 20 includes an expansion device 21 , an indoor heat exchanger 22 , and an indoor fan 23 .
• the indoor heat exchanger 22 exchanges heat between the indoor air and the refrigerant.
• the indoor heat exchanger 22 functions as an evaporator that evaporates the refrigerant and cools the indoor air with the heat of vaporization.
• the indoor heat exchanger 22 functions as a condenser that releases heat from the refrigerant to the indoor air to condense the refrigerant.
• the indoor fan 23 supplies indoor air to the indoor heat exchanger 22, and the amount of air sent to the indoor heat exchanger 22 is adjusted by controlling the rotation speed.
• FIG. 2 is a perspective view of the outdoor unit 10 of the air conditioning apparatus 1 according to the first embodiment, as seen from the front.
• FIG. 3 is a perspective view of the outdoor unit 10 of the air conditioning apparatus 1 according to the first embodiment, as seen from the back.
• FIG. 4 is an exploded perspective view of the outdoor unit 10 of the air conditioning apparatus 1 according to the first embodiment, as seen from the front.
• FIG. 5 is an exploded perspective view of the outdoor unit 10 of the air conditioning apparatus 1 according to the first embodiment, as seen from the side.
• FIG. 6 is a conceptual diagram showing a plan view of the internal configuration of the outdoor unit 10 of the air conditioning apparatus 1 according to the first embodiment.
• the basic configuration of the outdoor unit 10 will be described with reference to FIGS. 2 to 6.
• Each of the first surface 40a, the second surface 40b, and the third surface 40c of the housing 40 is a flow surface that allows air to flow, and has an air intake port 40f formed therein.
• a heat exchanger 30 is installed in each of the intake ports 40f on the first surface 40a, the second surface 40b, and the third surface 40c of the housing 40.
• the housing 40 contains a plurality of heat exchangers 30, internal parts 19 of the outdoor unit 10, a fan 18, and piping 110. More specifically, the housing 40 contains a plurality of heat exchangers 30, a compressor 11, an accumulator 16, a fan 18, and piping 110.
• the heat exchanger 30 is installed inside the housing 40 so as to cover the intake port 40f of the housing 40. Air flowing from the outside of the housing 40 to the inside due to the operation of the fan 18 flows in through the intake port 40f of the housing 40, passes between the heat transfer tubes 34 of the heat exchanger 30 described below, heads toward the fan 18 installed at the top, and is discharged to the outside of the housing 40 through the exhaust port 41.
• the specific configuration of the heat exchanger 30 will be described later.
• the internal parts 19 of the outdoor unit 10, such as the compressor 11 and the accumulator 16, are installed on the bottom 40e of the housing 40.
• the internal parts 19 are arranged inside the housing 40 closer to the center of the housing 40 than the multiple heat exchangers 30.
• the internal parts 19 are arranged on the air path leading from any one of the multiple heat exchangers 30 to the fan 18, generating ventilation resistance.
• the compressor 11 may include a compressor case 11a formed in a box shape.
• the compressor 11 is housed in the compressor case 11a formed in a box shape.
• the compressor case 11a is included in the internal parts 19.
• the fan 18 is, for example, a propeller fan, and is disposed inside the housing 40 at the top of the housing 40.
• the fan 18 is a blowing means equipped with an axial fan, and creates an air flow for efficient heat exchange in the heat exchanger 30.
• the fan 18 takes in air from the side of the housing 40, passes it through multiple heat exchangers 30, and then blows it out upwards from the air outlet 41.
• the number of fans 18 is not limited to one, and multiple fans 18 may be used.
• the outdoor unit 10 needs to have at least one fan 18.
• FIG. 7 is a perspective view that shows a schematic diagram of the heat exchanger 30 of the air-conditioning apparatus 1 according to the first embodiment.
• the outline arrows in Fig. 7 indicate the flow direction of air, and the solid arrows in Fig. 7 indicate the flow of the refrigerant.
• the inlet and outlet of the refrigerant in Fig. 7 indicate the inlet and outlet when the heat exchanger 30 functions as an evaporator.
• Heat exchanger 30 is disposed inside housing 40, has multiple heat transfer tubes 34 extending in the vertical direction, and exchanges heat between the refrigerant and air.
• Heat exchanger 30a, heat exchanger 30b, and heat exchanger 30c are of a corrugated fin tube type with parallel piping. As shown in FIG. 1, heat exchanger 30a, heat exchanger 30b, and heat exchanger 30 are each connected by piping in parallel in refrigerant circuit 100. In other words, the multiple heat exchangers 30 are each connected by piping in parallel.
• each heat exchanger 30 has a plurality of heat transfer tubes 34, a plurality of fins 35, two distribution headers 31, a first distribution header 31A and a second distribution header 31B, and a turn-up header 33.
• the distribution header 31 and the turn-up header 33 are also simply referred to as headers.
• the distribution header 31 is a general term for the first distribution header 31A and the second distribution header 31B.
• Each of the multiple heat exchangers 30 has multiple heat transfer tubes 34 extending in the vertical direction between the two distribution headers 31 and the turn-back header 33.
• the multiple heat transfer tubes 34 are arranged so as to be perpendicular to the distribution header 31 and the turn-back header 33 and parallel to each other.
• the heat transfer tube 34 When the heat transfer tube 34 is a flat tube, the heat transfer tube 34 has a flat cross section, the outer surface on the long side of the flat shape along the air flow direction is flat, and the outer surface on the short side perpendicular to the long direction is curved.
• the heat transfer tube 34 is a flat tube, the heat transfer tube 34 is a multi-hole flat tube having multiple holes inside the tube that serve as a flow path for the refrigerant.
• the holes that serve as the ducts of the heat transfer tube 34 are formed facing in the height direction because they serve as flow paths between the distribution header 31 and the turn-back header 33.
• each heat transfer tube 34 is inserted into an insertion hole (not shown) in the distribution header 31 and the turn-back header 33, and is brazed and joined to the distribution header 31 and the turn-back header 33.
• a brazing material containing aluminum, for example, is used for the brazing.
• the fins 35 are heat transfer promoting members, and are disposed between adjacent heat transfer tubes 34 among the plurality of heat transfer tubes 34, and are connected to the heat transfer tubes 34.
• the fins 35 are connected across the spaces between adjacent heat transfer tubes 34, and transfer heat between the connected heat transfer tubes 34.
• the fins 35 improve the efficiency of heat exchange between the air and the refrigerant, and the fins 35 are, for example, corrugated fins.
• each of the multiple heat exchangers 30 has multiple heat exchange elements 130 in the air flow direction.
• the heat exchange element 130 has the extension direction of the heat transfer tubes 34 in the up-down direction and has multiple heat transfer tubes 34 arranged at intervals in the horizontal direction.
• the heat exchange element 130 also has fins 35 joined to the heat transfer tubes 34. If the heat exchanger 30 does not have the fins 35, the heat exchange element 130 may be composed of only the multiple heat transfer tubes 34. In Fig. 7, two heat exchange elements 130 of the same size are arranged side by side in the air flow direction.
• the heat exchanger 30a is the first heat exchanger 231, and the heat exchangers 30b, 30c, and 30d are the second heat exchangers 232.
• the first piping section 111 is the piping section from the branching section P1 to the inlet section E1 of the heat exchanger 30a.
• the second piping section 112 is the piping section from the branching section P1 to the inlet section E1 of the heat exchanger 30b.
• the second piping section 112 is the piping section from the branching section P1 to the inlet section E1 of the heat exchanger 30c.
• the second piping section 112 is the piping section from the branching section P1 to the inlet section E1 of the heat exchanger 30d.
• FIG. 14 is a refrigerant circuit diagram of a third modified example of the air conditioning device 1 according to embodiment 1.
• the refrigerant circuit 100 may be configured as shown in FIG. 14.
• the refrigerant circuit 100 is configured so that the refrigerant flows in parallel through each of the multiple heat exchangers 30, namely, heat exchanger 30a, heat exchanger 30b, and heat exchanger 30c.
• the flow rate control valve 13a adjusts the flow rate of the refrigerant flowing into the heat exchanger 30a by changing its opening degree.
• the flow rate control valve 13b adjusts the flow rate of the refrigerant flowing into the heat exchanger 30b by changing its opening degree.
• the flow rate control valve 13c adjusts the flow rate of the refrigerant flowing into the heat exchanger 30c by changing its opening degree.
• the heat exchanger 30a is the first heat exchanger 231
• the heat exchanger 30b and the heat exchanger 30c are the second heat exchanger 232.
• the first piping section 111 is the piping section from the branching section P1 to the inlet section E1 of the heat exchanger 30a.
• the second piping section 112 is the piping section from the branching section P1 to the inlet section E1 of the heat exchanger 30b.
• the second piping section 112 is the piping section from the branching section P1 to the inlet section E1 of the heat exchanger 30c.
• the plurality of heat exchangers 30 of the outdoor unit 10 are configured by the flow rate adjustment mechanism 50 so that the refrigerant flow rate per each of the plurality of heat transfer tubes 34 flowing in the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the plurality of heat transfer tubes 34 flowing in the second heat exchanger 232.
• the internal parts 19 are arranged near the first heat exchanger 231, and the ventilation resistance of the air passing through the first heat exchanger 231 is greater than the ventilation resistance of the air passing through the second heat exchanger 232.
• the internal parts 19 are arranged near the first heat exchanger 231, and the amount of air passing through the first heat exchanger 231 is smaller than the amount of air passing through the second heat exchanger 232.
• an uneven air speed distribution occurs in the area where the first heat exchanger 231 is arranged and the area where the second heat exchanger 232 is arranged in the circumferential direction of the housing 40.
• the heat load distribution in the area where the first heat exchanger 231 is located is smaller than the heat load distribution in the area where the second heat exchanger 232 is located.
• the heat exchange performance of the multiple heat exchangers as a whole is improved when the refrigerant flow rate is adjusted in accordance with the wind speed distribution and heat load distribution, rather than when the refrigerant flow rate is uniform regardless of the wind speed distribution and heat load distribution.
• the multiple heat exchangers 30 of the outdoor unit 10 are configured by a flow rate adjustment mechanism 50 so that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing to the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing to the second heat exchanger 232.
• the outdoor unit 10 achieves appropriate refrigerant distribution in accordance with the wind speed distribution to reduce the impact of deterioration of the wind speed distribution due to internal parts 19 such as the compressor 11 or accumulator 16. Therefore, because the internal components 19 of the outdoor unit 10 are arranged close to each other, even if the amount of air passing through one of the heat exchangers 30 is small and an imbalance in the air speed distribution in the circumferential direction of the housing 40 occurs, the heat exchange performance of the entire heat exchangers 30 can be improved by controlling the amount of refrigerant flowing through the heat exchangers 30, compared to outdoor units that do not have the above configuration.
• the outdoor unit 10 achieves proper refrigerant distribution according to the air speed distribution by the above configuration in order to reduce the effect of deterioration of the air speed distribution due to internal parts 19 such as the compressor 11 or accumulator 16. Therefore, even if the air volume passing through one of the multiple heat exchangers 30 is small and an imbalance in the air speed distribution in the circumferential direction of the housing 40 occurs due to the internal parts 19 being arranged close to each other, the outdoor unit 10 can improve the heat exchange performance of the multiple heat exchangers 30 as a whole by controlling the refrigerant flow rate flowing through the multiple heat exchangers 30 compared to outdoor units that do not have the above configuration.
• the multiple heat exchangers 30 are configured so that the piping length L1 of the first piping section 111 is longer than the piping length L2 of the second piping section 112.
• the multiple heat exchangers 30 are configured so that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing in the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing in the second heat exchanger 232.
• the outdoor unit 10 achieves proper refrigerant distribution according to the air speed distribution by the above configuration in order to reduce the effect of deterioration of the air speed distribution due to internal parts 19 such as the compressor 11 or accumulator 16. Therefore, even if the air volume passing through one of the multiple heat exchangers 30 is small and an imbalance in the air speed distribution in the circumferential direction of the housing 40 occurs due to the internal parts 19 being arranged close to each other, the outdoor unit 10 can improve the heat exchange performance of the multiple heat exchangers 30 as a whole by controlling the refrigerant flow rate flowing through the multiple heat exchangers 30 compared to outdoor units that do not have the above configuration.
• the internal parts 19 are composed of either or both of a compressor 11 that compresses and discharges the refrigerant, or an accumulator 16 that stores liquid refrigerant inside the housing 40.
• the outdoor unit 10 can improve the heat exchange performance of the entire multiple heat exchangers 30 compared to outdoor units that do not have the above configuration by controlling the refrigerant flow rate and the like that flows through the multiple heat exchangers 30, even if the air volume passing through one of the multiple heat exchangers 30 becomes small and an imbalance in the air speed distribution in the circumferential direction of the housing 40 occurs.
• the piping section 110 in the flow rate adjustment mechanism 50 according to the second embodiment includes a bent section 113, which is a section where the piping is bent in the piping section 110.
• the number of bent sections 113 formed in the first piping section 111 is greater than the number of bent sections 113 formed in the second piping section 112.
• the angle of the bent sections 113 is formed at approximately 90 degrees, but the angle of the bent sections 113 is not limited to 90 degrees and may be other angles, such as 180 degrees.
• the bent sections 113 may be bent in the horizontal direction or in the vertical direction.
• the number of bent sections 113 is not limited to the number shown in FIG. 15.
• the flow rate adjustment mechanism 50 has more bends 113 formed in the first piping section 111 than in the second piping section 112, so that the pressure loss of the refrigerant flowing through the first piping section 111 is greater than the pressure loss of the refrigerant flowing through the second piping section 112. Therefore, by having the flow rate adjustment mechanism 50, the multiple heat exchangers 30 are configured so that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing through the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing through the second heat exchanger 232.
• the piping section 110 of the outdoor unit 10 includes a bent section 113, which is a section where the piping is bent in the piping section 110.
• the flow rate adjustment mechanism 50 includes a first piping section 111 and a second piping section 112.
• the plurality of heat exchangers 30 are formed such that the number of bent sections 113 formed in the first piping section 111 is greater than the number of bent sections 113 formed in the second piping section 112.
• the plurality of heat exchangers 30 are configured such that the refrigerant flow rate per each of the plurality of heat transfer tubes 34 flowing in the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the plurality of heat transfer tubes 34 flowing in the second heat exchanger 232.
• Embodiment 4. 17 is a conceptual diagram for explaining an example of a flow rate adjustment mechanism 50 in the outdoor unit 10 of an air conditioning apparatus 1 according to embodiment 4.
• the configuration of the flow rate adjustment mechanism 50 differs from that of embodiments 1 to 3.
• embodiment 4 will be explained, but explanations of parts that overlap with embodiments 1 to 3 will be omitted, and the same reference numerals will be used to denote the same or corresponding parts as in embodiments 1 to 3.
• the flow rate adjustment mechanism 50 is formed so that the height difference H1 between the bottom U1 and top T1 in the vertical direction of the pipeline of the first piping section 111 is greater than the height difference H2 between the bottom U2 and top T2 in the vertical direction of the pipeline of the second piping section 112.
• the flow rate adjustment mechanism 50 is formed so that the height difference H1 of the first piping section 111 is greater than the height difference H2 of the second piping section 112, so that the pressure loss of the refrigerant flowing through the first piping section 111 is greater than the pressure loss of the refrigerant flowing through the second piping section 112. Therefore, by having the flow rate adjustment mechanism 50, the multiple heat exchangers 30 are configured so that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing through the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing through the second heat exchanger 232.
• the flow rate adjustment mechanism 50 is composed of a plurality of heat exchangers 30.
• the flow rate adjustment mechanism 50 includes a first inner tube portion 361 which is the inner tube portion 36 of the first heat exchanger 231, and a second inner tube portion 362 which is the inner tube portion 36 of the second heat exchanger 232.
• the plurality of heat exchangers 30 are configured such that the refrigerant flow rate per each of the plurality of heat transfer tubes 34 flowing in the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the plurality of heat transfer tubes 34 flowing in the second heat exchanger 232 due to the difference between the shape of the first inner tube portion 361 which is the flow rate adjustment mechanism 50 and the shape of the second inner tube portion 362.
• the outdoor unit 10 achieves proper refrigerant distribution according to the air speed distribution by the above configuration in order to reduce the effect of deterioration of the air speed distribution due to internal parts 19 such as the compressor 11 or accumulator 16. Therefore, even if the air volume passing through one of the multiple heat exchangers 30 is small and an imbalance in the air speed distribution in the circumferential direction of the housing 40 occurs due to the internal parts 19 being arranged close to each other, the outdoor unit 10 can improve the heat exchange performance of the multiple heat exchangers 30 as a whole by controlling the refrigerant flow rate flowing through the multiple heat exchangers 30 compared to outdoor units that do not have the above configuration.
• the opening diameter of the distribution holes 39 in the first inner pipe section 361 and the opening diameter of the distribution holes 39 in the second inner pipe section 362 are the same size.
• the total opening area of the multiple distribution holes 39 obtained by adding up the opening areas of each of the multiple distribution holes 39 in the first inner pipe section 361 is smaller than the total opening area of the multiple distribution holes 39 obtained by adding up the opening areas of each of the multiple distribution holes 39 in the second inner pipe section 362.
• the flow rate adjustment mechanism 50 is configured so that the number of distribution holes 39 in the first inner tube section 361 is smaller than the number of distribution holes 39 in the second inner tube section 362, so that the pressure loss of the refrigerant flowing through the first inner tube section 361 is greater than the pressure loss of the refrigerant flowing through the second inner tube section 362. Therefore, by having the flow rate adjustment mechanism 50, the multiple heat exchangers 30 are configured so that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing through the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing through the second heat exchanger 232.
• the multiple heat exchangers 30 are formed such that the number of the multiple distribution holes 39 formed in the first inner pipe portion 361 is smaller than the number of the multiple distribution holes 39 formed in the second inner pipe portion 362.
• the multiple heat exchangers 30 are configured such that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing in the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing in the second heat exchanger 232.
• the air conditioning device 1 comprises an outdoor unit 10 having the above-mentioned configuration, and an indoor unit 20 that is connected to the outdoor unit 10 by piping through which a refrigerant flows, has an indoor heat exchanger 22, and performs heat exchange between the indoor air and the refrigerant flowing therethrough. Because the air conditioning device 1 comprises the outdoor unit 10 having the above-mentioned configuration, it can achieve the same effects as the outdoor unit 10.
• Embodiment 7. 20 is a conceptual diagram for explaining one example of a flow rate adjustment mechanism 50 in the outdoor unit 10 of an air conditioning apparatus 1 according to embodiment 7.
• the configuration of the flow rate adjustment mechanism 50 differs from that of embodiments 1 to 6.
• embodiment 7 will be explained, but explanations of parts that overlap with embodiments 1 to 6 will be omitted, and the same reference numerals will be used to denote the same or corresponding parts as those in embodiments 1 to 6.
• the flow rate adjustment mechanism 50 is composed of a plurality of heat exchangers 30.
• the flow rate adjustment mechanism 50 includes a first inner tube portion 361 which is the inner tube portion 36 of the first heat exchanger 231, and a second inner tube portion 362 which is the inner tube portion 36 of the second heat exchanger 232.
• the plurality of heat exchangers 30 are configured such that the refrigerant flow rate per each of the plurality of heat transfer tubes 34 flowing in the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the plurality of heat transfer tubes 34 flowing in the second heat exchanger 232 due to the difference between the shape of the first inner tube portion 361 which is the flow rate adjustment mechanism 50 and the shape of the second inner tube portion 362.
• the number of distribution holes 39 formed in the first inner pipe section 361 is the same as the number of distribution holes 39 formed in the second inner pipe section 362.
• the total opening area of the multiple distribution holes 39 obtained by adding up the opening areas of each of the multiple distribution holes 39 in the first inner pipe section 361 is smaller than the total opening area of the multiple distribution holes 39 obtained by adding up the opening areas of each of the multiple distribution holes 39 in the second inner pipe section 362.
• the multiple heat exchangers 30 are configured such that the opening diameter C1 of each of the multiple distribution holes 39 in the first inner tube section 361 is smaller than the opening diameter C2 of each of the multiple distribution holes 39 in the second inner tube section 362, so that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing in the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing in the second heat exchanger 232.
• the flow rate adjustment mechanism 50 is configured so that the opening diameter C1 of each of the multiple distribution holes 39 in the first inner tube section 361 is smaller than the opening diameter C2 of each of the multiple distribution holes 39 in the second inner tube section 362, so that the pressure loss of the refrigerant flowing through the first inner tube section 361 is greater than the pressure loss of the refrigerant flowing through the second inner tube section 362. Therefore, by having the flow rate adjustment mechanism 50, the multiple heat exchangers 30 are configured so that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing through the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing through the second heat exchanger 232.
• the flow rate adjustment mechanism 50 of the outdoor unit 10 includes a first inner pipe portion 361 and a second inner pipe portion 362.
• the opening diameter C1 of each of the multiple distribution holes 39 of the first inner pipe portion 361 is formed smaller than the opening diameter C2 of each of the multiple distribution holes 39 of the second inner pipe portion 362.
• the multiple heat exchangers 30 are configured so that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing in the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing in the second heat exchanger 232.
• the air conditioning device 1 comprises an outdoor unit 10 having the above-mentioned configuration, and an indoor unit 20 that is connected to the outdoor unit 10 by piping through which a refrigerant flows, has an indoor heat exchanger 22, and performs heat exchange between the indoor air and the refrigerant flowing therethrough. Because the air conditioning device 1 comprises the outdoor unit 10 having the above-mentioned configuration, it can achieve the same effects as the outdoor unit 10.
• Embodiment 8 Fig. 21 is a conceptual diagram for explaining an example of a flow rate adjustment mechanism 50 in the outdoor unit 10 of an air conditioning apparatus 1 according to embodiment 8.
• Fig. 22 is a conceptual diagram showing an example of an outdoor unit 10 of an air conditioning apparatus 1 according to embodiment 8.
• the configuration of the flow rate adjustment mechanism 50 differs from embodiments 1 to 7.
• embodiment 8 will be explained, but explanations of parts that overlap with embodiments 1 to 7 will be omitted, and the same reference numerals will be used to refer to the same or corresponding parts as embodiments 1 to 7.
• the piping section 110 of the outdoor unit 10 includes at least one or more flow rate adjustment valves 13e.
• the flow rate adjustment mechanism 50 has the piping section 110 including at least one or more flow rate adjustment valves 13e.
• the multiple heat exchangers 30 are configured such that the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing to the first heat exchanger 231 is smaller than the refrigerant flow rate per each of the multiple heat transfer tubes 34 flowing to the second heat exchanger 232, depending on the opening degree of the at least one or more flow rate adjustment valves 13e.

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• 2024
  • 2024-01-12 JP JP2025569241A patent/JPWO2025150184A1/ja active Pending
  • 2024-01-12 WO PCT/JP2024/000608 patent/WO2025150184A1/ja active Pending

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