JP2019052784A - Heat exchanger and air conditioner - Google Patents

Abstract

To provide a heat exchanger capable of further equally distributing a fluid which flows into a header, to multiple heat transfer pipes, and an air conditioner.SOLUTION: A heat exchanger comprises: a header into which ends of multiple heat transfer pipes are inserted; a first inflow pipe connected to one end of the header in a length direction; a second inflow pipe connected to the other end of the header in the length direction; and a partition wall partitioning the inside of the header into a first channel and a second channel. The header includes: a first inner wall surface on which multiple insertion holes to insert the ends of the multiple heat transfer pipes are formed; and a second inner wall surface which faces the first inner wall surface. The partition wall is formed while protruding from the second inner wall surface to the first inner wall surface, and a distal end of the partition wall in a protruding direction faces the ends of the multiple heat transfer pipes. The first inflow pipe is connected to the first channel, and the second inflow pipe is connected to the second channel.SELECTED DRAWING: Figure 7

Description

  The present invention relates to a heat exchanger and an air conditioner including a plurality of heat transfer tubes and a header.

  Patent Document 1 describes a heat exchanger provided with alternately stacked tubes and fins and tanks provided at both ends of the tubes. In the tank on the refrigerant inflow side, a wall protruding from the non-tube connection side toward the tube side is provided. The space in the tank is divided into an upstream portion and a downstream portion of the conditioned air by a wall. The tube is also separated into an upstream portion and a downstream portion of the conditioned air.

JP 2006-266521 A

  Patent Document 1 describes that the refrigerant can flow through all the tubes even when the flow rate of the refrigerant is small. However, the heat exchanger described in Patent Document 1 has a problem that the refrigerant is not necessarily distributed evenly to all the tubes.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a heat exchanger and an air conditioner that can evenly distribute the fluid flowing into the header to a plurality of heat transfer tubes. And

The heat exchanger according to the present invention is connected to a plurality of heat transfer tubes arranged in parallel to each other, a header into which each end portion of the plurality of heat transfer tubes is inserted, and one longitudinal end portion of the header. A first inflow pipe, a second inflow pipe connected to the other longitudinal end of the header, and a length extending along the longitudinal direction of the header; and the interior of the header includes a first flow path and a second flow path A first partition wall that is formed with a plurality of insertion holes into which respective end portions of the plurality of heat transfer tubes are inserted, and a header that is opposed to the first inner wall surface. The partition wall is formed so as to protrude from the second inner wall surface toward the first inner wall surface, and a front end portion of the partition wall in the protruding direction includes the plurality of wall surfaces. The first inflow pipe is connected to the first flow path. Are, the second inflow pipe is being connected to said second flow path.
The air conditioner according to the present invention includes the heat exchanger according to the present invention.

  In the present invention, the fluid that has flowed into the header from the first inflow pipe is distributed to the plurality of flat tubes while flowing in the first flow path in one direction. The fluid that has flowed into the header from the second inflow pipe is distributed to the plurality of flat tubes while flowing in the second flow path in the direction opposite to the one direction. Therefore, according to the present invention, even if fluid drift occurs in the longitudinal direction of each of the first channel and the second channel, the fluid can be more evenly distributed to the plurality of flat tubes.

It is a refrigerant circuit diagram which shows schematic structure of the air conditioner 100 which concerns on Embodiment 1 of this invention. It is a see-through | perspective perspective view which shows typically the structure of the heat source side unit 10 of the air conditioner 100 which concerns on Embodiment 1 of this invention. In the air conditioner 100 according to Embodiment 1 of the present invention, it is a PH diagram of a refrigeration cycle when a hydrofluorocarbon refrigerant R410a is used. It is an external appearance perspective view which shows the structure of the heat source side heat exchanger 13 which concerns on Embodiment 1 of this invention. It is a perspective view which shows the structure which looked at the V section vicinity of FIG. 4 from the upstream of the airflow. It is sectional drawing which shows typically the structure of the heat source side heat exchanger 13 which concerns on Embodiment 1 of this invention. It is sectional drawing which shows the VII-VII cross section of FIG. It is sectional drawing which shows the VIII-VIII cross section of FIG. It is a figure which shows the state of the refrigerant | coolant which flowed into the liquid header 1010 of the heat source side heat exchanger 13 which concerns on Embodiment 1 of this invention. In the heat source side heat exchanger 13 which concerns on Embodiment 1 of this invention, it is a graph which shows notionally the relationship between the position of the flat tube 13a, and the flow volume of the liquid phase refrigerant | coolant distributed to the flat tube 13a. The structure of the heat source side heat exchanger 13 which concerns on Embodiment 2 of this invention, and the branch structure 1050 connected to the 1st inflow pipe 1001 and the 2nd inflow pipe 1002 of the said heat source side heat exchanger 13 are typically shown. FIG. It is sectional drawing which shows typically the structure of the liquid header 1010 vicinity of the heat source side heat exchanger 13 which concerns on Embodiment 3 of this invention. It is sectional drawing which shows the XIII-XIII cross section of FIG. It is sectional drawing which shows typically the structure of the liquid header 1010 vicinity of the heat source side heat exchanger 13 which concerns on Embodiment 4 of this invention. It is sectional drawing which shows the XV-XV cross section of FIG. It is sectional drawing which shows typically the structure of the liquid header 1010 vicinity of the heat source side heat exchanger 13 which concerns on Embodiment 5 of this invention. It is sectional drawing which shows the XVII-XVII cross section of FIG. It is sectional drawing which shows the XVIII-XVIII cross section of FIG.

  Hereinafter, embodiments of a heat exchanger and an air conditioner according to the present invention will be described with reference to the drawings. In the drawings, components having the same functions and operations are denoted by the same reference numerals, and the description thereof is omitted or simplified as appropriate. In addition, the shape, size, arrangement, and the like of the components described in each drawing can be changed as appropriate within the scope of the present invention. The positional relationship (for example, up-and-down relationship) between the components in the specification is, as a rule, when the heat exchanger and the air conditioner are installed in a usable state.

Embodiment 1 FIG.
A heat exchanger and an air conditioner according to Embodiment 1 of the present invention will be described. FIG. 1 is a refrigerant circuit diagram illustrating a schematic configuration of an air conditioner 100 according to the present embodiment. In FIG. 1, the flow of the refrigerant during the heating operation is indicated by white arrows. FIG. 2 is a perspective view schematically showing the configuration of the heat source unit 10 of the air conditioner 100 according to the present embodiment. The air conditioner 100 according to the present embodiment includes a heat source side unit 10, a usage side unit 20 connected to the heat source side unit 10, and a usage side unit connected to the heat source side unit 10 in parallel with the usage side unit 20. 30 is a multi-type air conditioner. The heat source side unit 10 is installed outdoors, and the use side units 20 and 30 are installed in a room which is an air conditioning target. In the present embodiment, two use side units 20 and 30 are connected to the heat source side unit 10, but the number of use side units 20 and 30 is not limited.

  The heat source side unit 10 includes a compressor 11, a flow path switching device 12, heat source side heat exchangers 13 and 14, an accumulator 15, and a blower 16. The heat source side heat exchangers 13 and 14 are examples of the heat exchanger according to the present invention. The usage-side unit 20 includes a usage-side heat exchanger 20a, an expansion device 20b, and a blower (not shown). Similar to the use side unit 20, the use side unit 30 includes a use side heat exchanger 30 a, an expansion device 30 b, and a blower (not shown). The compressor 11, the flow path switching device 12, the heat source side heat exchangers 13 and 14, the accumulator 15, the use side heat exchangers 20a and 30a, and the expansion devices 20b and 30b are supplied with refrigerant according to the cooling operation and the heating operation, respectively. It connects with refrigerant | coolant piping so that it may circulate.

  The compressor 11 is a fluid machine that compresses the sucked low-temperature and low-pressure refrigerant into a high-temperature and high-pressure state. As the compressor 11, for example, a scroll compressor, a reciprocating compressor, a vane compressor, or the like is used.

  The flow path switching device 12 switches between a cooling flow path and a heating flow path according to switching of the operation mode between the cooling operation and the heating operation. The flow path switching device 12 is configured by, for example, a four-way valve. When the heating operation is performed, the flow path switching device 12 connects the discharge side of the compressor 11 and the use side heat exchangers 20a and 30a, and the suction side and the heat source side heat exchanger 13 of the compressor 11. , 14 are connected. In addition, when the cooling operation is performed, the flow path switching device 12 connects the discharge side of the compressor 11 and the heat source side heat exchangers 13 and 14, and exchanges heat between the suction side and the use side of the compressor 11. Connected to the devices 20a and 30a. Although the flow path switching device 12 of the present embodiment is configured by a four-way valve, the flow path switching device 12 may be configured by a combination of a plurality of two-way valves, for example.

  As shown in FIG. 2, the heat source side heat exchangers 13 and 14 are arranged at positions near the upper part in the housing 10 a of the heat source side unit 10. The heat source side heat exchangers 13 and 14 are arranged in an L shape in a top view along one side surface and the back surface of the housing 10a. Each of the heat source side heat exchangers 13 and 14 includes a plurality of flat tubes extending in parallel with each other and a plurality of corrugates provided between two adjacent flat tubes among the plurality of flat tubes. It has a fin, a header collecting pipe 1030 connected to each upper end of the plurality of flat tubes, and a liquid header 1010 connected to each lower end of the plurality of flat tubes. Each of the header collecting pipes 1030 is connected to the flow path switching device 12 via a refrigerant pipe. Each of the liquid headers 1010 is connected to the use side unit 20 and the use side unit 30 through refrigerant piping. The detailed configuration of the heat source side heat exchangers 13 and 14 will be described later.

  The blower 16 is provided in the upper part of the housing 10 a of the heat source side unit 10. The blower 16 is configured to suck outdoor air that has passed through the heat source side heat exchangers 13 and 14 and discharge it upward. Thereby, in each of the heat source side heat exchangers 13 and 14, heat exchange between the outdoor air supplied by the blower 16 and the refrigerant flowing through the plurality of flat tubes is performed. Hereinafter, the flow of outdoor air may be simply referred to as “airflow” or “wind”.

  The accumulator 15 is provided on the suction side of the compressor 11 in the refrigerant flow. The accumulator 15 stores the refrigerant that has flowed in through the flow path switching device 12 and separates the gas refrigerant and the liquid refrigerant. The gas refrigerant separated by the accumulator 15 is sucked by the compressor 11.

  The expansion device 20b is provided between the heat source side heat exchanger 13, the heat source side heat exchanger 14, and the use side heat exchanger 20a in the refrigerant flow. The expansion device 30b is provided between the heat source side heat exchanger 13, the heat source side heat exchanger 14, and the use side heat exchanger 30a in the refrigerant flow. As the expansion devices 20b and 30b, for example, linear electronic expansion valves capable of adjusting the refrigerant flow rate are used. The pressure and temperature of the refrigerant are adjusted by the expansion devices 20b and 30b, respectively. As the expansion devices 20b and 30b, on-off valves that switch the presence or absence of the refrigerant flow by a two-position operation can be used.

  Each of the usage-side heat exchangers 20a and 30a is configured to perform heat exchange between the refrigerant circulating in the interior and the indoor air supplied by a blower (not shown).

  The operation | movement at the time of the heating operation of the air conditioner comprised as mentioned above is demonstrated using FIG.1 and FIG.3. FIG. 3 is a PH diagram of the refrigeration cycle when the hydrofluorocarbon refrigerant R410a is used in the air conditioner 100 according to the present embodiment. The horizontal axis of FIG. 3 represents specific enthalpy [kJ / kg], and the vertical axis represents pressure [MPa]. In FIG. 3, a substantially trapezoidal solid line connecting points AA, AB, AC, and AD indicates the operating state of the refrigeration cycle. A thick curve that protrudes toward the high-pressure side is a saturation curve that connects points where the dryness X of the refrigerant is 0 or 1. The left side of the saturation curve is a region where the refrigerant is in a gas state, and the right side of the saturation curve is a region where the refrigerant is in a liquid state. The nine curves inside the saturation curve are equal dryness lines (X = 0.1, 0.2,..., 0.9) connecting points where the dryness X of the refrigerant is equal.

  First, the gas refrigerant separated by the accumulator 15 is sucked and compressed by the compressor 11 to become a high-temperature and high-pressure gas refrigerant (point AB in FIG. 3). The high-temperature and high-pressure gas refrigerant is discharged from the compressor 11 and flows into the use side heat exchangers 20a and 30a through the flow path switching device 12. During the heating operation, the use side heat exchangers 20a and 30a function as a condenser. The high-temperature and high-pressure gas refrigerant that has flowed into the use-side heat exchanger 20a is condensed by heat exchange with room air supplied by the blower of the use-side unit 20 and becomes a low-temperature and high-pressure liquid refrigerant (point AC in FIG. 3). . The room air is heated by heat dissipation from the refrigerant. This low-temperature and high-pressure liquid refrigerant flows out from the use-side heat exchanger 20a, is decompressed by the expansion device 20b, becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant, and flows out from the use-side unit 20 (point AD in FIG. 3). Similarly, the high-temperature and high-pressure gas refrigerant that has flowed into the use-side heat exchanger 30a is condensed by heat exchange with room air supplied by the blower of the use-side unit 30, and becomes a low-temperature and high-pressure liquid refrigerant. The low-temperature and high-pressure liquid refrigerant flows out from the use-side heat exchanger 30 a, is decompressed by the expansion device 30 b, becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant, and flows out from the use-side unit 30. In the example shown in FIG. 3, the dryness X of the refrigerant flowing out from the use side units 20 and 30 is about 0.23.

  The low-temperature and low-pressure gas-liquid two-phase refrigerant that has flowed out of the use side units 20 and 30 flows into the respective liquid headers 1010 of the heat source side heat exchangers 13 and 14. The low-temperature and low-pressure gas-liquid two-phase refrigerant that has flowed into the liquid header 1010 is distributed from the liquid header 1010 to a plurality of flat tubes. During the heating operation, the heat source side heat exchangers 13 and 14 function as an evaporator. The gas-liquid two-phase refrigerant that has flowed into the plurality of flat tubes evaporates by heat exchange with the outdoor air supplied by the blower 16, and becomes a low-pressure gas refrigerant (point AA in FIG. 3). This low-temperature and low-pressure gas refrigerant flows out of each of the heat source side heat exchangers 13 and 14 through the header collecting pipe 1030, and flows into the accumulator 15 through the flow path switching device 12. The refrigerant flowing into the accumulator 15 is separated into a liquid refrigerant and a gas refrigerant. The gas refrigerant separated by the accumulator 15 is sucked and compressed by the compressor 11 and becomes a high-temperature and high-pressure gas refrigerant (point AB in FIG. 3). During the heating operation, the above flow is continuously repeated. Thereby, the refrigerant circulates in the refrigerant circuit.

  Next, the detailed structure of the heat source side heat exchangers 13 and 14 will be described. Since the heat source side heat exchangers 13 and 14 have substantially the same configuration, the heat source side heat exchanger 13 will be described as an example here. FIG. 4 is an external perspective view showing the configuration of the heat source side heat exchanger 13 according to the present embodiment. FIG. 5 is a perspective view showing a configuration in which the vicinity of the portion V in FIG. 4 is viewed from the upstream side of the airflow.

  As shown in FIGS. 4 and 5, the heat source side heat exchanger 13 is a longitudinal flow type air-refrigerant heat exchanger that circulates a refrigerant as an internal fluid in the vertical direction, for example, the vertical vertical direction. The heat source side heat exchanger 13 is provided between each of a plurality of flat tubes 13a (an example of a heat transfer tube) extending in parallel in the vertical direction and two flat tubes 13a adjacent to each other among the plurality of flat tubes 13a. A plurality of corrugated fins 13b, a header collecting pipe 1030 connected to the respective upper ends of the plurality of flat tubes 13a, and a liquid header 1010 (an example of a header) connected to the respective lower ends of the plurality of flat tubes 13a. Have. The core portion 1040 in which heat exchange between the refrigerant and air is performed has a configuration in which a plurality of flat tubes 13a and a plurality of corrugated fins 13b are alternately stacked. The header collecting pipe 1030 and the liquid header 1010 are arranged so that their longitudinal directions are horizontal.

  The airflow generated by driving the blower 16 flows into the core portion 1040 of the heat source side heat exchanger 13 along the direction indicated by the arrow F1 in FIG. The airflow after passing through the core portion 1040 changes its direction in the upward direction indicated by the arrow F2 in FIG. 4 and flows out from the housing 10a.

  The plurality of flat tubes 13a are arranged in parallel in the left-right direction so as to be orthogonal to the airflow direction indicated by the arrow F1. Each of the flat tubes 13a is arranged so that the airflow direction and the flat surface 13e are parallel to each other. The interval between the flat surfaces 13e facing each other in the two adjacent flat tubes 13a is, for example, 10 mm. As the flat tube 13a, a multi-hole tube in which a plurality of refrigerant passages 13f are formed in parallel is used.

  The corrugated fin 13b has, for example, a shape in which a thin plate having a thickness of less than 1 mm is bent into a wave shape. The corrugated fin 13b has a main body portion 13g sandwiched between two flat tubes 13a and an end portion 13k protruding to the upstream side of the air flow from between the two flat tubes 13a in the air flow direction. . The bending top part of the main body part 13g of the corrugated fin 13b is joined to one of the flat surfaces 13e of the two flat tubes 13a.

  On each slope of the main body portion 13g of the corrugated fin 13b, there are a drain hole 13h for draining condensed water, a first louver 13i provided on the upstream side of the air stream from the drain hole 13h, and a downstream side of the air stream from the drain hole 13h. And a second louver 13j provided on the side.

  The flat tube 13a and the corrugated fin 13b are formed using aluminum having high thermal conductivity. The flat tube 13a and the corrugated fin 13b are joined using a metal joining method such as a Nocolok brazing method. In addition, the flat tube 13a and the corrugated fin 13b do not necessarily need to be formed with the same material.

  Next, the configuration of the liquid header 1010 and the header collecting pipe 1030 in the heat source side heat exchanger 13 will be described. FIG. 6 is a cross-sectional view schematically showing the configuration of the heat source side heat exchanger 13 according to the present embodiment. 7 is a cross-sectional view showing a VII-VII cross section of FIG. FIG. 8 is a cross-sectional view showing a VIII-VIII cross section of FIG. 6. As shown in FIGS. 6 to 8, the liquid header 1010 has a rectangular tube shape that is long in one direction and has a quadrangular cross section. The liquid header 1010 has at least a first inner wall surface 1011 positioned above the internal space of the liquid header 1010 and a second inner wall surface 1012 positioned below the internal space. A plurality of insertion holes 1014 are formed in the first inner wall surface 1011. Lower end portions 13a1 of the plurality of flat tubes 13a are inserted into the plurality of insertion holes 1014, respectively. The extending direction of the flat tube 13 a is orthogonal to the longitudinal direction of the liquid header 1010. The second inner wall surface 1012 faces the first inner wall surface 1011 with the inner space of the liquid header 1010 interposed therebetween.

  A straight tubular first inflow pipe 1001 is connected to one end in the longitudinal direction of the liquid header 1010 (the right end in FIGS. 6 and 7). A straight tubular second inflow pipe 1002 is connected to the other longitudinal end of the liquid header 1010 (the left end in FIGS. 6 and 7). During the heating operation in which the heat source side heat exchanger 13 functions as an evaporator, the gas-liquid two-phase refrigerant flows into the liquid header 1010 through the first inflow pipe 1001 and the second inflow pipe 1002. The gas-liquid two-phase refrigerant that has flowed into the liquid header 1010 is distributed to the plurality of flat tubes 13a. That is, the liquid header 1010 functions as a horizontal header distributor that distributes the fluid to the plurality of flat tubes 13a.

  The first inflow pipe 1001 is provided such that the tube axis 1001a (see FIG. 7) of the first inflow pipe 1001 is parallel to the longitudinal direction of the liquid header 1010. A part of the first inflow pipe 1001 is inserted into the liquid header 1010. The second inflow pipe 1002 is provided so that the tube axis 1002 a of the second inflow pipe 1002 is parallel to the longitudinal direction of the liquid header 1010. A part of the second inflow pipe 1002 is inserted into the liquid header 1010. The direction in which the refrigerant flows into the liquid header 1010 from the first inflow pipe 1001 and the direction in which the refrigerant flows into the liquid header 1010 from the second inflow pipe 1002 are opposite to each other.

  A flat partition wall 1013 extending along the longitudinal direction of the liquid header 1010 is formed inside the liquid header 1010. The interior of the liquid header 1010 is incompletely partitioned into a first channel 1021 and a second channel 1022 by a partition wall 1013. The first flow path 1021 is located on the windward side of the second flow path 1022. One surface 1013 b of the partition wall 1013 faces the first flow path 1021. The other surface 1013 c of the partition wall 1013 faces the second flow path 1022.

  The partition wall 1013 is formed to protrude from the second inner wall surface 1012 of the liquid header 1010 toward the first inner wall surface 1011. The leading end 1013a in the protruding direction of the partition wall 1013 is opposed to the lower end 13a1 of each of the plurality of flat tubes 13a via a gap. The distal end portion 1013a of the partition wall 1013 is opposed to the central portion in the longitudinal direction of the lower end portion 13a1 (that is, the flat direction of the flat tube 13a) among the lower end portions 13a1 of the plurality of flat tubes 13a. Here, the flat direction of the flat tube 13a is a direction perpendicular to the extending direction of the flat tube 13a and parallel to the flat surface 13e.

  When the heat source side heat exchanger 13 is placed upright so that the extending direction of the flat tube 13a is vertically up and down, the height position H1 of the lower end portion 13a1 of the flat tube 13a is the tip portion 1013a of the partition wall 1013. Is the same as or higher than the height position H2. Further, the height position H2 of the tip 1013a of the partition wall 1013 is the height position H3 above the first inflow pipe 1001 and the second inflow pipe 1002 (for example, the inside of the first inflow pipe 1001 and the second inflow pipe 1002). It is higher than the uppermost position of the flow path.

  The first inlet pipe 1001 and the second inlet pipe 1002 are provided so as to be shifted from each other in the wind flow direction. The first inflow pipe 1001 is connected to the upstream side of the partition wall 1013 in the liquid header 1010, that is, to the first flow path 1021. When viewed along the extending direction of the flat tube 13a, the tube axis 1001a of the first inflow tube 1001 extends on the first flow path 1021 along the longitudinal direction of the liquid header 1010 (see FIG. 7). Thereby, the gas-liquid two-phase refrigerant that has flowed into the liquid header 1010 via the first inflow pipe 1001 flows through the first flow path 1021 along the windward surface 1013b of the partition wall 1013.

  The second inflow pipe 1002 is connected to the leeward side of the liquid header 1010 from the partition wall 1013, that is, to the second flow path 1022. A tube axis 1002 a of the second inflow tube 1002 extends on the second flow path 1022 along the longitudinal direction of the liquid header 1010. Thereby, the gas-liquid two-phase refrigerant that has flowed into the liquid header 1010 via the second inflow pipe 1002 is opposite to the refrigerant flow direction in the first flow path 1021 along the leeward side surface 1013c of the partition wall 1013. The second channel 1022 is circulated in the direction.

  The header collecting pipe 1030 has a rectangular tube shape that is long in one direction and has a quadrangular cross section. Unlike the liquid header 1010, no partition wall is formed inside the header collecting pipe 1030. Upper end portions 13a2 of a plurality of flat tubes 13a are inserted into the header collecting tube 1030, respectively. An outflow pipe 1003 is connected to one end in the longitudinal direction of the header collecting pipe 1030 (the right end in FIG. 6). From the header collecting pipe 1030 during the heating operation, the gas refrigerant evaporated by heat exchange with the air in the flat pipe 13 a flows out through the outflow pipe 1003.

  Next, the state of the refrigerant flowing into the liquid header 1010 during the heating operation will be described. FIG. 9 is a diagram illustrating a state of the refrigerant that has flowed into the liquid header 1010 of the heat source side heat exchanger 13 according to the present embodiment. In FIG. 9, the example of the liquid level of the liquid phase refrigerant | coolant of the gas-liquid two-phase refrigerant | coolant which flowed into the 2nd flow path 1022 from the 2nd inflow pipe 1002 is shown as the continuous line, and the 1st flow from the 1st inflow pipe 1001 is shown. An example of the liquid level of the liquid-phase refrigerant of the gas-liquid two-phase refrigerant that has flowed into the path 1021 is indicated by a broken line.

  As shown in FIG. 9, during the heating operation, the gas-liquid two-phase refrigerant flows into the liquid header 1010 through the first inflow pipe 1001 and the second inflow pipe 1002. The gas-liquid two-phase refrigerant that has flowed into the liquid header 1010 is divided into each of the plurality of flat tubes 13a, and is evaporated by heat exchange with air. The evaporated gas refrigerant flows into the header collecting pipe 1030 from each of the plurality of flat tubes 13a and flows out through the outflow pipe 1003.

  Generally, the inflow pipe is connected to only one longitudinal end portion of the liquid header. For this reason, when the mass velocity of the gas-liquid two-phase refrigerant flowing into the liquid header via the inflow pipe is large, the liquid-phase refrigerant having a density higher than that of the gas refrigerant is biased toward the end side of the liquid header due to inertial force. On the other hand, when the mass velocity of the gas-liquid two-phase refrigerant flowing into the liquid header via the inflow pipe is small, the liquid-phase refrigerant drifts toward the inlet side of the liquid header. Therefore, the flow rate of the liquid phase refrigerant distributed to the flat tube located on the inlet side of the liquid header and the flow rate of the liquid phase refrigerant distributed to the flat tube located on the terminal side of the liquid header are likely to be uneven. . Thereby, it was easy to produce the fall of the heat exchange efficiency in a heat exchanger.

  FIG. 10 is a graph conceptually showing the relationship between the position of the flat tube 13a and the flow rate of the liquid-phase refrigerant distributed to the flat tube 13a in the heat source side heat exchanger 13 according to the present embodiment. The horizontal axis of the graph represents the connection position of the flat tube 13 a in the longitudinal direction of the liquid header 1010. In this horizontal axis, the left end represents the position of the second inflow pipe 1002 (in FIG. 9, the left end in the longitudinal direction of the liquid header 1010), and the right end represents the position of the first inflow pipe 1001 (in FIG. 9, the liquid header 1010). The right end portion in the longitudinal direction). The vertical axis of the graph represents the flow rate of liquid phase refrigerant (liquid distribution flow rate) distributed to the flat tube 13a. A line FR1 represents the distribution of the flow rate of the liquid-phase refrigerant that flows into the liquid header 1010 from the first inflow pipe 1001 and is distributed to the flat tubes 13a. A line FR2 represents the flow rate distribution of the liquid-phase refrigerant that flows into the liquid header 1010 from the second inflow pipe 1002 and is distributed to the flat tubes 13a. A line FRtotal represents the distribution of the total flow rate of the liquid-phase refrigerant distributed to each flat tube 13a. Note that the mass velocity of the gas-liquid two-phase refrigerant flowing into the liquid header 1010 from the first inflow pipe 1001 and the second inflow pipe 1002 is relatively high.

  As indicated by a line FR1 in FIG. 10, the flow rate of the liquid-phase refrigerant that flows into the liquid header 1010 from the first inflow pipe 1001 and is distributed to each flat tube 13a is away from the first inflow pipe 1001 and the first flow path 1021. The more you approach the end of On the other hand, as indicated by the line FR2, the flow rate of the liquid-phase refrigerant that flows into the liquid header 1010 from the second inflow pipe 1002 and is distributed to the respective flat tubes 13a is kept away from the second inflow pipe 1002 and The closer you are to the end, the more. The distribution of the flow rate of the liquid phase refrigerant indicated by the line FR1 and the distribution of the flow rate of the liquid phase refrigerant indicated by the line FR2 are substantially symmetric in the longitudinal direction of the liquid header 1010. For this reason, the total flow rate of the liquid-phase refrigerant distributed to each of the plurality of flat tubes 13a is substantially equal regardless of the position of each flat tube 13a in the longitudinal direction of the liquid header 1010, as indicated by a line FRtotal.

  As described above, in the present embodiment, the partition wall 1013 provided in the liquid header 1010 flows from the first flow path 1021 through which the refrigerant flowing in from the first inflow pipe 1001 flows and from the second inflow pipe 1002. The second flow path 1022 through which the circulated refrigerant flows is partitioned. As a result, the gas-liquid two-phase refrigerant can be circulated in the liquid header 1010 so as to face each other from one end side in the longitudinal direction and the other end side in the longitudinal direction. Therefore, the refrigerant can be more evenly distributed to the plurality of flat tubes 13a without depending on the operating conditions of the refrigerant circuit, that is, the flow rate of the refrigerant flowing into the liquid header 1010. Therefore, since the heat exchange efficiency of the heat source side heat exchanger 13 can be improved and the pressure loss of the refrigerant in the heat source side heat exchanger 13 can be reduced, the performance of the entire air conditioner 100 can be improved.

  As described above, the heat source side heat exchanger 13 according to the present embodiment is a liquid in which a plurality of flat tubes 13a arranged in parallel with each other and lower ends 13a1 of the plurality of flat tubes 13a are inserted. In the longitudinal direction of the header 1010, the first inflow pipe 1001 connected to one longitudinal end of the liquid header 1010, the second inflow pipe 1002 connected to the other longitudinal end of the liquid header 1010, and the liquid header 1010 A partition wall 1013 that extends along the liquid header 1010 and partitions the inside of the liquid header 1010 into a first flow path 1021 and a second flow path 1022 is provided. The liquid header 1010 includes a first inner wall surface 1011 formed with a plurality of insertion holes 1014 into which the respective lower end portions 13a1 of the plurality of flat tubes 13a are inserted, and a second inner wall surface 1012 facing the first inner wall surface 1011. ,have. The partition wall 1013 is formed to protrude from the second inner wall surface 1012 toward the first inner wall surface 1011. The leading end portion 1013a in the protruding direction of the partition wall 1013 faces the lower end portions 13a1 of the plurality of flat tubes 13a. The first inflow pipe 1001 is connected to the first flow path 1021. The second inflow pipe 1002 is connected to the second flow path 1022. Here, the heat source side heat exchanger 13 is an example of a heat exchanger. The flat tube 13a is an example of a heat transfer tube. The lower end portion 13a1 is an example of an end portion of the heat transfer tube. The liquid header 1010 is an example of a header.

  The fluid that has flowed into the liquid header 1010 from the first inflow pipe 1001 is distributed to the plurality of flat tubes 13a while flowing in the first flow path 1021 in one direction. The fluid that has flowed into the liquid header 1010 from the second inflow pipe 1002 is distributed to the plurality of flat tubes 13a while flowing in the second flow path 1022 in a direction opposite to the one direction. Therefore, according to this configuration, even if fluid drift due to inertia occurs in the longitudinal direction of each of the first channel 1021 and the second channel 1022, the fluid is more evenly distributed to the plurality of flat tubes 13a. be able to. Therefore, the heat exchange efficiency of the heat source side heat exchanger 13 can be improved.

  In the heat source side heat exchanger 13 according to the present embodiment, each of the plurality of heat transfer tubes is a flat tube 13a. The front end portion 1013a of the partition wall 1013 is opposed to the central portion in the longitudinal direction at the lower end portion 13a1 of the flat tube 13a. According to this configuration, the fluid can be distributed from each of the first flow path 1021 and the second flow path 1022 to each of the plurality of flat tubes 13a.

  Further, in the heat source side heat exchanger 13 according to the present embodiment, when the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 are viewed along the extending direction of the plurality of flat tubes 13a, the first inflow A tube axis 1001 a of the tube 1001 extends on the first flow path 1021 along the longitudinal direction of the liquid header 1010. A tube axis 1002 a of the second inflow tube 1002 extends on the second flow path 1022 along the longitudinal direction of the liquid header 1010. According to this configuration, the flow distribution of the fluid flowing through each of the first flow path 1021 and the second flow path 1022 can be made generally symmetric in the longitudinal direction of the liquid header 1010. Therefore, the fluid can be more evenly distributed to the plurality of flat tubes 13a.

  The air conditioner 100 according to the present embodiment includes the heat source side heat exchanger 13 described above. According to this structure, since the heat exchange efficiency of the heat source side heat exchanger 13 can be improved, the performance of the air conditioner 100 can be improved.

Embodiment 2. FIG.
A heat exchanger according to Embodiment 2 of the present invention will be described. FIG. 11 schematically shows a configuration of the heat source side heat exchanger 13 according to the present embodiment and a branch structure 1050 connected to the first inflow pipe 1001 and the second inflow pipe 1002 of the heat source side heat exchanger 13. FIG.

  As shown in FIG. 11, a branching structure 1050 that divides the refrigerant is provided on the upstream side of the heat source side heat exchanger 13 in the refrigerant flow during the heating operation. The branch structure 1050 includes a refrigerant pipe 1053, and a refrigerant pipe 1051 and a refrigerant pipe 1052 that are branched from the refrigerant pipe 1053 at a branch portion 1054 and connected to the first inflow pipe 1001 and the second inflow pipe 1002, respectively. Yes. During the heating operation in which the heat source side heat exchanger 13 functions as an evaporator, the gas-liquid two-phase refrigerant decompressed by the expansion devices 20b and 30b flows into the refrigerant pipe 1053. The gas-liquid two-phase refrigerant that has flowed into the refrigerant pipe 1053 is divided into the refrigerant pipe 1051 and the refrigerant pipe 1052 at the branching portion 1054. The gas-liquid two-phase refrigerant branched into the refrigerant pipe 1051 flows into the first flow path 1021 of the liquid header 1010 from the first inflow pipe 1001. The gas-liquid two-phase refrigerant divided into the refrigerant pipe 1052 flows into the second flow path 1022 of the liquid header 1010 from the second inflow pipe 1002. The branch structure 1050 is provided so as to have a generally symmetrical structure in the horizontal direction so that the mass flow rate and the dryness of the gas-liquid two-phase refrigerant that is divided into the refrigerant pipes 1051 and 1052 are approximately the same.

  According to the present embodiment, the mass flow rate and the dryness of the gas-liquid two-phase refrigerant flowing from the first inflow pipe 1001 into the first flow path 1021 and the air flowing from the second inflow pipe 1002 into the second flow path 1022. The mass flow rate and the dryness of the liquid two-phase refrigerant can be made approximately the same. Therefore, the gas-liquid two-phase refrigerant can be more evenly distributed to the plurality of flat tubes 13a.

Embodiment 3 FIG.
A heat exchanger according to Embodiment 3 of the present invention will be described. FIG. 12 is a cross-sectional view schematically showing a configuration in the vicinity of the liquid header 1010 of the heat source side heat exchanger 13 according to the present embodiment. 13 is a cross-sectional view showing a cross-section XIII-XIII in FIG.

  As shown in FIGS. 12 and 13, a plurality of holes 1060 are formed in the partition wall 1013 of the present embodiment. Each of the plurality of holes 1060 penetrates between the surface 1013b on the first flow path 1021 side of the partition wall 1013 and the surface 1013c on the second flow path 1022 side of the partition wall 1013 in the thickness direction of the partition wall 1013. ing. Thereby, a part of the refrigerant flowing through one of the first flow path 1021 or the second flow path 1022 can flow into the other of the first flow path 1021 or the second flow path 1022 through the hole 1060. It has become. The plurality of holes 1060 are provided in parallel with each other in the longitudinal direction of the liquid header 1010. The shape of the hole 1060 is not limited to a circle, but may be other shapes such as a slit shape.

  According to the present embodiment, even if the flow rate of the refrigerant flowing from the first inflow pipe 1001 and the flow rate of the refrigerant flowing from the second inflow pipe 1002 are different, the first flow path 1021 and the second flow path 1022 The liquid level height of the liquid phase refrigerant in each of the above can be made more uniform.

  As described above, in the heat source side heat exchanger 13 according to the present embodiment, the partition wall 1013 includes the surface 1013b on the first flow path 1021 side of the partition wall 1013 and the second flow of the partition wall 1013. A hole 1060 is formed so as to penetrate between the surface 1013c on the path 1022 side. According to this configuration, fluid can be circulated from one of the first flow path 1021 and the second flow path 1022 to the other through the hole 1060. Thereby, even if the flow rate of the fluid flowing in from the first inflow pipe 1001 and the flow rate of the fluid flowing in from the second inflow pipe 1002 are different, the fluid in each of the first flow path 1021 and the second flow path 1022 Can be made more uniform. Therefore, the fluid can be more evenly distributed to the plurality of flat tubes 13a.

Embodiment 4 FIG.
A heat exchanger according to Embodiment 4 of the present invention will be described. FIG. 14 is a cross-sectional view schematically showing a configuration in the vicinity of the liquid header 1010 of the heat source side heat exchanger 13 according to the present embodiment. FIG. 15 is a cross-sectional view showing the XV-XV cross section of FIG.

  As shown in FIGS. 14 and 15, the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 all have a circular tubular shape. The tube axes of the first inflow tube 1001 and the second inflow tube 1002 are parallel to the tube axis of the liquid header 1010. When the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 are viewed along the longitudinal direction of the liquid header 1010 (that is, the pipe axis of the liquid header 1010), the first inflow pipe 1001 and the second inflow pipe 1002 are viewed. Is located on the inner peripheral side of the pipe wall of the liquid header 1010 (see FIG. 15). The front end portion 1013a of the partition wall 1013 is opposed to the central portion in the longitudinal direction of the lower end portion 13a1 of each of the plurality of flat tubes 13a via a gap.

  In this embodiment, the hole 1060 is formed in the partition wall 1013, but the hole 1060 may not be formed. Moreover, the liquid header 1010 and the partition wall 1013 may be integrally formed by extrusion molding. In this case, the liquid header 1010 and the partition wall 1013 are formed of a material such as aluminum, for example. By integrally forming the liquid header 1010 and the partition wall 1013 by extrusion, the manufacturing cost of the heat source side heat exchanger 13 can be reduced.

  In the present embodiment, all of the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 have a tubular shape. Thereby, since the liquid header 1010, the 1st inflow pipe 1001, and the 2nd inflow pipe 1002 can all be formed by extrusion molding, the manufacturing cost of the heat source side heat exchanger 13 can be reduced. Further, since the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 all have a tubular shape, the respective pressure resistances of the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 are shown. Performance can be improved. Furthermore, since the liquid header 1010 has a tubular shape, the distance between the second inner wall surface 1012 that is the bottom surface of the liquid header 1010 and the lower end portion 13a1 of the flat tube 13a that is the outflow destination of the refrigerant is increased. can do. Thereby, the liquid level of the refrigerant can be formed below the liquid header 1010 (for example, below the lower end portion 13a1). Accordingly, since the droplets are likely to be scattered by the shearing force acting on the interface between the gas refrigerant and the liquid refrigerant, the refrigerant is easily stirred.

  As described above, in the heat source side heat exchanger 13 according to the present embodiment, the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 all have a circular tubular shape. When the liquid header 1010, the first inflow pipe 1001 and the second inflow pipe 1002 are viewed along the longitudinal direction of the liquid header 1010, the first inflow pipe 1001 and the second inflow pipe 1002 are more than the tube wall of the liquid header 1010. Located on the inner circumference. According to this configuration, the liquid level of the refrigerant is formed below the liquid header 1010, and the refrigerant is uniformly stirred by the gas. For this reason, compared with Embodiment 1-3, the refrigerant | coolant in the liquid header 1010 can be flowed more uniformly. Therefore, the fluid can be more evenly distributed to the plurality of flat tubes 13a.

Embodiment 5. FIG.
A heat exchanger and an air conditioner according to Embodiment 5 of the present invention will be described. FIG. 16 is a cross-sectional view schematically showing a configuration in the vicinity of the liquid header 1010 of the heat source side heat exchanger 13 according to the present embodiment. 17 is a cross-sectional view showing a cross section XVII-XVII in FIG. 18 is a cross-sectional view showing a cross section XVIII-XVIII in FIG. 16.

  As shown in FIGS. 16 to 18, the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 all have a circular tubular shape. The diameter of the first inflow pipe 1001 is larger than the diameter of the second inflow pipe 1002. That is, if the flow path cross-sectional area of the first inflow pipe 1001 is A1, and the flow path cross-sectional area of the second inflow pipe 1002 is A2, the flow path cross-sectional area A1 is larger than the flow path cross-sectional area A2 (A1 > A2). Here, in the flow of air supplied to the heat source side heat exchanger 13 by the blower 16 (not shown in FIGS. 16 to 18), the first inflow pipe 1001 and the first flow path 1021 are the second inflow pipe 1002. In addition, the second flow path 1022 is disposed on the windward side. A part of the first inflow pipe 1001 and a part of the second inflow pipe 1002 are inserted into the liquid header 1010. The tube axes of the first inflow tube 1001 and the second inflow tube 1002 are parallel to the tube axis of the liquid header 1010. When the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 are viewed along the longitudinal direction of the liquid header 1010 (that is, the pipe axis of the liquid header 1010), the first inflow pipe 1001 and the second inflow pipe 1002 are viewed. Is located on the inner peripheral side of the pipe wall of the liquid header 1010 (see FIG. 18).

  In this embodiment, the hole 1060 is formed in the partition wall 1013, but the hole 1060 may not be formed. Moreover, the liquid header 1010 and the partition wall 1013 may be integrally formed by extrusion molding. In this case, the liquid header 1010 and the partition wall 1013 are formed of a material such as aluminum, for example. By integrally forming the liquid header 1010 and the partition wall 1013 by extrusion, the manufacturing cost of the heat source side heat exchanger 13 can be reduced.

  In the heat source side heat exchanger 13 of the present embodiment, the flow path cross-sectional area of the first inflow pipe 1001 is larger than the flow path cross-sectional area of the second inflow pipe 1002, so More refrigerant flows than the path 1022. Thereby, more refrigerant | coolant can be poured into the refrigerant path 13f located in the front edge side of the flat tube 13a with respect to the flow of air than the refrigerant path 13f located in the rear edge side of the flat tube 13a. Since the heat load on the front edge side of the flat tube 13a is larger than that on the rear edge side, the heat exchange efficiency of the heat source side heat exchanger 13 is improved by flowing a large amount of refrigerant through the refrigerant passage 13f located on the front edge side of the flat tube 13a. Can be made.

  In the present embodiment, the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 all have a circular tubular shape. Thereby, since the liquid header 1010, the 1st inflow pipe 1001, and the 2nd inflow pipe 1002 can all be formed by extrusion molding, the manufacturing cost of the heat source side heat exchanger 13 can be reduced. Further, since the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 all have a tubular shape, the respective pressure resistances of the liquid header 1010, the first inflow pipe 1001, and the second inflow pipe 1002 are shown. Performance can be improved.

  As described above, the air conditioner 100 according to the present embodiment includes the blower 16 that supplies air to the heat source side heat exchanger 13. The first flow path 1021 is disposed on the windward side of the second flow path 1022. The flow passage cross sectional area A1 of the first inflow pipe 1001 is larger than the flow passage cross sectional area A2 of the second inflow pipe 1002. According to this structure, more refrigerant | coolants can be poured into the front edge side of the flat tube 13a with relatively large heat load than the rear edge side of the flat tube 13a. Therefore, since the heat exchange efficiency of the heat source side heat exchanger 13 can be improved, the performance of the entire air conditioner 100 can be improved.

The present invention is not limited to the above embodiment, and various modifications can be made.
For example, in the above-described embodiment, the flat tube 13a having a flat cross-sectional shape is exemplified as the heat transfer tube, but the cross-sectional shape and the insertion shape of the heat transfer tube are not limited to the flat shape. Moreover, in the said embodiment, although the multi-hole tube in which the some refrigerant path 13f was formed was mentioned as an example as a heat exchanger tube, heat exchanger tubes other than a multi-hole tube can also be used.

  The above embodiments can be implemented in combination with each other.

  DESCRIPTION OF SYMBOLS 10 Heat source side unit, 10a Case, 11 Compressor, 12 Flow path switching device, 13, 14 Heat source side heat exchanger, 13a Flat tube, 13a1 Lower end, 13a2 Upper end, 13b Corrugated fin, 13e Flat surface, 13f Refrigerant Passage, 13g body part, 13h drain hole, 13i first louver, 13j second louver, 13k end, 15 accumulator, 16 blower, 20 utilization side unit, 20a utilization side heat exchanger, 20b expansion device, 30 utilization side unit , 30a Use side heat exchanger, 30b Expansion device, 100 Air conditioner, 1001 First inflow pipe, 1001a Pipe shaft, 1002 Second inflow pipe, 1002a Pipe shaft, 1003 Outflow pipe, 1010 Liquid header, 1011 First inner wall surface 1012 2nd inner wall surface, 1013 Partition wall, 1013a Tip part, 101 3b, 1013c surface, 1014 insertion hole, 1021 first flow path, 1022 second flow path, 1030 header collecting pipe, 1040 core section, 1050 branch structure, 1051, 1052, 1053 refrigerant pipe, 1054 branch section, 1060 hole.

Claims (7)

A plurality of heat transfer tubes arranged in parallel with each other;
A header into which each end of the plurality of heat transfer tubes is inserted;
A first inflow pipe connected to one longitudinal end of the header;
A second inflow pipe connected to the other longitudinal end of the header;
A partition wall extending along the longitudinal direction of the header and partitioning the inside of the header into a first flow path and a second flow path,
The header includes a first inner wall surface formed with a plurality of insertion holes into which respective end portions of the plurality of heat transfer tubes are inserted, and a second inner wall surface facing the first inner wall surface. And
The partition wall is formed to protrude from the second inner wall surface toward the first inner wall surface,
The leading end portion in the protruding direction of the partition wall is opposed to each end portion of the plurality of heat transfer tubes,
The first inflow pipe is connected to the first flow path;
The second inflow pipe is a heat exchanger connected to the second flow path. Each of the plurality of heat transfer tubes is a flat tube,
The heat exchanger according to claim 1, wherein the distal end portion of the partition wall is opposed to a longitudinal central portion at an end portion of the flat tube. When viewing the header, the first inflow pipe and the second inflow pipe along the extending direction of the plurality of heat transfer tubes,
The tube axis of the first inflow pipe extends on the first flow path along the longitudinal direction of the header,
The heat exchanger according to claim 1 or 2, wherein a tube axis of the second inflow tube extends on the second flow path along a longitudinal direction of the header.   The hole which penetrated between the surface by the side of the said 1st flow path of the said partition wall and the surface by the side of the said 2nd flow path of the said partition wall is formed in the said partition wall. The heat exchanger as described in any one of. The header, the first inflow pipe, and the second inflow pipe all have a tubular shape,
When the header, the first inflow pipe and the second inflow pipe are viewed along the longitudinal direction of the header, the first inflow pipe and the second inflow pipe are on the inner peripheral side with respect to the pipe wall of the header. The heat exchanger as described in any one of Claims 1-4 located in.   An air conditioner provided with the heat exchanger as described in any one of Claims 1-5. A blower for supplying air to the heat exchanger;
The first flow path is disposed on the windward side of the second flow path,
The air conditioner according to claim 6, wherein a flow path cross-sectional area of the first inflow pipe is larger than a flow path cross-sectional area of the second inflow pipe.

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