JP4055449B2 - Heat exchanger and air conditioner using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve problems wherein a heat exchange quantity of the whole heat exchanger reduces since a leeward side heat transfer pipe inside passage reduces in heat exchange efficiency though a windward side heat transfer pipe inside passage efficiently exchanges heat, and a flat heat transfer pipe is worse in drainability of dewing water than a circular pipe-shaped heat transfer pipe in a heat exchanger using the flat heat transfer pipe. <P>SOLUTION: This heat exchanger has the heat transfer pipe arranging a plurality of passages inside a flat cross section bent in a U shape, a header for communicating with an end part of the heat transfer pipe, a vertical partition plate, and a horizontal partition plate for forming a refrigerant flow to an outflow pipe from an inflow pipe by separating a space in the header, and constitutes the refrigerant flow of an opposed flow or a parallel flow to a gas flow. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a heat exchanger in which a header is separated into two or more in the direction of the flow of heat exchange air and a plurality of header chambers are formed therein.
[0002]
[Prior art]
Conventionally, what is shown in FIG. 26 is known as a heat exchanger which comprises an air conditioner. This heat exchanger 100 is called a plate fin and tube type, and is a pair of headers 103 and 104 that extend vertically and are opposed to each other. A flat heat transfer tube 102 is provided, and each heat transfer tube is inserted into the plate fin 1 for heat exchange. A refrigerant flows in the flat heat transfer tube 102, and heat is exchanged with air flowing outside the heat exchanger. A refrigerant inflow pipe 110 is provided above the one header 103, and an outflow pipe 111 is provided below the header 104.
[0003]
In addition, as shown in FIG. 27, the flat heat transfer tube 102 has a partition wall that divides the inside thereof in the width direction, and a plurality of refrigerant flow paths 6a and 6b that oppose in the flow direction of the heat exchange air 5 by the partition wall. Is forming.
According to this heat exchanger 100, FIG. 28 is a view of the heat exchanger 100 of FIG. 26 cut along a horizontal cross section of a flat heat transfer tube, and the refrigerant flows into one header 103 via the inflow tube 110. The refrigerant flows into the other header 104 through the flat heat transfer tube 102. Then, it flows out through the outflow pipe 111 provided in the header 104.
[0004]
[Problems to be solved by the invention]
In the conventional heat exchanger 100 as described above, heat exchange air flows in the width direction of the flat heat transfer tube 102 as described above, and heat exchange is performed between the heat exchange air and the cooling medium. When the evaporator acts as an evaporator, the refrigerant flowing through the refrigerant flow path 6a in the heat transfer tube on the windward side of the flat heat transfer tube 102 is cooled by heat exchange air (low temperature air) that has not been sufficiently exchanged heat. The heat is exchanged efficiently and the refrigerant temperature is low. On the other hand, since the refrigerant flowing through the leeward heat transfer pipe refrigerant flow path 6b is already heat-exchanged and heat-exchanged with high-temperature heat exchange air, the heat exchange efficiency is lowered and the refrigerant is sufficiently used. Can not be cooled to.
[0005]
As described above, the conventional heat exchanger 100 has a problem that a large difference occurs in the heat exchange amount between the windward side and the leeward side of the flat heat transfer tube 102, and the overall heat exchange amount becomes small. .
Further, since the shape of the flat heat transfer tube 102 used in such a heat exchanger 100 is a flat shape, when the heat exchanger 100 is installed so that the long axis direction of the flat tube and the air flow main flow direction coincide with each other, The ventilation resistance of the air flow is greatly reduced, and the driving power of the blower that generates the air flow can be greatly reduced.
[0006]
However, when such a heat exchanger 100 is used as an evaporator, dew condensation water is generated. However, since the shape of the flat heat transfer tube 102 is flat, drainage of the dew condensation water compared to the circular heat transfer tube. However, the condensed water is held, and there is a problem that the effect of reducing the ventilation resistance cannot be obtained sufficiently.
[0007]
An object of the present invention is to provide a heat exchanger that improves the heat exchange efficiency in view of the conventional problems.
[0008]
[Means for Solving the Problems]
The heat exchanger according to claim 1 of the present invention is arranged in parallel, a plurality of plate-like fins in which gas flows between them, and arranged through the plate-like fins, and operates inside a flat cross section. A heat transfer pipe bent into a U-shape provided with a plurality of flow channels through which fluid flows, a header in which the end of the heat transfer pipe communicates, and an inflow pipe and an outflow pipe for the working fluid are connected, and in the header A first vertical partition plate in the header longitudinal direction that separates a space communicating from the inflow pipe to the heat transfer pipe and a space communicating from the heat transfer pipe to the outflow pipe; and the adjacent U-shaped heat transfer pipe Over Provided in the header space in the direction of air flow Opposite The second longitudinal partition plate in the header longitudinal direction to be separated, and both ends of the U-shaped heat transfer tube In the header space A separating partition, The header inner space is separated into a windward flow channel and a leeward flow channel with respect to the gas flow direction by the first and second vertical partition plates, and the working fluid flow in the header longitudinal direction is partitioned by the horizontal partition plates. When the working refrigerant that has flowed in from the inflow pipe is used as an evaporator, it flows through the windward flow path of the heat transfer pipe having the flat cross section and reaches the end space of the header to reach the leeward side of the heat transfer pipe. It flows through the flow path and flows out from the outflow pipe, and becomes a parallel flow with respect to the air flow direction.When used as a condenser, it flows through the leeward flow path of the heat transfer pipe having the flat cross section and flows through the header. When it reaches the end space, it flows through the windward flow path of the heat transfer tube and flows out of the outflow tube, and becomes a counterflow with respect to the air flow direction. Is.
[0009]
Further, the heat exchanger according to claim 2 of the present invention is configured such that, in a plurality of flow paths through which the working fluid separated by a partition flows inside the heat transfer pipe, the flow is separated for each region separated by the vertical partition plate. The road cross-sectional area is different.
[0010]
A heat exchanger according to a third aspect of the present invention includes the U-shaped heat transfer tubes arranged in a plurality of rows in the gas flow direction.
[0011]
Moreover, the heat exchanger which concerns on Claim 4 of this invention makes the flow-path cross-sectional area in the said header below the sum of the flow-path cross-sectional area of a heat exchanger tube.
[0012]
Moreover, the heat exchanger which concerns on Claim 5 of this invention forms the fitting groove into which the said heat exchanger tube inserts and locks in the through-hole which the said heat exchanger tube communicates with the said header, and the said vertical partition plate.
[0013]
Moreover, the heat exchanger which concerns on Claim 6 of this invention has a cut and raised between the said heat exchanger tubes of the said plate-shaped fin, and the said raise is not located in the long-axis center part of the said flat heat exchanger tube. .
[0014]
An air conditioner according to a seventh aspect of the present invention comprises at least a compressor, a condenser, a throttling device, and an evaporator connected in order by a pipe, and a refrigerant is used as a working fluid. Is used as an evaporator or a condenser.
[0015]
The air conditioner according to claim 8 of the present invention uses any one of HC refrigerant or a mixed refrigerant containing HC, R32, ammonia, and carbon dioxide as the refrigerant.
[0016]
Implementation of the Invention
Embodiment 1 FIG.
FIG. 1 is a perspective view of a heat exchanger according to Embodiment 1 of the present invention, and the same components as those in the conventional example are denoted by the same reference numerals. The heat exchanger 50 is generally called a plate fin-and-tube type in which a refrigerant flows inside the heat transfer tube and exchanges heat with air flowing outside the heat exchanger. The heat exchanger 50 includes a plate-like fin 1 and a row of flat heat transfer tubes 2 inserted perpendicularly to the plate-like fin 1, and a header 3 is provided on one side of the plurality of flat heat transfer tubes 2. Are connected to one end of each of the plurality of flat heat transfer tubes, and the other end 2a of each of the flat heat transfer tubes is bent into a U shape. Connected to each. FIG. 1 shows an example in which four sets of flat heat transfer tubes bent in a U shape are used in a one-pass flow path from the inflow to the outflow of the refrigerant. The gas flowing between the fins is air sent by a blower (shown in FIG. 3), the flow direction of which is perpendicular to the heat transfer tube axial direction and the heat transfer tube cross-section short axis direction is perpendicular to white. Indicated by an arrow. Further, the direction of refrigerant flow when the heat exchanger 101 is used as an evaporator is indicated by black arrows. The header 3 is provided with refrigerant inflow pipes 10a and 10b and refrigerant outflow pipes 11a and 11b.
[0017]
FIG. 2 is a shape when the heat exchanger of FIG. 1 is cut in a cross section parallel to the plate-like fin 1, and the heat transfer tube is provided with a plurality of flow paths 6 separated by partition walls 14. In this embodiment, the pitch Fp in the stacking direction of the fins 1 is Fp = 0.001 m, the fin thickness Ft = 0.0001 m, and the fin width Lp along the air flow is Lp = 0.025 m. The step pitch Dp, which is the distance between the centers of the heat transfer tubes adjacent in the direction, is Dp = 0.012 m, the long axis length Dl of the heat transfer tube is Dl = 0.02 m, the short axis length is Ds is Ds = 0.002 m, The distance La from the end of the air flow upstream fin to the heat transfer tube is La = 0.0025 m. In addition, eight channels 6 are provided, and the cross-sectional shape thereof is substantially square, and the thickness Dt of the partition wall 14 is Dt = 0.0003 m. In addition, the plate-like fin 1 surface shown in FIG. 2 is provided with a cut-and-raised portion 7 between the heat transfer tubes adjacent in the step direction to promote heat transfer between the air passing between the fins and the fin. In addition, when the heat transfer tube 2 is inserted, a fin collar (not shown) is provided in the flat heat transfer tube insertion portion in order to firmly fix the heat transfer tube 2 and the plate-like fins 1 and to secure a fin stacking direction pitch. .
[0018]
FIG. 3 shows a refrigerant circuit in which the heat exchanger 50 shown in FIG. 1 is used in a heat pump type refrigerating and air-conditioning cycle apparatus. The working fluid flowing in the heat transfer pipe is, for example, carbon dioxide or propane, which is an HC refrigerant, and the refrigerant circuit in FIG. 3 includes the compressor 21, the four-way valve 22, the outdoor heat exchanger 23, the expansion device 24, and the indoor heat exchanger. 25. In FIG. 3, the example which used the heat exchanger 50 by the 1st Embodiment of this invention for the indoor heat exchanger 25 is shown. As for the flow direction of the refrigerant, the solid line arrow is during cooling, and the dotted line arrow is during heating. The indoor heat exchanger 25 during cooling operates as an evaporator. Reference numeral 26 denotes an outdoor fan, 27 denotes an outdoor fan motor, 28 denotes an indoor fan, 29 denotes an indoor fan motor, and 31 and 32 denote refrigerant pipes connecting the outdoor unit 33 and the indoor unit 34, respectively.
[0019]
FIG. 4 shows a cross-sectional view of the header 3 of the heat exchanger 50 taken along the long-axis cross section shown in FIG. In addition, the some flow path 6 of the heat exchanger tube 2 is abbreviate | omitted. At this time, in the cylindrical header 3, the header space is separated into two or more facing the gas flow direction, and the internal working fluid is separated into two or more rows facing the gas flow direction, It comprises vertical partition members 8a and 8b and horizontal partition members 9a and 9b. Specifically, the first longitudinal partition member 8a in the header longitudinal axis direction that partitions the inlet and outlet of the internal working fluid in the header, and the working fluid of the upper and lower heat transfer tubes adjacent in the header And a second vertical partition member 8b that flows in the up-down direction and a horizontal partition member 9a, 9b in the header cross section that separates the vertical flow of the working fluid in the upper and lower heat transfer tubes adjacent in the header. In FIG. 4, the minimum combination of these partition members is four heat transfer tubes. FIG. 4 is a form in which two of these are combined, and a path partition member 9 c is provided in this partition portion. In FIG. 4, when the heat exchanger 50 is used as an evaporator, the refrigerant flow direction is indicated by a solid line arrow, and the refrigerant flow direction at the U-shaped bent portion of the heat transfer tube 2 across the plate-like fin 1 is indicated by a dotted line arrow. is there. Due to the partition plates 8 and 9 provided in the header 3, the refrigerant flowing from the inflow pipe 10 flows through the windward flow path of the heat transfer pipe 2 and reaches the uppermost or lowermost header space. And flows out from the outflow pipe 11. A schematic diagram of the refrigerant flow of the internal working fluid of the heat exchanger at this time is shown in FIGS.
[0020]
In the heat exchanger 50 used as an evaporator, the refrigerant temperature decreases from the refrigerant inflow pipe 10 toward the outflow pipe 11 due to refrigerant pressure loss. On the other hand, the temperature of the air decreases with respect to the flow direction 5. By defining the refrigerant flow direction in the heat transfer tube 2 by the header structure shown in FIG. 4, the heat transfer tube 2 cross-sectional length orthogonal to the heat transfer tube 2 tube axial direction in the plurality of flow paths 6 provided in the heat transfer tube 2. Since the axial refrigerant flow direction is parallel to the air flow direction 5, it is possible to realize a heat exchange mode in which a temperature difference between the air temperature and the refrigerant temperature can always be secured with respect to the air flow direction. FIG. 6 shows the air temperature and the refrigerant temperature distribution in the heat exchanger at this time. As can be seen from FIG. 6, in the first embodiment, a temperature difference between the air temperature and the refrigerant temperature can always be ensured, and a heat exchanger with high heat exchange efficiency can be provided.
[0021]
On the other hand, the operation of the heat exchanger 50 used as a condenser will be described. Although the air flow direction is the same as that of the evaporator, the refrigerant flow direction in FIG. 4 is opposite to the arrow, and therefore flows in from the outflow pipe 11 side and flows out to the inflow pipe 10 side. The refrigerant temperature decreases with respect to the refrigerant flow direction, and the temperature of air increases with respect to the flow direction 5. By defining the refrigerant flow direction in the heat transfer tube 2 by the header structure shown in FIG. 4, the long axis of the cross section of the heat transfer tube 2 orthogonal to the direction of the heat transfer tube 2 axis in the plurality of flow paths 6 provided in the heat transfer tube 2. Since the refrigerant flow direction of the direction is opposite to the air flow direction 5, it is possible to realize a heat exchange mode that can always ensure a temperature difference between the air temperature and the refrigerant temperature with respect to the air flow direction. FIG. 7 shows the air temperature and the refrigerant temperature distribution in the heat exchanger at this time. As can be seen from FIG. 7, in the first embodiment, a temperature difference between the air temperature and the refrigerant temperature can always be ensured, and a heat exchanger with high heat exchange efficiency can be provided.
[0022]
FIG. 8 shows an assembly structure of the vertical partition member 8 and the heat transfer tube 2. That is, a fitting groove 19a for insertion fitting of the heat transfer tube 2 is provided on one end surface (separation end surface 15) in the width direction of the vertical partition member 8, and the heat transfer tube 2 inserted through the through hole 13 of the header 3 is fitted. It is inserted into the mating groove 19a and stopped.
[0023]
FIG. 9 also shows another embodiment of the assembly structure of the vertical partition member 8 and the heat transfer tube 2. That is, the heat transfer tube 2 is provided with a groove 19b for insertion fitting of the vertical partition member 8, and the vertical partition member is not provided with a groove, and the heat transfer tube 2 inserted through the through hole 13 of the header 3 is locked. The
[0024]
By configuring the vertical partition member 8 and the fitting grooves 19a and 19b in this way, when the heat transfer tube is fitted to the header 3, the heat transfer tube 2 is securely fixed, and the heat transfer tube 2 is connected to the header 3. The amount of insertion becomes appropriate, manufacturing variations are reduced, productivity is improved, and manufacturing costs can be reduced.
[0025]
8, 9, and 10 show various examples of the shape of the header 3 and the partition member 8, and the vertical partition member 8 described above is inserted and welded to the header 3 in FIG. 8. FIG. 9 shows an example in which the header 3 and the vertical partition member 8 are integrally formed by extrusion molding.
[0026]
10A and 10B show a partition member formed by bending the header 3. In the example shown in FIG. 10 (a), a plate-shaped header material is bent into a substantially rectangular cross-sectional shape to constitute the outer shape of the header 3, and one end of the header material is bent and welded to the inner surface of the header 3. Thus, the vertical partition member 8 is configured. The cross-sectional shape of the header may be substantially circular, and the other end of the header material may be bent short and welded to one surface of the partition member 8. In the example shown in FIG. 10B, the header cross section is formed in a substantially semicircular shape. According to the structure shown in FIGS. 8, 9, and 10, the header 3 can be manufactured at low cost and in large quantities. Further, when the heat transfer tube 2 and the header 3 are manufactured by brazing and welding in an oven using an aluminum material, an aluminum clad material, a flux, etc., the fitting gaps of the respective parts can be securely adhered and joined together. Problems such as leakage can be prevented. The header 3 having a circular cross section in the axial direction has a higher internal pressure strength. However, if the header plate material is expanded in strength or the plate pressure is increased to ensure the internal pressure strength, the cross-sectional shape may be substantially rectangular. A cross-sectional shape may be used. Note that the volume of the header 3 is reduced and the heat exchanger 50 can be made compact when the substantially rectangular or semicircular cross-sectional shape is used.
[0027]
FIG. 11 is a view showing an assembly structure of the vertical partition member 9 and the heat transfer tube 2. The header 3 is provided with a fitting groove 18 into which the vertical partition member 9 is inserted in the cross-sectional direction. According to the structure shown in FIG. 11, the header 3 can be manufactured at a low cost and in a large amount as in FIG. Further, when the heat transfer tube 2 and the header 3 are manufactured by brazing and welding in an oven using an aluminum material, an aluminum clad material, a flux, etc., the fitting gaps of the respective parts can be securely adhered and joined together. Problems such as leakage can be prevented.
[0028]
Next, the dimensions of the header space 12 in the header 3 will be described. 12 is a cross-sectional view in which the header 3 having a substantially rectangular cross section is cut in a longitudinal direction along a surface that coincides with the flow direction of the working fluid in the heat transfer tube, and FIG. 13 is a cross-sectional view cut in a cross section orthogonal to the flat heat transfer tube 2. is there. The minimum flow path cross-sectional area in the refrigerant flow direction in the header space 12 in the refrigerant flow direction indicated by the arrows in FIGS. 12 and 13 is equal to or less than the sum of the cross-sectional areas of the plurality of flow paths 6 of the flat heat transfer tube 2, and preferably flat transfer. The cross-sectional area of the plurality of flow paths 6 of the heat pipe 2 is set to a hydraulic equivalent diameter or less. The reason is as follows. That is, in the flat heat transfer tube 2, heat exchange is more facilitated in the windward side refrigerant flow path 6 a, so that the refrigerant dryness varies from the windward side to the leeward side of each refrigerant flow path 6 and flows into the header space 12. Come on. For example, when the heat exchanger 50 acts as an evaporator, the refrigerant dryness on the windward side is larger than that on the leeward side, and when the heat exchanger 50 acts as a condenser, the refrigerant dryness on the windward side is smaller than that on the leeward side. And flows into the header space 12. When the refrigerant flows into the next flat heat transfer tube in the refrigerant state as it is, the difference in the dryness of the refrigerant further expands in the refrigerant flow path between the leeward side and the upwind side, causing a decrease in the heat exchange amount. For this purpose, the refrigerant flowing into the header space 12 is mixed to equalize the dryness of the refrigerant, and the refrigerant is allowed to flow through the next flat heat transfer tube. However, if the volume or the cross-sectional area of the header space 12 is too large, the refrigerant flow rate in the header space 12 is lowered, the gas-liquid two-phase refrigerant is easily separated, and the dryness uniform flow to the next flat heat transfer tube cannot be maintained. .
[0029]
FIG. 14 is a sectional view of an indoor unit configuration showing an example in which the heat exchanger 50 is used as an indoor heat exchanger of an air conditioner. The heat exchanger 50 is installed at an angle with respect to the vertical direction of the indoor unit. If the volume or the cross-sectional area of the header space 12 is too large, the refrigerant flow rate in the header space 12 decreases, and the gas-liquid It becomes easier to separate the phase refrigerant and it becomes impossible to maintain a uniform dryness flow to the next flat heat transfer tube. Accordingly, in FIGS. 12 and 13, the cross-sectional area in the refrigerant flow direction in the header space 12 is equal to or less than the sum of the cross-sectional areas of the plurality of flow paths 6 of the flat heat transfer tubes 2, preferably the flow paths 6 of the flat heat transfer tubes 2. By setting the cross-sectional area to be equal to or less than the hydraulic equivalent diameter, the refrigerant flow rate that can avoid two-phase separation is maintained. Thereby, the fall of the heat exchange amount can be prevented and a high-performance heat exchanger can be obtained. The minimum flow path cross-sectional area may not be the same in the header space with respect to the flow direction. For example, as shown in FIG. 13, the header partition wall thickness may be locally increased and narrowed.
[0030]
15A, 15B, and 15C show various examples of heat transfer tubes. FIG. 15A shows the heat transfer tube 2 described above, and a plurality of refrigerant flows between the plurality of partition walls 14. A path 6 is formed. In the partition wall 14, the separation end surface 15 of the vertical partition member 8 is in contact with the partition wall 14 a located substantially in the center, and the respective coolant channels are connected to the left and right coolant channels, that is, the coolant channel on the windward side of the heat exchange air and the leeward side. The refrigerant flow path is separated. In addition, the heat transfer tube 2 is configured by forming the central partition wall 14 a in contact with the separation end face 15 in the partition wall 14 to be larger than the thicknesses of the other partition walls 14. By increasing the thickness of the partition wall 14a in this way, the joining space of the separation end face 15 can be afforded, the degree of freedom in assembling the heat transfer tube 2 to the header 3 can be increased, and productivity can be improved.
[0031]
FIG. 15B and FIG. 15C are configured such that the refrigerant flow rate in the leeward refrigerant flow path 6b is smaller than the refrigerant flow rate in the leeward refrigerant flow path 6a. That is, the heat transfer tube 2 shown in FIG. 15B is formed by reducing the flow cross-sectional area of each of the refrigerant flow paths 6b on the leeward side to reduce the refrigerant flow rate. With this configuration, a large amount of refrigerant can be circulated through the refrigerant channel 6a on the windward side, and the amount of heat exchange can be improved. Further, in the heat transfer tube 3 shown in FIG. 15 (c), by shifting the position of the partition wall 14a from the center of the heat transfer tube to the leeward side, the leeward refrigerant flow path 6b has a small flow cross-sectional area, and the leeward refrigerant flow By increasing the number of paths 6a, the total flow cross-sectional area of the refrigerant is increased to the windward side. By comprising in this way, a large amount of refrigerant | coolants can be distribute | circulated to the refrigerant | coolant flow path 6a of an upwind side, and the amount of heat exchange can be improved.
[0032]
Embodiment 2. FIG.
FIG. 16 is a perspective view of the heat exchanger according to the second embodiment of the present invention, in which the same components as those in FIG. 1 of the first embodiment are denoted by the same reference numerals and used as an evaporator. The air flow direction is 5, and the refrigerant flow direction is the direction of the black arrow. In FIG. 16, the heat exchanger 50 includes a plate-like fin 1 and two rows of flat heat transfer tubes 2 inserted perpendicularly to the plate-like fin, and a header on one side of the plurality of flat heat transfer tubes 2. 3 is connected to the header 3 at predetermined intervals to connect one end of each of the plurality of flat heat transfer tubes, and the other end of each of the flat heat transfer tubes is bent into a U shape. Each is connected. FIG. 16 shows an example in which four sets of flat heat transfer tubes bent in a U-shape are used in one path flow path until the refrigerant flows in and out. The gas flowing between the fins is air sent by a blower, and the flow direction thereof is indicated by a white arrow in a direction 5 perpendicular to the heat transfer tube axial direction and the heat transfer tube section short axis direction orthogonal. Further, the direction of refrigerant flow when the heat exchanger 101 is used as an evaporator is indicated by black arrows. The header 3 is provided with refrigerant inflow pipes 10a and 10b and refrigerant outflow pipes 11a and 11b.
[0033]
FIG. 17 is a cross-sectional view of the heat exchanger of FIG. 16 taken along a cross section parallel to the plate-like fin 1, and the heat transfer tube 2 is provided with a plurality of flow paths 6 separated by partition walls 14. . In this embodiment, the pitch Fp in the stacking direction of the fins 1 is Fp = 0.001 m, the fin thickness Ft = 0.0001 m, and the fin width Lp along the air flow is Lp = 0.025 m. The step pitch Dp, which is the distance between the centers of the heat transfer tubes adjacent in the step direction, is Dp = 0.012 m, and the row pitch DL, which is the distance between the centers of the heat transfer tubes adjacent in the row direction of the heat transfer tubes, is DL = 0.012 m. The major axis length Dl of the heat tube is Dl = 0.01 m, the minor axis length is Ds = 0.002 m, and the distance La from the air flow upstream fin end to the heat transfer tube is La = 0.015 m. In addition, four channels 6 are provided, and the cross-sectional shape thereof is square, and the thickness Dt of the partition wall 14 is an example in which Dt = 0.0003 m. In addition, the plate-like fin surface shown in FIG. 17 is provided with a cut-and-raised portion 7 between the heat transfer tubes adjacent in the step direction as in FIG. 2 to promote heat transfer between the air passing between the fins and the fin. Yes.
[0034]
An example of the refrigerant circuit in which the heat exchanger 50 shown in FIG. 16 is used in the indoor heat exchanger 25 as an evaporator of a heat pump refrigeration air-conditioning cycle apparatus during cooling operation is the same as that in FIG.
[0035]
FIG. 18 shows a cross-sectional view of the header 3 of the heat exchanger 50 according to the second embodiment when cut along the cross section in the major axis direction shown in FIG. In addition, the some flow path 6 of the heat exchanger tube 2 is abbreviate | omitted. At this time, since two rows of heat transfer tubes 2 are inserted into the header, the through holes 13 are provided in two rows. As in FIG. 4, first and second vertical partition members 8 a and 8 b are provided in the header 3 in the major axis direction, and horizontal partition members 9 a, 9 b and 9 c are provided in the cross-sectional direction in the header 3. However, the configuration, purpose, and effect of the vertical and horizontal partition members 8 and 9 are the same as those of the first embodiment. Hereinafter, the operation of the heat exchanger 50 will be described.
[0036]
In the heat exchanger 50 used as an evaporator, when the refrigerant flows from the refrigerant inflow pipe 10 toward the outflow pipe 11, the refrigerant temperature decreases due to refrigerant pressure loss. On the other hand, the temperature of the air decreases with respect to the flow direction 5. By defining the refrigerant flow direction in the heat transfer tube 2 by the header structure shown in FIG. 18 as indicated by the arrows in the figure, the axial direction of the heat transfer tube 2 in the plurality of flow paths 6 provided in the heat transfer tube 2 Exchange direction in which the refrigerant flow direction in the longitudinal direction of the cross section of the heat transfer tube 2 orthogonal to the air flow direction 5 is parallel to the air flow direction 5, so that a temperature difference between the air temperature and the refrigerant temperature can always be secured with respect to the air flow direction And a heat exchanger with high heat exchange efficiency can be provided. Further, although the heat transfer tubes have a two-row configuration, the fin area, the heat transfer tube area, and the cut-and-raised portion 7 have the same size and shape as in FIG.
[0037]
In addition, when operating as an evaporator of an air conditioner, air is dehumidified under humid conditions, and condensed water is generated on the plate-like fins 1. At this time, if the condensed water is still folded on the plate-like fins 1, the heat transfer performance will decrease, the air flow will decrease due to the increase in ventilation resistance, and the blower drive power will increase. It is necessary to distribute the condensed water promptly under gravity because it causes a decrease in operating efficiency. As shown in FIG. 19, the dew condensation water tends to be accumulated at the upper and lower portions of the heat transfer tube 2, and the amount of accumulation becomes larger as the flat heat transfer tube major axis length is longer due to the influence of surface tension. In the second embodiment, the amount of accumulation can be reduced by forming the flat heat transfer tubes 2 in a two-row configuration. Moreover, the flow resistance which flows the dew condensation water dripped from the upper stage side heat exchanger tube will become large, the one where the long axis length of the flat heat exchanger tube is long. In the second embodiment, by forming the flat heat transfer tubes in a two-row configuration, the condensed water dripped from the upper heat transfer tubes as shown in FIG. 19 can be quickly flowed downward. Furthermore, since the dew condensation water at the lower part of the heat transfer tube 2 is likely to gather at the center of the heat transfer tube long axis, in the present embodiment, the cut-and-raised portion 7 is not provided at the center of the heat transfer tube long axis, as shown in FIG. The condensed water dripped from the lower part of the heat transfer tube can be quickly flowed downward.
[0038]
On the other hand, the value equivalent to Embodiment 1 can be obtained about the effect | action and effect of the heat exchanger 50 used as a condenser.
[0039]
In the first and second embodiments, the example in which the refrigerant inflow pipe 10 and the refrigerant outflow pipe 11 are installed at the center of the header 3 when used as an evaporator to the heat exchanger 50 has been shown. The refrigerant inflow pipe 10 and the refrigerant outflow pipe 11 may be arranged above and below the header 3 as shown in the perspective view of the vessel and the header cross-sectional view of FIG. Further, as shown in FIG. 21 (b), the minimum unit of the heat transfer tube combination of the header structure in the present embodiment is four flat heat transfer tubes 2 bent in a U-shape, so every four heat transfer tubes. One header may be combined, and these may be combined to form one heat exchanger. At this time, the inflow pipes 10a, 10b, and 10c and the outflow pipes 11a, 11b, and 11c for the internal working fluid can be set at arbitrary positions, respectively. In the first and second embodiments, the example in which the header 3 is partitioned into two rows in the inner shaft direction is shown, but multiple rows may be used. In this case, the partition member is also arranged so that the refrigerant flows in a parallel flow with respect to the air flow when used as an evaporator and an opposite flow with respect to the air flow when used as a condenser. The shape, position, thickness, and partition wall thickness of the heat transfer tube may be determined. The same applies to the case where the heat transfer tubes are arranged in multiple rows as in the second embodiment. In the first and second embodiments, an example in which four sets of U-shaped bending heat transfer tubes 2 are used per one flow path is shown, but a larger number of U-shaped bending heat transfer tubes 2 may be used. In the first and second embodiments, the U-shaped bending heat transfer tube 2 is used. However, as shown in FIG. 26, headers may be installed on both sides of the end portion in the axial direction of the heat transfer tube. At this time, the shape of the partition member of the header 4 may be configured such that the refrigerant flow is the same as that of the U-shaped bent heat transfer tube. Further, the number and size of the square flow paths 6 provided in the heat transfer tube 2 may be arbitrarily set. Also, the various shape parameters and the cut-and-raised portions 7 described in FIGS. 2 and 17 may be set to arbitrary values and shapes.
[0040]
Further, protrusions 41 may be provided in the plurality of flow paths 6 of the heat transfer tube 2 described in the first and second embodiments as shown in FIG. Since this protrusion can secure a large amount of the heat transfer area of the refrigerant, the performance of the heat exchanger can be improved. The protrusion may be twisted with respect to the working fluid flow tube axis direction. At this time, the film thickness of the refrigerant liquid in the pipe can be made uniform and thin by the effect of raising the refrigerant flow, so that the heat exchanger performance can be improved. The protrusion may be a combination of protrusions twisted leftward and rightward with respect to the direction of the working fluid flow tube axis. At this time, the refrigerant heat collision performance can be improved by the refrigerant flow collision effect, and the heat exchanger performance can be improved. Further, if the short axis length is the same as the flat tube, the heat transfer tube may have an elliptical shape or a bowl shape as shown in FIGS.
[0041]
Further, the shape of the plurality of flow paths 6 of the heat transfer tube 2 described in the first and second embodiments may be rectangular, circular, or oval as long as the refrigerant heat transfer area can be secured.
[0042]
As shown in FIG. 25, the arrangement of the heat transfer tubes 2 having the two-row configuration described in the second embodiment is a method in which a fin collar is provided on the plate-like fin 1 and inserted and held in from both ends of the plate-like fin 1. Also good. As a result, the fin collar gap size of the plate-like fins and the gap management of the inserted heat transfer tube become loose, and the heat transfer tube can be easily inserted, thereby improving the productivity. Further, the interval 42 between the heat transfer tube end portions at this time may be the total value of the distance from the fin end portion to the heat transfer tube end portion and the interval between both heat transfer tube end portions shown in FIG. FIG. 25 shows the case of a two-row heat transfer tube, but it is also possible to adopt a method of inserting and inserting from the end face on one side of the fin in the case of one row.
[0043]
The manufacturing method of the heat exchanger described in the first and second embodiments is as follows. First, the heat transfer tube 2 is manufactured by drawing or extruding a material having high thermal conductivity such as aluminum or copper. Further, the fin 1 is manufactured by pressing a material having high thermal conductivity such as an aluminum material or a copper material. Further, the header 3 is manufactured by extruding or forging a pipe, pressing a flat plate, or cutting a prism. These materials are coated on the surface with a flux for brazing in the furnace. For example, when using an aluminum material, an aluminum clad material is used on the heat transfer tube side, an aluminum material is used on the fin side, or vice versa. Further, an aluminum material may be used for both the heat transfer tube side and the fin side, and a brazing material may be applied to the surface of the heat transfer tube. Then, the fin and the heat transfer tube are fixed by fixing a jig or the like, or the header and the heat transfer tube are fixed by pressure welding or the like. After that, by using a vacuum furnace or a nitrogen furnace, it is possible to perform a large amount of joining by brazing the fins, the heat transfer tubes, and the headers at a high speed, thereby increasing productivity. Also, the contact heat transfer coefficient between the fin and the heat transfer tube can be made infinite by brazing, and the performance of the heat exchanger can be greatly improved. Also, by joining the header and heat transfer tube at once by brazing in the furnace, it is possible to prevent leakage of refrigerant due to poor brazing, flammable refrigerants such as HC, toxic refrigerants such as ammonia, and high-pressure refrigerants such as carbon dioxide. Safety against refrigerant leakage when used can be ensured. Moreover, recyclability can be improved by manufacturing a fin, a heat exchanger tube, and a header with the same material.
[0044]
The fin described in the first and second embodiments is coated with a hydrophilic material on the surface. Smooth drainage of condensed water when used as an evaporator, prevents increase in ventilation resistance due to accumulation of condensed water in the heat exchanger, and increases heat exchange volume due to increased air volume of heat exchange air In addition, the noise can be reduced, and the energy efficiency and comfort of the apparatus can be improved. Further, the coating may be performed before brazing in the furnace or after brazing.
[0045]
The fins, heat transfer tubes, and header pipes are manufactured by brazing in the furnace and coated with a hydrophilic material, so that smooth drainage of condensed water can be ensured when used as an evaporator, heat exchange. The increase in ventilation resistance due to the accumulation of condensed water in the chamber is prevented, the heat exchange amount can be increased due to the increase in the amount of heat exchange air, and the noise can be reduced, improving the energy efficiency and comfort of the device. be able to. Condensed water causes heat exchanger corrosion, but if a material is selected that gives a potential difference between the fin material and the heat transfer tube material, and the fin material is prone to corrode, the material will be transmitted even if corrosion proceeds. Corrosion of the heat pipe can be prevented, leakage of the refrigerant can be avoided, and safety can be ensured.
[0046]
In addition, as a refrigerant of the heat exchanger of Embodiments 1 and 2 and a refrigerating and air-conditioning cycle apparatus using the same, a single HC refrigerant such as methane, ethane, propane, butane, isobutane, propylene, isopropylene, or HC is used. By using the mixed refrigerant containing, the global warming potential can be made very small. Propane has a greater temperature drop with respect to refrigerant pressure loss than conventional refrigerant R22. For example, when the refrigerant saturation temperature changes from 10 ° C. to 0 ° C., R22 has a pressure change of 0.183 MPa, while propane has a pressure change of 0.162 MPa. Isobutane also has a greater temperature drop with respect to refrigerant pressure loss than the conventional refrigerant R134a. For example, when the refrigerant saturation temperature changes from −20 ° C. to −30 ° C., R134a has a pressure change of 0.0483 MPa, while isobutane has a pressure change of 0.0258 MPa. For this reason, in the refrigerating and air-conditioning cycle apparatus using these refrigerants, it is necessary to make the absolute value of the refrigerant pressure loss smaller than that of the conventional refrigerant. The heat exchanger of this embodiment is provided with a plurality of flow paths (for example, 10 or more flow paths having a diameter of 1.5 mm) provided in a flat heat transfer tube and separated by a partition wall, and connected to one header. By increasing the number of heat tubes, it is possible to construct a super multi-channel heat exchanger, and it is very easy to reduce the absolute value of the refrigerant pressure loss. Accordingly, even when a single HC refrigerant or a mixed refrigerant containing HC is used, a highly efficient refrigeration / air-conditioning cycle apparatus can be provided.
[0047]
Further, as the refrigerant of the heat exchangers of the first and second embodiments and the refrigerating and air-conditioning cycle apparatus using the same, R32 single or a mixed refrigerant containing R32 (R407A, R407B, R407C, R407D, R407E, R410A, R410B, etc.) can be used to make the global warming potential very small. However, the R32 refrigerant has a higher operating pressure than the conventional refrigerant R22. For example, the pressure at the saturation temperature of 50 ° C. for R22 is 1.94 MPa, whereas it is 3.14 MPa for R32 and 3.06 MPa for R410A. Since the heat exchanger of this embodiment is provided with a plurality of channels (for example, a channel having a diameter of 1.5 mm having 10 or more channels) separated by a partition wall having a thickness of about 0.3 mm in the flat heat transfer tube. The pressure strength can be increased. Therefore, it is possible to provide a refrigerating and air-conditioning cycle device that ensures high efficiency and sufficient reliability. Moreover, since the vertical and horizontal partition plates 8 and 9 are provided in the header 3, the pressure resistance can be further increased.
[0048]
In addition, by using a single ammonia or a mixed refrigerant containing ammonia as the refrigerant of the heat exchangers of the first and second embodiments and the refrigerating and air-conditioning cycle apparatus using the heat exchanger, the global warming potential is very small. can do. However, ammonia corrodes the copper heat transfer tube used in the conventional circular plate fin type heat exchanger. In the heat exchanger of this embodiment, corrosion-resistant aluminum is used for plate fin materials, flat heat transfer tubes and headers and brazed in an integrated furnace, ensuring corrosion resistance and refrigerant leakage due to poor brazing. It is possible to provide a refrigerating and air-conditioning cycle apparatus that can prevent the above-described problem and ensure high efficiency and sufficient safety.
[0049]
Further, as a refrigerant for the heat exchangers of the first and second embodiments and the refrigerating and air-conditioning cycle apparatus using the heat exchanger, global warming is achieved by using a single refrigerant of carbon dioxide, air, water, or a mixed refrigerant thereof. The coefficient can be made very small. However, these refrigerants have a higher operating pressure than R32 refrigerants. For example, the pressure of carbon dioxide at a saturation temperature of 30 ° C. is 7.205 MPa. The heat exchanger of the present embodiment is provided with a plurality of channels (for example, a channel having a diameter of 1.5 mm having 10 or more channels) separated by a partition wall having a thickness of about 0.3 mm in the flat heat transfer tube. Even if added to these ultra-high pressure refrigerants, the pressure resistance can be increased. Therefore, it is possible to provide a refrigerating and air-conditioning cycle device that ensures high efficiency and sufficient reliability. Moreover, since the partition plates 8 and 9 are provided in the header 3, the pressure strength can be further increased.
[0050]
Further, in the heat exchangers of the first and second embodiments and the refrigerating and air-conditioning cycle apparatus using the same, the cross-sectional area of the heat transfer tube channel 6 is considerably small, so that a minute substance such as sludge is mixed in the refrigerant circuit. If sludge is generated from a compressor or the like, the refrigerant circuit may be blocked. For this reason, by introducing sludge supplement devices such as a dryer and a filter into the refrigerant circuit, it is possible to prevent the heat transfer tube flow path 6 from becoming sludge from being blocked, and to provide a highly reliable refrigerating and air-conditioning cycle device. Can do. Moreover, by introducing mineral oil, alkylbenzene oil, ether oil, ester oil, fluorine oil, etc. as the refrigerating machine oil of the heat exchangers of the present embodiments 1 and 2 and the refrigerating and air-conditioning cycle apparatus using the same, the generation of sludge is suppressed. In addition, the reliability can be improved. Even when refrigeration oil that is incompatible or weakly compatible with each of the refrigerants described above is used, since the heat transfer tube channel 6 is fine, the refrigerant and the refrigeration oil are mixed very well, and the oil stays there. Insufficient refrigeration oil in the compressor due to, for example, is difficult to occur, and sliding failure of the compressor machine part due to insufficient refrigeration oil does not occur. Further, since the refrigerant and the refrigerating machine oil are mixed very well, there is no possibility that the refrigerant heat transfer performance is lowered by the refrigerating machine oil or the refrigerant pressure loss is increased due to oil accumulation.
[0051]
In the refrigerating and air-conditioning cycle apparatuses shown in the first and second embodiments, the compressor has any type, for example, a reciprocating compressor (single cylinder, multiple cylinders), a rotary compressor (single cylinder, multiple cylinders), A scroll compressor, a linear compressor, or the like may be used. Further, when an electric motor for rotating the compression portion is built in the compressor shell, the pressure structure in the shell may be high or low. In the high-pressure shell method, the refrigerant exiting the compression cylinder cools the motor and is heated and discharged from the compressor, so the discharge temperature increases. On the other hand, in the low-pressure shell method, the refrigerant flowing into the shell is sucked into the compression cylinder after being heated by cooling the motor, so that the suction temperature becomes high. However, since the refrigerant flowing out from the compression cylinder is directly discharged out of the compressor, the discharge temperature is lowered. Depending on the refrigerant used, the discharge temperature is increased or decreased. In particular, the R32 refrigerant has a higher discharge temperature than the R410A refrigerant, and the propane has a lower discharge temperature than the R410A refrigerant. You can select either high or low pressure. In general, the high-pressure shell has a larger amount of refrigerant and penetration into the compressor refrigeration oil than the low-pressure shell. Therefore, it is better to select the low-pressure shell method when it is desired to reduce the refrigerant charging amount, but the refrigerant amount can be reduced even in the high-pressure shell by using refrigerating machine oil in which the refrigerant does not dissolve easily.
[0052]
【The invention's effect】
As described above, the heat exchanger according to claim 1 of the present invention is arranged in parallel, and a plurality of plate-like fins in which gas flows between them, and is arranged through the plate-like fins, A heat transfer pipe bent into a U shape provided with a plurality of flow paths through which the working fluid flows inside a flat cross section, and a header in which the end of the heat transfer pipe communicates with the working fluid inflow pipe and the outflow pipe And a first longitudinal partition plate in the longitudinal direction of the header that separates a space that is provided in the header and communicates from the inflow pipe to the heat transfer pipe and a space that communicates from the heat transfer pipe to the outflow pipe. U-shaped heat transfer tube Over Provided in the header space in the air flow Opposite The second longitudinal partition plate in the header longitudinal direction to be separated, and both ends of the U-shaped heat transfer tube In the header space A separating partition, The header inner space is separated into a windward flow channel and a leeward flow channel with respect to the gas flow direction by the first and second vertical partition plates, and the working fluid flow in the header longitudinal direction is partitioned by the horizontal partition plates. When the working refrigerant that has flowed in from the inflow pipe is used as an evaporator, it flows through the windward flow path of the heat transfer pipe having the flat cross section and reaches the end space of the header to reach the leeward side of the heat transfer pipe. It flows through the flow path and flows out from the outflow pipe, and becomes a parallel flow with respect to the air flow direction.When used as a condenser, it flows through the leeward flow path of the heat transfer pipe having the flat cross section and flows through the header. When it reaches the end space, it flows through the windward flow path of the heat transfer tube and flows out of the outflow tube, and becomes a counterflow with respect to the air flow direction. Therefore, a plurality of refrigerant flow paths communicating in series can be formed, and a wide variety of refrigerant paths can be reliably formed. In addition, when used as an evaporator of a vapor compression type air conditioner using a refrigerant, the refrigerant flowing in the refrigerant channel on the windward side of the heat transfer tube flows in the refrigerant channel on the leeward side to reciprocate the refrigerant. It can be made to flow and heat exchange efficiency is improved by co-current with the air flow. In addition, when used as a condenser, the refrigerant that has flowed through the refrigerant channel on the lee side of the heat transfer tube can be caused to flow through the refrigerant channel on the leeward side to reciprocate the refrigerant, and counterflow with the air flow. In particular, the heat exchange efficiency is improved. Thereby, the capability increase and energy efficiency improvement of an air conditioner can be aimed at.
[0053]
In addition, the heat exchanger according to claim 2 of the present invention is configured such that, in a plurality of flow paths through which the working fluid separated by a partition flows inside the heat transfer tube, the flow paths are separated for each region separated by the vertical partition plate. Since the cross-sectional areas are different, the refrigerant flow rate is set in accordance with the heat exchange amount on the air side by making the passage cross-sectional areas of the refrigerant flow passages formed upstream and downstream of the heat transfer tube central partition in the air flow direction. Therefore, the performance of the heat exchanger can be maximized.
[0054]
Moreover, since the heat exchanger which concerns on Claim 3 of this invention has arrange | positioned the said U-shaped heat exchanger tube in multiple rows with respect to the flow direction of gas, this heat exchanger was used as an evaporator of an air conditioner. When it is possible to improve the drainage of the condensed water generated by heat exchange with the air, the ventilation resistance can be kept low and the air volume can be increased, improving the heat exchange performance and the fan driving force Since it decreases, the capacity | capacitance increase and energy efficiency improvement of an air conditioner can be aimed at.
[0055]
Further, in the heat exchanger according to claim 4 of the present invention, the flow passage cross-sectional area in the header is made equal to or less than the sum of the flow passage cross-sectional areas of the heat transfer tubes, so the distribution performance of the gas-liquid two-phase refrigerant flowing in the header The heat exchanger efficiency can be improved, the capacity of the air conditioner can be increased, and the operating energy efficiency can be improved.
[0056]
Moreover, since the heat exchanger which concerns on Claim 5 of this invention formed the fitting groove into which the said heat exchanger tube inserts and engages in the said through-hole and the said vertical partition plate which the said heat exchanger tube communicates, the heat exchanger tube Assembling to the header is reliable, and the insertion amount of the heat transfer tube into the header is also appropriate.
[0057]
In addition, the air conditioner according to claim 6 of the present invention has a cut-and-raised portion between the heat transfer tubes of the plate-like fins, and the cut-and-raised portion is not located at the center of the long axis of the flat heat transfer tube. The condensed water dripped from the lower part of the heat transfer tube can be quickly flowed downward.
[0058]
An air conditioner according to a seventh aspect of the present invention includes at least a compressor, a condenser, a throttling device, and an evaporator that are sequentially connected by a pipe and uses a refrigerant as a working fluid. Since the heat exchanger described in any of the above is used as an evaporator or a condenser, the capacity of the air conditioner can be increased and the energy efficiency can be improved.
[0059]
In addition, the air conditioner according to claim 7 of the present invention uses a single HC refrigerant or a mixed refrigerant containing HC, R32, ammonia, or carbon dioxide as the refrigerant, thereby preventing global warming. An air conditioner can be provided.
[Brief description of the drawings]
FIG. 1 is a perspective view of a heat exchanger according to Embodiment 1 of the present invention.
FIG. 2 is a cross-sectional view of a heat exchanger according to Embodiment 1 of the present invention.
FIG. 3 is a refrigerant circuit diagram according to Embodiment 1 of the present invention.
FIG. 4 is a longitudinal sectional view of a header according to the first embodiment of the present invention.
FIG. 5 is a diagram illustrating an internal working fluid flow of the heat exchanger according to the first embodiment of the present invention.
FIG. 6 is a diagram illustrating characteristics of the heat exchanger according to the first embodiment of the present invention.
FIG. 7 is a diagram illustrating still another characteristic of the heat exchanger according to the first embodiment of the present invention.
FIG. 8 is a diagram illustrating a structure of a joint portion of a partition member, a heat transfer tube, and a header according to the first embodiment of the present invention.
FIG. 9 is a diagram illustrating still another structure of the joining portion of the partition member, the heat transfer tube, and the header according to the first embodiment of the present invention.
FIG. 10 is a cross-sectional view of still another header according to the first embodiment of the present invention.
FIG. 11 is a diagram illustrating a structure of a joining portion of a partition member and a header according to the first embodiment of the present invention.
FIG. 12 is a cross-sectional view from another direction of the header according to the first embodiment of the present invention.
FIG. 13 is a cross-sectional view from yet another direction of the header according to the first embodiment of the present invention.
FIG. 14 is a diagram illustrating a configuration of an indoor unit according to the first embodiment of the present invention.
FIG. 15 is a diagram illustrating a plurality of flow paths of a heat transfer tube according to the first embodiment of the present invention.
FIG. 16 is a perspective view of a heat exchanger according to Embodiment 2 of the present invention.
FIG. 17 is a cross-sectional view of a heat exchanger according to Embodiment 2 of the present invention.
FIG. 18 is a sectional view of a header according to the second embodiment of the present invention.
FIG. 19 is a diagram illustrating the flow of condensed water in the heat exchanger according to the second embodiment of the present invention.
FIG. 20 is a perspective view of a heat exchanger in another example according to the first and second embodiments of the present invention.
FIG. 21 is a sectional view of a header in another example according to the first and second embodiments of the present invention.
FIG. 22 is a sectional view of a heat transfer tube in another example according to the first and second embodiments of the present invention.
FIG. 23 is a cross-sectional view of a heat transfer tube in still another example according to the first and second embodiments of the present invention.
FIG. 24 is a cross-sectional view of a heat transfer tube in still another example according to the first and second embodiments of the present invention.
FIG. 25 is a cross-sectional view of a heat exchanger in another example according to the first and second embodiments of the present invention.
FIG. 26 is a perspective view of a conventional heat exchanger.
FIG. 27 is a cross-sectional view of a conventional heat transfer tube.
FIG. 28 is a cross-sectional view of a conventional heat exchanger.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Fin, 2 Flat heat exchanger tube, 3 Header, 5 Air flow direction, 6 Heat transfer pipe refrigerant flow path, 8 Vertical partition member, 9 Horizontal partition member, 10 Inflow pipe, 11 Outflow pipe, 12 Header space, 13 Through-hole, 14 Bulkhead, 18 Fitting groove, 19 Fitting groove, 21 Compressor, 22 Four-way valve, 23 Outdoor heat exchanger, 24 Throttle device, 25 Indoor heat exchanger, 26 Outdoor blower, 28 Indoor blower, 31, 32 Refrigerant piping 33 outdoor units, 34 indoor units, 41 protrusions, 50 heat exchangers, 100 heat exchangers, 103, 104 headers, 102 flat heat transfer tubes, 110 inflow tubes, 111 outflow tubes.

Claims (8)

A plurality of plate-like fins arranged in parallel and through which gas flows, and a U-shape provided with a plurality of channels arranged through the plate-like fins and through which a working fluid flows in a flat cross section A heat transfer tube bent into a shape, a header in which an end of the heat transfer tube communicates, and an inflow tube and an outflow tube for working fluid are connected, and a space provided in the header and communicated from the inflow tube to the heat transfer tube And a first longitudinal partition plate in the header longitudinal direction that separates the space communicating from the heat transfer tube to the outflow tube, and the adjacent U-shaped heat transfer tube , and air flows in the header inner space. a second vertical partition plate of the header longitudinal separating opposite direction, both end portions of the heat transfer tube of the U-shaped and a lateral partition plate that separates at the header space, said header space Gas is generated by the first and second vertical partition plates. It separates into a windward flow path and a leeward flow path with respect to the flow direction, and the working fluid flow in the header longitudinal direction is divided by the horizontal partition plate, and the working refrigerant flowing in from the inflow pipe serves as an evaporator. When using, when it flows through the windward flow path of the heat transfer tube of the flat cross section and reaches the end space of the header, it flows through the leeward flow path of the heat transfer tube and flows out of the outflow pipe in the air flow direction. In contrast, when used as a condenser, when it is used as a condenser, it flows through the leeward flow path of the heat transfer tube having the flat cross section and reaches the end space of the header, and then flows through the windward flow path of the heat transfer tube. A heat exchanger characterized in that it flows out of the outflow pipe and becomes a counterflow with respect to the air flow direction .   2. The flow path cross-sectional area is different for each region separated by the vertical partition plate in a plurality of flow paths in which a working fluid separated by a partition flows inside the heat transfer tube. Heat exchanger.   The heat exchanger according to claim 1, wherein the U-shaped heat transfer tubes are arranged in a plurality of rows in the gas flow direction.   The heat exchanger according to any one of claims 1 to 3, wherein a flow path cross-sectional area in the header is equal to or less than a sum of flow path cross-sectional areas of the heat transfer tubes.   The heat according to any one of claims 1 to 3, wherein a through hole through which the heat transfer tube communicates with the header and a fitting groove into which the heat transfer tube is inserted and locked are formed in the vertical partition plate. Exchanger.   6. The plate-like fin has a cut-and-raised portion between the heat transfer tubes, and the cut-and-raised portion is not located at the center of the long axis of the flat heat transfer tube. Heat exchanger.   7. At least a compressor, a condenser, a throttle device, and an evaporator are connected sequentially by piping, and a refrigerant is used as a working fluid, and the heat exchanger according to claim 1 is used as the evaporator or the condenser. An air conditioner characterized by being used as a container.   The air conditioner according to claim 7, wherein the refrigerant is a single HC refrigerant or a mixed refrigerant containing HC, R32, ammonia, or carbon dioxide.

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