Patent Grant
10900721
This application is a U.S. national stage application of International Application No. PCT/JP2016/079942, filed on Oct. 7, 2016, the contents of which are incorporated herein by reference.
The present invention relates to a heat exchanger and an air-conditioning apparatus provided with the same.
Heat exchangers each include a heat-exchanger core in which heat transfer tubes are inserted into stacked flat fins, and efficiently cause heat exchange to be performed between refrigerant flowing through the heat transfer tubes and outdoor air in the heat-exchanger core. As examples of the heat transfer tubes, for example, cylindrical tubes and flat tubes are present. The cylindrical tubes have a circular cross-section, and the flat tubes have a cross section formed in the shape of a rectangle having rounded corners. In the following description, a heat exchanger including cylindrical tubes will be referred to as “cylindrical-tube heat exchanger”, and a heat exchanger including flat tubes will be referred to as “flat-tube heat exchanger”.
As a method for manufacturing a heat-exchanger core of a flat-tube heat exchanger, it is known that heat transfer tubes are press-fitted into U-shaped cuts of flat fins, the U-shaped cuts being each in a width direction of each flat fin from one side thereof. In some of the flat-tube heat exchangers, such heat-exchanger cores as described above are joined to each other in the width direction of flat fins, whereby the heat-exchanger cores are combined into a single heat exchanger (for example, Patent Literature 1 e).
Patent Literature 1: Japanese Patent No. 4845943
In each of such heat exchangers as described above, heat-exchanger cores are joined to each other in the width direction of fins, thereby forming a single heat exchanger. However, the heat-exchanger cores are displaced from each other.
The present invention has been made to solve the above problem, and an object of the invention is to reduce or prevent the displacement of heat-exchanger cores.
In a heat exchanger according to an embodiment of the present invention which includes a plurality of heat-exchanger cores each including flat fins arranged in a direction in which passages provided in heat transfer tubes extend, recesses formed in at least one of the heat-exchanger cores and protrusions of another one of the heat-exchanger cores are engaged with each other.
In the heat exchanger according to the embodiment of the present invention, protrusions of a heat-exchanger core are fitted in recesses of another heat-exchanger core, thereby reducing or preventing displacement of the heat-exchanger cores.
A heat exchanger according to the present invention includes a plurality of heat-exchanger cores joined to each other. In the heat exchanger, when the heat-exchanger cores are joined to each other, they are prevented from being displaced from each other, or such displacement is reduced.
Embodiment 1 of the present invention will be described below. With respect to embodiment 1, a heat exchanger including flat heat transfer tubes and an outdoor unit of an air-conditioning-apparatus provided with the heat exchanger will be described.
The configuration of an outdoor unit 1 of an air-conditioning apparatus will be described.
The outer casing of the outdoor unit 1 includes front panels 10 corresponding to a front surface of the outer casing, side panels 11 corresponding to side surfaces of the outer casing, and a fan guard 12 provided on an upper portion of the outdoor unit 1. The side panels 11 each include an air inlet 13 through which air is taken into the outdoor unit 1. The fan guard 12 includes an air outlet 14 through which air is discharged out of the outdoor unit 1.
A fan is provided in the fan guard 12 on the upper portion of the outdoor unit 1. The fan takes air into the outdoor unit 1 through the air inlet 13, and discharges the taken air from the outdoor unit 1 to the outside thereof through the air outlet 14. The fan is surrounded by the fan guard 12. By virtue of this configuration, air taken in the outdoor unit 1 through the air inlet 13 passes through the heat exchanger 2, and is then is discharged from the outdoor unit 1 to the outside thereof through the air outlet 14.
In the outdoor unit 1, the heat exchanger 2, a base panel 20, a compressor 21 and an accumulator 22 are provided. The base panels 20 supports the heat exchanger 2, etc. The compressor 21 compresses refrigerant. The accumulator 22 stores surplus refrigerant.
The base panel 20 corresponds to the bottom of the outer casing of the outdoor unit 1. The components provided in the outdoor unit 1 are screwed to the base panel 20 and thus supported thereby. The compressor 21 compresses the refrigerant and discharges it, and is provided on the base panel 20. In a cooling operation, a refrigerant discharge side of the compressor 21 is connected to the heat exchanger 2, and in a heating operation, the refrigerant discharge side is connected to a heat exchanger included in an indoor unit not illustrated. The accumulator 22 stores surplus liquid refrigerant, and is connected to a refrigerant suction side of the compressor 21.
The heat exchanger 2 according to embodiment 1 of the present invention includes heat-exchanger cores 3 and 4 in each of which flat tubes are inserted in flat fins. That is, the heat-exchanger cores 3 and 4 are joined to each other in the width direction of the flat fins to form the heat exchanger 2. The flat tubes are each bent in the U-shape. One end of each of the flat tubes is a hairpin portion having a U-shape, and the other end thereof is a cut portion formed in the shape of the cross-section of the flat tube.
Each flat tube is, for example, a flat multi-hole tube containing a plurality of refrigerant passages. Preferably, the flat tube should be formed of corrosion-resistant metal having good heat conductivity. For example, the flat tube can be considered formed of aluminum or copper. The flat tube through which a fluid, such as refrigerant, flows, has an elongated cross-section, as a result of which a contact area between the refrigerant and the heat transfer tube can be increased without increasing the resistance to air passing through the heat exchanger. As a result, even if the heat exchanger is made smaller, it can obtain a sufficient heat exchange performance.
The heat-exchanger core 30a provided with the recesses includes heat transfer tubes 33a and a fin body 32a in which flat fins 31a are arranged. Each of the flat fins 31a has a plurality of cuts 34a which are spaced apart from each other and arranged at regular intervals, and which are formed on one side of each flat fin 31a which is located at one end in a longitudinal direction thereof, and further includes a plurality of recesses 35a formed on the other side of each flat fin 31a, which is located opposite to the above one side. The cuts 34a are elongated and allow the heat transfer tubes 33a to be inserted into the cuts 34a. The recesses 35a are forward or backward offset relative to the cuts 34a by half a pitch P of the cuts 34a, that is, by ½P, in a direction in which the cuts 34a are arranged. The recesses 35a are semicircular. The flat fins 31a are arranged in a direction in which the passages in the heat transfer tubes 33a extend (or in a direction perpendicular to the plane of
The heat-exchanger core 40a having protrusions 45a has the same configuration as or a similar configuration to that of the heat-exchanger core 30a, except for the configurations of both end portions of the flat fins in a direction along the long sides thereof. The heat-exchanger core 40a includes heat transfer tubes 43a and a fin body 42a in which flat fins 41a are arranged. Other-end portions of the heat transfer tubes 43a protrude from cuts 44a, and serve as semicircular protrusion portions 47a. The protrusion portions 47a form the protrusions 45a which fit in the recesses 35a of the heat-exchanger core 30a.
In the heat exchanger 100 having the above configuration, the semicircular protrusions 45a, which are the protrusion portions of the heat transfer tubes 43a in the heat-exchanger core 40a, fit in the semicircular recesses 35a provided in the heat-exchanger core 30a, whereby the heat-exchanger core 30a and the heat-exchanger core 40a are joined to each other to have a desired positional relationship.
In the above case, the recesses 35a of the heat-exchanger core 30a are forward or backward offset relative to the cuts 34a by half the pitch P of the cuts 34a, i.e., ½P, in the direction in which the cuts 34a are arranged. Since the protrusions 45a of the heat-exchanger core 40a fit in the recesses 35a, the positional relationship between the heat transfer tubes 33a of the heat-exchanger core 30a and the heat transfer tubes 43a of the heat-exchanger core 40a are arranged in a staggered manner.
The heat transfer tubes and the flat fins of each heat-exchanger core are joined by, for example, brazing or bonding. Cladding material including a layer of a brazing material is applied to the heat transfer tubes or the flat fins or both the heat transfer tubes and the flat fins, to thereby join them to each other by brazing. If material which does not contain a brazing material layer is used, a brazing material or an adhesive is applied, and the heat transfer tubes and the flat fins are joined by brazing or bonding. In a joining method using brazing, the heat transfer tubes are joined to the flat fins by furnace brazing in which brazing is performed in a high-temperature atmosphere furnace.
Contact part of each flat fin to be in contact with an associated heat transfer tube is formed to include raised part which is called a fin collar or a burr, and is raised from a flat surface of the fin. Thereby, the heat transfer tubes are more firmly joined by brazing to or bonded to the flat fins.
A method of assembling the heat exchanger 100 will be described. The heat exchanger 100 is assembled by stacking a plurality of heat-exchanger cores together in the column direction as indicated in
In joining the heat transfer tubes 33a to the flat fins 31a and joining the heat transfer tubes 43a to the flat fins 41a, there is a case where the heat-exchanger core 30a and the heat-exchanger core 40a are joined to each other by a brazing material or an adhesive. If the heat-exchanger core 30a and the heat-exchanger core 40a are joined together, it is impossible to attach components between the heat-exchanger cores. Furthermore, when the assembled heat exchanger 100 are bent into a substantially U-shape or L-shape, displacement of the heat-exchanger cores in a direction where the fins are arranged occurs, since the heat-exchanger cores have different bend radii. In this case, if the heat-exchanger core 30a and the heat-exchanger core 40a are joined together, displacement of the heat-exchanger cores is reduced or prevented, and it is therefore hard to bend the heat exchanger into a substantially U-shape or L-shape.
As a method of preventing the heat-exchanger core 30a and the heat-exchanger core 40a from being joined together, there is provided a method of inserting a joining prevention sheet between the heat-exchanger cores. In the case where the above joining is performed by the furnace brazing, if as the above joining prevention sheet, a joining prevention sheet containing carbon fiber is used, and can be removed after the joining is performed by the furnace brazing. By virtue of use of the joining prevention sheet, the heat-exchanger core 30a and the heat-exchanger core 40a can be assembled into the heat exchanger such that the heat-exchanger cores are not joined together.
The assemblage of the heat exchanger 100 is performed on a workbench or a platform car. The heat-exchanger core 30a is connected to the heat-exchanger core 40a by attaching components for connecting the heat transfer tubes 33a and 43a together to cut portions of the heat transfer tubes 33a and 43a. As connection methods, the following methods are present: U-bend connection for connecting a pair of heat transfer tubes; header-connection; and distributor-connection. In the header-connection or distributor-connection, a main passage is connected to heat transfer tubes. To connect a cut end of a flat tube to, for example, a header, a distributor, or a cylindrical tube, an element called a joint which switches the passage to be used from the cylindrical tube to the flat tube may be used.
These connecting elements are attached to the heat transfer tubes by the furnace brazing, burner brazing in which a base material and a brazing material are burned with flames from a burner, or high-frequency brazing.
In a conventional heat exchanger, in the case of assembling a plurality of heat-exchanger cores, it is necessary to accurately position the heat-exchanger cores by joining sides of flat fins of the heat-exchanger cores, which extend in the width direction of the fins, or joining hairpin portions and cut ends of heat transfer tubes of the heat-exchanger cores. Therefore, the heat-exchanger cores are assembled using a positioning plate or jig.
Furthermore, even after the heat-exchanger cores are assembled and positioned, in the case where they are subjected to brazing, they are displaced from each other. It is therefore necessary to reduce displacement of the heat-exchanger cores by using the same positioning jig as in assemblage of the heat-exchanger cores, or another positioning jig, or connecting members.
The heat exchanger 100 according to embodiment 1 includes the heat-exchanger cores 30a and the heat-exchanger core 40a. The heat-exchanger core 30a includes the cuts 34a each of which is formed on one side of an associated one of the flat fins 31a, and which allow the heat transfer tubes 33a to be inserted into the cuts 34a, and the recesses 35a each of which is formed on the other side of the associated one of the flat fins 31a. The heat-exchanger core 40a includes the protrusions 45a each of which is formed on an associated one of the flat fins 41a, and which fit in the recesses 35a. By virtue of this configuration, since the protrusions 45a fit in the recesses 35a, it is possible to reduce or prevent displacement of the heat-exchanger cores, and easily position the heat-exchanger cores of the heat exchanger 100. Therefore, the heat-exchanger cores are easily positioned and assembled into the heat exchanger 100 without using a positioning plate or jig.
The recesses 35a are formed by partially cutting the flat fins 31a, and the protrusions 45a correspond to the protrusion portions 47a of the heat transfer tubes 43a. Thus, the number of elements for connecting the heat-exchanger cores or connecting the heat exchanger and a housing can be reduced. It is therefore possible to facilitate assemblage of components, reduce the time required for assemblage of the components, and also reduce the cost.
Furthermore, it is possible to reduce displacement of the heat-exchanger cores after they are assembled, and thus reduce the number of components for connecting the assembled heat-exchanger cores to each other. Also, it is possible to reduce deterioration of the performance of the heat exchanger 100, since staggered arrangement of the heat-exchanger cores is not broken. Because of this staggered arrangement of the heat-exchanger, air passing through an area of the inside of the heat exchanger 100, which is located outside the heat transfer tubes, is stirred, and results in turbulent flow. As a result, the coefficient of heat transfer of the heat exchanger 100 is improved.
The amount of protruding of the protrusion 45a corresponding to the protrusion portion 47a of the heat transfer tube 43a in embodiment 1 will be described.
In the case of using cylindrical tubes, unlike flat tubes, the cylindrical tubes have an outer periphery including no linear portion, and thus satisfy I/L 0.5 in order that a plurality of heat-exchanger cores be engaged with each other. In the case of using flat tubes, they have an outer periphery including linear portions, and can thus be manufactured in such a way as to satisfy I/L<0.5.
As indicated in the characteristic view of
By virtue of the above configuration, it is possible to facilitate positioning of the heat-exchanger cores while maintaining the performance of the heat exchanger 100.
In embodiment 1, all the heat transfer tubes 33a and 43a of the heat-exchanger cores 30a and 40a protrude from the flat fins. On the other hand, in embodiment 2, only one or more of heat transfer tubes protrude from flat fins, and serve as protrusion portions.
In a heat-exchanger core 30b having a recess or recesses, recesses 35b are not provided in respective spaces between a plurality of cuts 34b; i.e., one or more recesses 35b are intermittently provided, and arranged at positions which are offset relative to associated cuts 34b by the half the pitch P of the plurality of cuts 34b, that is, ½P, in the direction in which the cuts 34b are arranged. Furthermore, in a heat-exchanger core 40b, a protrusion or protrusions 45b, which fit in the recess or recesses 35b, are formed to face the recess or recesses 35b. In the heat-exchanger cores 30b and 40b, the cuts each have a depth equal to the length of the major axis of the cross-section of each of the heat transfer tubes. The heat transfer tubes 33b and 43b are inserted in the cuts 34b and 44b such that one end of each of the heat transfer tubes 33b and 43b is in contact with an associated one of deepest portions 36b and 46b of the cuts 34b and 44b, and each of arcuate portions 38b and 48b of the heat transfer tubes 33b and 43b do not protrude from an associated one of the cuts 34b and 44b. However, the cut 44b located in the position of the protrusion or protrusions 45b is shallower than the other cuts in such a manner that an associated heat transfer tube 43b protrudes from the cut 44b.
As described above, the cuts other than the cut for the protrusion or protrusion 45b each have a depth equal to the length of the major axis of the cross-section of the heat transfer tubes, such that each of the arcuate portions 38b and 48b do not protrude from the associated one of the cuts 34b and 44b; however, they may each have a depth which is greater than or equal to the length of the major axis of the cross-section of the heat transfer tubes such that so that each of the arcuate portions 38b and 48b do not protrude from the associated one of the cuts 34b and 44b.
Furthermore, in the above configuration, the cut 44b located in the position of the protrusion or protrusions 45b is shallower than the other cuts, such that the associated heat transfer tube 43b protrudes from the cut 44b; however, it may have the same depth as that of each of the other cuts, and the associated heat transfer tube 43b may be inserted into the cut 44b such that one end of the heat transfer tube 43b is located away from the deepest portion 46b of the cut 44b, and as a result the arcuate portion 48b of the associated heat transfer tube 43b, that is, the other end thereof, protrudes from the cut 44b.
In the heat exchanger 200 having the above configuration, the protrusion or protrusions 45b, which are protrusion portions of the heat transfer tube 43b of the heat-exchanger core 40b, and have a semicircular shape, fit in the recess or recesses 35b intermittently provided in the heat-exchanger core 30b and having a semicircular shape, whereby the heat-exchanger core 30b and the heat-exchanger core 40b are joined to each other to have a desired positional relationship.
In the above configuration, the recess or recesses 35b of the heat-exchanger core 30b are displaced from associated cuts 34b by half the pitch P of the cuts 34b, i.e., ½P, in the direction in which the cuts 34b are arranged. Since the protrusion or protrusions 45b of the heat-exchanger core 40b fit in the recess or recesses 35b, the heat transfer tubes 33b of the heat-exchanger core 30b and the heat transfer tubes 43b of the heat-exchanger core 40b are arranged in a staggered manner.
In the heat exchanger 200 according to embodiment 2, the cuts 34b and 44b each have a depth equal to the length of the major axis of the cross-section of each of the heat transfer tubes 33b and 43b. The heat transfer tubes 33b and 43b are inserted in the cuts 34b and 44b such that one end of each of the heat transfer tubes 33b and 43b is in contact with the associated one of the deepest portions 36b and 46b of the cuts 34b and 44b, and each of the arcuate portions 38b and 48b does not protrude from the associated one of the cuts 34b and 44b. Thus, the length l of each of the contact area between the heat transfer tube 33b and the flat fin 31b and the contact area between the heat transfer tube 43b and the flat fin 41b is greater than that in the configuration in embodiment 1 in which the heat transfer tubes 33b and 43b protrude from the flat fins 31b and 41b. Therefore, the amount of heat transferred from the heat transfer tubes 33b and 43b to the flat fins 31b and 41 is increased, thus improving the heat exchange performance of the heat exchanger 200.
The heat-exchanger cores are assembled such that the semicircular protrusion or protrusions 45b, which are the protrusion portions of the heat transfer tubes 43b of the heat-exchanger core 40b, fit in the semicircular recess or recesses 35b intermittently provided in the heat-exchanger core 30b. When the heat-exchanger cores are being assembled, if the protrusion 45b and the recess 35b are displaced from each other, they are not engaged with each other. It is therefore possible to prevent the heat-exchanger cores from being assembled at incorrect positions.
In Embodiment 1, the two heat-exchanger cores both include recesses. By contrast, in embodiment 3, one of heat-exchanger cores joined to each other has no recess, since a further heat-exchanger core is not joined to the above one of the heat-exchanger cores.
A heat-exchanger core 30c having recesses is configured as follows: recesses 35c are located in respective spaces between cuts 34c and at respective positions which are offset relative to the cuts 34c by half the pitch P of the cuts 34c, that is, ½P, in a direction in which the cuts 34c are arranged. The cuts 34c each have a depth equal to the length of the major axis of the cross-section of heat transfer tubes 33c. The heat transfer tubes 33c are inserted in the cuts 34c such that that one side of each of the heat transfer tubes 33c is in contact with the deepest portion 36c of an associated one of the cuts 34c, and the arcuate portion 38c of each heat transfer tube 33c does not protrude from the associated cut 34c. By contrast, a heat-exchanger core 40c having protrusions has no recess on the opposite side of a side on which cuts 44c are arranged. That is, the heat-exchanger core 40c has a linearly flat side. Heat transfer tubes 43c are formed such that one end of each of the heat-transfer tubes 43c is in contact with the deepest portion 46c of an associated one of the cuts 44c, and arcuate portions 48c of the heat transfer tubes 43c protrude from the cuts 44c to form protrusions 45c of the heat-transfer core 40c.
In the heat exchanger 300 having the above configuration, the protrusions 45c, which are semicircular and correspond to protrusion portions of the heat transfer tubes 43c of the heat-exchanger core 40c, fit in the recesses 35c, which are semicircular and located in respective spaces between the cuts 34c in the heat-exchanger core 30c, whereby the heat-exchanger core 30c and the heat-exchanger core 40c are joined to each other to have a desired positional relationship.
In this case, in a direction in which the cuts 34 are arranged, the recesses 35c of the heat-exchanger core 30c are located at respective positions which are offset relative to the cuts 34c by half the pitch P of the cuts 34c, that is, ½P. Since the protrusions 45c of the heat-exchanger core 40c fit in the recesses 35c, the positional relationship between the heat transfer tubes 33c of the heat-exchanger core 30c and the heat transfer tubes 43c of the heat-exchanger core 40c are arranged in a staggered manner.
In the heat exchanger 300 according to embodiment 3, the heat-exchanger core 40c has no recess on the opposite side of the side on which the cuts 44c are arranged. This configuration is highly resistant to the pressure acting on the opposite side of the side in which the cuts 44c of flat fins 41c are arranged, thus reducing or preventing deformation or falling of the flat fins 41c and flat fins 31c.
The cuts 34c each have a depth equal to the length of the major axis of the cross-section of the heat transfer tubes 33c. The heat transfer tubes 33c are inserted in the cuts 34c such that one end of each of the heat transfer tubes 33c is in contact with the deepest portion 36c of the associated one of the cuts 34c, and each of the arcuate portions 38c thereof does not protrude from the associated one of the cuts 34c. Thus, the length l of the contact area between the heat transfer tube 33c and the flat fin 31c is greater than that in a configuration in which the heat transfer tube 33c protrudes from the flat fin 31c. Therefore, the amount of heat transferred from the heat transfer tube 33c to the flat fin 31c is increased, thus improving the heat exchange performance of the heat exchanger 300.
In embodiments 1 to 3, the recesses are semicircular. However, the shape of the recesses is not limited to the semicircular shape. The recesses may be rectangular or V-shaped.
Also, it is described above that the protrusions are the protrusion portions of the heat transfer tubes. The flat fins may be formed to include protrusion portions, and the protrusion portions may be applied as the above protrusions.
The number of recesses provided in the heat-exchanger core having a recess or recesses, whether or not the heat-exchanger core includes a recess or recesses, and whether or not the heat-exchanger core including a protrusion or protrusions includes a recess or recesses are not limited to those of the above configurations. On this point, the above configurations may be combined.
In the heat exchanger 100 according to embodiment 1, the heat-exchanger core 30a which is a first heat-exchanger core having recesses and the heat-exchanger core 40a which is a second heat-exchanger core having protrusions are joined to each other. By contrast, in a heat exchanger 400 according to embodiment 4, a heat-exchanger core 50a which is a third heat-exchanger core having protrusions and a heat-exchanger core 60a which is a fourth heat-exchanger core having recesses are joined to each other.
The heat-exchanger core 50a having the protrusions includes a fin body 52a in which flat fins 51a are provided, and heat transfer tubes 53a. Each of the flat fins 51a has a plurality of cuts 54a which are provided in one of sides extending in a longitudinal direction, and which are arranged at regular intervals, and rectangular protrusions 55a which are provided on the other side, i.e., the opposite side of the above one side. The cuts 54a are elongated and allow the heat transfer tubes 53a to be inserted into the cuts 54a. The protrusions 55a are rectangular, and are located at respective positions which are offset relative to the cuts 54a by half the pitch P of the cuts 54a, i.e., ½P, in a direction in which the cuts 54a are arranged. The flat fins 51a are arranged in a direction in which passages provided in the heat transfer tubes 53a extend (or in a direction perpendicular to the plane of
The heat-exchanger core 60a having the recesses has the same configuration as or a similar configuration to that of the heat-exchanger core 50a, except for the both ends of the flat fins in the longitudinal direction thereof. The heat-exchanger core 60a includes a fin body 62a in which flat fins 61a are provided, and heat transfer tubes 63a. Cuts 64a each have a depth greater than the length of the major axis of the cross-section of each of the heat transfer tubes 63a. In each of the cuts 64a, arcuate portion 68a of the heat transfer tube 63a and one side of the fin body 62a define a recess 65a as in the heat-exchanger core 50a.
In the heat exchanger 400 having the above configuration, the protrusions 55a provided on the heat-exchanger core 50a fit in the recesses 65a of the heat-exchanger core 60a, whereby the heat-exchanger core 50a and the heat-exchanger core 60a are joined to each other to have a desired positional relationship.
In the above configuration, in the direction in which the cuts 54a are arranged, the protrusions 55a of the heat-exchanger core 50a are located at respective positions which are offset relative to the cuts 54a by half the pitch P of the cuts 54a, i.e., ½P. Since the protrusions 55a fit in the recesses 65a of the heat-exchanger core 60a, the heat transfer tubes 53a of the heat-exchanger core 50a and the heat transfer tubes 63a of the heat-exchanger core 60a are alternately arranged in a staggered manner.
The heat exchanger 400 according to embodiment 4 includes the heat-exchanger core 50a and the heat-exchanger core 60a. The heat-exchanger core 50a includes the cuts 54a which are provided on the one-end sides of the flat fins 51a, and into which the heat transfer tubes 53a are inserted, and the recesses 55a which are rectangular and provided on the other-end sides of the flat fins 51a. The heat-exchanger core 60a includes the recesses 65a which are provided on the one-end side of the flat fins 61a, and in which protrusions 55a fit. It is therefore possible to obtain the heat exchanger 400 in which the heat exchanger cores are easily positioned. Also, it is possible to easily assemble the heat exchanger 400 such that the heat exchange cores maintain a desired positional relationship, without using a positioning plate or a jig.
Furthermore, the protrusions 55a and each flat fin 51a are formed integrally with each other, and in each cut 64a, the recess 65a is defined by the arcuate portion 68a of the heat transfer tube 63a and one side of the fin body 62a. It is therefore possible to reduce the number of elements for connecting the heat-exchanger cores together or connecting the heat exchanger and a housing. Thus, it is possible to facilitate assemblage, and reduce the time required for assemblage and the cost.
The cuts 54a each have a depth greater than the length of the major axis of the cross-section of the heat transfer tubes 53a, and the heat transfer tubes 53c are inserted in the cuts 54c such that the heat transfer tubes 53c do not protrude from the cuts 54c. Therefore, the length l of the contact area between the heat transfer tube 53c and the flat fin 51c is greater than that in a configuration in which the heat transfer tube 53c protrudes from the flat fin 51c. Therefore, the amount of heat transferred from the heat transfer tube 53c to the flat fin 51c is increased, thus improving the heat exchange performance of the heat exchanger 400. In addition, since the flat fins 51c and the flat fins 61a include the rectangular protrusions, the effective heat transfer area is larger, thus improving the heat exchange performance of the heat exchanger 400.
In embodiment 4, the two heat-exchanger cores both have the protrusions. By contrast, in embodiment 5, a heat-exchanger core 60b, which is one of heat-exchanger cores joined to each other, has no protrusion on the opposite side of a side on which recesses 65b are arranged, since a further heat-exchanger core is not joined to the heat-exchanger core 60b.
A heat-exchanger core 50b having protrusions is configured such that protrusions 55b are located in respective spaces between cuts 54b and in respective positions which are offset relative to the cuts 54b by half the pitch P of the cuts 54b, i.e., ½P, in a direction in which the cuts 54b are arranged. The heat-exchanger core 60b having recesses has no protrusion on the opposite side of a side on which cuts 64b are provided. In other words, the heat-exchanger core 60b has a linear flat side. In the heat-exchanger cores 50b and 60b, the cuts each have a depth greater than the length of the major axis of the cross-section of the heat transfer tubes, and the heat transfer tubes are inserted in the cuts such that one end of each of the heat transfer tubes is in contact with the deepest portion of an associated one of the cuts. Therefore, in each heat transfer tube, an arcuate portion, which is the other end of the each transfer tube, does not protrude from the associated cut, and is located inward of one side of a fin body. In the cut, the arcuate portion of the heat transfer tube and the one side of the fin body define a recess.
In the heat exchanger 500 having the above configuration, the protrusions 55b provided on the heat-exchanger core 50b fit in the recesses 65b of the heat-exchanger core 60b, whereby the heat-exchanger core 50b and the heat-exchanger core 60b are joined to each other to have a desired positional relationship.
In the heat exchanger 500 according to embodiment 5, the heat-exchanger core 60b has no protrusion on the side opposite of the side on which the cuts 64b are arranged. Such a configuration is highly resistant to the pressure acting on the opposite side of the side on which the cuts 64b of flat fins 61b are arranged, and can thus prevent or reduce deformation and falling of the flat fins 61b and flat fins 51b.
In embodiments 4 and 5, the protrusions 55a and 55b are rectangular, but their shapes are not limited to the rectangular shape. The protrusions may be formed semicircular or V-shaped.
As described above, the cuts of the heat-exchanger cores each have a depth greater than the length of the major axis of the cross-section of the heat transfer tubes. In the heat-exchanger cores 50a and 50b having the protrusions, it is not indispensable that the recess is defined by the arcuate portion of the heat transfer tube and one side of the fin body in each of the cuts 54a and 54b. For example, the cuts 54a and 54b may be formed to have a depth greater than or equal to the length of the major axis of the cross-section of each of the heat transfer tubes 53a and 53b.
In embodiments 1 to 5, the recesses and protrusions formed at the flat fins are provided by cutting part of the flat fins. By contrast, in embodiment 6, at recesses provided in each of flat fins, fin collars are formed in such a way as to be raised from a flat surface of the fin.
In a heat-exchanger core having semicircular recesses 35a, at peripheries of the recesses 35a, fin collars 70 are raised from a flat surface of the fin.
When the heat-exchanger core 30a, which is a first heat-exchanger core having recesses, and the heat-exchanger core 40a, which is a second heat-exchanger core having protrusions, are joined to each other, the protrusions 45a which are the protrusion portions 47a of the heat transfer tubes 43a are fitted into the recesses 35a having the fin collars 70. Thereby, the fin collars 70 come into contact with the heat transfer tubes 43a.
While the fin collars 70 are in contact with the heat transfer tubes 43a, furnace brazing is performed, as a result of which the recesses 35a having the fin collars 70 are brazed to the protrusions 45a which are the protrusion portions 47a of the heat transfer tubes 43a.
When the fin collars 70 come into contact with the heat transfer tubes 43a, the contact area between the flat fins 31a and the heat transfer tubes 43a increases, thereby increasing a heat transfer area, and thus also increasing the amount of heat transfer. Therefore, the heat exchange performance of the heat exchanger 600 can be improved.
In addition, since the recesses 35a are brazed to the protrusions 45a, the heat exchange performance can be enhanced.
Although embodiment 6 is described above by referring to the case where the heat exchanger 100 according to embodiment 1 is applied, it is not limited to such a case, and the heat exchanger according to embodiment 6 may have any configuration so long as the heat-exchanger core has recesses provided with fin collars.
It is described above that in all embodiments 1 to 6 of the present invention, the heat transfer tubes are provided in a staggered manner such that the heat transfer tubes are offset relative to each other by half the distance between the cuts in the direction in which the cuts are arranged. However, it is not indispensable that the distance by which the heat transfer tubes are offset relative to each other is half the distance between the cuts. Each of the heat transfer tubes may be aligned with an associated one of the heat transfer tubes.
Furthermore, although the heat exchanger including the flat tubes and the air-conditioning-apparatus outdoor unit including the heat exchanger are described above, the heat transfer tubes are not limited to flat tubes. The heat exchanger may be a heat exchanger including cylindrical tubes or a heat exchanger including a combination of flat tubes and cylindrical tubes. In this case, it is preferable that cuts be shaped such that contact areas between the cylindrical tubes and the flat fins are large.
In addition, although in the above configurations, only two heat-exchanger cores are provided, needless to say, the present invention is also applicable to a case where three or more heat-exchanger cores are joined to each other.
The heat exchanger according to the present invention can be widely used as heat exchangers of air-conditioning apparatuses for domestic use and business use, etc.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2016/079942 | 10/7/2016 | WO | 00 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2018/066123 | 4/12/2018 | WO | A |
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| Number | Date | Country | |
|---|---|---|---|
| 20190242659 A1 | Aug 2019 | US |
