JP2016114282A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress a drift current of a refrigerant in a heat exchanger including a refrigerant header extending horizontally and a flat porous pipe.SOLUTION: A heat exchanger includes: a refrigerant header 51 extending in the horizontal direction; and a plurality of flat porous pipes 40 extending in the horizontal direction orthogonal to a header longitudinal direction. In the refrigerant header 51, a nozzle hole EN1 is formed. A plurality of holes 41 of the flat porous pipe 40 are arrayed in the vertical direction. An internal space IS10 of the refrigerant header 51 is partitioned into a first chamber IS 11 on the nozzle hole EN1 side and a second chamber IS12 different from that, by a vertical partition plate 69 extending in the header longitudinal direction. One part of the refrigerant entered the first chamber IS11 from the nozzle hole EN1 flows to the second chamber IS12 from the first chamber IS11, and returns to the first chamber IS11 from the second chamber IS 12 again.SELECTED DRAWING: Figure 7

Description

  The present invention relates to a heat exchanger, and more particularly to a heat exchanger having a structure in which a plurality of flat multi-hole tubes are connected to a refrigerant header.

  Conventionally, there is a heat exchanger using a flat multi-hole tube which is a flat tube having a large number of holes. For example, the heat exchanger disclosed in FIG. 4 of Patent Document 1 (Japanese Patent Application Laid-Open No. 2014-142165) is a stacked heat exchanger in which a flat multi-hole tube is horizontally disposed from a horizontally extending refrigerant header. It is extended and heat exchange is performed between the refrigerant flowing through the flat multi-hole tube and the water flowing through the flat tube.

  However, in a heat exchanger having a structure in which a refrigerant header is arranged along the horizontal direction and a plurality of holes of the flat multi-hole tube are arranged along the vertical direction, the heat exchange target is cooled by evaporating the refrigerant. In this case, the gas-liquid two-phase refrigerant that has entered the internal space of the refrigerant header drifts, and often flows into each hole of the flat multi-hole tube in a state where the liquid phase and the gas phase are biased. When such a drift of the refrigerant in the refrigerant header occurs, the performance of the heat exchanger decreases.

  An object of the present invention is to suppress refrigerant drift in a heat exchanger that includes a refrigerant header extending along a horizontal direction and a flat multi-hole tube having a plurality of holes arranged along the vertical direction.

  The heat exchanger according to the first aspect of the present invention includes a refrigerant header and a plurality of flat multi-hole tubes. A refrigerant inlet is formed in the refrigerant header, and the refrigerant header extends along the horizontal direction. The flat multi-hole tube extends in a direction intersecting with the longitudinal direction of the header of the refrigerant header, and extends along the horizontal direction. The refrigerant flows into the flat multi-hole tube from the header. The plurality of holes of the flat multi-hole tube through which the refrigerant flows are arranged along the vertical direction. The internal space of the refrigerant header is partitioned into a first chamber on the refrigerant inlet side and a second chamber different from the first chamber by a partition plate extending in the header longitudinal direction. Then, at least a part of the refrigerant that has entered the first chamber from the refrigerant inlet flows from the first chamber to the second chamber and returns again from the second chamber to the first chamber.

  Here, the refrigerant that has entered the internal space of the refrigerant header from the refrigerant inlet flows into each hole of the plurality of flat multi-hole tubes, and performs heat exchange with the fluid flowing outside the flat multi-hole tubes. Here, when the refrigerant is in a two-phase state in which the gas phase and the liquid phase are mixed, since the refrigerant header extends along the horizontal direction, if there is no partition plate, the internal space is close to the refrigerant inlet This causes a situation in which the refrigerant mainly becomes a liquid phase and the refrigerant far from the refrigerant inlet mainly becomes a gas phase. In such a situation, the multi-hole tube is divided into a flat multi-hole tube through which a large amount of liquid-phase refrigerant flows, and a flat multi-hole tube through which a large amount of gas-phase refrigerant flows.

  However, in the heat exchanger according to the first aspect, the internal space of the refrigerant header is divided into the first chamber and the second chamber by a partition plate extending in the header longitudinal direction. And the refrigerant | coolant header is comprised so that at least one part of the refrigerant | coolant which entered the 1st chamber from the refrigerant | coolant inlet may flow from the 1st chamber to the 2nd chamber, and may return to the 1st chamber from the 2nd chamber again. That is, in the internal space of the refrigerant header, a configuration in which a part of the refrigerant circulates (loops) is realized by the partition plate extending in the header longitudinal direction. Since such a configuration is adopted, the liquid-phase refrigerant reaches a position far from the refrigerant inlet along the circulating flow in the internal space of the refrigerant header, and the liquid phase / Less bias in the gas phase. When pulled, the drift of the refrigerant flowing through each flat multi-hole tube is also suppressed.

  A heat exchanger according to a second aspect of the present invention is the heat exchanger according to the first aspect, wherein the internal space of the refrigerant header has a first end opposite to the refrigerant inlet side in the header longitudinal direction. One opening is formed. The first opening allows the refrigerant to flow from the first chamber to the second chamber. Moreover, the 2nd opening is formed in the edge part by the side of the refrigerant | coolant inlet of the header longitudinal direction in the internal space of a refrigerant | coolant header. The second opening returns the refrigerant from the second chamber to the first chamber.

  Here, the first opening for flowing the refrigerant from the first chamber to the second chamber, and the second opening for returning the refrigerant from the second chamber to the first chamber are arranged on one end and the other end in the header longitudinal direction. It is arranged in the department. For this reason, the dead area where a refrigerant | coolant stagnates in the internal space of a refrigerant | coolant header becomes small, and it is suppressed that a liquid phase refrigerant | coolant retains in the internal space of a refrigerant | coolant header.

  The heat exchanger which concerns on the 3rd viewpoint of this invention is a heat exchanger which concerns on a 2nd viewpoint, Comprising: A refrigerant | coolant inlet_port | entrance is a nozzle with which the flow-path area was restrict | squeezed. The second opening is formed in the vicinity of the refrigerant inlet. And the flow of the refrigerant | coolant which returns to the 1st chamber from the 2nd opening through the 2nd opening will be in the low pressure state by the jet of the refrigerant which flows into the internal space of the refrigerant header from the refrigerant inlet. Arise.

  Here, since the refrigerant enters the internal space of the refrigerant header through the nozzle, the flow rate of the refrigerant increases. And the flow of the refrigerant | coolant from the 2nd chamber through the 2nd opening to the 1st chamber is produced | generated using the low pressure space produced in the vicinity of a nozzle (refrigerant inlet). For this reason, the circulation amount of the refrigerant in the internal space of the refrigerant header can be increased. That is, since a reduced pressure state is created by the venturi effect using the jet of refrigerant from the nozzle and the amount of refrigerant passing through the second opening disposed in the vicinity thereof is increased, the liquid phase / gas of the refrigerant in the internal space of the refrigerant header is increased. Phase bias is further reduced.

  The heat exchanger which concerns on the 4th viewpoint of this invention is a heat exchanger which concerns on either of the 1st-3rd viewpoints, Comprising: The partition plate has partitioned the internal space of the refrigerant | coolant header up and down. The first chamber is located below the second chamber. And the refrigerant | coolant of the internal space of a refrigerant | coolant header flows into the several hole of the lower part of a flat multi-hole pipe from a 1st chamber, and flows into the several hole of the upper part of a flat multi-hole pipe from a 2nd chamber.

  Here, the partition plate divides the internal space of the refrigerant header up and down so that the first chamber on the refrigerant inlet side is disposed below and the second chamber is disposed thereon. The holes of the flat multi-hole tube are exposed in both the first chamber and the second chamber, and not only from the first chamber on the refrigerant inlet side, but also from the second chamber to the hole of the flat multi-hole tube. Refrigerant flows. Since such a configuration is adopted, a large amount of refrigerant flows from the first chamber to the second chamber, and a part of the refrigerant returns from the second chamber to the first chamber again. As a result, the amount of refrigerant circulating in the internal space of the refrigerant header naturally increases, and the refrigerant drift is further suppressed.

  Moreover, in the heat exchanger which concerns on a 4th viewpoint, the drift of the refrigerant | coolant of the side near the refrigerant | coolant inlet of the internal space of a refrigerant | coolant header and the side far from a refrigerant | coolant inlet, ie, the refrigerant | coolant drift of the longitudinal direction of a refrigerant | coolant header is suppressed. In addition, since the partition plate divides the internal space of the refrigerant header vertically, it is possible to suppress the deviation of the refrigerant in the upper and lower portions of the internal space of the refrigerant header.

  The heat exchanger which concerns on the 5th viewpoint of this invention is a heat exchanger which concerns on either of the 1st-3rd viewpoints, Comprising: A partition plate divides the internal space of a refrigerant | coolant header into several holes of a flat multi-hole tube. Is partitioned into a first chamber in which no holes are exposed and a second chamber in which a plurality of holes of the flat multi-hole tube are exposed. Then, the refrigerant in the internal space of the refrigerant header flows into the plurality of holes of the flat multi-hole tube from the second chamber.

  Here, the partition plate is arranged so that the internal space of the refrigerant header is divided into the second chamber on the flat multi-hole tube side and the first chamber on the opposite side. The refrigerant that has entered the first chamber on the refrigerant inlet side first passes through the first chamber and then enters the second chamber, and then flows into the plurality of holes of the flat multi-hole tube. Since such a configuration is adopted, a large amount of refrigerant flows from the first chamber to the second chamber, and the refrigerant flows from the second chamber to the flat multi-hole tube. Then, a part of the refrigerant returns from the second chamber to the first chamber again. As a result, the amount of refrigerant circulating in the internal space of the refrigerant header naturally increases, and the refrigerant drift is further suppressed.

  The heat exchanger which concerns on the 6th viewpoint of this invention is a heat exchanger which concerns on a 5th viewpoint, Comprising: The refrigerant | coolant which returns to a 1st chamber from a 2nd chamber returns to a 1st chamber from the vicinity of the bottom face of a 2nd chamber. .

  First, when adopting a configuration in which the refrigerant flows from the first chamber to the second chamber and the refrigerant flows from the second chamber to the flat multi-hole tube, in the second chamber where the flow velocity is reduced, the liquid-phase refrigerant is in the lower part of the second chamber. It is also assumed that it stays in the area. In view of this, a structure is adopted here in which the refrigerant accumulated in the lower portion of the second chamber is returned from the vicinity of the bottom surface of the second chamber to the first chamber. Thereby, the quantity of the liquid-phase refrigerant | coolant which retains in the lower part of a 2nd chamber can be reduced. The liquid-phase refrigerant returned to the first chamber is mixed with the gas-phase refrigerant in the first chamber where the flow rate of the refrigerant is high, and flows to the flat multi-hole tube via the second chamber.

  The heat exchanger which concerns on the 7th viewpoint of this invention is a heat exchanger which concerns on either of the 1st-6th viewpoint, Comprising: The return | turnback refrigerant | coolant header different from a refrigerant | coolant header is further provided. The refrigerant header is a header to which a refrigerant inlet pipe is connected. The refrigerant flows into the internal space of the refrigerant header from the inlet pipe. The internal space of the folded refrigerant header is divided into a refrigerant inflow side internal space to which the flat multi-hole tube on the refrigerant inflow side is connected and a refrigerant outflow side internal space to which the flat multi-hole tube on the refrigerant outflow side is connected. The refrigerant outflow side internal space is partitioned into a third chamber on the refrigerant inflow side internal space side and a fourth chamber different from the third chamber by a partition plate extending in the header longitudinal direction. Then, at least a part of the refrigerant that has entered the third chamber from the refrigerant inflow side internal space flows from the third chamber to the fourth chamber, and returns from the fourth chamber to the third chamber again.

  In this heat exchanger, a folded refrigerant header is provided. However, when a heat exchanger in which the refrigerant is folded is used as an evaporator, the refrigerant dryness of the refrigerant when folded is generally high. However, not only the internal space of the refrigerant header but also the refrigerant outflow side internal space of the folded refrigerant header is divided into two chambers by the partition plate. And also in the refrigerant | coolant outflow side internal space of a return | turnback refrigerant | coolant header, the structure which a part of refrigerant | coolant circulates (loops) is implement | achieved by the partition plate extended in a header longitudinal direction. For this reason, even in the refrigerant outflow side internal space of the folded refrigerant header, the deviation of the liquid phase and gas phase of the refrigerant is reduced.

  According to the heat exchanger according to the first aspect of the present invention, the liquid-phase refrigerant reaches a position far from the refrigerant inlet along the circulating flow in the internal space of the refrigerant header, The deviation of the liquid phase and gas phase of the refrigerant is reduced, and the drift of the refrigerant flowing through each flat multi-hole tube is also suppressed.

  According to the heat exchanger according to the second aspect of the present invention, the liquid phase refrigerant is suppressed from staying in the internal space of the refrigerant header.

  According to the heat exchanger pertaining to the third aspect of the present invention, the refrigerant header is created because the reduced pressure state is created using the jet of refrigerant from the nozzle and the amount of refrigerant passing through the second opening disposed in the vicinity thereof is increased. The deviation of the liquid phase and gas phase of the refrigerant in the internal space of the interior space is further reduced.

  According to the heat exchanger according to the fourth aspect of the present invention, in addition to suppressing the refrigerant drift in the longitudinal direction of the refrigerant header, the partition plate partitions the internal space of the refrigerant header up and down. The bias of the refrigerant in the upper and lower parts of the internal space can also be suppressed.

  According to the heat exchanger according to the fifth aspect of the present invention, the refrigerant circulation amount in the internal space of the refrigerant header increases, and the refrigerant drift is further suppressed.

  With the heat exchanger according to the sixth aspect of the present invention, the amount of liquid-phase refrigerant that accumulates in the lower portion of the second chamber can be reduced.

  According to the heat exchanger according to the seventh aspect of the present invention, the liquid phase / gas phase deviation of the refrigerant is reduced even in the refrigerant outflow side internal space of the folded refrigerant header.

The figure which shows the refrigerant circuit and water circulation circuit of a heat pump type hot / cold water production | generation apparatus provided with the heat exchanger which concerns on one Embodiment of this invention. The figure which shows the internal structure of a freezing apparatus. The figure which shows a part of external appearance of a heat exchanger. The top view of a heat exchanger. The front view of a heat exchanger. FIG. 6 is a cross-sectional view taken along arrow VI in FIG. 3. The longitudinal cross-sectional view of the refrigerant header of the left side. The top view of an up-and-down partition plate. The figure which looked at the refrigerant header of a left side, and the flat multi-hole pipe connected from the back side. The transverse cross section of the refrigerant header of the heat exchanger concerning modification A. XI-XI arrow sectional drawing of FIG. The longitudinal cross-sectional view of the right side refrigerant | coolant header (folded refrigerant | coolant header) based on the modification B. FIG.

  A heat exchanger 10 according to an embodiment of the present invention is a heat exchanger that performs heat exchange between a refrigerant that causes a phase change during heat exchange and another heat medium. As the refrigerant, for example, HFC refrigerants such as R407C, R410A, R134a, and R32 are used. In the following, a case where water is used as another heat medium for exchanging heat with the refrigerant is described as an example, but the other heat medium is not limited to water.

  Hereinafter, an example in which the heat exchanger 10 according to one embodiment of the present invention is incorporated in a heat pump hot / cold water generator 90 will be described.

(1) Configuration of Heat Pump Type Hot Water / Cold Water Generation Device As shown in FIG. 1, the heat pump type hot water / cold water generation device 90 includes a refrigeration device 91 that is a heat source device and a water storage unit 92.

  The refrigeration apparatus 91 mainly includes a compressor 93 that compresses a refrigerant, a heat exchanger 10 that performs heat exchange between the refrigerant and water, an expansion valve 94 that functions as a refrigerant decompression unit, and outside air and refrigerant. And an air heat exchanger 95 that exchanges heat between the two. In the refrigeration apparatus 91, the compressor 93, the heat exchanger 10, the expansion valve 94, and the air heat exchanger 95 are connected by a refrigerant pipe to constitute a refrigerant circuit in which the refrigerant circulates. In addition, the refrigeration apparatus 91 has a four-way switching valve 91e in the refrigerant circuit. By switching this, the refrigeration apparatus 91 functions as a cold heat source and a warm heat source. When the four-way switching valve 91e is in the state shown in FIG. 1, the air heat exchanger 95 functions as a condenser and the heat exchanger 10 functions as an evaporator, so that the refrigeration apparatus 91 functions as a cold heat source. .

  The water storage unit 92 includes a water storage tank 96 and a water circulation pump 97. And in the water storage unit 92, the heat exchanger 10, the water storage tank 96, and the water circulation pump 97 are connected in order, and the water circulation circuit through which water circulates is comprised. The cold water or hot water stored in the water storage tank 96 is used for applications such as cooling, heating, and hot water supply in secondary equipment (not shown).

  FIG. 2 is a schematic diagram showing the internal structure of the refrigeration apparatus 91. In FIG. 2, the right compartment of the heat insulation wall 91c is the machine room 91a, and the left compartment of the heat insulation wall 91c is the blower room 91b. In the machine room 91a, a compressor 93, an expansion valve 94, and a four-way switching valve 91e are arranged. A fan 98 driven by a motor (not shown) is disposed in the blower chamber 91b.

  Moreover, the heat exchanger 10 is arrange | positioned through the heat insulation wall 91d below the blower chamber 91b. And in the heat exchanger 10, heat exchange is performed between the refrigerant | coolant which circulates through a refrigerant circuit, and the water which circulates through a water circulation circuit. In FIG. 2, the air heat exchanger 95 is arranged on the left side and the back side of the blower chamber 91b.

(2) Configuration of Heat Exchanger FIG. 3 is a view showing a part of the appearance of the heat exchanger 10. 6 is a cross-sectional view taken along the arrow VI in FIG. 3, FIG. 4 is a top view of the heat exchanger 10, and FIG. 5 is a front view of the heat exchanger 10.

  In the following description, the refrigerant flow in the heat exchanger 10 will be described using the refrigerant flow when the heat exchanger 10 functions as a refrigerant evaporator. The description of the refrigerant flow when the heat exchanger 10 functions as a refrigerant condenser will be omitted.

  The heat exchanger 10 is a laminated plate-type water heat exchanger that exchanges heat between refrigerant and water, and includes a plurality of flat tubes 20, a plurality of flat multi-hole tubes 40, and each flat multi-hole tube 40. And refrigerant headers 51 and 52 extending in a direction crossing the longitudinal direction. Each flat tube 20 communicates with the communicating portions 31 and 32. The communication portions 31 and 32 are provided in the vicinity of both end portions of the flat tube 20 and extend along the direction in which the refrigerant headers 51 and 52 extend. In addition, in the heat exchanger 10 of this embodiment, the 12 flat tubes 20 and the 13 flat multi-hole tubes 40 are laminated | stacked alternately. However, the number of the flat tubes 20 and the flat multi-hole tubes 40 to be laminated is appropriately selected according to the required performance, and the number of the flat tubes 20 and the flat multi-hole tubes 40 is the same as that of the present embodiment. It may be more or less than the heat exchanger 10 in the form.

  Then, water flows through the flat tube 20, and high-pressure refrigerant flows through the flat multi-hole tube 40. For this reason, the flat multi-hole tube 40 is required to have a higher pressure resistance than the flat tube 20. Inside the flat multi-hole tube 40, a plurality of holes 41 extending in the longitudinal direction (horizontal direction) of the flat multi-hole tube 40 are provided. The flat multi-hole tube can be formed of aluminum, an aluminum alloy, a copper alloy, stainless steel, or the like. Here, a flat multi-hole tube 40 made of an aluminum alloy is employed. A flat multi-hole tube 40 having a plurality of holes 41 is formed by drawing or extruding aluminum alloy.

  On the other hand, the flat tube 20 in which water flows is required to have high corrosion resistance. For this reason, it is preferable that the flat tube 20 is formed of stainless steel or a copper alloy. Moreover, although the flat tube 20 can also be made from aluminum or aluminum alloy, in this case, it is preferable to apply anticorrosion treatment such as alumite processing or resin processing coating on the inner surface serving as a water flow path. In addition, one flat tube 20 is configured by superimposing a pair of metal plates formed by pressing a metal plate and joining the outer peripheral edges thereof by brazing or welding.

(2-1) Water Flow Path in Heat Exchanger In FIG. 4 showing the heat exchanger 10 in which the flat tube 20, the flat multi-hole tube 40, and the refrigerant headers 51 and 52 are arranged to extend in the horizontal direction, heat exchange is performed. The left communication portion 31 including the water inlet pipe 37 and the outlet pipe 38 to the heat exchanger 10 is disposed in the vicinity of the left end portion of the flat tube 20, and the right communication portion 32 of the heat exchanger 10 is the right end of the flat tube 20. It is arranged near the part. An inlet side cock 80 and an outlet side cock 81 are provided on the inlet pipe 37 and the outlet pipe 38 of the communication portion 31, respectively. In addition, an inlet / outlet port 36 connected to a pipe or the like is provided in the inlet pipe 37 and the outlet pipe 38 of the communication portions 31 and 32 (see FIG. 3). Moreover, as shown in FIG. 4, the communication part 31 has an internal space partitioned into two spaces 31a and 31b by a partitioning part.

  With such a configuration, in FIG. 4, water enters the space 31 a from the inlet pipe 37 of the communication portion 31, branches into six flat tubes 20, flows through the inside from left to right, and the communication portion 32. Join in. The merged water branches into six flat tubes 20 on the outlet tube 38 side, flows through them from the right to the left, and merges in the space 31b of the communication portion 31. The merged water flows out of the heat exchanger 10 through the outlet pipe 38. When the heat exchanger 10 functions as a refrigerant evaporator, the water is cooled by being deprived of heat by the refrigerant in the flat multi-hole tube 40 while flowing through the twelve flat tubes 20.

(2-2) Refrigerant Flow Path in Heat Exchanger The straight refrigerant headers 51 and 52 are disposed at both ends in the longitudinal direction of 13 flat multi-hole tubes 40 extending horizontally in the left-right direction. In FIG. 4, which is a top view of the heat exchanger 10, the refrigerant header disposed at the left end portion of the flat multi-hole tube 40 is the refrigerant header 51, and the refrigerant header disposed at the right end portion of the flat multi-hole tube 40 is the refrigerant header 52. It is.

  As shown in FIG. 4, the refrigerant headers 51 and 52 are provided with front and rear partition plates 68a and 68b that divide the internal space into two spaces. The front and rear partition plates 68a and 68b form a surface orthogonal to the front and rear direction in which the refrigerant headers 51 and 52 extend. The front and rear partition plates 68a of the refrigerant header 51 divide the internal space of the refrigerant header 51 into a rear internal space IS10 and a front internal space IS20. Moreover, the front and rear partition plates 68b of the refrigerant header 52 divide the internal space of the refrigerant header 52 into a rear internal space IS30 and a front internal space IS40. The front and rear partition plates 68a of the refrigerant header 51 are not perforated, and the front and rear partition plates 68b of the refrigerant header 52 are perforated.

  Six rear flat multi-hole tubes 40 are connected to the rear internal space IS30 of the refrigerant header 52, and the refrigerant flows in from these six flat multi-hole tubes 40. In the front internal space IS40 of the refrigerant header 52 to which the seven flat multi-hole tubes 40 on the front side are connected, the refrigerant is branched into the seven flat multi-hole tubes 40 and flows out. That is, the refrigerant header 52 is a folded header that folds the refrigerant.

  In FIG. 4, the refrigerant enters the rear inner space IS10 from the inlet pipe 57, branches into the six flat multi-hole pipes 40 on the rear side, and flows through them from left to right, The refrigerant header 52 joins in the rear internal space IS30. The merged refrigerant moves from the rear inner space IS30 to the front inner space IS40 through the holes in the front and rear partition plates 68b, branches to the seven flat multi-hole tubes 40 on the front side, and passes through the inside from right to left. Flow and merge in the front internal space IS20 of the refrigerant header 51. Then, the merged refrigerant flows out of the heat exchanger 10 through the outlet pipe 58. When the heat exchanger 10 functions as a refrigerant evaporator, the refrigerant evaporates by taking heat from the water flowing through the flat tube 20 while flowing through the flat multi-hole tube 40.

  In addition, although the communication part 31 and the refrigerant | coolant headers 51 and 52 are each divided into two spaces here, the number of the space divided is not limited to this. Moreover, the internal space of the communication part 32 may be partitioned off.

(2-3) Detailed Configuration of Refrigerant Header Next, the detailed structure of the left-side refrigerant header 51, particularly when the heat exchanger 10 functions as a refrigerant evaporator, gas-liquid two-phase refrigerant flows from the inlet pipe 57. The structure related to the rear inner space IS10 of the refrigerant header 51 will be described.

  In FIG. 7, the longitudinal cross-sectional view of the refrigerant | coolant header 51 is shown. The refrigerant header 51 has a longitudinal direction of the header in the front-rear direction, and mainly a tubular member 65 extending long in the horizontal direction (front-rear direction), a rear end plate 66, a front end plate 67, and the above-described front and rear partition plates 68a. And an upper and lower partition plate 69.

(2-3-1) Cylindrical Member The cylindrical member 65 has an internal space IS10, IS20 that is substantially D-shaped in a front view (see FIG. 9), and a flat right side (left side in FIG. 9). 13 slits extending vertically are formed. As shown in FIGS. 4 and 5, the flat multi-hole tube 40 is inserted into these slits from the right side.

(2-3-2) Rear End Plate The rear end plate 66 is inserted from a rear slit formed on the left side surface of the cylindrical member 65 and closes the opening behind the cylindrical member 65. As shown in FIG. 9, the rear end plate 66 is provided with a nozzle hole EN1 in the lower portion. The diameter of the nozzle hole EN <b> 1 serving as the refrigerant inlet is smaller than the inner diameter of the inlet pipe 57 connected to the rear end plate 66. That is, the nozzle hole EN1 serves to narrow the flow area of the refrigerant flowing through the inlet pipe 57. The refrigerant entering the rear side internal space IS10 from the nozzle hole EN1 becomes a jet.

(2-3-3) Front End Plate The front end plate 67 is inserted from a front slit formed on the left side surface of the tubular member 65 and closes the front opening of the tubular member 65. As shown in FIG. 7, the front end plate 67 has a refrigerant outlet hole EX1 formed in the upper portion. An outlet pipe 58 is connected to the refrigerant outlet hole EX1.

(2-3-4) Front and rear partition plates The front and rear partition plates 68a are inserted from a central slit formed on the left side surface of the cylindrical member 65, and partition the internal space into a rear internal space IS10 and a front internal space IS20. . Six rear flat multi-hole tubes 40 are inserted into the rear internal space IS10, and seven front flat multi-hole tubes 40 are inserted into the front internal space IS20.

  The flat multi-hole tube 40 extends horizontally in the left-right direction, the refrigerant header 51 extends horizontally in the front-rear direction, and the longitudinal direction of the flat multi-hole tube 40 and the longitudinal direction of the refrigerant header 51 are orthogonal to each other. Further, in the installed state of the heat exchanger 10, the numerous holes 41 of each flat multi-hole tube 40 are arranged along the vertical direction.

(2-3-5) Upper / lower partition plate The upper / lower partition plate 69 extends in the longitudinal direction of the header and is divided into a first chamber IS11 facing the nozzle hole EN1 in the rear inner space IS10 and a second chamber IS12 separate from the first chamber IS11. Partitioning. More specifically, the upper and lower partition plates 69 divide the rear inner space IS10 into a lower first chamber IS11 and an upper second chamber IS12. As shown in FIG. 8, the rectangular upper and lower partition plates 69 are formed with a cutout 69a for avoiding the flat multi-hole tube 40, a front cutout 69b, and a rear cutout 69c. As shown in FIGS. 7 and 8, the front cutout 69b and the front and rear partition plates 68a form a first opening PA1 that allows the first chamber IS11 and the second chamber IS12 to communicate with each other. Further, the rear cutout 69c, together with the rear end plate 66, forms a second opening PA2 that allows the first chamber IS11 and the second chamber IS12 to communicate with each other. The first opening PA1 is located at the front end of the rear inner space IS10 far from the nozzle hole EN1, and the second opening PA2 is located at the rear end of the rear inner space IS10 close to the nozzle hole EN1. As shown in FIG. 7, the second opening PA2 is arranged in the vicinity of the nozzle hole EN1.

(2-3-6) Refrigerant Flow in Refrigerant Header A refrigerant flow in the rear inner space IS10 of the refrigerant header 51 will be described.

  The refrigerant flowing through the inlet pipe 57 and passing through the nozzle hole EN1 becomes a jet and flows into the first chamber IS11 below the rear internal space IS10. About half of the refrigerant flows into the plurality of holes 41 below the flat multi-hole tube 40, but the remaining refrigerant flows from the first chamber IS11 to the second chamber IS12 through the first opening PA1. Then, most of the refrigerant that has flowed into the second chamber IS12 flows from the second chamber IS12 into the plurality of holes 41 in the upper portion of the flat multi-hole tube 40. Part of the refrigerant that has flowed into the second chamber IS12 returns from the second chamber IS12 to the first chamber IS11 again through the second opening PA2.

  When the amount of refrigerant flowing through the refrigerant circuit of the refrigeration apparatus 91 is large, the amount of refrigerant that returns from the second chamber IS12 to the first chamber IS11 through the second opening PA2 increases, and the amount of refrigerant flowing through the refrigerant circuit of the refrigeration apparatus 91 increases. When the amount is small, the amount of refrigerant returning from the second chamber IS12 to the first chamber IS11 through the second opening PA2 decreases.

  Since the second opening PA2 is disposed in the vicinity of the nozzle hole EN1, the vicinity of the nozzle hole EN1 is in a low pressure state and passes from the second chamber IS12 to the first chamber IS11 through the second opening PA2. The return refrigerant flow is facilitated.

(3) Features of heat exchanger (3-1)
In the heat exchanger 10, the refrigerant that has entered the rear internal space IS <b> 10 from the nozzle hole EN <b> 1 flows into the holes 41 of the plurality of flat multi-hole tubes 40 and is adjacent to the flat multi-hole tube 40. Heat exchange with water flowing through Here, when the heat exchanger 10 functions as an evaporator and the refrigerant decompressed by the expansion valve 94 is in a two-phase state in which the gas phase and the liquid phase are mixed, the refrigerant header 51 extends along the horizontal direction. Therefore, if the upper and lower partition plates 69 are not provided, in the rear side internal space IS10, the refrigerant near the nozzle hole EN1 is mainly in the liquid phase, and the refrigerant far from the nozzle hole EN1 is mainly in the gas phase. In such a situation, the flat multi-hole tube 40 in which a large amount of liquid-phase refrigerant flows and the flat multi-hole tube 40 in which a large amount of gas-phase refrigerant flows are separated, resulting in refrigerant drift.

  However, in the heat exchanger 10 to which the present invention is applied, the rear inner space IS10 of the refrigerant header 51 is divided into the first chamber IS11 and the second chamber IS12 by the upper and lower partition plates 69 extending in the header longitudinal direction. Then, the refrigerant header 51 is configured so that a part of the refrigerant that has entered the first chamber IS11 from the nozzle hole EN1 flows from the first chamber IS11 to the second chamber IS12 and returns from the second chamber IS12 to the first chamber IS11 again. doing. That is, in the rear internal space IS10 of the refrigerant header 51, a configuration in which a part of the refrigerant circulates (loops) is realized by the upper and lower partition plates 69. Since such a configuration is adopted, the liquid-phase refrigerant reaches a position far from the nozzle hole EN1 along the circulation flow in the rear inner space IS10 of the refrigerant header 51, and the rear side of the refrigerant header 51. The deviation of the liquid phase and gas phase of the refrigerant in the internal space IS10 is reduced. As a result, the drift of the refrigerant flowing through each flat multi-hole tube 40 is also suppressed.

(3-2)
In the heat exchanger 10, the first opening PA1 for flowing the refrigerant from the first chamber IS11 to the second chamber IS12 in the rear internal space IS10 of the refrigerant header 51, and the refrigerant is returned from the second chamber IS12 to the first chamber IS11. 2nd opening PA2 is distribute | arranged to the front-end part and rear-end part of a header longitudinal direction. For this reason, the dead area where a refrigerant | coolant stagnates in the rear side internal space IS10 of the refrigerant | coolant header 51 becomes small, and it is suppressed that the liquid phase refrigerant | coolant stays in the rear side internal space IS10 of the refrigerant | coolant header 51.

(3-3)
In the heat exchanger 10, since the refrigerant enters the rear side internal space IS10 of the refrigerant header 51 through the nozzle hole EN1, the flow rate of the refrigerant increases. And the flow of the refrigerant | coolant from 2nd chamber IS12 to 1st chamber IS11 through 2nd opening PA2 is accelerated | stimulated using the low pressure space produced in the vicinity of nozzle hole EN1. For this reason, the circulation amount of the refrigerant in the rear inner space IS10 of the refrigerant header 51 can be increased. That is, since the reduced pressure state is created by the venturi effect using the jet of the refrigerant through the nozzle hole EN1, and the amount of the refrigerant passing through the second opening PA2 disposed in the vicinity thereof is increased, the rear internal space IS10 of the refrigerant header 51 is increased. The liquid-phase and gas-phase bias of the refrigerant is further reduced.

(3-4)
In the heat exchanger 10, the upper and lower partition plates 69 are arranged behind the refrigerant header 51 so that the first chamber IS 11 on the nozzle hole EN 1 side, which is the refrigerant inlet, is disposed below and the second chamber IS 12 is disposed thereon. Side internal space IS10 is divided up and down. The hole 41 of the flat multi-hole tube 40 is exposed in both the first chamber IS11 and the second chamber IS12, and not only from the first chamber IS11 on the nozzle hole EN1 side but also from the second chamber IS12. The refrigerant flows into the hole 41 of the flat multi-hole tube 40. Since such a configuration is adopted, a large amount of refrigerant flows from the first chamber IS11 to the second chamber IS12, and a part of the refrigerant returns from the second chamber IS12 to the first chamber IS11 again. As a result, the amount of refrigerant circulating in the rear inner space IS10 of the refrigerant header 51 increases naturally, and refrigerant drift is further suppressed.

  Further, in the heat exchanger 10, the refrigerant drift between the side closer to the nozzle hole EN1 (rear side) and the side farther from the nozzle hole EN1 (front side) of the rear inner space IS10 of the refrigerant header 51, that is, the refrigerant header 51 In addition to suppressing the refrigerant drift in the longitudinal direction, the upper and lower partition plates 69 vertically partition the rear inner space IS10 of the refrigerant header 51, so that the upper and lower portions of the rear inner space IS10 of the refrigerant header 51 are The bias of the refrigerant can also be suppressed.

(4) Modification (4-1) Modification A
In the heat exchanger 10 described above, a structure in which the rear internal space IS10 of the refrigerant header 51 is partitioned up and down by the upper and lower partition plates 69 is adopted, but a structure of partitioning right and left instead of up and down may be employed.

  In FIG. 10, sectional drawing which cut | disconnected the refrigerant | coolant header 151 of the heat exchanger which concerns on the modification A at the horizontal surface is shown. The left-right direction in FIG. 10 is the header longitudinal direction of the refrigerant header 151, and the up-down direction in FIG. 10 is the longitudinal direction of the flat multi-hole tube 140. As with the refrigerant header 51, the refrigerant header 151 has a longitudinal direction in the front-and-rear direction, mainly a tubular member 165 extending long in the horizontal direction (front-rear direction), a rear end plate 166, a front end plate 167, The front / rear partition plate 168a and the left / right partition plate 169 are configured.

  As with the cylindrical member 65, the cylindrical member 165 has a substantially D-shaped inner space IS110, IS120 when viewed from the front, and has 13 slits extending vertically on the flat right side surface (the upper side surface in FIG. 10). Is formed. A flat multi-hole tube 140 is inserted into these slits. As shown in FIG. 11, the flat multi-hole tube 140 is arranged so that a large number of holes 141 are arranged along the vertical direction (direction perpendicular to the paper surface of FIG. 10), as shown in FIG. .

  The rear end plate 166 is inserted from a rear slit formed on the left side surface of the tubular member 165 and closes the opening behind the tubular member 165. The rear end plate 166 is provided with a nozzle hole EN101 as shown in FIG. The diameter of the nozzle hole EN101 serving as the refrigerant inlet is smaller than the inner diameter of the inlet pipe 157 connected to the rear end plate 166. That is, the nozzle hole EN101 serves to narrow the flow area of the refrigerant flowing through the inlet pipe 157. The refrigerant entering the rear side internal space IS110 from the nozzle hole EN101 becomes a jet.

  The front end plate 167 is inserted from a front slit formed on the left side surface of the tubular member 165 and closes the opening in front of the tubular member 165. As shown in FIG. 10, the front end plate 167 has a refrigerant outlet hole EX101. An outlet pipe 158 is connected to the refrigerant outlet hole EX101.

  The front and rear partition plates 168a are inserted from a central slit formed on the left side surface of the tubular member 165, and partition the internal space of the tubular member 165 into a rear internal space IS110 and a front internal space IS120. Six rear flat multi-hole tubes 140 are inserted into the rear inner space IS110, and seven front flat multi-hole tubes 140 are inserted into the front inner space IS120. The flat multi-hole tube 140 extends horizontally in the left-right direction, the refrigerant header 151 extends horizontally in the front-rear direction, and the longitudinal direction of the flat multi-hole tube 140 and the longitudinal direction of the refrigerant header 151 are orthogonal to each other.

  The left and right partition plates 169 extend in the header longitudinal direction and divide the rear inner space IS110 into a first chamber IS111 facing the nozzle hole EN101 and a second chamber IS112 different from the first chamber IS111. More specifically, the left and right partition plates 169 have a rear inner space IS110, a left first chamber IS111 where the plurality of holes 141 of the flat multi-hole tube 140 are not exposed, and a plurality of holes 141 of the flat multi-hole tube 140. Is divided into the second chamber IS112 on the right side where the is exposed. Then, the refrigerant that has entered the internal space of the refrigerant header 151 flows into the plurality of holes 141 of the flat multi-hole tube 140 from the second chamber IS112. As shown in FIG. 11, the left and right partition plates 169 are formed with a front notch 169a and a rear notch 169b. The front notch 169a and the front and rear partition plates 168a form a first opening PA101 that allows the first chamber IS111 and the second chamber IS112 to communicate with each other. Further, the rear notch 169b and the rear end plate 166 form a second opening PA102 that allows the first chamber IS111 and the second chamber IS112 to communicate with each other. The first opening PA101 is far from the nozzle hole EN101, and the second opening PA102 is close to the nozzle hole EN101. As shown in FIG. 11, the second opening PA102 is disposed in the vicinity of the nozzle hole EN101 and in the vicinity of the bottom surfaces of the first chamber IS111 and the second chamber IS112.

  In the refrigerant header 151, the heat exchanger according to the modification having the above-described structure includes the second chamber IS112 (right chamber) on the flat multi-hole tube 140 side and the first chamber IS111 (left side) on the opposite side. The left and right partition plates 169 are arranged so that the internal space is divided into chambers. Then, the refrigerant that has entered the first chamber IS111 on the nozzle hole EN101 side first passes through the first chamber IS111 and then enters the second chamber IS112, and then flows into the plurality of holes 141 of the flat multi-hole tube 140. . Since such a configuration is adopted, a large amount of refrigerant flows from the first chamber IS111 to the second chamber IS112, and the refrigerant flows from the second chamber IS112 to the flat multi-hole tube 140. Then, a part of the refrigerant returns from the second chamber IS112 to the first chamber IS111 again. As a result, the amount of refrigerant circulating in the rear internal space IS110 of the refrigerant header 151 increases naturally, and refrigerant drift is suppressed.

  Further, since the refrigerant flows from the first chamber IS111 to the second chamber IS112 and the refrigerant flows from the second chamber IS112 to the flat multi-hole tube 140, the second chamber IS112 in which the flow rate of the refrigerant is weakened. It is also assumed that the liquid phase refrigerant stays in the lower part. In view of this, in the heat exchanger according to the modified example, in the rear inner space IS110 of the refrigerant header 151, the refrigerant returning from the second chamber IS112 to the first chamber IS111 passes from the vicinity of the bottom surface of the second chamber IS112 to the first chamber. The structure of returning to IS111 is adopted. That is, a structure is adopted here in which the refrigerant accumulated in the lower part of the second chamber IS112 is returned to the first chamber IS111 via the second opening PA102 from the vicinity of the bottom surface of the second chamber IS112. Thereby, the quantity of the liquid-phase refrigerant | coolant which retains in the lower part of 2nd chamber IS112 can be reduced. The liquid-phase refrigerant returned to the first chamber IS111 is mixed with the gas-phase refrigerant in the first chamber IS111 where the flow rate of the refrigerant is high, and flows to the flat multi-hole tube 140 via the second chamber IS112. become.

(4-2) Modification B
The heat exchanger 10 employs a structure in which the rear inner space IS10 of the refrigerant header 51 is vertically divided by the upper and lower partition plates 69. In the modified example A, the rear inner space IS10 is separated by the left and right partition plates 169. Although a partitioning structure is employed, such a partitioning structure can also be employed in the internal space of the refrigerant header 52. Specifically, the front internal space IS40 in front of the front and rear partition plates 68b of the refrigerant header 52 is divided into two chambers (third chamber and fourth chamber) by the upper and lower partition plates 69b (see FIGS. 4 and 12) or the left and right partition plates. It may be divided into rooms).

  For example, as shown in FIG. 12, when the front internal space IS40 is vertically divided by the vertical partition plate 69b and divided into the lower third chamber IS43 and the upper fourth chamber IS44, the front and rear partition plates 68b of the refrigerant header 52 At least part of the refrigerant that has entered the third chamber IS43 from the rear inner space IS30 through the lower hole 68b1 flows from the third chamber IS43 to the fourth chamber IS44. Then, the refrigerant that has flowed from the third chamber IS43 to the fourth chamber IS44 through the opening PA3 on the front side of the upper and lower partition plates 69b passes through the opening PA4 on the rear side of the upper and lower partition plates 69b again from the fourth chamber IS44. Return to room IS43. By adopting such a refrigerant loop configuration, even in the front internal space IS40 of the refrigerant header 52, which functions as a refrigerant folding portion and tends to increase the dryness of the refrigerant, there is less liquid / gas phase deviation of the refrigerant, The drift of the refrigerant flowing through the seven flat multi-hole tubes 40 on the front side is also suppressed.

DESCRIPTION OF SYMBOLS 10 Heat exchanger 40 Flat multi-hole pipe 41 Plural holes of flat multi-hole pipe 51 Refrigerant header 52 Refrigerant header (folded refrigerant header)
57 Inlet piping 69 Upper and lower partition plates (partition plates)
69b Upper and lower partition plates (partition plates)
140 Flat multi-hole tube 141 Plural holes of flat multi-hole tube 151 Refrigerant header 169 Left and right partition plates (partition plates)
EN1, EN101 Nozzle hole (refrigerant inlet)
IS10, IS110 Rear internal space (internal space of refrigerant header)
IS11, IS111 1st chamber IS12, IS112 2nd chamber IS30 Rear internal space (refrigerant inflow internal space)
IS40 front internal space (refrigerant outflow internal space)
IS43 3rd room IS44 4th room PA1, PA101 1st opening PA2, PA102 2nd opening

JP 2014-142165 A

Claims (7)

Refrigerant inlets (EN1, EN101) are formed, and extend along the horizontal direction, the refrigerant headers (51, 151),
A plurality of flat multi-hole tubes (40, 140) extending in a direction intersecting with the longitudinal direction of the header of the refrigerant header and along a horizontal direction, into which refrigerant flows from the refrigerant header;
With
The plurality of holes (41, 141) of the flat multi-hole pipe through which the refrigerant flows are arranged along the vertical direction,
The internal space (IS10, IS110) of the refrigerant header is separated from the first chamber (IS11, IS111) on the refrigerant inlet side and the first chamber by partition plates (69, 169) extending in the header longitudinal direction. It is divided into another second room (IS12, IS112),
At least part of the refrigerant that has entered the first chamber from the refrigerant inlet flows from the first chamber to the second chamber, and returns from the second chamber to the first chamber again.
Heat exchanger (10). In the internal space of the refrigerant header, a first opening (PA1, PA101) for flowing the refrigerant from the first chamber to the second chamber is provided at an end opposite to the refrigerant inlet side in the header longitudinal direction. A second opening (PA2, PA102) for returning the refrigerant from the second chamber to the first chamber is formed at an end of the header longitudinal direction on the side of the refrigerant inlet.
The heat exchanger according to claim 1. The refrigerant inlet is a nozzle with a reduced flow path area,
The second opening is formed in the vicinity of the refrigerant inlet,
Due to the jet of refrigerant flowing into the internal space of the refrigerant header from the refrigerant inlet, the vicinity of the refrigerant inlet is in a low pressure state and returns from the second chamber to the first chamber through the second opening. Refrigerant flow occurs,
The heat exchanger according to claim 2. The partition plate (69) partitions the internal space (IS10) of the refrigerant header up and down,
The first chamber (IS11) is located below the second chamber (IS12),
The refrigerant in the internal space of the refrigerant header flows from the first chamber into a plurality of holes in the lower portion of the flat multi-hole tube, and flows from the second chamber into a plurality of holes in the upper portion of the flat multi-hole tube.
The heat exchanger according to any one of claims 1 to 3. The partition plate (169) includes an internal space (IS10) of the refrigerant header, the first chamber (IS111) in which a plurality of holes of the flat multi-hole tube (140) are not exposed, and a plurality of flat multi-hole tubes. And is partitioned into the second chamber (IS112) where the hole is exposed,
The refrigerant in the internal space of the refrigerant header flows into the plurality of holes of the flat multi-hole tube from the second chamber,
The heat exchanger according to any one of claims 1 to 3. The refrigerant that returns from the second chamber (IS112) to the first chamber (IS111) returns to the first chamber from the vicinity of the bottom surface of the second chamber.
The heat exchanger according to claim 5. The refrigerant header (51) is a header to which a refrigerant inlet pipe (57) is connected,
A folded refrigerant header (52) separate from the refrigerant header (51),
Further comprising
Refrigerant flows into the internal space (IS10) of the refrigerant header (51) from the inlet pipe (57),
The internal space of the folded refrigerant header (52) includes a refrigerant inflow side internal space (IS30) to which the flat multi-hole tube (40) on the refrigerant inflow side is connected, and the flat multi-hole tube (40) on the refrigerant outflow side. Is divided into the refrigerant outflow side internal space (IS40) to which
The refrigerant outflow side internal space (IS40) is separated from the third chamber (IS43) on the refrigerant inflow side internal space (IS30) side and the third chamber by a partition plate (69b) extending in the header longitudinal direction. The fourth room (IS44)
At least part of the refrigerant that has entered the third chamber from the refrigerant inflow side internal space (IS30) flows from the third chamber to the fourth chamber, and returns from the fourth chamber to the third chamber again.
The heat exchanger according to any one of claims 1 to 6.

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