JPWO2016013100A1 - HEAT EXCHANGER AND AIR CONDITIONING REFRIGERATOR HAVING THE HEAT EXCHANGER - Google Patents

Abstract

A flat tube group 11A, 11B provided in a plurality of rows with gaps between rows in the depth direction of the heat exchanger, and corrugated fins 12 provided in common in the plurality of flat tube groups 11A, 11B. The tube groups 11A and 11B are provided with a heat exchanging portion 10 composed of a plurality of flat tubes 11 arranged upright in the direction of gravity, and the corrugated fins 12 are provided in common to the plurality of rows of flat tube groups 11A and 11B. The first drainage portion 17 communicating with the inter-row gap 16 is provided in a portion located between the rows of the flat tube groups 11A and 11B.

Description

  The present invention relates to a heat exchanger and an air conditioning refrigeration apparatus including the heat exchanger.

  Conventionally, there is a heat exchanger in which flat tubes and corrugated fins are alternately stacked in a direction orthogonal to the air flow direction, and both ends of each of the plurality of flat tubes are connected to a pair of headers (for example, Patent Document 1). 2).

  The corrugated fin is formed in a zigzag shape in which flat portions and curved portions are alternately connected, and in Patent Document 1, a heat exchanger using this type of corrugated fin is used as an evaporator. A technique for ensuring drainage of condensed water is disclosed. Specifically, in Patent Document 1, the flat portion of the corrugated fin is formed into a valley bottom shape with the center in the air flow direction as the bottom, and a through hole is provided at the junction between the valley bottom portion and the flat tube, and the corrugated fin surface The condensed water is led to the bottom of the flat part and drained from the through hole.

  Further, in Patent Document 2, flat tube groups composed of a plurality of flat tubes arranged in parallel at intervals are arranged in two rows in the heat exchanger depth direction, which is a direction orthogonal to the parallel arrangement direction of the flat tubes. A heat exchanger having a heat exchanging portion in which flat tubes and corrugated fins are alternately stacked in the parallel direction of the flat tubes is disclosed. In patent document 2, a pair of header is arrange | positioned at the upper and lower sides of a heat exchange part, and the technique which improves the drainage property of the condensed water collected on the lower header is disclosed.

Japanese Patent Laying-Open No. 2005-245187 (FIG. 1) Japanese Patent No. 4786234 (FIG. 1)

  Although Patent Document 1 discloses a technique for improving the drainage of condensed water, it is a technique for a configuration in which the flat tube group is in a single row.

  In recent years, in order to meet the demands for smaller and lighter heat exchangers and higher performance, a configuration in which flat tube groups are arranged in multiple rows as in Patent Document 2 is increasing. In Patent Document 2, corrugated fins are provided in common in flat tube groups provided in two rows, and are longer in the depth direction of the heat exchanger than corrugated fins corresponding to one row. Thus, although the corrugated fins become longer in the heat exchanger depth direction, improvement in drainage of condensed water is required, but Patent Document 2 does not discuss anything about drainage of condensed water from the corrugated fin itself. Absent.

  The present invention has been made to solve the above-described problems, and in a multi-row heat exchanger, the heat exchanger capable of improving drainage of condensed water and the heat exchanger are provided. It aims at obtaining an air-conditioning freezer.

  The heat exchanger according to the present invention includes a flat tube group provided in a plurality of rows with a space between rows in the depth direction of the heat exchanger, and corrugated fins provided in common to the plurality of flat tube groups. The heat exchanger is composed of a plurality of flat tubes in which the flat tube groups are arranged upright in the direction of gravity, and the corrugated fins communicate with the gaps between the rows of the flat tube groups. It has a 1st drainage part to do.

  Moreover, the air-conditioning refrigerating apparatus which concerns on this invention is equipped with said heat exchanger.

  ADVANTAGE OF THE INVENTION According to this invention, the drainage of condensed water can be improved in the heat exchanger of a multi-row structure.

It is the figure which showed collectively the front view and side view of a heat exchanger which concern on Embodiment 1 of this invention. It is a model perspective view of the flat tube of the heat exchanger which concerns on Embodiment 1 of this invention. It is a front expansion schematic diagram of the heat exchanger which concerns on Embodiment 1 of this invention. It is a cross-sectional view of the heat exchanger according to Embodiment 1 of the present invention. It is AA sectional drawing of FIG. It is a cross-sectional view of the heat exchanger according to Embodiment 2 of the present invention. It is a cross-sectional view of the heat exchanger which concerns on Embodiment 3 of this invention. It is a cross-sectional view of the heat exchanger which concerns on Embodiment 4 of this invention. It is a refrigerant circuit diagram of the air-conditioning refrigerating apparatus which concerns on Embodiment 5 of this invention.

Embodiment 1 FIG.
FIG. 1 is a diagram collectively showing a front view and a side view of a heat exchanger according to Embodiment 1 of the present invention. 1A is a front view, and FIG. 1B is a side view. FIG. 2 is a schematic perspective view of a flat tube of the heat exchanger according to Embodiment 1 of the present invention. In FIG. 1, FIG. 2, and the figure mentioned later, what attached | subjected the same code | symbol is the same or it corresponds, and this is common in the whole text of a specification. Furthermore, the forms of the constituent elements appearing in the entire specification are merely examples and are not limited to these descriptions.

  The heat exchanger 1 is used for an outdoor unit of an air conditioner, for example, and mainly includes a heat exchange unit 10, a header 20, and a header 30. In FIG. 1, the arrow shown in the header 20 indicates the flow direction of the refrigerant, and the white arrow indicates the flow direction of air in FIG.

  The heat exchanging unit 10 has a flat tube group 11 </ b> A and 11 </ b> B composed of a plurality of flat tubes 11 arranged side by side at intervals, with a space in the heat exchanger depth direction that is a direction orthogonal to the direction in which the flat tubes 11 are arranged. It has multiple rows (here 2 rows). Then, the flat tubes 11 and the corrugated fins 12 are alternately stacked in the direction in which the flat tubes 11 are arranged side by side. The corrugated fins 12 are two-row common fins provided in common to the windward side flat tube group 11A and the leeward side flat tube group 11B, and the heat exchanging unit 10 is configured in two rows as a whole.

  As shown in FIG. 2, each flat tube 11 has a plurality of through-holes 11a (four as an example here) serving as a refrigerant flow path, and is arranged in a gravitational direction. 11 are connected to a pair of headers 20 and 30 at both ends in the direction of gravity. Specifically, the lower end of each flat tube 11 is connected to a header 20 (20a, 20b) as an inlet / outlet header, and the upper end of each flat tube 11 is connected to a header 30 as a folded header. The corrugated fins 12 and the headers 20 and 30 are made of, for example, aluminum or an aluminum alloy.

  Here, an example in which the header 20 is composed of two headers 20a and 20b independent of the windward side flat tube group 11A and the leeward side flat tube group 11B is shown, but the inside of one header is separated by a partition plate. It is good also as a structure. In addition, although the square headers are illustrated as the headers 20 and 30 here, they may be cylindrical headers.

  When the heat exchanger 1 configured as described above is used as an evaporator, the refrigerant flows into the header 20a in the lower part of the gravity direction and on the windward side, and the header 20a makes the same path as the number of the windward flat tube group 11A. It separates and raises the inside of each flat tube 11 of 11A of windward flat tube groups. Thereafter, the refrigerant that has flowed out from the upper ends of the flat tubes 11 in the windward flat tube group 11A merges in the header 30, is folded back in the header 30, and flows into the flat tubes 11 in the leeward flat tube group 11B from the upper ends. . The refrigerant that has flowed in from the upper ends of the respective flat tubes 11 in the leeward flat tube group 11B passes through the flat tubes 11 and flows out from the lower ends, merges in the header 20b, and then flows out of the heat exchanger 1.

FIG. 3 is an enlarged schematic front view of the heat exchanger according to Embodiment 1 of the present invention. FIG. 4 is a cross-sectional view of the heat exchanger according to Embodiment 1 of the present invention. FIG. 5 is a cross-sectional view taken along the line AA in FIG.
As shown in FIG. 3, the corrugated fins 12 are formed in a zigzag shape in which the plane portions 13 and the curved portions 14 are alternately arranged, and a plurality of louvers 15 are formed in each plane portion 13. The louver 15 is cut and raised so as to be inclined with respect to the flat surface portion 13 of the corrugated fin 12, and in the flat surface portion 13, a plurality of louvers 15 (here, the same as the air flow direction) (here, (It is eight as an example.) As shown in FIG. 5, each louver 15 is formed so as to be inclined downward toward the center in the depth direction of the heat exchanger.

  In the first embodiment, the corrugated fins 12 have a configuration common to the two rows of the windward flat tube group 11A and the leeward flat tube group 11B, and are therefore longer in the heat exchanger depth direction than those corresponding to one row. For this reason, the improvement of the drainage property of the condensed water which generate | occur | produced on the surface of the corrugated fin 12 is calculated | required. Therefore, in the first embodiment, in the corrugated fins 12, the condensed water generated in the corrugated fins 12 is placed in a portion located between the windward flat tube group 11 </ b> B and the leeward flat tube group 11 </ b> B. A first drainage portion 17 is provided to guide a gap 16 between them (hereinafter referred to as an inter-column gap) 16.

  The first drainage portion 17 is a groove that extends in the parallel direction of the flat tubes 11 (the left-right direction in FIG. 4) at the center of the flat portion 13 in the depth direction of the heat exchanger, and is concave downward in the gravitational direction. 13 is formed. The first drainage portion 17 is aligned in the inter-row gap 16 and the heat exchanger depth direction, and the first drainage portion 17 and the inter-row gap 16 serving as a drainage path in the juxtaposed direction (left-right direction in FIG. 4). Are alternately arranged and communicated with each other.

  Further, the corrugated fin 12 has a fin windward side end 12a extending to the windward side of the flat tube 11 from the windward side end 11b, and a second drainage portion 18 is formed by this extended portion.

  When the heat exchanger 1 configured as described above is used as an evaporator, condensed water is generated on the surface of the corrugated fins 12. The condensed water is collected on the first drainage part 17 on the corrugated fins 12 and via the louver 15, moves to the flat tube 11 side, and is drained from the inter-column gap 16 to the lower part in the gravity direction. Here, since the plane portion 13 is inclined in the direction of gravity, the condensed water easily flows from the first drainage portion 17 to the inter-row gap 16.

  Further, in the evaporator, since it is easy to condense in the windward part where the air first collides, the condensed water generated on the windward side of the corrugated fin 12 flows through the second drainage part 18 due to the inclination of the flat part 13 and moves in the direction of gravity. Drained to the bottom.

  As described above, according to the first embodiment, in the heat exchanger 10, the inter-column gap is located in the portion located between the windward flat tube group 11 </ b> A and the leeward flat tube group 11 </ b> B in the heat exchanger depth direction. Since the 1st drainage part 17 which drains to 16 was provided, it has the following effects. That is, even if the corrugated fins 12 are long in the heat exchanger depth direction, the condensed water of the entire fins can be collected in the first drainage part 17 and drainage using the inter-row gaps 16 is possible. Can increase the sex.

  In addition, since the corrugated fins 12 are common two-row common fins between the two rows of flat tubes 11, compared to the case where the two-row divided fins are used, the fin insertion at the time of manufacturing is only once, thereby improving the productivity. .

  Further, when the heat exchanger 1 is used as an evaporator under a low outside air temperature condition, condensed water adhering to the surface of the corrugated fins 12 may freeze and form frost. In particular, the portion on the windward side where the air collides first tends to frost. Here, in this Embodiment 1, since the 2nd drainage part 18 was provided and the drainage property of the windward side part in the corrugated fin 12 was improved, even when driving | running on the conditions where frost formation occurs, the fin windward side of the corrugated fin 12 Concentration of frost near the end 12a can be avoided.

  Moreover, although it was set as the structure which inclines below the louver 15 toward the center part of the heat exchanger depth direction in the plane part 13 of the corrugated fin 12, the direction of the inclination of the louver 15 is not restricted to this direction. All may be in the same orientation.

Embodiment 2. FIG.
In the second embodiment, the inter-row gap 16 is provided with a drainage promoting body. Items not described in the second embodiment are the same as those in the first embodiment. The following description will focus on the differences of the second embodiment from the first embodiment.

FIG. 6 is a cross-sectional view of a heat exchanger according to Embodiment 2 of the present invention.
When the condensed water is drained to the lower part in the direction of gravity, the smaller the inter-row gap 16, that is, the smaller the drainage path, the greater the surface tension of the condensed water and the condensate flowing from the first drainage portion 17 into the inter-row gap 16. Water increases and drainage improves. Therefore, in the second embodiment, by arranging two rods 40 as drainage promotion bodies in the inter-row gap 16, the inter-row gap 16 communicates with the first drainage portion 17 and the other portions. A part that communicates with the partition and the first drainage part 17 is a drainage path 41.

  The rod 40 is a rod having a circular cross section in which a brazing material is clad (adhered) to the outer periphery in advance, and is made of, for example, aluminum or an aluminum alloy, and is fixed to at least one of the corrugated fin 12 and the flat tube 11.

  As described above, in the second embodiment, the same effects as those of the first embodiment can be obtained, and the rod 40 is disposed in the inter-column gap 16 to partition the inter-column gap 16. Since the small drainage channel 41 is configured, the following effects can be obtained. That is, in the first embodiment, the entire inter-row gap 16 is a drainage path, but in the second embodiment, the drainage path is reduced by disposing the rod 40, so that the condensation is performed compared to the case where the rod 40 is not provided. The effect | action which guides water to the drainage path 41 improves. Moreover, since the rod 40 extends in the direction of gravity, the effect of guiding condensed water in the direction of gravity is improved. Therefore, drainage can be further improved.

  Further, by using the rod 40 with the brazing material adhered to the outer periphery, the corrugated fin 12 and the flat tube 11 can be easily joined, and the productivity can be improved.

  In the second embodiment, the rod 40 has a circular cross section, but is not limited to this, and may have a rectangular cross section, an elliptical cross section, or the like.

  The number of bars 40 is two here, but the number is not limited to this, and may be one or three or more. In short, by disposing the rods 40, it is only necessary to form a drainage path that separates the inter-row gap 16 and communicates with the first drainage portion 17 in the inter-row gap 16, and the number of the rods 40 is arbitrary. is there.

Embodiment 3 FIG.
The third embodiment is different from the second embodiment in the configuration of the drainage promotion body, and items not described in the third embodiment are the same as those in the first and second embodiments. The following description will focus on the differences of the third embodiment from the first and second embodiments.

FIG. 7 is a cross-sectional view of a heat exchanger according to Embodiment 3 of the present invention.
In the third embodiment, a rectangular plate 50 curved in an arc shape in the short direction is inserted into the inter-column gap 16 of the flat tube 11. Two plates 50 are disposed in the inter-row gaps 16 and are fixed to the corrugated fins 12 by brazing material previously attached to both side surfaces of the arc. In the gap between the plate 50 and the corrugated fins 12, a drainage path 51 communicating with the first drainage unit 17 is formed separately in the inter-row gap 16.

  According to the third embodiment, the same effect as that of the second embodiment can be obtained.

  Further, the number of the plates 50 is two here, but the number is not limited to this. In short, by disposing the plates 50, it is only necessary to form a drainage path that divides the gaps 16 between the rows and communicates with the first drainage portions 17 separately in the gaps 16 between the rows, and the number of the plates 50 is arbitrary. is there.

Embodiment 4 FIG.
The fourth embodiment relates to the improvement of drainage at the leeward side end of the corrugated fin 12. Items not described in the fourth embodiment are the same as those in the first embodiment. Hereinafter, the difference between the fourth embodiment and the first embodiment will be mainly described.

FIG. 8 is a cross-sectional view of a heat exchanger according to Embodiment 4 of the present invention.
In the corrugated fin 12 of the heat exchanger 1 of the fourth embodiment, the fin leeward side end 12b extends further to the leeward side than the flat tube leeward side end 11c of the leeward side flat tube group 11B. A third drainage part 19 is formed. The extension distance a of the third drainage part 19 is configured to be shorter than the extension distance b of the second drainage part 18.

  According to the fourth embodiment, the same effects as those of the first embodiment can be obtained, and when used as an evaporator, the condensed water that has flowed to the leeward side due to the flow of air travels along the third drainage section 19 and between the rows. It can drain in the direction of gravity from the gap 16a.

  Further, both the fin windward end 12a and the fin windward end 12b of the corrugated fin 12 are extended from the flat tube windward end 11b and the flat tube windward end 11c so that the second drainage portion 18 and the third drainage portion 19 are provided. In the formation, the distribution of the extension distance was set such that the extension distance a of the third drainage portion 19 was shorter than the extension distance b of the second drainage portion 18. Thereby, drainage property can be ensured also in the 3rd drainage part 19 on the fin leeward side, while ensuring the drainage property and frosting resistance of the second drainage part 18 on the fin leeward side.

Embodiment 5. FIG.
FIG. 9 is a refrigerant circuit diagram of an air-conditioning refrigeration apparatus according to Embodiment 5 of the present invention.
The air conditioning refrigeration apparatus includes a compressor 61, a condenser 62, an expansion device 63, and an evaporator 64, and includes a refrigerant circuit in which refrigerant circulates and a blower 65. In the condenser 62 and the evaporator 64, heat exchange between the air blown by the blower 65 rotated by the blower motor 66 and the refrigerant is performed. By using the heat exchanger of any of the first to fourth embodiments described above for the condenser 62 or the evaporator 64, or both, an air-conditioning refrigeration apparatus with high energy efficiency can be realized.

Here, energy efficiency is constituted by the following equation.
Heating energy efficiency = Indoor heat exchanger (condenser) capacity / total input Cooling energy efficiency = Indoor heat exchanger (evaporator) capacity / total input

  In addition, about the heat exchanger described in the above-mentioned Embodiment 1-5 and the air-conditioning refrigerating apparatus provided with this heat exchanger, the effect can be achieved in refrigerant | coolants, such as R410A, R32, HFO1234yf.

  Moreover, although the example of air and a refrigerant | coolant was shown as a working fluid, even if it uses other gas, liquid, and gas-liquid mixed fluid, there exists the same effect.

  Moreover, the same effect can be produced even when the heat exchanger described in the first to fifth embodiments is used in an indoor unit.

  In addition, with respect to the heat exchanger described in the first to fifth embodiments and the air-conditioning refrigeration apparatus using the heat exchanger, a refrigerant and an oil such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil are used. The effect can be achieved with any refrigeration oil, whether or not it melts.

  In the first to fifth embodiments described above, the flat tube group has a two-row configuration of the windward flat tube group 11A and the leeward flat tube group 11B, but may have a plurality of rows. Also in this case, drainage performance can be secured by providing the first drainage portion 17 similar to the above in the corrugated fins 12 at the portion corresponding to the inter-row. Moreover, the 2nd drainage part 18 and the 3rd drainage part 19 are similarly applicable in a multi-row structure.

  In the above-described first to fifth embodiments, the embodiments have been described as different embodiments, but a heat exchanger and an air-conditioning refrigeration apparatus including the heat exchanger by appropriately combining the characteristic configurations of the embodiments. May be configured. For example, the second embodiment shown in FIG. 6 may be combined with the eighth embodiment shown in FIG. 8, and the third drainage unit 19 may be further provided in FIG.

  Further, in each of the first to fifth embodiments, the modification applied to the same components is similarly applied to other embodiments other than the embodiment described for the modification.

  As an application example of the present invention, it can be used in a heat pump device that is easy to manufacture, needs to improve heat exchange performance, and improve energy saving performance.

  DESCRIPTION OF SYMBOLS 1 Heat exchanger, 10 Heat exchange part, 11 Flat tube, 11A Upwind flat tube group, 11B Downward flat tube group, 11a Through-hole, 11b Flat tube wind upper end, 11c Flat tube leeward end, 12 Corrugated fin, 12a Fin wind upper end, 12b Fin wind lower end, 13 plane portion, 14 curved portion, 15 louver, 16 row clearance, 16a row clearance, 17 first drainage portion, 18 second drainage portion, 19 third drainage portion , 20 (20a, 20b) header, 30 header, 40 bar, 41 drainage path, 50 plate, 51 drainage path, 61 compressor, 62 condenser, 63 throttle device, 64 evaporator, 65 blower, 66 blower motor.

Japanese Patent Laying-Open No. 2005-24187 (FIG. 1) Japanese Patent No. 4786234 (FIG. 1)

The heat exchanger according to the present invention has a flat tube group provided in a plurality of rows with gaps between rows in the depth direction of the heat exchanger, and corrugated fins provided in common in the plurality of flat tube groups, The flat tube group is provided with a heat exchanging portion composed of a plurality of flat tubes arranged in a gravitational direction, and the corrugated fin is formed in a portion located between the rows of the flat tube group, and between the row gaps It has the 1st drainage part which communicates, and a plurality of louvers cut and raised so as to incline with respect to the fin surface, and each of the plurality of louvers is inclined downward toward the first drainage part. It is what has been .

Claims (14)

A flat tube group provided in a plurality of rows with gaps between rows in the depth direction of the heat exchanger, and corrugated fins provided in common to the flat tube groups in the plurality of rows, wherein the flat tube group is in the direction of gravity A heat exchanging part composed of a plurality of flat tubes arranged upright,
The corrugated fin has a first drainage portion that communicates between the row gaps at a portion located between the rows of the flat tube group.   The heat exchanger according to claim 1, wherein the first drainage part is a groove that is concave downward in the direction of gravity.   The heat exchanger according to claim 1 or 2, wherein the corrugated fin has a shape in which flat portions and curved portions are alternately arranged, and the first drainage portion is formed in the flat portion.   The heat exchanger according to claim 3, wherein the flat portion is inclined in the direction of gravity.   A member that extends in the direction of gravity, wherein a drainage promoting body that divides the gap between the rows into a portion that communicates with the first drainage portion and other portions is disposed between the row gaps. The heat exchanger according to any one of claims 4 to 5.   The heat exchanger according to claim 5, wherein the drainage promotion body is a rod.   The heat exchanger according to claim 6, wherein the rod is fixed to at least one of the corrugated fin and the flat tube by a brazing material previously attached to an outer periphery of the rod.   The heat exchanger according to claim 5, wherein the drainage promotion body is a rectangular plate that is curved in an arc shape in a short direction.   The heat exchanger according to claim 8, wherein the plate is fixed to the corrugated fin by a brazing material attached to both side surfaces of an arc of the plate.   The heat according to any one of claims 1 to 9, further comprising a second drainage portion configured such that an upwind end of the corrugated fin extends to an upwind side of an upwind end of the flat tube. Exchanger.   The heat according to any one of claims 1 to 10, further comprising a third drainage portion configured such that the leeward side end of the corrugated fin extends to the leeward side of the leeward side end of the flat tube. Exchanger.   The heat exchanger according to claim 11, which is dependent on claim 10, wherein the extension distance of the third drainage part is shorter than the extension distance of the second drainage part.   The corrugated fin has a plurality of louvers cut and raised so as to be inclined with respect to the fin surface, and each of the plurality of louvers is inclined downward toward a central portion in the depth direction of the heat exchanger. The heat exchanger as described in any one of Claims 1-12 currently formed.   An air-conditioning refrigeration apparatus comprising the heat exchanger according to any one of claims 1 to 13.

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