JP5627632B2 - Heat exchanger and heat pump device - Google Patents

Description

  The present invention relates to a heat exchanger and a heat pump apparatus using the heat exchanger.

  Conventionally, a fin tube type heat exchanger in which a flat portion of a flat tube is horizontally disposed and fins are disposed between the flat portion and the flat portion has been widely used. In such a finned tube heat exchanger, in order to improve the drainage of condensed water condensed with moisture contained in the passing air, the corrugated fin end protrudes to the leeward side, and a notch is provided in this protruding portion. Have been proposed (see, for example, Patent Document 1).

  Moreover, in order to improve the drainage of condensed water, a heat exchanger has been proposed in which corrugated fins protrude from between the flat part and the condensed water flows downward through the protruding part (for example, , See Patent Document 2).

  Further, in order to improve the drainage of condensed water, “a plurality of fins 1 arranged in parallel with each other with a narrow gap therebetween, and these fins are provided in parallel with each other and penetrating each other. A plurality of flat heat exchange pipes 2 and a first header pipe 3A and a second header pipe 3B respectively connected to both end portions projecting from the fins of the heat exchange pipes. The fin is made of an aluminum brazing sheet, and includes a plurality of punching holes 11 that are parallel to each other and between the through holes of the heat exchange pipe, and fine wire fins 12 that are formed between these punching holes. A heat exchanger has been proposed (see, for example, Patent Document 3).

Japanese Utility Model Publication No. 63-6632 (page 3, Fig. 3) JP 2008-101847 A (page 6, FIG. 1) JP-A-6-307785 (summary)

  In the technique described in Patent Document 1, condensed water droplets (condensed water) gather on the downstream side of the air flow and fall downward from the notch. However, the condensed water falls from the notch when the condensed water grows to a size that can be dropped by its own weight, and the condensed water may stay in the heat exchanger for a while, and the condensed water is ventilated. There existed a subject which becomes resistance and reduces heat exchange performance.

  In the technique described in Patent Document 2, in order to improve drainage, the fin is protruded from between the flat portion and the flat portion, and the dew condensation water flows downward through the protruding portion. However, in a situation where the heat exchanger is further downsized, the downsizing of the heat exchanger is likely to reduce the drainage of the heat exchanger with respect to condensed water, and further improvement of drainage is required. .

  In the technique described in Patent Document 3, the drainage of condensed water is improved by a fin portion having no punching hole. However, when the rigidity of the fin having the punched hole is weak, there is a problem that a clearance is generated between the heat exchange pipe and the fin, resulting in a defect when brazed.

Further, when the fin tube type heat exchanger is used in an environment where frost formation occurs (for example, it is used as an outdoor heat exchanger in an environment where the outside air temperature is about 2 degrees or less and the refrigerant evaporation temperature is zero degrees or less. ), Frost formation is likely to occur on the windward fins and flat tubes having a large amount of absolute humidity in the air, and there is a problem that the airflow resistance is increased and the air flow is reduced to reduce the heat exchange performance.
Moreover, also in the defrost operation which melt | dissolves frost, the condensed water stagnated on the fin and the subject which the retained condensed water became a base point and it became easy to produce frost occurred.

  In a finned tube heat exchanger in which corrugated fins are brazed and joined to a flat tube, the corrugated fins are annealed by brazing, which greatly reduces the proof strength of the corrugated fins and reduces the fin buckling strength. In some cases, the fins easily fall over. When the fin collapse occurs, there is a problem that the air flow resistance is increased, the air volume is decreased, and the heat exchange performance is decreased.

The present invention has been made to solve the above-described problems, and provides a heat exchanger capable of improving the drainage of condensed water and a heat pump device using the heat exchanger.
Moreover, the heat exchanger which can improve heat-transfer performance, and a heat pump apparatus using the same are obtained.
Moreover, the heat exchanger which can suppress the reduction | decrease in the rigidity of a fin, and a heat pump apparatus using the same are obtained.

The heat exchanger according to the present invention has a flat tube in which the direction of the long axis of the flat shape faces the flow direction of the air flow, and a plurality of flat tubes arranged at intervals in the direction of the short axis of the flat shape, A plurality of flat tubes, each having a plate-like shape through which an airflow flows, and having a plurality of flat tubes inserted therein, into which the airflow upstream side of the flat tubes is inserted; A plurality of first plate-like fins joined to the tube, and a plate-like shape in which a plurality of airflows are arranged between the first plate-like fins, and notches for inserting the plurality of flat tubes are formed, An air flow downstream side of the flat tube is inserted into the notch, and a second plate-like fin joined to the plurality of flat tubes, and an arrangement interval of the second plate-like fins is set to the first plate fin . This is shorter than the arrangement interval of the plate-like fins.

  The present invention inserts and joins the airflow upstream side of the flat tube to the first plate-like fin formed with the notch, and connects the airflow downstream side of the flat tube to the second plate-shaped fin formed with the notch. Since they are inserted and joined, both sides of the first and second plate-like fins on the side not having the notch can be used as drainage paths for the condensed water, and the drainage of the condensed water can be improved.

It is a block diagram of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view of the heat exchanger which concerns on Embodiment 1 of this invention. It is a figure explaining the assembly of the heat exchanger which concerns on Embodiment 1 of this invention. It is a block diagram of the air conditioner which concerns on Embodiment 1 of this invention. It is a figure explaining the drainage behavior of the condensed water of the heat exchanger which concerns on Embodiment 1 of this invention. It is a block diagram of the heat exchanger which concerns on Embodiment 2 of this invention. It is a block diagram of the heat exchanger which concerns on Embodiment 3 of this invention. It is a block diagram of the heat exchanger which concerns on Embodiment 4 of this invention.

Embodiment 1 FIG.
FIG. 1 is a configuration diagram of a heat exchanger according to Embodiment 1 of the present invention. FIG. 2 is a perspective view of the heat exchanger according to Embodiment 1 of the present invention. FIG. 3 is a diagram illustrating assembly of the heat exchanger according to Embodiment 1 of the present invention. In addition, in FIGS. 1-3, the principal part of the heat exchanger is shown typically.
As shown in FIGS. 1 to 3, the finned tube heat exchanger according to the first embodiment includes a plate-like fin 1, a plate-like fin 2, and a flat tube 3. This fin tube type heat exchanger is mounted on a heat pump device such as an air conditioner, for example, and exchanges heat between the air passing through the heat exchanger and the refrigerant flowing through the flat tube 3.

  The flat tube 3 is a heat transfer tube made of, for example, aluminum and having a flat or wedge-shaped cross-sectional outer shape. A plurality of flat tubes 3 are arranged with the long axis direction of the flat shape facing the flow direction of the air flow (left and right direction on the paper surface) and spaced apart in the direction of the short axis of the flat shape (vertical direction on the paper surface). Headers are connected to both ends of the flat tube 3, and the refrigerant is distributed to the flat tubes 3. In the flat tube 3, a plurality of refrigerant channels divided by partition walls are formed.

The plate-like fin 1 and the plate-like fin 2 are made of, for example, aluminum and have a plate-like shape. A plurality of the plate-like fins 1 and the plate-like fins 2 are arranged at a predetermined interval, and an air current flows between them.
Further, the plate-like fin 1 is formed with notches 1a for inserting a plurality of flat tubes 3, respectively, and the air flow upstream side of the flat tubes 3 is inserted into the notches 1a and joined to the plurality of flat tubes 3. ing.
Further, the plate-like fin 2 is formed with notches 2a for inserting a plurality of flat tubes 3, respectively, and the air flow downstream side of the flat tubes 3 is inserted into the notches 2a and joined to the plurality of flat tubes 3. ing.

  The plate fin 1 corresponds to the “first plate fin” in the present invention, and the plate fin 2 corresponds to the “second plate fin” in the present invention.

In the first embodiment, the length obtained by adding the length Lp1 of the notch 1a formed in the plate-like fin 1 and the length Lp2 of the notch formed in the plate-like fin 2 is the length of the flat tube 3 It is formed to be equal to the length of the shaft. For example, the lengths Lp1 and Lp2 are both set to a length that is half the long axis of the flat tube 3.
Further, the pitch Fp in the arrangement direction of the plate fin 1 and the plate fin 2 is the same, and the end surface of the plate fin 1 on the notch 1a side and the end surface of the plate fin 2 on the notch 2a side are brought into contact with each other. Is arranged.
For example, in the first embodiment, the pitch Fp in the arrangement direction of the plate-like fins 1 and 2 is Fp = 0.016 m, the fin thickness Ft is Ft = 0.0001 m, and the fin width Fd in the air flow passage direction is The distance Dp between the centers of the flat tubes 3 adjacent to each other in the stage direction of the heat exchanger is Dp = 0.015 m. Note that these values are specific examples, and different values may be used.

Here, the assembly process of the fin tube type heat exchanger in the present embodiment will be described.
For example, a finning process for forming the plate-like fins 1 and 2 with a mold press machine is performed. Thereafter, each flat tube 3 is inserted into the notch 1a of the plate-like fin 1 and the notch 2a of the plate-like fin 2, and the plate-like fins 1 and 2 and the flat tube 3 are brought into close contact with each other.
Since the cross-sectional shape of the flat tube 3 is a flat shape or a wedge shape, the plate-like fins 1 and 2 are inserted into the flat tube 3 without a gap, and the close contact between the plate-like fins 1 and 2 and the flat tube 3 becomes good. .

Next, the flat tube 3 is brazed and joined to the plate-like fins 1 and 2.
One or two brazing members are disposed at the end of the flat tube 3 in the form of a rod shorter than the width of the flat tube 3. Thereafter, it is put into a Noclock continuous furnace and heat-bonded, and a hydrophilic treatment coating material is applied to the surfaces of the plate-like fins 1 and 2 to complete. Alternatively, it is also possible to apply a brazing material to the flat tube 3 in advance and braze and join it. By applying the brazing material to the flat tube 3 in advance, the work time for arranging the rod-shaped brazing material on the flat tube 3 is shortened, and the production efficiency is improved. In addition, you may use the clad fin by which the brazing material was previously clad on the both sides or one side of the plate-like fins 1 and 2.

  Next, an example of a heat pump apparatus having the above heat exchanger will be described.

FIG. 4 is a configuration diagram of the air conditioner according to Embodiment 1 of the present invention.
As shown in FIG. 4, an air conditioner as a heat pump device includes a compressor 10, a four-way valve 11, an outdoor heat exchanger 12 mounted on an outdoor unit, an expansion valve 13 that is an expansion means, The indoor side heat exchanger 14 mounted on the machine is sequentially connected by refrigerant piping, and has a refrigerant circuit for circulating the refrigerant.
The four-way valve 11 switches between the heating operation and the cooling operation by switching the direction in which the refrigerant flows in the refrigerant circuit. In addition, when it is set as the air conditioner only for cooling or heating, the four-way valve 11 may be omitted.
The outdoor heat exchanger 12 corresponds to the fin-tube heat exchanger described above, and functions as a condenser that heats air or the like with the heat of the refrigerant during the cooling operation, and evaporates the refrigerant during the heating operation. It functions as an evaporator that cools air or the like by heat of vaporization at that time.
The indoor heat exchanger 14 corresponds to the fin tube heat exchanger described above, and functions as a refrigerant evaporator during the cooling operation and functions as a refrigerant condenser during the heating operation.
The compressor 10 compresses the refrigerant discharged from the evaporator and supplies it to the condenser at a high temperature.
The expansion valve 13 expands the refrigerant discharged from the condenser, supplies it to the evaporator at a low temperature.

Next, the drainage behavior of the condensed water generated in the heat exchanger will be described.
FIG. 5 is a diagram illustrating the drainage behavior of the condensed water of the heat exchanger according to Embodiment 1 of the present invention.
As shown in FIG. 5, the heat exchanger is mounted on a heat pump device such as an air conditioner so that the arrangement direction (stage direction) of the plurality of flat tubes 3 faces the direction of gravity.
When the heat exchanger exchanges heat between the air flowing through the heat exchanger and the refrigerant flowing through the flat tube 3, the surface of the plate-like fins 1 and 2 and the flat tube 3 is contained in the air. Water vapor is condensed and water droplets (condensed water) are generated.
In the heat exchanger according to the present embodiment, the upstream side of the airflow of the plate-like fin 1 (the side without the notch 1a) functions as the drainage portion 1b through which the condensed water flows, and the downstream side of the airflow of the plate-like fin 2 (the cut-off) The side without the notch 2a) functions as a drainage part 2b through which condensed water flows.

  As described above, in the present embodiment, the airflow upstream side of the flat tube 3 is inserted and joined to the plate-like fin 1 in which the notch 1a is formed, and the plate-like fin 2 in which the notch 2a is formed is flattened. The air flow downstream side of the tube 3 was inserted and joined. Therefore, both sides of the plate-like fins 1 and 2 on the side not having the notch can be used as drainage paths for condensed water. For example, when corrugated fins are provided between the flat tubes, the plate-like fins are provided only on one side of the flat tubes. Compared with the case where it provides in, the drainage of condensed water can be improved.

  In the present embodiment, the length obtained by adding the notch lengths Lp1 and Lp2 is equal to the length of the long axis of the flat tube 3, and the end face of the plate-like fin 1 and the plate-like fin 2 It is in contact with the end face. For this reason, the plate-like fins 1 and 2 are brazed and joined over the entire circumference of the flat tube 3, and heat is transmitted from the entire circumference of the flat tube 3 to the on-plate fins. Therefore, heat transfer performance can be improved. For example, when corrugated fins are provided between flat tubes, the brazed joint locations of the corrugated fins are only on the side portions of the flat tubes, and when plate fins are provided only on one side of the flat tubes, The brazed joint locations are only the side surface portion of the flat tube and the curved surface portion on one side, and heat transfer performance can be improved compared to these.

In this embodiment, the length Lp of the notch formed in one plate-like fin can be shortened compared to the case where the plate-like fin is provided only on one side of the flat tube. Reduction in rigidity can be suppressed. Thereby, in the process of inserting the flat tube 3 into the notches 1a and 2a of the plate-like fins 1 and 2, the flat tube 3 can be inserted without being disturbed by the plate-like fins 1 and 2, and there is no brazing defect. Can be joined. For example, if the rigidity of the fin is weak, the fin is disturbed in the process of inserting the flat tube into the notch of the plate-like fin, the clearance between the fin collar and the flat tube is increased, and brazing failure occurs.
Further, in order to improve the heat transfer performance of the heat exchanger, even when the flat tube 3 is mounted at a high density by reducing the center distance Dp of the flat tube 3, for example, plate-like fins are provided only on one side of the flat tube. Compared to the case, the length Lp of the notch can be shortened, and the fin rigidity can be ensured.

  In the present embodiment, plate-like fins 1 and 2 serving as drainage paths for condensed water are provided on both sides of the air flow upstream and downstream of the flat tube 3 (both sides of the flat curved surface portion). When the flat tubes 3 are arranged in a plurality of rows, there is no useless gap between the rows, and the flat tubes 3 can be installed compactly. For example, when the thickness of the header is increased in order to ensure the pressure resistance of the header connected to the end portion of the flat tube 3, a gap is generated between the rows of the flat tubes 3. Since the both side plate-like fins 1 and 2 are provided, there is no useless gap between the rows, so that the installation can be performed in a compact manner, and the header design of a plurality of rows is easy.

Embodiment 2. FIG.
FIG. 6 is a configuration diagram of a heat exchanger according to Embodiment 2 of the present invention.
As shown in FIG. 6, in this Embodiment 2, it arrange | positions so that the plate-shaped fin 1 and the plate-shaped fin 2 may not overlap in the distribution direction of airflow. For example, the plate-like fins 2 are installed at half the pitch Fp of the plate-like fins 1.
Other configurations are the same as those of the first embodiment.

Also in the present embodiment, the same effect as in the first embodiment can be obtained.
Moreover, in this Embodiment, since it arrange | positions so that the plate-shaped fin 1 and the plate-shaped fin 2 may not overlap, heat-transfer performance can further be improved with the front edge effect of the front-end | tip of the plate-shaped fin 2. FIG. .

Embodiment 3 FIG.
FIG. 7 is a configuration diagram of a heat exchanger according to Embodiment 3 of the present invention.
As shown in FIG. 7, in Embodiment 3, the pitch Fp <b> 2 (arrangement interval) in the arrangement direction of the plate-like fins 2 is shorter than the pitch Fp <b> 1 in the arrangement direction of the plate-like fins 1. For example, the pitch Fp2 of the plate-like fins 2 is half of the pitch Fp1 of the plate-like fins 1. Further, every other plate-like fin 2 is arranged so as to contact the end face of the plate-like fin 1.
Other configurations are the same as those of the first embodiment.

Also in the present embodiment, the same effect as in the first embodiment can be obtained.
Further, in the present embodiment, since the pitch Fp1 of the plate-like fins 1 located upstream of the airflow is larger than Fp2, the frost formation on the windward plate-like fins 1 having a large amount of absolute humidity in the air increases. Even so, an increase in ventilation resistance can be suppressed, a decrease in heat exchange performance can be suppressed, and the frost resistance can be improved.

Embodiment 4 FIG.
FIG. 8 is a configuration diagram of a heat exchanger according to Embodiment 4 of the present invention.
As shown in FIG. 8, in the fourth embodiment, the length Lp1 of the notch 1a formed in the plate-like fin 1 and the length Lp2 of the notch 2a formed in the plate-like fin 2 are added. The length is formed to be longer than the length of the long axis of the flat tube 3. For example, both the lengths Lp1 and Lp2 are set to be longer than half of the length of the long axis of the flat tube 3 and shorter than the length of the long axis of the flat tube 3.
In addition, the pitch Fp in the arrangement direction of the plate-like fins 1 and the plate-like fins 2 is the same, and the plate-like fins 1 and part of the plate-like fins 2 are arranged so as to overlap in the arrangement direction.
Furthermore, the plate-like fins 2 are installed at positions half the pitch Fp of the plate-like fins 1 so that the plate-like fins 1 and the plate-like fins 2 do not overlap in the airflow distribution direction.
Other configurations are the same as those of the first embodiment.

Also in the present embodiment, the same effect as in the first embodiment can be obtained.
Further, when the end portions of the plate-like fins 1 and the plate-like fins 2 are brought into contact with each other, there may be a gap on the contact surface between the plate-like fins 1 and the plate-like fins 2 at the time of manufacture, and this gap is reduced. In the present embodiment, the plate-like fins 1 and the plate-like fins 2 are overlapped so that part of the plate-like fins 1 and part of the plate-like fins 2 overlap each other. It is not necessary to manage the gap between the contact surfaces between them, and the productivity can be improved.

  As an application example of the present invention, it can be used in a heat exchanger of a heat pump apparatus that requires improved heat exchange performance and improved performance.

  DESCRIPTION OF SYMBOLS 1 Plate-like fin, 1a Notch, 1b Drain part, 2 Plate-like fin, 2a Notch, 2b Drain part, 3 Flat tube, 10 Compressor, 11 Four-way valve, 12 Outdoor heat exchanger, 13 Expansion valve, 14 Indoor heat exchanger.

Claims (2)

A flat tube in which the direction of the long axis of the flat shape faces the flow direction of the airflow, and a plurality of flat tubes are arranged at intervals in the direction of the short axis of the flat shape
A plurality of flat plates are arranged at a predetermined interval and airflow flows therethrough, and notches for inserting the plurality of flat tubes are formed, and the airflow upstream side of the flat tubes is inserted into the notches. A first plate-like fin joined to the plurality of flat tubes;
A plurality of plates are arranged at a predetermined interval, and a plate-like shape through which an airflow flows is formed. Notches for inserting the plurality of flat tubes are respectively formed, and an airflow downstream side of the flat tubes is inserted into the notches. A second plate-like fin joined to the plurality of flat tubes;
With
A heat exchanger characterized in that an arrangement interval of the second plate fins is shorter than an arrangement interval of the first plate fins. A compressor, a condenser, an expansion means, and an evaporator are sequentially connected by piping to provide a refrigerant circuit for circulating the refrigerant,
The heat exchanger according to claim 1 is used as at least one of the condenser and the evaporator,
The heat exchanger is installed in such a manner that the arrangement direction of the plurality of flat tubes is directed in the direction of gravity.

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