JPWO2014155560A1 - Heat exchanger and refrigeration cycle air conditioner using the same - Google Patents

Abstract

The heat exchanger 1 includes a parallel flow type heat exchange unit 3 having a plurality of heat exchange pipes 11 and 13 extending in the vertical direction. The parallel flow type heat exchange unit includes at least a front row portion 7 and a rear row portion 9. Each of the front row portion and the rear row portion has a plurality of heat exchange pipes extending in the vertical direction. A plate fin and tube type heat exchange unit 5 having plate fins 25 is arranged, and an outlet end of the plate fin and tube type heat exchange unit and an inlet end of the parallel flow type heat exchange unit are connected by a pipe. Yes.

Description

  The present invention relates to a heat exchanger and a refrigeration cycle air conditioner using the same.

  In heat exchangers, a decrease in heat exchange capacity due to frost formation is often a problem. As an invention related to such a problem, for example, there is a heat exchanger disclosed in Patent Document 1. In this heat exchanger, the heat exchanging parts are separated into the front and rear and arranged in the front and rear direction, and between the pair of heat exchanging parts and between the pair of header parts above and below the heat exchanging part, respectively. In addition, ensure a gap.

  According to such a heat exchanger, even if either one of the front and rear heat exchange parts loses air permeability due to frost formation, the other heat exchange part passes through the air flow through the gap and the minimum heat exchange is performed. It is intended to provide functionality.

JP-A-8-226727 (FIG. 1)

  However, in the conventional heat exchanger described above, it is not considered to suppress the growth of frost when it is used as an evaporator, and the frost once generated at the lower part of the heat exchanger is defrosted. There was a problem that it was difficult.

  This invention is made | formed in view of the above, and it aims at providing the heat exchanger which can suppress the growth of the frost which accumulates on the heat exchanger lower part.

  The present invention for achieving the above-described object is a heat exchanger including a parallel flow type heat exchange unit having a plurality of heat exchange pipes extending in the vertical direction, and the parallel flow type heat exchange unit includes at least a front row. A front row portion and a rear row portion, each of the front row portion and the rear row portion having a plurality of heat exchange pipes extending in the vertical direction, and in front of the lower portion of the front surface of the parallel flow type heat exchange portion. Is provided with a plate fin and tube type heat exchanging part each having a plurality of plate fins extending in the vertical direction, and an outlet end of the plate fin and tube type heat exchanging part and the parallel flow type heat exchanging part The inlet end is connected by piping.

  According to the present invention, it is possible to suppress the growth of frost accumulated in the lower part of the heat exchanger.

It is a front view of the heat exchanger which concerns on Embodiment 1 of this invention. It is a side view of the heat exchanger which concerns on this Embodiment 1. It is a figure of the same aspect as FIG. 1 regarding Embodiment 2 of this invention. It is a figure of the same aspect regarding FIG. It is a figure which shows the outline | summary of the refrigerating-cycle air conditioning apparatus which concerns on Embodiment 3 of this invention. It is a top view which shows typically the outdoor unit of the refrigerating-cycle air conditioning apparatus which concerns on this Embodiment 3.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. In the drawings, the same reference numerals indicate the same or corresponding parts. The directions in the description are “front” for the upstream side of the intended ventilation, “rear” for the downstream side, “down” for the direction of gravity, “up” for the opposite direction, and the front-rear direction and the vertical direction. The direction orthogonal to both the directions (gravity direction) is set as “left and right”. As an example, FIG. 2 shows the up and down direction in FIG. 2, the left and right sides in FIG. 2 are the front side and the rear side, and the front and back direction of the page in FIG. Note that the reference symbol WD in FIG. 2 indicates the airflow direction of ventilation.

Embodiment 1 FIG.
1 and 2 are a front view and a side view of the heat exchanger according to Embodiment 1 of the present invention, respectively. The heat exchanger 1 is an aluminum heat exchanger used for an outdoor unit of a refrigeration cycle air conditioner.

  The heat exchanger 1 includes a parallel flow type heat exchange unit 3. A plate fin and tube type heat exchanging unit 5 is provided in front of the parallel flow type heat exchanging unit 3 in the heat exchanger 1.

  First, the parallel flow type heat exchange unit 3 includes a front row portion 7 and a rear row portion 9 that are separated from each other in the front-rear direction and are arranged in the front-rear direction. Each of the front row portion 7 and the rear row portion 9 has a plurality of heat exchange pipes 11 and 13 extending in the vertical direction. The heat exchange pipes 11 and 13 are flat tubes that are crushed from the left-right direction. The plurality of heat exchange pipes 11 in the front row portion 7 are arranged in the left-right direction, and the plurality of heat exchange pipes 13 in the rear row portion 9 are also arranged in the left-right direction. Between the plurality of heat exchange pipes 11 in the front row portion 7 and the plurality of heat exchange pipes 13 in the rear row portion 9, gaps 15 are secured in the front-rear direction, and the heat exchange pipe 11 and the heat exchange pipe 13 It is far away. Further, as an example, the number of heat exchange pipes 11 and the number of heat exchange pipes 13 are the same.

  Fins 17 are provided between the plurality of heat exchange pipes 11 and 13. Specifically, the fins 17 are corrugated fins and extend in the vertical direction while meandering left and right between each pair of adjacent fins. In other words, the fins 17 are formed in a corrugated shape so as to alternately contact the left heat exchange pipe and the right heat exchange pipe.

  The heat exchange pipes 11 and 13 are arranged in two rows in the front-rear direction, but the fins 17 are in a row in the front-rear direction. That is, the continuous corrugated fins are located between the corresponding pair of heat exchange pipes 11 in the front row portion 7 and located between the corresponding pair of heat exchange pipes 13 in the rear row portion 9. The fin 17 protrudes in the windward direction from the heat exchange pipe 11 of the front row portion 7, that is, the front edge portion of the fin 17 is positioned in front of the front end of the heat exchange pipe 11 of the front row portion 7.

  An inlet header 19 that is a lower header on the front row portion 7 side is provided at the lower portion of the front row portion 7, and an outlet header 21 that is a lower header on the rear row portion 9 side is provided at the lower portion of the rear row portion 9. Yes. A row straddling header 23 is provided above the front row portion 7 and the rear row portion 9. The front row portion 7 and the rear row portion 9 share the same row crossing header 23 as their upper headers. In addition, each of the inlet header 19, the outlet header 21 and the row-crossing header 23 is configured as one room. Thus, the lower headers of the front row portion 7 and the rear row portion 9 are provided separately for each row, and the upper headers of the front row portion 7 and the rear row portion 9 are provided integrally across the rows. .

  In terms of functionality, the inlet header 19 and the outlet header 21 arranged at the lower part of the parallel flow type heat exchanging unit 3 have a mechanism for uniform distribution to the heat exchange pipes in the leeward row, on the leeward side. The row has a mechanism for concentrating the gas, and the lower header is divided for each row in the parallel flow type heat exchange unit 3 as a whole. On the other hand, the row-crossing header 23 arranged at the upper part of the parallel flow type heat exchange unit 3 has a mechanism that allows refrigerant to move between the rows. Two rows are provided as a unit.

  The lower end of the heat exchange pipe 11 in the front row portion 7 is connected to the inlet header 19, and the upper end of the heat exchange pipe 11 in the front row portion 7 is connected to the row crossing header 23. Further, the lower end of the heat exchange pipe 13 in the rear row portion 9 is connected to the outlet header 21, and the upper end of the heat exchange pipe 13 in the rear row portion 9 is connected to the row crossing header 23.

  The plate fin and tube type heat exchanging unit 5 is disposed in front of the lower part of the front surface of the parallel flow type heat exchanging unit 3, and more specifically, in front of the lower part of the front surface of the front row portion 7 and the inlet header 19. It is arranged above. The lowermost part of the plate fin and tube type heat exchanging unit 5 (the lowermost part of the plate fin 25) is located between the lowermost part of the fins 17 of the parallel flow type heat exchanging unit 3 and the inlet header 19.

  The plate fin and tube type heat exchanging section 5 has a plurality of plate fins 25 and a heat transfer pipe 27 for constituting at least one path.

  Each of the plurality of plate fins 25 extends in the vertical direction and is arranged substantially parallel to the horizontal direction. Further, the rear portions of the plurality of plate fins 25 are in contact with or approaching the front ends of the lower portions of the fins 17 of the parallel flow heat exchange unit 3.

  In the illustrated example, the heat transfer pipe 27 is a single circular pipe that forms one path, and extends vertically through the plurality of plate fins 25 so as to meander in the left-right direction. An inlet end 27a of the heat transfer pipe 27, which serves as a refrigerant inlet when functioning as an evaporator, is disposed below the plate fin 25, and serves as a refrigerant outlet when functioning as an evaporator. The outlet end 27 b is disposed on the upper portion of the plate fin 25. As the heat transfer pipe 27, a plurality of circular pipes may be used so as to form a plurality of paths as long as the number is less than the number of paths of the parallel flow heat exchange unit 3. Further, the heat transfer pipe 27 may be one or more flat tubes (plate fin and flat tube type) instead of the one or more circular tubes (plate fin and circular tube type). .

  The plate fin and tube type heat exchanging unit 5 and the parallel flow type heat exchanging unit 3 are connected by a connecting pipe 29. That is, one end of the connecting pipe 29 is connected to the outlet end 27b of the heat transfer pipe 27 of the plate fin and tube type heat exchanging unit 5, and the inlet end 19a of the inlet header 19 in the parallel flow type heat exchanging unit 3 is The other end of the connecting pipe 29 is connected.

  Next, the flow of the refrigerant will be described. In addition, the arrow shown by FIG.1 and FIG.2 shows typically the flow of the refrigerant | coolant in case the heat exchanger 1 functions as an evaporator. Therefore, when the heat exchanger 1 functions as a condenser, the refrigerant flows in the direction opposite to the arrow. When the heat exchanger 1 is used as an evaporator (for example, when installed in an outdoor unit and operated for heating), the refrigerant flows from the bottom to the top in one pass through the plate fin and tube heat exchanger 5. Then, after flowing out from the plate fin and tube type heat exchanging section 5 and passing through the connecting pipe 29, it flows into the inlet header 19 of the parallel flow type heat exchanging section 3. The refrigerant in the inlet header 19 flows from the bottom to the top through the plurality of heat exchange pipes 11 in the front row portion 7 on the windward side. That is, the number of paths is the same as the number of heat exchange pipes 11, and the front row portion 7 is lifted, and then flows into the row crossing header 23. Furthermore, after the refrigerant flows into the row-crossing header 23, the refrigerant flows from the top to the bottom through the plurality of heat exchange pipes 13 in the rear row portion 9 on the leeward side. That is, after flowing down the rear row portion 9 with the same number of paths as the number of heat exchange pipes 13, it flows into the outlet header 21 and finally flows out of the heat exchanger 1.

  In the first embodiment configured as described above, the following advantages are obtained. In the heat exchanger 1, since the plate fin and tube type heat exchange unit 5 is provided, condensed water is guided from the inlet header 19 and the fins 17 to the plate fins 25 during operation where frost formation may occur. That is, the condensed water mainly collects in the plate fin and tube type heat exchanging unit 5 having good drainage, and thus root ice can be prevented from being stacked on the lower part of the heat exchanger 1.

  Further, the number of passes of the plate fin and tube type heat exchanging unit 5 is smaller than the number of passes of the parallel flow type heat exchanging unit 3, and the pressure loss in the pipe through which the refrigerant passes is plate fin and tube type heat exchanging. The part 5 is larger than the parallel flow heat exchange part 3. Therefore, the evaporation temperature of the plate fin and tube heat exchange unit 5 is higher than the evaporation temperature of the parallel flow type heat exchange unit 3, the amount of frost formation during operation is reduced, and frost is formed in the lower part of the heat exchanger 1. Concentration can be suppressed. Moreover, when the heat exchanger 1 is used as a condenser, the flow rate of a supercooling part can be raised and the heat transfer rate in a pipe | tube can be improved, and heat exchanger efficiency improves.

  Further, when the heat exchanger 1 is used as an evaporator, the inlet of the plate fin-and-tube heat exchanger 5 is provided at the lowermost part of the plate fin-and-tube heat exchanger 5, so that the heat exchanger The temperature of the lowest part of 1 can be raised, and the amount of frost formation can also be suppressed by it.

Further, since the fins 17 used in the parallel flow type heat exchange section 3 are integrally formed with the two heat exchange pipes 11 and 13 in the front and rear rows, the layout of the heat exchange pipes 11 and 13 is parallel to each other. When two front and rear rows are provided in such a manner, the assemblability can be improved.
Moreover, the heat | fever cutoff is provided in the site | part between the row | line | columns before and behind in the fin 17, Thereby, the heat transfer by the temperature difference between the heat exchange pipes 11 and 13 can be suppressed, and heat exchanger efficiency Can be improved.

  Moreover, since the fin 17 is protruded and fixed to the heat exchange pipe 11 in the windward direction, the temperature of the front edge of the fin 17 is brought close to the air temperature, and the front edge of the fin 17 during the frosting operation. It is possible to avoid frost concentration.

  Further, as the first embodiment, a heat exchange method using the heat exchanger 1 can be mentioned. In the present heat exchange method, when the heat exchanger 1 functions as an evaporator, the refrigerant and the air are roughly Flowing in parallel (flowing in the same direction) (macroscopically, refrigerant and air flow from the front to the rear), the refrigerant has an evaporation temperature that decreases with respect to the flow direction due to pressure loss, and the air also has a temperature in the flow direction. Since the temperature decreases, the temperature difference between the refrigerant and air decreases. On the other hand, when functioning as a condenser, the refrigerant and the air generally flow in opposite directions (flow in the opposite direction) (air flows from the front to the rear, and the refrigerant flows from the rear to the front as viewed macroscopically). In the superheated, two-phase, supercooled region, the temperature of the refrigerant decreases with respect to the flow direction, and the temperature of the air increases with respect to the flow direction. Therefore, the temperature difference between the refrigerant and air becomes small. This also improves the heat exchanger efficiency. In other words, when the heat exchanger 1 functions as an evaporator as a refrigerant flow path across the parallel flow type heat exchange unit 3 and the plate fin and tube type heat exchange unit 5, the refrigerant and the air have the same direction in the front-rear direction. The refrigerant flow path has a refrigerant flow path in which the refrigerant and the air travel in opposite directions with respect to the front-rear direction.

Embodiment 2. FIG.
Next, a heat exchanger according to Embodiment 2 of the present invention will be described with reference to FIGS. 3 and 4. FIG. 3 and FIG. 4 are diagrams of the same mode as FIG. 1 and FIG. The second embodiment is the same as the first embodiment except for the parts described below. In addition, the collective connecting pipe and the divided connecting pipe, which will be described later, are illustrated with priority given to explaining the connection mode of the divided areas. Unlike the actual situation, the pipe diameter and the pipe length are illustrated. In FIG. 3 and FIG. 4, the divided connecting pipes are shown so as not to overlap each other.

  The heat exchanger 101 of the second embodiment has an inlet header 119 that is divided into a plurality of rooms (particularly three as an example) by partition walls as a lower header of the windward row, and further distributes. A container 131.

  The distributor 131 is arranged on the downstream side of the plate fin and tube type heat exchange unit 5 and the upstream side of the parallel flow type heat exchange unit 3 when the heat exchanger 101 functions as an evaporator. More specifically, the inlet header 119 has an inlet end 119a for each of a plurality of rooms, and the outlet end 27b of the heat transfer pipe 27 of the plate fin-and-tube heat exchanger 5 and the distributor 131 are: Each of the plurality (three) of inlet ends 119a of the inlet header 119 and the distributor 131 correspond to each of the plurality of (three) of divided connecting pipes 129b. They are connected by a split connecting pipe 129b. The divided connecting pipe 129b functions as a capillary tube. The row-crossing header 123 is also divided into a plurality (three) of at least the front row side corresponding to the entrance header 119.

  In the second embodiment as described above, when the heat exchanger 101 functions as an evaporator, the refrigerant flows out of the plate fin and tube type heat exchanging unit 5 and then is branched into three by the distributor 131, which is a parallel flow type. It flows into the three rooms of the inlet header 119 at the bottom of the windward side row of the heat exchange unit 3. Thereafter, the heat exchange pipe 11 is moved up, moved between the rows by the row-crossing header 123, flows down the heat exchange pipe 13, and then flows out from the outlet header 21 of the row on the leeward side.

  In the second embodiment, in addition to the above-described advantages of the first embodiment, the following advantages can be obtained. Since the interior of the header attached to the lower part of the windward row of the parallel flow type heat exchange section 3 is divided into three, the size of each room in the header is reduced, and refrigerant distribution adjustment in the header is easy can do. Further, by adjusting the length of each of a plurality of capillary tubes (divided connecting pipes) connecting between the distributor and the header, the refrigerant distribution can be made uniform. In addition, the distributor and capillary tube have a large pressure loss inside the tube, so when functioning as an evaporator, the evaporation temperature of the plate fin and tube heat exchanger can be raised, and frost growth under the heat exchanger is suppressed. can do.

Embodiment 3 FIG.
Next, a refrigeration cycle air conditioner according to Embodiment 3 of the present invention will be described with reference to FIGS. 5 and 6. FIG. 5 is a diagram showing an outline of the refrigeration cycle air conditioner according to the third embodiment, and FIG. 6 is a plan view schematically showing an outdoor unit of the refrigeration cycle air conditioner according to the third embodiment. .

  As shown in FIG. 5, the refrigeration cycle air conditioner 251 includes a refrigeration cycle circuit including at least a compressor 253, an outdoor heat exchanger 255, a throttle device (expansion valve) 257, and an indoor heat exchanger 259. In addition, the arrow of FIG. 5 has shown the flow direction of the refrigerant | coolant in the case of performing a cooling operation. In addition, the refrigeration cycle air conditioner 251 is provided with a fan 261 that blows air to each of the outdoor heat exchanger 255 and the indoor heat exchanger 259, and a drive motor 263 that rotates the fan 261.

  The outdoor unit 351 in the refrigeration cycle air conditioner 251 is divided into a machine room 367 and a blower room 369 by a partition plate 365 inside the housing. A compressor 253 is accommodated in the machine room 367, and an outdoor heat exchanger 255 and a fan 261 are accommodated in the blower room 369.

In Embodiment 3, the heat exchanger 1 of Embodiment 1 or the heat exchanger 101 of Embodiment 2 described above is used for one or both of the outdoor heat exchanger 255 and the indoor heat exchanger 259. It has been. Thereby, an energy efficient refrigeration cycle air conditioner can be realized. In addition, energy efficiency is comprised by following Formula.
Heating energy efficiency = indoor heat exchanger (condenser) capacity / total input Cooling energy efficiency = indoor heat exchanger (evaporator) capacity / total input

  In the case of a parallel flow type heat exchange unit using corrugated fins, there are few pipes at both ends in the left-right direction, and a heat exchanger (parallel flow type heat Therefore, it is possible to secure a sufficient mounting area without bending the heat exchanger, and there is an advantage that the heat exchange efficiency can be increased. In addition, even when the heat exchangers 1 and 101 are applied to an indoor unit, a heat exchanger (parallel flow type heat exchange unit) can be disposed on almost the entire housing surface on the windward side of the fan in the indoor unit. Similar advantages are obtained.

  Although the contents of the present invention have been specifically described with reference to the preferred embodiments, various modifications can be made by those skilled in the art based on the basic technical idea and teachings of the present invention. It is self-explanatory.

  First, with respect to the heat exchangers 1 and 101 described in the first and second embodiments and the refrigeration cycle air conditioner 251 using the heat exchangers 1 and 101, the effect can be achieved in refrigerants such as R410A, R32, and 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 heat exchangers 1 and 101 described in the first and second embodiments described above can achieve the same effect even when used in an indoor unit.

  Further, regarding the heat exchangers 1, 101 described in the first and second embodiments and the refrigeration cycle air conditioner 251 using the heat exchanger 1, 101, mineral oil, alkylbenzene oil, ester oil, ether oil, fluorine oil The effect can be achieved for any refrigerating machine oil regardless of whether the oil dissolves in the refrigerant.

  Further, as another application example of the present invention, use in a heat pump apparatus that is easy to manufacture, needs to improve heat exchange performance, and improve energy saving performance can be mentioned.

  1,101 heat exchanger, 3 parallel flow type heat exchange part, 5 plate fin and tube type heat exchange part, 7 front row part, 9 back row part, 11, 13 heat exchange pipe, 17 fin, 19, 119 inlet header (lower part Header), 21 outlet header (lower header), 23 row header (upper header), 25 plate fins, 27 heat transfer pipe, 129a collective connection pipe, 129b split connection pipe, 131 distributor, 251 refrigeration cycle air conditioner, 253 Compressor, 255 outdoor heat exchanger, 257 throttle device, 259 indoor heat exchanger, 261 fan.

Claims (11)

A heat exchanger comprising a parallel flow type heat exchange section having a plurality of heat exchange pipes extending in the vertical direction,
The parallel flow type heat exchange unit includes at least a front row portion and a rear row portion,
Each of the front row portion and the rear row portion has a plurality of heat exchange pipes extending in the vertical direction,
In front of the lower part of the front surface of the parallel flow type heat exchange unit, a plate fin and tube type heat exchange unit each having a plurality of plate fins extending in the vertical direction is arranged,
The outlet end of the plate fin and tube type heat exchange unit and the inlet end of the parallel flow type heat exchange unit are connected by a pipe,
Heat exchanger. The lowest part of the plate fin and tube type heat exchange part is located between the lowest part of the fins of the parallel flow type heat exchange part and the lower header of the front row part,
The heat exchanger according to claim 1. A circular pipe is used for the heat transfer pipe of the plate fin and tube heat exchange section,
The heat exchanger according to claim 1 or 2. The number of passes of the plate fin and tube type heat exchange unit is less than the number of passes of the parallel flow type heat exchange unit,
The heat exchanger according to any one of claims 1 to 3. The inlet end of the heat transfer pipe, which serves as a refrigerant inlet when functioning as an evaporator, is disposed below the plate fins,
The heat exchanger according to any one of claims 1 to 4. When the heat exchanger functions as an evaporator, the refrigerant and air travel in the same direction in the front-rear direction, and when functioning as a condenser, the refrigerant flow path in which the refrigerant and air travel in the reverse direction in the front-rear direction Having
The heat exchanger according to any one of claims 1 to 5. The fins of the parallel flow type heat exchange part protrude in the windward direction from the heat exchange pipe of the front row part,
The heat exchanger according to any one of claims 1 to 6. The lower headers of the front row portion and the rear row portion are provided separately for each row, and the upper headers of the front row portion and the rear row portion are provided integrally across the rows,
The heat exchanger according to any one of claims 1 to 7. The interior of the lower header of the front row portion is divided into a plurality of rooms by partition walls, and the lower header has an entrance end for each of the plurality of rooms,
A distributor is provided between the plate fin and tube type heat exchanging part and the lower header of the front row part,
The outlet end of the plate fin and tube type heat exchanging section and the distributor are connected by a collective pipe, and each of the plurality of inlet ends of the lower header and the distributor are divided into a plurality of parts. Are connected by the corresponding divided connecting pipes of the connecting pipes,
The heat exchanger according to claim 8. A refrigeration cycle air conditioner having a refrigeration cycle circuit including a compressor, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger,
The heat exchanger according to any one of claims 1 to 9 is used for one or both of the outdoor heat exchanger and the indoor heat exchanger.
Refrigeration cycle air conditioner. The fins of the parallel flow heat exchange unit are corrugated fins,
The parallel flow type heat exchange section is disposed on the entire casing surface on the windward side of the fan in the corresponding outdoor heat exchanger and the indoor heat exchanger.
The refrigeration cycle air conditioner according to claim 10.

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