CN203798027U - Heat exchanger and refrigeration cycle air conditioning device with same - Google Patents

Abstract

The utility model provides a heat exchanger and a refrigeration cycle air conditioning device with the same. The heat exchanger (1) is provided with a parallel flow type heat exchanging part (3). The parallel flow type heat exchanging part (3) is provided with a plurality of heat exchanging tubes (11 and 13) which extend vertically. The parallel flow type heat exchanging part at least comprises a front row part (7) and a rear row part (9). Each of the front row part and the rear row part is provided with the heat exchanging tubes which extend vertically. The plate-fin tube type heat exchanging part (5) of a plurality of plate fins (25) which respectively extend vertically is disposed in front of the lower portion of the front surface of the parallel flow type heat exchanging part. The outlet end of the plate-fin tube type heat exchanging part is connected with the inlet end of the parallel flow type heat exchanging part through a tubing. The lower headers of the front row part and the rear row part are disposed in a segmented manner according to rows. The upper headers of the front row part and the rear row part are integrated in a row span manner.

Description

Heat exchanger and refrigerating cycle air conditioner using the heat exchanger

technical field

The utility model relates to a heat exchanger and a refrigeration cycle air conditioner using the heat exchanger.

Background technique

In heat exchangers, the reduction of heat transfer capacity due to frost formation is often a problem. As an utility model related to such a problem, there is a heat exchanger disclosed in Patent Document 1, for example. In this heat exchanger, the heat exchange parts are separated from the front and rear and arranged to overlap in the front and rear direction, and a gap is ensured between the pair of heat exchange parts and between the pair of header parts respectively positioned above and below the heat exchange part. .

According to such a heat exchanger, even if one of the front and rear heat exchange parts loses air permeability due to frosting, the other heat exchange part can obtain a minimum heat exchange function through the flow of air passing through the gap.

prior art literature

patent documents

Patent Document 1: Japanese Patent Application Laid-Open No. 8-226727 (first drawing)

Utility model content

Problems to be solved by utility models

However, in the above-mentioned conventional heat exchanger, there are problems as follows: In the case of being used as an evaporator, it is not considered to suppress the growth of frost itself, and it is relatively difficult to defrost the frost locally generated at the lower part of the heat exchanger. difficulty.

This invention was made in view of the above, and it aims at providing the heat exchanger which can suppress the growth of the frost accumulated in the lower part of a heat exchanger.

Technical solutions for solving problems

The present invention for achieving the above object is to provide a heat exchanger including a parallel flow heat exchange section having a plurality of heat exchange tubes extending in the vertical direction, wherein the The parallel flow heat exchange part at least includes a front row part and a rear row part, and the front row part and the rear row part respectively have a plurality of heat exchange tubes extending along the up-down direction. In the parallel flow heat exchange part In front of the lower part of the front surface, a plate-fin tube-type heat exchange part with a plurality of sleeves extending in the vertical direction is arranged, and the outlet end of the plate-fin-tube heat exchange part is connected to the parallel flow heat exchange part. The inlet ends are connected by pipes, the lower headers of the front row and the rear row are divided into rows, and the upper headers of the front row and the rear row are integrally arranged across rows.

The heat exchanger of the present invention can also be configured such that the lowermost part of the plate-fin-tube heat exchange part is located between the lowermost part of the fins of the parallel flow heat exchange part and the lower header of the front part .

The heat exchanger of the present invention can also be configured such that the heat transfer tube of the plate-fin tube type heat exchange part uses a circular tube.

The heat exchanger of the present invention can also be configured such that the number of passages in the plate-fin-tube heat exchange part is less than the number of passages in the parallel flow heat exchange part.

In the heat exchanger according to the present invention, the inlet end of the heat transfer tube serving as a refrigerant inlet when functioning as an evaporator may be arranged at a lower portion of the heat sink.

The heat exchanger of the present invention may be configured such that the heat exchanger has a refrigerant flow path that allows the refrigerant and the air to travel in the same direction in the front-rear direction when the refrigerant flow path functions as an evaporator. And when functioning as a condenser, the refrigerant and the air are caused to travel in opposite directions in the front-rear direction.

In the heat exchanger of the present invention, the fins of the parallel flow heat exchange section may protrude in a windward direction compared with the heat exchange pipes of the front row.

The heat exchanger of the present invention may also be configured such that the inside of the lower header of the front row portion is divided into a plurality of spaces by a partition wall, and the lower header has an inlet port in each of the plurality of spaces. , a distributor is provided between the plate-fin-tube heat exchange part and the lower header of the front part, and the outlet end of the plate-fin-tube heat exchange part is connected to the distributor through a collective connecting pipe Each of the plurality of inlet ends of the lower header is connected to the distributor through a corresponding split connection pipe among the plurality of split connection pipes.

Another utility model for achieving the same purpose is to provide a refrigerating cycle air conditioner, which is equipped with a refrigerating cycle circuit, and the refrigerating cycle circuit includes a compressor, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger, wherein the The heat exchanger of the present invention is used in one or both of the outdoor heat exchanger and the indoor heat exchanger.

In addition, the refrigerating cycle air conditioner of the present utility model can also be configured such that the fins of the parallel flow heat exchange part are corrugated fins, and the parallel flow heat exchange part is arranged on the corresponding outdoor heat exchanger and The frame body on the windward side of the fan in the indoor heat exchanger has an integral surface.

Utility Model Effect

According to the present invention, it is possible to suppress the growth of frost deposited on the lower portion of the heat exchanger.

Description of drawings

FIG. 1 is a front view of a heat exchanger according to Embodiment 1 of the present invention.

FIG. 2 is a side view of the heat exchanger according to Embodiment 1. FIG.

Fig. 3 is a diagram of the same situation as Fig. 1 regarding Embodiment 2 of the present invention.

FIG. 4 is a diagram related to the second embodiment in the same situation as FIG. 2 .

Fig. 5 is a diagram showing an outline of a refrigeration cycle air conditioner according to Embodiment 3 of the present invention.

FIG. 6 is a plan view schematically showing an outdoor unit of the refrigeration cycle air-conditioning apparatus according to Embodiment 3. FIG.

Detailed ways

Hereinafter, embodiment of this invention is described based on drawing. It should be noted that, in the drawings, the same reference numerals represent the same or corresponding parts. In addition, the direction in the description is as follows: the upstream side of the planned ventilation is defined as "front", the downstream side is defined as "rear", the direction of the action of gravity is defined as "downward", and the opposite direction is defined as "upper". The direction perpendicular to both the front-rear direction and the up-down direction (direction of gravity) is referred to as "left and right". Taking Figure 2 as an example, the top and bottom of the paper in Figure 2 are the up and down directions in the description, the left and right sides of the paper in Figure 2 are the front and rear respectively, and the front and back directions of the paper in Figure 2 are left and right direction. In addition, the reference sign WD in FIG. 2 has shown the airflow direction of ventilation.

Implementation mode 1.

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 in an outdoor unit of a refrigeration cycle air conditioner.

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

First, the parallel-flow 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 aligned in the front-rear direction. Each of the front row part 7 and the rear row part 9 has a plurality of heat exchange tubes 11 and 13 extending in the vertical direction. The heat exchange pipes 11 and 13 are flat tubes that are flattened from the left and right directions. The plurality of heat exchange tubes 11 of the front row portion 7 are aligned in the left-right direction, and the plurality of heat exchange tubes 13 of the rear row portion 9 are also aligned in the left-right direction. Between the plurality of heat exchange tubes 11 of the front row portion 7 and the plurality of heat exchange tubes 13 of the rear row portion 9, gaps 15 are provided in the front-rear direction, and the heat exchange tubes 11 and 13 are separated in the front-rear direction. In addition, as an example, the number of heat exchange pipes 11 is the same as the number of heat exchange pipes 13 .

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 being bent in the left and right directions between a pair of adjacent fins. In other words, the fin 17 is formed in a wave shape so as to alternately contact the heat exchange pipe on its left side and the heat exchange pipe on its right side.

In addition, the heat exchange pipes 11 and 13 are arranged in two front and rear rows, and the fins 17 are arranged in one row in the front and rear direction. In other words, uninterrupted wave-shaped fins are located between a corresponding pair of heat exchange tubes 11 in the front row portion 7 and between a corresponding pair of heat exchange tubes 13 in the rear row portion 9 . The fins 17 protrude in the windward direction from the heat exchange pipes 11 of the front row portion 7 , that is, the front edges of the fins 17 are positioned forward of the front ends of the heat exchange pipes 11 of the front row portion 7 .

In the lower part of the front row part 7, a lower header on the front row part 7 side, that is, an inlet header 19 is provided, and on a lower part of the rear row part 9, a lower header on the rear row part 9 side, that is, an outlet header 21 is provided. On the upper parts of the front row part 7 and the rear row part 9, straddling headers 23 are provided. In the front row part 7 and the rear row part 9, the same straddle header 23 is shared as each upper header. In addition, each of the inlet header 19, the outlet header 21, and the straddle header 23 is constituted by one chamber. In this way, the lower headers of the front row part 7 and the rear row part 9 are divided into rows, and the upper headers of the front row part 7 and the rear row part 9 are integrally arranged across the rows.

In addition, from the functional point of view, the inlet header 19 and the outlet header 21 arranged at the lower part of the parallel flow heat exchange part 3 are provided with a mechanism for uniformly distributing the wind direction heat exchange tubes in the row on the windward side, and a mechanism for uniformly distributing the wind direction to the heat exchange tubes in the row on the leeward side. The mechanism for collecting gas in the rows, when viewed as a whole of the parallel flow heat exchange part 3, the lower headers are divided into rows. On the other hand, the straddle-row header 23 arranged on the upper part of the parallel-flow heat exchange part 3 has a mechanism capable of moving the refrigerant between rows. The columns are set as one.

The lower end of the heat exchange conduit 11 of the front row part 7 is connected to the inlet header 19 , and the upper end of the heat exchange conduit 11 of the front row part 7 is connected to the cross-row header 23 . In addition, the lower end of the heat exchange tubes 13 of the rear row part 9 is connected to the outlet header 21 , and the upper end of the heat exchange tubes 13 of the rear row part 9 is connected to the straddling header 23 .

The plate-fin-tube heat exchange part 5 is arranged in front of the lower part of the front surface of the parallel flow heat exchange part 3, more specifically, in front of the lower part of the front surface of the front row part 7, that is, in front of the inlet header 19. above. The lowermost part of the plate-fin-tube heat exchange part 5 (the lowermost part of the sleeve fin 25 ) is arranged between the lowermost part of the fins 17 of the parallel flow heat exchange part 3 and the inlet header 19 .

The plate-fin-tube heat exchange part 5 has a plurality of sleeve fins 25 and a heat pipe 27 for forming at least one passage.

The plurality of sleeve pieces 25 respectively extend in the vertical direction and are arranged substantially parallel in the left-right direction. In addition, the rear portions of the plurality of sleeve fins 25 are in contact with or come close to 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 circular pipe forming one passage, and extends vertically through the plurality of sleeves 25 while being bent in the left-right direction. The inlet port 27a of the heat transfer pipe 27, which is the refrigerant inlet when functioning as an evaporator, is arranged at the lower part of the sleeve 25, and the outlet of the heat transfer pipe 27, which is the refrigerant outlet when functioning as an evaporator. The end 27b is disposed on the upper portion of the sleeve 25 . It should be noted that, as the heat transfer pipe 27 , as long as the number of passages is smaller than that of the parallel flow heat exchange unit 3 , a plurality of round pipes may be used to form a plurality of passages. In addition, as the heat transfer tube 27 , one or more flat tubes (plate-fin flat tube type) may be used instead of the above-mentioned one or more round tubes (plate-fin circular tube type).

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

Next, the flow of the refrigerant will be described. It should be noted that the arrows shown in FIGS. 1 and 2 schematically indicate the flow of refrigerant when 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 it is installed in an outdoor unit and performs heating operation), the refrigerant flows from bottom to top in the plate-fin-tube heat exchange part 5 through a passage, and flows from the plate to the top. The flow out of the fin-tube heat exchange unit 5 flows into the inlet header 19 of the parallel flow heat exchange unit 3 after passing through the connecting pipe 29 . The refrigerant in the inlet header 19 flows from bottom to top through the plurality of heat exchange tubes 11 of the front section 7 on the windward side. That is, after being separated into the same number as the number of heat exchange tubes 11 , that is, the number of passages, and ascending in the front row portion 7 , it flows into the straddling header 23 . In addition, after the refrigerant flows into the straddle header 23 , it flows from top to bottom through the plurality of heat exchange tubes 13 in the rear row portion 9 which is the leeward side. That is, the same number as the number of heat exchange tubes 13 , that is, the number of passages, flows down the rear portion 9 , flows into the outlet header 21 , and finally flows out of the heat exchanger 1 .

In Embodiment 1 configured as described above, the following advantages are obtained. In the heat exchanger 1 , since the plate-fin-tube heat exchange unit 5 is provided, condensed water is guided from the inlet header 19 and the fins 17 to the cooling fins 25 during operation in which frost formation is likely to occur. That is, condensed water mainly concentrates on the plate-fin-tube heat exchange portion 5 having excellent drainage, so that ice can be prevented from accumulating on the lower portion of the heat exchanger 1 .

In addition, the number of passages of the plate-fin-tube heat exchange part 5 is less than that of the parallel-flow heat exchange part 3, and the pressure loss in the pipe through which the refrigerant passes is greater than that of the parallel-flow heat exchange part 5. Heat exchange part 3. Therefore, the evaporation temperature of the plate-fin-tube heat exchange section 5 is higher than the evaporation temperature of the parallel flow heat exchange section 3 , and the amount of frosting during operation is reduced, preventing frost from concentrating on the lower part of the heat exchanger 1 . In addition, when the heat exchanger 1 is used as a condenser, the flow velocity of the subcooler can be increased, the heat transfer rate in the tube can be improved, and the efficiency of the heat exchanger can be improved.

In addition, when the heat exchanger 1 is used as an evaporator, the inlet of the plate-fin-tube heat exchange part 5 is provided at the lowermost part of the plate-fin-tube heat exchange part 5, so that the lowermost part of the heat exchanger 1 can be The increase in temperature can also suppress the amount of frost formation.

In addition, since the fins 17 used in the parallel flow heat exchange part 3 are integrally formed with the heat exchange pipes 11 and 13 in the front and rear rows, the heat exchange pipes 11 and 13 are arranged so that the rows are parallel. Assemblability can be improved when there are two rows in front and back.

In addition, the fins 17 are provided with notches for heat insulation at the positions between the front and rear rows, thereby suppressing heat transfer caused by the temperature difference between the heat exchange pipes 11 and 13, and improving the performance of the heat exchanger. efficiency.

In addition, since the fins 17 are fixed so as to protrude in the windward direction with respect to the heat exchange pipe 11, the temperature of the front edge of the fin 17 is close to the air temperature, and it is possible to prevent frost from concentrating on the front edge of the fin 17 during the frosting operation. .

In addition, as Embodiment 1, an example of a heat exchange method using the heat exchanger 1 can be given. In this heat exchange method, when the heat exchanger 1 functions as an evaporator, the refrigerant and the air are approximately equal to each other. Parallel flow (flowing in the same direction) (refrigerant and air flow from front to back under macroscopic observation), under the action of pressure loss, the evaporation temperature of refrigerant decreases in the direction of flow, and the temperature of air also decreases in the direction of flow, so The temperature difference between the refrigerant and the air becomes smaller. On the other hand, when functioning as a condenser, the refrigerant and the air generally flow in opposite directions (flow in opposite directions) (the air flows from the front to the rear, and the refrigerant flows from the rear to the front under macroscopic observation), and the refrigerant In the superheated, two-phase, and supercooled regions, the temperature decreases in the direction of flow, and the temperature of air rises in the direction of flow, so the temperature difference between the refrigerant and air decreases. This also increases the efficiency of the heat exchanger. In other words, the heat exchanger 1 functions as an evaporator as a refrigerant flow path involving the parallel-flow heat exchange part 3 and the plate-fin-tube heat exchange part 5, and has a function of separating the refrigerant and the air in the front-rear direction. The refrigerant flow path runs in the same direction, and in the case of functioning as a condenser, the refrigerant and the air run in opposite directions in the front-rear direction.

Implementation mode 2.

Next, the heat exchanger according to Embodiment 2 of the present invention will be described based on FIGS. 3 and 4 . FIG. 3 and FIG. 4 are diagrams of the second embodiment in the same situation as FIG. 1 and FIG. 2 , respectively. It should be noted that this second embodiment is the same as the above-mentioned first embodiment except for the parts described below. In addition, the combined connection piping and the divisional connection piping described later will give priority to the connection of the divided areas and show them in the figure, and the illustration of the pipe diameter and the accuracy of the length of the pipe are omitted from the actual state, and are shown in Fig. 3 And any one of FIG. 4 is shown so that the divided connection pipes may not overlap each other.

The heat exchanger 101 according to Embodiment 2 has an inlet header 119 that is the lower header of the row on the windward side, and divides the interior into a plurality of (three as a specific example) spaces by a partition wall, and has a distribution device 131.

The distributor 131 is arranged on the downstream side of the plate-fin-tube heat exchange part 5 and on the upstream side of the parallel flow heat exchange part 3 when the heat exchanger 101 functions as an evaporator. In more detail, the inlet header 119 has an inlet port 119a in each of the plurality of spaces, and the outlet port 27b of the heat transfer tube 27 of the plate-fin-tube heat exchange part 5 is connected to the distributor 131 through a collective connecting pipe 129a. Each of the plurality of (three) inlet ends 119a of the inlet header 119 is connected to the distributor 131 through the corresponding divided connecting pipes 129b among the plurality of (three) divided connecting pipes 129b. The split connecting pipe 129b functions as a capillary. It should be noted that at least the front row side of the straddling header 123 is also divided into a plurality (three) corresponding to the inlet header 119 .

In Embodiment 2 as described above, when the heat exchanger 101 functions as an evaporator, the refrigerant flows out of the plate-fin-tube heat exchange unit 5, is branched into three paths by the distributor 131, and flows into the Three spaces of the inlet header 119 in the lower part of the column on the windward side of the parallel flow heat exchange unit 3 . Thereafter, it ascends in the heat exchange pipes 11 , moves between rows by the cross-row headers 123 , flows down in the heat exchange pipes 13 , and then flows out from the outlet headers 21 of the row on the leeward side.

In the second embodiment described above, in addition to the advantages described above in the first embodiment, the advantages described below are obtained. The interior of the header attached to the lower part of the row on the windward side of the parallel flow heat exchange unit 3 is divided into three places, so the size of each space in the header is reduced, and the refrigerant distribution adjustment in the header can be easily adjusted. . In addition, by adjusting the lengths of the multiple capillary tubes (divided connecting pipes) that connect the distributor and the header, it is also possible to make the refrigerant distribution uniform. When functioning as an evaporator, the evaporation temperature of the plate-fin-tube heat exchange part can be raised, and the growth of frost in the lower part of the heat exchanger can be suppressed.

Implementation mode 3.

Next, based on FIG.5 and FIG.6, the refrigeration cycle system air-conditioning apparatus which concerns on Embodiment 3 of this invention is demonstrated. 5 is a diagram showing an outline of a refrigeration cycle air conditioner according to Embodiment 3, and FIG. 6 is a plan view schematically showing an outdoor unit of the refrigeration cycle air conditioner according to Embodiment 3. FIG.

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 , an expansion device (expansion valve) 257 , and an indoor heat exchanger 259 . It should be noted that the arrows in FIG. 5 indicate the flow direction of the refrigerant during the cooling operation. Further, the refrigeration cycle air conditioner 251 is provided with a fan 261 for blowing air to each of the outdoor heat exchanger 255 and the indoor heat exchanger 259 , and a drive motor 263 for rotating the fan 261 .

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

In Embodiment 3, the heat exchanger 1 of the above-described Embodiment 1 or the heat exchanger 101 of Embodiment 2 is used for one or both of the outdoor heat exchanger 255 and the indoor heat exchanger 259 . Thereby, a refrigeration cycle air conditioner with high energy efficiency can be realized. It should be noted that the energy efficiency is constituted by the following formula.

Heating energy efficiency = indoor heat exchanger (condenser) capacity / full input

Cooling energy efficiency = indoor heat exchanger (evaporator) capacity / full input

In addition, in the case of a parallel-flow heat exchange unit using corrugated fins, there are fewer pipes at both ends in the left-right direction, and the heat exchanger can be arranged in almost the entire frame of the fan on the windward side of the outdoor unit ( Parallel flow type heat exchange part), therefore, a sufficient installation area can be secured without bending the heat exchanger, thereby also having the advantage of being able to increase heat exchange efficiency. It should be noted that, when the heat exchanger 1, 101 is applied to an indoor unit, the heat exchanger (parallel flow type heat exchange part ), gaining the same advantages.

Above, the contents of the present invention have been specifically described with reference to preferred embodiments, but it is self-evident that those skilled in the art can adopt various modifications based on the basic technical idea and enlightenment of the present invention.

First, the heat exchangers 1 and 101 described in Embodiments 1 and 2 and the refrigeration cycle air conditioner 251 using the heat exchangers can achieve their effects with refrigerants such as R410A, R32, and HFO1234yf.

In addition, examples of air and refrigerant are shown as working fluids, but the same effects can be achieved by using other gases, liquids, and gas-liquid mixed fluids.

In addition, when the heat exchangers 1 and 101 described in Embodiments 1 and 2 described above are used in an indoor unit, the same effect can be achieved.

In addition, mineral oil, alkylbenzene oil, ester oil, ether oil, Any refrigerating machine oil can achieve the above effects regardless of whether the oil is soluble in the refrigerant or not, such as fluorine-based oils.

In addition, as another application example of the present invention, an example of application to a heat pump device that requires easy manufacture, improved heat exchange performance, and improved energy saving performance can be given.

Explanation of reference signs:

1, 101 heat exchanger, 3 parallel flow heat exchange parts, 5 plate-fin tube heat exchange parts, 7 front part, 9 rear part, 11, 13 heat exchange pipes, 17 fins, 19, 119 inlet header (lower header), 21 outlet header (lower header), 23 straddle header (upper header), 25 sleeves, 27 heat transfer pipes, 129a collective connection piping, 129b split connection piping, 131 distributor, 251 Refrigeration cycle air conditioner, 253 compressors, 255 outdoor heat exchangers, 257 throttling devices, 259 indoor heat exchangers, 261 fans.

Claims (10)

1. A heat exchanger comprising a parallel flow heat exchange section having a plurality of heat exchange tubes extending vertically, wherein: The parallel flow heat exchange part at least includes a front row part and a rear row part, The front row part and the rear row part respectively have a plurality of heat exchange tubes extending along the up-down direction, In front of the lower part of the front surface in the parallel-flow heat exchange part, a plate-fin-tube heat exchange part having a plurality of sleeves each extending in the up-down direction is arranged, The outlet end of the plate-fin-tube heat exchange part is connected to the inlet end of the parallel flow heat exchange part through piping, The lower headers of the front row part and the rear row part are divided into rows, and the upper headers of the front row part and the rear row part are integrated in a manner of straddling rows. 2. The heat exchanger according to claim 1, characterized in that, The lowermost part of the plate-fin-tube heat exchange part is located between the lowermost part of the fins of the parallel flow heat exchange part and the lower header of the front row part. 3. The heat exchanger according to claim 1, characterized in that, Round tubes are used as the heat conduction tubes of the plate-fin-tube heat exchange unit. 4. The heat exchanger according to claim 1, characterized in that, The number of passages of the plate-fin-tube heat exchange part is less than the number of passages of the parallel flow heat exchange part. 5. The heat exchanger according to claim 1, characterized in that, When functioning as an evaporator, an inlet end of the heat transfer pipe serving as a refrigerant inlet is arranged at a lower portion of the sleeve. 6. The heat exchanger according to claim 1, characterized in that, The heat exchanger has a refrigerant flow path that makes the refrigerant and air travel in the same direction in the front-rear direction when functioning as an evaporator and that cools the air when functioning as a condenser. The agent and the air travel in opposite directions in the front-back direction. 7. The heat exchanger according to claim 1, characterized in that, The fins of the parallel flow heat exchange portion protrude in an upwind direction than the heat exchange tubes in the front row. 8. The heat exchanger according to claim 7, characterized in that, The interior of the lower header of the front row portion is divided into a plurality of spaces by a partition wall, the lower header has an inlet port in each of the plurality of spaces, A distributor is provided between the plate-fin-tube heat exchange part and the lower header of the front row part, The outlet end of the plate-fin-tube heat exchange unit is connected to the distributor through a collective connection pipe, and each of the plurality of inlet ends of the lower header is connected to the distributor through a plurality of divided connection pipes. The respective corresponding divided connection pipes are connected. 9. A refrigerating cycle air conditioner, which is equipped with a refrigerating cycle, and the refrigerating cycle includes a compressor, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger, characterized in that, The heat exchanger according to any one of claims 1 to 8 is used in one or both of the outdoor heat exchanger and the indoor heat exchanger. 10. The refrigerating cycle air conditioner according to claim 9, wherein: The fins of the parallel flow heat exchange part are corrugated fins, The parallel-flow heat exchange unit is disposed on the entire frame body surface on the windward side of the fan in the corresponding outdoor heat exchanger and the indoor heat exchanger.