JP2013015289A - Heat exchanger, and air conditioner equipped with same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the heat exchange efficiency in a side-flow-type parallel-flow heat exchanger.SOLUTION: The parallel-flow heat exchanger 1A includes vertical header pipes 2 and 3, and a plurality of horizontal flat tubes 4 that connect the header pipes 2 and 3 to each other. A refrigerant flows in a compartment S6 in the header pipe 3 through an inlet pipe 8, and flows in the header pipe 2 through the plurality of flat tubes 4 connected to the compartment S6. The plurality of flat tubes 4 connected to the compartment S6 are divided vertically by a partition plate P2 in the header pipe 2, and the refrigerant ultimately flows out from an upper outlet pipe 9 and a lower outlet pipe 10. The position of the partition plate P2 is set so that the refrigerant more easily enters a side of a refrigerant flow path reaching the upper outlet pipe 9 from the inlet pipe 8 than a refrigerant flow path reaching the outlet pipe 10 from the inlet pipe 8.

Description

  The present invention relates to a side flow parallel flow heat exchanger and an air conditioner equipped with the heat exchanger.

  A parallel flow type heat exchange in which a plurality of flat tubes are arranged between two header pipes so that a refrigerant passage inside the flat tubes communicates with the header pipe, and fins such as corrugated fins are arranged between the flat tubes. The equipment is widely used in car air conditioners and building air conditioners.

  In a parallel flow type heat exchanger, it is an important design matter to improve heat exchange efficiency so that the refrigerant flows evenly through a plurality of flat tubes. An example of a parallel flow type heat exchanger pursuing an even flow of refrigerant can be seen in Patent Documents 1 and 2.

  A parallel flow heat exchanger described in Patent Document 1 includes a cylindrical hollow header, a refrigerant inlet pipe connected to the refrigerant inflow chamber of the header, and a plurality of tubes connected to the refrigerant inflow chamber. Prepare. The refrigerant inflow chamber is divided into a plurality of inflow partition chambers, the refrigerant inlet pipe is branched into a corresponding number of branch pipes, and the branch pipes are connected to the inflow partition chambers so that the refrigerant is evenly divided into the tubes. Let

  The parallel flow heat exchanger described in Patent Document 2 has a configuration in which a vertical tube is combined with a horizontal header. In the lower header, a refrigerant dispersion pipe that communicates with the refrigerant inlet pipe is disposed along the length direction thereof. A plurality of refrigerant dispersion holes are provided in the peripheral wall of the refrigerant dispersion tube so that the liquid refrigerant flowing into the lower header through the refrigerant inlet pipe is evenly distributed to the tubes.

  Although the heat exchanger described in Patent Document 3 is not a parallel flow type but a fin-and-tube type, even in this heat exchanger, an equal distribution of refrigerant is pursued. In this heat exchanger, a crushing portion is provided in an inlet pipe connected to a plurality of heat exchange paths, and a flow path resistance capable of diverting an appropriate amount of refrigerant is provided.

JP-A-6-74609 Japanese Patent Laid-Open No. 6-159983 JP 9-145198 A

  Side flow type parallel flow type heat exchanger having two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes, with two outlet pipes for one inlet pipe It may be. In this case, one of the two outlet pipes is disposed above the inlet pipe and becomes an upper outlet pipe. The other outlet pipe is disposed below the inlet pipe and serves as a lower outlet pipe. The refrigerant flow that flows into the heat exchanger from the inlet pipe is divided into two parts up and down, the upper refrigerant flow finally flows out from the upper outlet pipe, and the lower refrigerant flow finally flows out from the lower outlet pipe. An object of the present invention is to further improve the heat exchange efficiency even when used as an evaporator in a parallel flow heat exchanger having such a configuration.

  The parallel flow heat exchanger according to the present invention includes two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes, and a refrigerant passes through an inlet pipe and is inside one of the two header pipes. To the other of the header pipes through the plurality of flat tubes connected to the section, and is divided into upper and lower parts by a partition plate in the header pipe, and finally the upper outlet pipe The refrigerant flow path is configured to flow out from the lower outlet pipe, and the refrigerant flow path from the inlet pipe to the upper outlet pipe is more than the refrigerant flow path from the inlet pipe to the lower outlet pipe. The refrigerant is easy to enter.

  In the parallel flow heat exchanger having the above-described configuration, the plurality of flat tubes connected to the section through which the refrigerant flows from the inlet pipe has a comparatively large number on the upper side and a comparatively small number on the lower side. It is preferable that the partition plate is divided up and down.

  In the parallel flow heat exchanger having the above configuration, it is preferable that the inlet pipe is connected to an upper position of the section into which the refrigerant flows from the inlet pipe.

  In the parallel flow heat exchanger configured as described above, the flat tubes are more distributed in the refrigerant flow path from the inlet pipe to the upper outlet pipe than in the refrigerant flow path from the inlet pipe to the lower outlet pipe. It is preferable that

  In the parallel flow heat exchanger configured as described above, a plurality of the inlet pipes are connected to one of the header pipes, and the upper outlet pipe and the lower outlet pipe are provided for each of the plurality of inlet pipes. Preferably it is.

  In the parallel flow heat exchanger configured as described above, one of a plurality of branch pipes separated from one refrigerant pipe is connected to each of the plurality of inlet pipes, and the refrigerant pipe is connected to the plurality of branch pipes. It is preferable that the flattening is performed immediately upstream of the location where the pipe branches.

  In the parallel flow heat exchanger having the above-described configuration, it is preferable that the refrigerant pipe is flattened in a side-by-side direction of the plurality of branch pipes arranged side by side.

  According to the present invention, the parallel flow heat exchanger configured as described above is mounted on an indoor unit or an outdoor unit of an air conditioner.

  The gas-liquid mixed refrigerant flowing from the inlet pipe tends to go downward as a natural tendency. From the header pipe on the side where the inlet pipe is connected, into the other header pipe into which the refrigerant flows through a plurality of flat tubes, the refrigerant is divided into two parts up and down, and finally from both the upper outlet pipe and the lower outlet pipe A partition plate that allows the refrigerant to flow out is provided, but the refrigerant is more likely to enter the refrigerant flow path from the inlet pipe to the upper outlet pipe than the refrigerant flow path from the inlet pipe to the lower outlet pipe. Therefore, the refrigerant can be allowed to flow in a balanced manner in the upper and lower refrigerant channels, and the heat exchange efficiency is improved.

It is a front view of the heat exchanger which concerns on 1st Embodiment of this invention. FIG. 2 is a vertical cross-sectional view of a heat exchanger cut along a line II-II in FIG. 1. It is a front view of the heat exchanger which concerns on 2nd Embodiment of this invention. It is a front view of the heat exchanger which concerns on 3rd Embodiment of this invention. It is a front view of the heat exchanger which concerns on 4th Embodiment of this invention. It is a front view of the heat exchanger which concerns on 5th Embodiment of this invention. It is an expanded sectional view of a part of FIG. It is a schematic block diagram of the air conditioner carrying the heat exchanger which concerns on this invention, and shows the state at the time of heating operation. It is a schematic block diagram of the air conditioner carrying the heat exchanger which concerns on this invention, and shows the state at the time of air_conditionaing | cooling operation.

  The structure of the side flow parallel flow heat exchanger according to the first embodiment of the present invention will be described with reference to FIG. In FIG. 1, the upper side of the paper is the upper side of the heat exchanger, and the lower side of the paper is the lower side of the heat exchanger.

  The parallel flow type heat exchanger 1A is a side flow type, and includes two vertical header pipes 2 and 3 and a plurality of horizontal flat tubes 4 disposed therebetween. The header pipes 2 and 3 are arranged in parallel in the horizontal direction at intervals, and the flat tubes 4 are arranged at a predetermined pitch in the vertical direction. Since the parallel flow type heat exchanger 1 is installed at various angles according to design requirements at the stage of actually mounting on equipment, “vertical direction” and “horizontal direction” in this specification should not be strictly interpreted. Absent. It should be understood as a mere measure of direction.

  The flat tube 4 is an elongated molded product obtained by extruding a metal, and as shown in FIG. 2, a refrigerant passage 5 through which a refrigerant flows is formed. Since the flat tube 4 is disposed so that the extrusion direction, which is the longitudinal direction, is horizontal, the refrigerant flow direction of the refrigerant passage 5 is also horizontal. A plurality of refrigerant passages 4 having the same cross-sectional shape and cross-sectional area are arranged in the left-right direction in FIG. 2, and therefore the vertical cross section of the flat tube 4 has a harmonica shape. Each refrigerant passage 5 communicates with the inside of the header pipes 2 and 3.

  Corrugated fins 6 are arranged between the adjacent flat tubes 4. Of the corrugated fins 6 arranged in the vertical direction, side plates 7 are arranged outside the uppermost and lowermost ones.

  The header pipes 2 and 3, the flat tubes 4, the corrugated fins 6, and the side plates 7 are all made of a metal having good heat conductivity such as aluminum. The flat tubes 4 are the flat tubes 4 with respect to the header pipes 2 and 3. On the other hand, the side plate 7 is fixed to the corrugated fin 6 by brazing or welding, respectively.

  The interior of the header pipe 2 is partitioned into four sections S1, S2, S3, and S4 by three partition plates P1, P2, and P3. The section S1 is responsible for four of the total 24 flat tubes 4, the section S2 is responsible for eight, the section S3 is responsible for seven, and the section S4 is responsible for five.

  The interior of the header pipe 3 is partitioned into three sections S5, S6, and S7 by two partition plates P4 and P5. The section S5 is responsible for eight of the total 24 flat tubes 4, the section S6 is responsible for six, and the section S7 is responsible for ten.

  The total number of the flat tubes 4 described above, the number of partition plates inside each header pipe and the number of partitions partitioned thereby, and the number of flat tubes 4 that each partition is responsible for are only examples and limit the invention. is not. The same applies to the second and subsequent embodiments.

  An inlet pipe 8 is connected to the section S6. The upper outlet pipe 9 is connected to the section S1, and the lower outlet pipe 10 is connected to the section S4. The inlet pipe 8 is disposed at the center in the vertical direction of the section S6.

  The six flat tubes 4 whose one ends are connected to the partition S6 are divided into the upper four and the lower two by the partition plate P2. The upper four flat tubes 4 connect the section S6 and the section S2 to form the refrigerant flow path A1. The lower two flat tubes 4 connect the sections S6 and S3 to form the refrigerant flow path A2. Refrigerant flow paths A1 and A2 are symbolized by block arrows, respectively.

  The four flat tubes 4 connecting the section S2 and the section S5 form the refrigerant flow path B. The four flat tubes 4 connecting the section S5 and the section S1 form a refrigerant flow path C. The five flat tubes 4 connecting the section S3 and the section S7 form a refrigerant flow path D. The five flat tubes 4 connecting the section S7 and the section S4 form a refrigerant flow path E.

  The function of the parallel flow type heat exchanger 1A is as follows. When the refrigerant is supplied to the compartment S6 through the inlet pipe 8, the refrigerant goes to the compartments S2 and S3 through the refrigerant flow paths A1 and A2. The refrigerant that has entered the compartment S2 is turned back through the refrigerant flow path B toward the compartment S5. The refrigerant that has entered the compartment S5 turns back there, and passes through the refrigerant flow path C toward the compartment S1. The refrigerant that has entered the compartment S1 flows out from the upper outlet pipe 9. The refrigerant that has entered the section S3 is turned back through the refrigerant flow path D and heads for the section S7. The refrigerant that has entered the compartment S7 is turned back through the refrigerant flow path E to the compartment S4. The refrigerant that has entered the compartment S4 flows out from the lower outlet pipe 10.

  The six flat tubes 4 connected to the section S6 are divided up and down by a partition plate P2. The partition plate P2 is compared with four on the upper side and two on the lower side and on the upper side. The refrigerant flow from the inlet pipe 8 to the upper outlet pipe 9 rather than the refrigerant flow path from the inlet pipe 8 to the lower outlet pipe 10 is divided so that a large number is formed and the lower one forms a comparatively small number. It is easy for refrigerant to enter the road. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path originally, particularly when used as an evaporator, gas-liquid separation is performed inside the header pipe 3 where the inlet pipe 8 is located, and the liquid refrigerant is lower. In spite of being easy to flow into the other refrigerant flow path, the refrigerant can flow in a balanced manner in the upper and lower refrigerant flow paths, and the heat exchange efficiency is improved.

  If the partition plate is slidable so that the height can be changed, prevention of drift according to the refrigerant circulation amount and the dryness of the refrigerant becomes easier.

  FIG. 3 shows the structure of a side flow type parallel flow heat exchanger according to the second embodiment of the present invention. Components that are functionally common to the components of the first embodiment are denoted by the same reference numerals as those used in the first embodiment, and description thereof is omitted. The same applies to the third and following embodiments.

  In the parallel flow type heat exchanger 1B of the second embodiment, the partition plate P2 divides the six flat tubes 4 connected to the section S6 into the same number of top and bottom, three on the top and three on the bottom. Yes. The three flat tubes 4 connecting the sections S6 and S2 form the refrigerant flow path A1, and the three flat tubes 4 connecting the sections S6 and S3 form the refrigerant flow path A2.

  In the parallel flow type heat exchanger 1B of the second embodiment, the position of the inlet pipe 8 is different from that of the parallel flow type heat exchanger 1A of the first embodiment. That is, the inlet pipe 8 is not positioned at the center in the up-down direction of the section S6 but at a position above the section S6.

  Most of the refrigerant that has flowed into the section S6 from the inlet pipe 8 is directed toward the refrigerant flow path A1 due to its own movement inertia. For this reason, although the refrigerant flow path A1 and the refrigerant flow path A2 are formed by the same number of flat tubes 4, the refrigerant flow path A1 can easily enter. As a result, the refrigerant is more likely to enter the refrigerant flow path from the inlet pipe 8 to the upper outlet pipe 9 than the refrigerant flow path from the inlet pipe 8 to the lower outlet pipe 10. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path originally, particularly when used as an evaporator, gas-liquid separation is performed inside the header pipe 3 where the inlet pipe 8 is located, and the liquid refrigerant is lower. In spite of being easy to flow into the other refrigerant flow path, the refrigerant can flow in a balanced manner in the upper and lower refrigerant flow paths, and the heat exchange efficiency is improved.

  FIG. 4 shows the structure of a side flow type parallel flow heat exchanger according to the third embodiment of the present invention.

  In the parallel flow type heat exchanger 1C of the third embodiment, the partition plate P2 has four upper flat tubes 4 connected to the section S6 as in the parallel flow type heat exchanger 1A of the first embodiment. It is placed in a position that is divided into two. Similarly to the parallel flow heat exchanger 1B of the second embodiment, the inlet pipe 8 is disposed at a position above the section S6.

  The refrigerant flow path A1 has more flat tubes 4 than the refrigerant flow path A2, and the upper inlet pipe 8 is connected to the upper position of the section S6, so that the refrigerant flowing into the section S6 flows into the refrigerant flow. Easy to enter road A1. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path, the amount of the refrigerant can flow in a balanced manner in the upper and lower refrigerant flow paths, and the heat exchange efficiency is improved.

  In the parallel flow type heat exchanger 1 </ b> C, the refrigerant flow path B is constituted by four flat tubes 4, and the refrigerant flow path C is constituted by five flat tubes 4. The refrigerant flow path D is composed of five flat tubes 4, and the refrigerant flow path E is composed of four flat tubes 4. Therefore, the number of the flat tubes 4 included in the refrigerant passages (A1, B, C) from the inlet pipe 8 to the upper outlet pipe 9 and the refrigerant passages (A2, D, E from the inlet pipe 8 to the lower outlet pipe 10). ) Includes 13 flat tubes 4 and 11 flat tubes. Thereby, the heat radiation area of the refrigerant passage from the inlet pipe 8 to the upper outlet pipe 9 is increased, and the heat exchange amount is increased.

  FIG. 5 shows the structure of a side flow parallel flow heat exchanger according to a fourth embodiment of the present invention.

  The parallel flow type heat exchanger 1D of the fourth embodiment is different from the parallel flow type heat exchangers 1A, 1B, 1C from the first embodiment to the third embodiment in that the partition plates in the header pipes 2, 3 The number and the number of compartments provided thereby, and the position of the upper outlet pipe 9 and the lower outlet pipe 10. That is, it is as follows.

  The inside of the header pipe 2 is partitioned into two sections S1 and S2 by one partition plate P1. The section S1 is responsible for 13 of the total 24 flat tubes 4, and the section S2 is responsible for 11.

  The interior of the header pipe 3 is partitioned into three sections S3, S4, and S5 by two partition plates P2 and P3. The section S3 is responsible for nine of the 24 flat tubes 4, the section S4 is responsible for six, and the section S5 is responsible for nine.

  An inlet pipe 8 is connected to the section S4. The upper outlet pipe 9 is connected to the section S3, and the lower outlet pipe 10 is connected to the section S5. The inlet pipe 8 is not located at the center in the up-down direction of the section S4 but at a position above the section S4.

  The six flat tubes 4 whose one ends are connected to the partition S4 are divided into the upper four and the lower two by the partition plate P1. The upper four flat tubes 4 connect the section S4 and the section S1 to form the refrigerant flow path A1. The two lower flat tubes 4 connect the section S4 and the section S2 to form the refrigerant flow path A2.

  The nine flat tubes 4 that connect the section S1 and the section S3 form the refrigerant flow path B. Nine flat tubes 4 connecting the sections S2 and S5 form a refrigerant flow path C.

  The function of the parallel flow type heat exchanger 1D is as follows. When the refrigerant is supplied to the section S4 through the inlet pipe 8, the refrigerant goes to the sections S1 and S2 through the refrigerant flow paths A1 and A2. The refrigerant that has entered the section S1 is turned back through the refrigerant flow path B toward the section S3. The refrigerant that has entered the compartment S3 flows out from the upper outlet pipe 9. The refrigerant that has entered the section S2 is turned back through the refrigerant flow path C and then travels to the section S5. The refrigerant that has entered the compartment S5 flows out from the lower outlet pipe 10.

The refrigerant flow path A1 has more flat tubes 4 than the refrigerant flow path A2, and the upper inlet pipe 8 is connected to the upper position of the section S4, so that the refrigerant flowing into the section S4 flows into the refrigerant flow. Easy to enter road A1. For this reason, despite the fact that the refrigerant tends to flow toward the lower refrigerant flow path, the liquid refrigerant tends to flow downward particularly when used as an evaporator,
The refrigerant can flow in a balanced manner in the upper and lower refrigerant channels, and the heat exchange efficiency is improved.

  In the parallel flow type heat exchanger 1D, the refrigerant flow path B and the refrigerant flow path C are each composed of nine flat tubes 4. For this reason, the number of flat tubes 4 included in the refrigerant passage (A1, B) from the inlet pipe 8 to the upper outlet pipe 9 and the refrigerant passage (A2, C) from the inlet pipe 8 to the lower outlet pipe 10 are included. The number of the flat tubes 4 is 13 for the former and 11 for the latter. Thereby, the heat radiation area of the refrigerant passage from the inlet pipe 8 to the upper outlet pipe 9 is increased, and the heat exchange amount is increased.

  In the parallel flow heat exchangers 1A, 1B and 1C from the first embodiment to the third embodiment, the upper outlet pipe 9 and the lower outlet pipe are connected to a header pipe different from the header pipe to which the inlet pipe 8 is connected. In contrast, in the parallel flow heat exchanger 1D of the fourth embodiment, the upper outlet pipe 9 and the lower outlet pipe 10 are also connected to the same header pipe to which the inlet pipe 8 is connected. For this reason, design and enforcement of refrigerant piping are easy.

  FIG. 6 shows the structure of a side flow type parallel flow heat exchanger according to a fifth embodiment of the present invention. The parallel flow heat exchanger 1E according to the fifth embodiment is characterized by a configuration in which the parallel flow heat exchanger 1D according to the fourth embodiment is stacked in two upper and lower stages.

  The header pipes 2 and 3 of the parallel flow heat exchanger 1E are longer than the header pipes 2 and 3 from the first embodiment to the fourth embodiment. The total number of the flat tubes 4 is 34, which is larger than the first to fourth embodiments.

  The internal space of the header pipe 2 is divided vertically by the intermediate partition plate MP1, and the internal space of the header pipe 3 is divided vertically by the intermediate partition plate MP2. The intermediate partition plates MP1 and MP2 are at the same height, and the parallel flow heat exchanger 1E is divided vertically by the intermediate partition plates MP1 and MP2. In each of the upper and lower sections, an arrangement of inlet pipe, upper outlet pipe and lower outlet pipe is arranged.

  Within the header pipe 2, the section above the intermediate partition plate MP1 is partitioned into two partitions S1H and S2H by a single partition plate P1H. The section S1H is responsible for nine of the 34 flat tubes 4, and the section S2H is responsible for eight.

  Inside the header pipe 2, the section below the intermediate partition plate MP1 is partitioned into two partitions S1L and S2L by one partition plate P1L. The section S1L is responsible for nine of the 34 flat tubes 4, and the section S2L is responsible for eight.

  Inside the header pipe 3, the section above the intermediate partition plate MP2 is partitioned into three partitions S3H, S4H, and S5H by two partition plates P2H and P3H. The section S3H is responsible for five of the total 34 flat tubes 4, the section S4H is responsible for six, and the section S5H is responsible for six.

  Inside the header pipe 3, the section below the intermediate partition plate MP2 is partitioned into three partitions S3L, S4L, and S5L by two partition plates P2L and P3L. The section S3L is responsible for five of the total 34 flat tubes 4, the section S4L is responsible for six, and the section S5L is responsible for six.

  An inlet pipe 8H is connected to the section S4H. An upper outlet pipe 9H is connected to the section S3H, and a lower outlet pipe 10H is connected to the section S5H. The inlet pipe 8H is not positioned at the center in the vertical direction of the section S4H, but is disposed at a position above the section S4H.

  An inlet pipe 8L is connected to the section S4L. The upper outlet pipe 9L is connected to the section S3L, and the lower outlet pipe 10L is connected to the section S5L. The inlet pipe 8L is not positioned at the center in the up-down direction of the section S4L, but is disposed at a position above the section S4L.

  The six flat tubes 4 whose one ends are connected to the partition S4H are divided into the upper four and the lower two by the partition plate P1H. The upper four flat tubes 4 connect the section S4H and the section S1H to form a refrigerant flow path A1H. The two lower flat tubes 4 connect the section S4H and the section S2H to form a refrigerant flow path A2H.

  The five flat tubes 4 connecting the section S1H and the section S3H form a refrigerant flow path BH. The six flat tubes 4 connecting the section S2H and the section S5H form a refrigerant channel CH.

  The six flat tubes 4 whose one ends are connected to the partition S4L are divided into the upper four and the lower two by the partition plate P1L. The upper four flat tubes 4 connect the section S4L and the section S1L to form a refrigerant flow path A1L. The lower two flat tubes 4 connect the section S4L and the section S2L to form a refrigerant flow path A2L.

  The five flat tubes 4 connecting the section S1L and the section S3L form a refrigerant flow path BL. The six flat tubes 4 connecting the section S2L and the section S5L form a refrigerant flow path CL.

  The function of the parallel flow type heat exchanger 1E is as follows. When the refrigerant is supplied to the section S4H through the inlet pipe 8H, the refrigerant goes to the sections S1H and S2H through the refrigerant flow paths A1H and A2H. The refrigerant that has entered the section S1H is turned back there and travels to the section S3H through the refrigerant flow path BH. The refrigerant that has entered the section S3H flows out from the upper outlet pipe 9H. The refrigerant that has entered the section S2H is turned back there and travels to the section S5H through the refrigerant channel CH. The refrigerant that has entered the compartment S5H flows out from the lower outlet pipe 10H.

  The refrigerant flow path A1H has more flat tubes 4 than the refrigerant flow path A2H, and the upper inlet pipe 8H is connected to the upper position of the section S4H, so that the refrigerant flowing into the section S4H flows into the refrigerant flow. Easy to enter road A1H. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path originally, especially when used as an evaporator, the liquid refrigerant tends to flow downward, but the refrigerant flows into the upper and lower refrigerant flow paths. In a well-balanced manner, improving the heat exchange efficiency.

  The number of flat tubes 4 included in the refrigerant flow path (A1H, BH) from the inlet pipe 8H to the upper outlet pipe 9H, and the flatness included in the refrigerant flow path (A2H, CH) from the inlet pipe 8H to the lower outlet pipe 10H. The number of tubes 4 is 9 for the former and 8 for the latter. Thereby, the heat radiation area of the refrigerant passage from the inlet pipe 8H to the upper outlet pipe 9H increases, and the heat exchange amount increases.

  When the refrigerant is supplied to the section S4L through the inlet pipe 8L, the refrigerant goes to the sections S1L and S2L through the refrigerant flow paths A1L and A2L. The refrigerant that has entered the section S1L is turned back there, and passes through the refrigerant flow path BL toward the section S3L. The refrigerant that has entered the compartment S3L flows out of the upper outlet pipe 9L. The refrigerant that has entered the section S2L turns back there, and travels to the section S5L through the refrigerant flow path CL. The refrigerant that has entered the compartment S5L flows out of the lower outlet pipe 10L.

  The refrigerant flow path A1L has more flat tubes 4 than the refrigerant flow path A2L, and the upper inlet pipe 8L is connected to the upper position of the section S4L, so that the refrigerant flowing into the section S4L flows into the refrigerant flow. Easy to enter road A1L. For this reason, although the refrigerant tends to flow toward the lower refrigerant flow path originally, especially when used as an evaporator, the liquid refrigerant tends to flow downward, but the refrigerant flows into the upper and lower refrigerant flow paths. In a well-balanced manner, improving the heat exchange efficiency.

  The number of flat tubes 4 included in the refrigerant flow path (A1L, BL) from the inlet pipe 8L to the upper outlet pipe 9L and the flatness included in the refrigerant flow path (A2L, CL) from the inlet pipe 8L to the lower outlet pipe 10L. The number of tubes 4 is 9 for the former and 8 for the latter. Thereby, the heat radiation area of the refrigerant passage from the inlet pipe 8L to the upper outlet pipe 9L increases, and the heat exchange amount increases.

  The inlet pipes 8 </ b> H and 8 </ b> L are connected to each of a plurality of branch pipes separated from the single refrigerant pipe 11. The side connected to the inlet pipe 8H is a branch pipe 12H, and the side connected to the inlet pipe 8L is a branch pipe 12L.

  The shunt used in the fifth embodiment is of a type having two shunt pipes. If the number of inlet pipes exceeds 2, the shunt has a number of shunt pipes corresponding to that number. Can be used. Or what is necessary is just to respond | correspond to the increase in the number of inlet pipes combining several diverters.

  As shown in FIG. 7, the refrigerant pipe 11 is branched by a flow divider 13 into a branch pipe 12H and a branch pipe 12L. The diversion pipes 12H and 12L are connected to the diversion device 13 in a side-by-side state, and are parallel to each other at the connection location. The refrigerant pipe 11 is formed in such a manner that one line parallel to these center lines is drawn at the center between the center lines of the branch pipes 12H and 12L that are parallel to each other, and the center line is aligned with the line. Be placed.

  The refrigerant pipe 11 is flattened at a branch point, that is, immediately upstream of the flow divider 13, and the point is a flat part 11 a. The refrigerant pipe 11 is flattened in the side-by-side direction of the two branch pipes 12H and 12L arranged side by side.

  When the refrigerant is sent from the refrigerant pipe 11 toward the diversion pipes 12H and 12L, the flow rate of the refrigerant that has passed through the refrigerant pipe 11 increases at the flat portion 11a, and strikes the tip of the diversion wall 13a inside the diversion device 13 with force. . By increasing the flow velocity in this way, the refrigerant can be easily divided equally. Further, the flow is stabilized by dividing the refrigerant against the flow dividing wall 13a inside the flow divider 13.

  When the flat portion 11a is formed in the refrigerant pipe 11, the flattening in the direction in which the flow dividing pipes 12H and 12L are arranged side by side makes the refrigerant hit the flow dividing wall 13a without spreading and facilitates the flow dividing more evenly.

  The parallel flow heat exchangers 1A, 1B, 1C, 1D, and 1E can be mounted on a separate air conditioner. A separate type air conditioner is composed of an outdoor unit and an indoor unit. The outdoor unit includes a compressor, a four-way valve, an expansion valve, an outdoor heat exchanger, an outdoor fan, and the like. The indoor unit is an indoor heat exchanger, a room Includes an internal blower. The outdoor heat exchanger functions as an evaporator during heating operation and functions as a condenser during cooling operation. The indoor heat exchanger functions as a condenser during heating operation and functions as an evaporator during cooling operation.

  FIG. 8 shows a basic configuration of a separate type air conditioner that uses a heat pump cycle as a refrigeration cycle. The heat pump cycle 101 includes a compressor 102, a four-way valve 103, an outdoor heat exchanger 104, a decompression / expansion device 105, and an indoor heat exchanger 106 connected in a loop. The compressor 102, the four-way valve 103, the heat exchanger 104, and the decompression / expansion device 105 are accommodated in the casing of the outdoor unit, and the heat exchanger 106 is accommodated in the casing of the indoor unit. An outdoor fan 107 is combined with the heat exchanger 104, and an indoor fan 108 is combined with the heat exchanger 106. The blower 107 includes a propeller fan, and the blower 108 includes a cross flow fan.

  The side flow parallel flow heat exchangers 1A, 1B, 1C, 1D, and 1E according to the present invention can be used as components of the heat exchanger 106 of the indoor unit. The heat exchanger 106 is a combination of three heat exchangers 106A, 106B, 106C like a roof that covers the blower 108, and any one of the heat exchangers 106A, 106B, 106C is a parallel flow heat exchanger. 1A, 1B, 1C, 1D, 1E.

  FIG. 8 shows a state during heating operation. At this time, the high-temperature and high-pressure refrigerant discharged from the compressor 102 enters the indoor heat exchanger 106 where it dissipates heat and condenses. The refrigerant exiting the heat exchanger 106 enters the outdoor heat exchanger 104 from the decompression / expansion device 105 and expands there, takes heat from the outdoor air, and returns to the compressor 102. The airflow generated by the indoor fan 108 promotes heat dissipation from the heat exchanger 106, and the airflow generated by the outdoor fan 107 accelerates heat absorption of the heat exchanger 104.

  FIG. 9 shows a state during cooling operation or defrosting operation. At this time, the four-way valve 103 is switched so that the refrigerant flow is reversed from that during the heating operation. That is, the high-temperature and high-pressure refrigerant discharged from the compressor 102 enters the outdoor heat exchanger 104, where it dissipates heat and condenses. The refrigerant exiting the heat exchanger 104 enters the heat exchanger 106 on the indoor side from the decompression / expansion device 105 and expands there, takes heat from indoor air, and returns to the compressor 102. The airflow generated by the outdoor fan 107 promotes heat dissipation from the heat exchanger 104, and the airflow generated by the indoor fan 108 promotes heat absorption of the heat exchanger 106.

  The parallel flow heat exchangers 1A, 1B, 1C, 1D, and 1E can also be used as the heat exchanger 104 of the outdoor unit.

  Although the embodiments of the present invention have been described above, the scope of the present invention is not limited to these embodiments, and various modifications can be made without departing from the spirit of the invention.

  The present invention is widely applicable to side flow parallel flow heat exchangers.

1A, 1B, 1C, 1D, 1E Heat exchanger 2, 3 Header pipe 4 Flat tube 5 Refrigerant passage 6 Corrugated fin 7 Side plate 8, 8H, 8L Inlet pipe 9, 9H, 9L Upper outlet pipe 10, 10H, 10L Lower Outlet pipe 11 Refrigerant pipe 12H, 12L Split pipe 13 Splitter 13a Split wall

Claims (8)

In a parallel flow type heat exchanger of a side flow type comprising two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes,
The refrigerant flows into a predetermined section inside one of the two header pipes through the inlet pipe, flows into the other of the two header pipes through the plurality of flat tubes connected to the section, and is partitioned by a partition plate in the header pipe. It is divided into upper and lower, and finally the refrigerant flow path is configured to flow out from the upper outlet pipe and the lower outlet pipe,
A parallel flow heat exchanger characterized in that the refrigerant is more likely to enter the refrigerant flow path from the inlet pipe to the upper outlet pipe than the refrigerant flow path from the inlet pipe to the lower outlet pipe. .   The plurality of flat tubes connected to the compartment into which the refrigerant flows from the inlet pipe is divided into upper and lower parts so that the upper part is a comparatively large number and the lower part is a comparatively small number. The parallel flow heat exchanger according to claim 1, wherein the heat exchanger is a parallel flow type heat exchanger.   The parallel flow heat exchanger according to claim 1, wherein the inlet pipe is connected to a position above the section into which the refrigerant flows from the inlet pipe.   The flat tube is more distributed in the refrigerant flow path from the inlet pipe to the upper outlet pipe than in the refrigerant flow path from the inlet pipe to the lower outlet pipe. The parallel flow type heat exchanger according to any one of items 1 to 3.   5. The plurality of inlet pipes are connected to one of the header pipes, and the upper outlet pipe and the lower outlet pipe are provided for each of the plurality of inlet pipes. The parallel flow type heat exchanger according to any one of the above.   One of a plurality of branch pipes separated from one refrigerant pipe is connected to each of the plurality of inlet pipes, and the refrigerant pipe is flattened immediately upstream of the branching point to the plurality of branch pipes. 6. The parallel flow heat exchanger according to claim 5, wherein the heat exchanger is a parallel flow type heat exchanger.   The parallel flow heat exchanger according to claim 6, wherein the refrigerant pipe is flattened in a side-by-side direction of the plurality of branch pipes arranged side by side.   An air conditioner in which the parallel flow heat exchanger according to any one of claims 1 to 7 is mounted on an indoor unit or an outdoor unit.

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