CN210773626U - Heat exchanger and refrigeration cycle device - Google Patents

Abstract

The heat exchanger is provided with: a heat exchange unit having a plurality of plate-like fins arranged in parallel with an interval therebetween and a plurality of heat transfer tubes intersecting the plurality of plate-like fins; a header main pipe for supplying a refrigerant to the heat exchanger; and a plurality of branch pipes connected between the plurality of heat transfer pipes and a header main pipe, the header main pipe having a plurality of pipe portions having different distances from the heat exchange portion, the plurality of pipe portions being arranged such that a pipe portion having a longer pipe length is farther from the heat exchange portion.

Description

Heat exchanger and refrigeration cycle device

Technical Field

The utility model relates to a heat exchanger of air conditioner and possess this heat exchanger's refrigeration cycle device.

Background

Conventionally, as an outdoor heat exchanger of an air conditioner, there is provided a refrigerant heat exchanger configured by connecting a plurality of branch pipes extending from a header main pipe to one end portions of a plurality of heat transfer pipes through which a refrigerant flows in parallel (see, for example, patent document 1).

Patent document 1: japanese laid-open patent publication No. 2009-222366

In many cases, a metal such as copper or aluminum is used for the header main pipe of the heat exchanger. Therefore, the header main pipe expands in the longitudinal direction of the header main pipe at a high temperature and contracts in the longitudinal direction of the header main pipe at a low temperature. When the header main pipe expands or contracts, the branch pipes connected to the header main pipe may be bent in the longitudinal direction of the header main pipe. Therefore, when the header main pipe expands or contracts, stress concentration due to deformation occurs between the expanded pipe portion of the heat transfer pipe into which the branch pipe is inserted and the side plate of the heat exchange portion. As a result, when the cycle of expansion and contraction of the header main pipe is repeated, fatigue may occur in a portion where stress is concentrated, and the heat transfer pipe may be damaged.

SUMMERY OF THE UTILITY MODEL

The present invention has been made to solve the above problems, and provides a heat exchanger and a refrigeration cycle apparatus that suppress stress concentration caused by deformation between an expanded pipe portion of a heat pipe into which a branch pipe is inserted and a side plate.

The utility model relates to a heat exchanger possesses: a heat exchange unit having a plurality of plate-like fins arranged in parallel with an interval therebetween and a plurality of heat transfer tubes intersecting the plurality of plate-like fins; a header main pipe for supplying a refrigerant to the heat exchanger; and a plurality of branch pipes connected between the plurality of heat transfer pipes and a header main pipe, the header main pipe having a plurality of pipe portions having different distances from the heat exchange portion, the plurality of pipe portions being arranged such that a pipe portion having a longer pipe length is farther from the heat exchange portion.

Further, the following configuration is possible: the length of the branch pipe is different depending on the length of the piping portion connected to the branch pipe, and the length of the branch pipe is increased in proportion to the length of the piping portion.

Further, the following configuration is possible: the plurality of pipe portions are formed linearly along the arrangement direction of the plurality of heat transfer pipes.

Further, the following configuration is possible: the plurality of piping portions are arranged along the arrangement direction of the plurality of heat transfer pipes.

Further, the following configuration is possible: the plurality of pipe portions are connected to each other by a crank portion connecting end portions of the plurality of pipe portions to each other, and the pipe lines are connected in series.

Further, the following configuration is possible: the header main pipe further includes a plurality of branched distribution pipes, the plurality of pipe portions are divided, and the plurality of pipe portions are connected to the distribution pipes, respectively.

Further, the following configuration is possible: the plurality of piping portions include a first main piping portion and a second main piping portion having different lengths of piping, the second main piping portion is formed longer than the first main piping portion and is disposed farther from the heat exchange portion than the first main piping portion, and the branch pipes connected to the second main piping portion are longer than the branch pipes connected to the first main piping portion.

Further, the following configuration is possible: the plurality of piping portions include first main piping portions, second main piping portions, and third main piping portions having different lengths of piping, the third main piping portion is formed longer than the first main piping portion and is arranged farther from the heat exchange portion than the first main piping portion, the second main piping portion is formed longer than the third main piping portion and is arranged farther from the heat exchange portion than the third main piping portion, the branch pipes connected to the third main piping portion are formed longer than the branch pipes connected to the first main piping portion, and the branch pipes connected to the second main piping portion are formed longer than the branch pipes connected to the third main piping portion.

The utility model relates to a refrigeration cycle device possesses above-mentioned heat exchanger.

In the heat exchanger according to the present invention, the header main pipe has a plurality of pipe portions having different distances from the heat exchange portion, and the plurality of pipe portions are arranged so that the pipe portion having the longer length of the pipe is farther from the heat exchange portion. Therefore, the header main pipe can be regarded as a structure equivalent to a structure having a plurality of headers shorter in length than the straight pipes. As a result, the amount of contraction and expansion in the longitudinal direction of the header main pipe can be suppressed, the amount of bending of the branch pipe connected to the header main pipe can be suppressed, and the stress concentration on the expanded pipe portion of the heat conduction pipe can be alleviated.

Drawings

Fig. 1 is a schematic view of a heat exchanger according to embodiment 1 of the present invention.

Fig. 2 is a schematic view of the header main pipe and branch pipe of fig. 1.

Fig. 3 is a schematic diagram of a heat exchanger according to a comparative example.

Fig. 4 is a conceptual diagram of a temperature change from a heating operation to a defrosting operation in the header main pipe of the heat exchanger of fig. 3.

Fig. 5 is a schematic diagram of the heat exchanger of fig. 3 during a heating operation.

Fig. 6 is a schematic diagram of the heat exchanger of fig. 3 during a cooling operation or a defrosting operation.

Fig. 7 is an enlarged view of a portion G in the heat exchanger of fig. 6.

Fig. 8 is a diagram showing a relationship between a distance to a pipe end portion with respect to a central portion in a longitudinal direction of a header main pipe, a length of a branch pipe, and a strain amount of an expanded pipe portion in the heat exchanger of fig. 1 and the heat exchanger of fig. 3.

Fig. 9 is a schematic view of a heat exchanger according to embodiment 2 of the present invention.

Fig. 10 is a schematic view of the header main pipe and branch pipe of fig. 9.

Fig. 11 is a schematic view of a heat exchanger according to embodiment 3 of the present invention.

Fig. 12 is a schematic view of the header main pipe and branch pipe of fig. 11.

Fig. 13 is a diagram showing a configuration of a refrigeration cycle apparatus according to embodiment 4 of the present invention.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that, in the drawings, the same or corresponding structures are denoted by the same reference numerals and are common throughout the specification. The form of the constituent elements shown throughout the specification is merely an example, and is not limited to the description thereof.

Embodiment 1.

[ Structure of Heat exchanger 100 ]

Fig. 1 is a schematic view of a heat exchanger 100 according to embodiment 1 of the present invention. Fig. 2 is a schematic view of the header main pipe 10 and the branch pipe 20 in fig. 1. The heat exchanger 100 will be described with reference to fig. 1 and 2. The heat exchanger 100 is configured as a fin-tube type air-cooled heat exchanger. As shown in fig. 1, the heat exchanger 100 includes header main pipes 10, branch pipes 20 connected to the header main pipes 10, and a heat exchange portion 30 connected to the branch pipes 20. The heat exchanger 100 includes a pipe 40 connected to the heat exchange unit 30, a capillary tube 50 connected to the pipe 40, and a distributor 60 connected to the capillary tube 50.

(header main pipe 10)

The header main pipe 10 is a pipe that distributes the refrigerant flowing inside to the branch pipes 20 or joins the refrigerant flowing from the branch pipes 20. The header main pipe 10 supplies the refrigerant to the heat exchanger 30 or collects the refrigerant from the heat exchanger 30 through the branch pipes 20. The header main pipe 10 has a plurality of pipe portions having different distances from the heat exchange portion 30. As shown in fig. 1, the header main pipe 10 includes a first main pipe portion 11 to which one or more branch pipes 20 are connected and a second main pipe portion 12 to which one or more branch pipes 20 are connected, as a plurality of pipe portions having different distances from the heat exchange portion 30. The header main pipe 10 includes a crank portion 13 that connects the first main pipe portion 11 and the second main pipe portion 12 in a crank shape.

The first main pipe portion 11 is located on one end portion side in the extending direction of the side plate 31, and the second main pipe portion 12 is located on the other end portion side in the extending direction of the side plate 31. The first main tube portion 11 and the second main tube portion 12 are arranged along the extending direction of the side plates 31 constituting the heat exchange portion 30. In other words, the plurality of pipe portions of the header main pipe 10 are arranged along the arrangement direction of the plurality of heat transfer pipes 33. The pipe passage of the first main pipe portion 11 and the pipe passage of the second main pipe portion 12 are arranged along the extending direction of the side plate 31. That is, the pipe portions of the header main pipe 10 are formed linearly along the arrangement direction of the plurality of heat transfer pipes 33.

As shown in fig. 2, the length b of the pipeline of the first main pipe portion 11 is shorter than the length c of the pipeline of the second main pipe portion 12. That is, the length c of the pipe line of the second main pipe portion 12 is longer than the length b of the pipe line of the first main pipe portion 11. The plurality of piping portions of the header main piping 10 are arranged so that the longer the length of the pipe, the farther away the heat exchange portion 30. Therefore, as shown in fig. 1, the second main tube part 12 is disposed farther from the heat exchange part 30 than the first main tube part 11, and the distance between the second main tube part 12 and the heat exchange part 30 is larger than the distance between the first main tube part 11 and the heat exchange part 30. The relationship between the length b of the pipeline in the first main pipe portion 11 and the length c of the pipeline in the second main pipe portion 12 is not limited to the length b of the pipeline in the first main pipe portion 11 being shorter than the length c of the pipeline in the second main pipe portion 12. For example, the length b of the pipeline of the first main pipe section 11 may be longer than the length c of the pipeline of the second main pipe section 12. In this case, the first main tube part 11 is disposed farther from the heat exchange part 30 than the second main tube part 12, and the distance between the first main tube part 11 and the heat exchange part 30 is larger than the distance between the second main tube part 12 and the heat exchange part 30.

As shown in fig. 1 and 2, the crank shaft portion 13 connects an end portion of the first main pipe portion 11 and an end portion of the second main pipe portion 12, and the header main pipe 10 is formed in a crank shape. The crankshaft 13 is disposed between the plurality of pipe portions, and connects end portions of the plurality of pipe portions to each other to form a pipeline in series. The crankshaft 13 is disposed at a position distant from the heat exchanger 30 in either the first main pipe portion 11 or the second main pipe portion 12. As shown in fig. 1, when the length b of the pipe line of the first main pipe portion 11 is longer than the length c of the pipe line of the second main pipe portion 12, and the length c of the pipe line of the second main pipe portion 12 is longer, the second main pipe portion 12 is disposed at a position farther from the heat exchanger 30 than the first main pipe portion 11. When the length b of the pipe line of the first main pipe portion 11 is longer than the length c of the pipe line of the second main pipe portion 12, the first main pipe portion 11 is disposed at a position farther from the heat exchange portion 30 than the second main pipe portion 12. The crankshaft 13 may be formed integrally with the first main pipe portion 11 and the second main pipe portion 12 by bending the pipe, or may be formed of a crank type joint pipe that joins the first main pipe portion 11 and the second main pipe portion 12.

(Branch pipe 20)

The branch pipes 20 are connected between the heat transfer pipes 33 and the header main pipe 10. More specifically, as shown in fig. 1, the branch pipes 20 connect the header main pipe 10 and the expanded pipe portions 34 provided at the ends of the heat transfer pipes 33. The branch pipes 20 are arranged along the longitudinal direction of the header main pipe 10. The branch pipes 20 may be formed integrally with the header main pipe 10, or may be formed separately from the header main pipe 10. As shown in fig. 2, the branch pipe 20 includes a first branch pipe 21 connected to the first main pipe portion 11 and a second branch pipe 22 connected to the second main pipe portion 12. As shown in fig. 2, the length B of the piping of the first branch pipe 21 is shorter than the length C of the piping of the second branch pipe 22. That is, the length C of the pipe of the second branch pipe 22 is longer than the length B of the pipe of the first branch pipe 21. The relationship between the length B of the pipeline of the first branch pipe 21 and the length C of the pipeline of the second branch pipe 22 is not limited to the case where the length B of the pipeline of the first branch pipe 21 is shorter than the length C of the pipeline of the second branch pipe 22. For example, when the first main pipe portion 11 is disposed at a position farther from the heat exchange portion 30 than the second main pipe portion 12, the length B of the pipe line of the first branch pipe 21 is longer than the length C of the pipe line of the second branch pipe 22. That is, the branch pipes 20 connected to the pipe portion disposed at the farthest position from the heat exchange unit 30 among the first main pipe portion 11 and the second main pipe portion 12 have the longest length. In other words, the branch pipes 20 connected to the pipe portion having the longest length among the plurality of pipe portions of the header main pipe 10 have the longest length. The length of the branch pipe 20 differs depending on the length of the pipe portion connected thereto, and the length of the branch pipe 20 is increased in proportion to the length of the pipe portion connected thereto. Between the first main pipe portion 11 and the second main pipe portion 12, n short branch pipes 20 are connected to a short pipe portion, and m long branch pipes 20 are connected to a long pipe portion. The header main pipe 10 is connected to the heat exchange portion 30 of the heat exchanger 100 via the branch pipes 20. Therefore, the total number of n and m branch pipes 20 is the same as the number of heat transfer pipes 33 constituting the heat exchange unit 30 of the heat exchanger 100.

(Heat exchange portion 30)

The heat exchange unit 30 includes a plurality of plate-shaped fins 32 arranged in parallel with an interval therebetween, and a plurality of heat transfer tubes 33 intersecting the plurality of plate-shaped fins 32. The heat exchange unit 30 has a side plate 31 extending along the arrangement direction of the plurality of heat transfer pipes 33.

The plate-shaped fins 32 improve the heat exchange efficiency between the air and the refrigerant. The plate fins 32 are plate fins, but may be, for example, corrugated fins instead of plate fins. The plurality of heat transfer pipes 33 are arranged in parallel with each other with an interval in the heat exchange unit 30. The heat transfer pipe 33 is, for example, a circular pipe having a circular cross-sectional shape or an elliptical pipe. Alternatively, the heat transfer pipe 33 may be a flat pipe having a plurality of flow paths formed therein. The heat transfer pipe 33 is formed as a bent pipe bent in a hairpin-like U shape. In the heat exchange unit 30, the plurality of plate-like fins 32 are arranged at intervals from each other, and heat is exchanged between the air flowing between the adjacent plate-like fins 32 and the heat exchange medium, for example, the refrigerant, flowing inside the plurality of heat transfer tubes 33. The expanded pipe portion 34 provided at the pipe end of the heat transfer pipe 33 is disposed to protrude from the side plate 31. The branch pipes 20 are connected to one expanded pipe portion 34 of the heat transfer pipe 33 formed in a U shape, and the pipe 40 is connected to the other expanded pipe portion 34 of the heat transfer pipe 33. The side plate 31 extends along the longitudinal direction of the header main pipe 10. The side plate 31 is a plate-like member having one end portion and the other end portion positioned on substantially the same plane. The side plate 31 pressing the plate-like fins 32 is formed with a through hole through which the tube end of the heat transfer tube 33 protrudes.

[ operation of Heat exchanger 100 ]

The operation of the heat exchanger 100 according to embodiment 1 of the present invention will be described. In the air conditioner, the heat exchanger 100 functions as a condenser during a cooling operation. The refrigerant flowing through the header main pipe 10 is distributed to the heat transfer pipes 33 via the branch pipes 20. The refrigerant having flowed into the heat transfer pipe 33 is condensed by heat exchange with the air passing through the plate-like fins 32. The refrigerant having undergone heat exchange in heat transfer pipe 33 flows out to pipe 40, passes through capillary tube 50, and joins in distributor 60. In the air conditioner, in the case of heating operation, that is, in the case where the heat exchanger 100 functions as an evaporator, the refrigerant flows in the direction opposite to the flow in the case of the condenser. In the refrigeration cycle, the refrigerant that has flowed into the distributor 60 is distributed to the heat transfer pipe 33 through the capillary tube 50 and the pipe 40. The refrigerant having flowed into the heat transfer pipe 33 is evaporated by heat exchange between the heat transfer pipe 33 and the air passing through the plate-like fins 32. The refrigerant having undergone heat exchange in the heat transfer tubes 33 flows out to the branch pipes 20 and joins the header main pipe 10.

Fig. 3 is a schematic diagram of a heat exchanger 200 according to a comparative example. Here, as a comparative example, a heat exchanger 200 in which the header main pipe 210 is formed of one straight pipe-shaped pipe will be described. Note that the same reference numerals are given to portions having the same configurations as those of the heat exchanger 100 of fig. 1 to 2, and the description thereof is omitted. First, a refrigerant circuit structure of a general air conditioner includes, on the outdoor unit side, a compressor, a flow path switching device such as a four-way valve for switching a flow path of a refrigerant, an outdoor heat exchanger, an outdoor blower, a valve for connecting a liquid-side extension pipe, a valve for connecting a gas-side extension pipe, and the like. The indoor unit side includes an indoor heat exchanger and an indoor fan. Further, a pressure reducing mechanism such as an electronic expansion valve or a capillary tube is provided in a liquid refrigerant passage between the outdoor heat exchanger and the indoor heat exchanger. The pressure reducing mechanism is disposed in the outdoor unit or the indoor unit, or disposed between the outdoor unit and the indoor unit in a casing different from the outdoor unit and the indoor unit.

When the air conditioner performs a cooling operation, the gas refrigerant discharged from the compressor flows to the outdoor heat exchanger through the flow switching device. After the refrigerant is subjected to the superheat exchange in the outdoor heat exchanger, the refrigerant flows through the decompression mechanism and the liquid-side extension pipe to the indoor heat exchanger, and returns to the compressor suction side again through the flow path switching device. When the air conditioner is in the heating operation, the gas refrigerant discharged from the compressor flows to the indoor heat exchanger through the flow switching device. After the refrigerant is subjected to the superheat exchange in the indoor heat exchanger, the refrigerant passes through the decompression mechanism and the outdoor heat exchanger in a direction opposite to the direction in which the refrigerant flows during the cooling operation, and returns to the suction side of the compressor. Here, when the air conditioner performs the heating operation, the temperature of the surface of the outdoor heat exchanger serving as the evaporator is negative in many cases, and in this case, moisture is caused to be adsorbed to the heat exchanger by the air having passed through the surface of the heat exchanger having reached the dew-point temperature, and therefore the moisture may remain in the heat exchanger as frost. When the heating operation of the air conditioner is continued in such a situation, the amount of frost adhering to the heat exchanger gradually increases, and therefore, it is necessary to periodically perform an operation of defrosting by observing the temperature of the outdoor heat exchanger, the operation elapsed time, or the like. The defrosting operation of the air conditioner is performed by temporarily interrupting the heating operation and causing the flow direction of the refrigerant to be the direction of the cooling operation by the flow path switching device. When the air conditioner is set to a cooling operation, a high-temperature refrigerant flows through the outdoor heat exchanger, the temperature of the heat exchanger rises, and the adhering frost can be melted.

Fig. 4 is a conceptual diagram of a temperature change from the heating operation to the defrosting operation of header main pipe 210 of heat exchanger 200 in fig. 3. In fig. 4, the vertical axis represents the temperature of header main pipe 210, and the horizontal axis represents the operating time of heat exchanger 200. The time T1 is the time immediately before the defrosting operation starts, and the time T2 is the time immediately before the defrosting operation ends. The period from time T0 to time T1 is the period during the heating operation, and the period P1 between time T1 and time T2 is the period during the defrosting operation. The header main pipe 210 of the heat exchanger 200 is in a temperature state substantially equal to the surface of the heat exchanger 200 during the heating operation. However, as shown in fig. 4, the header main pipe 210 of the heat exchanger 200 is in a high-temperature state because high-temperature gas refrigerant discharged from the compressor flows into it during the defrosting operation. As shown in fig. 4, the temperature of header main pipe 210 is the lowest temperature at time T1 immediately before the start of the defrosting operation, and is the highest temperature at time T2 immediately before the end of the defrosting operation.

Fig. 5 is a schematic diagram of the heat exchanger 200 of fig. 3 during a heating operation. Fig. 6 is a schematic diagram of the heat exchanger 200 of fig. 3 during a cooling operation or a defrosting operation. In general, a metal such as copper or aluminum is often used for a header main pipe of a heat exchanger. Therefore, in the heating operation in which the outdoor heat exchanger 200 functions as an evaporator, the header main pipe 210 of the heat exchanger 200 is at a low temperature, and the header main pipe 210 contracts in the longitudinal direction as shown in fig. 5. Note that the hollow arrows shown in fig. 5 indicate contraction of the header main pipe 210. At this time, for example, the branch pipes 20 connected to the lowest stage of the heat exchange unit 30 and connected to the header main pipes 210 are bent upward on the side connected to the header main pipes 210 as the header main pipes 210 contract. In the case of a cooling or defrosting operation in which the heat exchanger 200 on the outdoor side functions as a condenser, the header main pipe 210 of the heat exchanger 200 is at a high temperature, and the header main pipe 210 expands in the longitudinal direction as shown in fig. 6. Note that the hollow arrows shown in fig. 6 indicate the expansion of the header main pipe 210. At this time, for example, the branch pipes 20 connected to the lowest stage of the heat exchange unit 30 and connected to the header main pipes 210 are bent downward on the side connected to the header main pipes 210 as the header main pipes 210 expand.

Fig. 7 is an enlarged view of a portion G in the heat exchanger 200 of fig. 6. In fig. 7, the open arrows indicate the expansion of header main pipe 210 in the case of a cooling or defrosting operation in which heat exchanger 200 on the outdoor side functions as a condenser. In fig. 7, the broken line indicates a bent state of the branch pipe 20 accompanying expansion of the header main pipe 210. As described above, header main pipe 210 contracts in the longitudinal direction at a low temperature, and expands in the longitudinal direction at a high temperature. Then, the branch pipes 20 connected to the header main pipes 210 are bent in the vertical direction in accordance with the expansion and contraction of the header main pipes 210. Therefore, as shown in fig. 7, the expanded pipe portion 34 located at the pipe end of the heat transfer pipe 33 into which the branch pipe 20 is inserted generates stress concentration due to deformation in a portion in close contact with the side plate 31. When the cycle of expansion and contraction of the header main pipe 210 is repeated, fatigue may occur in a portion where stress is concentrated between the branch pipes 20 and the side plates 31, and the heat transfer pipe 33 may be damaged. The bends of the branch pipes 20 increase in proportion to the distance from the central portion in the longitudinal direction of the header main pipe 210, and thus the stress generated in the expanded pipe portion 34 of the heat transfer pipe 33 also increases. In recent years, there have been many demands for an expanded cooling capacity in the market, and to cope with such a demand, the heat exchanger on the outdoor side has been increased in size. Therefore, when the heat exchanger 200 is increased in size in the height direction, the length of the header main pipe 210 is inevitably longer than that of the conventional one. When the header main pipe 210 is lengthened, the distance from the branch pipes 20 located at the end portion to the central portion in the longitudinal direction of the header main pipe 210 becomes longer, and the concentration of stress to the expanded pipe portion 34 due to the bending of the branch pipes 20 becomes larger, and the heat transfer pipes 33 are more likely to be damaged.

Fig. 8 is a diagram showing the relationship between the distance to the pipe end at the center in the longitudinal direction of the header main pipe, the length of the branch pipe 20, and the strain amount of the expanded pipe portion 34 in the heat exchanger 100 of fig. 1 and the heat exchanger 200 of fig. 3. In fig. 8, the vertical axis represents the strain amount of the expanded pipe portion 34, and the horizontal axis represents the distance between the center portion and the pipe end portion in the longitudinal direction of the header main pipe 10 and the header main pipe 210. Further, the curve a1, the curve B1, and the curve C1 represent the branch pipes 20 having different lengths. Curve A1 represents a leg 20 of length A, curve B1 represents a leg 20 of length B, and curve C1 represents a leg 20 of length C. The length a of the branch pipe 20 is longer than the length C of the branch pipe 20, and the length C of the branch pipe 20 is longer than the length B of the branch pipe 20. The predetermined forms of the length a, length B, and length C of the branch pipe 20 will be described later. As shown in fig. 8, the strain amount of the expanded pipe portion 34 with respect to the length of the branch pipe 20 is larger as shown by proportional curves of a curve a1, a curve B1, and a curve C1, and the strain amount is larger for a pipe having a shorter length of the branch pipe 20.

Here, the allowable strain amount of the expanded pipe portion 34 of a certain heat exchange portion 30 is represented by X, and in the heat exchanger 200 of fig. 3, when the length of the header main pipe 210 is represented by length a, the length of the branch pipe 20 capable of mitigating the strain amount is represented by length a. In general, the strain amount of the expanded pipe portion 34 at the uppermost stage or the lowermost stage at the position farthest from the center portion in the longitudinal direction of the header main pipe 210 is the largest, and therefore the length a of the branch pipe 20 is determined at the position of the length a/2 of the header main pipe 210. As shown by the curve a1, the relationship between the distance between the axial center portion of the header main pipe 210 and the pipe end portion and the strain amount of the expanded pipe portion 34 at a certain length a of the branch pipe 20 is approximately proportional to each other as shown in fig. 8.

Next, as in the heat exchanger 100 shown in fig. 1 and 2, the crankshaft 13 is provided, and the length of the first main pipe portion 11 is denoted by length b, and the length of the second main pipe portion 12 is denoted by length c. In addition, in the header main pipe 210 and the header main pipe 10, it is assumed that "the length a of the header main pipe 210 is equal to the length b of the first main pipe portion 11 + the length c of the second main pipe portion 12" is satisfied. Assuming that the length of the first main pipe portion 11 is the length B, the length of the branch pipe 20 capable of reducing the strain amount is the length B. In general, the strain amount of the expanded pipe portion 34 at the uppermost stage or the lowermost stage at the position farthest from the center portion in the longitudinal direction of the first main pipe portion 11 is the largest, and therefore the length B of the branch pipe 20 is determined at the position of the length B/2 of the first main pipe portion 11. As shown by the curve B1, the relationship between the distance between the axial center portion of the first main pipe portion 11 and the pipe end portion at a certain length B of the branch pipe 20 and the strain amount of the expanded pipe portion 34 is approximately proportional to each other as shown in fig. 8.

Similarly, assuming that the length of the second main pipe portion 12 is the length C, the length of the branch pipe 20 capable of reducing the strain amount is the length C. In general, the strain amount of the expanded pipe portion 34 at the uppermost stage or the lowermost stage at the position farthest from the center portion in the longitudinal direction of the second main pipe portion 12 is the largest, and therefore the length C of the branch pipe 20 is determined at the position of the length C/2 of the second main pipe portion 12. As shown by the curve C1, the relationship between the distance between the axial center portion of the first main pipe portion 11 and the pipe end portion when the length C of the branch pipe 20 is constant and the strain amount of the expanded pipe portion 34 is approximately proportional as shown in fig. 8.

In the header main pipe 210 and the header main pipe 10, when the relationship "the length a of the header main pipe 210 is equal to the length B of the first main pipe portion 11 + the length C of the second main pipe portion 12" is satisfied, "the length B of the branch pipe 20 < the length C of the branch pipe 20 < the length a of the branch pipe 20" is satisfied. Therefore, in the heat exchanger 100 of fig. 1, the distance between the header main pipe 10 and the expanded pipe portion 34 of the heat transfer pipe 33 can be made smaller than the distance between the header main pipe 210 and the expanded pipe portion 34 of the heat transfer pipe 33, as compared with the heat exchanger 200 of fig. 3. As a result, the heat exchanger 100 of fig. 1 can be made smaller and the space in the casing of the outdoor unit can be effectively used, as compared with a case where the distance between the header main pipe 210 and the expanded pipe portion 34 is simply increased.

As described above, the header main pipe 10 of the heat exchanger 100 includes a plurality of pipe portions having different distances from the heat exchange unit 30, and the plurality of pipe portions are arranged so that the pipe portion having the longer length of the pipe is farther from the heat exchange unit 30. Therefore, the header main pipe 10 can be regarded as a structure equivalent to a structure having a plurality of headers each having a length shorter than that of a straight pipe. As a result, the contraction amount and the expansion amount in the longitudinal direction of the header main pipe 10 can be suppressed, the bending amount of the branch pipes 20 connected to the header main pipe 10 can be suppressed, and the stress concentration on the expanded pipe portions 34 of the heat conducting pipes 33 can be alleviated.

The length of the branch pipe 20 differs depending on the length of the pipe portion of the header main pipe 10 to be connected. The length of the branch pipe 20 is increased in proportion to the length of the pipe portion of the header main pipe 10 to be connected. As described above, the contraction amount and the expansion amount increase as the length of the header main pipe 10 increases. In the heat exchanger 100, the longer the pipe portion of the header main pipe 10 to be connected, the longer the branch pipes 20 are connected, and the longer the branch pipes 20 are provided, whereby the bending accompanying the expansion and contraction of the header main pipe 10 can be suppressed. Further, as a method of alleviating stress concentration between the branch pipes 20 and the side plate 31, for example, it is assumed that the distance between the header main pipe 210 and the expanded pipe portion 34 of the heat transfer pipe 33 is increased by extending all the branch pipes 20 in the heat exchanger 200. However, each of the compressor and the refrigerant circuit is housed in the casing of the outdoor unit housing the heat exchanger 200, and the distance between the header main pipe 210 and the expanded pipe portion 34 is increased, so that the space in the machine room is reduced, and a necessary space may not be secured. In contrast, in the heat exchanger 100, the length of the branch pipes 20 can be shortened as compared with a case where the distance between the header main pipe 210 and the expanded pipe portion 34 of the heat transfer pipe 33 is simply increased, and therefore, the heat exchanger 100 can be downsized. As a result, the space in the casing of the outdoor unit can be effectively used. Further, if the pipe portion of the header main pipe 10 is formed in a crank shape without changing the length of the branch pipes 20, the header main pipe 10 of the heat exchange portion 30 is arranged to enter the heat exchange portion 30, thereby reducing the volume of the heat exchange portion 30. In contrast, in the heat exchanger 100, the branch pipes 20 of the long header main pipe 10, which are far from the heat exchanger 100, are lengthened by the distance, and thus the heat exchange portion 30 connected to the branch pipes 20 of the short header main pipe 10 does not need to be reduced in volume.

The heat exchanger 100 is connected by a crank portion 13, and the crank portion 13 connects the end portions of the plurality of pipe portions to each other, and the pipe lines are connected in series. The length of the header main pipe 10 in the longitudinal direction is divided by the crank portion 13, and thus can be regarded as a structure equivalent to a structure having a plurality of headers shorter in length than the straight pipe headers. Therefore, the header main pipe 10 can be regarded as a structure equivalent to a structure in which a plurality of headers having a shorter length than the straight pipe headers are provided. As a result, the contraction amount and the expansion amount in the longitudinal direction of the header main pipe 10 can be suppressed, the bending amount of the branch pipes 20 connected to the header main pipe 10 can be suppressed, and the stress concentration on the expanded pipe portions 34 of the heat conducting pipes 33 can be relaxed.

In the heat exchanger 100, the pipe portion of the header main pipe 10 is formed linearly along the arrangement direction of the plurality of heat transfer pipes 33. The plurality of piping portions are arranged along the arrangement direction of the plurality of heat transfer pipes 33. Therefore, the header main pipe 10 can be disposed so that pipe portions having different lengths face the heat exchange portion 30. The header main pipe 10 can be regarded as a structure equivalent to a structure having a plurality of headers shorter in length than the straight pipes. As a result, the contraction amount and the expansion amount in the longitudinal direction of the header main pipe 10 can be suppressed, the bending amount of the branch pipes 20 connected to the header main pipe 10 can be suppressed, and the stress concentration on the expanded pipe portions 34 of the heat conducting pipes 33 can be relaxed.

The heat exchanger 100 includes a first main tube portion 11 and a second main tube portion 12 having different tube lengths as a plurality of tube portions of the header main tube 10. Also, the second main pipe portion 12 is formed longer than the first main pipe portion 11, and is disposed farther from the heat exchange portion 30 than the first main pipe portion 11. The second branch pipe 22 connected to the second main pipe portion 12 is longer than the first branch pipe 21 connected to the first main pipe portion 11. Therefore, the header main pipe 10 can be regarded as a structure equivalent to a structure having a plurality of headers shorter in length than the straight pipe headers. As a result, the contraction amount and the expansion amount in the longitudinal direction of the header main pipe 10 can be suppressed, the bending amount of the branch pipes 20 connected to the header main pipe 10 can be suppressed, and the stress concentration on the expanded pipe portions 34 of the heat conducting pipes 33 can be alleviated. In the heat exchanger 100, the longer the pipe portion of the header main pipe 10 to be connected, the longer the branch pipes 20 are connected, and the longer the branch pipes 20 are provided, whereby the bending accompanying the expansion and contraction of the header main pipe 10 can be further suppressed.

Embodiment 2.

Fig. 9 is a schematic diagram of a heat exchanger 100A according to embodiment 2 of the present invention.

Fig. 10 is a schematic view of the header main pipe 10A and the branch pipes 20 in fig. 9. Note that the same reference numerals are given to portions having the same configurations as those of the heat exchanger 100 of fig. 1 to 2, and the description thereof is omitted. The heat exchanger 100A according to embodiment 2 differs from the main header pipe 10 in the structure of the main header pipe 10A.

(header main pipe 10A)

The header main pipe 10A is a pipe that distributes the refrigerant flowing inside to the branch pipes 20 or joins the refrigerant flowing from the branch pipes 20. The header main pipe 10A supplies the refrigerant to the heat exchange portion 30 or collects the refrigerant from the heat exchange portion 30 via the branch pipes 20. The header main pipe 10A has a plurality of pipe portions having different distances from the heat exchange portion 30. As shown in fig. 9, the header main pipe 10A includes a first main pipe portion 11 to which one or more branch pipes 20 are connected and a second main pipe portion 12 to which one or more branch pipes 20 are connected, as a plurality of pipe portions having different distances from the heat exchange portion 30. The header main pipe 10A further includes a third main pipe portion 14 to which one or more branch pipes 20 are connected, as shown in fig. 9, as a plurality of pipe portions having different distances from the heat exchange portion 30. The header main pipe 10A includes a crank shaft portion 13A that connects the first main pipe portion 11 and the third main pipe portion 14 in a crank shape, and a crank shaft portion 13B that connects the third main pipe portion 14 and the second main pipe portion 12 in a crank shape.

The first main pipe portion 11 is located on one end portion side in the extending direction of the side plate 31, and the second main pipe portion 12 is located on the other end portion side in the extending direction of the side plate 31. The third main pipe portion 14 is disposed between the first main pipe portion 11 and the second main pipe portion 12. In other words, the plurality of pipe portions of the header main pipe 10A are arranged along the arrangement direction of the plurality of heat transfer pipes 33. The first main tube portion 11, the third main tube portion 14, and the second main tube portion 12 are arranged along the extending direction of the side plates 31 constituting the heat exchange portion 30. Therefore, the pipe passage of the first main pipe portion 11, the pipe passage of the third main pipe portion 14, and the pipe passage of the second main pipe portion 12 are arranged along the extending direction of the side plate 31. That is, the pipe portions of the header main pipe 10A are formed linearly along the arrangement direction of the plurality of heat transfer pipes 33. As shown in fig. 10, the length b of the pipeline of the first main pipe portion 11 is shorter than the length d of the pipeline of the third main pipe portion 14. Further, the length d of the pipe passage of the third main pipe portion is shorter than the length c of the pipe passage of the second main pipe portion 12. That is, the length c of the pipe line of the second main pipe portion 12 is longer than the length d of the pipe line of the third main pipe portion 14, and the length d of the pipe line of the third main pipe portion 14 is longer than the length b of the pipe line of the first main pipe portion 11. The relationship among the length b of the pipeline in the first main pipe portion 11, the length d of the third main pipe portion 14, and the length c of the pipeline in the second main pipe portion 12 is not limited to the relationship "length c > length d > length b". For example, the relationship between the length b of the pipeline in the first main pipe portion 11, the length d of the third main pipe portion 14, and the length c of the pipeline in the second main pipe portion 12 may be, for example, "length c < length d < length b", or "length c > length d-length b".

As shown in fig. 9 and 10, the crank shaft portion 13A connects the end of the first main pipe portion 11 and the end of the third main pipe portion 14, and the header main pipe 10A is formed in a crank shape. The crankshaft 13B is disposed between the plurality of pipe portions, and connects the ends of the plurality of pipe portions to each other, thereby configuring the pipeline in a serial manner. The crankshaft 13A disposes either the first main pipe portion 11 or the third main pipe portion 14 at a position distant from the heat exchange portion 30. As shown in fig. 9, when the length b of the pipe line of the first main pipe portion 11 is longer than the length d of the pipe line of the third main pipe portion 14 and the length d of the pipe line of the third main pipe portion 14 is longer, the third main pipe portion 14 is disposed at a position farther from the heat exchanger 30 than the first main pipe portion 11. When the length b of the pipe line of the first main pipe portion 11 is longer than the length d of the pipe line of the third main pipe portion 14, the first main pipe portion 11 is disposed at a position farther from the heat exchanger 30 than the third main pipe portion 14. The bent portion 13A may be formed integrally with the first main pipe portion 11 and the third main pipe portion 14 by bending the pipe, or may be formed of a pipe joining the first main pipe portion 11 and the third main pipe portion 14.

As shown in fig. 9 and 10, the crank portion 13B connects an end of the third main pipe portion 14 and an end of the second main pipe portion 12, and configures the header main pipe 10A in a crank shape. The crankshaft 13B is disposed between the plurality of pipe portions, and connects the ends of the plurality of pipe portions to each other, thereby configuring the pipeline in a serial manner. The crankshaft 13B disposes either the third main pipe portion 14 or the second main pipe portion 12 at a position distant from the heat exchange portion 30. As shown in fig. 9, when the length d of the pipe line of the third main pipe portion 14 is longer than the length c of the pipe line of the second main pipe portion 12 and the length c of the pipe line of the second main pipe portion 12 is longer, the second main pipe portion 12 is disposed at a position farther from the heat exchanger 30 than the third main pipe portion 14. When the length d of the pipe passage of the third main pipe portion 14 is longer than the length c of the pipe passage of the second main pipe portion 12, the third main pipe portion 14 is disposed at a position farther from the heat exchange portion 30 than the second main pipe portion 12. The bent portion 13B may be formed integrally with the third main pipe portion 14 and the second main pipe portion 12 by bending the pipe, or may be formed of a pipe joining the third main pipe portion 14 and the second main pipe portion 12.

(Branch pipe 20)

The branch pipes 20 are connected between the heat transfer pipes 33 and the header main pipe 10A. More specifically, as shown in fig. 10, the branch pipes 20 connect the header main pipe 10A and the expanded pipe portions 34 provided at the ends of the heat transfer pipes 33. The branch pipes 20 are arranged along the longitudinal direction of the header main pipe 10A. The branch pipes 20 may be formed integrally with the header main pipe 10A, or may be formed separately from the header main pipe 10A. The branch pipe 20 includes a first branch pipe 21 disposed in the first main pipe portion 11, a second branch pipe 22 disposed in the second main pipe portion 12, and a third branch pipe 23 disposed in the third main pipe portion 14. As shown in fig. 10, the length B of the piping of the first branch pipe 21 is shorter than the length D of the piping of the third branch pipe 23. That is, the length D of the pipe of the third branch pipe 23 is longer than the length B of the pipe of the first branch pipe 21. In addition, as shown in fig. 10, the length D of the pipe of the third branch pipe 23 is shorter than the length C of the pipe of the second branch pipe 22. That is, the length C of the pipe of the second branch pipe 22 is longer than the length D of the pipe of the third branch pipe 23. The relationship among the length B of the pipeline of the first branch pipe 21, the length C of the pipeline of the second branch pipe 22, and the third branch pipe 23 is not limited to the length B of the pipeline of the first branch pipe 21 being shorter than the length C of the pipeline of the second branch pipe 22. For example, in the case where the first main pipe portion 11 is disposed at a position farther from the heat exchange portion 30 than the third main pipe portion 14, the length B of the pipe passage of the first branch pipe 21 is longer than the length D of the pipe passage of the third branch pipe 23. Similarly, when the third main pipe portion 14 is disposed at a position farther from the heat exchange portion 30 than the second main pipe portion 12, the length D of the pipe line of the third branch pipe 23 is longer than the length C of the pipe line of the second branch pipe 22. That is, the branch pipes 20 of the pipes disposed at the farthest positions from the side plates 31 among the first main pipe portion 11, the second main pipe portion 12, and the third main pipe portion 14 have the longest length. In other words, the branch pipes 20 connected to the longest piping portion among the plurality of piping portions of the header main piping 10A have the longest length. The length of the branch pipe 20 differs depending on the length of the pipe portion connected thereto, and the length of the branch pipe 20 is increased in proportion to the length of the pipe portion connected thereto. Between the first main pipe portion 11 and the second main pipe portion 12, n short branch pipes 20 are attached to the short header main pipe 10A, and m long branch pipes 20 are attached to the long main pipe portion. In addition, p branch pipes 20 are attached to the third main pipe portion 14. The header main pipe 10A is connected to the heat exchange portion 30 of the heat exchanger 100A via the branch pipes 20. Therefore, the total number of n, m, and p t branch pipes 20 is the same as the number of heat transfer pipes 33 constituting the heat exchange unit 30 of the heat exchanger 100A.

As described above, the header main pipe 10A of the heat exchanger 100A has a plurality of pipe portions having different distances from the heat exchange portion 30, and the plurality of pipe portions are arranged so that the pipe portion having the longer length of the pipe is farther from the heat exchange portion 30. Therefore, the header main pipe 10A can be regarded as a structure equivalent to a structure having a plurality of headers shorter in length than the straight pipe headers. As a result, the contraction amount and the expansion amount in the longitudinal direction of the header main pipe 10A can be suppressed, the bending amount of the branch pipes 20 connected to the header main pipe 10A can be suppressed, and the stress concentration on the expanded pipe portions 34 of the heat conducting pipes 33 can be relaxed.

The heat exchanger 100A includes, as a plurality of pipe portions of the header main pipe 10A, a first main pipe portion 11, a second main pipe portion 12, and a third main pipe portion 14 having different pipe lengths. Also, the third main pipe portion 14 is formed longer than the first main pipe portion 11, and is disposed farther from the heat exchange portion 30 than the first main pipe portion 11. In addition, the second main tube part 12 is formed longer than the third main tube part 14, and is disposed farther from the heat exchange part 30 than the third main tube part 14. The third branch pipe 23 connected to the third main pipe portion 14 is formed longer than the first branch pipe 21 connected to the first main pipe portion 11, and the second branch pipe 22 connected to the second main pipe portion 12 is formed longer than the third branch pipe 23 connected to the third main pipe portion 14. Therefore, the header main pipe 10A can be regarded as a structure equivalent to a structure having a plurality of headers shorter in length than the straight pipe headers. As a result, the contraction amount and the expansion amount in the longitudinal direction of the header main pipe 10A can be suppressed, the bending amount of the branch pipes 20 connected to the header main pipe 10A can be suppressed, and the stress concentration on the expanded pipe portions 34 of the heat conducting pipes 33 can be relaxed. In the heat exchanger 100A, the longer the pipe portion of the header main pipe 10A to be connected, the longer the branch pipes 20 are connected, and the longer the branch pipes 20 are provided, whereby the bending accompanying the expansion and contraction of the header main pipe 10A can be further suppressed. The header main pipe 10A of the heat exchanger 100A has 3 portions having different distances from the heat exchange unit 30. Therefore, the heat exchanger 100A can be made smaller by shortening the length of the branch pipes 20, and the space in the casing of the outdoor unit can be used more effectively.

The header main pipe 10A of the heat exchanger 100A has 3 portions having different distances from the heat exchange portion 30, and has two crank portions 13A and 13B, but the heat exchanger 100A is not limited to this configuration. For example, the header main pipe 10A of the heat exchanger 100A may have 4 or more portions having different distances from the heat exchange portion 30, and may have 3 or more crank portions 13. That is, the heat exchanger 100A may be configured such that the header main pipe 10A has n or more portions having different distances from the heat exchange portion 30, and has n-1 or more crank portions 13.

Embodiment 3.

Fig. 11 is a schematic diagram of a heat exchanger 100B according to embodiment 3 of the present invention. Fig. 12 is a schematic view of the header main pipe 10B and the branch pipe 20 in fig. 11. Note that the same reference numerals are given to portions having the same configurations as those of the heat exchanger 100 of fig. 1 to 2, and the description thereof is omitted. The heat exchanger 100B according to embodiment 2 differs from the main header pipe 10 in the structure of the main header pipe 10B.

(header main pipe 10B)

The header main pipe 10B is a pipe that distributes the refrigerant flowing inside to the branch pipes 20 or joins the refrigerants flowing from the branch pipes 20. The header main pipe 10B supplies the refrigerant to the heat exchange portion 30 or collects the refrigerant from the heat exchange portion 30 via the branch pipes 20. The header main pipe 10B has a plurality of pipe portions having different distances from the heat exchange portion 30. As shown in fig. 11, the header main pipe 10B includes a first main pipe portion 11 to which one or more branch pipes 20 are connected and a second main pipe portion 12 to which one or more branch pipes 20 are connected, as a plurality of pipe portions having different distances from the heat exchange portion 30. The manifold main pipe 10B is divided into a plurality of pipe portions, and a first main pipe portion 11 and a second main pipe portion 12. The header main pipe 10B further includes a plurality of branched distribution pipes 15.

The first main pipe portion 11 is located on one end portion side in the extending direction of the side plate 31, and the second main pipe portion 12 is located on the other end portion side in the extending direction of the side plate 31. The first main tube portion 11 and the second main tube portion 12 are arranged along the extending direction of the side plates 31 constituting the heat exchange portion 30. In other words, the plurality of pipe portions of the header main pipe 10B are arranged along the arrangement direction of the plurality of heat transfer pipes 33. The pipe passage of the first main pipe portion 11 and the pipe passage of the second main pipe portion 12 are arranged along the extending direction of the side plate 31. That is, the pipe portions of the header main pipe 10B are formed linearly along the arrangement direction of the plurality of heat transfer pipes 33.

As shown in fig. 12, the length b of the pipeline of the first main pipe portion 11 is shorter than the length c of the pipeline of the second main pipe portion 12. That is, the length c of the pipe line of the second main pipe portion 12 is longer than the length b of the pipe line of the first main pipe portion 11. The plurality of piping portions of the header main piping 10B are arranged so that the longer the length of the pipe, the farther away the heat exchange portion 30. Therefore, as shown in fig. 12, the second main pipe portion 12 is disposed farther from the heat exchange portion 30 than the first main pipe portion 11. That is, the distance between the second main tube part 12 and the heat exchange part 30 is greater than the distance between the first main tube part 11 and the heat exchange part 30. The relationship between the length b of the pipeline in the first main pipe portion 11 and the length c of the pipeline in the second main pipe portion 12 is not limited to the case where the length b of the pipeline in the first main pipe portion 11 is shorter than the length c of the pipeline in the second main pipe portion 12. For example, the length b of the pipeline of the first main pipe section 11 may be longer than the length c of the pipeline of the second main pipe section 12. In this case, the first main pipe portion 11 is disposed farther from the heat exchange portion 30 than the second main pipe portion 12. That is, the distance between the first main tube part 11 and the heat exchange part 30 is greater than the distance between the second main tube part 12 and the heat exchange part 30.

The distribution pipe 15 is connected to a plurality of divided pipe portions of the header main pipe 10B. As shown in fig. 11 and 12, the distribution pipe 15 is branched and connected to the first main pipe portion 11 and the second main pipe portion 12. The distribution pipe 15 divides a path through which the refrigerant flows in advance before flowing into the header main pipe 10B into a plurality of paths. The distribution pipes 15 are branched into the same number as the number into which the header main pipe 10B is divided. The distribution pipe 15 is disposed at a position distant from the heat exchange portion 30 in either the first main pipe portion 11 or the second main pipe portion 12. As shown in fig. 11, when the length b of the pipe line of the first main pipe portion 11 is longer than the length c of the pipe line of the second main pipe portion 12 and the length c of the pipe line of the second main pipe portion 12 is longer, the second main pipe portion 12 is disposed at a position farther from the heat exchanger 30 than the first main pipe portion 11. When the length b of the pipe line of the first main pipe portion 11 is longer than the length c of the pipe line of the second main pipe portion 12, the first main pipe portion 11 is disposed at a position farther from the heat exchange portion 30 than the second main pipe portion 12. The distribution pipe 15 may be formed integrally with the first main pipe portion 11 and the second main pipe portion 12 by bending the pipe, or may be formed of a pipe joining the first main pipe portion 11 and the second main pipe portion 12.

As described above, the header main pipe 10B of the heat exchanger 100B has a plurality of pipe portions having different distances from the heat exchange portion 30, and the plurality of pipe portions are arranged so that the pipe portion having the longer length of the pipe is farther from the heat exchange portion 30. Therefore, the header main pipe 10B can be regarded as a structure equivalent to a structure having a plurality of headers shorter in length than the straight pipes. As a result, the contraction amount and the expansion amount in the longitudinal direction of the header main pipe 10B can be suppressed, the bending amount of the branch pipes 20 connected to the header main pipe 10B can be suppressed, and the stress concentration on the expanded pipe portions 34 of the heat conducting pipes 33 can be relaxed.

The header main pipe 10B of the heat exchanger 100B further includes a plurality of branched distribution pipes 15, and the plurality of pipe portions are divided, and the pipe portions are connected to the distribution pipes 15. Therefore, the header main pipe 10B can be regarded as a structure equivalent to a structure having a plurality of headers shorter in length than the straight pipes. As a result, the contraction amount and the expansion amount in the longitudinal direction of the header main pipe 10B can be suppressed, the bending amount of the branch pipes 20 connected to the header main pipe 10B can be suppressed, and the stress concentration on the expanded pipe portions 34 of the heat conducting pipes 33 can be relaxed. In the heat exchanger 100B, the longer the pipe portion of the header main pipe 10B to be connected, the longer the branch pipes 20 are connected, and the longer the branch pipes 20 are provided, whereby the bending accompanying the expansion and contraction of the header main pipe 10B can be further suppressed. The header main pipe 10B of the heat exchanger 100B has 3 portions having different distances from the heat exchange unit 30. Therefore, the heat exchanger 100B can be made smaller by shortening the length of the branch pipes 20, and the space in the outdoor unit casing can be used more effectively.

Further, although the heat exchanger 100B has the distribution pipe 15 branched into 2 by dividing the header main pipe 10B into 2, the heat exchanger 100B is not limited to this configuration. For example, the heat exchanger 100B may have the header main pipe 10B divided into 3 or more and the distribution pipes 15 branched into 3 or more. That is, the heat exchanger 100B may have the header main pipe 10B divided into n or more and the distribution pipes 15 branched into n or more.

Embodiment 4.

[ refrigeration cycle device 150]

Fig. 13 is a diagram showing the configuration of a refrigeration cycle apparatus 150 according to embodiment 4 of the present invention. The outdoor heat exchanger 153 used in the refrigeration cycle apparatus 150 according to embodiment 4 is any one of the heat exchanger 100 according to embodiment 1, the heat exchanger 100A according to embodiment 2, and the heat exchanger 100B according to embodiment 3. The refrigeration cycle apparatus 150 according to embodiment 4 performs air conditioning by heating or cooling the room by transferring heat between the outside air and the air in the room via the refrigerant. The refrigeration cycle apparatus 150 according to embodiment 4 includes an outdoor unit 300 and an indoor unit 400. In the refrigeration cycle apparatus 150, the outdoor unit 300 and the indoor units 400 are connected by refrigerant piping to form a refrigerant circulation circuit in which a refrigerant circulates. In the refrigerant circulation circuit of the refrigeration cycle apparatus 150, the compressor 151, the flow switching device 152, the outdoor heat exchanger 153, the expansion valve 154, and the indoor heat exchanger 155 are connected in this order via refrigerant pipes.

(outdoor unit 300)

The outdoor unit 300 includes a compressor 151, a flow path switching device 152, and an outdoor heat exchanger 153. The compressor 151 compresses a sucked refrigerant and discharges it. Here, the compressor 151 may be provided with an inverter device, and the inverter device may be configured to change the operating frequency to change the capacity of the compressor 151. The capacity of the compressor 151 is the amount of refrigerant sent per unit time. The flow path switching device 152 is, for example, a four-way valve, and is a device for switching the direction of the refrigerant flow path. The refrigeration cycle apparatus 150 can perform a heating operation or a cooling operation by switching the flow of the refrigerant using the flow switching device 152 based on an instruction from a control device (not shown).

The outdoor heat exchanger 153 performs heat exchange between the refrigerant and outdoor air. The outdoor heat exchanger 153 functions as an evaporator during the heating operation, and exchanges heat between the low-pressure refrigerant flowing in from the refrigerant pipe and the outdoor air to evaporate and vaporize the refrigerant. The outdoor heat exchanger 153 functions as a condenser during the cooling operation, and exchanges heat between the refrigerant compressed by the compressor 151 and flowing in from the flow switching device 152 side and the outdoor air to condense and liquefy the refrigerant.

(indoor machine 400)

The indoor unit 400 includes an indoor heat exchanger 155 for exchanging heat between the refrigerant and the indoor air, and an expansion valve 154. The indoor heat exchanger 155 functions as a condenser during the heating operation, and performs heat exchange between the refrigerant flowing from the refrigerant pipe and the indoor air to condense and liquefy the refrigerant. The indoor heat exchanger 155 functions as an evaporator during the cooling operation, and exchanges heat between the refrigerant in a low-pressure state by the expansion valve 154 and the indoor air, thereby depriving the refrigerant of heat of the air and evaporating and gasifying the refrigerant. The expansion valve 154 is an expansion device (flow rate control means) that functions as an expansion valve by adjusting the flow rate of the refrigerant flowing through the expansion valve 154, and adjusts the pressure of the refrigerant by changing the opening degree. For example, when the expansion valve 154 is an electronic expansion valve or the like, the opening degree is adjusted based on an instruction from a control device (not shown) or the like. The expansion valve 154 may be provided in the outdoor unit 300.

[ operation example of refrigeration cycle device 150]

Next, the cooling operation will be described as an example of the operation of the refrigeration cycle apparatus 150. The high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 151 flows into the outdoor heat exchanger 153 via the flow switching device 152. The gas refrigerant flowing into the outdoor heat exchanger 153 condenses by heat exchange with the outside air, becomes a low-temperature refrigerant, and flows out of the outdoor heat exchanger 153. The refrigerant flowing out of the outdoor heat exchanger 153 is expanded and decompressed by the expansion valve 154, and turns into a low-temperature, low-pressure, two-phase gas-liquid refrigerant. The two-phase gas-liquid refrigerant flows into the indoor heat exchanger 155 of the indoor unit 400, evaporates through heat exchange with the indoor air, turns into a low-temperature low-pressure gas refrigerant, and flows out of the indoor heat exchanger 155. At this time, the indoor air cooled by the heat absorbed by the refrigerant becomes air-conditioning air (discharge air), and is discharged from the discharge port of the indoor unit 400 into the room (air-conditioning target space). The gas refrigerant flowing out of the indoor heat exchanger 155 is sucked into the compressor 151 via the flow switching device 152, and is compressed again. The above operation is repeated.

Next, a heating operation will be described as an example of the operation of the refrigeration cycle apparatus 150. The high-temperature and high-pressure gas refrigerant compressed and discharged by the compressor 151 flows into the indoor heat exchanger 155 of the indoor unit 400 via the flow switching device 152. The gas refrigerant flowing into the indoor heat exchanger 155 is condensed by heat exchange with the indoor air, becomes a low-temperature refrigerant, and flows out of the indoor heat exchanger 155. At this time, the indoor air heated by the heat received from the gas refrigerant becomes air-conditioned air (discharge air), and is discharged into the room (air-conditioned space) from the discharge port of the indoor unit 400. The refrigerant flowing out of the indoor heat exchanger 155 is expanded and decompressed by the expansion valve 154, and turns into a low-temperature low-pressure two-phase gas-liquid refrigerant. The two-phase gas-liquid refrigerant flows into the outdoor heat exchanger 153 of the outdoor unit 300, is evaporated by heat exchange with the outside air, becomes a low-temperature and low-pressure gas refrigerant, and flows out of the outdoor heat exchanger 153. The gas refrigerant flowing out of the outdoor heat exchanger 153 is sucked into the compressor 151 via the flow switching device 152 and compressed again. The above operation is repeated.

The refrigeration cycle apparatus 150 according to embodiment 4 includes any one of the heat exchanger 100 according to embodiment 1, the heat exchanger 100A according to embodiment 2, and the heat exchanger 100B according to embodiment 3. Therefore, the refrigeration cycle device 150 having the effects of embodiments 1 to 3 can be obtained.

Description of reference numerals:

10 … header main pipe; 10a … header main pipe; 10B … header main pipe; 11 … a first main pipe portion; 12 … second main pipe portion; 13 … crankshaft part; 13a … crankshaft portion; 13B … crankshaft portion; 14 … a third main pipe portion; 15 … dispensing tube; 20 … branch pipes; 21 … a first branch tube; 22 … second branch tube; 23 … third branch pipe; 30 … heat exchange portion; 31 … side panels; 32 … plate fins; 33 … heat conduction pipe; 34 … expanding the tube; 40 … piping; a 50 … capillary tube; a 60 … dispenser; 100 … heat exchanger; 100a … heat exchanger; 100B … heat exchanger; 150 … refrigeration cycle device; 151 … compressor; 152 … flow path switching means; 153 … outdoor heat exchanger; 154 … expansion valve; 155 … indoor heat exchanger; 200 … heat exchanger; 210 … header main piping; 300 … outdoor unit; 400 … indoor unit.

Claims (9)

1. A heat exchanger is characterized by comprising:

a heat exchange unit having a plurality of plate-shaped fins arranged in parallel with an interval therebetween and a plurality of heat transfer tubes intersecting the plurality of plate-shaped fins;

a header main pipe that supplies the refrigerant to the heat exchange portion; and

a plurality of branch pipes connected between the plurality of heat transfer pipes and the header main pipe,

the header main pipe has a plurality of pipe portions having different distances from the heat exchange portion,

the piping portions are arranged so that the piping portion having a longer tube length is farther from the heat exchange portion.

2. The heat exchanger of claim 1,

the length of the branch pipe is different according to the length of the piping part connected with the branch pipe,

the length of the branch pipe is increased in proportion to the length of the piping portion.

3. The heat exchanger of claim 1,

the plurality of pipe portions are formed linearly along the arrangement direction of the plurality of heat transfer pipes.

4. The heat exchanger of claim 1,

the plurality of piping portions are arranged along the arrangement direction of the plurality of heat transfer pipes.

5. The heat exchanger of claim 1,

the plurality of pipe portions are connected to each other by a crank portion connecting end portions of the plurality of pipe portions to each other, and the pipe lines are connected in series.

6. The heat exchanger of claim 1,

the header main pipe further has a plurality of branched distribution pipes,

the plurality of piping portions are each divided,

the plurality of piping portions are connected to the distribution pipes, respectively.

7. The heat exchanger of claim 1,

the plurality of piping sections have a first main pipe section and a second main pipe section having different lengths of pipes,

the second main pipe portion is formed longer than the first main pipe portion and is disposed farther from the heat exchange portion than the first main pipe portion,

the branch pipes connected to the second main pipe portion are longer than the branch pipes connected to the first main pipe portion.

8. The heat exchanger of claim 1,

the plurality of piping sections have a first main pipe section, a second main pipe section, and a third main pipe section having different pipe lengths,

the third main pipe portion is formed longer than the first main pipe portion and is disposed farther from the heat exchange portion than the first main pipe portion,

the second main pipe portion is formed longer than the third main pipe portion and is disposed farther from the heat exchange portion than the third main pipe portion,

the branch pipe connected to the third main pipe portion is formed longer than the branch pipe connected to the first main pipe portion,

the branch pipe connected to the second main pipe portion is formed longer than the branch pipe connected to the third main pipe portion.

9. A refrigeration cycle apparatus, characterized in that,

a heat exchanger according to claim 1.

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