WO2019186674A1

WO2019186674A1 - Heat exchanger, heat exchange module, and refrigeration cycle

Info

Publication number: WO2019186674A1
Application number: PCT/JP2018/012297
Authority: WO
Inventors: 亜由美小野寺; 崇史畠田; 司高山; 亮輔是澤
Original assignee: 東芝キヤリア株式会社
Priority date: 2018-03-27
Filing date: 2018-03-27
Publication date: 2019-10-03
Also published as: CN111699351A; JP6963098B2; JPWO2019186674A1

Abstract

The present invention provides: a heat exchanger in which a refrigerant can be more uniformly distributed to a plurality of heat exchange pipes; a heat exchange module; and an air conditioner. A heat exchanger (31) is provided with: a pair of header pipes (32), (33) arranged substantially in parallel; a plurality of flat pipes (35) which are arranged in the extension direction of the pair of header pipes (32), (33) and installed between the pair of header pipes (32), (33), and which circulate a refrigerant between the upstream-side header pipe (32) and the downstream-side header pipe (33); and an upstream-side connector (37) that delivers the refrigerant into the upstream-side header pipe (32). The upstream-side connector (37) has: a distal end opening (45) provided at the distal end thereof; and at least one lateral opening (46) provided on a side surface of the upstream-side connector (37) and facing an inner surface (32c) of the upstream-side header pipe (32). The angle θ formed between an opening direction (Z2) of the lateral opening (46) of the upstream-side connector (37) and a line segment L perpendicular to the header pipe is smaller than 45 degrees. The opening area of the lateral opening (46) is less than the opening area of the distal end opening (45).

Description

Heat exchanger, heat exchange module, and refrigeration cycle apparatus

Embodiments according to the present invention relate to a heat exchanger, a heat exchange module, and a refrigeration cycle apparatus.

A heat exchanger including a pair of header pipes and a plurality of parallel heat exchange tubes connected to both header pipes is known.

The joint that connects one header pipe and the refrigerant inflow pipe is provided by being inserted on the opposite side of the header pipe to the side to which the heat exchange tube is connected. The tip of the joint is closed. A plurality of refrigerant flow holes opened in a direction orthogonal to the refrigerant flow direction are provided at the tip of the joint.

JP 2016-183847 A

Conventional heat exchangers are provided with coolant circulation holes only in the circumferential direction of the joint inserted into the header pipe. The refrigerant circulation hole distributes the refrigerant to the plurality of heat exchange tubes.

However, in the conventional heat exchanger, the amount of refrigerant distributed to the heat exchange tube far from the joint insertion point is small, while the refrigerant distribution amount to the heat exchange tube close to the joint insertion point is large. In other words, in the conventional heat exchanger, there is still room for improvement in the uniform distribution amount of the refrigerant to the plurality of heat exchange tubes.

Therefore, the present invention proposes a heat exchanger, a heat exchange module, and a refrigeration cycle apparatus that can distribute refrigerant more evenly to a plurality of parallel heat exchange tubes.

In order to solve the above-described problems, a heat exchanger according to an embodiment of the present invention includes a pair of header pipes arranged substantially in parallel, arranged in the extending direction of the pair of header pipes, and the pair of header pipes. A plurality of heat exchange pipes installed between the one header pipe and the other header pipe, and provided on a side surface of the one header pipe. Or a joint for letting out the refrigerant from the one header pipe. The joint extends toward the heat exchange pipe and is provided at a tip opening provided at a tip of the joint; at least one side opening provided on a side surface of the joint and facing an inner wall surface of the one header pipe; have. The angle formed by the extending direction of the line passing through the center of the side opening and the line perpendicular to the header pipe with respect to the center line in the extending direction of the joint is less than 45 degrees. The opening area of the side opening is larger than the opening area of the tip opening.

In order to solve the above-described problems, a heat exchanger module according to an embodiment of the present invention includes a plurality of the heat exchangers and a relay pipe that connects the plurality of heat exchangers in series. In the refrigerant flow direction, the total opening area of the side opening and the tip opening of the heat exchanger on the downstream side is larger than the total opening area of the side opening and the tip opening of the heat exchanger on the upstream side.

Furthermore, in order to solve the above-described problems, a refrigeration cycle apparatus according to an embodiment of the present invention includes a compressor, a condenser, an expansion device, the heat exchanger, an evaporator having the module, and the compressor. , The condenser, the expansion device, and a refrigerant pipe for connecting the evaporator and circulating the refrigerant.

The refrigeration cycle figure of the air conditioner which concerns on embodiment of this invention. The top view of the heat exchanger of the air conditioner which concerns on embodiment of this invention. The partial perspective view of the heat exchanger of the air conditioner concerning the embodiment of the present invention. The partial sectional view of the heat exchanger concerning the embodiment of the present invention. The partial cross section perspective view of the heat exchanger which concerns on embodiment of this invention. The partial sectional view of the heat exchanger concerning the embodiment of the present invention. The partial sectional view of the heat exchanger concerning the embodiment of the present invention. Sectional drawing which represents typically the mode of distribution of the refrigerant | coolant in the heat exchanger which concerns on embodiment of this invention. The fragmentary sectional view in other examples of the heat exchanger concerning the embodiment of the present invention. The fragmentary sectional view in other examples of the heat exchanger concerning the embodiment of the present invention. The refrigerating cycle figure of the other example of the air conditioner which concerns on embodiment of this invention. The top view of the heat exchanger module of the air conditioner which concerns on embodiment of this invention.

Embodiments of a heat exchanger, a heat exchange module, and a refrigeration cycle apparatus according to the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the same or equivalent structure in several drawing.

FIG. 1 is a refrigeration cycle diagram of an air conditioner that is a refrigeration cycle apparatus according to an embodiment of the present invention.

As shown in FIG. 1, the air conditioner 1 according to the present embodiment includes an indoor unit 2 and an outdoor unit 3.

The indoor unit 2 generates an indoor unit housing 11, an indoor heat exchanger 12 accommodated in the indoor unit housing 11, and an air flow accommodated in the indoor unit housing 11 and passing through the indoor heat exchanger 12. And an indoor blower 13 to be operated.

The indoor blower 13 includes a fan 13a and a power source that drives the fan 13a, for example, an electric motor 13b. When the fan 13a is driven, indoor air is sucked into the indoor unit 2, passes through the indoor heat exchanger 12, and blows out from the indoor unit 2.

The outdoor unit 3 includes an outdoor unit housing 15, a compressor 16 housed in the outdoor unit housing 15, a four-way valve 17 housed in the outdoor unit housing 15, and an outdoor unit housed in the outdoor unit housing 15. A heat exchanger 18, an expansion mechanism 19 as an expansion device, and an outdoor blower 21 that is accommodated in the outdoor unit housing 15 and generates an air flow passing through the outdoor heat exchanger 18 are provided.

The throttle mechanism 19 is, for example, an electronic expansion valve (Pulse Motor Valve, PMV) or a capillary tube.

The outdoor blower 21 includes a propeller fan 21a and a power source that drives the propeller fan 21a, for example, an electric motor 21b. When the propeller fan 21 a is driven, outdoor air is sucked into the outdoor unit 3, passes through the outdoor heat exchanger 18, and blows out from the outdoor unit 3.

The air conditioner 1 also includes a refrigerant pipe 23 that connects the compressor 16, the four-way valve 17, the outdoor heat exchanger 18, the throttle mechanism 19, and the indoor heat exchanger 12 to distribute the refrigerant.

The refrigerant pipe 23 sequentially connects the compressor 16, the four-way valve 17, the outdoor heat exchanger 18, the throttle mechanism 19, and the indoor heat exchanger 12.

The refrigerant pipe 23 includes a first refrigerant pipe 23 a that connects the discharge port 16 a of the compressor 16 and the four-way valve 17, a second refrigerant pipe 23 b that connects the four-way valve 17 and the suction port 16 b of the compressor 16, and the four-way valve 17. A third refrigerant pipe 23c that connects the outdoor heat exchanger 18 and the fourth refrigerant pipe 23d that connects the outdoor heat exchanger 18 and the throttle mechanism 19, a first pipe connection portion 25a of the throttle mechanism 19 and the outdoor unit 3, and A fifth refrigerant pipe 23e that connects the first pipe connection part 25a of the outdoor unit 3 and a second pipe connection part 25b of the indoor unit 2, and a second pipe connection part 25b of the indoor unit 2. A seventh refrigerant pipe 23g connecting the indoor heat exchanger 12 and the eighth refrigerant pipe 23h connecting the indoor heat exchanger 12 and the third pipe connecting portion 25c of the indoor unit 2, and a third pipe connection of the indoor unit 2. 9th cold which connects part 25c and the 4th piping connection part 25d of outdoor unit 3 A pipe 23i, includes a tenth refrigerant pipe 23j for connecting the fourth pipe connecting portion 25d and the four-way valve 17 of the outdoor unit 3, a.

The sixth refrigerant pipe 23f and the ninth refrigerant pipe 23i allow the refrigerant to pass between the outdoor unit 3 and the indoor unit 2.

Each of the first pipe connection part 25a and the fourth pipe connection part 25d is a refrigerant pipe 23 on the outdoor unit 3 side, that is, a first refrigerant pipe 23a, a second refrigerant pipe 23b, a third refrigerant pipe 23c, and a fourth refrigerant pipe 23d. Also, it serves as a joint corresponding to the entrance and exit of the fifth refrigerant pipe 23e and the tenth refrigerant pipe 23j.

Each of the 2nd piping connection part 25b and the 3rd piping connection part 25c serves also as the coupling corresponded to the refrigerant | coolant piping 23 by the side of the indoor unit 2, ie, the 7th refrigerant | coolant piping 23g, and the 8th refrigerant | coolant piping 23h.

The air conditioner 1 also includes a control unit 27 that is electrically connected to the four-way valve 17 via a signal line (not shown).

The control unit 27 includes a central processing unit (not shown), a storage device (not shown) for storing various arithmetic programs executed by the central processing unit, parameters, and the like. The control unit 27 reads various control programs from the auxiliary storage device into the main storage device, and executes the various control programs read into the main storage device by the central processing unit.

The control unit 27 controls the four-way valve 17 based on an operation input to a remote controller (not shown), and performs a cooling operation of the air conditioner 1 (a refrigerant flow indicated by a broken line in FIG. 1) and a heating operation ( In FIG. 1, the refrigerant flow (shown by a solid line) is switched.

During the cooling operation, the air conditioner 1 discharges the high-temperature and high-pressure gas refrigerant compressed from the compressor 16 and sends this refrigerant to the outdoor heat exchanger 18 via the four-way valve 17. The outdoor heat exchanger 18 exchanges heat between the outdoor air and the refrigerant, and cools the refrigerant into a high-pressure liquid state. That is, the outdoor heat exchanger 18 functions as a condenser. The refrigerant that has passed through the outdoor heat exchanger 18 passes through the throttle mechanism 19 and is reduced in pressure to become a low-pressure liquid refrigerant and reaches the indoor heat exchanger 12. The indoor heat exchanger 12 exchanges heat between the indoor air and the liquid refrigerant, cools the air blown into the indoor space, and evaporates the refrigerant to make a transition from the gas-liquid two-phase state to the gas state. That is, the indoor heat exchanger 12 functions as an evaporator. The refrigerant that has passed through the indoor heat exchanger 12 is sucked back into the compressor 16.

On the other hand, during the heating operation, the air conditioner 1 inverts the four-way valve 17 to cause the refrigerant flow in the opposite direction to the refrigerant flow during the cooling operation in the refrigeration cycle. That is, the indoor heat exchanger 12 functions as a condenser, and the outdoor heat exchanger 18 functions as an evaporator.

In addition, the air conditioner 1 may not be provided with the four-way valve 17 and may be dedicated to cooling. In this case, the discharge port 16a of the compressor 16 is directly connected to the outdoor heat exchanger 18 via the refrigerant pipe 23, and the suction port 16b of the compressor 16 is directly connected to the indoor heat exchanger 12 via the refrigerant pipe 23. Connected. The indoor heat exchanger 12 always functions as an evaporator.

In the case of the air conditioner 1 capable of cooling and heating, the direction of the refrigerant flow in the indoor heat exchanger 12 and the outdoor heat exchanger 18 is reversed between the cooling operation and the heating operation (opposite) become). Therefore, the indoor heat exchanger 12 and the outdoor heat exchanger 18 that function as an evaporator are hereinafter simply referred to as a heat exchanger 31. Thereafter, the heat exchanger 31 functioning as an evaporator will be described unless otherwise specified.

2 and 3, the heat exchanger 31 according to this embodiment has a rectangular plate-like appearance.

The air heat-exchanged by the heat exchanger 31 circulates in the front and back direction of the paper surface in FIG. 2 and in the direction of the solid arrow FL in FIG. In other words, the air exchanged by the heat exchanger 31 flows in a direction penetrating the front and back of the plate-shaped heat exchanger 31. The direction in which the air that is heat-exchanged by the heat exchanger 31 flows is referred to as the air flow direction FL of the heat exchanger 31 or the ventilation direction FL of the heat exchanger 31.

The heat exchanger 31 is arranged in a pair of

header pipes

32 and 33 that are substantially parallel to each other and in the extending direction of the pair of header pipes 32 and 33 (in the direction indicated by the solid arrow X in FIG. 2). The flat tubes 35 as a plurality of heat exchange tubes that are installed between the upstream header pipe 32 and the downstream header pipe 33 and circulate between the upstream header pipe 32 and the downstream header pipe 33, and the adjacent flat tubes 35. A corrugated fin 36, an upstream joint 37 that allows the refrigerant to flow into the upstream header pipe 32, and a downstream joint 38 that allows the refrigerant to flow out from the downstream header pipe 33 are provided.

The heat exchanger 31 divides the refrigerant that has flowed from the upstream joint 37 into the upstream header pipe 32 into a plurality of flat tubes 35, and the refrigerant that has passed through the flat tubes 35 and has undergone heat exchange joins in the downstream header pipe 33. The refrigerant is caused to flow out from the downstream header pipe 33 to the downstream joint 38.

The distinction between the upstream side of the refrigerant flow and the downstream side of the refrigerant flow in the heat exchanger 31 is based on the refrigerant flow when the heat exchanger 31 functions as an evaporator. Accordingly, according to the refrigerant flow when the heat exchanger 31 functions as a condenser, the distinction between the upstream side of the refrigerant flow and the downstream side of the refrigerant flow in the heat exchanger 31 is reversed. Therefore, the upstream header pipe 32 is referred to as “one header pipe 32”, the downstream header pipe 33 is referred to as “the other header pipe 33”, and the upstream joint 37 is simply referred to as “joint 37”, “first joint 37”. ”Or“ one joint 37 ”, and the downstream joint 38 may be referred to as“ second joint 38 ”or“ the other joint 38 ”.

The

header pipes

32 and 33, the flat tubes 35, the corrugated fins 36, the upstream joint 37, and the downstream joint 38 are made of aluminum or an aluminum alloy. The

header pipes

32 and 33, the flat tubes 35, the corrugated fins 36, and the downstream side joints 38 are integrated by brazing. The

header pipes

32 and 33, the flat tubes 35, the corrugated fins 36, and the downstream side joints 38 may be joined by a method other than brazing.

Each of the

header pipes

32 and 33 is a straight pipe having a circular cross section (annular cross section). The upstream header pipe 32 is disposed at a portion corresponding to one side of the four sides of the heat exchanger 31. The downstream header pipe 33 is disposed at a portion corresponding to the side facing the side where the upstream header pipe 32 is disposed, among the four sides of the heat exchanger 31. End caps 39 made of aluminum or aluminum alloy are provided at the

end portions

32a, 32b, 33a, 33b of the

header pipes

32, 33, respectively. The end cap 39 closes each end of the

header pipes

32 and 33. Each end cap 39 is brazed to the

header pipes

32 and 33.

The heat exchanger 31 includes the second end 32b of the upstream header pipe 32 and the second end 33b of the downstream header pipe 33 as the first end 32a of the upstream header pipe 32 and the downstream header pipe. It is preferable that the first end portion 33a of 33 is disposed above the first end portion 33a.

The plurality of flat tubes 35 are straight tubes having a flat rounded rectangular cross-sectional shape. The plurality of flat tubes 35 are arranged at substantially equal intervals in the extending direction X of the

header pipes

32 and 33. The plurality of flat tubes 35 are substantially orthogonal to the

header pipes

32 and 33. Each end of the plurality of flat tubes 35 is inserted into the

header pipes

32 and 33 and fixed.

Each flat tube 35 has a flat rounded rectangular cross section extending in the air flow direction FL of the heat exchanger 31. The short side in the cross-sectional shape of the flat tube 35 extends in the direction in which the flat tubes 35 are arranged, that is, in the extending direction X of the

header pipes

32 and 33. The long side in the cross-sectional shape of the flat tube 35 extends in a direction penetrating the front and back of the heat exchanger 31. A pair of adjacent flat tubes 35 faces a wide surface corresponding to the long side in the cross-sectional shape.

Each flat tube 35 has a plurality of refrigerant flow passages 35a arranged in a direction penetrating the front and back of the heat exchanger 31, that is, in an air flow direction FL of the heat exchanger 31. The plurality of refrigerant flow passages 35a extend substantially in parallel. The flat tube 35 is generally manufactured by extrusion molding of aluminum.

Each corrugated fin 36 is a thin aluminum plate having alternating folds and valleys. Each corrugated fin 36 is a thin plate that moves back and forth in a continuous V-shape with a separation distance between a pair of adjacent flat tubes 35. Each corrugated fin 36 is sandwiched between adjacent flat tubes 35. That is, each fold line of each corrugated fin 36 is in contact with the wide surface of the flat tube 35.

Further, the heat exchanger 31 includes a pair of side plates 41. The pair of side plates 41 are made of aluminum or aluminum alloy. The pair of side plates 41 is arranged at a portion corresponding to two opposing sides, which is different from the sides of the four sides of the heat exchanger 31 that the pair of

header pipes

32 and 33 bear. That is, the heat exchanger 31 has a rectangular plate shape drawn by a pair of

opposed header pipes

32 and 33 and a pair of opposed side plates 41. Each side plate 41 is brazed to a corrugated fin 36 disposed on the outer edge of the heat exchanger 31.

The upstream joint 37 is a straight pipe having a circular cross section (annular cross section). The upstream joint 37 is connected to the side surface of the upstream header pipe 32 from the opposite side of the flat tube 35. That is, the upstream side joint 37 is connected to the upstream side header pipe 32 from the opposite side of the side where the flat tube 35 is disposed. The upstream side joint 37 is connected to the refrigerant pipe 23 of the air conditioner 1.

The downstream joint 38 is a straight pipe having a circular cross section (annular cross section). The downstream side joint 38 is connected to the downstream side header pipe 33 from the opposite side of the flat tube 35. In other words, the downstream joint 38 is connected to the downstream header pipe 33 from the opposite side of the side where the flat tube 35 is disposed. The downstream joint 38 is connected to the refrigerant pipe 23 of the air conditioner 1. The inner diameter dimension of the downstream side joint 38 is equal to or larger than the inner diameter dimension of the upstream side joint 37.

The upstream joint 37 is connected in the vicinity of the first end 32 a of the upstream header pipe 32, and the downstream joint 38 is connected in the vicinity of the second end 33 b of the downstream header pipe 33. That is, the upstream side joint 37 and the downstream side joint 38 are arranged in the vicinity of two diagonal corners of the four corners of the rectangular heat exchanger 31. In other words, the flat tube 35 close to the upstream side joint 37 is far from the downstream side joint 38, and the flat tube 35 far from the upstream side joint 37 is close to the downstream side joint 38.

The upstream side joint 37 is connected to the upstream header pipe 32 toward a region between the side plate 41 and the flat tube 35 or a region between a pair of adjacent flat tubes 35, that is, a region where the corrugated fins 36 are disposed. Is plugged into. The upstream joint 37 may be inserted into the upstream header pipe 32 toward the side plate 41 or the flat tube 35. Further, the heat exchanger 31 may include a plurality of upstream side joints 37 as indicated by a two-dot chain line in FIG. The plurality of upstream joints 37 may be provided in a region between the side plate 41 and the flat tube 35 and a region between a pair of adjacent flat tubes 35. The plurality of upstream joints 37 easily and uniformly distribute the refrigerant to the flat tubes 35.

The downstream side joint 38 is located downstream of the header pipe 33 toward a region between the side plate 41 and the flat tube 35 or a region between a pair of adjacent flat tubes 35, that is, a region where the corrugated fins 36 are disposed. Is plugged into. The downstream joint 38 may be inserted into the downstream header pipe 33 toward the side plate 41 or the flat tube 35.

FIG. 4 is a cross-sectional view orthogonal to the center line of the upstream header pipe 32 and passing through the center line of the upstream joint 37.

As shown in FIGS. 4 and 5, the upstream joint 37 of the heat exchanger 31 according to the present embodiment extends toward the flat tube 35 when viewed from the X direction that is the extending direction of the upstream header pipe 32. ing. The outer diameter and inner diameter of the upstream joint 37 are smaller than the width of the flat tube 35. The tip of the upstream joint 37 is a protruding end that protrudes inside the upstream header pipe 32. A gap G is provided between the flat tube 35 and the upstream joint 37 when viewed from the extending direction of the upstream header pipe 32.

The upstream joint 37 is provided at the distal end of the upstream joint 37 and faces the extending direction Y of the upstream joint 37, and the inner wall surface of the upstream header pipe 32 provided on the side surface of the upstream joint 37. And a side opening 46 facing 32c. One or more side openings 46 may be provided.

The tip opening 45 and the side opening 46 allow the refrigerant to flow into the upstream header pipe 32 when the heat exchanger 31 functions as an evaporator (solid arrow f in FIG. 4). In other words, the refrigerant flowing in the upstream joint 37 is divided into the tip opening 45 and the side opening 46 and flows into the upstream header pipe 32.

The tip opening 45 causes the refrigerant flowing in the upstream side joint 37 to travel substantially straight. The opening diameter of the tip opening 45 is smaller than the inner diameter of the upstream side joint 37. In other words, the tip opening 45 restricts the refrigerant flowing out from the upstream side joint 37. The tip opening 45 may be, for example, a hole (so-called orifice) that is made in a plate that closes the tip of the upstream joint 37, or a hole that is made in a cap that closes the tip of the upstream joint 37. good. Further, the tip opening 45 may be an open end of the upstream side joint 37 whose diameter is reduced by plastic deformation by a processing method such as drawing. The center of the tip opening 45 is preferably coincident with the center line of the upstream joint 37.

The side opening 46 is provided on the side surface of the portion disposed in the upstream header pipe 32 of the upstream joint 37. The side opening 46 faces the direction orthogonal to the flow direction of the refrigerant in the upstream joint 37. An extension line of a line passing through the center of the side opening 46 reaches the inner wall surface 32 c of the upstream header pipe 32. The side opening 46 changes the traveling direction of the refrigerant flowing in the upstream joint 37 and causes the refrigerant to flow substantially outward in the radial direction of the upstream joint 37.

The opening area of the side opening 46 is larger than the opening area of the tip opening 45. The opening shape of the side opening 46 and the opening shape of the tip opening 45 are circular, but may be non-circular such as a triangle or a quadrangle. The side opening 46 and the tip opening 45 are holes having a uniform diameter, but may be conical holes. The non-circular hole has a refrigerant spray effect, promotes mixing of the liquid refrigerant and the gas refrigerant, and equalizes the distribution amount of the refrigerant supplied to the plurality of flat tubes. The conical hole increases the flow rate of the refrigerant to promote the mixing of the liquid refrigerant and the gas refrigerant, and equalizes the distribution amount of the refrigerant supplied to the plurality of flat tubes.

FIG. 6 is a cross-sectional view passing through the center line of the upstream header pipe 32 and the center line of the upstream joint 37.

As shown in FIG. 6, the extending directions of the flat tube 35, the side plate 41, and the upstream side joint 37 of the heat exchanger 31 according to the present embodiment are substantially parallel.

The outer diameter and inner diameter of the upstream joint 37 are larger than the height of the flat tube 35.

The upstream joint 37 extends toward the inner wall surface 32 c of the upstream header pipe 32 between the side plate 41 and the flat tube 35 or between a pair of adjacent flat tubes 35. Therefore, the tip opening 45 faces the inner wall surface 32 c of the upstream header pipe 32 between the side plate 41 and the flat tube 35 or between a pair of adjacent flat tubes 35. The upstream side joint 37 preferably extends toward an intermediate position between the side plate 41 and the flat tube 35 or between a pair of adjacent flat tubes 35. Therefore, it is preferable that the tip opening 45 faces an intermediate position between the side plate 41 and the flat tube 35 or between a pair of adjacent flat tubes 35. In other words, it is preferable that the separation distance between the upstream joint 37 and the side plate 41 and the separation distance between the upstream joint 37 and the flat tube 35 are substantially equal. That is, it is preferable that the separation distance between the tip opening 45 and the side plate 41 and the separation distance between the tip opening 45 and the flat tube 35 are substantially equal.

Note that the upstream joint 37 may extend toward the side plate 41 or the flat tube 35. Therefore, the tip opening 45 may face the side plate 41 or the flat tube 35. In this case, the upstream joint 37 is disposed on the extension line in the extending direction of the side plate 41 or the flat tube 35.

FIG. 7 is a cross-sectional view taken along line VII-VII in FIG.

7, the side opening 46 of the heat exchanger 31 according to the present embodiment allows the refrigerant in the upstream joint 37 to flow out in a direction perpendicular to the center line of the upstream header pipe 32, for example. The side openings 46 are provided substantially symmetrically with respect to the center line of the upstream header pipe 32.

The center line Z1 in the extending direction of the upstream side joint 37 and the extending direction Z2 of the line segment passing through the center of the side opening 46 (that is, the opening direction Z2 of the side opening 46) are the center of the upstream header pipe 32. Although it is preferable to correspond to the direction orthogonal to the line H, it is not limited to this. The opening direction Z 2 of the side surface opening 46 may be inclined within a range smaller than ± 45 degrees with respect to the line segment L orthogonal to the center line H of the upstream header pipe 32. Therefore, the angle θ formed by the opening direction Z2 of the side opening 46 and the line segment L orthogonal to the center line H of the upstream header pipe 32 with respect to the center line Z1 in the extending direction of the upstream joint 37 is 45 degrees. A smaller range is sufficient. FIG. 7 shows a case where the angle θ is 0 degree.

In addition, the opening direction Z2 of the side surface opening 46 passes through the center line Z1 of the upstream side joint 37 and is perpendicular to the center line H of the upstream side header pipe 32. Two ends 32b, that is, the case facing toward the end far from the upstream side joint 37 is positive, and the first end 32a of the upstream header pipe 32, ie, the end closer to the upstream side joint 37 is directed toward. If it is negative. The opening direction of the side opening 46 is preferably directed in the positive direction.

As shown in FIG. 7, when the upstream joint 37 has a plurality of side openings 46, the plurality of side openings 46 are arranged in a range of an angle θ <45 degrees.

Furthermore, the upstream joint 37 may have a second side opening having an opening area smaller than that of the side opening 46. In the second side surface opening, the angle θ may be smaller than 45 degrees, or the angle θ may be larger than 45 degrees.

FIG. 8 is a cross-sectional view schematically representing the state of refrigerant distribution in the heat exchanger according to the embodiment of the present invention.

8 has eight flat tubes 35. The heat exchanger 31 shown in FIG. The eight flat tubes 35 are connected to the first-stage flat tube 35a, the second-stage flat tube 35b, the third-stage flat tube 35c, the fourth-stage flat tube 35d, and the fifth-stage from the side closer to the upstream side joint 37. These are called a flat tube 35e, a sixth flat tube 35f, a seventh flat tube 35g, and an eighth flat tube 35h. Further, the heat exchanger 31 shown in FIG. 8 includes an upstream joint 37 that is inserted into the upstream header pipe 32 toward the space between the first-stage flat tube 35a and the second-stage flat tube 35b.

And the front-end opening 45 of the upstream side joint 37 distribute | circulates a refrigerant | coolant toward the inner wall surface 32c of the upstream header pipe 32 between the 1st stage flat tube 35a and the 2nd stage flat tube 35b (FIG. Medium, solid arrow F1). On the other hand, the side opening 46 of the upstream joint 37 allows the refrigerant to flow in a direction perpendicular to the center line of the upstream header pipe 32. The refrigerant that has flowed out of the tip opening 45 and the side opening 46 and collided with the inner wall surface 32c of the upstream header pipe 32 is in a state where the gas component and the liquid component are mixed, and is directed in the direction of the center line of the upstream header pipe 32 (Solid arrow F2 in the figure).

Incidentally, the liquid refrigerant having a large mass falls below the upstream header pipe 32 (first end portion 32a) due to the influence of gravity. Further, when the side opening 46 faces the range of the angle θ ≧ 45 degrees, the separation distance from the side opening 46 to the inner wall surface 32c of the upstream header pipe 32 is longer than the range of the angle θ <45 degrees. The amount of refrigerant distributed to the flat tubes 35 (for example, the fifth flat tube 35e to the eighth flat tube 35h) decreases.

However, the heat exchanger 31 according to the present embodiment causes the refrigerant flowing into the upstream header pipe 32 from the tip opening 45 and the side opening 46 to collide with the inner wall surface 32c of the upstream header pipe 32 at an early stage, thereby causing liquid refrigerant and gas Mixing with the refrigerant is promoted, and a larger amount of the refrigerant reaches the upper flat tube 35 by the surface tension at the inner wall surface 32c of the upstream header pipe 32 to increase the distribution amount of the refrigerant. In FIG. 8, the state of distribution of the refrigerant distributed to the eight flat tubes 35 is expressed by a difference in length of solid arrows extending from the flat tubes 35. This solid line arrow is an example of refrigerant distribution in the heat exchanger 31 including the upstream joint 37 having one side opening 46 facing the upwind direction of the heat exchanger 31 and one tip opening 45. Is shown. The broken-line arrows extending from the respective flat tubes 35 are refrigerants in a conventional heat exchanger having only one side opening 46 facing the upwind direction of the heat exchanger 31 and having an upstream joint without the tip opening 45. This is a comparative example.

Further, the heat exchanger 31 according to the present embodiment causes the refrigerant flowing into the upstream header pipe 32 from the front end opening 45 to collide with the inner wall surface 32c of the upstream header pipe 32 at an early stage, so that the flatness in the vicinity of the upstream joint 37 is obtained. It is possible to prevent the refrigerant from staying on the upper surface of the pipe 35 or the side plate 41 (portion in the upstream header pipe 32). Since the retention of the refrigerant reduces the distribution amount of the refrigerant to the flat tube 35, the prevention of the retention improves the distribution amount of the refrigerant to the flat tube 35.

Next, another example of the heat exchanger 31 according to this embodiment will be described. In addition, in

heat exchanger

31A and 31B demonstrated in each example, the same code | symbol is attached | subjected to the same structure as the heat exchanger 31 shown in FIGS. 1-8, and the overlapping description is abbreviate | omitted.

FIG. 9 is a partial cross-sectional view of another example of the heat exchanger according to the embodiment of the present invention. FIG. 9 is a cross-sectional view orthogonal to the center line of the upstream header pipe 32 and passing through the center line of the upstream joint 37.

As shown in FIG. 9, only one side opening 46 A of the heat exchanger 31 A according to the present embodiment is provided, and the upstream header pipe 32 is viewed from the X direction that is the extending direction of the upstream header pipe 32. The refrigerant is caused to flow out into one region A.

One region A is preferably the windward side in the air flow direction FL of the heat exchanger 31 (upstream side, the start end side of the solid line arrow FL).

FIG. 10 is a partial cross-sectional view of another example of the heat exchanger according to the embodiment of the present invention. FIG. 10 is a cross-sectional view orthogonal to the center line of the upstream header pipe 32 and passing through the center line of the upstream joint 37.

As shown in FIG. 10, the heat exchanger 31 B according to this embodiment includes protrusions 49 provided on the inner wall surface 32 c of the upstream header pipe 32 and projecting toward the side opening 46 and the tip opening 45. ing.

The protrusion 49 may be formed by plastically deforming the upstream header pipe 32, or may be a part in which another part is fixed to the upstream header pipe 32. The protrusion 49 is provided in front of the side opening 46, that is, at the intersection of the line segment connecting the center of the upstream joint 37 and the center of the side opening 46 and the inner wall surface 32 c of the upstream header pipe 32. Further, the protrusion 49 is provided in front of the tip opening 45, that is, at the intersection of the center line of the upstream joint 37 and the inner wall surface 32 c of the upstream header pipe 32.

The protrusion 49 preferably has a chevron-shaped curved surface so that the gas phase and the liquid phase of the refrigerant that flows out of the tip opening 45 or the side opening 46 and collides with the protrusion 49 can be efficiently mixed.

The protrusion 49 arranged on the extension line of the tip opening 45 of the upstream joint 37 is a flow of refrigerant (liquid refrigerant, gas refrigerant) from the tip opening 45 toward the inner wall surface 32c of the upstream header pipe 32 (solid arrow F1). Stir. The protrusion 49 disposed on the extension line of the side opening 46 agitates the flow of refrigerant (liquid refrigerant, gas refrigerant) from the side opening 46 toward the inner wall surface 32c of the upstream header pipe 32 (solid arrow F1). The stirred refrigerant is uniformly distributed by the respective flat tubes 35.

In the heat exchanger 31 according to each of the above embodiments, the upstream joint 37 extends toward the flat tube 35 when viewed from the X direction that is the extending direction of the upstream header pipe 32. However, the present invention is not limited to this. For example, the upstream joint 37 may extend in a direction orthogonal to the flat tube 35 as viewed from the X direction, which is the extending direction of the upstream header pipe 32, or may face in any direction.

Further, the heat exchanger 31 is not limited to the corrugated fins 36 and may include plate-like fins.

Next, another example of the air conditioner 1 according to this embodiment will be described. In the air conditioner 1A described in each example, the same components as those of the

heat exchangers

31, 31A, and 31B illustrated in FIGS. 1 to 9 are denoted by the same reference numerals, and redundant description is omitted.

FIG. 11 is a refrigeration cycle diagram of another example of the air conditioner according to the embodiment of the present invention.

As shown in FIG. 11, the air conditioner 1 A according to the present embodiment includes a heat exchanger module 51 instead of the indoor heat exchanger 12 functioning as an evaporator or the heat exchanger 31 as an outdoor heat exchanger 18. ing.

FIG. 12 is a plan view of the heat exchanger module of the air conditioner according to the embodiment of the present invention.

As shown in FIGS. 11 and 12, a heat exchanger module 51 according to this embodiment includes a plurality of, for example, two heat exchangers 31a and 31b connected in series and a plurality of heat exchangers 31a and 31b in series. And at least one relay pipe 53 connected to the.

The heat exchanger module 51 may include three or more heat exchangers 31 connected in series. In this case, the relay pipe 53 is provided for each pair of adjacent heat exchangers 31.

The relay pipe 53 may be an extension of the downstream joint 38 of the upstream heat exchanger 31a, or may be an extension of the upstream joint 37 of the downstream heat exchanger 31b.

The upstream heat exchanger 31a when the heat exchanger module 51 functions as an evaporator diverts the refrigerant that has flowed from the upstream joint 37 into the upstream header pipe 32 into a plurality of flat tubes 35. The refrigerant that has passed and exchanged heat is merged in the downstream header pipe 33, and the refrigerant flows out from the downstream header pipe 33 to the downstream joint 38. Next, the heat exchanger module 51 causes the refrigerant to flow from the downstream joint 38 of the upstream heat exchanger 31a through the relay pipe 53 to the upstream joint 37 of the downstream heat exchanger 31b. The heat exchanger 31b on the downstream side of the heat exchanger module 51 diverts the refrigerant that has flowed from the upstream joint 37 into the upstream header pipe 32 into a plurality of flat tubes 35, and passes through the flat tubes 35 to exchange heat. The resulting refrigerant is merged in the downstream header pipe 33, and the refrigerant flows out from the downstream header pipe 33 to the downstream joint 38.

In the refrigerant flow direction (the direction of the solid arrow in FIG. 12), the total opening area of the side opening 46 and the tip opening 45 of the downstream heat exchanger 31b is equal to the side opening 46 of the upstream heat exchanger 31a. It is larger than the total opening area of the tip opening 45. The upstream joint 37 of the downstream heat exchanger 31b may have the same configuration as the upstream joint 37 of the upstream heat exchanger 31a, but either the side opening 46 or the tip opening 45 may be used. Only one of them may be provided, and the opening direction of the side opening 46 may be an arbitrary direction. However, even in that case, the total area of the openings is desirably larger than the total opening area of the side opening 46 and the tip opening 45 of the upstream heat exchanger 31a.

In the refrigerant flow direction, the inner diameter dimension of the upstream joint 37 of the downstream heat exchanger 31b is larger than the inner diameter dimension of the upstream joint 37 of the upstream heat exchanger 31a.

Note that, for each heat exchanger 31 (heat exchangers 31 a and 31 b), the inner diameter dimension of the downstream side joint 38 is equal to or larger than the inner diameter dimension of the upstream side joint 37 provided in the same heat exchanger 31.

The

heat exchangers

31 and 31A, the heat exchanger module 51, and the air conditioners 1 and 1A according to the present embodiment configured as described above are provided at the distal end of the upstream joint 37 and are extended from the upstream joint 37. A front end opening 45 facing the existing direction Y, and at least one side opening 46 provided on a side surface of the upstream side joint 37 and facing the inner wall surface 32c of the upstream side header pipe 32, and the opening direction Z2 of the side opening 46 And the line segment L perpendicular to the center line H of the upstream header pipe 32 is smaller than 45 degrees, and the opening area of the side opening 46 is larger than the opening area of the tip opening 45. Therefore, the

heat exchangers

31 and 31A, the heat exchanger module 51, and the air conditioners 1 and 1A collide and disperse the main flow of the refrigerant with the inner wall surface 32c of the upstream header pipe 32 by the side opening 46, Phase separation between the liquid refrigerant and the gas refrigerant in the upstream header pipe 32 can be suppressed, and the distribution amount of the refrigerant supplied to the flat tube 35 can be made uniform. Further, the

heat exchangers

31 and 31A, the heat exchanger module 51, and the air conditioners 1 and 1A prevent liquid refrigerant from staying on the flat tube 35 near the upstream joint 37 by the refrigerant flowing out from the tip opening 45, Phase separation between the liquid refrigerant and the gas refrigerant in the upstream header pipe 32 can be suppressed, and the distribution amount of the refrigerant supplied to the flat tube 35 can be made uniform.

Moreover, the

heat exchangers

31 and 31A, the heat exchanger module 51, and the air conditioners 1 and 1A according to the present embodiment have the inner wall surface 32c of the upstream header pipe 32 between a pair of adjacent flat tubes 35. A front end opening 45 is provided. Therefore, the

heat exchangers

31 and 31A, the heat exchanger module 51, and the air conditioners 1 and 1A more reliably retain the liquid refrigerant on the flat tube 35 near the upstream joint 37 by the refrigerant flowing out from the tip opening 45. Therefore, the phase separation between the liquid refrigerant and the gas refrigerant in the upstream header pipe 32 can be suppressed, and the distribution amount of the refrigerant supplied to the flat tube 35 can be made uniform.

Furthermore, the

heat exchangers

31 and 31A, the heat exchanger module 51, and the air conditioners 1 and 1A according to the present embodiment have a plurality of side openings 46. Therefore, the

heat exchangers

31 and 31A, the heat exchanger module 51, and the air conditioners 1 and 1A reduce pressure loss in the refrigerant flow path, and effectively supply the refrigerant to the inner wall surface 32c of the upstream header pipe 32. The refrigerant is dispersed by colliding, and the distribution amount of the refrigerant supplied to the flat tube 35 can be made more uniform.

Further, the heat exchanger 31 A, the heat exchanger module 51, and the

air conditioners

1, 1 A according to the present embodiment have side openings 46 that allow the refrigerant to flow out to the upstream side area A of the upstream header pipe 32. Yes. In other words, the heat exchanger 31A, the heat exchanger module 51, and the air conditioners 1 and 1A cause the refrigerant to collide with the inner wall surface 32c of the upstream-side header pipe 32 on the windward side where the heat source temperature difference is large. Therefore, the heat exchanger 31A, the heat exchanger module 51, and the air conditioners 1 and 1A positively flow the refrigerant into the refrigerant flow passage 35a that is located on the windward side of the flat tube 35 and has a large amount of heat transfer work. The amount of heat exchange of the refrigerant can be increased.

Furthermore, the heat exchanger 31B, the heat exchanger module 51, and the air conditioners 1 and 1A according to the present embodiment are provided on the inner wall surface 32c of the upstream header pipe 32 to the side opening 46 and the tip opening 45, respectively. A projection 49 is provided that protrudes toward the surface. Therefore, the heat exchanger 31B, the heat exchanger module 51, and the air conditioners 1 and 1A further promote the stirring of the liquid refrigerant and the gas refrigerant that collide with the inner wall surface 32c of the upstream header pipe 32, and the flat tube 35 The distribution amount of the refrigerant supplied to can be made even more uniform.

In the heat exchanger module 51 and the air conditioner 1A according to the present embodiment, the total opening area of the upstream joint 37 of the downstream heat exchanger 31b is equal to the upstream joint 37 of the upstream heat exchanger 31a. It is larger than the total opening area of the side opening 46 and the tip opening 45. Therefore, the heat exchanger module 51 and the air conditioner 1A according to the present embodiment suppress an excessive increase in pressure loss in each of the heat exchangers 31a and 31b, and are flat tubes formed by the side opening 46 and the tip opening 45. The refrigerant flow to 35 can be made uniform.

Furthermore, in the heat exchanger module 51 and the air conditioner 1A according to the present embodiment, the inner diameter dimension of the downstream side joint 38 is equal to or larger than the inner diameter dimension of the upstream side joint 37 provided in the same heat exchanger 31. The inner diameter dimension of the upstream joint 37 of the heat exchanger 31b is larger than the inner diameter dimension of the upstream joint 37 of the upstream heat exchanger 31a. Therefore, an excessive increase in pressure loss in each of the heat exchangers 31a and 31b can be suppressed, and the refrigerant flow to the flat tube 35 by the side opening 46 and the tip opening 45 can be made more uniform.

Therefore, according to the

heat exchangers

31, 31 A, 31 B, the heat exchanger module 51, and the

air conditioners

1, 1 A according to this embodiment, the refrigerant can be more evenly distributed to the plurality of parallel flat tubes 35. is there.

Although several embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

DESCRIPTION OF SYMBOLS 1, 1A ... Air conditioner, 2 ... Indoor unit, 3 ... Outdoor unit, 11 ... Indoor unit housing, 12 ... Indoor heat exchanger, 13 ... Indoor fan, 13a ... Fan, 13b ... Electric motor, 15 ... Outdoor unit housing Body, 16 ... compressor, 16a ... discharge port, 16b ... suction port, 17 ... four-way valve, 18 ... outdoor heat exchanger, 19 ... throttle mechanism, 21 ... outdoor blower, 21a ... propeller fan, 21b ... electric motor, 23 ... Refrigerant piping, 23a ... first refrigerant piping, 23b ... second refrigerant piping, 23c ... third refrigerant piping, 23d ... fourth refrigerant piping, 23e ... fifth refrigerant piping, 23f ... sixth refrigerant piping, 23g ... seventh refrigerant Pipe, 23h ... eighth refrigerant pipe, 23i ... ninth refrigerant pipe, 23j ... tenth refrigerant pipe, 25a ... first pipe connection part, 25b ... second pipe connection part, 25c ... third pipe connection part, 25d ... Four pipe connection parts, 27 ... control part, 31 and 31A 31B ... Heat exchanger, 31a ... Upstream heat exchanger, 31b ... Downstream heat exchanger, 32 ... Upstream header pipe, 32a ... First end, 32b ... Second end, 32c ... Inner wall surface, 33 ... downstream header pipe, 33a ... first end, 33b ... second end, 35 ... flat tube, 35a ... refrigerant flow passage, 36 ... corrugated fin, 37 ... upstream joint, 38 ... downstream joint, 39 ... End cap, 41 ... Side plate, 45 ... Tip opening, 46, 46A ... Side opening, 48 ... Second side opening, 49 ... Projection, 51 ... Heat exchanger module, 53 ... Relay piping.

Claims

A pair of header pipes arranged substantially in parallel;
A plurality of heat exchange tubes that are arranged in the extending direction of the pair of header pipes and are laid between the pair of header pipes to allow refrigerant to flow between the one header pipe and the other header pipe;
Provided on a side surface of the one header pipe, and includes a joint that allows the refrigerant to flow into the one header pipe, or allows the refrigerant to flow out of the one header pipe,
The joint has a tip opening provided at a tip, and at least one side opening provided on a side surface of the joint and facing an inner wall surface of the one header pipe,
The angle formed by the extending direction of the line passing through the center of the side opening and the line perpendicular to the header pipe with respect to the center line in the extending direction of the joint is less than 45 degrees,
The heat exchanger has an opening area of the side opening larger than an opening area of the tip opening.
The joint extends toward the heat exchange pipe, and when viewed from the extending direction of the header pipe, a gap is provided between the heat exchange pipe and the joint.
The heat exchanger according to claim 1, wherein the tip opening faces an inner wall surface of the one header pipe between a pair of adjacent heat exchange tubes.
The heat exchanger according to claim 1, wherein the joint has a plurality of the side openings.
4. The heat exchanger according to claim 1, wherein only one side opening is provided, and the refrigerant flows out to a region on the windward side of the header pipe when viewed from the extending direction of the header pipe. .
The heat exchanger according to any one of claims 1 to 4, further comprising a protrusion provided on an inner wall surface of the one header pipe and projecting toward each of the side opening and the tip opening.
A plurality of heat exchangers according to any one of claims 1 to 5;
A relay pipe connecting the plurality of heat exchangers in series,
In the flow direction of the refrigerant, the total opening area of the side opening and the tip opening of the heat exchanger on the downstream side is larger than the total opening area of the side opening and the tip opening of the upstream heat exchanger. Exchanger module.
The heat exchanger includes a second joint that allows the refrigerant to flow into the other header pipe, or allows the refrigerant to flow out from the other header pipe,
The inner diameter dimension of the second joint is not less than the inner diameter dimension of the joint provided in the same heat exchanger,
The heat exchanger module according to claim 7, wherein an inner diameter dimension of the joint of the heat exchanger on the downstream side is larger than an inner diameter dimension of the joint of the heat exchanger on the upstream side in the flow direction of the refrigerant.
A compressor,
A condenser,
An expansion device;
An evaporator having the heat exchanger according to any one of claims 1 to 5, or the heat exchanger module according to any one of claims 6 to 7,
A refrigeration cycle apparatus comprising: the compressor, the condenser, the expansion device, and a refrigerant pipe that connects the evaporator and distributes the refrigerant.