JP2006336909A - Condenser, and indoor unit for air conditioner using it - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a performance enhanced and compactified condenser, and an indoor unit for an air conditioner using it by combining a supercooling part with a novel structure with a condensing liquefaction part using a high performance type heat exchanger with corrugated fins intervened between flat tubes. <P>SOLUTION: The condenser is composed of the condensing liquefaction parts 34 and 35, and the supercooling parts 36 and 37. The condensing liquefaction parts 34 and 35 are structured such that the corrugated fins 39 are intervened between the flat tubes 38. The supercooling parts 36 and 37 are heat exchangers with fins provided with fins 52 around heat exchange tubes 51, and they are separately arranged on the windward side of the condensing liquefaction parts 34 and 35. In the indoor unit using the condenser, a centrifugal fan 2 is used as an indoor fan, and it is arranged such that a rotary shaft is in a fore and aft direction. The supercooling parts 36 and 37, the condensing liquefaction parts 34 and 35, and an indoor blowout opening 13 are arranged in a blowout side of the centrifugal fan 2. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a condenser used for an air conditioner or the like and an indoor unit for an air conditioner using the same, and in particular, a heat exchanger part for condensing and liquefying refrigerant and a heat exchanger part for supercooling liquid refrigerant. And an indoor unit for an air conditioner using such a condenser.

  Conventionally, in a refrigeration cycle apparatus such as an air conditioner, in order to improve the efficiency of the condenser and improve the performance of the refrigeration cycle apparatus, a heat exchanger of a type in which corrugated fins are interposed between flat tubes has been adopted. ing. In addition to such a change in the type of heat exchanger, it has been conventionally considered to efficiently increase the degree of supercooling in the condenser.

  There exists a thing of patent document 1 as a prior art example of the condenser which made such supercooling degree large efficiently. In the condenser described in Patent Document 1, the heat exchanger portion of the liquid refrigerant portion flowing out from the condenser of the heat exchanger acting as a condenser is separated from the other heat exchanger portions and positioned on the windward side. It was. The “heat exchanger portion of the liquid refrigerant portion flowing out from the condenser of the heat exchanger acting as a condenser” in Patent Document 1 is mainly intended for supercooling of the liquid refrigerant. In the document, such a heat exchanger part for the purpose of supercooling is referred to as a “supercooling part”. The “other part” in Patent Document 1 is mainly intended to condense and liquefy the high-pressure gas refrigerant. In the present specification, heat for condensing and liquefying such a high-pressure gas refrigerant. The exchanger part is referred to as a “condensation liquefaction part”.

Another conventional example of a condenser in which the degree of supercooling is efficiently increased is described in Patent Document 2. In order to improve the heat exchange efficiency of the supercooling section, the condenser described in Patent Document 2 is provided with a supercooling section (referred to as a rear heat exchanger in Patent Document 2) and a condensing liquefaction section (Patent Document 2). Is called an auxiliary heat exchanger) and is thermally shut off. Furthermore, in the thing of patent document 2, while the supercooling part is arrange | positioned in the windward side of a condensing liquefaction part, the refrigerant | coolant passage area of a supercooling part is formed smaller than the refrigerant | coolant passage area of a condensing liquefaction part.
JP-A-1-302079 JP-A-8-313049, paragraph numbers 0082 to 0086

  However, in the condensers described in Patent Documents 1 and 2, both the condensate liquefaction unit and the supercooling unit are cross fin coil heat exchangers, and the air inflow surfaces of both planes have a narrow interval. And has a structure arranged so as to face each other. That is, the ones described in Patent Documents 1 and 2 are a combination of a supercooling section and a condensing liquefaction section in a specific relationship, and use a heat exchanger other than the cross fin coil type. It was not supposed to be. Moreover, when using the condenser of patent document 1 and 2, the substantially rectangular box-shaped space for accommodating the thing which combined the above-mentioned supercooling part and a condensate liquefaction part is required, and an air distribution direction The dimensions of were larger. As described above, the condensers described in Patent Documents 1 and 2 have a problem that the size in the air circulation direction is large. As a condenser or an air conditioner using this condenser, high performance and compactness are achieved. However, there was still a need for improvement.

  The present invention was made paying attention to such problems existing in the prior art, and for the condensing liquefaction section using a high-performance heat exchanger in which corrugated fins are interposed between flat tubes, An object of the present invention is to provide a condenser with high performance and compactness by combining a supercooling section having a novel structure. It is another object of the present invention to provide an air conditioner indoor unit that is improved in performance and size by using a condenser formed in this manner.

  The condenser according to the present invention includes a condensing and liquefying unit for condensing and liquefying the high-pressure gas refrigerant, and a supercooling unit for supercooling the liquid refrigerant liquefied by the condensing and liquefying unit. The tubes are arranged in multiple rows in parallel, and corrugated fins are interposed between these flat tubes, and the supercooling section is a heat exchanger with fins that have fins around the heat exchange tubes. It is characterized by being arranged separately on the windward side of the part. In the present invention, the condenser is a condenser that acts as an evaporator or a condenser by switching the refrigerant circuit, such as a heat exchanger in a refrigeration cycle apparatus such as a heat pump air conditioner. It shall mean a heat exchanger when acting.

  According to the condenser according to the present invention configured as described above, a heat exchanger having a structure in which corrugated fins are interposed between flat tubes arranged in a plurality of rows in parallel is used as the condensate liquefaction part. The condensate liquefaction part can be improved in performance and made compact. Moreover, since the supercooling part and the condensate liquefaction part are isolate | separated and the supercooling part is arrange | positioned in the windward side of the condensate liquefaction part, supercooling can be enlarged efficiently. In addition, the supercooling section is formed as a finned heat exchanger with fins around the heat exchange tube and is separated from the condensing liquefaction section. The shape and arrangement can be made in consideration of downsizing.

  The supercooling section is preferably formed such that the refrigerant passage area is smaller than the refrigerant passage area of the condensate liquefaction section. If comprised in this way, the refrigerant | coolant flow rate of a supercooling part can be made quick, and the fall of the heat exchange capability of a supercooling part can be reduced. Moreover, this supercooling part can also be made into the heat exchanger provided with the spine fin around the heat exchange tube. If comprised in this way, since the heat exchange performance of a fin improves, the performance improvement and compactification of a supercooling part can be advanced further.

  An indoor unit for an air conditioner according to the present invention includes an indoor fan that circulates indoor air, an indoor heat exchanger that exchanges heat with indoor air, and an indoor that blows out air that has been heat-exchanged by the indoor heat exchanger. The indoor fan is a centrifugal fan that blows out air in the radial direction of the impeller, and is arranged in the main body casing with the rotation axis in the front-rear direction, and the indoor heat exchanger includes the above-described condenser. The heat exchanger is a condensing and liquefying portion that constitutes the indoor heat exchanger, and is disposed on the blowout side of the indoor fan, and the supercooling portion is disposed between the blowout side of the indoor fan and the condensing and liquefying portion. The indoor outlet is arranged on the leeward side of the condensate liquefaction unit.

  In the indoor unit for an air conditioner formed as described above, the depth dimension of the indoor unit can be considered to be determined from the thickness dimension in the rotation axis direction of the centrifugal fan or the space required for installing the indoor heat exchanger. . Moreover, since the space required for installation of the indoor heat exchanger is configured as a finned heat exchanger in which the supercooling part is separated from the condensate liquefaction part, it is considered to be governed by the depth dimension of the condensate liquefaction part. be able to. In addition, the depth dimension of the condensate liquefaction part is separated from the supercooling part, so that the depth dimension of the condensate liquefaction part is smaller than that of the condensate liquefaction part and the supercooling part facing each other like a conventional indoor heat exchanger. Can be significantly reduced. As a result, the depth dimension of the indoor heat exchanger can be made smaller than the depth dimension of the centrifugal fan arranged as described above. Therefore, according to the present invention, the depth dimension of the indoor unit can be reduced to a value determined from the dimension in the front-rear direction of the centrifugal fan arranged as described above, and an indoor unit suitable for thinning can be obtained. it can.

  Further, in the indoor unit for an air conditioner, the condensate liquefying part of the indoor heat exchanger is disposed on two opposing side parts on the blowing side of the indoor fan, and the supercooling part is at least one of the blowing side of the indoor fan and It is good also as what was arrange | positioned between either one of the condensate liquefaction parts. If comprised in this way, the thin indoor unit with a small vertical dimension can be comprised.

  Further, in the indoor unit for an air conditioner, the condensate liquefying part of the indoor heat exchanger is disposed on two opposing side parts on the blowout side of the indoor fan, and the supercooling part is disposed on the blowout side of the indoor fan and the both sides. It is good also as what was each arrange | positioned between the condensate liquefaction parts. If comprised in this way, since a supercooling part can be disperse | distributed and arrange | positioned right and left and it can reduce in size, the indoor unit further reduced in thickness with a smaller vertical dimension can be comprised. .

  Further, in each of the indoor units for an air conditioner, the indoor fan has a suction port on the front side, a flat hub on the back side, and is configured to blow out air in the left-right direction. Is provided with an indoor air inlet for sucking indoor air at a portion facing the air inlet of the centrifugal fan, and the indoor air outlet is provided at a side end portion of the front of the main body casing. It may be. If comprised in this way, it can be comprised in the thin indoor unit with a small vertical dimension suitable for a wall hanging type.

  In each of the indoor units described above, the indoor air outlet may be configured to blow out obliquely forward in the left-right direction at the side end portion on the front surface of the main body casing. If comprised in this way, a wide blowing airflow can be comprised toward indoor.

  The condensate liquefying unit may be arranged so as to be inclined so that the front side of the air suction surface is close to the indoor fan. If it does in this way, a condensing liquefying part can be functioned as a guide part with respect to the airflow in an indoor unit (inside a main body casing).

  Moreover, you may make it arrange | position the said supercooling part near the back side between the blowing side of a centrifugal fan, and a condensate liquefaction part. In the indoor unit configured as above, the air resistance of the ventilation path passing through the back side is increased by installing the supercooling unit close to the back side, and the air resistance of the ventilation path passing through the front side and the air resistance passing through the back side. The air resistance of the ventilation path is made uniform. As a result, the wind speed distribution of the condensate liquefaction unit is made uniform, and the wind speed distribution at the indoor outlet is made uniform, so that comfort during heating operation can be improved.

  In the indoor unit configured as described above, a plurality of the indoor fans may be arranged in parallel in the main body casing. With this configuration, it is possible to configure an indoor unit that has a large capacity by increasing the size in the vertical or horizontal direction without increasing the size in the front-rear direction.

  According to the condenser according to the present invention, a heat exchanger having a structure in which corrugated fins are interposed between flat tubes arranged in a plurality of rows in parallel is used as the condensing liquefaction unit. And can be made compact. Moreover, since the supercooling part and the condensate liquefaction part are isolate | separated and the supercooling part is arrange | positioned in the windward side of the condensate liquefaction part, supercooling can be enlarged efficiently. In addition, the supercooling section is formed as a finned heat exchanger with fins around the heat exchange tube and is separated from the condensing liquefaction section. The shape and arrangement can be made in consideration of downsizing. Further, according to the indoor unit for an air conditioner according to the present invention, the centrifugal fan is arranged in the main body casing so that the rotation axis is in the front-rear direction, and the supercooling part is separated from the condensing liquefaction part, Since it arrange | positions between the blowing side and a condensate liquefaction part, the dimension of the front-back direction required for an indoor side heat exchanger can be made small. As a result, the depth dimension of the indoor unit can be designed to substantially match the dimension in the front-rear direction of the centrifugal fan, and the thickness can be reduced.

  Hereinafter, a condenser according to an embodiment of the present invention and an indoor unit for an air conditioner using the condenser will be described with reference to the drawings. In addition, in order to avoid duplication description about each embodiment, the same code | symbol is attached | subjected to the part which is common in each drawing, and the description of the part in each embodiment is abbreviate | omitted or simplified.

(Embodiment 1)
First, the indoor unit for an air conditioner according to Embodiment 1 will be described with reference to FIGS. 1 is a schematic plan sectional view of an indoor unit for an air conditioner according to Embodiment 1. FIG. FIG. 2 is a front view of the indoor unit for the air conditioner. FIG. 3 is a perspective view of a condensing and liquefying unit constituting the indoor heat exchanger mounted on the indoor unit for the air conditioner. FIG. 4 is a perspective view around a flat tube constituting a condensate liquefying section in the indoor heat exchanger. FIG. 5 is an exploded perspective view of the flat tube. FIG. 6 is a refrigerant flow diagram shown in a front perspective view of the indoor heat exchanger in the indoor unit for the air conditioner. FIG. 7 is a reference refrigerant flow chart related to the indoor heat exchanger. 8 to 12 illustrate various heat exchangers that can be applied to the subcooling section of the indoor heat exchanger.

  The indoor unit for an air conditioner according to Embodiment 1 is capable of heating operation by the heat of condensation of the refrigerant. For example, a wall-mounted indoor unit for a heat pump air conditioner. In this indoor unit, a centrifugal fan 2 as an indoor fan and an indoor heat exchanger 3 acting as a condenser are accommodated in a main casing 1 as shown in a schematic plan sectional view of FIG.

  As shown in FIG. 1, the main body casing 1 is formed in a horizontally long box shape, and an indoor suction port 12 for sucking room air is provided at the center of the front panel 11, and both left and right end portions of the front panel 11 are provided. An air outlet 13 is provided for blowing out the air heat-exchanged in the main body casing 1 into the room. The indoor suction port 12 also serves as a bell mouth of the centrifugal fan 2 described later, and a protective net is attached (not shown) so that an operator's hand and large foreign matter do not enter inside. Although omitted in FIG. 2, a suction grill 14 is provided as shown in the front view of FIG. On the other hand, as shown in the front view of FIG. The corner inner surfaces 16 on the left and right rear sides of the main casing 1 are formed in an arc shape so that the air flow in the main casing 1 flows smoothly to the indoor outlet 13.

  The centrifugal fan 2 is a turbo fan, and is configured to suck air from the front side and blow it out in the left and right radial directions. That is, the centrifugal fan 2 has the rotation shaft 21 in the front-rear direction, the suction port 23 of the impeller 22 is opposed to the indoor suction port 12, and the hub 24 is disposed along the back plate of the main casing 1. The indoor air is sucked from the indoor suction port 12 in the center of the front and blown out from the centrifugal fan 2 in the radial direction of the impeller 22. In this case, the upper and lower spaces of the impeller 22 are formed small, and the blowing direction from the centrifugal fan 2 is the left-right direction of the impeller 22, that is, the direction of the left and right indoor outlets 13. The centrifugal fan 2 configured in this manner uses a thin motor, such as a print motor, as the drive motor 25 in order to effectively reduce the thickness of the indoor unit.

  The indoor heat exchanger 3 is a heat exchanger that acts as a condenser. When the indoor unit is an indoor unit for a heat pump air conditioner, the indoor heat exchanger 3 acts as a condenser during heating operation. Since the present invention relates to an improvement of a condenser, only the case where the indoor heat exchanger 3 acts as a condenser will be described here.

  As shown in FIG. 1, the indoor side heat exchanger 3 is distributed substantially symmetrically on both the left and right sides, which are the blow-out side of the centrifugal fan 2. As shown in FIG. 2, the two heat exchange units 31 and 32 that are arranged in a distributed manner are connected by a refrigerant pipe 33 using the bottom space in the main body casing 1 and are configured to work together. . The left and right heat exchange units 31 and 32 supercool the condensate liquefaction units 34 and 35 for condensing and liquefying the high-pressure gas refrigerant discharged from the compressor, and the liquid refrigerant condensed and liquefied by the condensate liquefaction units 34 and 35. For this purpose, it is composed of supercooling sections 36 and 37. As shown in the perspective view of the condensate liquefaction part in FIG. 3, the condensate liquefaction parts 34, 35 are arranged with six rows of flat tubes 38 arranged in the vertical direction in parallel in the front-rear direction, and corrugated fins between these flat tubes 38. 39 is interposed. The flat tube 38 and the corrugated fin 39 are joined by brazing or the like. Further, the condensate liquefaction units 34 and 35 are fixed by frame members A, B, C, and D at the front and rear and the top and bottom.

  The flat tube 38 is made of aluminum or aluminum alloy having excellent corrosion resistance and thermal conductivity, and is joined so that the inner surfaces thereof face each other as shown in the partially exploded perspective views of FIGS. 4 and 5. A pair of rectangular plates 41. Each rectangular plate 41 has a communication port 43 formed at the lower end. The communication ports 43 of both rectangular plates 41 are formed coaxially. A communication pipe 45 connected to the communication port 43 of the rectangular plate 41 is disposed at the lower end of the corrugated fin 39, and the flat tubes 38 to be communicated communicate with each other through the communication pipe 45. In addition, a partition wall 47 that partitions an internal space formed by joining the pair of rectangular plates 41 in the vertical direction is provided on the inner surfaces of the pair of rectangular plates 41. The partition wall 47 forms two passages in the vertical direction inside the flat tube 38 to which the pair of rectangular plates 41 are joined. The two passages communicate with the respective communication ports 43 at the lower portion and communicate with each other at the upper portion to form an inverted U-shaped passage. As will be described later, the communication pipe 45 may not be connected depending on the flat tube 38, and the connection port 43 is not provided at this point.

  On the other hand, the supercooling sections 36 and 37 are finned heat exchangers separated from the condensing and liquefying sections 34 and 35, and are formed so that the refrigerant passage area is smaller than that of the condensing and liquefying sections 34 and 35. Further, the number of passes of the condensate liquefaction units 34 and 35 is 3, whereas the number of passes of the supercooling units 36 and 37 is 1. This is shown in FIG. 6 and will be described in detail later. Further, since the condensate liquefaction sections 34 and 35 may be formed as one pass, as shown in FIG. 8, a simple structure with a small cylindrical fin with a spine fin 52 wound around one heat exchange tube 51 is provided. It is formed as a heat exchanger. Moreover, the supercooling parts 36 and 37 are arrange | positioned in the windward side of both the condensate liquefaction parts 34 and 35 so that the heat exchange tube 51 may face an up-down direction, as shown in FIG.

  The heat exchanger constituting the supercooling sections 36 and 37 is not limited to such a type, and other types of heat exchangers can be used. This will be specifically described. In FIG. 9, a narrow plate-like fin 56 is wound around the heat exchange tube 55. However, such a plate-like fin 56 is difficult to manufacture and has a poor heat exchange rate as compared with the one in which the spine fin 52 of FIG. 8 is wound. In FIG. 10, the low fin 63 is plastically processed on the surface of the heat exchange tube 62 by the roller 61, but as is clear from FIG. 10, the heat exchange area of the low fin 63 cannot be increased. The exchange efficiency is low. The thing of FIG. 11 cuts and raises the low fin 72 by the method like FIG. 10 on the surface of the heat exchange tube 71 of a soft material (for example, aluminum), and covered this with the tube 73 of a hard material (for example, iron). is there. Although this heat exchanger can form a low fin larger than the thing of FIG. 10, it cannot expect heat exchange efficiency as the thing of FIG. In FIG. 12, the fins 76 are cut and raised on the surface of a flat heat exchange tube 75 formed by extrusion, but it is difficult to increase the heat exchange area of the fins 76 and the heat exchange efficiency is increased. Cannot be increased. As described above, various types of heat exchangers with fins constituting the supercooling sections 36 and 37 can be adopted, but the one shown in FIG. 8 is considered most desirable from the viewpoint of heat exchange efficiency. .

  Next, the detail of the refrigerant | coolant flow path in the indoor side heat exchanger 3 comprised in this way is demonstrated based on FIG. In addition, the white arrow in FIG. 6 has shown the flow direction of the air which is heat-exchanged. As shown in FIG. 6, the indoor side heat exchanger 3 includes a plurality of flat tubes 38 arranged on the left side when viewed from the front side as shown in FIG. The three blocks on the side are classified as the second block, and the three blocks on the right side are divided into the third block on the front side and the fourth block on the back side. And in each block, the flat tube 38 is connected by the connection piping 45 between the flat tubes 38 for every 2 channel | paths divided into 2 lengthwise directions. In addition, between the first block and the second block and between the third block and the fourth block, there is a connection between the outer passages, that is, between the passages on the leeward side. In addition, the second block and the third block are connected between the passages on the central side, that is, between the passages on the windward side. Then, from the windward side of the fourth block, it is connected to a supercooling unit 37 shown on the right side in FIG. 6, and this supercooling unit 37 is connected to a supercooling unit 36 shown on the left side in FIG. It is formed so that it may leave this indoor side heat exchanger 3 from below. Further, the gas pipe 81 through which the high-pressure gas refrigerant discharged from the compressor flows is connected to the flat tube 38 of the first block, and the liquid refrigerant supercooled by the indoor heat exchanger 3 is used as the next device such as an expansion valve. A liquid pipe 82 is connected to the lower part of the right supercooling section 36. As can be seen from the configuration shown in FIG. 6, the flat tube 38 on the second block side in the first block, the flat tube 38 on the first block side in the second block, and the flat tube on the fourth block side in the third block 38 and the flat tube 38 on the third block side in the fourth block, only one of the two passages configured inside is connected to the communication pipe 45, and the other passage is connected to the communication pipe 45. It has not been. Therefore, the communication port 43 is not formed on the wall surface of the rectangular plate 41 not connected to the communication passage 45.

  As a result of the flow paths being formed as described above, the indoor side heat exchanger 3 is condensed and liquefied by the condensate liquefaction units 34 and 35 when it acts as a condenser. The flow of the refrigerant in the condensate liquefaction units 34 and 35 is as follows. First, the discharge gas refrigerant from the compressor is supplied to the central side (that is, the windward side) passage of the flat tube 38 constituting the first block. Then, it flows in three passes from the central passage to the outer (that is, leeward) passage. The refrigerant cooled in the first block is supplied to the outside (that is, the leeward side) passage of the flat tube 38 constituting the second block, and flows from the outside passage to the center side (ie, the upwind side) passage in three passes. The refrigerant cooled in the second block is supplied to the central side (that is, the windward side) passage of the third block. Then, the air flows from the central passage to the outer (that is, leeward) passage in three passes. The refrigerant cooled in the third block is supplied to the outside (that is, the leeward side) passage of the fourth block. Then, the air flows from the outer passage to the central side (that is, the windward side) in three passes.

  The following points are taken into consideration for the refrigerant flow passage. The reason why the refrigerant is flowing in three passes in each block is to obtain an appropriate refrigerant flow rate while suppressing an increase in refrigerant flow resistance. The reason why the refrigerant flowing in each block is gathered and sent to the next block is to facilitate communication between the blocks. Further, the flow direction differs for each block in order to simplify the communication configuration between the blocks. In this way, in the fourth block, the refrigerant is allowed to flow out from the center side (windward side). This facilitates supercooling in the last passage. In this embodiment, it is set so that supercooling starts in the second half of the outer passage of the fourth block. The solid line part in FIG. 6 shows the part through which the supercooled refrigerant flows.

  Next, the refrigerant that has started to be supercooled in the condensing and liquefying units 34 and 35 is supplied to a supercooling unit 37 installed on the windward side of the fourth block in order to further efficiently perform supercooling. The refrigerant supercooled by the supercooling unit 37 is further supercooled by the supercooling unit 36 provided on the windward side of the flat tube 38 of the first block.

The condenser according to the present embodiment configured as described above can achieve the following operational effects.
The high-pressure gas refrigerant discharged from the compressor flows into the indoor heat exchanger 3 that acts as a condenser, and is condensed and liquefied by the condensing and liquefying units 34 and 35. The condensate liquefaction in the condensate liquefaction units 34 and 35 is set to be finished in the middle of the central side passage of the flat tube 38 of the fourth block. In FIG. 6, the thick solid line indicates that the supercooling zone is entered from the middle of the central passage of the flat tube 38 of the fourth block. Incidentally, in FIG. 7, the refrigerant flows as shown in FIG. 6 are performed in the condensing and liquefying units 34 and 35, but the supercooling units 36 and 37 are not provided as in the above-described embodiment. It is what I have listed. In FIG. 7, white arrows indicate the flow of air as in the case of FIG. In this reference example, as shown by a thick solid line in FIG. 7, in the flat tube 38 constituting the fourth block, the entire center side passage acts as a supercooling portion from the second half of the outer passage. For this reason, in the reference example, the capacity of the heat exchanger of the fourth block is reduced, and the heat exchanger cannot be effectively operated. As a result, the heating amount of the air passing through the fourth block is reduced. Therefore, when the condenser configured as described above is used as a heater, air having a low temperature is partially blown out, which causes a problem of impairing comfort during heating operation. In contrast to such a reference example, in the present embodiment, in the condensing and liquefying sections 34 and 35, the portion where the heat exchange capacity is reduced due to the circulation of the supercooled refrigerant is locally limited and used as a heater. You can improve your comfort.

  Moreover, since the refrigerant passage area of the supercooling parts 36 and 37 is made smaller than the refrigerant passage area of the condensing and liquefying parts 34 and 35, the refrigerant flow rate of the supercooling parts 36 and 37 can be increased, and the supercooling part 36. , 37 can be prevented from lowering the heat exchange capacity. Moreover, since the supercooling parts 36 and 37 are arrange | positioned on the windward side of the condensate liquefaction parts 34 and 35, supercooling can be enlarged efficiently.

  Moreover, since the supercooling parts 36 and 37 which concern on this invention are formed as a heat exchanger with a fin provided with the fin 52 around the heat exchange tube 51, and are isolate | separated from the condensate liquefaction parts 34 and 35, they are condensed liquefaction. The parts 34 and 35 and the supercooling parts 36 and 37 can be easily selected in size and type by individually adapting to the conditions for mounting in the apparatus. That is, the condensate liquefaction units 34 and 35 are not caught by the size and type of the supercooling units 36 and 37, and the subcooling units 36 and 37 are not caught by the size and type of the condensate liquefaction units 34 and 35. Each size and format can be selected. Specifically, in the present embodiment, the condensate liquefaction units 34 and 35 are a high-performance type in which a plurality of flat tubes 38 are arranged in parallel, and corrugated fins 39 are interposed between the flat tubes 38. Condensed liquefaction sections 34 and 35 are provided. Thereby, the condensate liquefaction parts 34 and 35 are improved in performance and miniaturized. In addition, the supercooling parts 36 and 37 are adapted to the installation conditions on the windward side of the condensing and liquefying parts 34 and 35 as a small cylindrical finned heat exchanger having a simple structure provided with fins around the heat exchange tube 51. The structure is easy to do. More specifically, the supercooling units 36 and 37 in the present embodiment are heat exchangers in which the spine fins 52 are wound around the heat exchange tubes 51, and by using the spine fins 52, heat can be efficiently generated. It can be exchanged.

Furthermore, according to the indoor unit for an air conditioner using the above-described condenser, the following operational effects can be further achieved.
The indoor unit for an air conditioner according to the present embodiment sucks indoor air from the indoor suction port 12 and is sucked into the impeller 22 from the suction port 23 of the centrifugal fan 2 during the heating operation. Erupted in the direction. A part of the air blown out from the centrifugal fan 2 is heated by the supercooling units 36 and 37 and conveyed to the condensing and liquefying units 34 and 35. The air conveyed to the condensate liquefaction units 34 and 35 is heated by passing through the corrugated fins 39 and is blown into the room from the indoor outlet 13 as warm air. At this time, since the supercooling parts 36 and 37 are heat-exchanged with unheated room air, the degree of supercooling by the supercooling parts 36 and 37 can be efficiently increased.

  Moreover, since the indoor side heat exchanger 3 is configured as a finned heat exchanger in which the supercooling units 36 and 37 are separated from the condensate liquefaction units 34 and 35, the depth dimension of the condensate liquefaction unit is the conventional indoor side heat. Smaller than the depth of the exchanger. For this reason, the dimension of the front-back direction required for the indoor side heat exchanger 3 can be made small. As a result, the depth dimension of the indoor unit can be designed substantially in accordance with the dimension in the front-rear direction of the centrifugal fan 2 arranged as described above, and can be thinned.

  In addition, the condensate liquefaction units 34 and 35 of the indoor heat exchanger 3 are arranged on two opposite sides of the blowout side of the centrifugal fan 2, and the supercooling units 36 and 37 are connected to the blowout side of the centrifugal fan 2 and the condensate liquefaction unit. 34 and 35, it is possible to configure a thin indoor unit with a small vertical dimension. In addition, the supercooling parts 36 and 37 can also be arrange | positioned only at one side. However, as in this embodiment, the number of the supercooling parts 36 and 37 is two, and the two supercooling parts 36 and 37 are arranged between the outlet side of the centrifugal fan 2 and the condensing liquefaction parts 34 and 35. If it comprises, the supercooling parts 36 and 37 can be reduced in size, and arrangement | positioning etc. of an apparatus can be set more easily in thickness reduction of an indoor unit.

  Further, the centrifugal fan 2 as an indoor fan housed in the main casing 1 has a suction port 23 on the front side and a flat hub 24 on the back side, and is configured to blow out air in the left-right direction. Further, the front panel 11 on the front side of the main body casing 1 is provided with an indoor suction port 12 at a portion facing the suction port 23 of the centrifugal fan 2, and further, an indoor blower is provided at a side end portion of the front panel 11. Since the outlet 13 is provided, it can be configured as a thin indoor unit having a small vertical dimension suitable for a wall-mounted type.

  Moreover, in the indoor unit configured as described above, the airflow on the front side is greatly bent in front of the indoor outlet 13 compared to the airflow on the back side. In the indoor unit having such a configuration, the air resistance is larger on the front side than on the rear side, and the wind speed distribution of the indoor side heat exchanger 3 becomes uneven. However, in the present embodiment, the supercooling units 36 and 37 are arranged close to the back side between the blowout side of the centrifugal fan 2 and the condensing liquefaction units 34 and 35. The air resistance on the side can be made uniform, and the heat exchange efficiency of the condensate liquefaction units 34 and 35 can be improved. Moreover, since the wind speed distribution of the indoor outlet 13 can be made uniform, the comfort during heating operation can be made efficient.

(Embodiment 2)
In the second embodiment, the condensate liquefying sections 34 and 35 are inclined as shown in the plan sectional view of FIG. In the first embodiment, the condensate liquefaction units 34 and 35 are arranged in the front-rear direction. On the other hand, in the second embodiment, as shown in FIG. 13, the front side of the air suction surface of the condensate liquefaction units 34 and 35 is disposed so as to be close to the centrifugal fan 2. If it does in this way, the condensate liquefying parts 34 and 35 can be functioned as a guide part with respect to the airflow in an indoor unit (inside the main body casing 1).

(Embodiment 3)
In the third embodiment, the above-described supercooling sections 36 and 37 are each constituted by two supercooling heat exchangers. As shown in the sectional plan view of FIG. 14 and the refrigerant flow diagram shown in the front perspective view of the indoor heat exchanger of FIG. 15, there are two front and rear units between the outlet side of the centrifugal fan 2 and the condensate liquefaction units 34 and 35. The supercooling parts 36a, 36b, 37a, 37b are arranged side by side. If comprised in this way, since the magnitude | size of each subcooling part 36a, 36b, 37a, 37b can be made small, the dimension of the left-right direction can be made small, or the airflow distribution in an indoor unit (inside the main body casing 1). Can be improved. As can be seen from the third embodiment, the present invention is not particularly limited to the number of supercooling sections.

(Embodiment 4)
In the fourth embodiment, the indoor outlet is modified. As shown in FIG. 16, in the fourth embodiment, the indoor air outlets 13 a provided at the left and right ends of the front surface of the main body casing 1 are provided at the corners of the main body casing 1 so as to be blown out obliquely forward in the left-right direction. ing. By comprising in this way, a wide blowing airflow can be comprised toward the room.

(Embodiment 5)
In the fifth embodiment, two centrifugal fans 2 are arranged side by side to increase the capacity. FIG. 17 is a cross-sectional plan view of an air conditioner indoor unit according to Embodiment 5. As shown in FIG. 17, the configuration of Embodiment 1 is arranged side by side. In this embodiment, two centrifugal fans 2 are arranged in the left-right direction in the main body casing 1, and the two indoor suction ports 12 are opposed to the suction port 23 of the centrifugal fan 2 on the front side of the main body casing 1. (Front panel 11 side). Further, an indoor outlet 13 is provided at a side end portion of the front surface (front panel 11) of the main casing 1 and a portion corresponding to the space between the centrifugal fan 2. If comprised in this way, it can be comprised in the thin indoor unit with a small vertical dimension suitable for a wall hanging type.

  In the fifth embodiment, two centrifugal fans 2 are arranged in the left-right direction. However, the number of centrifugal fans 2 is three or more, and the interior unit is configured according to the fifth embodiment. In addition, the capacity can be further increased.

  In the fifth embodiment, an example of an indoor unit for an air conditioner that has been increased in the left-right direction to increase the capacity has been described. However, the configuration described in the first embodiment has two or more stages in the height direction. It is also possible to increase the capacity by overlapping the number of steps and increasing the dimension in the height direction.

  In the third to fifth embodiments, the condensate liquefaction units 34 and 35 may be inclined as in the second embodiment. In the second, fourth, and fifth embodiments, the supercooling sections 36 and 37 may be configured by two supercooling heat exchangers as in the third embodiment. Further, in the second, third and fifth embodiments, the indoor air outlets 13 provided at the left and right end portions on the front surface of the main body casing 1 may be formed as indoor air outlets that blow obliquely forward in the left-right direction as in the fourth embodiment. Good.

  The indoor unit for an air conditioner of the present invention may be a dedicated heating unit or a heat pump type air conditioning unit. Moreover, the condenser which concerns on this invention can also be used for refrigeration cycle apparatuses other than air conditioning apparatuses, such as a refrigerator.

It is a schematic plane sectional view of the indoor unit for an air conditioner according to Embodiment 1 of the present invention. It is a front view of the indoor unit for the air conditioner It is a perspective view of the condensing liquefaction part which comprises the indoor side heat exchanger mounted in the indoor unit for air conditioners. It is a perspective view around the flat tube which comprises the condensate liquefaction part in the indoor side heat exchanger. It is a disassembled perspective view of the flat tube. It is a refrigerant | coolant flowchart represented to the front perspective view of the indoor side heat exchanger. It is a reference refrigerant flowchart related to the indoor side heat exchanger. It is an example of the heat exchanger which can be applied to the supercooling part of the indoor side heat exchanger. It is another example of the heat exchanger applicable to the supercooling part of the indoor side heat exchanger. It is another example of the heat exchanger applicable to the supercooling part of the indoor side heat exchanger. It is another example of the heat exchanger applicable to the supercooling part of the indoor side heat exchanger. It is another example of the heat exchanger applicable to the supercooling part of the indoor side heat exchanger. It is a plane sectional view of an indoor unit for an air conditioner according to Embodiment 2. It is a plane sectional view of the indoor unit for an air conditioner according to Embodiment 3. It is a refrigerant | coolant flowchart represented to the front perspective view of the indoor side heat exchanger in the indoor unit. It is a plane sectional view of an indoor unit for an air conditioner according to Embodiment 4. FIG. 10 is a cross-sectional plan view of an indoor unit for an air conditioner according to Embodiment 5.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Main body casing 2 Centrifugal fan (as an indoor fan) 3 Indoor side heat exchanger 12 Indoor inlet 13,13a Indoor outlet 21 Rotating shaft 22 Impeller 23 Inlet 24 Hub 34, 35 Condensation liquid parts 36, 36a, 36b , 37, 37a, 37b Supercooling section 38 Flat tube 39 Corrugated fins 51, 55, 62, 71, 75 Heat exchange tube 52 Spine fins 56, 76 Fins

Claims (11)

  The condensate liquefaction unit condensates and liquefies the high-pressure gas refrigerant, and a supercooling unit that supercools the liquid refrigerant liquefied in the condensate liquefaction unit. The condensate liquefaction unit includes a plurality of flat tubes arranged in parallel in a plurality of rows. The corrugated fins are interposed between the flat tubes, and the supercooling section is a finned heat exchanger having fins around the heat exchange tubes, separated to the windward side of the condensing liquefaction section. A condenser characterized by being arranged so that the refrigerant passage area is smaller than the refrigerant passage area of the condensate liquefaction section.   The condenser according to claim 1, wherein the supercooling section is formed so that a refrigerant passage area is smaller than a refrigerant passage area of the condensing liquefaction section.   The condenser according to claim 1 or 2, wherein the supercooling section is a finned heat exchanger including a spine fin around a heat exchange tube. A main body casing, an indoor fan that circulates the indoor air, an indoor heat exchanger that exchanges heat with the indoor air, and an indoor outlet that blows out the air heat-exchanged by the indoor heat exchanger,
The indoor fan is a centrifugal fan that blows out air in the radial direction of the impeller, and is arranged with the rotation axis in the main body casing as the front-rear direction,
An indoor side heat exchanger is a heat exchanger which comprises the condenser of any one of Claims 1-3, The condensation liquefying part which comprises this indoor side heat exchanger is arrange | positioned at the blowing side of an indoor fan And the supercooling unit is configured to be disposed between the outlet side of the indoor fan and the condensate liquefaction unit,
An indoor unit for an air conditioner, wherein the indoor outlet is disposed on the leeward side of the condensate liquefaction unit.   The condensate liquefaction part is disposed on two opposite sides on the blowout side of the indoor fan, and the supercooling part is disposed between the blowout side of the indoor fan and at least one of the condensate liquefaction parts. The indoor unit for an air conditioner according to claim 4, wherein the indoor unit is an air conditioner.   The condensate liquefaction unit is disposed on two opposing sides on the blowout side of the indoor fan, and the supercooling unit is disposed between the blowout side of the indoor fan and the two condensate liquefaction units, respectively. The indoor unit for an air conditioner according to claim 4.   The indoor unit for an air conditioner according to any one of claims 4 to 6, wherein the indoor fan has a suction port on the front side, a flat hub on the back side, and air in the left-right direction. It is configured to blow out, and on the front surface of the main body casing, a portion facing the suction port of the centrifugal fan is provided with an indoor suction port for sucking room air, and on the side end portion on the front surface of the main body casing, An indoor unit for an air conditioner, characterized in that the indoor outlet is provided.   The indoor unit for an air conditioner according to claim 7, wherein the indoor outlet is configured to blow out in a diagonally forward direction at a side end portion of the front surface of the main casing.   The indoor unit for an air conditioner according to claim 7 or 8, wherein the condensate liquefying portion is disposed so as to be inclined such that a front side of an air suction surface is close to an indoor fan.   The air conditioner according to any one of claims 7 to 9, wherein the supercooling section is arranged close to the back side between the blowout side of the centrifugal fan and the condensing liquefaction section. Indoor unit.   The indoor unit for an air conditioner according to any one of claims 4 to 10, wherein a plurality of the indoor fans are arranged in parallel in the main body casing.

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