JP2010133656A - Indoor unit of air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve space efficiency and heat exchanging efficiency by reasonably disposing a fan and a heat exchanger in a housing of an indoor unit of an air conditioner. <P>SOLUTION: The indoor unit 1 of the air conditioner includes a housing 10 flat in the vertical direction, having a supply opening 12 on its front face, and a suction opening 13 on its top face. Inside of the housing 10, a cross flow fan 20 for forming the supply airflow is disposed at an inner side of the supply opening 12. A parallel flow type heat exchanger 30 is disposed at a position below the suction opening 13 at the back of the cross flow fan 20. A fin and tube type heat exchanger 40 is disposed in the airflow passing through the parallel flow type heat exchanger 30 and directing to the cross flow fan 20. The parallel flow type heat exchanger 30 and the fin and tube type heat exchanger 40 are disposed within a range of vertical width of a fan casing 21 of the cross flow fan 20 in an inclined state that a side of the cross flow fan 20 is high. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an indoor unit of an air conditioner.

  In an air conditioner, a heat exchanger of a kind such as a fin and tube type, a parallel flow type, or a serpentine type is used. The fin-and-tube type is a type in which one tube penetrates a large number of parallel fins while meandering, and is commonly used. In the parallel flow type, a plurality of flat tubes are arranged between two header pipes so that a refrigerant passage inside the flat tubes communicates with the inside of the header pipe, and fins such as corrugated fins are arranged between the flat tubes. It is. The serpentine type is the same as the parallel flow type until the flat tube is placed between the two header pipes, but the number of flat tubes is one, and this single flat tube snakes and snakes. Fins such as corrugated fins are arranged between the flat tubes. Patent Document 1 describes an air conditioner using a parallel flow type heat exchanger.

  In the heat exchanger unit, in order to increase the amount of heat exchange, a plurality of heat exchangers are often arranged back and forth in the ventilation path. Patent Document 2 describes a configuration in which two or more parallel flow type or serpentine type heat exchangers are arranged in parallel. Patent Document 3 describes a configuration in which a plurality of rows of fin-and-tube heat exchangers are arranged before and after.

In a heat exchanger of an air conditioner, the wind speed of an airflow passing through the heat exchanger is generally large at a location near the blower and small at a location far from the blower. When the wind speed distribution is biased in this way, the heat exchange efficiency at a location where the wind speed is slow is lowered, and at a location where the wind speed is fast, the heat exchange efficiency is increased, but noise is increased, which is not preferable. Therefore, proposals have been made to make the wind speed uniform by changing the ease of airflow passing through the fins depending on the location. For example, in Patent Document 4, a heat exchanger with a narrow fin interval is installed on the side closer to the blower, a heat exchanger with a wide fin interval is installed on the side far from the blower, and the flow path resistance difference between these heat exchangers A cooling device with a mark is described. Patent Document 5 describes a heat exchanger air blower in which fins of a fin-and-tube type heat exchanger have a fin interval close to the cross flow fan and a portion remote from the cross flow fan sparse. . In Patent Document 6, a side flow parallel flow type heat exchanger is disposed in an inclined shape with respect to the flow direction of heat exchange air, and the air flow resistance of the heat exchange portion of this heat exchanger is relatively relative to the windward side. In particular, a configuration is described in which the setting is relatively small on the leeward side.
JP 2001-66083 A JP 2005-55108 A JP-A-7-198166 JP 59-161687 JP 59-210299 A Japanese Patent No. 2901338

  An object of this invention is to arrange | position a fan and a heat exchanger rationally in the housing | casing of the indoor unit of an air conditioner, and to improve space efficiency and heat exchange efficiency.

  In order to achieve the above object, an indoor unit for an air conditioner according to the present invention includes a vertically flat casing having a blower outlet on a front surface and a suction port on an upper surface, and a blown airflow disposed inside the blower outlet. A cross flow fan for forming, and a parallel flow type heat exchanger disposed behind the cross flow fan and below the suction port, the parallel flow type heat exchanger including the cross flow fan The fan is characterized in that it is disposed within the fan casing vertical width range of the cross flow fan in an inclined state where the fan side becomes high.

  According to this configuration, the parallel flow type heat exchanger is disposed within the vertical range of the fan casing of the cross flow fan in an inclined state where the cross low fan side becomes high. It can be combined into a compact shape with little thickness.

  In the indoor unit of the air conditioner configured as described above, the density of the fins disposed between the flat tubes of the parallel flow type heat exchanger is relatively dense on the side close to the cross flow fan and relatively sparse on the far side. It is preferable that

  With such a configuration, the air flow resistance on the side close to the cross flow fan that tends to increase the wind speed among the parallel flow type heat exchangers becomes relatively large, and conversely, it is far from the cross flow fan that tends to decrease the wind speed. Since the air flow resistance becomes relatively small on the side, the deviation of the wind speed distribution is corrected, and the overall heat exchange efficiency is improved.

  In the air conditioner indoor unit configured as described above, the flat tubes of the parallel flow type heat exchanger are parallel to the axis of the cross flow fan, and the interval between the flat tubes is close to the cross flow fan. Then, it is preferable that the width is relatively narrow and the distance is relatively wide on the far side.

  With such a configuration, the air flow resistance on the side close to the cross flow fan that tends to increase the wind speed among the parallel flow type heat exchangers becomes relatively large, and conversely, it is far from the cross flow fan that tends to decrease the wind speed. Since the air flow resistance becomes relatively small on the side, the deviation of the wind speed distribution is corrected, and the overall heat exchange efficiency is improved.

  In the indoor unit of the air conditioner having the above-described configuration, it is preferable that a fin-and-tube type heat exchanger is disposed in an airflow that passes through the parallel flow type heat exchanger and goes to the cross flow fan.

  With such a configuration, the heat exchanger has a dual structure of a parallel flow type heat exchanger and a fin-and-tube type heat exchanger, so that heat exchange with room air can be sufficiently performed. .

  In the indoor unit of the air conditioner having the above-described configuration, it is preferable that during cooling, the refrigerant flows through the fin-and-tube type heat exchanger and then flows into the parallel flow type heat exchanger.

  With such a configuration, since the refrigerant gradually evaporates until reaching the parallel flow type heat exchanger, the refrigerant having a high dryness flows into the parallel flow type heat exchanger. Since the parallel flow type heat exchanger has a large number of tubes that distribute the refrigerant, if the refrigerant is highly dry, the flow of the refrigerant is uneven and does not flow evenly in each tube, and the temperature distribution in the entire heat exchanger is uneven. There is a possibility. On the other hand, the fin-and-tube type heat exchanger flows in with a refrigerant having a low dryness, and the number of tubes through which the refrigerant is distributed is small. The temperature distribution can be made uniform. In a situation where the temperature of the air sucked into the crossflow fan is not uniform, sufficiently cooled air is sucked into a specific part of the crossflow fan, and insufficiently cooled air is sucked into other parts. The cross flow fan is cooled by the sufficiently cooled air, and the entire cross flow fan is cooled by the heat conduction of the cross flow fan. Since air with insufficient cooling hits here, dew condensation occurs on the cross flow fan, and the dew splashes on the air blown out from the indoor unit, which may cause discomfort to the user. According to the configuration of the present invention, even if a drift occurs in the parallel flow type heat exchanger and the temperature distribution is biased, the air sucked into any part of the cross flow fan immediately before the fin and tube type Since heat is exchanged by the heat exchanger, the insufficiently cooled air is cooled, and the above-described problem of condensation of the cross flow fan can be avoided.

  In the air conditioner indoor unit configured as described above, during cooling, the refrigerant preferably flows into a lower header pipe of the parallel flow type heat exchanger from a refrigerant outlet provided at a lower portion of the fin and tube type heat exchanger. .

  With this configuration, the pipe or tube connecting the fin and tube heat exchanger and the parallel flow type heat exchanger is guided from the top of the fin and tube type heat exchanger to the bottom of the parallel flow type heat exchanger. The amount of materials can be reduced. Further, in the parallel flow type heat exchanger, when used as an evaporator, if the refrigerant flows in from the upper header pipe, the flow of the refrigerant is biased in the flat tube closer to the inflow portion, so-called drift is likely to occur. However, in the configuration in which the refrigerant flows from the lower header tube as in the present invention, the refrigerant is properly divided into the respective flat tubes, and the uneven flow hardly occurs. Therefore, the heat exchange performance can be kept good.

  According to the present invention, by devising the arrangement of the three parts of the cross flow fan, the parallel flow type heat exchanger, and the fin and tube type heat exchanger, the heat exchange efficiency is high, yet the compact shape with a small upper and lower thickness. An indoor unit of an air conditioner can be obtained.

  A first embodiment of the present invention will be described below with reference to FIGS. FIG. 1 is a sectional view showing a schematic configuration of an indoor unit of an air conditioner, and FIG. 2 is a schematic schematic configuration diagram of a heat exchanger unit.

  The indoor unit 1 of an air conditioner includes a rectangular parallelepiped casing 10 that is flat in the vertical direction. The housing 10 is attached to an indoor wall surface (not shown) by a base 11 fixed to the back surface thereof. The housing 10 has a blower outlet 12 on the front surface, and has a suction port 13 formed of a set of a plurality of slits or openings partitioned in a lattice shape on the upper surface. A cover 14 and a wind direction plate 15 are provided at the air outlet 12. Both the cover 14 and the wind direction plate 15 rotate in the vertical plane, and assume a horizontal posture (open state) shown in FIG. 1 during operation, and a vertical posture (closed state) when operation is stopped. A filter 16 that collects dust contained in the sucked air is disposed inside the suction port 13.

  A cross flow fan 20 for forming a blown airflow is disposed inside the blowout port 12 with its axis line horizontal. The cross flow fan 20 is housed in a fan casing 21 and is rotated in the direction of the arrow in FIG. 1 by an electric motor (not shown) to form an airflow that flows from the suction port 13 and blows out from the blower port 12.

  A heat exchanger unit U1 is disposed behind the cross flow fan 20. The heat exchanger unit U1 includes a parallel flow type heat exchanger 30 disposed at a position below the suction port 13 and a down flow type parallel flow type heat exchanger 30 (hereinafter simply referred to as a parallel flow type heat exchanger 30). And a fin-and-tube type heat exchanger 40 disposed in an airflow passing through the cross-flow fan 20. The cross flow fan 20 is arranged with the axis line horizontal. The parallel flow type heat exchanger 30 and the fin and tube type heat exchanger 40 are both in an inclined state where the side of the cross low fan 20 is raised, and the parallel flow type heat exchanger 30 is moved upward, and the fin and tube type heat exchanger 40. Is arranged within the vertical width range of the fan casing 21 of the cross flow fan 20.

  The parallel flow type heat exchanger 30 includes an upper header pipe 31 and a lower header pipe 32 that are spaced apart from each other horizontally, that is, in parallel with each other, and between the upper header pipe 31 and the lower header pipe 32. A plurality of flat tubes 33 extending in the direction are arranged at a predetermined pitch. The flat tube 33 is an elongated molded product obtained by extruding a metal having good heat conductivity such as aluminum, and a refrigerant passage 34 for circulating a refrigerant is formed therein. In one configuration example of the refrigerant passage 34, a plurality of ones having the same cross-sectional shape and cross-sectional area are arranged in the depth direction of FIG. 2, so that the flat tube 33 has a harmonica-like cross section. Each refrigerant passage 34 communicates with the inside of the upper header pipe 31 and the lower header pipe 32.

  Corrugated fins 35 are disposed between adjacent flat tubes 33. The upper header pipe 31, the lower header pipe 32 and the flat tube 33, and the flat tube 33 and the corrugated fin 35 are fixed by brazing or welding, respectively. In addition to the flat tube 33, the upper header pipe 31, the lower header pipe 32, and the corrugated fins 35 are also made of a metal having good thermal conductivity such as aluminum.

  Since many flat tubes 33 are provided between the upper header pipe 31 and the lower header pipe 32 and the corrugated fins 35 are provided between the flat tubes 33, the heat radiation (heat absorption) area of the parallel flow type heat exchanger 30 is as follows. Large and efficient heat exchange. In the arrangement state of FIG. 1, the upper header pipe 31 is located on the higher side near the cross flow fan 20, and the lower header pipe 32 is located on the lower side far from the cross flow fan 20.

  The density of the corrugated fins 35 (in this case, the distance between the ridges of the corrugated fins 35 or the peak-valley pitch is referred to as “density”) varies depending on the location. That is, the density close to the cross flow fan 20, that is, the side close to the upper header pipe 31 is relatively dense, and the side far from the cross flow fan 20, that is, the side close to the lower header pipe 32 has a relatively low density. It has become. With this configuration, in the parallel flow type heat exchanger 30, the air flow resistance on the side close to the cross flow fan 20 where the wind speed tends to be high is relatively large, and conversely, the side far from the cross flow fan 20 where the wind speed tends to be slow. Then, since the air flow resistance becomes relatively small, the deviation of the wind speed distribution is corrected, and the heat exchange efficiency as a whole is improved.

  The fin-and-tube type heat exchanger 40 includes a large number of fins 41 and one meandering tube 42. The individual fins 41 have a strip shape with the vertical direction as the longitudinal direction, and a large number of the fins 41 are arranged in the horizontal direction with a predetermined gap therebetween. The tube 42 penetrates through the group of fins 41 so as to meander and sew from the top to the bottom. The inside of the tube 42 becomes a refrigerant passage 43 through which the refrigerant flows. The tube 42 has a refrigerant inlet 44 when used as an evaporator at the upper end, and a refrigerant outlet 45 at the lower end. The fin 41 and the tube 42 are made of a metal having good heat conductivity such as aluminum or copper, and are fixed by crimping by expanding the tube 42.

  In the arrangement state of FIG. 1, the refrigerant inlet 44 is located on the higher side near the cross flow fan 20, and the refrigerant outlet 45 is located on the lower side far from the cross flow fan 20. And the fin and tube type heat exchanger 40 is arrange | positioned so that the suction inlet 21a of the fan casing 21 may be covered in the position hidden in the plane projection of the parallel flow type heat exchanger 30. FIG.

When the parallel flow type heat exchanger 30 is used as an evaporator, that is, during cooling, the refrigerant flows from the lower header pipe 32. The refrigerant evaporates while ascending the flat tube 33 and flows out from the upper header pipe 31. One end of the lower header pipe 32 is provided with a refrigerant inlet 36 connected to the refrigerant outlet 45 of the fin-and-tube heat exchanger 40. The upper header pipe 31 is provided with a refrigerant outlet 37 at an end diagonally opposite to the refrigerant inlet 36. As in the modified embodiment of FIG. 3, the refrigerant outlet 37 may be provided on the same side as the refrigerant inlet 36. 2 and 3, the refrigerant inlet 44 of the fin-and-tube type heat exchanger 40 and the refrigerant outlet 37 of the parallel flow type heat exchanger 30 are preferably disposed on the same side.

  When the heat exchanger unit U1 is used as an evaporator, that is, during cooling, the refrigerant flows from the refrigerant inlet 44 of the fin-and-tube type heat exchanger 40. The refrigerant evaporates while passing through the refrigerant passage 43 and removes heat from the surrounding air. The refrigerant that has passed through the fin-and-tube type heat exchanger 40 enters the lower header pipe 32 from the refrigerant inlet 36 of the parallel flow type heat exchanger 30 and rises in the refrigerant passage 34 of the flat tube 33. In the process of ascending the refrigerant passage 34, the refrigerant further evaporates and takes heat from the surrounding air. Finally, the refrigerant enters the upper header pipe 31 and flows out from the refrigerant outlet 37.

  During cooling, the refrigerant flows through the fin and tube type heat exchanger 40 and then flows into the parallel flow type heat exchanger 30. Since the refrigerant gradually evaporates by the time it reaches the parallel flow type heat exchanger 30, the refrigerant having a high dryness flows into the parallel flow type heat exchanger 30. Since the parallel flow type heat exchanger 30 has a large number of flat tubes 33 for distributing the refrigerant, if the refrigerant has a high degree of dryness, the flow of the refrigerant is uneven and does not flow evenly to the flat tubes 33, and the heat exchanger as a whole. There is a possibility of non-uniform temperature distribution. On the other hand, the fin-and-tube type heat exchanger 40 flows into the refrigerant having a low dryness and the number of tubes 42 for distributing the refrigerant is small. The temperature distribution of the entire vessel can be made uniform.

  If the temperature of the air sucked into the cross flow fan 20 is not uniform, a sufficiently cooled air is sucked into a specific part of the cross flow fan 20, and air with insufficient cooling is sucked into other parts. Is born. Due to the heat conduction inside the cross flow fan 20, heat escapes to the part where the sufficiently cooled air hits. Therefore, the cross flow fan 20 itself is considerably cooled even in the part where the insufficiently cooled air is sucked. It becomes a state. If air with insufficient cooling hits it, moisture contained in the air will condense on the surface of the cross flow fan 20, and the dew will scatter on the air blown from the air outlet 12, causing discomfort to the user. May give. In the configuration of the first embodiment, the air sucked into any part of the cross flow fan 20 is heat-exchanged immediately before by the fin-and-tube type heat exchanger 40, so that the above-described problem of condensation of the cross flow fan 20 is avoided. be able to.

  When looking at the flow of the refrigerant when the heat exchanger unit U1 is used as an evaporator, the refrigerant flows from the upper part to the lower part of the fin-and-tube type heat exchanger 40, and the parallel flow from the refrigerant outlet 45 provided in the lower part. It flows into the lower header pipe 32 of the type heat exchanger 30. For this reason, the structure which guides the pipe and tube which connect fin and tube type heat exchanger 40 and parallel flow type heat exchanger 30 from the upper part of fin and tube type heat exchanger 40 to the lower part of parallel flow type heat exchanger 30 The amount of materials can be reduced. Further, when the refrigerant flows from the upper header pipe 31 in the parallel flow type heat exchanger 30, the flow of the refrigerant is likely to be biased in the flat tube 33 closer to the inflow portion. If it is the structure which flows in, the flow of the refrigerant | coolant to each flat tube 33 will be performed favorably, and uneven flow will not arise easily. Therefore, the heat exchange performance can be kept good.

  The parallel flow type heat exchanger is not limited to a configuration in which a plurality of flat tubes extending in the vertical direction are disposed between the upper header pipe and the lower header pipe. It may be a side flow type parallel flow type heat exchanger in which header pipes extending in the vertical direction are arranged at both left and right ends, and a plurality of horizontal flat tubes are arranged therebetween. An example of such a configuration is shown in FIG. 4 as a second embodiment. FIG. 4 is a schematic schematic configuration diagram of a heat exchanger unit according to the second embodiment.

  The heat exchanger unit U2 shown in FIG. 4 combines a side flow type parallel flow type heat exchanger 50 (hereinafter sometimes simply referred to as a parallel flow type heat exchanger 50) with a fin-and-tube type heat exchanger 40. ing. In the parallel flow type heat exchanger 50, a left header pipe 51L and a right header pipe 51R extending in the vertical direction are arranged in parallel with a space therebetween, and extend in the horizontal direction between the left header pipe 51L and the right header pipe 51R ( That is, a plurality of flat tubes 52 extending in parallel to the axis of the cross flow fan 20 are arranged at a predetermined pitch. The flat tube 52 is an elongated molded product obtained by extruding a metal having good heat conductivity such as aluminum, and a refrigerant passage 53 through which a refrigerant flows is formed inside. In the configuration example of the refrigerant passage 53, a plurality of pieces having the same cross-sectional shape and cross-sectional area are arranged in the depth direction of FIG. 4, and therefore the flat tube 52 has a harmonica-like cross section. Each refrigerant passage 53 communicates with the inside of the left header pipe 51L and the right header pipe 51R.

  Corrugated fins 54 are disposed between adjacent flat tubes 52. The left header pipe 51L and the right header pipe 51R and the flat tube 52, and the flat tube 52 and the corrugated fin 54 are fixed by brazing or welding, respectively. In addition to the flat tube 52, the left header pipe 51L, the right header pipe 51R, and the corrugated fins 54 are also made of a metal having good heat conductivity such as aluminum.

  The parallel flow type heat exchanger 50 is arranged in an inclined state so that the upper part in FIG. 4 is close to the cross flow fan 20 and is high, and the lower part in FIG. 4 is far from the cross flow fan 20 and is low. Is done. In the left header pipe 51 </ b> L, a refrigerant inflow port 55 is formed at a low position far from the cross flow fan 20, and a refrigerant outflow port 56 is formed at a high position near the cross flow fan 20.

  The density of the corrugated fins 54 is relatively dense on the side near the cross flow fan 20, that is, on the side near the refrigerant outlet 56, and relatively on the side far from the cross flow fan 20, that is, on the side near the refrigerant inlet 55. It has become. With this configuration, in the parallel flow type heat exchanger 50, the air flow resistance on the side close to the cross flow fan 20 where the wind speed is likely to be fast becomes relatively large, and conversely, the side far from the cross flow fan 20 where the wind speed is likely to be slow. Then, since the air flow resistance becomes relatively small, the deviation of the wind speed distribution is corrected, and the heat exchange efficiency as a whole is improved.

  Inside the left header pipe 51L, a partition wall 57a is formed at a position elevated by a predetermined distance from the lower end, and a partition wall 57b is formed at a position further elevated by a predetermined distance therefrom. A partition wall 57c is formed in the right header pipe 51R at a position elevated by a predetermined distance from the lower end. The partition wall 57c is provided at an intermediate height between the partition walls 57a and 57b. As a result, the parallel flow type heat exchanger 50 is divided into four sections in the vertical direction. That is, the first section 58A from the lower end to the partition wall 57a, the second section 58B from the partition wall 74a to the partition wall 57c, the third section 58C from the partition wall 57c to the partition wall 57b, and the fourth section 58D from the partition wall 57b to the upper end. It is.

  During the cooling operation, that is, when the heat exchanger unit U2 is used as an evaporator, the refrigerant flowing into the left header pipe 51L from the fin-and-tube type heat exchanger 40 through the refrigerant inlet 55 passes through the first section 58A from the left to the right. Then, the second section 58B exits from the right to the left, the third section 58C exits from the left to the right, and finally the fourth section 58D exits from the right to the left, and flows out from the refrigerant outlet 56. . In this way, the refrigerant takes in heat from the indoor air and evaporates while rising inside the parallel flow type heat exchanger 50 in a zigzag locus.

  FIG. 5 shows a first modified embodiment of the second embodiment. In the configuration of FIG. 4, the intervals between the flat tubes 52 are uniform, but the intervals may be unequal as shown in FIG. In the configuration of FIG. 5, the interval between the flat tubes 52 included in the first section 58A and the interval between the flat tubes 52 adjacent at the boundary between the first section 58A and the second section 58B are the widest. The interval between the flat tubes 52 included in the second section 58B and the interval between the flat tubes 52 adjacent at the boundary between the second section 58B and the third section 58C are slightly narrowed. The interval between the flat tubes 52 included in the third section 58C and the interval between the flat tubes 52 adjacent at the boundary between the third section 58C and the fourth section 58D are further narrowed. The interval between the flat tubes 52 included in the fourth section 58D is the narrowest. The density of the corrugated fins 54 is relatively dense on the side near the cross flow fan 20, that is, on the side near the refrigerant outlet 56, and relatively on the side far from the cross flow fan 20, that is, on the side near the refrigerant inlet 55. In addition, the air flow resistance on the side close to the cross flow fan 20 in the parallel flow type heat exchanger 50 where the wind speed tends to be fast becomes relatively large, and conversely the wind speed tends to be slow. Since the air flow resistance is relatively small on the side far from the air, the deviation of the wind speed distribution is corrected, and the overall heat exchange efficiency is improved.

  FIG. 6 shows a second modified embodiment of the second embodiment. In the second modified embodiment, the corrugated fins 54 are removed from the first modified embodiment to form finless. In the second modified embodiment, the interval between the flat tubes 52 is exclusively wide, that is, the interval between the flat tubes 52 is relatively narrow on the side close to the cross flow fan 20 and relatively wide on the far side. In the parallel flow type heat exchanger 50, the air flow resistance on the side close to the cross flow fan 20 where the wind speed tends to be high is relatively increased, and conversely, the air flow is on the side far from the cross flow fan 20 where the wind speed tends to be slow. The resistance is made relatively small to correct the bias in the wind speed distribution, improving the overall heat exchange efficiency.

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

  The present invention is widely applicable to indoor units of air conditioners.

Sectional drawing which shows schematic structure of 1st Embodiment of an air conditioner indoor unit Schematic schematic block diagram of the heat exchanger unit according to the first embodiment The schematic schematic block diagram of the heat exchanger unit which concerns on the deformation | transformation aspect of 1st Embodiment. Schematic schematic block diagram of a heat exchanger unit according to the second embodiment Typical schematic block diagram of the heat exchanger unit which concerns on the 1st deformation | transformation aspect of 2nd Embodiment. Typical schematic block diagram of the heat exchanger unit which concerns on the 2nd deformation | transformation aspect of 2nd Embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Indoor unit 10 Housing | casing 11 Base 12 Outlet 13 Inlet 20 Cross flow fan 21 Fan casing U1, U2 Heat exchanger unit 30 Parallel flow type heat exchanger 31 Upper header pipe 32 Lower header pipe 33 Flat tube 34 Refrigerant passage 35 Corrugated fin 40 Fin and tube type heat exchanger 41 Fin 42 Tube 43 Refrigerant passage 50 Parallel flow type heat exchanger 51L Left header pipe 51R Right header pipe 52 Flat tube 53 Refrigerant passage 54 Corrugated fin

Claims (6)

  A vertically flat casing having a blower outlet on the front surface and a suction port on the upper surface, a cross flow fan for forming a blown air flow disposed inside the blower outlet, and behind the cross flow fan, the suction A parallel flow type heat exchanger disposed at a position below the mouth, wherein the parallel flow type heat exchanger is in an inclined state in which the cross low fan side is high, and within a fan casing vertical width range of the cross flow fan. An indoor unit of an air conditioner characterized by being arranged in   The density of the fins arranged between the flat tubes of the parallel flow type heat exchanger is relatively dense on the side close to the cross flow fan and relatively sparse on the far side. The indoor unit of the air conditioner described in 1.   The flat tubes of the parallel flow type heat exchanger are parallel to the axis of the cross flow fan, and the interval between the flat tubes is relatively narrow on the side close to the cross flow fan, and relatively on the far side. The indoor unit for an air conditioner according to claim 1 or 2, wherein the indoor unit is widened.   The fin-and-tube type heat exchanger is arrange | positioned in the airflow which passes the said parallel flow type heat exchanger and goes to the said cross flow fan, The any one of Claim 1 to 3 characterized by the above-mentioned. Air conditioner indoor unit.   The air conditioner indoor unit according to claim 4, wherein during cooling, the refrigerant flows through the fin-and-tube type heat exchanger and then flows into the parallel flow type heat exchanger.   6. The air conditioner according to claim 5, wherein during cooling, the refrigerant flows into a lower header pipe of the parallel flow type heat exchanger from a refrigerant outlet provided at a lower portion of the fin and tube type heat exchanger. Indoor unit.

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