JP2005214529A - Air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioner capable of designing a thin indoor machine by making arrangement of a heat exchanger proper and providing stable air conditioning capability. <P>SOLUTION: The heat exchanger 3 has a first heat exchanger 21 positioned on a front side of a cross flow fan 4 and arranged along the vertical direction and a second heat exchanger 22 which is arranged on an upper side of the first heat exchanger 21 and whose upper end side is backward inclined. Thickness T1 in the forward and backward directions of the first heat exchanger 21 is made thinner than thickness T2 in the forward and backward directions of the second heat exchanger 22. An air flow downstream end 23a on an upper end face 23 of the first heat exchanger 21 and an air flow downstream end 24a on a lower end face 24 of the second heat exchanger 22 are arranged in close proximity. An angle θ formed by a perpendicular M lowered into the first heat exchanger 21 from the axis 0 of the cross flow fan 4 and a line segment N connecting the axis 0 with a close proximity part of the first heat exchanger 21 and the second heat exchanger 22 is made 20 degrees or less. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an air conditioner.

  In recent years, air conditioners tend to make the indoor units thinner. Therefore, conventionally, in an air conditioner including an indoor unit having a crossflow fan and a heat exchanger arranged on the windward side around the crossflow fan, the crossflow fan front corresponding portion of the heat exchanger is thinned. Yes (see, for example, Patent Document 1).

That is, the indoor unit of the air conditioner described in Patent Document 1 houses a cross flow fan 51, a heat exchanger 52 disposed on the windward side of the cross flow fan 51, and these as shown in FIG. A casing 53. And the heat exchanger 52 was arrange | positioned so that an upper end side might incline back, The heat exchanger tube 54 of the lower part side was made into 1 row. Thus, the thickness of the casing 53 is reduced by reducing the thickness in the front-rear direction.
JP 61-59126 A (FIG. 1)

  In this case, by making the heat transfer tubes 54 thin in a row at the lower end portion of the heat exchanger 52, the ventilation resistance is reduced at this lower end portion (the overall air volume is improved), but the overall wind speed distribution is unbalanced. The air conditioning capability (cooling / heating capability) may be reduced. In addition, by inclining the heat exchanger 52, dew condensation water may drop from the heat exchanger 52 to the cross flow fan 51, and the moisture may be scattered indoors. Further, there is a range in which the distance between the heat exchanger 52 and the cross flow fan 51 is extremely small, which may increase noise.

  Moreover, the entire heat exchanger 52 is inclined, and the lower end of the heat exchanger 52 protrudes forward, which cannot be said to be the best in reducing the thickness. That is, in order to reduce the thickness, the heat exchanger is separated into a lower heat exchanger arranged along the vertical direction and an upper heat exchanger inclined above the lower heat exchanger. preferable. However, when an inclined upper heat exchanger is disposed on the lower heat exchanger, the upstream end of the air flow at the lower end surface of the upper heat exchanger may be lower depending on the inclination angle of the upper heat exchanger. There is a possibility that it protrudes larger than the side heat exchanger and hinders thinning. Further, when the dimension between the cross flow fan 51 and the lower heat exchanger is reduced, the noise is increased. When this dimension is increased to suppress the noise, the thickness of the entire indoor unit is increased.

  The present invention has been made to solve the above-mentioned conventional drawbacks, and its object is to make the indoor unit thinner by optimizing the arrangement of the heat exchangers and to exhibit stable air-conditioning capability. An object of the present invention is to provide an air conditioner capable of performing the above-described operation.

  Accordingly, an air conditioner according to a first aspect of the present invention is an air conditioner including an indoor unit 1 having a cross flow fan 4 and a heat exchanger 3 disposed on the windward side around the cross flow fan 4. Is located on the front side of the cross-flow fan 4 and disposed in the vertical direction, and is disposed on the upper side of the first heat exchanger 21 and its upper end side is inclined rearward. The first heat exchanger 21 has a thickness T1 in the front-rear direction that is smaller than the thickness T2 in the front-rear direction of the second heat exchanger 22, and the top of the first heat exchanger 21. The air flow downstream end 23a of the end face 23 and the air flow downstream end 24a of the lower end face 24 of the second heat exchanger 22 are arranged close to each other, and the axial center O of the cross-flow fan 4 is moved to the first heat exchanger 21. The lowered perpendicular M, the axis O, the first heat exchanger 21 and the second heat exchanger 22 The angle formed by the line segment N theta connecting the contact portion is characterized in that it has a 20 degrees or less.

  In the air conditioner of claim 1, the air flow downstream end 24 a of the lower end surface 24 of the second heat exchanger 22 is close to the air flow downstream end 23 a of the upper end surface 23 of the first heat exchanger 21. The second heat exchanger 22 is placed on the first heat exchanger 21, and the foremost position of the second heat exchanger 22 is the air flow upstream end 24 b of the lower end surface 24 of the second heat exchanger 22. In this case, because of the necessity of suppressing the generation of noise, the distance L1 between the crossflow fan 4 and the first heat exchanger 21 and the distance L2 between the crossflow fan 4 and the second heat exchanger 22 are set. Preferably they are equal. In this state, a perpendicular line M dropped from the axial center O of the cross flow fan 4 to the first heat exchanger 21 and the proximity of the axial center O, the first heat exchanger 21, and the second heat exchanger 22. When the angle θ formed with the connecting line segment N is changed, the inclination angle α (inclination angle with respect to the horizontal plane) of the second heat exchanger 22 changes. That is, if the angle θ between the perpendicular line M and the line segment N is 0 degree, the inclination angle α of the second heat exchanger 22 is increased to approach 90 °, and the second heat exchanger 22 The foremost position advances, and the thickness in the front-rear direction of the indoor unit 1 increases. In addition, when the inclination angle α of the second heat exchanger 22 is reduced, the foremost position of the second heat exchanger 22 (the air flow upstream end 24b on the lower end surface of the second heat exchanger 22) is the second heat exchanger. The foremost position moves backward on the circular arc around the air flow downstream end 24a of the lower end surface of the front end 22a. For this reason, when the inclination angle α of the second heat exchanger 22 is reduced and the second heat exchanger 22 is laid down, the projecting dimension L from the axial center O of the cross flow fan 4 to the foremost position of the heat exchanger is reduced. be able to. However, when the second heat exchanger 22 is laid in this manner, the dew condensation water easily drops from the second heat exchanger 22 to the crossflow fan 4. For this reason, it is necessary to set the inclination angle α of the second heat exchanger 22 so that the condensed water does not easily drop on the cross-flow fan 4, and the angle θ is set to 20 degrees or less from the inclination angle α. Is preferred. That is, if the angle θ is 20 degrees or less, the projecting dimension L from the axial center O of the crossflow fan 4 to the foremost position of the heat exchanger 3 can be set small, and the second heat exchanger 22 The second heat exchanger 22 is inclined at an angle at which the dew condensation water is difficult to drop onto the crossflow fan 4.

  The air conditioner according to claim 2 is characterized in that an inclination angle α of the heat exchanger 3 to the fan side of the second heat exchanger 22 is 60 degrees or more.

  In the air conditioner according to the second aspect, the inclination angle α toward the fan side of the second heat exchanger 22 is set to 60 degrees or more. Therefore, the second heat exchanger 22 is close to an upright state, and dew condensation water is generated. It becomes difficult to drip onto the crossflow fan 4.

  In the air conditioner according to claim 3, the heat exchanger 3 includes a front heat exchanger 10 having the first heat exchanger 21 and a second heat exchanger 22, and the second heat exchanger 22. The rear surface side heat exchanger 11 configured in a substantially inverted V shape is provided, and the inclination angle α1 of the rear surface side heat exchanger 11 to the fan side is set to 60 degrees or more.

  In the air conditioner according to the third aspect, the inclination angle α1 to the fan side of the rear surface side heat exchanger 11 is set to 60 degrees or more. Therefore, the rear surface side heat exchanger 11 is close to an upright state, and dew condensation water is generated. It becomes difficult to drip onto the crossflow fan 4.

  The air conditioner according to claim 4 is characterized in that an upstream recess 25 formed by notching or bending is provided on the upstream side of the air flow at the lower end of the second heat exchanger 22.

  In the air conditioner according to the fourth aspect, since the recess 25 is provided on the upstream side of the air flow at the lower end of the second heat exchanger 22, the front of the heat exchanger from the axis O of the cross flow fan 4 is accordingly provided. The projecting dimension L to the position can be further reduced.

  The air conditioner according to claim 5 is characterized in that a downstream recess 34 formed by notching or bending is provided on the downstream side of the air flow at the lower end of the second heat exchanger 22.

  In the air conditioner according to claim 5, even if the dew condensation forms water droplets at the lower end of the second heat exchanger 22, a dent is formed on the downstream side of the air flow at the lower end of the second heat exchanger 22. Since 34 is provided, the center of gravity of the water droplet is located on the upstream side, so that it is possible to prevent the water droplet from dropping on the side of the cross flow fan 4.

  The air conditioner according to claim 6, wherein the first heat exchanger 21 and the second heat exchanger 22 are provided with a plurality of fins each provided with slits 26 and 30 for increasing ventilation resistance per unit width of air passing therethrough. 21a and 22a, the ventilation resistance of the first heat exchanger 21 is increased as compared with the second heat exchanger 22.

  In the air conditioner of the sixth aspect, the front-rear direction thickness T1 of the first heat exchanger 21 is smaller than the front-rear direction thickness T2 of the second heat exchanger 22, but the ventilation resistance of the first heat exchanger 21 Is larger than the ventilation resistance of the second heat exchanger 22. This is because the thickness T1 of the first heat exchanger 21 is smaller than the thickness T2 of the second heat exchanger 22, so that the first heat exchanger 21 and the second heat exchanger 22 have the same fin resistance. For example, since the flow velocity of the air passing through the first heat exchanger 21 is faster (higher), the first air exchanger 21 has a ventilation resistance higher than that of the second heat exchanger 22, so that the first The air volume of the heat exchanger 21 is reduced so that the overall air volume balance of the front side heat exchanger 10 is achieved. Thereby, the fall of the air conditioning capability by having made it thin can be prevented.

  In the air conditioner of claim 7, the first heat exchanger 21 and the second heat exchanger 22 have heat transfer tubes 21b and 22b, respectively, and the heat transfer tube 21b and the second heat exchanger of the first heat exchanger 21. The space dimension P1 between the heat transfer tubes 21b and 22b in the portion close to the 22 heat transfer tubes 22b is smaller than the space size P2 between the heat transfer tubes 21b and 22b in the other portions.

  In the air conditioner according to the seventh aspect, since the air flow is dense between the upper end portion of the first heat exchanger 21 and the lower end portion of the second heat exchanger 22, the heat transfer tube of the first heat exchanger 21. By making the interval dimension P1 of these heat transfer tubes 21b, 22b in the portion where 21b and the heat transfer tube 22b of the second heat exchanger 22 are close to each other smaller than the interval size P2 of the heat transfer tubes 21b, 22b in other portions The heat transfer tubes 21b and 22b can be arranged in a portion where the air flow is dense.

  According to the air conditioner of the first aspect, by setting the inclination angle to 20 degrees or less, the projecting dimension from the axial center of the cross flow fan to the foremost position of the heat exchanger can be set small. Thereby, the thickness of the casing of the indoor unit in which the heat exchanger is housed can be reduced, and the indoor unit can be made compact. In addition, since the second heat exchanger is inclined at an appropriate angle so as not to sleep too much, it is possible to prevent a decrease in reliability as the heat exchanger 3 and to exhibit a stable air conditioning capability, Condensed water is less likely to drip from the second heat exchanger to the crossflow fan.

  According to the air conditioner of claim 2, the second heat exchanger can be set to an angle at which the second heat exchanger does not sleep too much as the inclination angle of the second heat exchanger. Reliability of dripping prevention (dew drop prevention) is improved.

  According to the air conditioner of claim 3, the rear side heat exchanger is close to an upright state, and the reliability of preventing dripping water from the rear side heat exchanger onto the cross-flow fan (prevention of dew drop) is ensured. improves.

  According to the air conditioner of the fourth aspect, the projecting dimension from the axial center of the cross-flow fan to the foremost position of the heat exchanger can be further reduced, and further downsizing of the indoor unit can be achieved.

  According to the air conditioner of the fifth aspect, even if the dew condensation forms water droplets at the lower end of the second heat exchanger, the gravity center of the water droplet is located on the upstream side, Dropping of water droplets can be prevented. Thereby, scattering of moisture into the room can be avoided.

  According to the air conditioner of claim 6, the front-rear direction thickness of the first heat exchanger is made smaller than the front-rear direction thickness of the second heat exchanger, but the overall air volume balance of the front-side heat exchanger 10 is achieved. Can do. As a result, a decrease in the capacity of the front heat exchanger 10 can be prevented, and a stable air conditioning operation (cooling / heating operation) can be performed.

  According to the air conditioner of the seventh aspect, the heat transfer tube can be arranged in a portion where the air flow is dense, efficient heat exchange can be performed, and the economy is excellent.

  Next, a specific embodiment of the air conditioner of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a cross-sectional view of an indoor unit of an air conditioner. This indoor unit 1 constitutes this air conditioner with an outdoor unit (not shown). The indoor unit 1 has a casing 2 provided with a heat exchanger 3, a cross flow fan (cross flow fan) 4, and the like. The casing 2 includes a casing body 5, a front grill 6 attached to the front surface of the casing body 5, a front panel 7 attached to the front surface of the front grill 6, and the like, and sucks into the front grill 6 and the front panel 7. Mouth 8 is provided. The heat exchanger 2 has a substantially inverted V shape, and has a front side heat exchanger 10 and a rear side heat exchanger 11, and the front side heat exchanger 10 and the rear side heat exchanger. 11, the cross flow fan 4 is disposed between the two.

  A front wall 12 and a rear wall 13 are provided in the casing 2 to form an air blowing path 14. The rear wall 13 is formed by a back scroll 15 and a rear casing 16 that is provided continuously from the tip of the back scroll 15. Further, the front wall 12 is formed by a front casing 17, a sub-wall 18 connected to the front casing 17, and the like. Thus, the air outlet 20 of the air outlet 14 is formed by the front end 12 a of the front wall 12 and the front end 13 a of the rear wall 13. The air outlet 20 is provided with a louver (not shown) for changing the direction of the blown air.

  By the way, the front-side heat exchanger 10 of the heat exchanger 3 is located on the front side of the cross-flow fan 4 and is disposed along the vertical direction, and the first heat exchanger 21 includes It has the 2nd heat exchanger 22 arrange | positioned above and the upper end side inclines back. At this time, the air flow downstream end (fan side edge) 24a of the lower end surface 24 of the second heat exchanger 22 and the air flow downstream end (fan side edge) 23a of the upper end surface 23 of the first heat exchanger 21 Are placed close together. In this example, the air flow downstream end 24a of the lower end surface 24 and the air flow downstream end 23a of the upper end surface 23 are abutted.

  Each of the first heat exchanger 21 and the second heat exchanger 22 is a cross fin tube type heat exchanger, and has a plurality of thin plate-like fins 21a,. And a plurality of heat transfer tubes 21b, 22b, which pass through the fins 21a, 22a,. Each of the heat transfer tubes 21b,..., 22b,... Is connected to each other by a substantially U-shaped connecting tube (not shown), meandering through the fins 21a,. A refrigerant passage is formed. The rear side heat exchanger 11 is also a cross fin tube type heat exchanger, and penetrates through a plurality of thin plate-like fins 11a arranged at predetermined intervals, and these fins 11a. Are provided with a plurality of heat transfer tubes 11b..., Each of the heat transfer tubes 11b... Being connected by a substantially U-shaped connection tube (not shown) and penetrating through the fins 11a. A meandering refrigerant passage is formed.

  The thickness (front-rear direction thickness) T1 of the first heat exchanger 21 is set smaller than the thickness (front-rear direction thickness) T2 of the second heat exchanger 22. In this case, the thickness T1 in the front-rear direction of the first heat exchanger 21 is approximately half of the thickness T2 in the front-rear direction of the second heat exchanger 22. Further, in the first heat exchanger 21, a plurality of heat transfer tubes 21b are arranged in a single row along the vertical direction, but in the second heat exchanger 22, the plurality of heat transfer tubes 22b. Two rows are arranged along the direction.

  Next, an important gain amount (gain amount from the maximum protrusion position K1 of the second heat exchanger 22) for reducing the thickness of the indoor unit 1 will be discussed with reference to FIG. In this case, the distance L2 between the crossflow fan 4 and the second heat exchanger 22 is made equal to the distance L1 between the crossflow fan 4 and the first heat exchanger 21 because of the necessity of suppressing the generation of noise. Is preferred. For this reason, as shown in FIG. 8, the perpendicular line M dropped from the axial center O of the crossflow fan 4 to the first heat exchanger 21, the axial center O, the first heat exchanger 21, and the second heat exchanger 22, If the angle θ formed by the line segment N connecting the adjacent portion (in this embodiment, the butting portion) is changed, the inclination angle α of the second heat exchanger 22 (inclination angle with respect to the horizontal plane on the side of the cross-flow fan 4) ) Will change. In this case, if the angle θ between the perpendicular line M and the line segment N is 0 degree, the inclination angle α is 90 degrees, and the second heat exchanger 22 is placed on the upper end surface 23 of the first heat exchanger 21. It will be in the state in which the lower end surface 24 of this was mounted. This state is a state in which the upstream end 24b of the lower end surface 24 of the second heat exchanger 22 protrudes forward to the maximum. And if the said angle (theta) is increased from this state, the 2nd heat exchanger 22 will fall in the upper end side back, and the inclination angle (alpha) will become small.

  That is, as the angle θ is increased from 0, the upstream end 24b of the lower end surface 24 of the second heat exchanger 22 moves on the circular arc locus K, and the heat exchanger from the axis O of the crossflow fan 4 is moved. The projecting dimension L up to the forefront position 3 is reduced. That is, if the angle θ is increased from 0, the gain amount G from the maximum protrusion position K1 of the second heat exchanger 22 increases. The gain amount G can be obtained from the following equation (1). At this time, the thickness (front-rear direction thickness) of the first heat exchanger 21 is LP, and the thickness (front-rear direction thickness) of the second heat exchanger 22 is 2 LP. Furthermore, since the distance L1 between the crossflow fan 4 and the first heat exchanger 21 is substantially equal to the distance L2 between the crossflow fan 4 and the second heat exchanger 22, β = 2θ Become. Here, β is an angle formed by the upper end surface 23 of the first heat exchanger 21 and the lower end surface 24 of the second heat exchanger 22.

  When the angle θ is increased, the gain amount G can be increased as shown in FIG. However, as the gain amount G increases, the tilt angle α decreases. If the inclination angle α is small, the second heat exchanger 22 is greatly laid down, so that the dew condensation water easily drops from the second heat exchanger 22 to the cross-flow fan 4. For this reason, if the inclination angle (for example, 50 degree | times) of the 2nd heat exchanger 22 is set so that it may become the inclination which a dew condensation water does not dripping to the crossflow fan 4 easily, the said angle (theta) can be determined. That is, since the inclination angle α can be expressed by (90−2θ), if α is 50 degrees, 50 = (90−2θ), and the angle θ is 20 degrees. For this reason, when aiming at prevention of dripping of condensed water, it is preferable to set this angle θ to 20 degrees or less. Thus, if the angle θ is 20 degrees or less, an appropriate gain amount G can be obtained, and the projecting dimension L from the axial center O of the crossflow fan 4 to the forefront position of the heat exchanger 3 can be reduced. Moreover, the inclination angle α is such that the condensation water can be prevented from dripping.

  In addition, the height dimension h from the axis O of the cross flow fan 4 to the upper end surface 23 of the first heat exchanger 21 can be obtained as in the following Expression 2 using the angle θ and the like. In Equation 2, L1 indicates the distance between the crossflow fan 4 and the first heat exchanger 21, and R indicates the radial dimension of the crossflow fan 4. In this case, for example, when the angle θ is set so that the height dimension is about 18 to 19 mm when L1 is about 10 mm, the gain amount G can be about 6 mm.

  Moreover, in order to prevent dripping (dew drop) of the dew condensation water, it is preferable that the inclination angle α is set to 60 degrees or more to approach the standing state. Thus, if it is 60 degrees or more, L2 is not the same as L1, but even in such a case, there is almost no problem with noise, and the reliability of prevention of dew drop can be improved. Further, it is possible to stably avoid the dew condensation water from the indoor unit 1.

  By the way, in the heat exchanger 3 shown in FIG. 1, the upstream side recessed part 25 formed by notching or bending is formed in the air flow upstream in the lower end part of the 2nd heat exchanger 22. FIG. As a result, the foremost position of the second heat exchanger 22 is moved backward as the position A. That is, if this upstream side dent 25 is not provided, the foremost position is the position B as indicated by the phantom line.

  Further, as shown in FIG. 1, the rear heat exchanger 11 is inclined so as to face the axial fan 4, but the inclination angle α1 is set to 60 degrees or more. Thereby, it is possible to prevent the condensed water from dripping from the rear surface side heat exchanger 11 to the cross flow fan 4. In this case, if the height dimension of the first heat exchanger 21 is reduced by reducing the angle θ, the rear side heat exchanger 11 is displaced with its lower end as a fulcrum, and this rear side heat exchange is performed. The inclination angle α1 of the vessel 11 becomes small. On the contrary, if the height of the first heat exchanger 21 is increased by increasing the angle θ, the angle of the inclination angle α1 of the rear surface side heat exchanger 11 is ensured to be 60 or more. Therefore, the height of the indoor unit 1 is increased. For this reason, when the inclination angle α1 is set to 60 or more, the inclination angle α1 is set in consideration of the angle θ and the inclination angle α.

  By the way, as shown in FIGS. 2-4, the 1st heat exchanger 21 is provided with the slit 26 ... for increasing the ventilation resistance per unit width with the passing air. In this case, six parallel vertical slits 26 are provided between the through holes through which the heat transfer tubes 21b, 21b disposed above and below pass, and the first vertical slit 26a and the second vertical slit are provided. 26b, the remaining portion 27a between the third vertical slit 26c and the fourth vertical slit 26d, and the remaining portion between the fifth vertical slit 26e and the sixth vertical slit 26f. 27e is projected to one surface 28 side, and the remaining portion 27b between the second vertical slit 26b and the third vertical slit 26c, and between the fourth vertical slit 26d and the fifth vertical slit 26e. The remaining portion 27d protrudes toward the other surface 29 side.

  Further, as shown in FIGS. 5 to 7, the second heat exchanger 22 is also increased in ventilation resistance (fin resistance) per unit width of air passing through (the length dimension of the heat exchanger in the ventilation direction). Slits 30 are provided for the purpose. In this case, six parallel vertical slits 30... Are provided between the through holes through which the heat transfer tubes 22b, 22b are vertically disposed, and the first vertical slit 30a and the second vertical slit. The remaining portion 31a between 30b, the third vertical slit 30c, the remaining portion 31c between the fourth vertical slit 30d, the remaining portion between the fifth vertical slit 30e and the sixth vertical slit 30f 31e is protruded to the one surface 32 side. The remaining portion 27b between the second up-down direction slit 26b and the third up-down direction slit 26c, and the remaining portion 27d between the fourth up-down direction slit 26d and the fifth up-down direction slit 26e are left in a planar state. Is maintained. As a result, the ventilation resistance per unit width of the first heat exchanger 21 is made larger than the ventilation resistance of the second heat exchanger 22.

  By the way, since thickness T1 of the 1st heat exchanger 21 was made smaller than thickness T2 of the 2nd heat exchanger 22, if the 1st heat exchanger 21 and the 2nd heat exchanger 22 are the same fin resistance, The flow rate of air passing through the first heat exchanger 21 becomes faster (higher) (about half of the flow rate of air passing through the second heat exchanger 22), and the air volume of the first heat exchanger 2 increases. Thus, when the air volume increases (the air volume split increases), the total heat quantity decreases (capacity decreases). For this reason, by making the ventilation resistance of the 1st heat exchanger 21 larger than the ventilation resistance of the 2nd heat exchanger 22, the air volume of the 1st heat exchanger 21 is decreased, and this front side heat exchanger 10's The overall air volume is balanced. As a result, a decrease in the capacity of the front-side heat exchanger 10 is prevented.

  Further, as shown in FIG. 1, the interval dimension P1 between the uppermost heat transfer tube 21b of the first heat exchanger 21 and the lowermost heat transfer tube 22b of the second heat exchanger 22 is set to the other heat transfer tube 21b. , 22b is set to be smaller than the interval dimension P2. That is, since air flows relatively densely between the upper end portion of the first heat exchanger 21 and the lower end portion of the second heat exchanger 22, the heat transfer tubes 21b and 22b are arranged in the densely flowing range. ing.

  The air conditioner can perform a cooling operation, a heating operation, a reheat dry operation, and the like. For example, in the cooling operation, an indoor unit heat exchanger (not shown) functions as a condenser, and the heat exchanger 3 of the indoor unit 1 functions as an evaporator to cool the room. In the heating operation, the heat exchanger 3 of the indoor unit 1 is caused to function as a condenser, and the indoor unit is heated by causing the heat exchanger of the outdoor unit to function as an evaporator. In the reheat dry operation, the front-side heat exchanger 10 of the heat exchanger 3 of the indoor unit 1 functions as a condenser, and the rear-side heat exchanger 11 of the heat exchanger 3 functions as an evaporator. Thus, after the indoor air is cooled and dehumidified by the rear side heat exchanger 11 functioning as an evaporator, it is heated again by the front side heat exchanger 10 functioning as a condenser and returned to the room. Dry operation is performed.

  In the air conditioner, the perpendicular line M dropped from the axial center O of the cross flow fan 4 to the first heat exchanger 21, and the proximity of the axial center O, the first heat exchanger 21, and the second heat exchanger 22. Since the angle θ formed by the line segment N connecting the two and N is set to 20 degrees or less, the projecting dimension L from the axis O of the crossflow fan 4 to the forefront position of the heat exchanger 3 can be set small. As a result, the thickness of the casing of the indoor unit 1 in which the heat exchanger 3 is housed can be reduced, and the indoor unit 1 can be made compact. In addition, since the second heat exchanger 22 is inclined at an appropriate angle so as not to sleep too much, it is possible to prevent a decrease in reliability as the heat exchanger 3 and to exhibit a stable air conditioning capability. The condensed water is less likely to drop from the second heat exchanger 22 to the cross flow fan 4. Furthermore, the distance between the crossflow fan 4 and the second heat exchanger 22 can be maintained substantially the same as the distance between the crossflow fan 4 and the first heat exchanger 21, and a quiet operation is possible.

  Moreover, since the recessed part 25 was provided in the air flow upstream in the lower end part of the 2nd heat exchanger 22, the protrusion dimension L to the forefront position of the heat exchanger 3 from the axial center O of the crossflow fan 4 is equivalent to it. Can be small. Thereby, further downsizing of the indoor unit 1 can be achieved. Note that, when the recess 25 is provided, even if a part of the fin 21a is cut out, this part is not so effective in heat exchange, and thus does not affect.

  Furthermore, although the front-rear direction thickness T1 of the first heat exchanger 21 is smaller than the front-rear direction thickness T2 of the second heat exchanger 22, the unit width of the first heat exchanger 21 is larger than that of the second heat exchanger 22. Since the perimeter ventilation resistance is increased, the overall air volume balance of the front side heat exchanger 10 can be achieved, and the deterioration of the capacity of the front side heat exchanger 10 is prevented. Thereby, the fall of the air-conditioning capability by having made it thin can be prevented, and the stable air-conditioning operation (air-conditioning operation) can be performed. Moreover, since the air flow is dense between the upper end portion of the first heat exchanger 21 and the lower end portion of the second heat exchanger 22, the heat transfer tube 21 b of the first heat exchanger 21 and the second heat exchanger 22. By making the interval dimension P1 of the heat transfer tubes 21b, 22b in the portion close to the heat transfer tube 22b smaller than the interval size P2 of the heat transfer tubes 21b, 22b in the other portions, the flow of this air becomes dense. The heat transfer tubes 21b and 22b can be arranged at a certain portion. Thereby, efficient heat exchange can be performed.

  Next, FIG. 10 shows another embodiment. In this case, the upstream recess 25 of the second heat exchanger 22 is made larger than the upstream recess 25 of the second heat exchanger 22 shown in FIG. In the second heat exchanger 22, the number of front heat transfer tubes 22b is reduced. In addition, the other structure is the same as that of the air conditioning apparatus shown in the said FIG.

  FIG. 11 shows another embodiment. In this case, a downstream recess 34 formed by notching or bending is provided on the downstream side of the air flow at the lower end of the second heat exchanger 22. The downstream recess 34 is triangular in a side view. That is, when the condensed water adhering to the second heat exchanger 22 accumulates as water droplets W due to condensation, by providing the downstream-side recess 34, the water droplets W are reduced as shown in FIG. The center of gravity moves forward, so that dripping onto the side flow fan 4 can be prevented.

  On the other hand, if the downstream recess 34 is not provided, due to manufacturing variations such as assembly errors, the air flow downstream end 24a of the lower end surface 24 of the second heat exchanger 22 becomes less as shown in FIG. The first heat exchanger 21 may be located on the inner side (cross flow fan 4 side) of the air flow downstream end 23a of the upper end surface 23. In such a case, the condensed water adhering to the second heat exchanger 22 is accumulated as water droplets W at the downstream end 24a of the air flow due to condensation, and the water droplets W are dropped on the lateral flow fan 4 side. The moisture is scattered from the fan 4 into the room through the air outlet 20 of the air outlet 14. However, if the downstream recess 34 is provided, even if the lower end of the second heat exchanger 22 is located slightly inside (cross flow fan 4 side) from the normal position due to manufacturing variation or the like, Since the center of gravity of the water droplet W moves forward, it is possible to prevent the water droplet W from dropping on the side of the cross flow fan 4. For this reason, when assembling the 2nd heat exchanger 22, it is not necessary to assemble with accuracy and the operation becomes easy. In addition, the lower end part of the 1st heat exchanger 21 has entered into the drain pan (illustration omitted), and the dew condensation water of the 1st heat exchanger 21 or the 2nd heat exchanger 22 flows into this drain pan, and is outside. Is discharged.

  By the way, when forming the front side heat exchanger 10 and the rear side heat exchanger 11, as shown to Fig.13 (a), the 2nd heat exchanger 22 and the rear side heat exchanger of the front side heat exchanger 10 are shown. 11 is first formed, and the heat exchanger component 36 is cut and assembled. In other words, the second heat exchanger is cut at a notch recess 37 provided at a portion where the heat exchanger component 36 is separated, along a cutting line 38 having a predetermined inclination angle with respect to the heat exchanger component 36. 22 and the rear surface side heat exchanger 11 are formed, and fins are bent to bend the cut end portion 39 of the rear surface side heat exchanger 11. Then, the cut surface 40 of the second heat exchanger 22 and the end surface 41 on the front side heat exchanger 10 side of the inner surface of the rear side heat exchanger 11 are assembled so as to face each other with a slight clearance (not shown). . That is, as shown in FIG. 13B, since the recess 42 is formed in the portion where the fin is tilted, a seal member (not shown) is attached to the recess 42 to ensure the clearance. The clearance is, for example, about 2 mm.

  As described above, if fins are not tilted at the cut end portion 39 of the rear surface side heat exchanger 11, this portion of the rear surface side heat exchanger 11 is part of the second heat exchanger 22 of the front surface side heat exchanger 10. Will come into contact. Such contact may cause noise (fin sound) due to a temperature difference that occurs during defrosting or the like, but the occurrence of such noise can be prevented by tilting the fin. Further, when a prefilter (not shown) is disposed on the front surface side of the heat exchanger 3, the prefilter can be prevented from being caught at this portion by tilting the fins. In addition, in this case, since a slight clearance is provided between the inner surface of the rear heat exchanger 11 and the end surface 41 on the front heat exchanger 10 side by disposing the seal member, it is possible to perform defrosting or the like. It is possible to prevent the generation of fin sounds due to the difference in expansion.

  Although specific embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the present invention. For example, the number of heat transfer tubes 21b, 22b of each heat exchanger 21, 22 and the arrangement pitch can be arbitrarily changed. Further, in order to reduce the thickness, it can be said that it is preferable to provide the upstream-side dent 25. However, even if the upstream-side dent 25 is not provided, the air conditioner can sufficiently reduce the thickness of the indoor unit 1. . And when forming the upstream dent 25, it is sufficient if the upstream end 24b (corner part) shown in FIG. 8 and the like is omitted and the foremost position of the second heat exchanger 22 is moved backward. The shape in the side view is not limited to that shown in FIG. That is, although the upstream side recessed part 25 in FIG.1, FIG.10 etc. forms side view substantially trapezoid shape, it may be made into triangular shape by side view, for example. Further, the case where the downstream recess 34 is provided is not limited to the shape shown in the figure, and the center of gravity of the water droplet W formed at the lower end of the second heat exchanger 22 moves to the upstream side so that the cross current flows. What is necessary is just to prevent this water droplet W from dripping to the fan 4 side. Furthermore, the number of slits 26 and 30 of each heat exchanger 21 and 22 can be changed. In FIG. 8, the thickness T2 in the front-rear direction of the second heat exchanger 22 is twice the thickness T1 in the front-rear direction of the first heat exchanger 21, but it is not limited to this. Furthermore, in the said embodiment, although the air flow downstream end 23a of the upper end surface 23 of the 1st heat exchanger 21 and the air flow downstream end 24a of the lower end surface 24 of the 2nd heat exchanger 22 are faced | matched, air flow The downstream end 23a and the air flow downstream end 24a may be arranged close to each other without abutting each other. In this case, the air flow downstream end 24a of the second heat exchanger 22 is shifted forward or backward relative to the air flow downstream end 23a of the first heat exchanger 21 even if the interval is the vertical interval. It may be an interval in the direction.

It is principal part sectional drawing which shows embodiment of the air conditioning apparatus of this invention. It is a principal part side view of the fin of the 1st heat exchanger of the said air conditioning apparatus. It is a principal part cross-sectional front view of the fin of the 1st heat exchanger of the said air conditioning apparatus. It is a principal part cross-sectional top view of the fin of the 1st heat exchanger of the said air conditioning apparatus. It is a principal part side view of the fin of the 2nd heat exchanger of the said air conditioning apparatus. It is a principal part sectional front view of the fin of the 2nd heat exchanger of the above-mentioned air harmony device. It is a principal part cross-sectional top view of the fin of the 2nd heat exchanger of the said air conditioning apparatus. It is a simplification figure showing the relation of the 1st heat exchanger of the above-mentioned air harmony device, the 2nd heat exchanger, and a cross flow fan. It is a graph which shows the relationship between the angle of the said air conditioning apparatus, and a gain amount. It is a principal part simplification figure of the other heat exchanger of the air conditioning apparatus of this invention. It is a principal part simplification figure of another heat exchanger of the air conditioning apparatus of this invention. The effect | action of the heat exchanger of the said air conditioning apparatus is shown, (a) is a principal part simplification figure when it does not have a dent part, (b) is a simplification figure when it has a dent part. The manufacturing method of the heat exchanger of an air conditioning apparatus is shown, (a) is the simplified figure before an assembly, (b) is the simplified figure after an assembly. It is a simplified sectional view of a conventional air conditioner.

Explanation of symbols

  3 .. Heat exchanger 4 .. Cross-flow fan 11 .. Rear side heat exchanger 21.. First heat exchanger 21 a. Fins 21 b Heat transfer tube 22 Second heat exchanger , 22a ·· Fins, 22b · · Heat transfer tubes, 23 ·· Upper end surface, 23a · · Air flow downstream end, 24 · · Lower end surface, 24a · · Air flow downstream end, 25 · · Upstream recess, 26 · ·・ Slit, 30 ・ ・ Slit, 34 ・ ・ Downstream recess, M ・ ・ Vertical line, N ・ ・ Line segment O ・ ・ Axis center, P1, P2 ・ ・ Distance dimensions, T1, T2

Claims (7)

  In the air conditioner including an indoor unit (1) having a cross flow fan (4) and a heat exchanger (3) arranged on the windward side around the cross flow fan (4), the heat exchanger (3) Is disposed on the front side of the cross-flow fan (4) and disposed in the vertical direction, and is disposed above the first heat exchanger (21). A second heat exchanger (22) whose upper end is inclined rearward, and the thickness (T1) of the first heat exchanger (21) in the front-rear direction thickness (T1) ( The air flow downstream end (24a) of the air flow downstream end (23a) of the upper end surface (23) of the first heat exchanger 21 and the lower end surface (24) of the second heat exchanger (22). ) In close proximity to each other, and a perpendicular (M) dropped from the axial center (O) of the cross-flow fan (4) to the first heat exchanger 21 The angle (θ) formed by the line (N) connecting the axial center (O) and the adjacent portion of the first heat exchanger (21) and the second heat exchanger (22) is set to 20 degrees or less. An air conditioner characterized by.   The air conditioner according to claim 1, wherein an inclination angle (α) of the heat exchanger (3) to the fan side of the second heat exchanger (22) is 60 degrees or more.   The heat exchanger (3) includes a front heat exchanger (10) having the first heat exchanger (21) and a second heat exchanger (22), and the second heat exchanger (22). And a rear surface side heat exchanger (11) configured in a substantially inverted V shape, and an inclination angle (α1) to the fan side of the rear surface side heat exchanger (11) is set to 60 degrees or more. The air conditioner according to claim 1 or 2.   The upstream recess (25) formed by notching or bending is provided on the upstream side of the air flow at the lower end of the second heat exchanger (22). Air conditioner.   The air conditioner according to any one of claims 1 to 4, wherein a downstream recess (34) formed by notching or bending is provided on the downstream side of the air flow at the lower end of the second heat exchanger (22). apparatus.   The first heat exchanger (21) and the second heat exchanger (22) have a plurality of fins (21a) each provided with a slit (26) (30) for increasing the ventilation resistance per unit width of the passing air. ) (22a), and the ventilation resistance of the first heat exchanger (21) is increased as compared with the second heat exchanger (22). Air conditioner. The first heat exchanger (21) and the second heat exchanger (22) have heat transfer tubes (21b) and (22b), respectively, and the heat transfer tube (21b) and the second heat of the first heat exchanger (21). The interval dimension (P1) of these heat transfer tubes (21b) and (22b) in the region where the heat transfer tube (22b) of the exchanger (22) is in close proximity is set to the interval between the heat transfer tubes (21b) and (22b) in other regions. The air conditioner according to any one of claims 1 to 6, wherein the air conditioner is smaller than a dimension (P2).