JPH10132372A - Air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make a heat exchanger compact, decrease noise and improve heat exchanging capability by making the amount of heat exchanging per unit area of the front surface of a heat exchanger in a front side larger than that of a heat exchanger in a rear side. SOLUTION: When indoor air is sucked from a front face inlet port 4 and an upper face inlet port 5 by rotating and driving a fan rotor 3 and air flows from the suction side 14 of a main body casing 19 to an outlet side 15, the air is supplied to a room again from an outlet port 13 along a scroll part 6 as air conditioned air by heat exchanging it in a heat exchanger 10. The amount of heat exchanging per unit area of the front surface of a heat exchanger 2 in a rear surface side is smaller than that of a heat exchanger 1 in a front surface side. Thus, the amount of drain water generated in the heat exchanger 2 in the rear surface side during a cooling operation is relatively small, and it is not necessary to make a drain pan 9 in the rear surface side large. As a result, the capacity of the compact heat exchanger 10 is improved without increasing and the size of the heat exchanger 10 itself and a decrease of air supply performance and the generation of abnormal noise can be prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner provided with an inverted V-shaped heat exchanger.

[0002]

2. Description of the Related Art In an air conditioner, particularly an indoor unit of a separation type air conditioner, it is required that a main body casing be made compact and thin so that a living space can be used as much as possible. Is done. However, when the main body casing is made compact, the heat exchanger must be miniaturized accordingly, and therefore, there has been a problem that the heat exchange amount of the heat exchanger is reduced and the heat exchange capacity is reduced.

In order to solve this problem, there is an air conditioner in which a heat exchanger is divided into a front side and a rear side and combined in an inverted V-shape, and a suction port is also provided on the upper surface of a main body casing. (For example, Japanese Utility Model Publication No. 57-35771)
No., Japanese Patent Application No. 7-192351). FIG. 9 is a cross-sectional view illustrating an indoor unit of a separation type air conditioner including the above-described inverted V-shaped heat exchanger. In this indoor unit, a front grille 41 having a front suction port 34 formed on the front side of a main body casing 49 is provided, and an upper grille 42 having a top suction port 35 formed on the upper surface side. A front side heat exchanger 38 is provided behind the front grille 41, and the lower end of the front side heat exchanger 38 is close to the lower part of the front grille 41, and the upper end is closer to the rear side. It is arranged to be inclined near the lower side of the upper grille 42. Further, on the back side of the front side heat exchanger 38, the rear side heat exchanger 3 whose vertical width is about 2/5 of the front side heat exchanger 38 is provided.
2 are arranged. The rear-side heat exchanger 32 is inclined so that the upper end thereof is close to the upper end of the front-side heat exchanger 38, while the lower end is positioned further rearward. The front-side heat exchanger 38 and the rear-side heat exchanger 32 are combined to form an inverted V-shaped heat exchanger 40, and the upper end of the front-side heat exchanger 38 and the upper end of the rear-side heat exchanger 32 The heat exchanger 4 whose section is the inverted V-shaped heat exchanger 4
It is the top of 0. The inverted V-shaped outside of the heat exchanger 40 is a suction side 44 in the main body casing 49, and the inside thereof is a blowout side 45. Further, a cylindrical fan rotor 33 having a rotating shaft 33a extending in a direction substantially perpendicular to the paper surface of the drawing is provided on the blowout side 45.
A tongue portion 37 provided so as to be close to the fan rotor 33 along the axial direction;
Scroll portion 36 formed so as to be smoothly connected to
The cross flow fan is constituted by the above.

When the fan rotor 33 is driven to rotate, a vortex is generated by the action of the cross-flow fan, and the vortex causes air to be sucked in from the front suction port 34 and the top suction port 35. The sucked room air further flows from the suction side 44 to the blowout side 45 of the main body casing 49, and at that time, heat is exchanged by the heat exchanger 40 to be conditioned air. The conditioned air is blown out of the outlet 43 again into the room while changing the flow direction to the front side along the scroll portion 36.

In the above air conditioner, the main body casing 49
The indoor air is sucked from both the front and upper surfaces of the heat exchanger, and the sucked indoor air is supplied to the front heat exchanger 38 and the rear heat exchanger 3.
2 is exchanged by both. Therefore, the contact area where the heat exchanger 40 comes into contact with the room air is the sum of the two heat exchangers 38 and 32. For example, the front heat exchanger 38 is connected to the rear heat exchanger 3 at the upper end.
It is almost the same as a heat exchanger having a shape extended by two. Therefore, this air conditioner can be made compact without lowering the heat exchange capacity.

[0006]

However, there is a strong demand for downsizing and high performance of the air conditioner, and the heat exchanger 40 is formed in an inverted V-shape to reduce the heat exchange capacity to some extent without lowering the heat exchange capacity. The indoor unit of the air conditioner of the above-described conventional example, which was able to achieve
There is a need to make this more powerful and compact.

[0007] In order to make the above-mentioned conventional indoor unit compact without deteriorating the heat exchange capacity, a heat exchanger 4 is required.
It is necessary to improve the capacity of the heat exchanger 40, that is, to increase the amount of heat exchange per unit front area of the heat exchanger 40. However, if the capacity of the rear heat exchanger 32 is improved in the same manner as the front heat exchanger 38, the amount of drain water generated in the rear heat exchanger 38 during the cooling operation increases.
It is necessary to enlarge the back side drain pan 39. Since the ventilation path of the rear heat exchanger 32 is formed from the upper side to the lower side, if the rear side drain pan 39 is enlarged, the rear side drain pan 39 will protrude above the ventilation path, and the ventilation performance Is reduced, and as a result, the capacity of the rear heat exchanger 32 is reduced. In addition, since the ventilation path is narrowed by the rear-side drain pan 39 having a large size, a new problem that abnormal noise is generated is caused.

The present invention has been made in order to solve the above-mentioned conventional drawbacks, and an object of the present invention is to provide an air conditioner capable of improving heat exchange capacity while achieving compactness and low noise. To provide.

[0009]

Therefore, the air conditioner of the present invention has a front heat exchanger 1 and a rear heat exchanger 2 in a main body casing 19 having suction ports 4 and 5 on the front and upper surfaces thereof. And a fan rotor 3 arranged on the downstream side of the heat exchanger 10,
In an air conditioner provided with a front side drain pan 8 arranged below the front side heat exchanger 1 and a back side drain pan 22 arranged below the back side heat exchanger 2, the air conditioner of the front side heat exchanger 1 It is characterized in that the amount of heat exchange per unit front area is larger than that of the rear heat exchanger 2.

In the air conditioner of the first aspect, the front-side heat exchanger 1 is configured so that the amount of heat exchange per unit front area is larger than that of the rear-side heat exchanger 2. Therefore,
The capacity of the heat exchanger 10 can be improved without increasing the size of the heat exchanger 10 itself, and the size can be reduced. Further, since the heat exchange amount per unit front area of the rear heat exchanger 2 is smaller than that of the front heat exchanger 1,
The amount of drain water generated in the rear heat exchanger 2 during the cooling operation is relatively small, and there is no need to increase the size of the rear drain pan 22. Therefore, the rear side drain pan 22 does not protrude above the air supply path of the rear side heat exchanger 2 to narrow the air supply path, so that it is possible to prevent the deterioration of the air supply performance and the generation of abnormal noise. By increasing the capacity of the front-side heat exchanger 1 (the amount of heat exchange per front area), the amount of drain water generated increases, and it is necessary to enlarge the front-side drain pan 8 accordingly. The side drain pan 8 is arranged below the front side heat exchanger 1, and the ventilation path is formed from the front side to the back side, so that the front side drain pan 8 is on the ventilation path of the front side heat exchanger 1. Does not protrude. Therefore, problems such as a decrease in the blowing capacity and generation of abnormal noise do not occur.

[0011] The air conditioner according to claim 2 is the heat exchanger 1.
Numeral 0 denotes a cross fin tube type heat exchanger in which the heat transfer tubes 21 are arranged in a penetrating state on a plurality of fins 17 arranged side by side, and two fins 17 of the heat exchanger 10 have two parallel fins. A plurality of slits 24 formed by raising a portion 28 sandwiched between the notches 27 on one surface side are formed, and the slits 2 in the fins 17 of the front-side heat exchanger 1 are formed.
4. The air conditioner according to claim 3, wherein the occupied area ratio of the heat exchanger is larger than that of the rear heat exchanger, and the fin of the heat exchanger is adjacent to one side of the notch. A plurality of louvers 29 formed by raising the portion 31 to be formed on one surface side are formed, and the occupied area ratio of the louvers 24 in the fins 17 of the front heat exchanger 1 is made larger than that of the front heat exchanger 2. It is characterized by.

In the air conditioners of the second and third aspects, the heat exchange amount of the front side heat exchanger 1 increases due to the improvement of the heat conductivity on the air side (fin 17).

The air conditioner according to claim 4 is characterized in that the heat exchanger 1
Reference numeral 0 denotes a cross fin tube type heat exchanger in which the heat transfer tubes 21 are arranged in a state of being penetrated by a plurality of fins 17 arranged in parallel, and the fin pitch P1 of the front side heat exchanger 1
The air conditioner according to claim 5, wherein the width W1 of the fins 17 of the front heat exchanger 1 in the air flow direction is set to be smaller than that of the rear heat exchanger 2. 2
The feature is that it is larger than that.

In the air conditioner of the fourth and fifth aspects, the front-side heat exchanger 1
Increases the amount of heat exchange.

In the air conditioner of the present invention, the heat exchanger 1
Reference numeral 0 denotes a cross-fin tube type heat exchanger in which the heat transfer tubes 21 are arranged in a plurality of fins 17 arranged side by side in a penetrating state, and the heat transfer tube pitch Pt1 of the front-side heat exchanger 1 is set.
Is smaller than the rear-side heat exchanger 2, and the air conditioner according to claim 7, wherein the plate thickness T1 of the fins 17 of the front-side heat exchanger 1 is smaller than that of the rear-side heat exchanger 2. It is characterized by being thick.

In the air conditioners according to the sixth and seventh aspects, the amount of heat exchange of the front side heat exchanger 1 increases due to the improvement of the fin efficiency of the fins 17.

The air conditioner according to claim 8 is characterized in that the heat exchanger 1
Numeral 0 denotes a cross-fin tube type heat exchanger in which the heat transfer tubes 21 are arranged in a plurality of fins 17 arranged side by side in a penetrating state, and the heat conductivity of the heat transfer tubes 21 of the front side heat exchanger 1 is set. Is higher than that of the rear heat exchanger 2, but this also increases the amount of heat exchange of the front heat exchanger 1.

In the air conditioner according to the ninth aspect, the heat exchanger 1
Reference numeral 0 denotes a cross-fin tube type heat exchanger in which the heat transfer tubes 21 are arranged in a plurality of fins 17 arranged side by side in a penetrating state, and the heat transfer tubes 21 of the heat exchanger 10 are connected to form a plurality of heat transfer tubes. The routes R1, R2, and R3 are configured, and the refrigerant from the coolant supply means is supplied by being divided from the supply ports of the plurality of routes R1, R2, and R3, and after passing through the routes R1, R2, and R3, the plurality of coolants are supplied. The number of heat transfer tubes 21 discharged from the outlets of the paths R1, R2, and R3, merged again, and returned to the refrigerant supply means, and included in the path R1 passing through the rear heat exchanger 2, Route R passing through front side heat exchanger 1
2. The number of heat transfer tubes 21 included in R3 is larger than that of R3.

In the air conditioner of the ninth aspect, the pressure loss on the refrigerant side in the paths R1 and R2 in the front side heat exchanger 1 is reduced, so that the temperature difference with the air side is increased.
The heat exchange amount of the front heat exchanger 1 increases.

[0020]

Next, specific embodiments of the air conditioner of the present invention will be described in detail with reference to the drawings. FIG. 1 is a cross-sectional view showing an application example when one embodiment of the air conditioner is applied to an indoor unit of a separation type air conditioner. In this indoor unit, similarly to the above-mentioned conventional example, a front grill 11 having a front suction port 4 formed on the front side of a main body casing 19 is provided, and a top grill having a top suction port 5 also formed on the upper side thereof. 12 are provided. 1 shown in the figure is a front-side heat exchanger. The front-side heat exchanger 1 is configured by inserting 20 refrigerant pipes 21..., And the first through first refrigerant exchangers 21. 5 divisions 1a-
It is divided into five sections 1e. Then, by bending between adjacent partition portions, it is curved so as to protrude toward the front side from the top portion to the lower portion, and the fourth partition portion 1d corresponding to the fourth counting from the top portion is positioned at the frontmost side. ing. In addition, 2 in FIG.
It is. This back side heat exchanger 2 has eight refrigerant pipes 21.
, And the first and second partitioning portions 2a, 2b are formed with the portion through which the four refrigerant pipes 21 are inserted as one partition, similarly to the front-side heat exchanger 1. The two sections 2a and 2b are bent to bend from the top to the bottom so as to protrude rearward. The tops of the heat exchangers 1 and 2 are arranged close to each other, and the heat exchangers 1 and 2 are combined with this portion as the top to form an inverted V-shaped heat exchanger 10. . The inverted V-shaped outside of the heat exchanger 10 is a suction side 14 in the main body casing 19, and the inside thereof, that is, the downstream side of the heat exchanger 10 is a blowing side 15. Further, the front upper corner portion of the main body casing 19, that is, the front grill 11 and the upper grill 1
2, a certain space is formed between the upper part of the front heat exchanger 1 and the upper part of the front heat exchanger 1. In this space, an air purifying filter 1 having an antibacterial and deodorizing action is provided.
6 are provided.

Further, a cross-flow fan constituted by a columnar fan rotor 3, a tongue 7, a scroll 6 and the like is provided on the blow-out side 15 as in the conventional example. The fan rotor 3 of the cross flow fan is arranged such that the rotation shaft 3a is located behind the fourth partition 1d of the front heat exchanger 1, and the scroll portion 6
Is formed such that the lower end side thereof is smoothly connected to the outlet 13. In addition, during the cooling operation, the tongue portion 7 receives the drain water generated in the front-side heat exchanger 1.
A drain drain pan 8 formed integrally with the heat exchanger support portion 23 receives drain water generated in the rear heat exchanger 2. It has become. Further, drain water may also be generated on the back of the scroll section 6, but this is configured to be received by the back drain pan 9.

When the fan rotor 3 shown in FIG. 1 is driven to rotate in the indoor unit configured as described above, a vortex is generated by the action of the cross flow fan, and the vortex causes the front suction port 4 and the top suction. The indoor air is sucked from the mouth 5. The sucked room air further flows from the suction side 14 to the blowout side 15 of the main body casing 19, and at that time, heat is exchanged (cooled) by the heat exchanger 10 to be conditioned air. This air-conditioned air changes its flow direction to the front side along the scroll part 6 and is
3 again blows into the room.

In the heat exchanger 10 of the indoor unit, the heat exchange capacity is improved as compared with the conventional heat exchanger by various methods described later, but the heat exchanger 1 on the front side has heat per unit front area. The exchange amount is configured to be larger than that of the rear-side heat exchanger 2. Therefore, the capacity of the heat exchanger 10 can be improved without increasing the size of the heat exchanger 10 itself, and the size can be reduced.

Further, as described above, the back side heat exchanger 2
The amount of heat exchange per unit front area of the front side heat exchanger 1
Therefore, the amount of drain water generated in the rear heat exchanger 2 during the cooling operation is relatively small, and there is no need to increase the size of the rear drain pan 9. The air flow path of the back side heat exchanger 2 is as follows.
5, that is, from the upper part of the main body casing 19 to the outlet 1
3 is formed toward the lower part, so that if the rear-side drain pan 9 disposed below the rear-side heat exchanger 2 is enlarged, the rear-side drain pan 9 will be provided so as to protrude from the air passage, and the air passage is narrowed. However, there is a problem in that the ventilation performance is lowered and abnormal noise is generated. However, in the present invention, it is not necessary to increase the size of the back side drain pan 9, and the above problem does not occur.

It is to be noted that drain water generated by improving the capacity of the front-side heat exchanger 1, that is, the amount of heat exchange per unit front area increases, and the front-side drain pan 8 may need to be enlarged. However, the front side drain pan 8 is disposed below the front side heat exchanger 1, and the blowing path is from the front side suction port 4 to the outlet side 15, and the fan rotor 3.
Therefore, the front drain pan 8 does not protrude into the air blowing path. Therefore, problems such as a reduction in the blowing capacity and generation of abnormal noise do not occur.

Next, with reference to FIGS. 2 to 8, a specific method for realizing a larger heat exchange amount per unit front area of the front heat exchanger 1 than that of the rear heat exchanger 2 will be described. explain.

FIG. 2 is a perspective view showing the structure of the heat exchanger 10. The heat exchanger 10 is composed of the front heat exchanger 1 and the rear heat exchanger 2 as described above. The configuration of each of the heat exchangers 1 and 2 is basically the same, and is a cross-fin tube type heat exchanger. is there. In this cross fin tube type heat exchanger, a plurality of fins 17 are arranged in parallel as shown in FIG.
In addition, a plurality of heat transfer tubes 21 are arranged in a penetrating state.

The front-side heat exchanger 1 includes a fin 1 having a thickness T1.
7 are arranged side by side at a fin pitch P1, and the front surface area S1
= L × H1. Here, L is the effective length of the heat exchanger, specifically, the length from the fin at one side end to the fin at the other side end. H1 is the length of the air flow suction side of the fin 17. The rear heat exchanger 2 has a thickness T
The two fins 17 are arranged side by side at a fin pitch P2,
The front surface area S2 = L × H2. H2 is the length of the fin 17 on the air flow suction side. Further, the total front area S of the heat exchanger 10 is S = S1 + S2. The total heat exchange amount of the front-side heat exchanger 1 is calculated by comparing the front-side area S1 of the front-side heat exchanger 1.
Is referred to as the amount of heat exchange per unit front area of the front heat exchanger 1, and the total heat exchange amount of the rear heat exchanger 2 divided by the front area S2 of the rear heat exchanger 2. Is referred to as the amount of heat exchange per unit front area of the rear heat exchanger 2.

FIG. 3 is a partially enlarged plan view of the fins 17 of the front heat exchanger 1, and FIG. 4 is a partially enlarged plan view of the fins 17 of the rear heat exchanger 2. The first realization method is to use the fins 17 of the heat exchangers 1 and 2 as shown in FIGS.
Are formed so that the occupied area ratio of the slits 24 in the fins 17 of the front-side heat exchanger 1 is larger than that of the rear-side heat exchanger 2.

FIG. 5 is a view for explaining a method of forming the slit 24. The slit 24 forms a pair of parallel cuts 27 in the fin 17 as shown in FIG.
The raising portion 28 sandwiched between the cuts 27 is formed by raising the fin 17 on one surface side, as shown in FIG.

By forming the slit 24, an edge is formed in the fin 17, and the edge effect of the edge improves the heat transfer coefficient and increases the amount of heat exchange. Therefore, by making the occupied area ratio of the slits 24 in the fins 17 larger in the front heat exchanger 1 than in the rear heat exchanger 2, a difference can be provided in the heat exchange amount per unit front area. .

In FIGS. 3 and 4, reference numeral 26 denotes a projection, which is provided to improve the heat transfer coefficient by increasing the surface area. A slit 25 is provided near the center of the fin 17 in the width direction.
Are formed at regular intervals substantially parallel to the longitudinal direction of
It is provided for thermally separating two regions separated by the slits 25.

A second realization method is to form a louver 29 instead of the slit 24. FIG.
FIG. 4 is a diagram illustrating a method of forming a louver 29. As shown in FIG. 6A, the louver 29 forms a linear cut 30 in the fin 17, and a substantially rectangular portion 31 adjacent to one side of the cut 30 is shown in FIG. 6B. As described above, the fin 17 is formed on one surface side of the fin 17 by raising it by a certain angle. The louver 29 is not limited to the one having such a structure. For example, a pair of parallel cuts is formed, and at a position between the cuts, a roughly rectangular portion adjacent to one cut is formed on one surface side. A structure in which a louver shown by a virtual line is added to a louver 29 shown by a solid line in FIG. 6B in which a substantially rectangular portion adjacent to the other cut is raised by a certain angle on the other surface side while being caused by a certain angle. Structure).

By forming the louver 29, an edge is formed on the fin 17, and the edge effect of the edge improves the heat transfer coefficient and increases the heat exchange amount. Therefore, by making the occupied area ratio of the louver 29 in the fins 17 larger in the front heat exchanger 1 than in the rear heat exchanger 2, a difference can be provided in the heat exchange amount per unit front area. .

The above first and second realization methods can be formed relatively easily by processing the existing fins 17, so that they can be implemented relatively easily.

The third realization method is to make the fin pitch P1 of the front heat exchanger 1 (see FIG. 2) smaller than the fin pitch P2 of the rear heat exchanger 2. When the fin pitch P1 is reduced, the number of the fins 17 included in the same effective length L increases, and as a result, the heat transfer area of the heat exchanger 1 increases and the heat exchange amount increases.

In a fourth method, the length W1 (see FIG. 3) of the front heat exchanger 1 in the air flow direction is changed by changing the length of the rear heat exchanger 2
Is longer than the length W2 in the air flow direction (see FIG. 4). When the length W1 in the air flow direction is increased, the heat transfer area of the heat exchanger 1 increases by that amount, and the heat exchange amount increases.

In the fifth method, the pipe pitch Pt1 of the heat transfer tubes 21 of the front heat exchanger 1 (see FIG. 3) is made smaller than the pipe pitch Pt2 of the rear heat exchanger 2 (see FIG. 4). That is. When the tube pitch Pt1 is reduced, more heat transfer tubes 21 penetrate the fins 17, the heat transfer coefficient is improved, and the heat exchange amount of the front heat exchanger 1 is increased.

In a sixth method, the thickness T1 of the fins 17 of the front-side heat exchanger 1 is reduced by changing the thickness T1 of the fins 17 of the rear-side heat exchanger 2.
Is to be larger than the plate thickness T2. By increasing the plate thickness T1 of the fin 17, the heat transfer coefficient is improved,
The heat exchange amount of the front-side heat exchanger 1 increases.

A seventh realization method is to make the heat transfer coefficient of the heat transfer tube 21 of the front heat exchanger 1 higher than that of the rear heat exchanger 2. For example, if a material having a high heat conductivity is used, Good. By improving the heat transfer coefficient, the amount of heat exchange of the front-side heat exchanger 1 increases.

Next, an eighth implementation method will be described.
First, FIG. 7 is a diagram for explaining a supply route of the refrigerant to the heat exchanger 10 in the present invention, and FIG. 8 is a diagram for explaining a supply route of the refrigerant to the heat exchanger 40 in the related art. 7 and 8, the heat transfer tube 2
A solid line connecting 1, 50 indicates that two heat transfer tubes are connected on the front side of the drawing, and a broken line indicates that two heat transfer tubes are connected on the rear side of the drawing.

The refrigerant is supplied to the heat exchangers 10 and 40 from the refrigerant supply means 20 and 46 through a plurality of supply ports I1, I2 and I2.
3, i1 and i2, are supplied separately, discharged from the same number of outlets O1, O2, O3, o1, and o2 as the supply ports, and then merged again and returned to the refrigerant supply means 20, 46. Therefore, a plurality of paths through which the refrigerant in the heat exchangers 10 and 40 flows is provided.

The conventional heat exchanger 40 is provided with two paths R4 and R5 as shown in FIG. Conventional heat exchanger 4
At 0, both paths R4, R5 include 14 heat transfer tubes 50. Accordingly, the refrigerant-side pressure loss per path is substantially the same, and the heat exchange amounts of the front-side heat exchanger 31 and the rear-side heat exchanger 32 are the same. On the other hand, as shown in FIG.
In the present invention, the heat exchanger 10 has three paths R1, R2,
R3 is provided. In the heat exchanger 10, the path R1 passing through the rear heat exchanger 2 includes 12 heat transfer tubes 21, and the paths R2 and R3 passing through the front heat exchanger 1 each include 8 heat transfer tubes 21. Therefore, since the refrigerant-side pressure loss of the routes R2 and R3 is smaller than that of the route R1, the refrigerant easily flows,
Therefore, the temperature difference between the fins 17 (air side) and the heat transfer tubes 21 is larger in the front-side heat exchanger 1 than in the rear-side heat exchanger 2, whereby the front-side heat exchanger 1 has a larger heat exchange amount. Becomes larger. This is because most of the refrigerant in the evaporator is 2
This is a phase flow state, and the concentration of the two-phase flow of the refrigerant is determined by the pressure.

The above-described realization methods may be implemented individually or in combination of a plurality of types. Further, the present invention can be applied to a heat exchanger having a structure other than the cross fin tube type heat exchanger.

[0045]

According to the air conditioner of the first aspect, the front-side heat exchanger is configured such that the amount of heat exchange per unit front area is larger than that of the rear-side heat exchanger. Therefore, the capacity of the heat exchanger can be improved without increasing the size of the heat exchanger itself, and the size can be reduced. In addition, the amount of heat exchange per unit front area of the rear heat exchanger is smaller than that of the front heat exchanger, and the amount of drain water generated in the rear heat exchanger is relatively small. There is no need to increase the size. Therefore, the rear side drain pan does not protrude above the air supply path of the rear side heat exchanger to narrow the air supply path, and it is possible to prevent the deterioration of the air supply performance and the generation of abnormal noise.

In the air conditioners of the second and third aspects, the slits and the louvers are formed by processing existing fins, so that the operation can be performed relatively easily.

It should be noted that, even if the constitutions of claims 4 to 9 are adopted to increase the heat exchange amount of the front-side heat exchanger, it is suitable for the implementation.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing an embodiment in which an air conditioner of the present invention is configured as an indoor unit of a separation type air conditioner.

FIG. 2 is a perspective view illustrating a schematic configuration of a heat exchanger according to the embodiment of the present invention.

FIG. 3 is a partially enlarged plan view of the front-side heat exchanger according to the embodiment of the present invention.

FIG. 4 is a partially enlarged plan view of the back side heat exchanger in the embodiment of the present invention.

FIG. 5 is an explanatory diagram illustrating a method for forming a slit.

FIG. 6 is an explanatory view illustrating a method of forming a louver.

FIG. 7 is an explanatory diagram illustrating a supply path of the refrigerant to the heat exchanger according to the embodiment of the present invention.

FIG. 8 is an explanatory diagram illustrating a supply path of a refrigerant to a heat exchanger in a conventional technique.

FIG. 9 is a sectional view showing a conventional example of an indoor unit of a separation type air conditioner.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Front heat exchanger 2 Rear heat exchanger 3 Fan rotor 4 Front suction port 5 Top suction port 8 Front drain pan 10 Heat exchanger 19 Main casing 20 Refrigerant supply means 21 Heat transfer tube 22 Rear drain pan 24 Slit 27 Cut 28 Raised portion 29 Louver 30 Notch 31 Raised portion R1 route R2 route R3 route I1 supply port I2 supply port I3 supply port O1 discharge port O2 discharge port O3 discharge port

Claims (9)

[Claims] 1. Suction ports (4) (5) on the front and upper surfaces thereof
A heat exchanger (10) comprising a front-side heat exchanger (1) and a rear-side heat exchanger (2) combined in an inverted V-shape in a main body casing (19) having A fan rotor (3) arranged downstream of 10), a front drain pan (8) arranged below the front heat exchanger (1),
In an air conditioner provided with a rear-side drain pan (22) disposed below the rear-side heat exchanger (2), the amount of heat exchange per unit front area of the front-side heat exchanger (1) is calculated based on the rear-side heat exchanger. An air conditioner characterized by being larger than the heat exchanger (2). 2. The heat exchanger (10) is a cross fin tube type heat exchanger in which a heat transfer tube (21) is disposed in a state penetrating a plurality of fins (17) arranged in parallel,
The fin (17) of the heat exchanger (10) has a plurality of slits (24) formed by causing a portion (28) sandwiched between two parallel cuts (27) on one surface side. The occupied area ratio of the slits (24) in the fins (17) of the front-side heat exchanger (1) is larger than that of the rear-side heat exchanger (2).
Air conditioner. 3. The heat exchanger (10) is a cross-fin tube type heat exchanger having a plurality of fins (17) arranged in parallel with a heat transfer tube (21) disposed therethrough.
The fins (17) of the heat exchanger (10) are formed with a plurality of louvers (29) formed by raising a portion (31) adjacent to one side of the cut (30) toward one surface side, 2. The air conditioner according to claim 1, wherein the occupied area ratio of the louvers (24) in the fins (17) of the front heat exchanger (1) is larger than that of the front heat exchanger (2). 3. 4. The heat exchanger (10) is a cross-fin tube type heat exchanger comprising a plurality of fins (17) arranged side by side and a heat transfer tube (21) arranged in a penetrating state.
The fin pitch (P1) of the front side heat exchanger (1) is
The air conditioner according to any one of claims 1 to 3, wherein the air conditioner is smaller than the rear heat exchanger (2). 5. The heat exchanger (10) is a cross-fin tube type heat exchanger comprising a plurality of fins (17) arranged side by side and a heat transfer tube (21) arranged in a penetrating state.
The width (W1) of the fins (17) of the front-side heat exchanger (1) in the air flow direction is larger than that of the rear-side heat exchanger (2). Any air conditioner. 6. The heat exchanger (10) is a cross-fin tube type heat exchanger having a plurality of fins (17) arranged side by side and a heat transfer tube (21) arranged in a penetrating state.
Heat transfer tube pitch (Pt1) of the front side heat exchanger (1)
The air conditioner according to any one of claims 1 to 5, wherein the air conditioner is smaller than the rear heat exchanger (2). 7. The heat exchanger (10) is a cross-fin tube type heat exchanger having a plurality of fins (17) arranged side by side and a heat transfer tube (21) disposed in a penetrating state.
The thickness (T) of the fins (17) of the front-side heat exchanger (1)
The air conditioner according to any one of claims 1 to 6, wherein 1) is thicker than the rear heat exchanger (2). 8. The heat exchanger (10) is a cross-fin tube type heat exchanger having a plurality of fins (17) arranged side by side and a heat transfer tube (21) arranged in a penetrating state.
The air according to any one of claims 1 to 7, wherein a heat conductivity of the heat transfer tube (21) of the front heat exchanger (1) is higher than that of the rear heat exchanger (2). Harmony machine. 9. The heat exchanger (10) is a cross-fin tube type heat exchanger comprising a plurality of fins (17) arranged side by side and a heat transfer tube (21) disposed in a penetrating state.
The heat transfer tubes (21) of the heat exchanger (10) are connected to form a plurality of paths (R1) (R2) (R3), and the refrigerant from the refrigerant supply means is supplied to the plurality of paths (R1) (R2). (R
3) Merged and supplied from each supply port, and each path (R1)
After passing through (R2) and (R3), a plurality of routes (R
1) Heat transfer tubes discharged from the respective outlets of (R2) and (R3), merged again, returned to the refrigerant supply means, and included in a path (R1) passing through the rear heat exchanger (2). (2
The number (1) is set to the path (R) passing through the front-side heat exchanger (1).
2) The air conditioner according to any one of claims 1 to 8, wherein the number of heat transfer tubes (21) included in (R3) is increased.