CN109996994B

CN109996994B - Air conditioner

Info

Publication number: CN109996994B
Application number: CN201780071215.4A
Authority: CN
Inventors: 丸本一彦; 名越健二; 山本宪昭; 大城崇裕; 奥村拓也
Original assignee: Panasonic Intellectual Property Management Co Ltd
Current assignee: Panasonic Intellectual Property Management Co Ltd
Priority date: 2016-12-15
Filing date: 2017-11-15
Publication date: 2021-05-14
Anticipated expiration: 2037-11-15
Also published as: WO2018110186A1; JP2018096635A; MY195659A; CN109996994A; JP6739001B2

Abstract

The air conditioner of the present invention includes: a heat exchanger formed by stacking plate fins; a fan for blowing air to the heat exchanger; and a drain pan disposed vertically below the heat exchanger. Gaps are formed between the adjacent plate fins by the projecting portions of the plurality of projections disposed on the plate fins. The heat exchanger is disposed obliquely. The projection portion has a plurality of lower projections disposed inward of the lower end edges of the plate fins.

Description

Air conditioner

Technical Field

The present invention relates to an air conditioner, and more particularly to an air conditioner capable of suppressing an increase in size of a drain pan for condensed water and a decrease in performance of the entire apparatus, which are caused when a plate-fin stacked heat exchanger is used.

Background

In general, in an air conditioner, cooling or heating is performed by circulating a refrigerant compressed by a compressor through a heat exchanger such as a condenser or an evaporator and performing heat exchange with air. Here, the heat exchanger is provided in an air passage in the main body in an inclined manner, and a water receiving tray for receiving condensed water generated in the heat exchanger during cooling or the like is provided (for example, see patent document 1).

Fig. 12 shows an air conditioner described in patent document 1. This conventional air conditioner has an air outlet 101 provided above a main body 100 and an air inlet 102 provided on a lower surface thereof. An air passage 103 is formed in the main body 100 to ventilate from below to above. A heat exchanger 104 is provided obliquely above the air passage 103, and an air blower 105 is disposed. A drain pan 106 for receiving condensed water from the heat exchanger generated during cooling or the like is provided below the heat exchanger 104 provided in the air passage 103 in an inclined manner.

The performance and energy saving performance of such a conventional air conditioner are largely influenced by the heat exchange efficiency of the heat exchanger 104. Therefore, the heat exchanger 104 is strongly required to be efficient.

In order to increase the efficiency of the heat exchanger 104, a technique of reducing the diameter of the heat transfer pipe penetrating the fin group has been proposed in the related art.

However, since there is a limit to the reduction in the diameter of the heat transfer pipe, the improvement in heat exchange efficiency and the reduction in size are becoming more and more limited.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2016-95038

Disclosure of Invention

The present inventors have attempted to improve the efficiency of a heat exchanger by using a heat exchanger in which a plurality of plate fins are stacked, that is, a so-called plate fin stacked heat exchanger.

In the plate-fin stacked heat exchanger, heat is exchanged between the refrigerant flowing through the flow channels formed in the plate fins and the air flowing between the stacked plate fins. Since the refrigerant flow path is formed by press-forming the concave groove in the plate fin, the cross-sectional area of the flow path can be made smaller than that of the fin-tube-type heat transfer tube, and the heat exchange efficiency can be improved.

In the plate fin stacked heat exchanger, it is considered that a plurality of projections for forming gaps between the stacked plate fins are arranged in a row, and a part of the plurality of projections is provided along the long edges of the plate fins.

In this case, when the plate-fin stacked heat exchanger is used, there is a possibility that: when water droplets condensed on the heat exchanger flow down along the lower end edge of the obliquely arranged heat exchanger (hereinafter, referred to as the lower end edge), the water droplets are caught by the protrusions aligned with the lower end edge of the plate fin, and thus drip downward from the protrusions due to gravity.

Therefore, when the plate-fin stacked heat exchanger is installed at an inclination, the size of the water receiving tray installed below the heat exchanger needs to be approximately equal to the inclination width of the heat exchanger (the dimension of the heat exchanger when projected vertically downward). As a result, the size of the water receiving tray may be increased, which may cause a technical problem of performance deterioration due to an increase in size of the apparatus, an increase in air passage resistance, and the like.

The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a compact, high-performance air conditioner having high heat exchange efficiency.

The air conditioner of the present invention includes: a heat exchanger formed by stacking plate fins; a fan for blowing air to the heat exchanger; and a drain pan disposed vertically below the heat exchanger. Gaps are formed between the adjacent plate fins by the projecting portions of the plurality of projections disposed on the plate fins. The heat exchanger is obliquely disposed in an air passage in the housing of the air conditioner. The projection portion has a plurality of lower projections disposed inward of the lower end edges of the plate fins.

This heat exchanger can improve heat exchange efficiency by reducing the diameter of the flow path. Further, the condensed water can be prevented from dripping from the projecting portion provided on the inner side of the lower end edge of the obliquely provided plate fin. This makes it possible to reduce the size of the drain pan for receiving condensed water, and to suppress the size of the facility and the performance deterioration due to the increase in the air passage resistance.

According to the above configuration, the present invention provides a compact, high-performance air conditioner having high heat exchange efficiency.

Drawings

Fig. 1 is a schematic cross-sectional view showing an air conditioner according to embodiment 1 of the present invention, the air conditioner having a heat exchanger.

Fig. 2 is a perspective view showing a heat exchanger of the air conditioner.

Fig. 3 is a perspective view showing the heat exchanger in a separated state.

Fig. 4 is a perspective view showing a plate-fin stacked body constituting the heat exchanger, with a part thereof cut.

Fig. 5 is a plan view of the plate fin constituting the plate fin laminate.

Fig. 6 is an enlarged plan view of the plate fin.

Fig. 7 is an exploded perspective view showing a part of the plate fin in an enlarged manner.

Fig. 8 is an enlarged perspective view showing a protrusion provided on the plate fin.

Fig. 9 is a schematic perspective view for explaining the operation of the heat exchanger.

Fig. 10 is a schematic cross-sectional view illustrating the operation of the heat exchanger.

Fig. 11 is an enlarged perspective view of plate fins constituting a heat exchanger included in an air conditioner according to embodiment 2 of the present invention.

Fig. 12 is a schematic configuration diagram showing a conventional air conditioner.

Detailed Description

An air conditioner according to claim 1 is an air conditioner according to the present invention, including: a heat exchanger formed by stacking plate fins; a fan for blowing air to the heat exchanger; and a drain pan disposed vertically below the heat exchanger. Gaps are formed between the adjacent plate fins by the projecting portions of the plurality of projections disposed on the plate fins. The heat exchanger is obliquely disposed in an air passage in the housing of the air conditioner. The projection portion has a plurality of lower projections disposed inward of the lower end edges of the plate fins.

This heat exchanger can improve heat exchange efficiency by reducing the diameter of the flow path. Further, the condensed water can be prevented from dripping from the projection portion provided on the inner side of the lower end edge of the obliquely provided plate fin. This makes it possible to suppress performance deterioration due to an increase in size of the apparatus and an increase in air passage resistance, which are caused by downsizing of the drain pan for receiving the condensed water.

In the 2 nd aspect, the plurality of lower protrusions include: a plurality of 1 st protrusions provided on the inner side of the lower side edge than the gap; and a 2 nd projection provided closer to the lower end edge than the 1 st projections.

Thus, even when the condensed water flows down over the gaps between the fin plate stacked layers at the lower end edges of the plate fins, the water that has dripped can be prevented from hitting the protrusions. Therefore, when the water dropped flows downward with such a force, the water is prevented from hanging on the projection and dropping from the projection. This can more reliably prevent dripping.

In the 3 rd aspect, the top portions of the plurality of protrusions are spherical. Here, "spherical" includes a substantially spherical shape.

Thus, even if a part of the condensed water flowing down the lower end edges of the plate fins collides with the projecting portions, the condensed water is easily separated from the top portions of the projecting portions because the top portions of the projecting portions have a spherical shape, and thus the condensed water can flow down the lower end edges of the plate fins. Therefore, the condensed water can be more reliably prevented from dripping from the projection.

In the 4 th aspect, the plurality of 1 st projections are provided in a region where the water receiving tray is not present vertically below the lower end edge.

Accordingly, the projection of the lower end edge of the plate fin in the portion where the water receiving tray is present vertically below is provided very close to the lower end edge to increase the strength of the end edge of the fin having a weak strength, thereby improving the rigidity thereof. Moreover, the projection is provided very close to the end edge, whereby the heat exchange effective area located inside the projection is increased, and the heat exchange efficiency is improved by a corresponding amount. That is, both rigidity of the plate fin and improvement of heat exchange efficiency can be achieved.

In the 5 th aspect, the projection portion includes a plurality of upper projections disposed in the vicinity of the upper end edges of the plate fins.

This improves the rigidity of the upper end edge portions of the plate fins and improves the heat exchange efficiency due to the increase in the effective heat exchange area, thereby more effectively improving the rigidity and heat exchange efficiency of the plate fins.

In the 6 th aspect, the heat exchanger is disposed such that the lower end edge is located on the upstream side of the air passage.

This can suppress the falling action due to the gravity of the condensed water flowing down at the lower end edge of the plate fin by the air flow flowing in the air passage. As a result, the condensed water flows down more and then drops to the lower portion of the plate fin. Therefore, the water collector can be made more compact, and the number of projections provided near the lower end edges of the plate fins is increased, thereby further improving the effects of improving the rigidity and the heat exchange efficiency.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. The embodiment described below is an example, and the present invention is not limited to this embodiment.

(embodiment mode 1)

Fig. 1 is a schematic cross-sectional view of an air conditioner according to embodiment 1 of the present invention.

In the air-conditioning apparatus of the present embodiment, although not shown, the refrigerant circulates in the order of the compressor, the four-way valve, the heat-source-side heat exchanger, the expansion valve, the use-side heat exchanger, the four-way valve, and the compressor, the heat-source-side heat exchanger functions as a condenser, and the use-side heat exchanger functions as an evaporator, thereby performing cooling operation. In this air conditioner, the four-way valve is switched, and the refrigerant circulates through the compressor, the four-way valve, the use-side heat exchanger, the expansion valve, the heat-source-side heat exchanger, the four-way valve, and the compressor in this order, and the use-side heat exchanger functions as a condenser and the heat-source-side heat exchanger functions as an evaporator, thereby performing a heating operation.

The air conditioner is a split type air conditioner in which an indoor unit and an outdoor unit are connected by a pipe, and the indoor unit houses a utility side heat exchanger and the like, and the outdoor unit houses a compressor, a four-way valve, an expansion valve, a heat source side heat exchanger and the like.

As shown in fig. 1, the main body 1 of the indoor unit of the air conditioner configured as described above is provided with a suction port 2 on the lower surface, a discharge port 3 on the front surface, and an L-shaped (including substantially L-shaped) air passage 4 between the suction port 2 and the discharge port 3 in the present embodiment. The air passage 4 is provided with a heat exchanger 5 as a use-side heat exchanger and a fan 6.

The heat exchanger 5 is disposed obliquely with respect to the vertical line, and a drain pan 7 for receiving the condensed water condensed by the heat exchanger 5 is provided at the lower end of the heat exchanger 5.

Next, the structure of the heat exchanger 5 will be described with reference to fig. 2 to 10.

Fig. 2 is a perspective view showing a heat exchanger of the air conditioner. Fig. 3 is a perspective view showing the heat exchanger in a separated state. Fig. 4 is a perspective view showing a plate-fin stacked body constituting a main body of the heat exchanger, with a part of the plate-fin stacked body cut. Fig. 5 is a plan view of the plate fin constituting the plate fin laminate. Fig. 6 is an enlarged plan view of the plate fin. Fig. 7 is an exploded perspective view showing a part of the plate fin in an enlarged manner. Fig. 8 is an enlarged perspective view showing a protrusion provided on the plate fin. Fig. 9 is a schematic perspective view illustrating the operation of the heat exchanger. Fig. 10 is a schematic cross-sectional view illustrating the operation of the heat exchanger.

As shown in fig. 2 and 3, the heat exchanger 5 of the present embodiment is configured by stacking a plurality of plate fins 11 having a rectangular plate shape, and

end plates

12a and 12b having the same shape (including substantially the same shape) as the plate fins 11 in plan view are provided on both sides (left and right sides in fig. 2 and 3) in the stacking direction. The

end plates

12a and 12b are formed of a rigid plate material, and are formed by grinding a metal material such as aluminum, an aluminum alloy, or stainless steel and performing metal working.

The

end plates

12a, 12b and the plurality of plate fins 11 are stacked and brazed and integrated together to form a plate fin stacked body 13 forming a main body of the heat exchanger.

The plate fin 11 has a plurality of refrigerant flow path groups arranged in parallel and through which a refrigerant of the 1 st fluid can flow. The refrigerant flow path group is formed in a U shape (including a substantially U shape). The 1 st header flow path 14 and the 2 nd header flow path 15 connected to the refrigerant flow path group are provided on one end side (left side in fig. 1) of the end plate 12a on one side of the plate fin laminate 13.

Specifically, as shown in fig. 5 to 7, the plate fin 11 is configured such that a plurality of parallel refrigerant passages 16 are brazed in opposition to a pair of plate-

like members

17a and 17b (see fig. 7) in which the 1 st header passage 14 and the 2 nd header passage 15 connected to the refrigerant passages 16 are formed. The plurality of refrigerant flow paths 16 are formed in a U shape (including a substantially U shape), and the 1 st header flow path 14 and the 2 nd header flow path 15 connected to the refrigerant flow paths 16 are arranged so as to be concentrated on one end side of the plate fin 11.

A plurality of the plate fins 11 having the above-described structure are stacked as shown in fig. 4 to form a plate fin stacked body 13 shown in fig. 2 and 3. Gaps 19 through which air can flow are formed between the plate fins 11 by protrusions 18 arranged between both longitudinal ends of the plate fins 11 and the refrigerant flow paths 16 (see fig. 4). The projection 18 is formed of a plurality of projections. As described above, the heat exchanger 5 allows the 2 nd fluid to flow between the respective plate fin stacked bodies of the plate fin stacked body having the flow path through which the 1 st fluid can flow, and allows heat exchange between the 1 st fluid and the 2 nd fluid.

The protrusions 18 also have a function of joining the adjacent plate fins 11 to each other and linking the plate fins 11.

Further, the refrigerant flow path 16 is formed as a concave groove in the plate-

like members

17a and 17b, and thus the diameter can be easily reduced.

In the refrigerant flow path 16, a slit 20 for preventing heat transfer between the forward side refrigerant flow path 16a connected to the 1 st header flow path 14 and the return side refrigerant flow path 16b connected to the 2 nd header flow path 15 is formed between the two.

The heat exchanger 5 configured as described above is provided obliquely so that air can flow through the gaps 19 between the plate fins 11. Here, as shown in fig. 9 and 10, and particularly in fig. 10, on the lower surface side of the obliquely arranged plate fin 11, lower projections 18a arranged in a row at a lower end edge 11a on the upstream side of the air passage 4 are provided so that all or a part thereof is positioned inward of the lower end edge 11 a. In the present embodiment, the 2 nd protrusion 18ab located at the obliquely lower portion of the lower end edge 11a is provided so as to be closer to the lower end edge 11a than the 1 st protrusion 18aa located at the obliquely upper portion of the lower end edge 11 a.

In other words, heat exchanger 5 is provided such that 1 st projection 18aa located outside the projection range of the opening of water receiving tray 7, which is a portion where the opening of water receiving tray 7 does not exist vertically below obliquely provided heat exchanger 5, is located inward of lower end edge 11a of plate fin 11 by a predetermined distance. Further, the 2 nd projection 18ab positioned within the opening projection range of the water receiving tray 7 is provided in the vicinity of the fin lower end edge 11a of the plate fin 11. The 2 nd projection 18ab may be provided so as to be flush with the lower end edge 11 a.

In the present embodiment, the 1 st projection 18aa is provided so as to be located inward of the dimension of the gap 19 in which air flows between the plate fins 11 from the lower end edge 11 a.

The upper projections 18b arranged in rows at the upper end edges 11b of the plate fins 11 are provided on the inner side of the upper end edges 11b, for example, in the vicinity of the upper end edges 11b of the fins, like the 2 nd projections 18ab, over the entire longer sides of the plate fins 11.

The positional relationship of the protrusions 18(18a, 18aa, 18ab, 18b) is as clearly shown in the enlarged plan view of fig. 6 (in fig. 6, the lower side of the plate fin 11 is the lower side end edge 11a, and the upper side is the upper side end edge 11 b).

Further, all of the protrusions 18(18a, 18aa, 18ab, 18b) or at least the top portions of the lower protrusions 18a (18aa, 18ab) provided at the lower end edge 11a of the plate fin 11 are spherical (have a substantially spherical shape).

The inclination angle of the heat exchanger 5 may be appropriately set depending on the structure of the air passage 4, and may be 20 to 50 degrees, preferably 30 to 40 degrees, with respect to the vertical line in consideration of the relationship between the flow (stream) and the dripping of the condensed water.

In the air conditioner configured as described above, the operational effects will be described by taking the case of the cooling operation in which condensation occurs as an example.

First, the flow of the refrigerant and the heat exchange action are explained. The refrigerant flows from the 1 st header flow path 14, which is the inflow side of the plate-fin laminated body 13, into the refrigerant flow path 16 group. The refrigerant flowing into the refrigerant flow paths 16 of each plate fin 11 is turned back from the outward flow side refrigerant flow path 16a, which is the outward flow side of the refrigerant flow paths 16, to the return side refrigerant flow path 16b, which is the return side, and then flows from the 2 nd header flow path 15, which is the outlet side, to the refrigerant circuit of the refrigeration system.

Then, when the refrigerant flows in the refrigerant flow path 16, it exchanges heat with air passing through the gaps 19 between the plate fin stacked bodies 13.

In this case, the refrigerant flow paths 16 through which the refrigerant can flow can be reduced in diameter by reducing the cross-sectional area of the concave grooves formed in the plate fins 11 for the refrigerant flow paths. As a result, the heat exchange efficiency can be improved and the size can be reduced as compared with the heat pipe system.

The heat exchanger 5 exchanges heat with air passing through the gaps 19 between the plate-fin stacked layers, and turns the air into cold air or warm air. When this air is heat-exchanged to become cold air, moisture in the air may be condensed on the surface of the heat exchanger 5. Since the heat exchanger 5 is provided obliquely, the condensed water flows downward along the lower end edges 11a of the plate fins 11 constituting the heat exchanger 5 as shown in fig. 9.

Here, since the heat exchanger 5 is a plate-fin stacked heat exchanger, as shown in fig. 10, the end edge portions of the plate fins 11 and the like are provided with the protrusions 18(18a (18aa, 18ab), 18b) in rows that form gaps between the plate fins. Since the plurality of 1 st projections 18aa arranged in a row at the obliquely upper portion of the lower end edge 11a of the plate fin 11 through which the condensed water can flow are located inward (inward side) of the lower end edge 11a by a predetermined distance, the condensed water flows downward along the lower end edge 11a of the plate fin 11 without hitting the 1 st projections 18 aa. In the present embodiment, since the 2 nd projections 18ab of the lowermost portion of the plate fin 11 are provided in the vicinity of the fin lower end edge 11a, the condensed water flowing downward hits the 2 nd projections 18ab and is caught, and drops downward from the 2 nd projections 18 ab.

Therefore, the pan 7 for receiving the condensed water dripping from the heat exchanger 5 can be made smaller in size than the size M of the 2 nd projection 18ab, and can be made smaller in size than the inclined size L (the size of the heat exchanger when projected vertically downward) of the inclined heat exchanger 5 (see fig. 10). Further, since water receiving tray 7 can be made compact, restrictions such as a portion of water receiving tray 7 entering air passage 4 or having to narrow air passage 4 can be reduced, and performance deterioration due to the above-described factors can be suppressed.

In the present embodiment, as is apparent from the above description, of the lower projections 18a provided at the lower end edges 11a of the plate fins 11, at least the 1 st projection 18aa located at a portion not facing the water collector 7 is provided closer to the inside of the plate fin 11 than the 2 nd projection 18ab, and the 2 nd projection 18ab located at a portion facing the water collector 7 is provided in the vicinity of the lower end edges of the fins.

Therefore, in the heat exchanger 5, the 2 nd protrusions 18ab are positioned near the lower end edges 11a of the plate fins 11 at the portion facing the water receiving tray 7, and the strength of the fin end edges having relatively low strength is increased to provide rigidity. Further, by providing the 2 nd projection 18ab near the lower end edge 11a, the heat exchange effective area inside the 2 nd projection 18ab is increased, and the heat exchange efficiency is improved by that amount.

Specifically, as shown in fig. 6, when the protrusion 18 is provided near the lower end edge 11a of the plate fin 11, the heat exchange effective area X, which is higher in heat exchange efficiency, inside the 2 nd protrusion 18ab provided near the lower end edge 11a, that is, near the refrigerant flow path 16, is larger than the heat exchange effective area Y inside the 1 st protrusion 18aa provided so as to be located inside (far side) the lower end edge 11 a. Therefore, the heat exchange efficiency is improved by a corresponding amount.

In addition, the lower side projections 18a (18aa, 18ab) do not contribute effectively to their own heat exchange. Therefore, when the lower side projections 18a (18aa, 18ab) themselves are reduced, the heat exchange area contributing to the heat exchange of the plate fin 11 can be increased, and the heat exchange efficiency can be further improved. Therefore, it is preferable to reduce the lower projections 18a (18aa, 18ab) and the upper projections 18b to the minimum required dimensions.

As described above, when one projection is provided in the vicinity of the lower end edge 11a in the projection row provided at the lower end edge 11a of the plate fin 11, both the improvement of the rigidity of the plate fin 11 and the improvement of the heat exchange efficiency can be achieved.

The dimension Z (see fig. 6) inward from the lower end edge 11a of the 1 st projection 18aa is larger than the gap 19 (see fig. 4) between the plate fins 11. Therefore, even if the condensed water flows down through the gaps 19 between the fin plates 11 at the lower end edges 11a of the plate fins 11, the condensed water can flow down to the lower portion without coming into contact with the 1 st projections 18 aa. Therefore, the condensed water can be prevented from dripping from the 1 st projection 18aa as a starting point in a state where the condensed water is caught by the 1 st projection 18aa provided at the obliquely upper portion not facing the water receiving tray 7, and the dripping can be more reliably prevented.

As shown in fig. 8, the top of the protrusion 18(18a, 18aa, 18ab, 18b) is spherical (including substantially spherical). Accordingly, even when a part of the condensed water flowing down the lower end edge 11a of the plate fin 11 hits the 1 st projection 18aa, the top of the 1 st projection 18aa is spherical (including substantially spherical), and therefore the condensed water is less likely to be caught on the top. Therefore, the condensed water is prevented from dropping from the 1 st projection 18aa as a starting point along the fin lower end edge 11a as it is.

In the heat exchanger 5, upper protrusions 18b are arranged in rows on the lower end edges 11a and the upper end edges 11b of the plate fins 11, and the upper protrusions 18b on the upper end edges 11b are arranged in the vicinity of the upper end edges 11 b. Therefore, the rigidity of the upper end edges 11b of the plate fins 11 can be increased, and the heat exchange efficiency can be improved by increasing the heat exchange effective area. Therefore, the rigidity of the plate fin 11 and the heat exchange efficiency can be improved at the same time more effectively.

In this embodiment, the heat exchanger 5 is arranged such that the lower end edges 11a of the plate fins 11 are partially positioned on the upstream side of the air passage 4. This can suppress a falling action due to the gravity of the condensed water flowing down the lower end edge 11a of the plate fin 11, and the condensed water can drip from a portion below the plate fin 11. Therefore, the water tray 7 can be made more compact. In addition, the number of the 2 nd protrusions 18ab provided in the vicinity of the lower end edges 11a of the plate fins 11 is increased, and the rigidity and the heat exchange efficiency can be further improved.

(embodiment mode 2)

Fig. 11 shows a projection of a plate fin according to embodiment 2. In the present embodiment, the projections 18(18a, 18aa, 18ab, 18b) provided to the plate fins 11 are formed by cutting along the refrigerant flow paths 16 as shown in fig. 11, and the cut edges E are configured to face the flow direction W of the air flowing between the stacked layers of the plate fins 11.

Thus, in the protrusion 18(18a, 18aa, 18ab, 18b), the interval between the plate-fin stacked layers is constant, and the dead water region which is likely to occur on the downstream side of the protrusion 18(18a, 18aa, 18ab, 18b) is extremely small, and the leading edge effect is exerted at the cut-forming end edge E portion. Further, since the cut-formed edge E portion is opposed to the flow direction W of the air, the flow resistance to the air becomes small. Therefore, the increase in flow path resistance in the flow path region of the plate fin laminated body 13 can be suppressed, and the heat exchange efficiency can be further improved.

The cut-out formation of the protrusion 18(18a, 18aa, 18ab, 18b) is formed along the refrigerant flow path 16 of the plate-fin stacked body 13. Therefore, it is not necessary to provide a thinned portion for forming a cut-out portion from the concave plane 21 between the refrigerant flow paths in the direction intersecting the refrigerant flow paths 16. Therefore, as compared with the case where the projection portions 18(18a, 18aa, 18ab, 18b) are formed so as to be raised in a columnar shape, the concave planar dimensions between the refrigerant flow paths can be reduced by an amount that does not require the provision of the wall-thickness-reduced portion, and the plate fin 11, in other words, the heat exchanger can be downsized accordingly.

The operation and effects of the other structures are the same as those of embodiment 1, and the description thereof is omitted.

The air conditioner of the present invention has been described above with reference to the above embodiments, but the present invention is not limited thereto. That is, the embodiments of the present invention are illustrative in all aspects and should not be considered as limited, and the scope of the present invention is not given by the above description but by the scope of the claims, and is intended to include the scope of the claims and all changes within the scope and range equivalent thereto.

Industrial applicability of the invention

As is apparent from the above description of the embodiments, the present invention can provide a compact, high-performance air conditioner having high heat exchange efficiency. Therefore, the present invention can be widely used not only as a household air conditioner but also as an industrial air conditioner.

Description of the reference numerals

1 main body

2 suction inlet

3 air outlet

4 wind path

5 Heat exchanger

6 blower

7 water pan

11 plate fin

11a lower end edge

11b upper end edge

12a, 12b end plate

13-plate fin laminate

14 st 1 manifold flow path

15 No. 2 manifold flow path

16 refrigerant flow path

16a outgoing-side refrigerant passage

16b return side refrigerant passage

17a, 17b plate-like member

18 projection

18a lower side projection

18aa 1 st projection

18ab 2 nd protrusion

18b upper side projection

19 gap

20 slot

21 concave plane.

Claims

1. An air conditioner characterized by comprising:

a heat exchanger configured by stacking a plurality of plate fins;

a fan for supplying air to the heat exchanger; and

a water receiving tray disposed vertically below the heat exchanger,

a gap is formed between adjacent ones of the plurality of plate fins by a plurality of protrusions arranged on the plurality of plate fins, respectively,

the heat exchanger is obliquely arranged in an air passage in the casing of the air conditioner,

the projection portion includes a plurality of lower projections arranged inside lower end edges of the plurality of plate fins,

the plurality of lower protrusions include: a plurality of 1 st protrusions provided at predetermined intervals from the lower end edge; and a 2 nd projection provided closer to the lower end edge side than the plurality of 1 st projections, the predetermined interval being longer than the interval of the gap.

2. The air conditioner according to claim 1, characterized in that:

the top of each of the plurality of protrusions is spherical.

3. The air conditioner according to claim 1, characterized in that:

the plurality of 1 st projections are provided in a region where the water receiving tray is not present vertically below the lower end edge.

4. The air conditioner according to claim 1, characterized in that:

the projection portion includes a plurality of upper projections disposed in the vicinity of upper end edges of the plurality of plate fins.

5. The air conditioner according to claim 1, characterized in that:

the heat exchanger is disposed such that the lower end edge is located on an upstream side of the air passage.