WO1998019112A1 - Conditionneur d'air - Google Patents

Conditionneur d'air Download PDF

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Publication number
WO1998019112A1
WO1998019112A1 PCT/JP1997/003730 JP9703730W WO9819112A1 WO 1998019112 A1 WO1998019112 A1 WO 1998019112A1 JP 9703730 W JP9703730 W JP 9703730W WO 9819112 A1 WO9819112 A1 WO 9819112A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
fins
heat
air conditioner
heat transfer
Prior art date
Application number
PCT/JP1997/003730
Other languages
English (en)
Japanese (ja)
Inventor
Junichirou Tanaka
Yoshiaki Fukumura
Original Assignee
Daikin Industries, Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to AU45732/97A priority Critical patent/AU4573297A/en
Publication of WO1998019112A1 publication Critical patent/WO1998019112A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0071—Indoor units, e.g. fan coil units with means for purifying supplied air

Definitions

  • the present invention relates to an air conditioner provided with an inverted V-shaped heat exchanger.
  • FIG. 9 is a cross-sectional view showing an indoor unit of a separation type air conditioner equipped with the above-described inverted V-shaped heat exchanger.
  • 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 also 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 lower end. Also, it is inclined so as to be located near the lower side of the upper surface grill 42 on the back side.
  • a rear-side heat exchanger 32 whose vertical width is about 2/5 of the front-side heat exchanger 38 is disposed.
  • the upper end of the rear heat exchanger 32 is the upper end of the front heat exchanger 38.
  • the lower end is inclined further so as to be closer to the rear side than the lower end.
  • 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 rear-side heat exchanger
  • the upper end of the heat exchanger 32 is the top of the inverted V-shaped heat exchanger 40.
  • the inverted V-shaped outer side of the heat exchanger 40 is a suction side 44 in the main body casing 49, and the inner side thereof is an outlet side 45.
  • the blower side 45 has a cylindrical fan rotor 33 having a rotating shaft 33a extending in a direction substantially perpendicular to the paper surface of the drawing, and a fan rotor 33 close to the fan rotor 33 along the axial direction.
  • a cross flow fan is constituted by the tongue portion 37 provided as described above, and a scroll portion 36 formed so that the lower end side thereof is smoothly connected to the air outlet 43.
  • the indoor air is sucked from both the front and top surfaces of the main body casing 49, and the sucked indoor air is heat-exchanged by both the front heat exchanger 38 and the rear heat exchanger 82. It is supposed to be. Therefore, the contact area where the heat exchanger 40 contacts the indoor air is the sum of the two heat exchangers 38 and 32. It is almost the same as that of the heat exchanger whose shape is extended by the length of the heat exchanger 32. Therefore, in this air conditioner, it is necessary to reduce the heat exchange capacity without reducing its heat exchange capacity. And you can do it.
  • the capacity of the heat exchanger 40 In order to make the above-mentioned conventional indoor unit compact without reducing the heat exchange capacity, the capacity of the heat exchanger 40 must be improved, that is, per unit frontal area of the heat exchanger 40. It is necessary to increase the amount of heat exchange. However, if the capacity of the rear-side heat exchanger 32 is improved in the same way as the capacity of the front-side heat exchanger 38, the amount of drain water generated in the rear-side heat exchanger 38 during continuous cooling is reduced. Therefore, it is necessary to increase the size of the rear drain pan 39. Since the ventilation path of the rear heat exchanger 32 is formed from above to below, if the rear drain pan 89 becomes large, the rear drain pan 39 will protrude above the ventilation path. However, the ventilation performance is reduced, and as a result, the capacity of the rear heat exchanger 32 is reduced. In addition, the large-sized rear-side drain pan 39 narrows the air passage, which causes a new problem of generating abnormal noise.
  • the present invention has been made to solve the above-mentioned conventional disadvantages, 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. Is to do.
  • the air conditioner of the present invention includes 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.
  • Heat exchanger 10 which is made up of inverted V-shape and this heat exchange Fan rotor 3 arranged downstream of unit 10, front drain pan 8 arranged below front heat exchanger 1, and rear drain pan 2 arranged below rear heat exchanger 2 2
  • the amount of heat exchange per unit front area of the front heat exchanger 1 is larger than that of the rear heat exchanger 2.
  • the heat exchange amount per unit front area of the front heat exchanger 1 is configured to be larger than the heat exchange amount per unit front area of the rear heat exchanger 2. I have. Therefore, the capacity of the heat exchanger 10 can be improved without increasing the size of the heat exchanger 10 itself, and compactness can be achieved. Also, 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 cooling operation is relatively small. Therefore, there is no need to increase the size of the rear drain pan 22.
  • 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.
  • the front-side drain pan 8 is located below the front-side heat exchanger 1, and the ventilation path is formed from the front side to the rear side. It does not protrude on the path. Therefore, there are no problems such as a decrease in the blowing capacity and generation of abnormal noise.
  • the heat exchanger 10 is a cross-fin tube type heat exchanger formed by arranging the heat transfer tubes 21 through a plurality of fins 17 arranged in parallel.
  • the fin 17 of the heat exchanger 10 is formed by raising a part 28 sandwiched between two parallel cuts 27 toward one surface side. Multiple slits 24 were formed, and the area occupied by the slits 24 in the fins 17 of the front heat exchanger 1 was made larger than that of the rear heat exchanger 2.
  • the fin 17 of the heat exchanger 10 has a louver 29 formed by raising a portion 31 adjacent to one side of the cut 30 on one surface side.
  • the occupied area ratio of the louvers 24 in the fins 17 of the front-side heat exchanger 1 is made larger than that of the front-side heat exchanger 2.
  • the heat exchange amount of the front-side heat exchanger 1 increases due to the improvement of the heat conductivity on the air side (fins 17). Further, since the slit louver can be formed by processing an existing fin, it can be implemented relatively easily.
  • the heat exchanger 10 is a cross-fin tube type heat exchanger in which a plurality of fins 17 arranged side by side and heat transfer tubes 21 are arranged in a penetrating state.
  • the fin pitch P 1 of the front-side heat exchanger 1 is smaller than that of the rear-side heat exchanger 2.
  • the air conditioner of another embodiment is characterized in that the width W 1 of the fins 17 of the front heat exchanger 1 in the air flow direction is larger than that of the rear heat exchanger 2. In these air conditioners, the amount of heat exchange of the front heat exchanger 1 increases due to an increase in the heat transfer area on the air side.
  • the heat exchanger 10 is a cross-fin tube type heat exchanger in which a plurality of fins 17 arranged side by side and heat transfer tubes 21 are arranged in a penetrating state.
  • the heat transfer tube pitch Pt1 of the front-side heat exchanger 1 is smaller than that of the rear-side heat exchanger 2.
  • the air conditioner of another embodiment is characterized in that the plate thickness T1 of the fins 17 of the front heat exchanger 1 is larger than that of the rear heat exchanger 2.
  • the heat exchanger 10 is a cross-fin 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.
  • the heat conductivity of the heat transfer tubes 21 of the front heat exchanger 1 is higher than that of the rear heat exchanger 2. By doing so, the heat exchange amount of the front heat exchanger 1 also increases.
  • the heat exchanger 10 is a cross-fin tube type heat exchange configured by disposing the heat transfer tube 21 in a state of being penetrated by a plurality of fins 17 arranged in parallel.
  • the heat transfer tubes 21 of the heat exchanger 10 are connected to form a plurality of paths Rl, R2, R3, and the refrigerant from the refrigerant supply means receives the plurality of paths Rl, R2 and R8 are supplied separately from the supply ports, and after passing through each II path Rl, R2 and R3, are discharged from the discharge ports of the above multiple paths Rl, R2 and R3 And is returned to the refrigerant supply means, and the number of heat transfer tubes 21 included in the route R 1 passing through the rear heat exchanger 2 is reduced by the route R 2 passing through the front heat exchanger 1.
  • the number of heat transfer tubes 21 included in R3 is larger than that of R3.
  • the pressure loss arrow on the refrigerant side in the routes Rl and R2 in the front side heat exchanger 1 is reduced, and the temperature difference with the air side is increased. The amount of heat exchange in vessel 1 increases.
  • FIG. 1 is a cross-sectional view showing an embodiment in which the air conditioner of the present invention is configured as an indoor unit of a separation type air conditioner.
  • FIG. 2 is a perspective view showing a schematic configuration of the 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. 3 ⁇ 4 o
  • FIG. 4 is a partially enlarged plan view of the rear heat exchanger according to the embodiment of the present invention.
  • FIG. 5A and FIG. 5B are explanatory views for explaining a method of forming a slit.
  • 6A and 6B are explanatory views 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.
  • 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.
  • a front grill 11 having a front suction port 4 is provided on the front side of the main body casing 19, and a top suction port 5 is also formed on the upper surface side.
  • Top grille 12 is provided.
  • 1 shown in the figure is a front-side heat exchanger.
  • the front-side heat exchanger 1 is configured by inserting 20 refrigerant tubes 21, and the first to the first sections are defined by a section where the four refrigerant tubes 21 are inserted as one section.
  • the division is divided into 5 divisions, 1 a to le. Then, by bending between the adjacent partitioning portions, it is curved so as to protrude forward from the top to the lower portion, and the fourth partitioning portion 1 d, which is the fourth counting from the top, is the frontmost side. Is located.
  • Reference numeral 2 in the figure denotes a rear-side heat exchanger 2.
  • the rear-side heat exchanger 2 is configured by inserting eight refrigerant pipes 21 into the rear-side heat exchanger 2.
  • the portion through which the four refrigerant pipes 21 are inserted is divided into two sections, a first section and a second section 2a, 2b, as one section, and the space between the two sections 2a, 2b is folded.
  • an inverted V-shaped heat exchanger 10 is formed.
  • the outside of the inverted V-shaped heat exchanger 10 is the suction side 14 in the main body casing 19, and the inside, that is, the downstream side of the heat exchanger 10 is the discharge side 15.
  • a certain space is formed between the upper part of the front heat exchanger 1 and the upper space.
  • an air purification filter 16 having antibacterial and deodorizing effects is provided in this space.
  • a cross-flow fan composed of a columnar fan rotor 3, a tongue 7, a scroll 6 and the like is provided on the outlet side 15 as in the conventional example.
  • the fan rotor 3 of the cross flow fan is arranged such that the rotating shaft 3 a is located behind the fourth partition 1 d of the front-side heat exchanger 1.
  • the scroll portion 6 is formed such that the lower end side thereof is smoothly connected to the outlet 13.
  • a front-side drain pan 8 integrally formed with the tongue 7 is provided to receive drain water generated in the front-side heat exchanger 1 during the cooling operation. Drain water generated in the rear heat exchanger 2 is received by a rear drain pan 22 integrally formed with the heat exchanger support 23. 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.
  • the fan rotor 3 shown in FIG. When driven in rotation, a swirling air flow is generated by the action of the cross-floor fan, and the swirling air current sucks indoor air from the front suction port 4 and the top suction port 5.
  • the sucked room air further flows from the suction side 14 of the main body casing 19 to the blowout side 15, where it is heat-exchanged (cooled) by the heat exchanger 10 to be conditioned air.
  • the conditioned air is blown out of the outlet 13 again into the room while changing the flow direction to the front side along the scroll portion 6.
  • the heat exchange capacity is improved over the conventional heat exchanger by various methods described later, but the heat exchange capacity per unit front area of the front side heat exchanger 1 is increased.
  • the heat exchange amount is configured to be larger than the heat exchange amount per unit front area of the rear 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 compactness can be achieved.
  • the heat exchange amount per unit front area of the rear heat exchanger 2 is smaller than that of the front heat exchanger 1, so it is generated in the rear heat exchanger 2 during cooling rotation.
  • the amount of drain water generated is relatively small, and there is no need to increase the size of the rear drain pan 9.
  • the ventilation path of the rear side heat exchanger 2 is formed from the upper surface inlet 5 to the outlet side 15 through the inlet side 14, that is, from the upper part of the main body casing 19 to the lower part where the outlet 13 is located. Therefore, if the rear drain pan 9 arranged below the rear heat exchanger 2 is made larger, it will be provided so as to protrude into the ventilation path, and the ventilation path will be narrowed, resulting in reduced ventilation performance and noise.
  • the rear side drain pan 9 arranged below the rear heat exchanger 2 is made larger, it will be provided so as to protrude into the ventilation path, and the ventilation path will be narrowed, resulting in reduced ventilation performance and noise.
  • the rear side drain pan 9 arranged below the rear heat exchanger 2
  • the front drain pan 8 is located below the front heat exchanger 1, and the air flow is roughly from the front inlet 4 to the outlet 15 and the fan Since it is formed toward the air outlet 13 through the rotor 3, the front drain pan 8 does not protrude into the air supply path. Therefore, problems such as a reduction in the blowing capacity and generation of abnormal noise do not occur.
  • FIG. 2 is a perspective view showing a configuration 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, and the configuration of each of the heat exchangers 1 and 2 is basically the same. It is a vessel.
  • the cross fin tube type heat exchanger includes a plurality of fins 17 arranged side by side, and a plurality of heat transfer tubes 21 arranged in a penetrating state.
  • 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.
  • HI is the length of the air flow suction side of the fin 17.
  • H 2 is the length of the air flow suction side of the fin 17.
  • the value obtained by dividing the total heat exchange amount of the front heat exchanger 1 by the front area S1 of the front heat exchanger 1 is called the heat exchange amount per unit front area of the front heat exchanger 1, and Heat exchange per unit front area of rear heat exchanger 2 divided by total heat exchange amount of rear heat exchanger 2 by front area S 2 of rear heat exchanger 2 Called quantity.
  • FIG. 3 is a partially enlarged plan view of the fins 17 of the front-side heat exchanger 1
  • FIG. 4 is a partially enlarged plan view of the fins 17 of the rear-side heat exchanger 2.
  • the first method is to form a plurality of slits 24 on the fins 17 of the heat exchangers 1 and 2 as shown in FIGS.
  • the occupied area ratio of the slit 24 is to be larger than the occupied area ratio of the slit 24 in the fins 17 of the rear heat exchanger 2.
  • FIG. 5A and FIG. 5B are diagrams illustrating a method of forming the slit 24.
  • the slit 24 forms a pair of parallel cuts 27 in the fins 17 as shown in FIG. 5A, and the causing portion 28 sandwiched between the cuts 27 is shown in FIG. 5B.
  • fins 17 are formed on one surface side of the fins.
  • an edge is formed on the fin 17, and the edge effect of the edge improves the heat transfer coefficient and increases the amount of heat exchange. Therefore, by increasing the ratio of the area occupied by the slits 24 in the fins 17 of the front-side heat exchanger 1 to that of the rear-side heat exchanger 2, the amount of heat exchange per unit frontal area can be reduced. A difference can be provided.
  • reference numeral 26 denotes a protrusion, which is provided to improve the heat transfer coefficient by increasing the surface area.
  • Reference numeral 25 denotes a notch slit, which is formed near the center of the fin 17 in the width direction at a constant interval substantially in parallel with the longitudinal direction of the fin 17. The cut slits 25 are provided for thermally separating each of the two regions separated by them.
  • the second realization method is to form a louver 29 instead of the slit 24.
  • 6A and 6B are views for explaining a method of forming the louver 29.
  • FIG. Louver 29 is straight to fin 17 as shown in Figure 6A
  • a notch 30 is formed, and a roughly rectangular portion 31 adjacent to one side of the notch 30 is raised by a certain angle on one surface side of the fin 17 as shown in FIG. 6B. It is formed.
  • the louver 29 is not limited to such a structure. For example, a pair of parallel cuts is formed, and a roughly rectangular portion adjacent to one cut is formed on one surface at a position between the cuts.
  • a structure in which a rectangular portion adjacent to the other cut is raised by a certain angle on the other surface side (a louver shown by a virtual line is added to a louver 29 shown by a solid line in FIG. 6B). Structure).
  • the louver 29 By forming the louver 29, an edge is formed on the fin 17, and the heat transfer coefficient is improved by the edge effect of the edge, and the heat exchange amount is increased. Therefore, by making the occupied area ratio of the louver 29 in the fins 17 of the front heat exchanger 1 larger than that of the rear heat exchanger 2, the heat exchange amount per unit front area becomes different. Can be provided.
  • the third realization method is to make the fin pitch P 1 of the front heat exchanger 1 (see FIG. 2) smaller than the fin pitch P 2 of the rear heat exchanger 2.
  • the fin pitch P 1 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.
  • the length W 1 of the front heat exchanger 1 in the air flow direction is changed to the length W 2 of the rear heat exchanger 2 in the air flow direction (see FIG. 4). It is longer.
  • the fifth realization method is to make the pipe pitch Pt1 of the heat transfer tubes 21 of the front heat exchanger 1 (see Fig. 3) more than the pipe pitch Pt2 of the rear heat exchanger 2 (see Fig. 4). It is to make it smaller.
  • the tube pitch Pt1 is reduced, more heat transfer tubes 21 penetrate the fins 17, thereby improving the heat transfer coefficient and increasing the heat exchange amount of the front heat exchanger 1.
  • the sixth realization method is to make the thickness T1 of the fins 17 of the front heat exchanger 1 larger than the thickness T2 of the fins 17 of the rear heat exchanger 2. By increasing the plate thickness T1 of the fins 17, the heat transfer coefficient is improved, and the amount of heat exchange of the front heat exchanger 1 is increased.
  • a seventh realization method is to make the heat transfer coefficient of the heat transfer tubes 21 of the front heat exchanger 1 higher than the heat transfer coefficient of the heat transfer tubes of the rear heat exchanger 2.
  • a material having high thermal conductivity may be used.
  • FIG. 7 is a diagram for explaining a supply path of the refrigerant to the heat exchanger 10 in the present invention
  • FIG. 8 is a diagram for explaining a supply path of the refrigerant to the heat exchanger 40 in the conventional technology.
  • the solid line connecting the heat transfer tubes 21 and 50 indicates that the two heat transfer tubes are connected on the near side of the drawing
  • the broken line indicates that the two tubes are on the back side of the drawing. Indicates that the heat transfer tubes are connected.
  • Refrigerant is provided to the heat exchangers 10 and 40 from the refrigerant supply means 20 and 46 through a plurality of supply ports 1, 1, 1, 2, 1, 3, i 1, and i 2. After being discharged from the same number of outlets 0 1, 0 2, 0 3, ol, 02 as the supply ports, they are joined 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 are provided.
  • the conventional heat exchanger 40 has two paths R4 and R5 as shown in Fig. 8. Can be In the conventional heat exchanger 40, the paths R4 and R5 each 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.
  • the heat exchanger 10 is provided with three paths R1, R2, and R3.
  • 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 are both 8 Including heat transfer tubes 21 Therefore, the refrigerant-side pressure loss in the paths R 2 and R 3 is smaller than that in the path R 1, so that the refrigerant can easily flow c. Therefore, the fins 17 (air side) and the heat transfer tubes 21 in the front-side heat exchanger 1 Is larger than the temperature difference between the fins 17 (air side) in the rear heat exchanger 2 and the heat transfer tubes 21, whereby the temperature difference in the front heat exchanger 1 However, the amount of heat exchange increases. This is because most of the refrigerant in the evaporator is in a two-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 performed independently, or may be performed in combination of a plurality of types.
  • the present invention can also be applied to a heat exchanger having a structure other than the cross fin tube type heat exchanger.
  • the heat exchanger of the present invention can be suitably applied to an air conditioner, particularly an indoor unit of a separation type air conditioner which is required to be compact and thin.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

Un échangeur de chaleur (10) comprend un échangeur de chaleur avant (1) et un échangeur de chaleur arrière (2) qui sont combinés selon une configuration en V inversé, l'échangeur de chaleur avant (1) ayant un volume d'échange de chaleur par unité de surface supérieur à celui de l'échangeur de chaleur arrière (2). Concrètement, des fentes (24) ou des louvres (29), par exemple, sont formés sur les ailettes (17) de l'échangeur (10) et le rapport d'occupation de la surface par les fentes (24) ou les louvres sur les ailettes de l'échangeur de chaleur avant (1) est supérieur à celui sur l'échangeur arrière (2). Ainsi, il est possible de produire un dispositif à capacité d'échange de chaleur accrue, compact et à faible bruit.
PCT/JP1997/003730 1996-10-31 1997-10-16 Conditionneur d'air WO1998019112A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU45732/97A AU4573297A (en) 1996-10-31 1997-10-16 Air conditioner

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP8307341A JPH10132372A (ja) 1996-10-31 1996-10-31 空気調和機
JP8/307341 1996-10-31

Publications (1)

Publication Number Publication Date
WO1998019112A1 true WO1998019112A1 (fr) 1998-05-07

Family

ID=17967960

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1997/003730 WO1998019112A1 (fr) 1996-10-31 1997-10-16 Conditionneur d'air

Country Status (3)

Country Link
JP (1) JPH10132372A (fr)
AU (1) AU4573297A (fr)
WO (1) WO1998019112A1 (fr)

Cited By (1)

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CN107843030A (zh) * 2017-11-22 2018-03-27 广东美的制冷设备有限公司 室内换热器、空调室内机及空调器

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Publication number Priority date Publication date Assignee Title
JP4624146B2 (ja) * 2005-03-15 2011-02-02 シャープ株式会社 空気調和機の室内機
CN102207310A (zh) * 2010-03-31 2011-10-05 乐金电子(天津)电器有限公司 具有弧形热交换器的除湿机

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CN107843030B (zh) * 2017-11-22 2024-04-26 广东美的制冷设备有限公司 室内换热器、空调室内机及空调器

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JPH10132372A (ja) 1998-05-22

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