JP2006258306A - Indoor unit for air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an indoor unit for an air conditioner capable of realizing high performance and reducing cost. <P>SOLUTION: The indoor unit 20 for the air conditioner is provided with a fan 14; and at least three heat exchangers 11a, 11b, 11c. The heat exchangers 11a, 11b, 11c are arranged at a periphery of the fan 14 and have a group of fins 12a, 12b, 12c arranged spaced apart from one another; and a group of heat-transfer tubes 13a, 13b, 13c connected to the group of fins 12a, 12b, 12c and flowed with a refrigerant at the inside. A tube diameter of the group of each heat-transfer tubes 13a, 13b, 13c possessed by the respective heat exchangers 11a, 11b, 11c is approximately same in every heat exchanger. At least three heat exchangers are constituted by a first heat exchanger group comprising at least two heat exchangers 11a, 11b; and a second heat exchanger group comprising a heat exchanger 11c including a group of heat-transfer tubes having a larger tube diameter than the tube diameter of the group of heat-transfer tubes of the first heat exchanger group. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an indoor unit for an air conditioner, and more particularly to an indoor unit for an air conditioner including a finned heat exchanger.

  In recent years, with the progress of energy saving of air conditioners, there has been a demand for higher efficiency of heat exchangers with fins constituting the air conditioners. As one means of increasing efficiency, the heat exchanger can be bent in multiple stages or formed into an arc shape to increase the heat transfer exchange area in a limited space and improve the performance of the heat exchanger. Is planned. Further, as another means, by providing an auxiliary heat exchanger for promoting supercooling on the windward side of the heat exchanger, the heat exchanger is improved in performance during heating operation.

  In addition, the efficiency of the heat exchanger is improved by devising the heat transfer tubes and the like constituting the heat exchanger. An air conditioner that achieves high efficiency by paying attention to the diameter and arrangement of heat transfer tubes of a heat exchanger is disclosed in, for example, Japanese Patent Application Laid-Open No. 2001-174047 (Patent Document 1). An air conditioner that achieves high efficiency by paying attention to the wind speed distribution is disclosed in, for example, Japanese Patent Application Laid-Open No. 9-264555 (Patent Document 2).

  FIG. 10 is a schematic side view showing an indoor unit of an air conditioner disclosed in Patent Document 1. Referring to FIG. 10, an indoor unit 100 of an air conditioner includes a blower 152 and three heat exchangers 121 including a fin group and a heat transfer tube group. The heat exchanger 121 is arranged so as to be bent in multiple stages and surround the blower 152. The front heat exchanger 122 with the highest ventilation resistance is placed closest to the front face of the blower 152, and the central heat exchanger 123 with the next highest ventilation resistance is placed at the center located above the front heat exchanger 122. A rear heat exchanger 124 having low ventilation resistance is disposed on the rear surface of the central heat exchanger 123. The front surface heat exchanger 122, the center heat exchanger 123, and the back surface heat exchanger 124 use a plurality of heat transfer tubes having different diameters. Thereby, the ventilation efficiency by the uniform ventilation resistance is improved. Further, by causing the refrigerant to flow sequentially from the thickest heat transfer tube A to the intermediate heat transfer tube B and the thinnest heat transfer tube C during the heating operation, the heat transfer coefficient on the refrigerant side is improved.

FIG. 11 is a cross-sectional view of the air conditioner heat exchanger disclosed in Patent Document 2 when the air conditioner is assembled. Referring to FIG. 11, the heat exchanger 200 of the air conditioner includes a front side heat exchanger 201 including a fin 204 and a heat transfer tube 203, and a rear side heat exchanger 202. The heat exchanger 200 is bent in multiple stages, and the number of rows of the heat transfer tubes 203 in a part of the front side heat exchanger 201 and the rear side heat exchanger 202 is set as the number of rows of the heat transfer tubes 203 in the other part of the rear side heat exchanger 202. The number of columns is less. Thereby, ventilation resistance can be reduced, and cost reduction is aimed at maintaining performance by supplementing the part which heat exchange efficiency fell with ventilation efficiency.
JP 2001-174047 A JP-A-9-264555

  However, since the indoor unit 100 of the air conditioner disclosed in Patent Document 1 needs to devise the tube diameter and the tube arrangement of the heat transfer tubes, the heat transfer in the front surface heat exchanger 122 and the back surface heat exchanger 124 is required. The diameter of the heat pipe is different. Moreover, since the arrangement | sequence of the heat exchanger tube in the front part heat exchanger 122, the center part heat exchanger 123, and the back surface heat exchanger 124 differs, it is necessary to manufacture a special fin and a special heat exchanger tube. Thus, production efficiency is reduced and costs are increased.

  Moreover, since the heat exchanger 200 of the air conditioner disclosed in Patent Document 2 has a reduced number of rows of the heat transfer tubes 203, the heat transfer area capable of heat exchange is reduced. Therefore, the performance of the heat exchanger cannot be improved.

  SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide an air conditioner indoor unit that can achieve high performance, increase production efficiency, and reduce costs.

  The indoor unit of an air conditioner according to the present invention includes a blower and at least three heat exchangers. The heat exchanger includes a fin group disposed around the blower and spaced apart from each other, and a heat transfer tube group that is connected to the fin group and in which the refrigerant flows. The tube diameter of each heat exchanger tube group which each heat exchanger has is substantially the same for every heat exchanger. At least three heat exchangers have a pipe diameter larger than the pipe diameter of the first heat exchanger group including at least two heat exchangers and the heat transfer pipe group in the heat exchanger of the first heat exchanger group. And a second heat exchanger group including a heat exchanger including a heat tube group.

  According to the indoor unit of the air conditioner of the present invention, a heat exchanger with a thin tube diameter of the heat transfer tube group of the first heat exchanger group has a reduced ventilation resistance, and thus the air volume passing through the heat exchanger increases. it can. Therefore, the amount of heat exchange between the air and the refrigerant in the heat exchanger is improved, the efficiency of the entire heat exchanger is improved, and the performance of the indoor unit of the air conditioner can be improved.

  Moreover, since the tube diameter of each heat exchanger tube group which each heat exchanger has is substantially the same for every heat exchanger, production efficiency can be raised and cost reduction can be aimed at.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following drawings, the same or corresponding parts are denoted by the same reference numerals, and description thereof will not be repeated.

(Embodiment 1)
FIG. 1 is a side view showing an indoor unit of an air conditioner according to Embodiment 1 of the present invention. With reference to FIG. 1, the indoor unit of the air conditioner by Embodiment 1 is demonstrated. The air conditioner 10 according to Embodiment 1 includes, for example, three heat exchangers 11a, 11b, and 11c and a blower 14, as shown in FIG. The three heat exchangers 11a, 11b, and 11c are respectively connected to the fin groups 12a, 12b, and 12c spaced apart from each other, and the heat transfer tubes that are connected to the fin groups 12a, 12b, and 12c and in which the refrigerant flows. Groups 13a, 13b and 13c.

  The tube diameter of the heat transfer tube group 13a included in the heat exchanger 11a is substantially the same. Similarly, the tube diameter of the heat transfer tube group 13b included in the heat exchanger 11b is substantially the same, and the tube diameter of the heat transfer tube group 13c included in the heat exchanger 11c is approximately the same. The tube diameter of the heat transfer tube group 13c is larger than the tube diameters of the heat transfer tube groups 13a and 13b.

  The first heat exchanger group includes a heat exchanger 11a and a heat exchanger 11b. The second heat exchanger group includes a heat exchanger 11c. That is, the first heat exchanger group is composed of at least two heat exchangers, and the second heat exchanger group has a tube diameter larger than the tube diameter of the heat transfer tube group of the heat exchanger constituting the first heat exchanger group. It consists of a heat exchanger having a heat transfer tube group.

  As shown in FIG. 1, the heat exchangers 11 a, 11 b, and 11 c are arranged around the blower 14 in the order close to the blower 14. In the heat exchangers 11a, 11b, and 11c, the heat transfer tube groups 13a, 13b, and 13c pass through the fin groups 12a, 12b, and 12c, respectively, and the refrigerant flows through the heat transfer tube groups 13a, 13b, and 13c. In the heat exchangers 11a, 11b, and 11c, the air sent from the blower 14 flows between the fin groups 12a, 12b, and 12c.

  Next, an operation method of the indoor unit 10 of the air conditioner will be described. With reference to FIG. 1, the air blower 14 is operated and air is sent into the heat exchangers 11a, 11b, and 11c. Further, the refrigerant is caused to flow through the heat transfer tube groups 13a, 13b, and 13c. Therefore, the air sent to the heat exchangers 11a, 11b, and 11c is cooled or overheated by the refrigerant flowing through the heat transfer tube groups 13a, 13b, and 13c. In addition, the air volume which passed heat exchanger 11a, 11b, 11c is shown as air volume 15a, 15b, 15c, and the flow path of a refrigerant | coolant is not shown in figure.

  As described above, according to the indoor unit 10 of the air conditioner according to Embodiment 1, the pipe diameter larger than the pipe diameter of the heat transfer tube group in the two heat exchangers 11a and 11b of the first heat exchanger group. And a second heat exchanger group composed of one heat exchanger including a heat transfer tube group having Therefore, the heat exchangers 11a and 11b having a thin tube diameter of the heat transfer tube group have low ventilation resistance. Therefore, since the air volume 15a, 15b of the air passing through the heat exchangers 11a, 11b can be increased, the amount of heat exchange between the air and the refrigerant in the heat exchangers 11a, 11b is improved. Therefore, the efficiency of the heat exchanger as a whole is improved. As a result, the indoor unit 10 of the air conditioner can achieve high performance.

  Moreover, the tube diameter of each heat exchanger tube group 13a, 13b, 13c which the three heat exchangers 11a, 11b, 11c have is substantially the same for every heat exchanger. Therefore, the production efficiency of the heat exchanger can be increased as compared with the case where heat transfer tube groups having different tube diameters are arranged in the heat exchanger. As a result, the air conditioner indoor unit 10 can achieve cost reduction.

(Embodiment 2)
FIG. 2 is a side view showing the indoor unit of the air conditioner according to Embodiment 2 of the present invention. With reference to FIG. 2, the indoor unit of the air conditioner by Embodiment 2 is demonstrated. Referring to FIG. 2, the configuration of air conditioner indoor unit 20 according to the second embodiment is basically the same as that of the first embodiment of the present invention shown in FIG. The difference is that the heat exchanger 11c constituting the second heat exchanger group constituted by the heat tube group 13c is arranged on the front surface portion closest to the blower 14.

  Next, an operation method of the indoor unit 20 of the air conditioner will be described. With reference to FIG. 2, the air blower 14 is operated and air is sent into the heat exchangers 11a, 11b, and 11c. Further, the refrigerant is caused to flow through the heat transfer tube groups 13a, 13b, and 13c. Therefore, the air sent to the heat exchangers 11a, 11b, and 11c is cooled or overheated by the refrigerant flowing through the heat transfer tube groups 13a, 13b, and 13c.

  As explained above, according to the indoor unit 20 of the air conditioner according to Embodiment 2, the heat exchanger 11c constituting the second heat exchanger group is arranged on the front surface portion closest to the blower. Therefore, since the tube diameter of the heat transfer tube group 13c of the heat exchanger 11c is large, the heat exchanger 11c has the largest ventilation resistance among the three heat exchangers 11a, 11b, and 11c. Since the heat exchanger 11c having the highest ventilation resistance is disposed in the front portion of the blower 14 with the fastest wind speed, the air flow rates 15a, 15b, and 15c of the air fed into the heat exchangers 11a, 11b, and 11c are substantially the same. . Therefore, the wind speed distribution in the three heat exchangers 11a, 11b, and 11c is uniform, and each of the three heat exchangers 11a, 11b, and 11c can contribute to heat exchange effectively. As a result, the indoor unit 20 of the air conditioner can achieve higher performance.

(Embodiment 3)
FIG. 3 is a side view showing an indoor unit of an air conditioner according to Embodiment 3 of the present invention. With reference to FIG. 3, the indoor unit of the air conditioner by Embodiment 3 is demonstrated. Referring to FIG. 3, the configuration of air conditioner indoor unit 30 according to the third embodiment is basically the same as that of the second embodiment of the present invention shown in FIG. The difference is that a portion 36a, a heating refrigerant outflow portion 36b, a cooling operation refrigerant outflow portion 37a, a heating refrigerant inflow portion 37b, and a refrigerant flow path 37c are provided.

  Specifically, during the heating operation, the heating refrigerant inflow portion 37b is provided in the heat exchanger 11c constituting the second heat exchanger group, and the heating refrigerant is provided in the heat exchanger 11a constituting the first heat exchanger group. An outflow portion 36b is provided. On the other hand, at the time of cooling operation, the cooling-time refrigerant inflow portion 36a is provided in the heat exchanger 11a constituting the first heat exchanger group, and the cooling-time refrigerant outflow portion 37a is provided in the heat exchanger 11c constituting the second heat exchanger group. Is provided.

  Moreover, in the indoor unit 30 of the air conditioner, the heat exchangers 11a and 11b constituting the first heat exchanger group are configured such that the tube diameters of the heat transfer tube groups 13a and 13b are different from each other. In the present embodiment, for example, the tube diameter of the heat transfer tube group 13a of the heat exchanger 11a is configured to be thinner than the tube diameter of the heat exchanger 11b.

  Note that the refrigerant inflow portion means a member for charging the refrigerant to flow the refrigerant to the heat transfer tube group, and the refrigerant outflow portion means a member for discharging the refrigerant that has flowed through the heat transfer tube group. .

  In the refrigerant flow path 37c during the heating operation, the refrigerant flows in from the refrigerant inflow portion 37b during heating, and the heat transfer tube groups 13c, 13b, and 13a in the heat exchangers 11c, 11b, and 11a are arranged in descending order. The refrigerant circuit is configured so as to flow sequentially and discharged from the refrigerant outflow portion 36b during heating.

  On the other hand, in the refrigerant flow path 37c during the cooling operation, the refrigerant is introduced from the cooling refrigerant inflow portion 36a, and the heat transfer tube groups 13a, 13b, 13b in the heat exchangers 11a, 11b, 11c The refrigerant circuit is configured so as to flow sequentially to 13c and be discharged from the refrigerant outflow portion 37a during cooling.

  Next, an operation method of the indoor unit 30 of the air conditioner will be described. With reference to FIG. 3, the air blower 14 is operated to send air into the heat exchangers 11a, 11b, and 11c.

  During the heating operation, the refrigerant flows in from the heating refrigerant inflow portion 37b, flows through the flow path 37c, and is discharged from the heating refrigerant inflow portion 36b. Therefore, the air sent into the heat exchangers 11c, 11b, and 11a is heated by the refrigerant flowing through the heat transfer tube groups 13c, 13b, and 13a constituting the flow path 37c.

  The state of the refrigerant in the heating refrigerant inflow portion 37b during the heating operation is a high-temperature and high-pressure gas state. When flowing in the heat transfer tube groups 13c, 13b, 13a constituting the flow path 37c of the heat exchangers 11c, 11b, 11a, the refrigerant exchanges heat with air. At this time, since the refrigerant is cooled by air, the refrigerant enters a gas-liquid two-phase state in the middle of the flow path 37c, and the refrigerant changes into a low-temperature and high-pressure liquid in the refrigerant outlet portion 36b during heating.

  During the heating operation, the ratio of the liquid state in the refrigerant in the two-phase state increases as the refrigerant in the refrigerant passage 37c approaches the heating refrigerant outflow portion 36b. Therefore, the flow rate of the refrigerant decreases, and heat transfer between the air and the heat transfer tube group decreases.

  However, in the indoor unit 30 of the air conditioner, the tube diameters of the heat transfer tube groups 13a and 13b of the heat exchangers 11a and 11b constituting the heating refrigerant outflow portion 36b are relatively smaller than the tube diameter of the heat transfer tube group 13c. . Therefore, a decrease in the flow rate of the supercooled refrigerant in which the ratio of the liquid state is increased is suppressed, and heat transfer between the refrigerant and the heat transfer tube group in the vicinity of the refrigerant outlet portion 36b during heating is promoted.

  On the other hand, during the cooling operation, the refrigerant flows in from the cooling refrigerant inflow portion 36a, flows through the refrigerant flow path 37c, and is discharged from the cooling refrigerant outflow portion 37a. Therefore, the air is cooled by the refrigerant flowing through the heat exchangers 11a, 11b, and 11c.

  The state of the refrigerant in the cooling refrigerant inflow portion 36a during cooling is a two-phase state in which the liquid ratio of low temperature and low pressure is high. When flowing in the heat transfer tube groups 13a, 13b, and 13c in the heat exchangers 11a, 11b, and 11c constituting the flow path 37c, the refrigerant exchanges heat with air. At that time, since the refrigerant is superheated by air, the refrigerant changes into a low-temperature and low-pressure gaseous refrigerant in the cooling-time refrigerant outflow portion 37a.

  During the cooling operation, the ratio of the gas state in the refrigerant in the two-phase state increases as the refrigerant in the flow path 37c approaches the cooling outflow portion 37a. Therefore, as the heat transfer tube groups 13a, 13b, and 13c constituting the flow path 37c are advanced, the pressure loss therein increases. As a result, the heat transfer coefficient as a whole heat exchanger decreases.

  However, in the indoor unit 30 of the air conditioner, the tube diameter of the heat transfer tube group 13c of the heat exchanger 11c constituting the cooling refrigerant outflow portion 37a is large. Therefore, an increase in the pressure loss of the superheated refrigerant in which the gas state ratio is increasing can be suppressed, and a decrease in the heat transfer coefficient can be suppressed.

  In the dehumidifying operation, the refrigerant flow path 37c is the same as in the cooling operation. Specifically, a cycle in which the air volume is suppressed and humidity is preferentially removed, that is, a weak cooling operation is performed. Therefore, the flow state of the refrigerant is the same as in the cooling operation.

  Note that the refrigerant inflow portion 36a during cooling operation and the refrigerant outflow portion 36b during heating may be one pipe that also serves as the refrigerant inflow and exhaust, or may be two pipes. Similarly, the refrigerant outflow portion 37a during cooling operation and the refrigerant inflow portion 37b during heating may be one pipe that also serves as the refrigerant inflow and exhaust, or may be two pipes.

  As described above, according to the indoor unit 30 of the air conditioner in Embodiment 3, the heating-time refrigerant inflow portion 37b is provided in at least one of the heat exchangers constituting the second heat exchanger group during the heating operation. At the same time, at least one of the heat exchangers constituting the first heat exchanger group is provided with a heating refrigerant outflow portion 36b. And the refrigerant is made to flow from heat exchanger 11c which constitutes the 2nd heat exchanger group to heat exchangers 11b and 11a which constitute the 1st heat exchanger group. Moreover, it is made to flow sequentially from the heat exchanger 11b with a relatively large diameter of the heat transfer tube group to the heat exchanger 11a with a relatively small diameter of the heat transfer tube group in the first heat exchanger group. Therefore, even if the high-temperature and high-pressure refrigerant changes to low-temperature and high-pressure as it travels through the flow path 37c, the pipe diameter of the heat transfer tube group becomes thin, so that a decrease in flow rate is suppressed. As a result, the indoor unit 30 of the air conditioner can achieve high performance.

  Further, during cooling operation, at least one of the heat exchangers constituting the first heat exchanger group is provided with a cooling refrigerant inflow portion 36a, and at least one of the heat exchangers constituting the second heat exchanger group is provided. A cooling refrigerant outflow portion 37a is provided. And the refrigerant is made to flow from heat exchanger 11a, 11b which constitutes the 1st heat exchanger group to heat exchanger 11c which constitutes the 2nd heat exchanger group. Moreover, it is made to flow sequentially from the heat exchanger 11a with a relatively small diameter of the heat transfer tube group to the heat exchanger 11b with a relatively large diameter of the heat transfer tube group in the first heat exchanger group. Accordingly, as the refrigerant in a two-phase state with a high liquid ratio of low temperature and low pressure advances through the flow path 37c, the tube diameter of the heat transfer tube group becomes thick even if the gas ratio becomes high. Increase in pressure loss can be suppressed. As a result, the indoor unit 30 of the air conditioner can achieve high performance.

(Embodiment 4)
FIG. 4 is a side view showing an indoor unit of an air conditioner according to Embodiment 4 of the present invention. With reference to FIG. 4, the indoor unit of the air conditioner by Embodiment 4 is demonstrated. Referring to FIG. 4, the configuration of the indoor unit 40 of the air conditioner according to the fourth embodiment is basically the same as that of the third embodiment of the present invention shown in FIG. 3, but the first heat exchanger The difference is that a throttle means 48 is provided in the refrigerant flow path 37c connecting the group and the second heat exchanger group.

  Specifically, the heat transfer tube group 13b of the heat exchanger 11b in which the width of the fin group 12b is Lb, which constitutes the first heat exchanger group, and the fins that constitute the second heat exchanger group A throttle means 48 is provided between the group 12c and the heat transfer tube group 13c of the heat exchanger 11c whose width is Lc.

  Next, an operation method of the indoor unit 40 of the air conditioner will be described. Since the heating operation and the cooling operation are the same as those of the indoor unit 30 of the air conditioner according to Embodiment 3, the description thereof will not be repeated. It should be noted that the throttle means 48 does not act during heating operation and cooling operation. Hereinafter, the reheat dehumidifying operation of the indoor unit 40 of the air conditioner will be described.

  During the reheat dehumidifying operation, the blower 14 is operated to send air into the heat exchangers 11a, 11b, and 11c. The refrigerant flows from the cooling refrigerant inflow portion 36a, flows through the heat transfer tube groups 13a and 13b, passes through the throttle means 48, flows through the heat transfer tube group 13c, and is discharged from the cooling refrigerant outflow portion 37a. And heat exchange is performed between the refrigerant | coolant which flows through heat exchanger 11a, 11b, 11c, and the sent air.

  Next, the flow of the refrigerant during the reheat dehumidification operation will be described. During the reheat dehumidifying operation, the refrigerant is brought to a high temperature and pressure through a compressor, an outdoor heat exchanger, and the like. And the refrigerant | coolant made into the high temperature / high pressure flows in from the refrigerant | coolant inflow part 36a at the time of a cooling, and flows through the heat exchangers 11a and 11b which comprise the 1st heat exchanger group with a thin pipe diameter of a heat exchanger tube group. Next, when passing through the throttle means 48, the refrigerant is depressurized by the throttle means 48 and becomes a low temperature and low pressure state. Thereafter, the refrigerant flows into the heat exchanger 11c having the large diameter of the heat transfer tube group constituting the second heat exchanger group, and flows out from the cooling refrigerant outflow portion 37a. That is, during the dehumidifying operation, since the refrigerant is hot in the first heat exchanger group, the first heat exchanger group acts as a condensing unit, and since the refrigerant is low in the second heat exchanger group, The refrigerant is caused to flow so that the two heat exchanger groups act as an evaporation section.

  The air sent to the heat exchanger is dehumidified in the heat exchanger 11c because the refrigerant is at low temperature and low pressure. On the other hand, in the heat exchangers 11a and 11b, since the refrigerant is high temperature and pressure, the air is overheated. Therefore, the air cooled and dehumidified by the second heat exchanger group is mixed with the air warmed by the first heat exchanger group, and the entire air is dehumidified without lowering the temperature.

  The throttle means 48 means a member that depressurizes the refrigerant flowing from the first heat exchanger group to the second heat exchanger group during the reheat dehumidifying operation. The throttle means 48 is constituted by, for example, an electromagnetic valve, a capillary tube or the like.

  As described above, according to the indoor unit 40 of the air conditioner in the fourth embodiment, the throttle means 48 is provided in the refrigerant flow path 37c that connects the first heat exchanger group and the second heat exchanger group. ing. Therefore, the reheat dehumidifying operation can be performed by operating the throttle means 48.

  Further, during the dehumidifying operation, the refrigerant is caused to flow so that the first heat exchanger group acts as a condenser and the second heat exchanger group acts as an evaporator. Therefore, the refrigerant can be set to a high temperature and a high pressure in the first heat exchanger group, and to a low temperature and a low pressure in the second heat exchanger group. And since the 1st heat exchanger group which comprises a condensation part has the thin pipe diameter of a heat exchanger tube group, as shown in Embodiment 3, the heat transfer rate by the side of a condensation improves. On the other hand, since the second heat exchanger group constituting the evaporator section has a large heat transfer tube group, the heat transfer coefficient on the evaporation side is improved. As a result, the indoor unit 40 of the air conditioner can greatly improve the dehumidifying performance, and can achieve higher performance.

  Next, the modification of the indoor unit 40 of the air conditioner in Embodiment 4 is demonstrated. FIG. 5 is a side view of heat exchangers 11a and 11c in a modification of indoor unit 40 of the air conditioner according to Embodiment 4 of the present invention.

  Referring to FIG. 5, in heat exchangers 11a and 11c, heat transfer tube groups 13a and 13c pass through fin groups 12a and 12c, and the through-hole positions of heat transfer tube groups 13a and 13c on the main surfaces of fin groups 12a and 12c are as follows. These are arranged in two rows in a certain direction (vertical direction in the figure).

  Fin width of one row of heat transfer tube groups 13a and 13c, which is obtained by dividing the width in the direction perpendicular to the extending direction of the rows (lateral direction in the figure) on the main surface of fin groups 12a and 12c by the number of rows And As shown in FIG. 5, the widths of the fins 12a and 12c for one row of the heat exchangers 11a and 11c are Lc / 2 and La / 2, respectively. In the present modification, the relationship that the widths of the fins for one row are Lc / 2> La / 2 is established.

  According to this modification, the heat transfer tube group penetrates the fin group, and the penetration position of the heat transfer tube group on the main surface of the fin group through which the heat transfer tube group penetrates constitutes one or more rows aligned in a certain direction. The width of the fins for one row of the heat transfer tube group in the first heat exchanger group is smaller than the width of the fins for one row of the heat transfer tube group in the second heat exchanger group. That is, the fin width for one row in the heat exchanger 11c that constitutes the second heat exchanger group that is located close to the blower 14, has a high wind speed, and has a large tube diameter of the heat transfer tube group 13c is increased. Therefore, it becomes possible to improve the heat transfer efficiency of the heat exchanger 11c. On the other hand, the fin width for one row of the heat exchanger 11a constituting the first heat exchanger group that is positioned relatively far from the blower 14, the wind speed is slow, and the tube diameter of the heat transfer tube group 13a is small. . Therefore, ventilation resistance can be reduced, fan power can be reduced, and fan efficiency can be improved. As a result, the efficiency of the entire heat exchanger can be improved.

(Embodiment 5)
FIG. 6 is a side view showing an indoor unit of an air conditioner according to Embodiment 5 of the present invention. With reference to FIG. 6, the indoor unit of the air conditioner by Embodiment 5 is demonstrated. Referring to FIG. 6, the configuration of air conditioner indoor unit 50 according to the fifth embodiment is basically the same as that of the fourth embodiment of the present invention shown in FIG. The difference is that the number of rows of the heat transfer tube groups 13a and 13b in the heat exchangers 11a and 11b constituting the group is increased from two rows to three rows.

  Specifically, as shown in FIG. 6, in the heat exchangers 11 a and 11 b where the tube diameter of the heat transfer tube group is thin, the number of rows of the heat transfer tube groups 13 a and 13 b is three, and the tubes of the heat transfer tube group In the heat exchanger 11c having a large diameter, the number of rows of the heat transfer tube groups 13c is two. The flow path 37c is basically the same as the indoor unit 40 of the air conditioner according to Embodiment 4, but the amount of increase in the number of rows by one in the heat exchangers 11a and 11b becomes longer. The heat exchangers 11a and 11b have three rows. However, as shown in the modification of the fourth embodiment, the width of one row of the fins 12a and 12b is one row of the fins 12c. The same is true for points narrower than the minute width.

  About the operation method of the indoor unit 50 of an air conditioner, since it is the same as that of the indoor unit 40 of the air conditioner in Embodiment 4 about the heating operation, the cooling operation, and the reheat dehumidification operation, the description Do not repeat.

  As described above, the flow path 37c becomes longer as the number of rows in the heat exchangers 11a and 11b increases.

  As explained above, according to the indoor unit 50 of the air conditioner in the fifth embodiment, the number of rows of the heat transfer tube groups in the first heat exchanger group is equal to the row of the heat transfer tube groups in the second heat exchanger group. More than the number. Therefore, it is possible to increase the heat exchangeable surface area by the number of rows increased. As a result, the heat transfer rate can be further improved.

  Even if the number of rows is increased, the width of the fins for one row of the heat transfer tube group in the first heat exchanger group is made smaller than the width of the fins for one row of the heat transfer tube group in the second heat exchanger group. ing. Therefore, even if the number of rows is increased, the ventilation resistance is not greatly deteriorated. As a result, the indoor unit 50 of the air conditioner can achieve higher performance.

(Embodiment 6)
FIG. 7 is a side view showing an indoor unit of an air conditioner according to Embodiment 6 of the present invention. With reference to FIG. 7, the indoor unit of the air conditioner by Embodiment 6 is demonstrated. Referring to FIG. 7, the configuration of air conditioner indoor unit 60 according to the sixth embodiment is basically the same as that of the fifth embodiment of the present invention shown in FIG. It differs in the point which has provided the part 66a and the refrigerant | coolant outflow part 66b at the time of heating in all the heat exchangers 11a and 11b which comprise the 1st heat exchanger group.

  Specifically, in the refrigerant flow path 37c, when the refrigerant flows into the first heat exchanger group or flows out of the first heat exchanger group, the heat exchanger 11a constituting the first heat exchanger group. , 11b from both sides. That is, the cooling operation refrigerant inflow portion 66a and the heating operation refrigerant outflow portion 66b are provided in both of the heat exchangers 11a and 11b constituting the first heat exchanger group.

  Next, an operation method of the indoor unit 60 of the air conditioner will be described. Since it is basically the same during the heating operation, the cooling operation, and the reheat dehumidification operation, the same description will not be repeated, and the state of the refrigerant during the heating operation, which is a different point, will be described.

  During the heating operation, high-temperature and high-pressure refrigerant flows from the heat exchanger 11c having a large diameter of the heat transfer tube group from the heating refrigerant inflow portion 37b. By exchanging heat with the air through the fin group 12c, the refrigerant condenses and condenses, and merges at the outlet portions of the heat exchangers 11a and 11b where the tube diameter of the heat transfer tube group is small, and flows out from the refrigerant outflow portion 66b during heating. To do.

  At that time, in the heat exchangers 11a and 11b in the latter half of the flow path 37c, the refrigerant is liquefied and the temperature of the refrigerant is lowered. In the supercooling region, which is a region where the refrigerant is liquefied, the flow velocity is decreased and the heat transfer coefficient is also decreased.

  However, in the indoor unit 60 of the air conditioner, since the heating refrigerant outflow portion 66b is provided at the ends of the heat transfer tube groups 13a and 13b of both the heat exchangers 11a and 11b, the supercooling region is the heat exchanger 11a. , 11b, a row of heat transfer tube groups 67a and 67b in the vicinity of the refrigerant outlet portion 66b for heating. Therefore, even if a supercooling zone exists during heating operation, the two rows close to the blowers of the heat exchangers 11a and 11b do not become supercooling zones. Thus, a significant decrease in heat exchange efficiency can be suppressed.

  As described above, according to the indoor unit 60 of the air conditioner in the fifth embodiment, during the heating operation, all the heat exchangers constituting the first heat exchanger group are provided with the heating refrigerant outflow portion. Yes. Therefore, the supercooling region is not increased and the heat transfer coefficient of the entire heat exchanger is improved. As a result, the indoor unit of a higher performance air conditioner can be obtained.

(Embodiment 7)
FIG. 8 is a side view showing an indoor unit of an air conditioner according to Embodiment 7 of the present invention. With reference to FIG. 8, the indoor unit of the air conditioner by Embodiment 7 is demonstrated. Referring to FIG. 8, the configuration of air conditioner indoor unit 70 according to the seventh embodiment is basically the same as that of the sixth embodiment of the present invention shown in FIG. The difference is that the refrigerant flow paths in the heat transfer tube groups 13a and 13b of the heat exchangers 11a and 11b constituting the group include flow path portions connected in parallel in two rows.

  Specifically, in the heat exchangers 11a and 11b, the refrigerant flow paths 37c have paths that branch and merge. Therefore, the first heat exchanger group has flow path portions connected in parallel in two rows in each of the heat exchangers 11a and 11b. In other words, the refrigerant flow paths in the heat transfer tube groups 13a and 13b of the heat exchangers 11a and 11b constituting the first heat exchanger group have flow path portions connected in parallel in four rows. In addition, it is the same as that of Embodiment 6 in the point that the flow path of the refrigerant | coolant in the heat exchanger tube group 13c of the heat exchanger 11c which comprises a 2nd heat exchanger group is connected in parallel with 2 rows.

  Further, the tube diameters of the heat transfer tube groups 13a and 13b constituting the first heat exchanger group are 4 mm or more and 6 mm or less, and the tube diameter of the heat transfer tube group 13c constituting the second heat exchanger group is 7 mm or more and 13 mm or less. . This is because if the tube diameters of the heat transfer tube groups 13a and 13b are smaller than 4 mm, problems such as clogging during brazing work will occur, and the thickness of the heat transfer tube group will decrease, resulting in problems with pressure resistance. On the other hand, if the tube diameter of the heat transfer tube group 13c is larger than 13 mm, it is restricted by the size of the heat exchangers 11a and 11b that can be mounted in the indoor unit 70 of the air conditioner.

  Next, an operation method of the indoor unit 70 of the air conditioner will be described. With reference to FIG. 8, the air blower 14 is operated to send air into the heat exchangers 11a, 11b, and 11c.

  During the heating operation, high-temperature and high-pressure gaseous refrigerant flows from the heating refrigerant inflow portion 37b into the heat exchanger 11c having a large diameter of the heat transfer tube group, and exchanges heat with air through the flow path 37c. Thereafter, in the heat exchangers 11a and 11b having the thin tube diameters of the heat transfer tube group, the refrigerant changes from the gas-liquid two-phase state to the liquid one-phase state, and flows out as low-temperature and high-pressure liquid refrigerant from the heating refrigerant outflow portion 66b. The

  At that time, as described above, in the supercooling region where the refrigerant is liquefied, the flow velocity is reduced, and the heat transfer coefficient in the heat transfer tube group is also reduced.

  However, in the indoor unit 70 of the air conditioner, the total number of channels in the portions close to the outlets of the heat exchangers 11a and 11b where the tube diameter of the heat transfer tube group is small decreases from 4 channels to 2 channels. Therefore, it is possible to suppress a decrease in the flow rate of the refrigerant in the supercooling region, and it is possible to improve the heat transfer coefficient in the heat transfer tube group.

  On the other hand, during the cooling operation, the low-temperature and low-pressure refrigerant in the two-phase state flows from the cooling refrigerant inflow portion 66a into the heat exchangers 11a and 11b having a small diameter of the heat transfer tube group, respectively, and air flows through the fins 12a and 12b. And heat exchange. When heat exchange is performed, the refrigerant gradually evaporates and flows into the heat exchanger 11c having a large pipe diameter, and the refrigerant whose dryness has progressed is discharged from the cooling refrigerant outflow portion 37a.

  At that time, when the vaporization of the refrigerant proceeds, the pressure loss in the heat transfer tube group is increased by the gas component in the refrigerant, and the circulation amount of the refrigerant is decreased.

  However, in the indoor unit 70 of the air conditioner, the number of channels in the heat exchangers 11a and 11b having a small diameter of the heat transfer tube group is expanded to a total of 4 channels with 2 channels each. Therefore, it is possible to suppress an increase in pressure loss due to the vaporization of the refrigerant in the heat exchangers 11a and 11b. As a result, it is possible to suppress a decrease in the refrigerant circulation amount during cooling, and the cooling capacity can be improved.

  As described above, according to the indoor unit 70 of the air conditioner in the seventh embodiment, the flow path of the refrigerant in the heat transfer tube group of the heat exchanger constituting the first heat exchanger group is in the range of 2 to 4 rows. The flow path portions are connected in parallel to the two rows, and the flow paths of the refrigerant in the heat transfer tube group constituting the second heat exchanger group have the flow path portions connected in parallel to the two rows. is doing. Therefore, in any operation, it becomes possible to further improve the heat transfer coefficient of the entire heat exchanger. As a result, the indoor unit of a higher performance air conditioner can be obtained.

(Embodiment 8)
FIG. 9 is a side view showing an indoor unit of an air conditioner according to Embodiment 8 of the present invention. With reference to FIG. 9, the indoor unit of the air conditioner by Embodiment 8 is demonstrated. Referring to FIG. 9, the configuration of indoor unit 80 of the air conditioner according to the eighth embodiment is basically the same as that of the seventh embodiment of the present invention shown in FIG. The difference is that the flow path configurations of the heat exchangers 11a and 11b constituting the first heat exchanger group having a small diameter and the arrangement of the bends are unified.

  The channel configuration means the channel 37c through which the refrigerant in the heat exchangers 11a and 11b flows. Specifically, the flow path 37c through which the refrigerant flows in the heat exchangers 11a and 11b is substantially the same in that it is branched into two flow paths and merged into one flow path, and the flow paths are also substantially the same.

  Next, since the operation method of the indoor unit 70 of the air conditioner is the same as that of the indoor unit 60 of the air conditioner in Embodiment 6, the description thereof will not be repeated.

  As described above, according to the indoor unit 70 of the air conditioner in the eighth embodiment, the flow path configuration in which the refrigerant flows is substantially the same in all of the heat exchangers constituting the first heat exchanger group. . Therefore, it is possible to produce the heat exchangers 11a and 11b in the same manner, and it is possible to prevent confusion or mistakes during production. As a result, it is possible to improve production efficiency.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above-described embodiment but by the scope of claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of claims.

It is a side view which shows the indoor unit of the air conditioner in Embodiment 1 of this invention. It is a side view which shows the indoor unit of the sky level conditioner in Embodiment 2 of this invention. It is a side view which shows the indoor unit of the air conditioner in Embodiment 3 of this invention. It is a side view which shows the indoor unit of the air conditioner in Embodiment 4 of this invention. It is a side view which shows the indoor unit of the air conditioner in the modification of Embodiment 4. It is a side view which shows the indoor unit of the air conditioner in Embodiment 5 of this invention. It is a side view which shows the indoor unit of the air conditioner in Embodiment 6 of this invention. It is a side view which shows the indoor unit of the air conditioner in Embodiment 7 of this invention. It is a side view which shows the indoor unit of the air conditioner in Embodiment 8 of this invention. It is a schematic side view which shows the indoor unit of the air conditioner disclosed by patent document 1. FIG. It is sectional drawing at the time of the air conditioner built-in of the heat exchanger of the air conditioner disclosed by patent document 2. FIG.

Explanation of symbols

  10 air conditioner indoor units, 11a heat exchanger, 11b heat exchanger, 11c heat exchanger, 12a fin group, 12b fin group, 12c fin group, 13a heat transfer tube group, 13b heat transfer tube group, 13c heat transfer tube group, 14 Blower, 15a Air volume, 15b Air volume, 15c Air volume, 20 Air conditioner indoor unit, 30 Air conditioner indoor unit, 36a Cooling refrigerant inflow part, 36b Heating refrigerant outflow part, 37a Cooling refrigerant outflow part, 37b Refrigerant inflow part during heating, 37c flow path, 40 indoor unit of air conditioner, 48 throttle means, 50 indoor unit of air conditioner, 60 indoor unit of air conditioner, 66a refrigerant inflow part during cooling, 66b refrigerant outflow during heating Part, 67a heat transfer tube group, 70 indoor unit of air conditioner, 80 indoor unit of air conditioner.

Claims (14)

A blower,
A fin group disposed around the blower and spaced apart from each other; and at least three heat exchangers having a heat transfer tube group connected to the fin group and in which a refrigerant flows;
The tube diameter of each of the heat transfer tube groups that each of the heat exchangers has is substantially the same for each heat exchanger,
The at least three heat exchangers are:
A first heat exchanger group comprising at least two heat exchangers;
An air constituted by a second heat exchanger group including a heat exchanger including the heat transfer tube group having a tube diameter larger than that of the heat transfer tube group in the heat exchanger of the first heat exchanger group. The indoor unit of the harmony machine.   The indoor unit of the air conditioner of Claim 1 which has arrange | positioned the at least 1 said heat exchanger which comprises a said 2nd heat exchanger group in the front part nearest to the said air blower.   The refrigerant flows from the heat exchanger constituting the second heat exchanger group to the heat exchanger constituting the first heat exchanger group during the heating operation. The indoor unit of the air conditioner described in 1. The first heat exchanger group includes the heat exchangers having different diameters of the heat transfer tube groups,
The refrigerant flowed from the second heat exchanger group during heating operation is caused to flow sequentially from the heat exchanger having a relatively large diameter of the heat transfer tube group in the first heat exchanger group. The indoor unit of the air conditioner according to claim 3.   The air conditioner according to any one of claims 1 to 4, wherein a throttle means is provided in a flow path of a refrigerant connecting the first heat exchanger group and the second heat exchanger group. Indoor unit.   6. The air conditioner according to claim 5, wherein during the dehumidifying operation, the refrigerant is caused to flow such that the first heat exchanger group functions as a condensing unit and the second heat exchanger group functions as an evaporating unit. Indoor unit.   During cooling operation, at least one of the heat exchangers constituting the first heat exchanger group is provided with a cooling refrigerant inflow portion, and at least one of the heat exchangers constituting the second heat exchanger group The air conditioner indoor unit according to any one of claims 1 to 6, wherein a cooling refrigerant outflow part is provided in the air conditioner. The heat transfer tube group penetrates the fin group, and the penetration position of the heat transfer tube group on the main surface of the fin group through which the heat transfer tube group penetrates is arranged to form one or more rows aligned in a certain direction. And
The width in the direction perpendicular to the extending direction of the rows on the main surface of the fin group is a value obtained by dividing the width by the number of rows as the width of the fins for one row of the heat transfer tube group,
The width of the fins for one row of the heat transfer tube group in the first heat exchanger group is smaller than the width of the fins for one row of the heat transfer tube group in the second heat exchanger group, The indoor unit of the air conditioner in any one of Claims 1-7.   The number of the rows of the heat transfer tube groups of the first heat exchanger group is greater than the number of the rows of the heat transfer tube groups of the second heat exchanger group. Air conditioner indoor unit. The heat transfer tube group penetrates through the fin group, and the penetration positions of the heat transfer tube groups on the main surface of the fin group through which the heat transfer tube group penetrates form one or more rows aligned in a certain direction. Placed in
The number of the rows of the heat transfer tube groups of the first heat exchanger group is greater than the number of the rows of the heat transfer tube groups of the second heat exchanger group. An air conditioner indoor unit according to any one of the above.   The air conditioner according to any one of claims 1 to 10, wherein a heating refrigerant outflow portion is provided in all of the heat exchangers constituting the first heat exchanger group during heating operation. Indoor unit.   The tube diameter of the heat transfer tube group constituting the first heat exchanger group is 4 mm or more and 6 mm or less, and the tube diameter of the heat transfer tube group constituting the second heat exchanger group is 7 mm or more and 13 mm or less. The indoor unit of an air conditioner according to any one of claims 1 to 11, wherein the indoor unit is an air conditioner. The flow path of the refrigerant in the heat transfer tube group of the heat exchanger constituting the first heat exchanger group has a flow path portion connected in parallel in 2 rows to 4 rows,
The flow path of the refrigerant in the heat transfer tube group of the heat exchanger constituting the second heat exchanger group includes a flow path portion connected in parallel in two rows. The indoor unit of the air conditioner in any one of -12.   The air conditioner according to any one of claims 1 to 13, wherein all of the heat exchangers constituting the first heat exchanger group have substantially the same flow path configuration in which the refrigerant flows. Indoor unit.

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